JP2019108966A - Bearing device and rotary machine - Google Patents

Abstract

To provide a bearing device which can be used in a wider temperature range.SOLUTION: A bearing device includes: a bearing pad 41 having a pad surface 41A slidably supporting an outer peripheral surface of a rotary shaft which rotates around an axis; a liner 42A which fits in an outer peripheral surface of the bearing pad 41; a carrier ring which forms an annular shape with the axis set its center so as to cover the bearing pad 41 and the liner 42A from the outer peripheral side and houses the bearing pad 41 and the liner 42A at the inner side; and a support part 44 provided on an inner peripheral surface of the carrier ring and swingably supporting the liner. Rigidity of the liner 42A is lower than those of the bearing pad 41, the carrier ring, and the support part 44.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a bearing device and a rotary machine.

  A rotary machine such as a steam turbine or a gas turbine includes a rotor, a moving blade provided on the rotor, a casing for housing the rotor, and a stationary blade provided on the casing. As the rotor rotates about its own axis, working fluid flows through the inside of the casing.

  In order to facilitate smooth rotation of the rotor, the axial end of the rotor is generally supported by a bearing device. As an example of such a bearing device, a tilting pad bearing described in Patent Document 1 below is known. The bearing has a plurality of pivots provided on an annular bearing outer ring, and a plurality of bearing pads pivotally supported by the pivots. The inner circumferential surface of the bearing pad is in sliding contact with the outer circumferential surface of the rotor via lubricating oil to support the same.

  Here, in order to suppress the vibration of the rotor, the clearance between the bearing pad and the rotor may be made smaller than the processing radius clearance at the time of assembly. As a result, an initial load (preload) is applied between the bearing pads and the rotor, and the vibration of the rotor can be reduced.

JP 10-228220 A

  However, when the rotor rotates, shear heat generation of the lubricating oil causes the temperature of the rotor and the bearing pads to rise. As the temperature rises, thermal expansion occurs on the rotor and the bearing pad to the side where the bearing gap is clogged. As a result, the load and heat generation between the rotor and the bearing pads may increase and cause damage to the rotor or the bearing pads. As a result, stable operation of the rotary machine is impeded.

  The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a bearing device and a rotary machine which can be used in a wider temperature range.

  According to a first aspect of the present invention, a bearing device includes a bearing pad having a pad surface slidably supporting an outer peripheral surface of a rotating shaft rotating about an axis, and the bearing pad is fitted to the outer peripheral surface of the bearing pad A liner, an annular ring centered on the axis so as to cover the bearing pad and the liner from the outer circumferential side, a carrier ring for receiving the bearing pad and the liner inside, and an inner circumferential surface of the carrier ring And a support that pivotally supports the liner, wherein the rigidity of the liner is lower than that of the bearing pad, the carrier ring, and the support.

  According to this configuration, since the rigidity of the liner is lower than the rigidity of the bearing pad, the carrier ring, and the support portion, when thermal expansion occurs in the rotating shaft and the bearing pad, the load from the bearing pad gives priority to the liner. To be deformed. Thereby, the clearance between the rotating shaft and the bearing pad can be maintained.

  According to the second aspect of the present invention, a housing having a support surface for supporting the carrier ring from the outer peripheral side, a key formed at the same position in the circumferential direction on the support surface and the outer peripheral surface of the carrier ring The key member may be inserted into the groove, and the rigidity of the key member may be lower than that of the bearing pad, the support, and the carrier ring.

  According to this configuration, since the rigidity of the key member is lower than the rigidity of the bearing pad, the support portion, and the carrier ring, when the rotary shaft, the bearing pad, and the carrier ring undergo thermal expansion, the load from the carrier ring Causes the key member to deform preferentially. Thereby, the clearance between the rotating shaft and the bearing pad can be maintained.

  According to a third aspect of the present invention, the liner has a liner support surface that abuts on the outer peripheral surface of the bearing pad, and is recessed radially inward from the axial direction on the liner support surface. A liner recess may be formed.

  According to this configuration, the bearing pad can be stably supported by the liner support surface, and the rigidity of the liner can be lowered by forming the liner recess. Thus, when the load from the bearing pad is increased, the liner can be easily deformed in the direction in which the liner recess extends.

  According to the fourth aspect of the present invention, the rigidity of the key member may be smaller than the rigidity of the liner.

  According to this configuration, since the rigidity of the key member is smaller than the rigidity of the liner, when a load is applied to the key member and the liner, the key member is deformed preferentially. That is, while maintaining the state in which the bearing pad is stably supported by the liner, the load can be released by the deformation of the key member.

  According to the fifth aspect of the present invention, the key member has a key support surface that abuts on the outer peripheral surface of the carrier ring, and the key support surface is directed from the inside to the outside in the radial direction with respect to the axis. A recessed key recess may be formed.

  According to this configuration, the carrier ring can be stably supported by the key support surface, and the rigidity of the key member can be lowered by forming the key recess. Thus, when the load from the carrier ring increases, the key member can be easily deformed in the direction in which the key recess is spread.

  According to a sixth aspect of the present invention, a plurality of the bearing pads circumferentially spaced apart, the liner, and the support portion are provided, with respect to an axis extending in the horizontal direction as a reference rather than the axis The rigidity of only the upper liner may be lower than that of the bearing pad, the carrier ring, and the support.

  When the bearing device supports a rotating shaft in which the axis extends in the horizontal direction, the bearing pad, liner, and supporting portion below the axis have high rigidity because they support the weight of the rotating shaft. There is a need. On the other hand, bearing pads, liners, and supports above the axis are not affected by the weight of the rotating shaft. According to the above configuration, while the weight of the rotating shaft is stably supported by the lower bearing pad, the liner, and the support portion, only the upper liner is prioritized by lowering the rigidity of only the upper liner. Can be deformed.

  According to the seventh aspect of the present invention, the bearing device includes a bearing pad having a pad surface slidably supporting an outer peripheral surface of a rotating shaft rotating about an axis, and the bearing pad is fitted to the outer peripheral surface of the bearing pad A liner, an annular ring centered on the axis so as to cover the bearing pad and the liner from the outer circumferential side, a carrier ring for receiving the bearing pad and the liner inside, and an inner circumferential surface of the carrier ring A support portion for swingably supporting the liner, a housing having a support surface for supporting the carrier ring from the outer peripheral side, the support surface, and the same circumferential position on the outer peripheral surface of the carrier ring And a key member inserted into the formed key groove, wherein the rigidity of the key member is lower than that of the bearing pad, the liner, the carrier ring, and the support portion. .

  According to this configuration, when the rigidity of the key member is lower than the rigidity of the bearing pad, the support portion, the carrier ring, and the support portion, thermal expansion occurs in the rotary shaft, the bearing pad, the carrier ring, and the support portion The load from the carrier ring preferentially deforms the key member. Thereby, the clearance between the rotating shaft and the bearing pad can be maintained.

  According to the eighth aspect of the present invention, the key member has a key support surface that abuts on the outer peripheral surface of the carrier ring, and the key support surface extends radially inward from the axis with respect to the axis. A recessed key recess may be formed.

  According to this configuration, the carrier ring can be stably supported by the key support surface, and the rigidity of the key member can be lowered by forming the key recess. Thus, when the load from the carrier ring increases, the key member can be easily deformed in the direction in which the key recess is spread.

  A rotary machine according to a ninth aspect of the present invention includes any one of the bearing devices described above.

  According to the present invention, it is possible to provide a bearing device and a rotary machine which can be used in a wider temperature range.

It is a mimetic diagram showing composition of a steam turbine concerning a first embodiment of the present invention. It is a figure showing composition of a bearing device concerning a first embodiment of the present invention. It is a principal part enlarged view of the bearing apparatus which concerns on 1st embodiment of this invention, Comprising: It is a figure which shows the state before a liner deform | transforms. It is a principal part enlarged view of the bearing apparatus which concerns on 1st embodiment of this invention, Comprising: It is a figure which shows the state which the liner deformed. It is a principal part enlarged view of the bearing apparatus which concerns on 2nd embodiment of this invention, Comprising: It is a figure which shows the state before a key member deform | transforms.

First Embodiment
A first embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1, the steam turbine 1 (rotary machine) includes a steam turbine rotor 3 (rotary shaft) extending along the direction of the axis O, and a steam turbine casing 2 (casing) covering the steam turbine rotor 3 from the outer peripheral side. A journal bearing 4 (bearing device) rotatably supporting an axial end 11 of the steam turbine rotor 3 about an axis O, and a thrust bearing 5 are provided.

  The steam turbine rotor 3 has a plurality of moving blades 30. A plurality of moving blades 30 are arrayed at regular intervals in the circumferential direction of the steam turbine rotor 3. Also in the direction of the axis O, the rows of the plurality of moving blades 30 are arranged at constant intervals. The blade 30 has a blade body 31 and a blade shroud 34 (shroud). The wing body 31 protrudes radially outward from the outer peripheral surface of the steam turbine rotor 3. The wing body 31 has a wing-shaped cross section as viewed in the radial direction. A moving blade shroud 34 is provided at the tip end (radially outer end) of the wing body 31.

  The steam turbine casing 2 has a substantially cylindrical shape covering the steam turbine rotor 3 from the outer peripheral side. A steam supply pipe 12 for taking in steam is provided on one side in the direction of the axis O of the steam turbine casing 2. On the other side of the steam turbine casing 2 in the direction of the axis O, a steam discharge pipe 13 for discharging steam is provided. In the following description, the side where the steam supply pipe 12 is located as viewed from the steam discharge pipe 13 is referred to as the upstream side, and the side where the steam discharge pipe 13 is located as viewed from the steam supply pipe 12 is referred to as the downstream side.

  A plurality of stationary blades 21 are provided along the inner peripheral surface of the steam turbine casing 2. The stationary blade 21 is a blade-like member connected to the inner peripheral surface of the steam turbine casing 2 via the stationary blade pedestal 24. Further, a vane shroud 22 is provided at a tip end (a radially inner end) of the vane 21. Similar to the moving blades 30, a plurality of the stationary blades 21 are arranged along the circumferential direction and the direction of the axis O on the inner circumferential surface. The moving blade 30 is disposed to enter an area between the plurality of adjacent stationary blades 21.

  In the inside of the steam turbine casing 2, a region in which the stationary blades 21 and the moving blades 30 are arranged forms a main flow passage 20 through which the steam S, which is a working fluid, flows. Between the inner circumferential surface of the steam turbine casing 2 and the bucket shroud 34, a recess 50 that is recessed radially outward with respect to the axis O is formed over the entire circumferential direction. The recess 50 forms a cavity that accommodates the tip of the moving blade 30 (moving blade shroud 34). That is, the recess 50 has a sufficiently large volume compared to the volume of the bucket shroud 34.

  The steam S is supplied via the upstream steam supply pipe 12 to the steam turbine 1 configured as described above. Thereafter, as the steam turbine rotor 3 rotates, it passes through the row of the stationary blades 21 and the moving blades 30 and is eventually discharged toward the subsequent device (not shown) through the downstream steam discharge pipe 13. When passing the row of the stationary blades 21 and the moving blades 30, the steam S also flows into the above-described recess 50.

  The journal bearing 4 supports a load in the radial direction with respect to the axis O. One journal bearing 4 is provided at each end of the steam turbine rotor 3. The thrust bearing 5 supports a load in the direction of the axis O. The thrust bearing 5 is provided only at the upstream end of the steam turbine rotor 3.

  FIG. 2 is a view showing the detailed configuration of the journal bearing 4. As shown in the figure, the journal bearing 4 includes a plurality of (four) bearing pads 41, a liner 42 fitted on the outer peripheral surface of the bearing pads 41, and a carrier ring 43 for receiving the bearing pads 41 and the liner 42. , A support portion 44 for supporting the liner 42, and a key member 90.

  The bearing pad 41 is substantially fan-shaped in a cross-sectional view orthogonal to the axis O. More specifically, the cross section of the bearing pad 41 gradually expands in size in the circumferential direction as it goes from the radially inner side to the outer side ing. The radially inward facing surface of the bearing pad 41 is a pad surface 41 A that slidably supports the outer peripheral surface of the steam turbine rotor 3. The pad surface 41A has an arc shape which is recessed from the radially inner side to the outer side. The radius of curvature of the pad surface 41A is slightly larger than the radius of curvature of the outer peripheral surface of the steam turbine rotor 3. That is, only a partial region of the pad surface 41A is in sliding contact with the outer peripheral surface of the steam turbine rotor 3. Lubricating oil is supplied onto the pad surface 41A from a device (not shown). The lubricating oil forms an oil film between the pad surface 41 A and the outer peripheral surface of the steam turbine rotor 3.

  The surface (pad outer peripheral surface 41B) which faces the radial direction outer side of the bearing pad 41 protrudes in circular arc shape toward the outer side from radial direction inner side. An accommodation groove 45 for accommodating a liner 42 described later is formed in the pad outer peripheral surface 41B. The accommodation groove 45 has a rectangular groove shape which is recessed inward from the radially outer side in a cross-sectional view orthogonal to the axis O. The accommodation groove 45 is formed at a substantially central position of the arc of the pad outer peripheral surface 41B.

  The liner 42 is fitted into the above-mentioned receiving groove 45. In the present embodiment, the shapes of the pair of liners 42 (upper liner 42A) located above the axis O and the liners 42 (lower liner 42B) located below the axis O are different.

  As shown in FIG. 3, the upper liner 42A has a bottomed cylindrical shape. Specifically, the upper liner 42A has a liner bottom 51 and a liner side 52. The liner bottom 51 has a circular shape when viewed in the radial direction with respect to the axis O. The liner side portion 52 cylindrically extends radially inward from the edge of the liner bottom 51. A region surrounded by the radially inner surface of the liner bottom portion 51 and the inner circumferential surface of the liner side portion 52 is a liner recess 53. That is, the liner recess 53 opens radially inward. Furthermore, in other words, the liner recess 53 is recessed outward in the radial direction.

  The radially inner end surface of the liner side portion 52 is a liner support surface 54 that abuts on the outer peripheral surface (the accommodation groove 45) of the bearing pad 41. The liner support surface 54 has an annular shape as viewed in the radial direction with respect to the axis O. The bearing pad 41 is supported from the radially outer side only by the liner support surface 54. Therefore, when a load directed from the radially inner side to the outer side acts on the bearing pad 41, stress is generated only in the center portion of the liner support surface 54 and the liner bottom portion 51 between the bearing pad 41 and the support portion 44 described later. As a result, as shown in FIG. 4, in the liner 42, the liner bottom 51 preferentially deforms so as to protrude radially inward. That is, the rigidity of the liner 42 is lower than the rigidity of the bearing pad 41, the carrier ring 43, and the support portion 44.

  On the other hand, the lower liner 42B has a cylindrical shape. That is, the lower liner 42B does not have the liner recess 53 formed in the upper liner 42A. The radially inward facing surface of the lower liner 42B abuts the inner surface of the accommodation groove 45 without any gap.

  A plurality of (four) support portions 44 are provided on the inner peripheral surface of the carrier ring 43 (on the ring inner peripheral surface 43A) at equal intervals in the circumferential direction. The support portion 44 protrudes radially inward from the ring inner circumferential surface 43A. The distal end surface (radially inner end surface) of the support portion 44 has a hemispherical shape. Thus, the support portion 44 supports the surface (the liner outer surface 55) of the liner bottom 51 facing radially outward. That is, the liner 42 and the bearing pad 41 are swingably supported on the support portion 44.

  In addition, the aspect of the support part 44 is not limited above. As another example of the support portion 44, a member having the same cross-sectional shape as that described above and continuously extending in the direction of the axis O can also be used as the support portion 44. In this case, the liner outer surface 55 and the support portion 44 make line contact.

  The carrier ring 43 has an annular (cylindrical) shape centered on the axis O. The carrier ring 43 is supported from below by a housing 80 installed on the floor surface. In the cross-sectional view orthogonal to the axis O, the upper half of the housing 80 is formed with a housing portion 81 recessed in a circular arc shape from the upper side to the lower side. The inner surface of the housing portion 81 is a support surface 81 A that supports the carrier ring 43.

  A pair of key grooves 43C and a B key groove 82 are formed at the same positions in the circumferential direction of the carrier ring 43 and the support surface 81A. The key groove 43 </ b> C has an angular groove shape which is recessed inward in the radial direction with respect to the axis O from the outer peripheral surface of the carrier ring 43. The B-key groove 82 has an angular groove shape which is recessed outward in the radial direction with respect to the axis O from the support surface 81A. The key member 90 is inserted into the key groove 43C and the B key groove 82 in a state where the positions of the key groove 43C and the B key groove 82 in the circumferential direction coincide with each other. The key member 90 is provided to prevent the carrier ring 43 from rolling on the support surface 81A.

  Next, operations of the steam turbine 1 and the journal bearing 4 according to the present embodiment will be described. When operating the steam turbine 1, high temperature and high pressure steam is supplied from the external steam supply source (not shown) to the inside (main flow passage 20) of the steam turbine casing 2 through the steam supply pipe 12. The steam forms a flow that flows from the upstream side toward the downstream side along the main flow passage 20. The steam flow alternately collides with the stationary blades 21 and the moving blades 30 to impart rotational force to the steam turbine rotor 3 via the moving blades 30. The rotation of the steam turbine rotor 3 is taken out from the shaft end to drive an external device such as a generator (not shown).

  While the steam turbine 1 is in operation, the journal bearing 4 rotatably supports the steam turbine rotor 3. Here, as the steam turbine rotor 3 rotates, the temperatures of the steam turbine rotor 3 and the bearing pads 41 rise. This temperature rise causes thermal expansion of the steam turbine rotor 3 and the bearing pads 41. When the thermal expansion is enhanced, the clearance between the outer peripheral surface of the steam turbine rotor 3 and the pad surface 41A is reduced. As a result, the surface pressure between the steam turbine rotor 3 and the pad surface 41A may increase, which may cause so-called holding.

  However, in the journal bearing 4 according to the present embodiment, the liner recess 53 is formed in the liner 42 (upper liner 42A). That is, the rigidity of the liner 42 is lower than the rigidity of the bearing pad 41, the carrier ring 43, and the support portion 44. Therefore, when a load directed from the inside to the outside in the radial direction acts on the bearing pad 41, stress is generated only at the liner support surface 54 and the central portion of the liner bottom 51. As a result, as shown in FIG. 4, in the liner 42, the liner bottom 51 preferentially deforms so as to protrude radially inward. In other words, in the liner 42, deformation occurs such that the liner recess 53 expands in the circumferential direction. Thus, even when the temperatures of the steam turbine rotor 3 and the bearing pads 41 rise, the clearance between the outer circumferential surface of the steam turbine rotor 3 and the pad surface 41A can be maintained. In other words, the journal bearing 4 of the present embodiment can be used in a wider temperature range.

  As described above, according to the configuration according to the present embodiment, the rigidity of the liner 42 is lower than the rigidity of the bearing pad 41, the carrier ring 43, and the support portion 44. When thermal expansion occurs, the load from the bearing pad 41 preferentially deforms the liner 42. Thereby, the clearance between the rotating shaft and the bearing pad 41 can be maintained.

  Furthermore, in the above-described configuration, the liner 42 has the liner support surface 54 that abuts on the outer peripheral surface of the bearing pad 41, and on the liner support surface 54, a liner recess that is recessed outward in the radial direction with respect to the axis O 53 are formed. According to this configuration, the bearing pad 41 can be stably supported by the liner support surface 54, and the rigidity of the liner 42 can be lowered by forming the liner recess 53. Thus, when the load from the bearing pad 41 increases, the liner 42 can be easily deformed in the direction in which the liner recess 53 spreads.

  In addition, in the above configuration, the rigidity of only the liner 42 located above the axis O is lower than that of the bearing pad 41, the carrier ring 43, and the support portion 44 with respect to the axis O extending in the horizontal direction.

  Here, in order to support the weight of the steam turbine rotor 3, the bearing pad 41 below the axis O, the liner 42, and the support portion 44 need to have high rigidity. On the other hand, the bearing pad 41, the liner 42, and the support portion 44 above the axis O are not affected by the weight of the steam turbine rotor 3. According to the above configuration, while the weight of the steam turbine rotor 3 is stably supported by the lower bearing pad 41, the liner 42, and the support portion 44, the rigidity of only the upper liner 42 is lowered. Only the upper liner 42 can be deformed preferentially.

  The first embodiment of the present invention has been described above. Note that various changes and modifications can be made to the above-described configuration without departing from the scope of the present invention. For example, in the above embodiment, an example in which four bearing pads 41 are provided has been described. However, the number of bearing pads 41 is not limited to four, and may be three or five or more as needed.

  Furthermore, the shape of the liner 42 is not limited by the above embodiment, and the liner 42 may have any shape as long as the rigidity can be made relatively low with respect to the bearing pad 41, the support portion 44, and the carrier ring 43. Is also possible. As another example, for example, it is possible to form a plurality of grooves extending radially from the central portion on the radially inner end surface of the liner 42. As yet another example, it is possible to form a plurality of radially extending through holes in the liner 42. In either configuration, the rigidity of the liner 42 can be relatively low.

Second Embodiment
Subsequently, a second embodiment of the present invention will be described with reference to FIG. In addition, about the structure similar to the said 1st embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted. In the present embodiment, in addition to the configuration described in the first embodiment, the rigidity of the key member 90 is lower than the rigidity of the bearing pad 41, the liner 42, the carrier ring 43, and the support portion 44.

  More specifically, as shown in FIG. 5, the key member 90 has a key bottom portion 91 and a key side portion 92 in a cross-sectional view orthogonal to the axis O. The key bottom 91 and the key side 92 extend in the direction of the axis O. The key side 92 cylindrically extends radially inward from the edge of the key bottom 91. An area surrounded by the radially inner surface of the key bottom portion 91 and the inner circumferential surface of the key side portion 92 is a key concave portion 93. That is, the key recess 93 opens radially inward. Furthermore, in other words, the key recess 93 is recessed outward in the radial direction.

  The radially inner end surface of the key side portion 92 is a key support surface 94 that abuts on the outer peripheral surface (key groove 43C) of the carrier ring 43. The carrier ring 43 is supported from outside in the radial direction only by the key support surface 94. Therefore, when a load acting from the radially inner side to the outer side acts on the carrier ring 43 or when the carrier ring 43 itself thermally expands and spreads radially outward, only the central portion of the key support surface 94 and the key bottom portion 91 Is stressed. As a result, in the key member 90, the key bottom portion 91 is preferentially deformed so as to protrude radially inward. That is, the rigidity of the key member 90 is lower than the rigidity of the bearing pad 41, the carrier ring 43, and the support portion 44. Further, the rigidity of the key member 90 is set to be lower than the rigidity of the liner 42 described above.

  As described above, according to the configuration according to the present embodiment, since the rigidity of the key member 90 is lower than the rigidity of the bearing pad 41, the support portion 44, and the carrier ring 43, the steam turbine rotor 3 and the bearing pad When thermal expansion occurs in the carrier ring 41 and the carrier ring 43, the load from the carrier ring 43 causes the key member 90 to be deformed preferentially. Thereby, the clearance between the steam turbine rotor 3 and the bearing pad 41 can be maintained.

  Further, according to the above configuration, since the rigidity of the key member 90 is smaller than the rigidity of the liner 42, when a load is applied to the key member 90 and the liner 42, the key member 90 is deformed preferentially. . That is, while maintaining the state in which the bearing pad 41 is stably supported by the liner 42, the load can be released by the deformation of the key member 90.

  In addition, according to the above configuration, the key member 90 has the key support surface 94 that abuts on the outer peripheral surface of the carrier ring 43, and the key recess 93 is formed on the key support surface 94. According to this configuration, the carrier ring 43 can be stably supported by the key support surface 94, and the rigidity of the key member 90 can be reduced by the formation of the key recess 93. Thus, when the load from the carrier ring 43 is increased, the key member 90 can be easily deformed in the direction in which the key recess 93 spreads.

The second embodiment of the present invention has been described above. Note that various changes and modifications can be made to the above-described configuration without departing from the scope of the present invention. For example, the shape of the key member 90 is not limited by the above embodiment, and the key member 90 may have any shape as long as the rigidity can be made relatively low with respect to the bearing pad 41, the support portion 44, and the carrier ring 43. It is also possible to take.
Moreover, although the example which applied this invention to the steam turbine 1 as a rotary machine was demonstrated in embodiment, it is not limited to this, for example, you may apply this invention to other rotary machines, such as a gas turbine, etc. .

1 ... Steam turbine (rotary machine)
2 ... steam turbine casing 3 ... steam turbine rotor 4 ... journal bearing (bearing device)
DESCRIPTION OF REFERENCE NUMERALS 5 thrust bearing 6 seal fin 11 shaft end 12 steam supply pipe 13 steam discharge pipe 20 main flow path 24 vane base 30 blade 31 blade body 34 blade shroud 41 bearing pad 42 Liner 43: Carrier ring 44: Support portion 45: Housing groove 51: Liner bottom portion 52: Liner side portion 53: Liner recess 54: Liner support surface 55: Liner outer surface 80: Housing 81: Housing portion 82: B key groove 90: Key Member 91: Key bottom portion 92: Key side portion 93: Key concave portion 94: Key support surface 41A: Pad surface 41B: Pad outer peripheral surface 42A: Upper liner 42B: Lower liner 43A: Ring inner peripheral surface 43B: Ring outer peripheral surface 43C: Key Groove 81A ... Support surface O ... Axis

Claims (9)

A bearing pad having a pad surface slidably supporting an outer peripheral surface of a rotating shaft rotating about the axis;
A liner fitted to the outer peripheral surface of the bearing pad;
An annular ring centered on the axis so as to cover the bearing pad and the liner from the outer peripheral side, and a carrier ring for receiving the bearing pad and the liner inside;
A support portion provided on an inner circumferential surface of the carrier ring and pivotally supporting the liner;
Equipped with
A bearing device wherein the stiffness of the liner is lower than the bearing pad, the carrier ring, and the support. A housing having a support surface for supporting the carrier ring from the outer peripheral side;
A key member inserted into a key groove respectively formed at the same position in the circumferential direction on the support surface and the outer peripheral surface of the carrier ring;
And further
The bearing device according to claim 1, wherein the rigidity of the key member is lower than that of the bearing pad, the support portion, and the carrier ring.   The liner according to claim 1, wherein the liner has a liner support surface that abuts on the outer peripheral surface of the bearing pad, and the liner support surface is formed with a liner recess that is recessed radially inward from the axis. The bearing apparatus as described in 2.   The bearing device according to claim 2, wherein the rigidity of the key member is lower than the rigidity of the liner.   The key member has a key support surface that abuts on the outer peripheral surface of the carrier ring, and a key recess is formed on the key support surface so as to be recessed outward in the radial direction with respect to the axis. Or the bearing apparatus as described in 4. A plurality of said circumferentially spaced bearing pads, said liners, and said supports;
The rigidity of only the liner located above the axis with respect to the axis extending in the horizontal direction is smaller than that of the bearing pad, the carrier ring, and the support portion. Bearing device as described. A bearing pad having a pad surface slidably supporting an outer peripheral surface of a rotating shaft rotating about the axis;
A liner fitted to the outer peripheral surface of the bearing pad;
An annular ring centered on the axis so as to cover the bearing pad and the liner from the outer peripheral side, and a carrier ring for receiving the bearing pad and the liner inside;
A support portion provided on an inner circumferential surface of the carrier ring and pivotally supporting the liner;
A housing having a support surface for supporting the carrier ring from the outer peripheral side;
A key member inserted into a key groove respectively formed at the same position in the circumferential direction on the support surface and the outer peripheral surface of the carrier ring;
Equipped with
A bearing device in which the rigidity of the key member is lower than that of the bearing pad, the liner, the carrier ring, and the support portion.   8. The key member according to claim 7, further comprising: a key support surface that abuts on an outer peripheral surface of the carrier ring, and a key recess that is recessed outward in the radial direction with respect to the axis is formed on the key support surface. Bearing device described in.   A rotary machine comprising the bearing device according to any one of claims 1 to 8.

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