Dynamic and static pressure sliding bearing with tilted shaft journal

Abstract

The present disclosure provides a dynamic and static pressure sliding bearing suitable for shaft neck inclination, comprising: a shaft sleeve; a plurality of oil grooves arranged in sequence on the inner wall of the shaft sleeve along the circumference of the shaft sleeve, the oil groove comprising: a first groove and a second groove, the first groove and the second groove are distributed along the circumference of the shaft sleeve, and the first groove is connected with the second groove, the cross-sectional area of the first groove along the radial direction of the shaft sleeve is larger than the cross-sectional area of the second groove along the radial direction of the shaft sleeve, an oil inlet hole is arranged in the first groove, and an oil outlet hole is arranged in the second groove. In the dynamic and static pressure sliding bearing suitable for shaft neck inclination, when the shaft neck in the shaft sleeve is inclined, the oil film with larger pressure can support the shaft neck, thereby offsetting the inclination force on the shaft neck, avoiding the reduction of the thickness of the oil film, and further ensuring the stable lubrication of the oil film to the shaft sleeve, avoiding the problem of excessive wear of the bearing. Therefore, not only the normal operation of the bearing is ensured, but also the service life of the bearing is prolonged.

Description

Technical Field

[0001] This disclosure relates to the field of hydrostatic sliding bearing technology, and more particularly to a hydrostatic sliding bearing suitable for journal tilting. Background Technology

[0002] Hydrostatic sliding bearings are one of the commonly used bearing types in mechanical equipment. During use, hydrostatic sliding bearings are prone to journal misalignment due to manufacturing and installation errors and eccentric loads. Furthermore, due to insufficient load-bearing capacity of the oil film on the inner wall of the bushing, the thickness of the oil film on the inner wall of the bushing is reduced, which leads to excessive wear of the hydrostatic sliding bearing. This not only affects the normal operation of the hydrostatic sliding bearing, but also shortens its lifespan. Summary of the Invention

[0003] This disclosure aims to at least partially address one of the technical problems in the related art.

[0004] Therefore, the purpose of this disclosure is to provide a hydrostatic sliding bearing suitable for journal tilting.

[0005] To achieve the above objectives, this disclosure provides a hydrostatic sliding bearing suitable for journal tilting, comprising: a bushing; and a plurality of oil grooves, wherein the plurality of oil grooves are sequentially arranged on the inner wall of the bushing along the circumference of the bushing, and each oil groove includes: a first groove and a second groove, the first groove and the second groove being distributed along the circumference of the bushing, and the first groove being connected to the second groove, the cross-sectional area of ​​the first groove along the radial direction of the bushing being greater than the cross-sectional area of ​​the second groove along the radial direction of the bushing, an oil inlet hole being provided in the first groove, and an oil outlet hole being provided in the second groove.

[0006] Optionally, the hydrostatic sliding bearing includes: a first groove group, the first groove group including: a plurality of oil grooves, the plurality of oil grooves of the first groove group being evenly distributed along the circumference of the bushing; a second groove group, the second groove group including: a plurality of oil grooves, the plurality of oil grooves of the second groove group being evenly distributed along the circumference of the bushing; wherein, the first groove group and the second groove group are arranged sequentially along the axial direction of the bushing, and the plurality of oil grooves of the first groove group and the plurality of oil grooves of the second groove group are staggered along the circumference of the bushing.

[0007] Optionally, the first groove group includes: a first oil groove, a second oil groove, and a third oil groove, the first oil groove, the second oil groove, and the third oil groove being evenly distributed along the circumference of the bushing; the second groove group includes: a fourth oil groove, a fifth oil groove, and a sixth oil groove, the fourth oil groove, the fifth oil groove, and the sixth oil groove being evenly distributed along the circumference of the bushing; wherein, the projections of the first oil groove, the second oil groove, and the third oil groove along the axial direction of the bushing do not overlap with the projections of the fourth oil groove, the fifth oil groove, and the sixth oil groove along the axial direction of the bushing.

[0008] Optionally, the projections of the first oil groove along the axial direction of the bushing, the fourth oil groove along the axial direction of the bushing, the second oil groove along the axial direction of the bushing, the fifth oil groove along the axial direction of the bushing, the third oil groove along the axial direction of the bushing, and the sixth oil groove along the axial direction of the bushing are sequentially connected along the circumference of the bushing.

[0009] Optionally, the length of the first groove along the axial direction of the bushing is equal to the length of the second groove along the axial direction of the bushing, and the depth of the first groove along the radial direction of the bushing is greater than the depth of the second groove along the radial direction of the bushing.

[0010] Optionally, the depth of the second groove along the radial direction of the bushing is less than half the depth of the first groove along the radial direction of the bushing.

[0011] Optionally, the width of the first groove along the circumference of the bushing is smaller than the width of the second groove along the circumference of the bushing.

[0012] Optionally, the oil inlet is located in the middle of the bottom of the first groove, and the oil outlet is located in the middle of the bottom of the second groove.

[0013] The technical solution provided in this disclosure may include the following beneficial effects:

[0014] Because the cross-sectional area of ​​the first groove along the radial direction of the bushing is larger than that of the second groove along the radial direction of the bushing, the flow rate of lubricating oil in the first groove decreases and the pressure increases when it enters the second groove. This increases the load-bearing capacity of the oil film. When the journal inside the bushing is misaligned, the higher-pressure oil film can support the journal, thereby counteracting the misalignment force on the journal and preventing a decrease in the oil film thickness. This ensures stable lubrication of the bushing by the oil film and avoids excessive wear of the bearing. As a result, not only is normal operation of the bearing guaranteed, but the bearing life is also extended.

[0015] Additional aspects and advantages of this disclosure will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this disclosure. Attached Figure Description

[0016] The above and / or additional aspects and advantages of this disclosure will become apparent and readily understood from the following description of the embodiments taken in conjunction with the accompanying drawings, in which:

[0017] Figure 1 This is a cross-sectional schematic diagram of a hydrostatic sliding bearing suitable for journal tilting according to an embodiment of the present disclosure;

[0018] Figure 2 This is a cross-sectional schematic diagram of a hydrostatic sliding bearing suitable for journal tilting according to an embodiment of the present disclosure;

[0019] As shown in the figure: 1. Bushing;

[0020] 2. Oil groove; 21. First groove; 22. Second groove; 23. Oil inlet hole;

[0021] 3. First oil tank group; 31. First oil tank; 32. Second oil tank; 33. Third oil tank;

[0022] 4. Second oil tank group, 41. Fourth oil tank, 42. Fifth oil tank, 43. Sixth oil tank. Detailed Implementation

[0023] Embodiments of this disclosure are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are used only to explain this disclosure, and should not be construed as limiting this disclosure. Rather, embodiments of this disclosure include all variations, modifications, and equivalents falling within the spirit and scope of the appended claims.

[0024] like Figure 1 As shown in the figure, this disclosure proposes a hydrostatic sliding bearing suitable for journal tilting, including a bushing 1 and multiple oil grooves 2. The multiple oil grooves 2 are sequentially arranged on the inner wall of the bushing 1 along the circumference. The oil grooves 2 include a first groove 21 and a second groove 22. The first groove 21 and the second groove 22 are distributed along the circumference of the bushing 1, and the first groove 21 is connected to the second groove 22. The cross-sectional area of ​​the first groove 21 along the radial direction of the bushing 1 is larger than the cross-sectional area of ​​the second groove 22 along the radial direction of the bushing 1. An oil inlet hole 23 is provided in the first groove 21, and an oil outlet hole (not shown in the figure) is provided in the second groove 22.

[0025] Understandably, the lubricating oil enters the first groove 21 from the oil inlet 23, the lubricating oil in the first groove 21 enters the second groove 22 and is discharged from the oil outlet. At the same time, the lubricating oil in the oil groove 2 also enters the inner wall of the bushing 1 to form an oil film on the inner wall of the bushing 1, thereby meeting the lubrication requirements.

[0026] Because the cross-sectional area of ​​the first groove 21 along the radial direction of the bushing 1 is larger than that of the second groove 22 along the radial direction of the bushing 1, the flow rate of the lubricating oil in the first groove 21 decreases and the pressure increases when it enters the second groove 22. This increases the load-bearing capacity of the oil film. When the journal in the bushing 1 is misaligned, the oil film with higher pressure can support the journal, thereby counteracting the misalignment force on the journal and preventing the oil film thickness from decreasing. This ensures stable lubrication of the bushing 1 by the oil film and avoids excessive wear of the bearing. As a result, not only is the normal operation of the bearing guaranteed, but the bearing life is also extended.

[0027] It should be noted that when the journal is misaligned, the clearance between one side of the journal and the bushing 1 decreases, while the clearance between the other side of the journal and the bushing 1 increases. This results in a decrease in the oil film thickness on one side of the journal and an increase in the oil film thickness on the other side of the journal, which in turn creates a pressure difference between the oil films on both sides of the journal. However, this pressure difference is small and cannot offset the large load on the journal. Therefore, by setting the oil groove 2, the pressure difference between the two sides of the journal is increased, thereby satisfying the offsetting of the large load on the journal and ensuring the stable operation of the bearing.

[0028] Since multiple oil grooves 2 are arranged sequentially on the inner wall of the bushing 1 along the circumference of the bushing 1, the bushing 1 can use the oil groove structure on it to counteract the misalignment force of the bushing 1 by using the oil film pressure to ensure the stable operation of the bearing, no matter which direction the journal is misaligned.

[0029] The flow rate and pressure of lubricating oil are negatively correlated; that is, the greater the flow rate of lubricating oil, the lower the pressure, and vice versa.

[0030] Among them, bushing 1 is the part of the bearing that contacts the journal. The specific type of bushing 1 can be set according to actual needs and is not limited thereto. For example, bushing 1 may include two bearing shells. The inner wall of the bearing shell is a smooth semi-cylindrical surface in the shape of a tile. The two bearing shells are combined to form bushing 1 with a smooth cylindrical surface on the inner wall. Bushing 1 is fitted on the journal, and an oil film for lubrication is formed between the journal and bushing 1.

[0031] Journal misalignment refers to the misalignment of the central axis of the journal with the central axis of the bushing 1. Journal misalignment can be caused by the bearing material, bearing manufacturing process, bearing installation error, load on the journal, etc.

[0032] The number of oil tanks 2 and the relative positions between multiple oil tanks 2 can be set according to actual needs, and there are no restrictions on this.

[0033] like Figure 1 and Figure 2As shown, in some embodiments, the hydrostatic sliding bearing includes a first groove group 3 and a second groove group 4. The first groove group 3 includes a plurality of oil grooves 2, which are evenly distributed along the circumference of the bushing 1. The second groove group 4 includes a plurality of oil grooves 2, which are evenly distributed along the circumference of the bushing 1. The first groove group 3 and the second groove group 4 are arranged sequentially along the axial direction of the bushing 1, and the plurality of oil grooves 2 of the first groove group 3 and the plurality of oil grooves 2 of the second groove group 4 are staggered along the circumference of the bushing 1.

[0034] It is understandable that, since the multiple oil grooves 2 of the first groove group 3 are evenly distributed along the circumference of the bushing 1, and the multiple oil grooves 2 of the second groove group 4 are evenly distributed along the circumference of the bushing 1, and the multiple oil grooves 2 of the first groove group 3 and the multiple oil grooves 2 of the second groove group 4 are staggered along the circumference of the bushing 1, multiple oil grooves 2 are evenly distributed along the circumference of the inner wall of the bushing 1. This allows the bushing to achieve a uniform distribution of oil film thickness and pressure using multiple oil grooves 2, thereby ensuring the stable operation of the bearing.

[0035] In this design, the multiple oil grooves 2 of the first groove group 3 and the multiple oil grooves 2 of the second groove group 4 are staggered along the circumference of the bushing 1, so that the areas between the oil grooves 2 in the first groove group 3 and the adjacent oil grooves 2 in the second groove group 4 are adjacent. This allows the lubricating oil in the oil grooves 2 in the first groove group 3 to enter the area between the adjacent oil grooves 2 in the second groove group 4, thereby forming an oil film on the inner wall of the bushing 1 to meet the lubrication requirements. At the same time, since the oil grooves 2 have a certain depth relative to the area between the adjacent oil grooves 2, when the lubricating oil in the oil grooves 2 in the first groove group 3 enters the area between the adjacent oil grooves 2 in the second groove group 4, the flow rate of the lubricating oil decreases and the pressure increases, thereby further increasing the pressure of the oil film and improving the load-bearing capacity of the oil film.

[0036] Similarly, since the multiple oil grooves 2 of the first groove group 3 and the multiple oil grooves 2 of the second groove group 4 are staggered along the circumference of the bushing 1, the areas between the oil grooves 2 in the second groove group 4 and the adjacent oil grooves 2 in the first groove group 3 are arranged adjacently. This allows the lubricating oil in the oil grooves 2 in the second groove group 4 to enter the area between the adjacent oil grooves 2 in the first groove group 3, thereby forming an oil film on the inner wall of the bushing 1 to meet the lubrication requirements. At the same time, since the oil grooves 2 have a certain depth relative to the area between the adjacent oil grooves 2, when the lubricating oil in the oil grooves 2 in the second groove group 4 enters the area between the adjacent oil grooves 2 in the first groove group 3, the flow rate of the lubricating oil decreases and the pressure increases, thereby further increasing the pressure of the oil film and improving the load-bearing capacity of the oil film.

[0037] Therefore, when the journal inside bushing 1 is misaligned, the oil film with higher pressure can support the journal, thereby counteracting the misalignment force on the journal, preventing the oil film thickness from decreasing, and thus ensuring stable lubrication of bushing 1 by the oil film, avoiding excessive wear of the bearing. This not only ensures the normal operation of the bearing, but also extends the bearing's life.

[0038] It should be noted that the lubricating oil in the oil groove 2 of the first groove group 3 can not only enter the area between adjacent oil grooves 2 in the second groove group 4, but also enter other areas of the inner wall of the bushing 1. The lubricating oil in the oil groove 2 of the second groove group 4 can not only enter the area between adjacent oil grooves 2 in the first groove group 3, but also enter other areas of the inner wall of the bushing 1. This ensures the stable formation of the oil film on the inner wall of the bushing 1, and also increases the pressure of the oil film in other areas.

[0039] like Figure 2 As shown, in some embodiments, the first groove group 3 includes a first oil groove 31, a second oil groove 322, and a third oil groove 332, which are evenly distributed along the circumference of the bushing 1; the second groove group 4 includes a fourth oil groove 412, a fifth oil groove 422, and a sixth oil groove 432, which are evenly distributed along the circumference of the bushing 1. The projections of the first oil groove 31, the second oil groove 322, and the third oil groove 332 along the axial direction of the bushing 1 do not overlap with the projections of the fourth oil groove 412, the fifth oil groove 422, and the sixth oil groove 432 along the axial direction of the bushing 1.

[0040] It is understandable that, since the first oil groove 31, the second oil groove 322, and the third oil groove 332 are evenly distributed along the circumference of the bushing 1, and the fourth oil groove 412, the fifth oil groove 422, and the sixth oil groove 432 are also evenly distributed along the circumference of the bushing 1, and the projections of the first oil groove 31, the second oil groove 322, and the third oil groove 332 along the axial direction of the bushing 1 do not overlap with the projections of the fourth oil groove 412, the fifth oil groove 422, and the sixth oil groove 432 along the axial direction of the bushing 1, the first oil groove 31, the fourth oil groove 412, the second oil groove 322, the fifth oil groove 422, the third oil groove 332, and the sixth oil groove 432 are evenly distributed along the circumference of the inner wall of the bushing 1, thereby enabling the bushing to achieve a uniform distribution of oil film thickness and pressure using the first oil groove 31, the fourth oil groove 412, the second oil groove 322, the fifth oil groove 422, the third oil groove 332, and the sixth oil groove 432, thus ensuring the stable operation of the bearing.

[0041] Since the projections of the first oil groove 31, the second oil groove 322, and the third oil groove 332 along the axial direction of the bushing 1 do not overlap with the projections of the fourth oil groove 412, the fifth oil groove 422, and the sixth oil groove 432 along the axial direction of the bushing 1, the areas between the first oil groove 31 and the fourth oil groove 412 and the fifth oil groove 422 are adjacent, the areas between the second oil groove 322 and the fifth oil groove 422 and the sixth oil groove 432 are adjacent, and the areas between the third oil groove 332 and the sixth oil groove 432 and the fourth oil groove 412 are adjacent, the lubricating oil in the first oil groove 31 can enter the area between the fourth oil groove 412 and the fifth oil groove 422, the lubricating oil in the second oil groove 322 can enter the area between the fifth oil groove 422 and the sixth oil groove 432, and the lubricating oil in the third oil groove 332 can enter the area between the sixth oil groove 432 and the fourth oil groove 412. The area between the grooves 412 allows an oil film to form on the inner wall of the bushing 1, satisfying lubrication requirements. Simultaneously, since the first oil groove 31, the second oil groove 322, and the third oil groove 332 have a certain depth relative to the areas between the fourth and fifth oil grooves 412 and 422, and between the sixth oil groove 432 and the fourth oil groove 412, the flow rate of the lubricating oil decreases and the pressure increases when the lubricating oil in the first oil groove 31 enters the area between the fourth and fifth oil grooves 422, the lubricating oil in the second oil groove 322 enters the area between the fifth and sixth oil grooves 422, and the lubricating oil in the third oil groove 332 enters the area between the sixth oil groove 432 and the fourth oil groove 412. This further increases the pressure of the oil film and improves its load-bearing capacity.

[0042] Similarly, since the projections of the first oil groove 31, the second oil groove 322, and the third oil groove 332 along the axial direction of the bushing 1 do not overlap with the projections of the fourth oil groove 412, the fifth oil groove 422, and the sixth oil groove 432 along the axial direction of the bushing 1, the areas between the fourth oil groove 412 and the third oil groove 332 and the first oil groove 31 are adjacent, the areas between the fifth oil groove 422 and the first oil groove 31 and the second oil groove 322 are adjacent, and the areas between the sixth oil groove 432 and the second oil groove 322 and the third oil groove 332 are adjacent. This allows the lubricating oil in the fourth oil groove 412 to enter the area between the third oil groove 332 and the first oil groove 31, the lubricating oil in the fifth oil groove 422 to enter the area between the first oil groove 31 and the second oil groove 322, and the lubricating oil in the sixth oil groove 432 to enter the area between the second oil groove 322 and the third oil groove 332. This, in turn, forms an oil film on the inner wall of the bushing 1, satisfying the lubrication requirements.

[0043] Meanwhile, since the fourth oil groove 412, the fifth oil groove 422, and the sixth oil groove 432 have a certain depth relative to the areas between the third oil groove 332 and the first oil groove 31, the first oil groove 31 and the second oil groove 322, and the second oil groove 322 and the third oil groove 332, when the lubricating oil in the fourth oil groove 412 enters the area between the third oil groove 332 and the first oil groove 31, the lubricating oil in the fifth oil groove 422 enters the area between the first oil groove 31 and the second oil groove 322, and the lubricating oil in the sixth oil groove 432 enters the area between the second oil groove 322 and the third oil groove 332, the flow rate of the lubricating oil decreases and the pressure increases, thereby further increasing the pressure of the oil film and improving the carrying capacity of the oil film.

[0044] Therefore, when the journal inside bushing 1 is misaligned, the oil film with higher pressure can support the journal, thereby counteracting the misalignment force on the journal, preventing the oil film thickness from decreasing, and thus ensuring stable lubrication of bushing 1 by the oil film, avoiding excessive wear of the bearing. This not only ensures the normal operation of the bearing, but also extends the bearing's life.

[0045] Among them, since the first oil groove 31, the fourth oil groove 412, the second oil groove 322, the fifth oil groove 422, the third oil groove 332 and the sixth oil groove 432 are evenly distributed in the circumferential direction on the inner wall of the bushing 1, the bushing 1 can use the oil groove 2 structure on it to make the oil film pressure counteract the misalignment force of the journal when the journal is misaligned in any direction, thus ensuring the stable operation of the bearing.

[0046] It should be noted that the implementation method of making the radial cross-sectional area of ​​the first groove 21 along the bushing 1 greater than the radial cross-sectional area of ​​the second groove 22 along the bushing 1 can be set according to actual needs and is not limited thereto. For example, the radial depth of the first groove 21 along the bushing 1 can be equal to the radial depth of the second groove 22 along the bushing 1, and the axial length of the first groove 21 along the bushing 1 can be greater than the axial length of the second groove 22 along the bushing 1; or the axial length of the first groove 21 along the bushing 1 can be equal to the axial length of the second groove 22 along the bushing 1, and the radial depth of the first groove 21 along the bushing 1 can be greater than the radial depth of the second groove 22 along the bushing 1.

[0047] like Figure 1 and Figure 2 As shown, in some embodiments, the length of the first groove 21 along the axial direction of the bushing 1 is equal to the length of the second groove 22 along the axial direction of the bushing 1, and the depth of the first groove 21 along the radial direction of the bushing 1 is greater than the depth of the second groove 22 along the radial direction of the bushing 1.

[0048] Understandably, since the length of the first groove 21 along the axial direction of the bushing 1 is equal to the length of the second groove 22 along the axial direction of the bushing 1, and the depth of the first groove 21 along the radial direction of the bushing 1 is greater than the depth of the second groove 22 along the radial direction of the bushing 1, the cross-sectional area of ​​the first groove 21 along the radial direction of the bushing 1 is greater than the cross-sectional area of ​​the second groove 22 along the radial direction of the bushing 1. This allows the flow rate of lubricating oil in the first groove 21 to decrease when entering the second groove 22, thereby increasing the pressure and effectively improving the load-bearing capacity of the oil film. When the journal in the bushing 1 is misaligned, the higher pressure oil film can support the journal, thereby counteracting the misalignment force on the journal and preventing the reduction of the oil film thickness. This ensures stable lubrication of the bushing 1 by the oil film and avoids excessive wear of the bearing. Thus, it not only ensures the normal operation of the bearing but also extends the bearing's life.

[0049] It should be noted that the specific length of the first groove 21 along the axial direction of the bushing 1 and the specific length of the second groove 22 along the axial direction of the bushing 1 can be set according to actual needs, and there is no limitation on this.

[0050] The specific depth of the first groove 21 along the radial direction of the bushing 1 and the specific depth of the second groove 22 along the radial direction of the bushing 1 can be set according to actual needs, and there is no limitation thereto.

[0051] like Figure 2 As shown, in some embodiments, the depth of the second groove 22 along the radial direction of the bushing 1 is less than half the depth of the first groove 21 along the radial direction of the bushing 1.

[0052] It is understandable that, since the length of the first groove 21 along the axial direction of the bushing 1 is equal to the length of the second groove 22 along the axial direction of the bushing 1, and the depth of the second groove 22 along the radial direction of the bushing 1 is less than half the depth of the first groove 21 along the radial direction of the bushing 1, the cross-sectional area of ​​the first groove 21 along the radial direction of the bushing 1 is larger than the cross-sectional area of ​​the second groove 22 along the radial direction of the bushing 1. As a result, when the lubricating oil in the first groove 21 enters the second groove 22, the flow rate can be greatly reduced and the pressure can be greatly increased. This effectively improves the load-bearing capacity of the oil film, ensures that the oil film can counteract the large misalignment force on the journal, and makes the bearing more adaptable and more stable.

[0053] like Figure 1 and Figure 2 As shown, in some embodiments, the width of the first groove 21 along the circumference of the bushing 1 is smaller than the width of the second groove 22 along the circumference of the bushing 1.

[0054] It is understandable that, since the width of the first groove 21 along the circumference of the bushing 1 is smaller than the width of the second groove 22 along the circumference of the bushing 1, the second groove 22 can occupy a larger area on the inner wall of the bushing 1, ensuring that the high-pressure lubricating oil in the second groove 22 has a larger contact area with the journal, thereby effectively improving the support force of the pressure oil film on the journal and ensuring the stable operation of the bearing.

[0055] It should be noted that the specific width of the first groove 21 along the circumference of the bushing 1 and the specific width of the second groove 22 along the circumference of the bushing 1 can be set according to actual needs, and there are no restrictions on this.

[0056] The positions of the oil inlet hole 23 within the first groove 21 and the oil outlet hole within the second groove 22 can be set according to actual needs and are not limited thereto. For example, the oil inlet hole 23 can be set on the side wall of the first groove 21 or on the bottom of the first groove 21. The oil inlet hole 23 can be set radially along the bushing 1 or axially along the bushing 1. The oil outlet hole can be set on the side wall of the second groove 22 or on the bottom of the second groove 22. The oil outlet hole can be set radially along the bushing 1 or axially along the bushing 1.

[0057] like Figure 1 and Figure 2 As shown, in some embodiments, the oil inlet 23 is located in the middle of the bottom of the first groove 21, and the oil outlet is located in the middle of the bottom of the second groove 22.

[0058] Understandably, since the oil inlet 23 is located in the middle of the bottom of the first groove 21, the external lubricating oil can enter the first groove 21 evenly, and the lubricating oil in the first groove 21 can enter the second groove 22 evenly. This ensures that the oil film is evenly formed on the inner wall of the bushing 1. At the same time, since the oil outlet is located in the middle of the bottom of the second groove 22, the lubricating oil in the second groove 22 can be evenly distributed, thereby ensuring that the high-pressure oil film can stably support the journal and ensure the stable operation of the bearing.

[0059] It should be noted that in the description of this disclosure, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Furthermore, in the description of this disclosure, unless otherwise stated, "a plurality of" means two or more.

[0060] Any process or method description in the flowchart or otherwise herein can be understood as representing a module, segment, or portion of code comprising one or more executable instructions for implementing a particular logical function or process, and the scope of preferred embodiments of this disclosure includes additional implementations in which functions may be performed not in the order shown or discussed, including substantially simultaneously or in reverse order depending on the function involved, as will be understood by those skilled in the art to which embodiments of this disclosure pertain.

[0061] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this disclosure. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0062] Although embodiments of the present disclosure have been shown and described above, it is to be understood that the above embodiments are exemplary and should not be construed as limiting the present disclosure. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present disclosure.

Claims

1. A hydrostatic sliding bearing suitable for journal tilting, characterized in that, include: bushing; Multiple oil grooves are arranged sequentially on the inner wall of the bushing along the circumference of the bushing. Each oil groove includes a first groove and a second groove. The first groove and the second groove are distributed along the circumference of the bushing, and the first groove is connected to the second groove. The cross-sectional area of ​​the first groove along the radial direction of the bushing is larger than the cross-sectional area of ​​the second groove along the radial direction of the bushing. An oil inlet hole is provided in the first groove, and an oil outlet hole is provided in the second groove. The hydrostatic sliding bearing includes: A first groove group, comprising: a plurality of oil grooves, wherein the plurality of oil grooves of the first groove group are evenly distributed along the circumference of the bushing; The second groove group includes a plurality of oil grooves, wherein the plurality of oil grooves of the second groove group are evenly distributed along the circumference of the bushing; The first groove group and the second groove group are arranged sequentially along the axial direction of the bushing, and the plurality of oil grooves in the first groove group and the plurality of oil grooves in the second groove group are staggered along the circumferential direction of the bushing. The length of the first groove along the axial direction of the bushing is equal to the length of the second groove along the axial direction of the bushing, and the depth of the first groove along the radial direction of the bushing is greater than the depth of the second groove along the radial direction of the bushing. The oil inlet is located in the middle of the bottom of the first groove, and the oil outlet is located in the middle of the bottom of the second groove.

2. The hydrostatic sliding bearing suitable for journal tilting according to claim 1, characterized in that, The first groove group includes: a first oil groove, a second oil groove and a third oil groove, wherein the first oil groove, the second oil groove and the third oil groove are evenly distributed along the circumference of the bushing; The second groove group includes: a fourth oil groove, a fifth oil groove and a sixth oil groove, wherein the fourth oil groove, the fifth oil groove and the sixth oil groove are evenly distributed along the circumference of the bushing; The projections of the first oil groove, the second oil groove, and the third oil groove along the axial direction of the bushing do not overlap with the projections of the fourth oil groove, the fifth oil groove, and the sixth oil groove along the axial direction of the bushing.

3. The hydrostatic sliding bearing suitable for journal tilting according to claim 2, characterized in that, The projections of the first oil groove along the axial direction of the bushing, the fourth oil groove along the axial direction of the bushing, the second oil groove along the axial direction of the bushing, the fifth oil groove along the axial direction of the bushing, the third oil groove along the axial direction of the bushing, and the sixth oil groove along the axial direction of the bushing are sequentially connected along the circumference of the bushing.

4. The hydrostatic sliding bearing suitable for journal tilting according to claim 1, characterized in that, The depth of the second groove along the radial direction of the bushing is less than half the depth of the first groove along the radial direction of the bushing.

5. The hydrostatic sliding bearing suitable for journal tilting according to claim 1, characterized in that, The width of the first groove along the circumference of the bushing is smaller than the width of the second groove along the circumference of the bushing.

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