Thrust Bearing Device

Abstract

To provide a thrust bearing device that can enhance reliability by keeping an oil film temperature low in a simple structure without using an auxiliary machine.SOLUTION: A thrust bearing device 100 according to an embodiment comprises: a plurality of stationary plates 110 opposed to a rotating plate, arranged in a circumferential direction, and each comprising a sliding member 112 in an upper surface; an annular supporting plate 14; and a plurality of elastic members 15 for transmitting a load of the stationary plates 110 to the supporting plate 14. The stationary plates 110 each comprise: a first inclined part 112a and a second inclined part 112b formed from each end part of the sliding member 112 on an upstream side and a downstream side in the circumferential direction over the whole area of the sliding member 112 in a radial direction; and an oil injection communication hole 114a formed so as to establish communication between at least one outflow port 116 provided in the second inclined part 112b, and at least one inflow port 115a provided in a portion facing lubricating oil 9 having a higher pressure than a pressure in the second inclined part.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] An embodiment of the present invention relates to a thrust bearing device. [Background technology]

[0002] A thrust bearing device generally used in a vertical shaft type rotating electric machine, such as a water turbine generator or a pumped-storage generating motor, supports the rotating bodies of the generator and the water turbine while bearing the weight of the rotating bodies of the generator and the water turbine as well as the water thrust force generated during operation of the rotating electric machine.

[0003] 9 is a partial cross-sectional elevation view showing the state of the stationary plate 10 during rotation of a rotor shaft (not shown) in a conventional thrust bearing device. Hereinafter, the circumferential direction and radial direction about the rotor shaft will be simply referred to as the circumferential direction and radial direction, respectively. FIG. 9 is a partial cross-sectional view of a cross section cut in the circumferential direction, viewed from the radially inner side. The support plate 14 of the thrust bearing device, the elastic members 15 such as coil springs attached to the support plate 14, and the stationary plates 10 mounted on the elastic members 15 are immersed in the lubricating oil 9 stored in an oil tank (not shown). The rotating plate 3, which rotates together with the rotor shaft while being supported from below by the stationary plates 10, is also in the lubricating oil 9. The lower surface of the rotating plate 3 and the upper surfaces of the stationary plates 10 provided below the rotating plate 3 face each other via an oil film of the lubricating oil 9. The white arrow indicates the rotation direction of the rotating plate 3. Only two of the stationary plates 10 are shown in FIG. 9.

[0004] The multiple stationary plates 10 are arranged at intervals in the circumferential direction. The weight of the rotating body including the members attached to the rotor shaft and the downward thrust force due to the water thrust generated during operation of the rotating electric machine are transmitted from the rotating plate 3 to the multiple stationary plates 10. The thrust force transmitted to the multiple stationary plates 10 is transmitted to the support plate 14 via the elastic member 15.

[0005] When the rotating plate 3 rotates, the lubricating oil 9 is drawn into the gap between the rotating plate 3 and the stationary plate 10 to form an oil film. This gap is a narrow gap of about several tens of micrometers to several hundreds of micrometers. As the rotating plate 3 rotates, the lubricating oil flows into this gap at a high speed of several tens of meters per second in the direction of rotation of the rotating plate 3. For this reason, an oil film pressure against the thrust force is generated in the oil film. During operation of the rotating electric machine, fluctuations in the rotation speed and fluctuations in the load due to the water thrust occur. The stationary plate 10 is elastically supported by the elastic member 15, so that the position and inclination of the stationary plate 10 have a degree of freedom. As a result, even if the load fluctuates, an appropriate oil film shape and oil film pressure are maintained. In the following, the side into which the lubricating oil 9 flows from the stationary plate 10 is called the upstream side, and the side from which it flows out is called the downstream side. In FIG. 9, in accordance with the flow direction of the lubricant 9, the two stationary plates 10 are shown as an upstream stationary plate 10a and a downstream stationary plate 10b.

[0006] In FIG. 9, a first inclined portion 12a is formed in the radial direction on the upstream portion of the upper surface of the stationary plate 10 to facilitate the flow of the lubricating oil into the gap between the upstream stationary plate 10a and the rotating plate 3. The lubricating oil 9, as indicated by the dashed arrow f11, that flows into the gap between the upstream stationary plate 10a and the rotating plate 3 rises in temperature due to friction caused by its viscosity. In addition, a second inclined portion 12b is formed in the radial direction on the downstream portion of the upper surface of the stationary plate 10 to facilitate the flow of the lubricating oil 9, whose temperature has risen, into the oil tank. The lubricating oil 9 that flows into the oil tank hits the upstream end face of the downstream stationary plate 10b and flows downward as indicated by the dashed arrow f21. For this reason, a circulating flow is formed as indicated by the dashed arrow f22. A part of the lubricating oil 9, whose temperature has been reduced in the oil tank, flows from the upstream end of the downstream stationary plate 10b into the gap between the downstream stationary plate 10b and the rotating plate 3 as indicated by the dashed arrow f23.

[0007] The temperature of the lubricating oil 9 increases while passing through the gap between the upstream stationary plate 10a and the rotating plate 3. A part of the lubricating oil 9 whose temperature has increased due to the flow indicated by f11 remains attached to the lower surface of the rotating plate 3 and flows into the gap between the rotating plate 3 and the downstream stationary plate 10b as indicated by the dashed arrow f12. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] U.S. Pat. No. 4,077,682 Summary of the Invention [Problem to be solved by the invention]

[0009] As described above, among the lubricating oil 9 whose temperature has risen during the process of passing through the gap between the upstream stationary plate 10a and the rotating plate 3, some of the lubricating oil 9 flows directly into the gap between the rotating plate 3 and the downstream stationary plate 10b as shown by the dashed arrow f12. The lubricating oil 9 that flows directly from the upstream stationary plate 10a to the downstream stationary plate 10b in this way can cause the temperature of the oil film to rise. If the temperature of the oil film becomes excessively high, the viscosity of the oil film decreases, so that sufficient oil film pressure is not generated. Since such an oil film cannot support the thrust force of the rotating body, there is a risk of contact between the rotating plate 3 and the stationary plate 10. In addition, if the temperature of the oil film becomes excessively high, there is a risk that the material strength of the sliding member provided on the upper surface of the stationary plate 10 and in contact with the oil film will decrease.

[0010] In light of this background, a method has been proposed in which low-temperature lubricating oil is forcibly sprayed from between adjacent stationary plates 10 toward the rotating plate 3, known as direct lubrication. With direct lubrication, the oil film can be maintained at a low temperature, reducing the risk of contact between the rotating plate and sliding members and the risk of a decrease in the material strength of the sliding members. For this reason, there are many examples of direct lubrication being put to practical use.

[0011] This type of direct lubrication method is effective in maintaining the oil film at a low temperature, but it also has disadvantages, such as the need for auxiliary equipment such as a pump to inject the lubricating oil, and the need for a structure to inject the lubricating oil.

[0012] An object of the present invention is to provide a thrust bearing device that has a simple structure without using any auxiliary equipment, and that is capable of maintaining a low oil film temperature and improving reliability. [Means for solving the problem]

[0013] According to an embodiment, the thrust bearing device is attached to a lower end of a thrust collar attached to a rotor shaft in a vertical shaft type rotating electric machine, and is disposed below a rotating plate that rotates inside an oil tank that stores lubricating oil, and rotatably supports the rotating plate, the thrust bearing device including: a plurality of stationary plates, disposed in the oil tank at intervals from one another in the circumferential direction so as to face the rotating plate, and having sliding members on their upper surfaces; a ring-shaped support plate, disposed in the oil tank below the plurality of stationary plates and receiving a load from the plurality of stationary plates; and a ring-shaped support plate, disposed in the oil tank at an upper surface of the support plate, and having sliding members for supporting the plurality of stationary plates. and a plurality of elastic members for mounting plates and transmitting loads from the plurality of stationary plates to the support plate, each of the plurality of stationary plates having a first inclined portion formed from an upstream end of the sliding member in the circumferential direction over the entire radial range of the sliding member, a second inclined portion formed from a downstream end of the sliding member in the circumferential direction over the entire radial range of the sliding member, and an oil injection communication hole formed to communicate at least one outlet provided in the second inclined portion with at least one inlet provided in a portion of the second inclined portion facing the lubricating oil having a pressure higher than that of the lubricating oil. The at least one inlet is provided in the first inclined portion. It is characterized by: [Brief description of the drawings]

[0014] [Figure 1] 1 is a partial elevational sectional view showing the configuration of an upper bearing including a thrust bearing device according to a first embodiment. [Diagram 2] 2 is a plan view taken along the line AA in FIG. 1, showing the arrangement and configuration of a stationary plate of the thrust bearing device according to the first embodiment. [Diagram 3] 3 is a vertical cross-sectional view taken along the line BB in FIG. 2, showing the configuration of a stationary plate of the thrust bearing device according to the first embodiment. [Figure 4] 3 is a partial sectional elevation view taken along the line BB in FIG. 2 during rotation of a rotor shaft, illustrating the effect of a stationary plate of the thrust bearing device according to the first embodiment. FIG. [Diagram 5] FIG. 11 is a partial plan view showing the configuration of a stationary plate of a thrust bearing device according to a second embodiment. [Figure 6] 6 is a sectional elevation view taken along the line CC in FIG. 5 during rotation of a rotor shaft, illustrating the effect of a stationary plate of a thrust bearing device according to a second embodiment. [Figure 7] FIG. 11 is a partial plan view showing the configuration of a stationary plate of a thrust bearing device according to a third embodiment. [Figure 8] 8 is a cross-sectional elevation view taken along the line DD in FIG. 7 during rotation of a rotor shaft, illustrating the effect of a stationary plate of a thrust bearing device according to a third embodiment. FIG. [Figure 9] 1 is a partial cross-sectional elevation view showing a state of a stationary plate during rotation of a rotor shaft in a conventional thrust bearing device. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0015] Hereinafter, a thrust bearing device according to an embodiment of the present invention will be described with reference to the drawings. Here, the same or similar parts are denoted by the same reference numerals, and duplicated explanations will be omitted.

[0016] [First embodiment] Fig. 1 is a partial elevational cross-sectional view showing the configuration of an upper bearing 5 including a thrust bearing device 100 according to a first embodiment. The left half is omitted in Fig. 1. This embodiment relates to a thrust bearing device 100 used in a vertical shaft type rotating electric machine.

[0017] The upper bearing 5 has a thrust bearing device 100, a guide bearing 6, and an oil tank 4 that stores lubricating oil 9. The thrust bearing device 100 and the guide bearing 6 are immersed in the lubricating oil 9 stored in the oil tank 4 and are supported stationary.

[0018] A rotor (not shown) is attached to rotor shaft 1, which rotates around a vertical rotation axis C. A thrust collar 2 is attached to the top of rotor shaft 1. An annular rotating plate 3 is attached to the bottom of thrust collar 2. The rotor shaft 11 and the rotor and thrust collar 2 attached thereto and rotating integrally therewith are collectively referred to as rotating body 7.

[0019] The thrust bearing device 100 is provided below the rotating plate 3. The thrust bearing device 100 supports the rotating body 7 against its own weight and the downward thrust force generated during operation of the rotating electric machine. The guide bearing 6 is disposed radially outside the thrust collar 2 and restricts radial movement of the rotating body 7.

[0020] The thrust bearing device 100 has a support plate 14 placed on the bottom of the oil tank 4, a plurality of elastic members 15 attached to the support plate 14, and a plurality of stationary plates 110 mounted on the tops of the plurality of elastic members 15. The plurality of stationary plates 110 are restrained by members (not shown) so as to maintain a planar position. Here, the elastic members 15 are not limited to coil springs as shown in Fig. 1, and may be leaf springs or air-type or other cushion-like members as long as they provide freedom in the height position and inclination of the stationary plates 110 and can maintain an appropriate oil film shape and oil film pressure through elastic support even when the load fluctuates.

[0021] As the rotating plate 3 rotates on top of multiple stationary plates 110, the frictional force between the underside of the rotating plate 3 and the lubricating oil 9 causes the lubricating oil 9 to flow between the underside of the rotating plate 3 and the upper surface of the stationary plates 110.

[0022] FIG. 2 is a plan view taken along the line AA in FIG. 1, showing the arrangement and configuration of the stationary plates 110 of the thrust bearing device 100 according to the first embodiment. FIG. 3 is a vertical cross-sectional view taken along the line BB in FIG. 2. In FIG. 3, only two of the multiple stationary plates 110 are shown as an upstream stationary plate 110p and a downstream stationary plate 110q. Here, the rotation direction of the rotating plate 3 is clockwise as viewed from above in the plan view of FIG. 2. Note that, in the following description, although the reference numerals for the two stationary plates 110 may be given to only one of them for convenience of illustration, they are common to each stationary plate 110.

[0023] As shown in Fig. 2, the stationary plates 110 have a shape obtained by dividing an annular flat plate in the circumferential direction. That is, the shape is formed by two concentric arcs centered on the center of rotation of the rotor shaft 1 and a straight line connecting the ends of each arc. The stationary plates 110 are arranged at intervals in the circumferential direction, with the wider side facing outward in the radial direction. Hereinafter, the direction facing outward from the rotor shaft 1 is referred to as the radial direction, and the circumferential direction from the rotor shaft 1 is referred to as the circumferential direction.

[0024] As shown in FIG. 3, each stationary plate 110 has a plate-like main body 111 that is sector-shaped when viewed from above, and a film-like sliding member 112 provided over the entire upper surface of the main body 111 .

[0025] A first inclined portion 112a, a second inclined portion 112b, and a planar effective sliding portion 112c excluding the first inclined portion 112a and the second inclined portion 112b are formed on the upper surface of the sliding member 112. In the sliding member 112, the planar effective sliding portion 112c has the greatest thickness, and the upstream end and downstream end portions have the smallest thickness.

[0026] In detail, a first inclined portion 112a whose thickness increases from the upstream end of the sliding member 112 in the circumferential direction toward the effective sliding portion 112c is formed over the entire radial area. Also, a second inclined portion 112b whose thickness increases from the downstream end of the sliding member 112 toward the effective sliding portion 112c on the upstream side is formed over the entire radial area.

[0027] As shown in Fig. 2, the second inclined portion 112b has outlets 116 spaced apart from each other in the radial direction. Also, as shown in Fig. 3, an inlet 115a is provided on the lower surface 110b of the stationary plate 110. An oil ejection communication hole 114a that communicates the inlet 115a and the outlet 116 is formed in the stationary plate 110. Fig. 3 shows an example in which the oil ejection communication hole 114a is formed in a direction perpendicular to the lower surface 110b of the stationary plate 110, but the oil ejection communication hole 114a may be inclined in a direction such that the flow resistance of the lubricating oil 9 is reduced.

[0028] 2 shows an example in which the number of outlets 116, i.e., the number of oil ejection holes 114a, is four, but is not limited to this. The number of outlets 116 and inlets 115a, i.e., the number of oil ejection holes 114a, may be at least one, three or less, or five or more, other than four.

[0029] FIG. 4 is a partial sectional elevation view taken along the line BB in FIG. 2, illustrating the effect of the stationary plate 110 of the thrust bearing device 100 according to the first embodiment while the rotor shaft 1 is rotating.

[0030] 4, the rotating plate 3 is moving from the left to the right. Therefore, due to friction with the rotating plate 3, the lubricating oil 9 flows from the left to the right in the figure through the gap 120 between the rotating plate 3 and the stationary plate 110, as indicated by the dashed arrow f11.

[0031] The graph shown above the cross-sectional view in FIG. 4 shows the oil film pressure along the flow direction.

[0032] In the first inclined portion 112a and the effective sliding portion 112c, the gap 120 narrows toward the downstream side of the rotation. In such a section, the lubricating oil 9 is forced into the gap 120, generating a positive pressure as shown in the graph of FIG. 4. On the other hand, in the second inclined portion 112b, the gap 120 widens toward the downstream side of the rotation. In such a section, the lubricating oil is released, generating a negative pressure as shown in the graph of FIG. 4.

[0033] The stationary plate 110 is inclined toward the upstream side in the circumferential direction while being mounted on the elastic member 15. The outlet 116 is formed at a position where the pressure of the lubricating oil 9 in the gap 120 becomes negative when the rotor 7 is in the rotating state as described above.

[0034] A part of the lubricating oil 9 that flows out from the gap between the upstream stationary plate 110p and the rotating plate 3 flows downward in the space between the upstream stationary plate 110p and the downstream stationary plate 110q as shown by the dashed arrow f21. A part of the lubricating oil 9 shown by the dashed arrow f21 returns upward again as shown by the dashed arrow f23.

[0035] On the other hand, the inlet 115a is located at the bottom of the oil tank 4 where the lubricating oil 9 at a relatively low temperature exists, and is formed at a location having a positive pressure equivalent to the hydrostatic head of the lubricating oil 9. Therefore, as shown by the dashed arrow f24, the lubricating oil 9 flows through the oil injection communication hole 114a that connects the inlet 115a located at the positive pressure location to the outlet 116 located at the negative pressure location, and is injected above the second inclined portion 112b.

[0036] Here, since the injected lubricating oil 9 is relatively cold, the lubricating oil 9 adhering to and flowing on the surface of the rotating plate 3 is cooled, and the cooled lubricating oil 9 adheres to the surface of the rotating plate 3 and flows into the gap 120 with the downstream stationary plate 110q.

[0037] As described above, in this embodiment, by flowing the lubricating oil 9 at a relatively low temperature into the gap 120, it is possible to suppress a decrease in the viscosity of the lubricating oil 9, maintain the oil film pressure, and support the thrust force of the rotor. This makes it possible to prevent the risk of contact between the rotating plate 3 and the stationary plate 110.

[0038] [Second embodiment] Fig. 5 is a partial plan view showing the configuration of the stationary plate 110 of the thrust bearing device 100 according to the second embodiment. Also, Fig. 6 is an elevational cross-sectional view taken along the line CC in Fig. 5, showing a state during one rotation of the rotor shaft, and explaining the effect of the stationary plate 110 of the thrust bearing device 100 according to the second embodiment. In each case, only two of the multiple stationary plates 110 are shown.

[0039] This embodiment is a modification of the first embodiment, and multiple outlets 116a are also provided in the first inclined portion 112a. Multiple inlets 115b are formed in the lower surface 110b below the outlets 116a of the stationary plate 110. Oil injection communication holes 114b are formed to connect each of the inlets 115b to each of the outlets 116a. In other respects, this embodiment is similar to the first embodiment.

[0040] Fig. 6 shows a case where the rotating plate 3 rotates in the opposite direction to that of the first embodiment. That is, the right side in Fig. 6 is the upstream side. Even in this case, the oil injection communication hole 114b is formed on the downstream side of the flow, i.e., in the first inclined portion 112a, so that the effect of cooling the lubricating oil film can be obtained similarly to the first embodiment.

[0041] The difference from the first embodiment is that the original oil injection communication 114a is formed on the second inclined portion 112b side, which is the upstream side when the stationary plate 110 rotates in the opposite direction to the first embodiment. As shown in FIG. 4, a positive pressure is formed on the upper surface of the inclined portion on the upstream side, but a positive pressure is also generated on the lower surface side due to the hydrostatic head. That is, in the case of the oil injection communication hole 114b, one side is connected to the part with a positive pressure and the other side is connected to the part with a negative pressure, so the pressure difference is large. On the other hand, in the case of the oil injection communication 114a, as described above, the positive pressure parts are connected to each other, so the pressure difference is small. In addition, the flow resistance from the flow indicated by the dashed arrow f12 to the oil injection communication 114a side is large. Therefore, the flow rate of the lubricating oil 9 flowing from the flow indicated by the dashed arrow f12 on the upstream side to the oil injection communication 114a side is sufficiently small.

[0042] The configuration of this embodiment is particularly effective in the case of a generator motor in a pumped-storage power station, since the rotation direction of the rotor 7 is reversed when the motor is operated as a generator to generate electricity and when the motor is operated as a motor to pump water to a dam.

[0043] [Third embodiment] Fig. 7 is a partial plan view showing the configuration of the stationary plate 110 of the thrust bearing device 100 according to the third embodiment. Fig. 8 is a vertical cross-sectional view taken along line DD in Fig. 7, showing a state during rotation of the rotor shaft, for explaining the effect of the stationary plate 110 of the thrust bearing device 100 according to the third embodiment. Note that Fig. 7 shows only one stationary plate 110.

[0044] In this embodiment, the outlet 116 is provided at the same position as in the first embodiment. On the other hand, the inlet 115c is provided in the first inclined portion 112a. The oil ejection communication hole 114c is formed so as to connect the inlet 115c and the outlet 116. Other than this, it is the same as the first embodiment.

[0045] 8, the oil injection communication hole 114c is formed by forming a first and a second hole from the inlet 115c and the outlet 116 to a position midway toward the lower surface 110b of the stationary plate 110, respectively, and a third hole that linearly connects the tip portions of these holes. The third hole can be formed by forming a through hole from the upstream side surface 110c to the downstream side surface 110d of the stationary plate 110, and then closing both sides of this through hole.

[0046] In the stationary plate 110 of the thrust bearing device 100 of this embodiment formed in this manner, the oil injection communication holes 114c are formed to connect between the first inclined portion 112a where the pressure of the lubricating oil 9 is high and the second inclined portion 112b where the pressure of the lubricating oil 9 is low, so that the lubricating oil 9, which has not passed through the effective sliding portion 112c and has not yet risen in temperature, is supplied to the gap 120 between the second inclined portion 112b and the rotating plate 3. For this reason, it is possible to obtain the same effect as in the first embodiment.

[0047] Furthermore, the stationary plate 110 is cooled from the inside by passing the lubricating oil 9 before its temperature rises through the oil injection communication holes 114c formed inside the stationary plate 110 in the flow direction of the lubricating oil 9. As a result, the temperature of the effective sliding portion 112c of the stationary plate 110 drops, and the temperature rise of the lubricating oil 9 in the gap 120 can be suppressed.

[0048] Furthermore, in this embodiment, the same effect can be obtained even if the rotating plate 3 rotates in the opposite direction, and similarly to the second embodiment, the effect is particularly great when applied to a generator motor in a pumped-storage power station.

[0049] According to the embodiment described above, it is possible to provide a thrust bearing device 100 that is capable of maintaining a low oil film temperature and improving reliability with a simple structure without using any auxiliary equipment.

[0050] Although several embodiments of the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and spirit of the invention, and are included in the scope of the invention and its equivalents described in the claims. [Explanation of symbols]

[0051] Reference Signs List 1...rotor shaft, 2...thrust collar, 3...rotating plate, 4...oil tank, 5...upper bearing, 6...guide bearing, 7...rotating body, 9...lubricating oil, 10...conventional stationary plate, 10a...upstream stationary plate, 10b...downstream stationary plate, 12a...first inclined portion, 11b...second inclined portion, 14...support plate, 15...elastic member, 100...thrust bearing device, 110...stationary plate, 110a...upper surface, 110b...lower surface, 110c...upstream side surface , 110d... downstream side surface, 110e... radially inner side surface, 110f... radially outer side surface, 110p... upstream side stationary plate, 110q... downstream side stationary plate, 111... main body, 112... sliding member, 112a... first inclined portion, 112b... second inclined portion, 112c... effective sliding portion, 114a, 114b, 114c... oil injection communication hole, 115a, 115b, 115c... inlet, 116, 116a... outlet, 120... gap

Claims

1. 1. A thrust bearing device for a vertical shaft type rotating electric machine, the thrust bearing device being attached to a lower end of a thrust collar attached to a rotor shaft, the thrust collar being disposed below a rotating plate that rotates inside an oil tank that stores lubricating oil, and rotatably supporting the rotating plate, the thrust bearing device comprising: a plurality of stationary plates disposed in the oil tank at intervals in a circumferential direction so as to face the rotating plate and having sliding members on their upper surfaces; an annular support plate disposed in the oil tank below the plurality of stationary plates and receiving a load from the plurality of stationary plates; a plurality of elastic members attached to an upper surface of the support plate in the oil tank, carrying the plurality of stationary plates, and transmitting loads from the plurality of stationary plates to the support plate; Equipped with Each of the plurality of stationary plates is a first inclined portion formed from an upstream end of the sliding member in a circumferential direction over an entire radial area of ​​the sliding member; a second inclined portion formed from a downstream end of the sliding member in a circumferential direction over an entire radial area of ​​the sliding member; an oil injection communication hole formed to communicate at least one outlet provided in the second inclined portion with at least one inlet provided in a portion of the second inclined portion facing the lubricating oil having a pressure higher than the pressure of the lubricating oil; having The thrust bearing device according to claim 1, wherein the at least one inlet is provided in the first inclined portion.

2. the at least one outlet comprises a plurality of outlets; The plurality of outlets are spaced apart from one another in the radial direction.

2. The thrust bearing device according to claim 1, wherein the thrust bearing device is a bearing having a first end and a second end.

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