A plug-in type gas dynamic pressure bearing

Abstract

The present invention relates to the technical field of gas dynamic pressure bearings and provides a disc-type gas dynamic pressure bearing comprising: an inner ring, a first disc, a second disc, and a bearing sleeve. The inner ring is formed by a plurality of inner ring bodies connected by a hinge. The inner ring body has a plurality of disc slots distributed circumferentially, with adjacent disc slots oriented in opposite directions. A plurality of first discs and second discs are distributed circumferentially and axially, with one end of each first disc and second disc inserted into two adjacent disc slots and the other end positioned in a groove of the bearing sleeve. Adjacent first discs and second discs are alternately arranged axially and in opposite directions. This invention utilizes discs distributed circumferentially and axially with the hinged inner ring body to form a bearing structure characterized by "tilting" deformation of the inner ring and structural stiffness and damping provided by the discs. This ensures a fixed air film gap between the rotor and the inner ring, allows the inner ring to adapt to the rotor's motion trajectory, and provides a certain degree of friction damping in the bearing. This improves the bearing's ability to withstand impact loads and its durability, thereby addressing the technical problems of existing foil gas dynamic pressure bearings, such as the air film gap increasing with speed and the rotor system becoming unstable at high speeds.

Description

Technical Field

[0001] The present invention relates to the technical field of hydrodynamic bearings, and in particular to an insert-type gas hydrodynamic bearing. Background Art

[0002] Common foil gas bearings consist of a top foil, an elastic foil, and a bearing sleeve. The dynamic pressure air film surrounding the top foil and the rotor keeps the rotor in a suspended state, giving the rotor system advantages such as oil-free lubrication, low friction, and high speed (high energy density DN value). They are widely used in high-speed rotating mechanical equipment such as fuel cell air compressors, air cycle machines, and micro gas turbines.

[0003] When the rotor system is stationary, the relaxed top foil and elastic foil surround the rotor, resulting in no significant nominal bearing clearance. As rotor speed increases, the rotor draws more surrounding gas into the convergence zone between the rotor and top foil surfaces. This slows the gas velocity and forms a high-pressure zone. This high-pressure gas distributes the rotor load onto the top foil, causing the top and elastic foils to move radially and gradually increasing the air film gap. When the resultant vertical air film pressure exceeds the rotor load, the rotor is fully suspended. The top and elastic foils experience some deformation, providing structural stiffness and damping for the rotor system. At this point, the rotor speed decreases, and rotor instability (subsynchronous vibration) is eliminated. To achieve high energy density output, the rotor speed must be continuously increased. However, the high-speed rotor generates a wide, high-pressure air film, which further compresses the top and elastic foils. This structural deformation increases, enlarging the air film space and compressing the rotor, thus affecting rotor stability. Therefore, subsynchronous instability is inevitable above a certain rotor speed.

[0004] In order to suppress subsynchronous vibrations of the rotor, gas tilting pad bearings are applied to the rotor system. This type of gas tilting pad bearing is theoretically immune to subsynchronous instability because the pads can adaptively deflect along the rotor's trajectory. However, tilting pads cut from metal have no damping effect and therefore cannot withstand external impact loads well in engineering applications. CN104653598B provides a tilting pad radial gas bearing that connects a traditional foil gas hydrodynamic bearing and a tilting pad bearing in parallel, introducing structural stiffness and damping into the gas tilting pad bearing, achieving the advantages of both bearings. However, it also introduces the disadvantage of increased gas film thickness of the top foil and elastic foil when the rotor is at high speed. Summary of the Invention

[0005] In response to the above-mentioned technical deficiencies, the present application provides a plug-in gas dynamic pressure bearing, which adopts circumferentially and axially distributed plugs and a hinged inner ring body to form a "tiltable" deformation of the inner ring, and the plugs provide structural stiffness and damping. The bearing structure has the characteristics of a fixed air film gap between the rotor and the inner ring, the inner ring adapts to the motion trajectory of the rotor, and the bearing has a certain friction damping, which greatly suppresses the subsynchronous vibration of the rotor system, improves the bearing's ability to withstand impact loads and durability, and solves the technical problem of the existing foil gas dynamic pressure bearing that the air film gap increases with the speed and the rotor system becomes unstable at high speed. The many technical effects that can be produced by the preferred technical solution among the many technical solutions provided by the present invention are explained below.

[0006] In order to achieve the above technical objectives, the present invention provides the following technical solutions: a blade-type gas dynamic pressure bearing, comprising: an inner ring, a first blade, a second blade, and a bearing sleeve; wherein the inner ring is composed of an inner ring body, a hinge, and blade grooves distributed circumferentially on the inner ring body, the hinge is a circular ring of a certain thickness obtained by cutting different "U-shaped" materials at several circumferential positions of the circular ring and inside and outside the inner ring by a linear cutting method, the uncut part is the inner ring body, and multiple circumferentially distributed inner ring bodies are connected by the hinge, the radial thickness of the hinge with a circular arc chamfer is much smaller than that of the inner ring body, and the hinge ensures the inner ring The relationship between the main bodies and the tiltable deformation of the inner ring body; there are multiple insert slots distributed along the circumferential direction on the inner ring body, and the two adjacent insert slots are in opposite directions and form a certain angle. The width of the insert slot is consistent with the thickness of the first insert and the second insert, and the radial depth of the insert slot is less than the thickness of the inner ring body; multiple first inserts and second inserts are distributed along the circumferential direction, one end of the first insert and the second insert are respectively inserted into two adjacent insert slots, and the other end is placed in the groove of the bearing sleeve, and the adjacent first insert and second insert are arranged alternately axially and in opposite directions.

[0007] The first inserts and the second inserts distributed circumferentially and axially are metal sheets of the same size. The lengths of the first inserts and the second inserts are less than the length of the bearing sleeve. Multiple groups of the first inserts and the second inserts are distributed axially. One end of adjacent first inserts and second inserts are respectively inserted into two adjacent insert slots with different orientations, and the other end is placed in the groove of the bearing sleeve. Adjacent first inserts and second inserts are arranged alternately axially and in opposite directions. The circumferentially crossed first inserts and the second inserts provide certain support for the circumferential and radial movements of the inner ring body.

[0008] The inner surface of the bearing sleeve is provided with a plurality of grooves, and the ends of the first inserting piece and the second inserting piece are placed in the grooves to limit the circumferential movement of the first inserting piece and the second inserting piece.

[0009] Optionally, the inner surface of the bearing sleeve may not have a groove. In this case, the width of the first insert and the second insert is larger, forming a wide insert. After being installed between the inner ring and the bearing sleeve, the wide insert is compressed and exerts a certain preload pressure, resulting in natural bending. The friction between the wide insert and the bearing sleeve provides friction damping for the bearing.

[0010] Optionally, the first insert and the second insert are replaced by long inserts having the same length as the bearing sleeve. In this case, the insert slots on the inner ring body only accommodate the circumferentially distributed long inserts, and the direction of the long inserts is opposite to the direction of rotation of the rotor.

[0011] Optionally, the first insert and the second insert can be replaced by an insert group, which consists of several inserts of different widths. The bottom of the insert group is placed in the groove of the bearing sleeve, and the widest insert is inserted into the insert groove. The inserts of different widths form a "step shape" to provide varying stiffness and friction damping for the bearing.

[0012] Optionally, the first insert and the second insert can be replaced by V-shaped inserts, the two metal plates of the V-shaped insert have the same width and are both inserted into the insert slot, the V-shaped insert is placed circumferentially and axially, and the axially adjacent V-shaped inserts are staggered by a certain angle.

[0013] Optionally, the length of the V-shaped insert is the same as that of the bearing sleeve, and the bearing support structure is composed of only one type of V-shaped insert.

[0014] Optionally, the V-shaped insert is replaced by two unequal width V-shaped inserts of metal plates with different widths, wherein one metal plate with a smaller width is inserted into the insert slot, and the other metal plate with a larger width contacts the outer surface of the inner ring, and the directions of the insert slots in which adjacent unequal width V-shaped inserts are inserted can be the same or opposite.

[0015] Optionally, the first insert or the second insert is replaced by a V-shaped insert group, which consists of multiple V-shaped inserts with the same angle and different widths, and the metal plates on both sides of a single V-shaped insert can be the same or different; the upper end of the V-shaped insert group is inserted into the insert slot, and the lower end is placed in the groove of the bearing sleeve.

[0016] Optionally, the circular inner surface of the inner ring may be composed of preloaded inner ring bodies with different radii.

[0017] Optionally, a porous structure can be placed on the inner surface of the inner ring body to form a static-dynamic hybrid bearing, a portion of the material in the middle part of the inner ring body is cut off to form a recess, and the middle part of the inner ring body is processed into horizontal and vertical grid-shaped air flow channels such as "straight-shaped", "cross-shaped" or "well-shaped". The unprocessed part in the middle part of the inner ring body and the surrounding parts of the inner ring body are used to fix the tilting pad structure, and a threaded hole is processed at the end of the inner ring body, which is connected to the air flow channel inward and to the air intake pipe outward.

[0018] Due to the adoption of the above technology, the present invention has the following positive effects compared with the prior art: the present invention provides a blade-type gas dynamic pressure bearing, which structurally includes an inner ring, a first blade, a second blade, and a bearing sleeve; wherein, the inner ring is formed by connecting the inner ring body with a hinge, the hinge is close to the inner surface of the inner ring body, and the hinge thickness is smaller than the inner ring body, which is conducive to the inner ring body undergoing tilting angular deformation with the movement of the rotor, suppressing the subsynchronous vibration of the rotor, and at the same time, the inner ring body does not undergo structural deformation, which is conducive to maintaining the consistency of the bearing nominal clearance and system performance; the first blade and the second blade distributed along the circumferential direction and the axial direction are inserted into the blade slots in opposite directions, and the other end is placed in the groove of the bearing sleeve to form a cross and support the inner ring, so as to ensure that the rotor does not hit the membrane after being subjected to the impact load through structural deformation, allowing the rotor to rotate forward and reverse. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0020] Figure 1 An exploded view of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0021] Figure 2 A front view of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0022] Figure 3 A partially enlarged view of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0023] Figure 4 A schematic diagram of an insert of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0024] Figure 5 A schematic diagram of a bearing sleeve of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0025] Figure 6 A schematic diagram of a wide insert of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0026] Figure 7 An exploded view of a modified bearing 1 of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0027] Figure 8 This is a front view of a modified bearing 1 of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0028] Figure 9 An exploded view of a modified bearing 2 of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0029] Figure 10 This is a front view of a modified bearing 2 of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0030] Figure 11 A schematic diagram of a modified bearing sleeve 2 of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0031] Figure 12 An exploded view of a modified bearing 3 of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0032] Figure 13 A schematic diagram of a V-shaped insert of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0033] Figure 14 A schematic diagram of a V-shaped insert assembly of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0034] Figure 15 A schematic diagram of unequal length V-shaped inserts of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0035] Figure 16 A schematic diagram of a preloaded inner ring body of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0036] Figure 17 A schematic diagram of the porous structure of an insert-type gas dynamic pressure bearing provided in an embodiment of the present invention.

[0037] Among them, the marks of the figures in the figure are: 1-inner ring, 2-first insert, 3-second insert, 4-bearing sleeve, 5-long insert, 6-rotor, 7-insert group, 8-V-shaped insert, 9-V-shaped insert group, 10-V-shaped insert of unequal width, 11-porous structure, 21-wide insert, 101-hinge, 102-insert groove, 103-inner ring body, 104-preloaded inner ring body, 105-air flow channel, 106-threaded hole, 401-groove, 402-bearing sleeve groove, 701-insert 1 of insert group, 702-insert 2 of insert group, 703-insert 3 of insert group, 901-V-shaped insert 1 of V-shaped insert group, 902-V-shaped insert 2 of V-shaped insert group, 903-V-shaped insert 3 of V-shaped insert group. DETAILED DESCRIPTION

[0038] To make the objectives, technical solutions, and advantages of the present invention more apparent, the technical solutions of the present invention will be described in detail below. Obviously, the embodiments described are only some of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other implementations obtained by those of ordinary skill in the art without inventive effort are within the scope of protection of the present invention.

[0039] In the description of the present invention, it should be noted that, unless otherwise specified, “several” and “plurality” mean two or more; the orientations or positional relationships indicated by terms such as “upper”, “lower”, “top”, “bottom”, “inner”, “outer”, “first” and “second” are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as limiting the present invention.

[0040] In the description of the present invention, it should be noted that, unless otherwise specified, the term "preload" should be understood in a broad sense, that is, the thickness of the air film is uneven in the radial direction of the bearing. For example, the bearing structure is preloaded before installation, or it can be formed during the working process of the bearing and has the same effect as the preload applied in advance. For ordinary technicians in this field, the specific meaning of the above terms in the present invention can be understood according to the specific circumstances.

[0041] The insert-type gas dynamic pressure bearing provided in the embodiment of the present application is now described.

[0042] like Figures 1 to 5As shown, the insert-type gas dynamic pressure bearing comprises: an inner ring (1), a first insert (2), a second insert (3), and a bearing sleeve (4); wherein the inner ring (1) is composed of an inner ring body (103), a hinge (101), and insert slots (102) distributed circumferentially on the inner ring body (103); the hinge (101) is a circular ring of a certain thickness obtained by cutting different "U-shaped" materials at several circumferential positions of the circular ring and inside and outside the inner ring (1) by a processing method such as linear cutting; the uncut part is the inner ring body (103); the plurality of circumferentially distributed inner ring bodies (103) are connected by the hinge (101); the hinge (101) ensures the association between the inner ring bodies (103) and the tiltable deformation of the inner ring (1); the inner ring body (103) has a plurality of circumferentially distributed inner ring bodies (103). The insert slots (102) are arranged such that two adjacent insert slots (102) are arranged in opposite directions, a plurality of the first insert slots (2) and the second insert slots (3) are distributed along the circumferential direction, one end of the first insert slot (2) and the second insert slot (3) are respectively inserted into two adjacent insert slots (102), and the other end is placed in the groove (401) of the bearing sleeve (4), the adjacent first insert slots (2) and the second insert slots (3) are arranged alternately in the axial direction, and are placed in opposite directions and at a certain angle, the width of the insert slot (102) is consistent with the thickness of the first insert slot (2) and the second insert slot (3), the radial depth of the insert slot (102) is less than the thickness of the inner ring body (103), and the position of the insert slot (102) in the inner ring body (103) does not affect the stiffness of the hinge (101) and the inner ring body (103).

[0043] like Figure 1-4 As shown, the first inserts (2) and the second inserts (3) distributed in the circumferential direction and in the axial direction are metal thin plates of the same size, the lengths of the first inserts (2) and the second inserts (3) are less than the length of the bearing sleeve (4), and multiple groups of first inserts (2) and second inserts (3) are distributed in the axial direction. One end of the first insert (2) and the second insert (3) are respectively inserted into two adjacent insert slots (102) with different directions, and the other end is placed in the groove (401) of the bearing sleeve (4), and the adjacent first inserts (2) and the second inserts (3) are arranged alternately in the axial direction and in opposite directions; the circumferentially crossed first inserts (2) and the second inserts (3) play a certain supporting role in the circumferential movement and radial movement of the inner ring body (103).

[0044] like Figure 5 As shown, the inner surface of the bearing sleeve (4) has a plurality of grooves (401) for limiting the circumferential movement of the first insert (2) and the second insert (3).

[0045] like Figure 6As shown, as an optional embodiment, the inner surface of the bearing sleeve (4) may not have a groove. In this case, the width of the first insert and the second insert is larger, forming a wide insert (21). After being installed between the inner ring (1) and the bearing sleeve (4), the wide insert (21) is compressed and exerts a certain preload pressure, resulting in natural bending. The friction between the bottom of the wide insert (21) and the bearing sleeve provides friction damping for the bearing.

[0046] like Figure 7 and Figure 8 As shown, as an optional embodiment, the first insert (2) or the second insert (3) can be replaced by a long insert (5) having the same length as the bearing sleeve (4). In this case, the insert slot (102) on the inner ring body (103) only accommodates the circumferentially distributed long inserts (5), and the direction of the long inserts (5) is opposite to the rotation direction of the rotor (6).

[0047] like Figure 9-11 As shown, as an optional embodiment, the first insert (2) or the second insert (3) can be replaced by an insert group (7), the insert group (7) is composed of a plurality of inserts (701, 702, 703) of different widths, the bottom of the insert group (7) is placed in the bearing sleeve groove (402), the widest insert is inserted into the insert slot (102), and the inserts of different widths form a "stepped shape" to provide varying stiffness and friction damping for the bearing. The insert group (7) can also be aligned at the top and inserted into the insert slot (102), and the inserts of different widths (701, 702, 703) are compressed to have different preload deformations.

[0048] like Figure 12 and Figure 13 As shown, as an optional embodiment, the first insert (2) or the second insert (3) can be replaced by a V-shaped insert (8), the two metal plates of the V-shaped insert (8) have the same width and form a certain angle, and are both inserted into the insert slot (102), and the bottom of the V-shaped insert (8) is placed in the insert slot (102); the V-shaped insert (8) is placed along the circumferential direction and the axial direction, and the axially adjacent V-shaped inserts (8) are staggered at a certain angle; the length of the V-shaped insert (8) can be the same as the length of the bearing sleeve (4), and the bearing support structure is composed of only one type of V-shaped insert (8).

[0049] like Figure 14 As shown, as an optional embodiment, the first insert (2) or the second insert (3) can be replaced by a V-shaped insert group (9), which is composed of a plurality of V-shaped inserts (901, 902, 903) of the same angle and different widths, wherein the metal plates on both sides of the V-shaped inserts can be the same or different; the upper end of the V-shaped insert group (9) is inserted into the insert slot (102), and the lower end is placed in the groove (401) of the bearing sleeve (4).

[0050] like Figure 15 As shown, as an optional embodiment, the first insert (2) or the second insert (3) can be made of two unequal width V-shaped inserts (10) with different metal plate widths, wherein one metal plate with a smaller width is inserted into the insert slot (102), and a metal plate with a larger width contacts the outer surface of the inner ring (1), and the directions of the insert slots (102) into which adjacent unequal width V-shaped inserts (10) are inserted can be the same or opposite.

[0051] like Figure 16 and Figure 17 As shown, as an optional embodiment, the circular inner surface of the inner ring (1) can be composed of a preloaded inner ring body (104) with different radii; a porous structure (11) can be placed on the inner surface of the inner ring body (103) to form a static-dynamic hybrid bearing, a portion of the material in the middle part of the inner ring body (103) is cut off to form a recess, and the middle part of the inner ring body (103) is processed into a "straight-shaped", "cross-shaped" or "well-shaped" horizontal and vertical grid-shaped air flow channel (105), the unprocessed part in the middle part of the inner ring body (103) and the surrounding part of the inner ring body (103) are used to fix the tilting pad structure (11), and a threaded hole (106) is processed at the end of the inner ring body (105), and the threaded hole (106) is connected to the air flow channel (105) inwardly and to the air intake pipe outwardly.

[0052] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art may still modify the technical solutions described in the aforementioned embodiments or substitute equivalents for some of the technical features. Any modifications, equivalent substitutions, or modifications made within the spirit and principles of the present invention shall be included within the scope of protection of the present invention.

Claims

1. A blade-type gas dynamic pressure bearing, characterized in that: include: An inner ring (1), a first insert (2), a second insert (3), and a bearing sleeve (4); wherein the inner ring (1) is composed of an inner ring body (103), a hinge (101), and insert slots (102) distributed circumferentially on the inner ring body (103); the circumferentially distributed hinge (101) is obtained by cutting different "U-shaped" materials on the inner and outer sides of a circular ring of a certain thickness through a wire cutting method; the uncut portion is the inner ring body (103); a plurality of circumferentially distributed inner ring bodies (103) are connected via the hinge (101); the radial thickness of the hinge (101) with a circular arc chamfer is much smaller than that of the inner ring body (103); the hinge (101) ensures the association between the inner ring bodies (103) and the tiltable deformation of the inner ring (1); the inner ring body (103) There are a plurality of insert slots (102) distributed along the circumferential direction, and two adjacent insert slots (102) are in opposite directions; the first insert (2) and the second insert (3) are metal thin plates of the same size, and their axial length is less than the length of the bearing sleeve (4); the plurality of first inserts (2) and the second insert (3) are distributed along the circumferential direction, one end of the first insert (2) and the second insert (3) are respectively inserted into two adjacent insert slots (102), and the other end is placed in the groove (401) of the bearing sleeve (4); the adjacent first insert (2) and the second insert (3) are arranged alternately in the axial direction and in opposite directions; the circumferentially crossed first insert (2) and the second insert (3) play a certain supporting role in the circumferential movement and radial movement of the inner ring body (103).

2. The insert-type gas dynamic pressure bearing according to claim 1, characterized in that: The first insert (2) and the second insert (3) are replaced by an insert group (7), the insert group (7) consisting of a plurality of inserts (701, 702, 703) of different widths. The bottom of the insert group (7) is placed in the bearing sleeve groove (402), and the widest insert is inserted into the insert groove (102). The inserts of different widths form a "stepped shape" to provide varying stiffness and friction damping for the bearing.

3. The insert-type gas dynamic pressure bearing according to claim 1, characterized in that: The first insert (2) and the second insert (3) are replaced by a V-shaped insert (8), the two metal plates of the V-shaped insert (8) having the same width and both inserted into the insert slot (102), the V-shaped insert (8) being distributed circumferentially and placed axially, and the axially adjacent V-shaped inserts (8) being staggered at a certain angle.

4. The insert-type gas dynamic pressure bearing according to claim 3, characterized in that: The axial length of the V-shaped insert (8) is the same as the length of the bearing sleeve (4), and the bearing support structure is composed of only one type of V-shaped insert (8).

5. The insert-type gas dynamic pressure bearing according to claim 3, characterized in that: The first insert (2) and the second insert (3) are replaced by two unequal width V-shaped inserts (10) of different metal plate widths, wherein one metal plate with a smaller width is inserted into the insert slot (102), and a metal plate with a larger width contacts the outer surface of the inner ring (1), and the directions of the insert slots (102) in which the adjacent unequal width V-shaped inserts (10) are inserted can be the same or opposite.

6. The insert-type gas dynamic pressure bearing according to claim 1, characterized in that: The first insert (2) and the second insert (3) are replaced by a V-shaped insert group (9), the V-shaped insert group (9) consisting of a plurality of V-shaped inserts (901, 902, 903) of the same angle and different widths, wherein the metal plates on both sides of the V-shaped inserts can be the same or different, the upper end of the V-shaped insert group (9) is inserted into the insert slot (102), and the lower end is placed in the groove (401) of the bearing sleeve (4).

7. The insert-type gas dynamic pressure bearing according to claim 1, characterized in that: The circular inner surface of the inner ring (1) is replaced by a preloaded inner ring body (104) with a different radius; a porous structure (11) is placed on the inner surface of the inner ring body (103) to form a static-dynamic hybrid bearing.

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