JP2013148145A - Bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device that can prevent damage due to partial contact of a rotation shaft.SOLUTION: A bearing device includes: a supporting member 11 provided around a rotation shaft 2; a circular surface part 21 disposed between the rotation shaft 2 and the supporting member 11 and facing an outer circumferential surface of the rotation shaft 2; a pad member 12 having a back surface part 22 facing the supporting member 11; a pivot part 13 supporting the pad member 12 to be able to tilt in an axial direction of the rotation shaft 2 with respect to the supporting member 11; a lubricant supply part supplying a pressure oil for lubricating between the rotation shaft 2 and the surface part 21 so that an oil membrane is formed between the rotation shaft 21 and the surface part 21; and a tile regulation part 14 regulating the tile in the axial direction of the pad member 12.

Description

  The present invention relates to a bearing device that rotatably supports a large rotating machine such as a steam turbine or a compressor.

  Conventionally, a plurality of tilting pads can be tilted around the rotating shaft of a rotating machine, and an oil film is formed between the rotating shaft and the tilting pad, and the rotating shaft is rotatably supported by the tilting pad. A bearing device configured to do this is known (see, for example, Patent Document 1). In the bearing device described in Patent Document 1, the tilting pad is supported by the pivot so as to be able to tilt in the axial direction and the circumferential direction of the rotating shaft so that the tilting pad can follow the tilt of the rotating shaft.

JP 2004-197890 A

  However, when the tilting pad is supported by the pivot as in the device described in Patent Document 1, the thickness of the oil film between the rotating shaft and the tilting pad may vary in the axial direction when the supply of lubricating oil is started. There is. As a result, the rotating shaft may come into contact with the tilting pad and damage such as seizure may occur on the rotating shaft.

  An object of the present invention is to provide a bearing device capable of preventing damage due to a single contact of a rotating shaft.

  One aspect of the bearing device of the present invention includes a support member provided around the rotation shaft, an arcuate surface portion that is disposed between the rotation shaft and the support member and faces the outer peripheral surface of the rotation shaft, and a support member The rotation shaft and the surface so that an oil film is formed between the rotation shaft and the surface portion. A lubricating oil supply part that supplies pressure oil for lubrication between the two parts and an inclination restricting part that restricts the inclination of the pad member with respect to the axial direction of the rotating shaft.

  According to this configuration, when the lubricating oil is supplied unevenly in the axial direction between the surface portion of the pad member and the rotating shaft, and the pad member is inclined with respect to the axial direction, the inclination with respect to the axial direction is reduced. Be regulated. Therefore, it is possible to prevent damage due to the contact of the rotating shaft.

  In the bearing device according to another aspect of the present invention, the lubricating oil supply unit is provided on the surface portion, the oil supply port that opens to the surface portion, supplies the lubricating oil toward the outer peripheral surface of the rotating shaft, and communicates with the oil supply port. And the groove portions are formed symmetrically with each other on both sides in the axial direction of the fuel filler opening.

  According to this configuration, it is possible to increase the pressure oil area where the lubricating oil pressure acts on the outer peripheral surface of the rotating shaft at the start of supply of the lubricating oil, and the rotating shaft can be easily floated from the pad member.

  In the bearing device according to another aspect of the present invention, the inclination restricting portion includes an elastic support member that elastically supports the pad member from the support member.

  According to this configuration, when the pad member is tilted in the axial direction, the reaction force from the elastic member acts on the pad member, so that the tilt of the pad member in the axial direction can be easily corrected.

  In the bearing device according to another aspect of the present invention, the inclination restricting portion includes a protruding member that protrudes from the support member toward the back surface portion of the pad member.

  According to this configuration, when the pad member is tilted by a predetermined amount or more, the back surface portion of the pad member comes into contact with the distal end portion of the protruding member, so that the maximum tilt of the pad member can be limited.

  In the bearing device according to another aspect of the present invention, the tilt restricting portions are provided on both sides in the axial direction of the pivot portion.

  According to this configuration, the inclination of the pad member in one axial direction and the other axial direction can be effectively suppressed.

  According to the present invention, it is possible to prevent damage due to the contact of the rotating shaft.

FIG. 1 is a perspective view of a steam turbine to which a bearing device according to an embodiment of the present invention is applied. 2 is a cross-sectional view taken along line II-II in FIG. FIG. 3 is a perspective view showing a configuration of a bearing pad constituting the bearing device according to the embodiment of the present invention. FIG. 4 is a diagram for explaining how the rotating shaft floats due to the lubricating oil. FIG. 5 is a diagram illustrating an example of the inclination of the bearing pad. FIG. 6 is a diagram schematically showing a main configuration of the bearing device according to the first embodiment of the present invention. FIG. 7 is a diagram schematically showing a main configuration of a bearing device according to the second embodiment of the present invention. FIG. 8 is a diagram showing a modification of the present invention.

(First embodiment)
Hereinafter, a bearing device according to a first embodiment of the present invention will be described with reference to FIGS. In the following, as an example, a bearing device that rotatably supports a rotating shaft of a steam turbine will be described. A steam turbine is a large-sized rotating machine that generates electricity by being rotationally driven using steam, and is used in a pressurized water reactor or the like.

  FIG. 1 is a perspective view of a steam turbine 1 to which a bearing device according to this embodiment is applied. The steam turbine 1 has a pair of rotating shafts 2 and 3 extending along a central axis L0 and a blade portion 4 disposed between the pair of rotating shafts 2 and 3. The steam turbine 1 has a symmetrical shape with respect to the central axis L0, and rotates around the central axis L0. In FIG. 1, the wing part 4 is shown in a cylindrical shape having a larger diameter than the rotation shafts 2 and 3, and detailed illustration of the wing part 4 is omitted. In the following, the direction parallel to the central axis L0 is the axial direction, the circumferential direction of the cylindrical surface around the central axis L0 is the circumferential direction, and the direction from the central axis L0 to the cylindrical surface or vice versa is the central axis from the cylindrical surface. The direction toward L0 is defined as the radial direction. The outer peripheral surfaces of the rotary shafts 2 and 3 have a cylindrical shape, and the tangent in the axial direction of the outer peripheral surfaces of the rotary shafts 2 and 3 is parallel to the central axis L0.

  The bearing device 10 is a sliding bearing device that slidably supports the rotating shafts 2 and 3 via lubricating oil, and a pair of bearing devices 10 are provided facing the outer peripheral surfaces of the rotating shafts 2 and 3. FIG. 2 is a cross-sectional view showing a schematic configuration of the bearing device 10 according to the first embodiment, and is a cross-sectional view taken along a plane perpendicular to the central axis L0 (a cross-sectional view taken along the line II-II in FIG. 1). . The configuration of the bearing device 10 around the rotary shaft 2 and the configuration of the bearing device 10 around the rotary shaft 3 are equal to each other, and the configuration of the bearing device 10 around the rotary shaft 2 will be mainly described below.

  As shown in FIG. 2, the bearing device 10 includes an annular bearing housing 11 provided around the rotating shaft 2, and a pair of members disposed between the inner peripheral surface of the bearing housing 11 and the outer peripheral surface of the rotating shaft 2. A bearing pad 12 and a pivot 13 that supports each bearing pad 12 from the bearing housing 11 so as to be swingable (inclinable) in the axial direction and the circumferential direction. The bearing pad 12 is an arc-shaped pad member having a curved surface extending in the circumferential direction and the axial direction so as to support a part in the circumferential direction and a part in the axial direction of the rotating shaft 2 (see FIG. 3). Also called a pad. The bearing pad 12 has a surface portion 21 that faces the outer peripheral surface of the rotating shaft 2 and a back surface portion 22 that faces the inner peripheral surface of the bearing housing 11.

  The surface portion 21 is formed by a concave curved surface having a predetermined curvature corresponding to the outer peripheral surface of the rotating shaft 2. Lubricating oil is supplied between the surface portion 21 and the outer peripheral surface of the rotating shaft 2, and the surface portion 21 supports the rotating shaft 2 through an oil film 30 in a rotatable manner. Therefore, the surface portion 21 constitutes a sliding surface of the bearing device 10. The back surface portion 22 is formed by a convex curved surface having a predetermined curvature corresponding to the inner peripheral surface of the bearing housing 11. The central portion in the circumferential direction and the central portion in the axial direction of the back surface portion 22 are supported by the pivot 13. Therefore, the bearing pad 12 can swing in the circumferential direction and the axial direction with the central portion as a fulcrum.

  The pivot 13 is provided in a region below the axis L1 extending in the horizontal direction through the central axis L0, and on both sides in the circumferential direction across the axis L2 extending in the vertical direction through the central axis L0. Yes. An angle θ1 formed between a straight line L3 connecting the circumferential center of one pivot 13 and the central axis L0 to the axis L2 is, for example, 45 degrees, and connects the circumferential central part of the other pivot 13 and the central axis L0. An angle θ2 formed by the straight line L4 and the axis L2 is, for example, −45 degrees. That is, the rotating shaft 2 is supported by the two bearing pads 12 arranged in a circumferentially symmetric position with respect to the axis L2. By supporting the rotating shaft 2 with the pair of bearing pads 12 in this way, the number of parts can be reduced and the installation space for the parts can be reduced.

  FIG. 3 is a perspective view showing the configuration of the surface portion 21 of the bearing pad 12. As shown in FIG. 3, an oil filler port 23 is opened at the center portion in the circumferential direction and the center portion in the axial direction of the surface portion 21. The oil supply port 23 communicates with a lubricating oil pump (not shown) through a through hole 24 that penetrates the bearing pad 12, and the lubricating oil discharged from the lubricating oil pump is directed from the oil supply port 23 toward the outer peripheral surface of the rotary shaft 2. Supplied. In addition, although the support part supported by the pivot 13 is provided in the back surface part 22 of the bearing pad 12, the through-hole 24 is formed avoiding this support part.

  Further, a pair of groove portions 25 having a predetermined depth are provided on the surface portion 21 of the bearing pad 12 on both sides in the axial direction of the oil filler 23. Each groove portion 25 is formed symmetrically with respect to the fuel filler opening 23. In this embodiment, the groove part 25 has a rhombus shape. One apex of the rhombus of each groove portion 25 overlaps with the fuel filler 23, and the groove 25 communicates with the fuel filler 23.

  In the bearing device 10 configured as described above, before the steam turbine 1 is rotated, the lubricating oil is not supplied to the oil supply port 23, and the rotating shafts 2 and 3 are in contact with the surface portion 21 of each bearing pad 12. It is supported. At this time, the distribution of the contact pressure due to the weight of the steam turbine 1 is represented by, for example, a region P0 in FIG.

  When rotating the steam turbine 1, first, lubricating oil is supplied to the oil supply port 23 by starting the lubricating oil pump. The supplied lubricating oil spreads from the oil supply port 23 to the respective groove portions 25 and causes the rotary shafts 2 and 3 to float on the outer peripheral surfaces of the rotary shafts 2 and 3 from the respective groove portions 25 as shown in FIG. Pressure (levitation pressure P) is generated. In the initial stage of supplying the lubricating oil, the bearing load W due to the own weight of the steam turbine 1 is such that the floating force PT obtained by multiplying the area (pressure oil area S) where the lubricating oil pressure acts on the outer peripheral surfaces of the rotary shafts 2 and 3 by the floating pressure P. It is larger than (pressure oil area S × flying pressure P), and the rotary shafts 2 and 3 do not float.

  Thereafter, as shown in FIG. 4 (b), when the flying pressure P exceeds the contact pressure P0, a gap is formed between the outer peripheral surface of the rotary shafts 2 and 3 and the surface portion 21, and FIG. As shown by the arrow a in b), the lubricating oil oozes out beyond the groove 25. As a result, the pressure oil area S increases and the levitation force PT (= S × P) increases. As shown in FIG. 4C, when the levitation force PT exceeds the bearing load W, the rotary shafts 2 and 3 start to float. Finally, the floating pressure due to the lubricating oil becomes a static pressure distribution as shown in the region R1 of FIG. Supported. In this state, the steam turbine 1 is rotationally driven to prevent seizure on the rotary shafts 2 and 3 when the steam turbine 1 starts to rotate. When the steam turbine 1 rotates, the drive of the lubricating oil pump is stopped. At this time, a rust-like oil film is formed between the outer peripheral surfaces of the rotary shafts 2 and 3 and the surface portion 21 without the need for dynamic pressure generation, and the vibrations of the rotary shafts 2 and 3 are attenuated.

  Thus, by providing the groove part 25 in the surface part 21 of the bearing pad 12, the pressure oil area S on which lubricating oil pressure acts can be increased easily. Therefore, the levitation force PT can be increased without significantly increasing the levitation pressure P, which is suitable for use in a large-sized large rotating machine such as the steam turbine 1. Further, since the bearing pad 12 is supported by the pivot 13, the bearing pad 12 can easily follow the inclination of the rotary shafts 2 and 3.

  By the way, when the supply of the lubricating oil is started, for example, if the axis La (FIG. 3) passing through the central portion in the circumferential direction of the bearing pad 12 is parallel to the central axis L0 (FIG. 1), the initial posture of the bearing pad 12 is horizontal. Become posture. In this state, for example, the lubricating oil is uniformly distributed in the dotted line region R2 of FIG. Therefore, the thickness of the oil film 30 in the dotted line region R2 becomes uniform, and the rotating shaft 2 can be supported in parallel to the surface portion 21.

  On the other hand, when the initial posture of the bearing pad 12 is an inclined posture inclined in the axial direction, the gap between the surface portion 21 and the outer peripheral surface of the rotating shaft 2 becomes uneven in the axial direction, and the gap is large. More lubricating oil flows in one axial direction. As a result, as shown in FIG. 5, a moment M that tilts the bearing pad 12 by the lubricating oil is generated, and the rotary shaft 2 is supported while being inclined relative to the bearing pad 12. At this time, the axis line La passing through the circumferential center of the bearing pad 12 and the central axis L0 are not parallel. If the steam turbine 1 is rotated in this state, the rotating shaft 2 may come into contact with the bearing pad 12 and damage such as seizure may occur on the sliding surface. In order to prevent this, the bearing device 10 is configured as follows in the first embodiment.

  FIG. 6 is a diagram schematically illustrating a main configuration of the bearing device 10 according to the first embodiment. As shown in FIG. 6, the bearing housing 11 includes an annular peripheral wall portion 11 a and a pair of side wall portions 11 b that protrude from both axial ends of the peripheral wall portion 11 a toward the rotation shaft. The bearing pad 12 is disposed facing the outer peripheral surface of the rotating shaft 2 in the space SP formed by the peripheral wall portion 11a and the side wall portion 11b.

  On both sides in the axial direction of the pivot 13, there are provided anti-vibration rubbers 14 having elasticity at symmetrical positions with respect to the pivot 13. The anti-vibration rubbers 14 are the same parts. Each anti-vibration rubber 14 extends in the radial direction, one end portion on the outer side in the radial direction is fixed to the inner peripheral surface of the peripheral wall portion 11 a of the bearing housing 11, and the other end portion on the inner side in the radial direction is on the bearing pad 12. The back portion 22 is fixed to the center portion in the circumferential direction. That is, the pair of pivots 13 and the anti-vibration rubber 14 are arranged at the same position in the circumferential direction.

  As shown in FIG. 6, if the axis line La passing through the central portion in the circumferential direction of the bearing pad 12 is parallel to the central axis L0, the bearing pad 12 is in a horizontal posture. At this time, neither the compressive force nor the tensile force acts on each anti-vibration rubber 14, and the reaction forces (biasing forces) acting on the bearing pads 12 from the anti-vibration rubbers 14 are equal to each other and zero. In addition, when each anti-vibration rubber 14 is provided between the back surface portion 22 and the peripheral wall portion 11a in a state where the anti-vibration rubbers 14 are previously contracted or expanded by the same amount, a predetermined initial load is applied to each anti-vibration rubber 14. In this case as well, the reaction forces acting on the bearing pads 12 from the antivibration rubbers 14 are equal to each other.

  On the other hand, when the bearing pad 12 is tilted in one axial direction and the axis La of the bearing pad 12 is tilted with respect to the central axis L0, the compressive force is applied to one vibration isolating rubber 14 and the tensile force applied to the other anti-vibrating rubber 14 Each works. As a result, one vibration isolating rubber 14 applies a reaction force to approach one end of the bearing pad 12 in the axial direction, and the other anti-vibration rubber 14 is the other end in the axial direction of the bearing pad 12. A reaction force is applied to the side away from the rotary shaft 2. As a result, the inclination of the bearing pad 12 in the axial direction can be reduced, and the bearing pad 12 can be corrected to a horizontal posture.

According to 1st Embodiment, there can exist the following effects.
(1) A bearing pad having a surface portion 21 facing the outer peripheral surface of the rotating shafts 2 and 3 and a back surface portion 22 facing the peripheral wall portion 11a of the bearing housing 11 between the rotating shafts 2 and 3 and the bearing housing 11. 12, and the bearing pad 12 is supported by the pivot 13 so as to be able to incline in the circumferential direction and the axial direction with respect to the bearing housing 11, and an oil film 30 is formed between the rotary shafts 2 and 3 and the surface portion 21. Thus, the lubricating oil is supplied through the oil supply port 23 and the groove 25. Further, a pair of vibration isolating rubbers 14 are arranged on both sides in the axial direction with the pivot 13 interposed therebetween, and the bearing pad 12 is elastically supported from the bearing housing 11 by the vibration isolating rubber 14. As a result, when the bearing pad 12 is inclined in the axial direction, an elastic force is applied to the bearing pad 12 from the vibration isolating rubber 14, and the inclination of the bearing pad 12 in the axial direction can be corrected. Therefore, it is possible to prevent the rotating shafts 2 and 3 from hitting the bearing pad 12 and to prevent damage such as seizure of the rotating shafts 2 and 3.

(2) Since the pair of anti-vibration rubbers 14 are provided on both sides of the pivot 13 in the axial direction, when the bearing pad 12 is tilted in the axial direction, reaction forces are applied to the one axial end and the other axial end of the bearing pad 12, respectively. It acts, and the inclination of the bearing pad 12 can be reduced at an early stage.
(3) The oil filler 23 is opened in the surface portion 21 of the bearing pad 12, and the grooves 25 are provided in communication with the oil filler 23 and symmetrically on both sides in the axial direction of the oil filler 23. As a result, the pressure oil area S on which the lubricating oil pressure acts on the outer peripheral surfaces of the rotating shafts 2 and 3 at the start of supply of the lubricating oil can be increased, and the rotating shafts 2 and 3 can be easily floated from the bearing pad 12. be able to.

(Second Embodiment)
A bearing device according to a second embodiment of the present invention will be described with reference to FIG. The second embodiment differs from the first embodiment in the configuration for restricting the inclination of the bearing pad 12 in the axial direction. That is, in the first embodiment, the anti-vibration rubber 14 is provided on both sides in the axial direction of the pivot 13 so as to restrict the inclination of the bearing pad 12. However, in the second embodiment, instead of the anti-vibration rubber 14. A stopper 15 is provided to restrict the inclination in the axial direction.

  FIG. 7 is a diagram schematically illustrating a main configuration of the bearing device 10 according to the second embodiment. In addition, the same code | symbol is attached | subjected to the location same as FIG. 6, and the difference with 1st Embodiment is mainly demonstrated below.

  As shown in FIG. 7, a pair of stoppers 15 are provided between the peripheral wall portion 11 a of the bearing housing 11 and the bearing pad 12 so as to be symmetrical with each other with the pivot 13 interposed therebetween and at the same circumferential position as the pivot 13. Is provided. The stopper 15 is a rod-like member extending in the radial direction, and one end portion (base end portion) on the outer side in the radial direction is fixed to the inner peripheral surface of the peripheral wall portion 11 a of the bearing housing 11. The other end portion (tip portion) on the radially inner side of the stopper 15 is separated from the back surface portion 22 of the bearing housing 11. The length of each stopper 15 is set so that the gap ΔL between the tip of each stopper 15 and the outer peripheral surface of the rotating shaft 2 becomes the same amount when the bearing pad 12 is in a horizontal posture as shown in the figure. ing.

  With such a configuration, when the bearing pad 12 is tilted in one axial direction, the back surface portion 22 comes into contact with one stopper 15, and when the bearing pad 12 is tilted in the other axial direction, the back surface portion 22 contacts the other stopper 15. Touch. Thereby, the inclination of the bearing pad 12 in the axial direction is limited, and damage due to the contact of the rotary shafts 2 and 3 can be prevented.

(Modification)
In the above embodiment, the anti-vibration rubber 14 (FIG. 6) or the stopper 15 (FIG. 7) is provided on both sides of the pivot 13 in the axial direction, but both the anti-vibration rubber 14 and the stopper 15 are provided as shown in FIG. You may make it provide. As a result, when a large axial moment is applied to the bearing pad 12, the maximum inclination of the bearing pad 12 is limited by the stopper 15, and the posture of the bearing pad 12 is quickly lowered by the elastic force of the vibration isolating rubber 14. It can be.

  In the above embodiment, the bearing housing 11 is provided around the rotary shafts 2 and 3 to support the anti-vibration rubber 14 and the stopper 15, but the configuration of the support member is not limited to this. The configuration of the bearing pad 12 having the arc-shaped surface portion 21 that faces the outer peripheral surface of the rotary shafts 2 and 3 and the back surface portion 22 that faces the bearing housing 11 is not limited to that described above. In other words, the pad member may have any configuration as long as it is disposed between the rotary shafts 2 and 3 and the bearing housing 11 and supports the rotary shafts 2 and 3 via the oil film 30 so as to be rotatable.

  In the above embodiment, the bearing pad 12 is supported by the pivot 13 so as to be tiltable in the circumferential direction and the axial direction. However, the pivot 13 may be supported so as to be tiltable only in the axial direction. It is not restricted to what was mentioned above. In the above embodiment, the oil supply port 23 and the groove portion 25 are formed in the surface portion 21 of the bearing pad 12 to supply the lubricating oil between the rotary shafts 2 and 3 and the surface portion 21. The configuration of the lubricating oil supply part for forming the oil film 30 between the shafts 2 and 3 and the surface part 21 is not limited to this. Although the diamond-shaped groove portions 25 are provided on both sides in the axial direction of the fuel filler opening 23, the groove portions 25 may have other shapes.

  In the above-described embodiment, the inclination of the bearing pad 12 with respect to the rotation axis direction is restricted by the anti-vibration rubber 14 and the stopper 15, but the configuration of the inclination restriction part is not limited to this. Here, restricting the inclination means that, as shown in FIG. 6, from the central axis L0 at both axial ends of the bearing pad 12 (both left and right ends in FIG. 6) on the plane including the central axis L0 and the axis La. This means that the change in the distance to the axis La is suppressed. In other words, it means that the angle formed by the central axis L0 and the axis La in FIG. Note that the angle formed by the central axis L0 and the axis line La is minimized when the central axis L0 and the axis line La are parallel.

  In the above embodiment, the anti-vibration rubber 14 and the stopper 15 are provided on both sides of the pivot 13 in the axial direction, but may be provided only on one side in the axial direction. In the above embodiment (FIG. 6), the bearing pad 12 is elastically supported from the bearing housing 11 by the anti-vibration rubber 14. In other words, the bearing pad 12 is elastically supported on the bearing housing 11 via the vibration isolating rubber 14, but another elastic supporting member such as a spring can be used instead of the vibration isolating rubber 14. In the above embodiment (FIG. 7), the stopper 15 is projected from the bearing housing 11 toward the back surface portion 22, but the configuration of the protruding member is not limited to that described above.

  Although the said embodiment applied the bearing apparatus to the steam turbine 1, the bearing apparatus of this invention is applicable similarly to other rotating machines, such as a gas turbine and a compressor.

  The above description is merely an example, and the present invention is not limited to the above-described embodiments and modifications unless the features of the present invention are impaired. The constituent elements of the embodiment and the modified examples include those that can be replaced while maintaining the identity of the invention and that are obvious for replacement. That is, other forms conceivable within the scope of the technical idea of the present invention are also included in the scope of the present invention. Moreover, it is also possible to arbitrarily combine one or more of the above-described embodiments and modified examples.

DESCRIPTION OF SYMBOLS 1 Steam turbine 2, 3 Rotating shaft 10 Bearing apparatus 11 Housing 12 Bearing pad 13 Pivot 14 Anti-vibration rubber 15 Stopper 21 Surface portion 22 Back surface portion 23 Oil supply port 25 Groove portion

Claims (5)

A support member provided around the rotation shaft;
A pad member that is disposed between the rotating shaft and the support member and has an arcuate surface portion facing the outer peripheral surface of the rotating shaft, and a back surface portion facing the support member;
A pivot part for tiltingly supporting the pad member with respect to the support member;
A lubricating oil supply section that supplies pressure oil for lubrication between the rotating shaft and the surface portion so that an oil film is formed between the rotating shaft and the surface portion;
An inclination restricting portion for restricting an inclination of the pad member with respect to an axial direction of the rotating shaft. The bearing device according to claim 1,
The lubricating oil supply unit
An oil supply port that opens to the surface portion and supplies lubricating oil toward the outer peripheral surface of the rotating shaft;
A groove provided in the surface portion in communication with the oil filler,
The groove part is formed symmetrically with each other on both sides of the axial direction of the oil filler opening. The bearing device according to claim 1 or 2,
The said inclination control part has an elastic support member which elastically supports the said pad member from the said support member, The bearing apparatus characterized by the above-mentioned. The bearing device according to any one of claims 1 to 3,
The said inclination control part has a protrusion member protrudingly provided toward the said back part of the said pad member from the said supporting member, The bearing apparatus characterized by the above-mentioned. In the bearing device according to any one of claims 1 to 4,
The inclination restricting portion is provided on both sides of the pivot portion in the axial direction.

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