JP2014202280A - Bearing device and rotary machine having the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device capable of stably supporting a rotor while the rotor is efficiently rotated.SOLUTION: The bearing device comprises a thrust collar 20 provided to project from the outer peripheral surface of a rotor 2 extending along an axis line O; and a plurality of bearing pad groups 30, in which a pad surface is arranged to face the thrust collar 20 in an axis line O direction. In the plurality of bearing pad groups 30, opposite distances h1 and h2 to the thrust collar 20 are arranged differently with each other in the bearing pad groups 30, and most close proximity bearing pad groups 40, which are at least bearing pad groups 30 that approach most the thrust collar 20 in the bearing pad groups 30, comprise a retraction drive part 42 for retracting from the thrust collar 20, the retraction drive part 42 retracting the bearing pad groups when a force applied to the bearing pad groups from the thrust collar 20 exceeds a prescribed threshold value.

Description

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

  It is known that a thrust bearing is used as a bearing device for supporting a rotor in an axial direction in large rotating machines such as a steam turbine, a gas turbine, a nuclear turbine, a compressor, a water turbine, and a pump. In the thrust bearing, a plurality of bearing pads are arranged across the circumferential direction which is the rotational direction of the rotor so as to face the thrust collar. In a bearing device using a thrust bearing, a thrust collar is supported by a bearing pad via an oil film, and the rotor is restrained in the axial direction.

  As such a bearing device, for example, in Patent Document 1, among a plurality of bearing pads used in the bearing device, constant pressure is applied by using hydraulic pressure so that an excessive force is not applied only to some of the bearing pads. A technique is disclosed in which a bearing pad that receives the above force is moved and the thrust collar is supported by another bearing pad. By using such a bearing device, the force from the thrust collar can be uniformly distributed and received by the plurality of bearing pads, and it is possible to prevent the specific bearing pad from being excessively damaged and damaged.

Japanese Patent No. 5000044

  Incidentally, the allowable thrust force, which is the allowable load that can be received by the bearing pad of the thrust bearing through the thrust collar from the rotor of the rotating machine, generally varies depending on the size of the bearing pad. That is, if the pressure receiving area of the bearing pad increases, the allowable thrust load increases. Conversely, if the pressure receiving area of the bearing pad decreases, the allowable thrust load decreases. Therefore, in a bearing device that receives a large force from the rotor, it is necessary to enlarge the bearing pad and increase the surface facing the thrust collar.

  However, when the bearing pad is enlarged, problems such as a reduction in the rotational efficiency of the rotor and an increase in the amount of lubricating oil to be used occur due to an increase in friction loss between the thrust collar and the bearing pad. On the other hand, if the bearing pad is made smaller, the rotational efficiency of the rotor is improved, but as described above, a large force from the rotor cannot be supported, and the temperature of the surface of the bearing pad facing the thrust collar rises and the bearing pad increases. As a result of the damage, the performance of the thrust bearing is greatly reduced, and it becomes difficult to stably support the rotor.

  The present invention has been made to solve the above-described problems, and provides a bearing device capable of stably supporting a rotor while efficiently rotating the rotor, and a rotary machine including the bearing device. The purpose is to provide.

In order to solve the above problems, the present invention proposes the following means.
A bearing device according to an aspect of the present invention includes a thrust collar provided so as to protrude from an outer peripheral surface of a rotor extending along an axis, and a pad surface facing the thrust collar in the axial direction. A plurality of bearing pad groups, and the plurality of bearing pad groups are arranged such that the distances between the bearing pad groups are different from each other, and at least the thrust collar of the bearing pad groups is arranged. The closest bearing pad group, which is the closest bearing pad group, includes a retreat drive unit that retreats from the thrust collar, and the retreat drive unit has a predetermined threshold value for the force that the bearing pad group receives from the thrust collar. The bearing pad group is retracted when exceeding.

  According to such a configuration, when the force received from the thrust collar is small, the loss generated in the rotor can be reduced by supporting the rotor via the thrust collar only by the nearest bearing pad group, and the efficiency The rotor can be rotated well. When the force received from the thrust collar exceeds a predetermined threshold value, the bearing pad group can be moved backward by the backward drive unit, and the thrust collar can be supported by another bearing pad group. Therefore, the number of bearing pads that support the thrust collar can be increased according to the force received by the bearing pad from the rotor via the thrust collar, and the threshold of the bearing pad that supports the thrust collar can be increased as a whole bearing device. Can do. As a result, even if the force received from the thrust collar increases, the bearing device has an allowable thrust force necessary to support the rotor, and the rotor can be stably supported. Thereby, it is possible to change the allowable thrust force necessary to stably support the rotor while efficiently rotating the rotor.

  In the bearing device according to another aspect of the present invention, the closest bearing pad group is disposed on the innermost side in the radial direction of the axis among the plurality of bearing pad groups.

  According to such a configuration, the nearest bearing pad group is disposed on the innermost side in the radial direction of the axis, and the circumferential speed is reduced by the distance from the rotor being closer than the other bearing pad group. Than can be suppressed. And the force which the nearest bearing pad group receives can be reduced by suppressing peripheral speed. Thereby, the friction loss generated in the rotor can be further reduced, and the rotor can be rotated more efficiently.

  Furthermore, in the bearing device according to another aspect of the present invention, the reverse drive unit is capable of sliding the piston part in the axial direction, and a piston part that supports the bearing pad group from the back surface facing the pad surface. When the force that the bearing pad group receives from the thrust collar exceeds a predetermined threshold, the cylinder portion that is accommodated as described above, the working fluid that is filled to support the piston portion in the cylinder portion, A valve portion for discharging the working fluid from the cylinder portion, and the piston portion is retracted along the axial direction when the working fluid is discharged.

  According to such a configuration, the force received by the nearest bearing pad group from the thrust collar can be converted into the pressure received by the working fluid filled in the cylinder part via the piston part. Then, when the force received by the bearing pad from the thrust collar exceeds a predetermined threshold value, the valve is detected via the working fluid, and the working fluid is discharged to retreat the bearing pads of the bearing pad group. A drive part can be formed. Thereby, a backward drive part can be provided easily.

  In the bearing device according to another aspect of the present invention, the cylinder part includes at least one throttle part that divides the cylinder part into a plurality of parts.

  According to such a configuration, the amount of the working fluid is automatically changed for each small space by moving the working fluid in the cylinder defined by the throttle portion according to the force received by the piston portion from the bearing pad. Can be made. Therefore, by moving the working fluid and changing the amount of the working fluid for each small space, the piston part itself can be tilted to follow the thrust collar. As a result, the rotor can be flexibly adapted to the inclination with respect to the axis, and the rotor can be efficiently rotated.

  Furthermore, the bearing device according to another aspect of the present invention includes the position measuring unit that measures the facing distance, and the retracting unit so that the size of the facing distance measured by the position measuring unit is a predetermined size. And a position control unit that adjusts an amount by which the driving unit moves the bearing pad group.

  According to such a structure, the position of a rotor can be returned to a desired position by moving a bearing pad with respect to a thrust collar based on the opposing distance which a position measurement part measures. Thereby, the position of the rotor is adjusted to a desired position, so that the rotor can be rotated while the axial position is maintained at the optimum position.

  Further, in the bearing device according to another aspect of the present invention, the bearing pad group is moved backward by the lubricating oil supply unit that supplies lubricating oil between the bearing pad group and the thrust collar, and the reverse drive unit. And a lubricating oil control unit for adjusting the amount of lubricating oil supplied from the lubricating oil supply unit to other bearing pad groups other than the retracted bearing pad group.

According to such a configuration, until the bearing pad group is retracted, the clearance between the bearing pad of the other bearing pad group other than the retracted bearing pad group and the thrust collar is wide, so that The bearing pads of the pad group do not support the thrust collar. Therefore, the friction loss to the rotor by the bearing pads of other bearing pad groups can be reduced.
Moreover, since it is not necessary to supply lubricating oil to the bearing pad which does not support the thrust collar, the supply amount of lubricating oil can be reduced.

  Furthermore, the bearing device according to another aspect of the present invention includes a temperature monitoring unit that measures a temperature of a surface of the bearing pad of the closest bearing pad group that faces the thrust collar, and a temperature measured by the temperature monitoring unit. A temperature determination unit that determines whether or not a predetermined temperature is exceeded, and a temperature control unit that causes the reverse drive unit to retract the bearing pad group based on a determination result in the temperature determination unit. To do.

  According to such a configuration, when some abnormality occurs in the closest bearing pad group and the pad surface is hot, the bearing is based on the temperature of the surface facing the thrust collar of the bearing pad of the closest bearing pad group. It is possible to detect and reverse the pad abnormality. As a result, the thrust collar is not supported by the nearest bearing pad group in which an abnormality has occurred, so the rotor can be protected even if the rotor is continuously rotated without performing an emergency stop or the like, and a highly reliable bearing The device can be easily formed.

  A rotating machine according to an aspect of the present invention includes the above-described bearing device.

  According to the rotating machine including such a bearing device, the rotor can be efficiently rotated, and the efficiency of the rotating machine can be improved.

  According to the bearing device of the present invention, when the force received from the thrust collar is small, the thrust collar is supported only by the nearest bearing pad group, and when the force received from the thrust collar is increased, other bearing pad groups are also used. Since the rotor can be supported, it is possible to stably support the rotor by increasing the allowable thrust force as necessary while efficiently rotating the rotor.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic diagram explaining the bearing apparatus which concerns on 1st embodiment of this invention, The figure (a) is a cross-sectional view, The figure (b) is a longitudinal cross-sectional view in AA which looked at the bearing apparatus from the axial direction. is there. The graph explaining the relationship between the thrust force and bearing surface pressure of the bearing apparatus which concerns on 1st embodiment of this invention, The figure (a) is the graph explaining the relationship between the conventional thrust force and bearing surface pressure, FIG. 5B is a graph for explaining the relationship between the thrust force and the bearing surface pressure in the bearing device of this embodiment. It is a cross-sectional view explaining a part of bearing device concerning a second embodiment of the present invention. It is a transverse cross section explaining some bearing devices concerning a third embodiment of the present invention. It is a schematic diagram explaining a part of the bearing device according to the fourth embodiment of the present invention, in which (a) is a cross-sectional view, and (b) is a longitudinal section taken along line BB when the bearing device is viewed from the axial direction. FIG. It is a transverse cross section explaining some bearing devices concerning a fifth embodiment of the present invention.

Hereinafter, a first embodiment according to the present invention will be described with reference to FIG.
The bearing device 3 according to the first embodiment is used for a rotating machine. A rotating machine is a prime mover that obtains power by bringing a fluid such as steam or gas into contact with an impeller and converting fluid energy into rotational energy. Here, the rotary machine in the present embodiment is described as being the steam turbine 1, but may be a gas turbine, a nuclear turbine, or the like, for example.
A steam turbine 1 having a bearing device 3 according to the first embodiment includes a rotor 2 that rotates about an axis O, a turbine body 10 that is connected to the rotor 2 and rotates integrally with the rotor 2, and the rotor 2. And a bearing device 3 that supports the rotor 2 in the direction of the axis O.

The rotor 2 is formed in a cylindrical shape centered on the axis O. The rotor 2 extends in the direction of the axis O with respect to the steam turbine 1, and forms the rotation axis of the steam turbine 1. A turbine body 10 that rotates together with the rotor 2 and has moving blades that are a plurality of impellers is attached to the outer peripheral side of the rotor 2.
Although the details of the schematic configuration of the turbine body 10 are not shown, for example, a plurality of moving blades (impellers) projecting from the rotor 2, a casing that accommodates the plurality of moving blades, and an inner periphery of the casing And a stationary blade projecting from the surface. The plurality of moving blades are arranged radially around the rotor 2, and the plurality of moving blades and the plurality of stationary blades are alternately arranged in the direction of the axis O. The turbine main body 10 is a power generation unit that generates power when a fluid flows in and strikes a moving blade and a stationary blade.

  As shown in FIG. 1 (a), the bearing device 3 includes a thrust collar 20 formed to project radially outward from the outer peripheral surface of the rotor 2, and a plurality of opposingly arranged so as to sandwich the thrust collar 20. A bearing pad group 30, and a bearing box 60 that covers the thrust collar 20 and the plurality of bearing pad groups 30 from the radially outer side are provided.

The thrust collar 20 has a disk shape with the axis O as the center, and integrally protrudes radially outward from the rotor 2 so as to form a flange shape.
The plurality of bearing pad groups 30 are disposed so as to surround the outer peripheral surface side of the rotor 2 in the circumferential direction, and the closest bearing disposed in the radially innermost direction of the axis O among the plurality of bearing pad groups 30. It has a pad group 40 and a second bearing pad group 50 that is another bearing pad group 30 disposed radially outside the axis O with respect to the closest bearing pad group 40.

  Two closest bearing pad groups 40 are provided so as to sandwich the thrust collar 20 from both sides in the direction of the axis O, and are arranged at positions closest to the outer peripheral surface of the rotor 2 among the plurality of bearing pad groups 30. The closest bearing pad group 40 includes a plurality of main bearing pads 41 that are opposed to the thrust collar 20 in the direction of the axis O and spaced apart from the outer peripheral surface of the rotor 2 in the circumferential direction, and the thrust collar 20. And a backward drive portion 42 that supports the main bearing pad 41.

  As shown in FIG. 1B, the main bearing pad 41 is a bearing pad having a main pad surface 411 which is a pad surface facing the thrust collar 20 along the direction of the axis O, and has a disk shape. . A plurality of main bearing pads 41 are provided (e.g., eight locations in the present embodiment) so that the main pad surface 411 is separated from the thrust collar 20, and the main bearing pads 41 are equally spaced apart from each other along the circumferential direction of the rotor 2. ing. In the main bearing pad 41, lubricating oil is supplied to a space between the main pad surface 411 and the thrust collar 20 from a lubricating oil supply source (not shown).

The reverse drive unit 42 supports the main bearing pad 41 from the back side facing the main pad surface 411 of the main bearing pad 41 along the axis O direction. The reverse drive unit 42 enables the main bearing pad 41 to be retracted when the force received by the main bearing pad 41 from the thrust collar 20 exceeds a preset load L _set which is a predetermined threshold value. The reverse drive part 42 includes a piston part 421 that directly supports the main bearing pad 41 from the back side, a cylinder part 422 that accommodates the piston part 421 so as to be slidable in the direction of the axis O, and a working fluid f in the cylinder part 422. And a valve portion 424 for discharging the working fluid f when the force related to the working fluid f in the cylinder portion 422 exceeds a predetermined threshold value.

  The piston portion 421 supports the main bearing pad 41 from the back side facing the main pad surface 411 along the direction of the axis O. The piston portion 421 has a ring shape centered on the axis O and extends along the direction of the axis O, and a piston connection portion 421b that connects the piston body 421a and the back of the main bearing pad 41. And a seal ring 421c disposed on the inner and outer peripheral surfaces of the piston main body 421a.

The piston main body 421a is arranged along the outer peripheral surface of the rotor 2 in a ring shape centered on the axis O. The piston main body 421a includes a ring portion having a ring shape centered on the axis O and a second ring portion having a ring shape centered on the axis O and having a diameter larger than that of the ring portion. Are integrally formed along the axis O, and the ring portion is disposed on the thrust collar 20 side, so that the outer peripheral surface has a stepped shape. Moreover, the piston part 421 main-body part is provided with the seal ring 421c in the inner peripheral surface and outer peripheral surface of a 2nd ring part, respectively.
The piston connection part 421b connects the ring part of the piston main body part 421a and the back surface of the bearing pad.
The seal ring 421c is disposed so as to be slidably contacted on an inner peripheral surface of a cylinder portion 422, which will be described later, and is fixed to the inner peripheral surface and the outer peripheral surface of the piston main body portion 421a.

  The cylinder portion 422 has a ring shape, and a space corresponding to the shape of the piston portion 421 is formed therein so as to open the thrust collar 20 side, and the piston portion 421 is accommodated. The cylinder part 422 is configured such that the inner and outer peripheral surfaces of the piston part 421 and the inner peripheral surface of the space formed in the cylinder part 422 can slide in the axis O direction. The cylinder portion 422 has a reduced diameter opening so as to correspond to the ring portion having a small diameter of the piston portion 421. That is, the cylinder part 422 corresponds to the shape of the inner diameter of the opening part of the cylinder part 422 and the outer diameter of the ring part of the piston part 421, and the opening part of the cylinder part 422 passes through the second ring part of the piston part 421. The stopper 422a is formed in a size that is not allowed to be formed. The piston portion 421 is installed so as not to be detached from the cylinder portion 422 by the stopper 422a. The working fluid f is supplied and filled in the cylinder part 422, and the cylinder part 422 is actuated by the bottom surface part of the piston part 421 in the direction of the axis O and the seal ring 421c provided in the piston part 421. The fluid f is sealed.

  The pump unit 423 includes a supply pipe 423a connected to a bottom surface portion corresponding to the opening portion of the cylinder portion 422 in the axis O direction, and a pump 423b that discharges the working fluid f. The pump part 423 continues to supply the working fluid f into the cylinder part 422 via the supply pipe 423a.

The valve part 424 is a discharge mechanism that discharges the working fluid f from the cylinder part 422. The valve portion 424 includes a discharge pipe 424a that discharges the working fluid f from the cylinder portion 422, and a relief that can be adjusted so that the flow passage cross section of the discharge pipe 424a has an arbitrary width according to the pressure received by the working fluid f. And a valve 424b.
When the relief valve 424b detects that the working fluid f filled in the cylinder portion 422 has received a pressure exceeding a preset surface pressure _Pset which is a predetermined pressure, the relief valve 424b automatically releases a large amount of the working fluid f to the outside. The discharge pipe 424a is completely expanded so as to be discharged. The main bearing pad 41 of the nearest bearing pad group 40 is set to the set load L _{set so} that the set surface pressure P _set corresponds to a preset set load L _set as a force that the nearest bearing pad group 40 can receive. The pressure is set to the magnitude that the working fluid f receives when it reaches. Further, the relief valve 424b of the valve portion 424 slightly opens the flow path of the discharge pipe 424a so that the working fluid f supplied into the cylinder portion 422 does not exceed a certain amount and is not filled in the cylinder portion 422. The supply amount of the working fluid f from the pump unit 423 is limited so that the working fluid f supplied from the pump unit 423 is not excessively supplied to the cylinder unit 422.

  The second bearing pad group 50 is provided at two locations so as to sandwich the thrust collar 20 from both sides in the direction of the axis O, and the closest bearing pad group 40 of the plurality of bearing pad groups 30 is circumferentially arranged from the outer side in the radial direction of the rotor 2. It is the bearing pad group 30 arrange | positioned so that it may surround. The second bearing pad group 50 includes a plurality of sub-bearing pads 51 that are opposed to the thrust collar 20 in the direction of the axis O and are spaced apart from the outer peripheral surface of the rotor 2 evenly in the circumferential direction. And a bearing pad support portion 52 that supports the pad 51.

  As shown in FIG. 1 (b), the sub bearing pad 51 is a bearing pad having a sub pad surface 511 that is a pad surface facing the thrust collar 20 along the axis O direction. It has a large disk shape. The sub bearing pad 51 has a plurality of sub pad surfaces 511 spaced apart from the thrust collar 20 rather than the main pad surface 411 of the main pad bearing (for example, eight locations in the present embodiment), and extends in the circumferential direction of the rotor 2. Are evenly spaced from each other. Similarly to the main bearing pad 41 of the closest bearing pad group 40, in the sub bearing pad 51, the lubricating oil is supplied to the space between the sub pad surface 511 and the thrust collar 20 from a lubricating oil supply source (not shown). ing.

Here, a distance between the thrust collar 20 and the pad surface of the bearing pad is defined as a facing distance h. The opposing distance h between the thrust collar 20 and the main pad surface 411 in the closest bearing pad group 40 is the opposing distance h1, and the opposing distance h between the thrust collar 20 and the sub pad surface 511 in the second bearing pad group 50 is the opposing distance h2. And
The opposing distance h is such that the distance between the thrust collar 20 that is the opposing distance h1 in the closest bearing pad group 40 and the main pad surface 411 is the thrust collar 20 that is the opposing distance h2 in the second bearing pad group 50 and the subpad. It arrange | positions so that it may become smaller than the distance with the surface 511. FIG. That is, in the closest bearing pad group 40 and the second bearing pad group 50 that are the plurality of bearing pad groups 30, the facing distance h1 and the facing distance h2 that are the facing distance h to the thrust collar 20 are the same between the bearing pad groups 30. The bearing distances h <b> 1 of the nearest bearing pad group 40 are arranged closest to the thrust collar 20 in the bearing pad group 30.

  The bearing pad support part 52 is formed integrally with the cylinder part 422 of the reverse drive part 42 in a ring shape in the circumferential direction of the rotor 2, and faces the sub bearing pad 51 along the axis O direction with respect to the sub pad surface 511. Support from the back side.

  The bearing housing 60 has an annular shape, and the rotor 2 is inserted through the center thereof. The bearing housing 60 covers the plurality of bearing pad groups 30 that are the closest bearing pad group 40 and the second bearing pad group 50 from the outside in the radial direction, and fixes the plurality of bearing pad groups 30.

Next, the operation of the bearing device 3 of the first embodiment will be described.
According to the bearing device 3 of the first embodiment, when the rotor 2 moves toward one side in the direction of the axis O (for example, rightward in FIG. 1) during operation of the steam turbine 1, the thrust collar 20 and the main pad surface. The closest bearing pad group 40 disposed on one side in the direction of the axis O receives the force from the thrust collar 20 through the lubricating oil between the thrust collars 411 and 411. As a result, the closest bearing pad group 40 operates as a thrust bearing and supports the rotor 2 via the thrust collar 20. At this time, the force received by the main bearing pad 41 of the closest bearing pad group 40 is retracted along the axis so as to press the piston main body 421a against the cylinder 422 along the axis O direction via the piston connecting part 421b. Try to. Therefore, the working fluid f sealed in the cylinder part 422 is compressed by the piston main body part 421a, and the working fluid f receives pressure.

Thereafter, when the rotor 2 further moves toward one side in the direction of the axis O, the main bearing pad 41 of the closest bearing pad group 40 receives a larger force. When the force received by the main bearing pad 41 is increased, the piston portion 421 that supports the main bearing pad 41 receives further force, and the pressure received by the working fluid f filled between the piston portion 421 and the cylinder portion 422 is also interlocked. Rise. When the force received by the main bearing pad 41 exceeds a predetermined set load L _set , the pressure received by the working fluid f also exceeds the _set surface pressure P _set, and the relief valve 424b of the valve portion 424 is completely removed from the discharge pipe 424a. Open to widen the cross section of the flow path. By completely opening the flow passage cross section of the discharge pipe 424a and discharging the working fluid f, the working fluid f is discharged in large quantities from the cylinder portion 422, and the pressure received by the working fluid f is released. When the working fluid f is discharged from the cylinder portion 422, the piston main body portion 421a starts to slide in the cylinder portion 422 so as to move away from the thrust collar 20 along the axis O direction. As a result, the piston portion 421 that is the retreat drive unit 42 retreats the main bearing pad 41 of the closest bearing pad group 40 away from the thrust collar 20.

  When the working fluid f is discharged, the main bearing pad 41 of the closest bearing pad group 40 moves backward to the position of the sub bearing pad 51 of the second bearing pad group 50. Therefore, the facing distance h of the main pad surface 411 of the main bearing pad 41 of the closest bearing pad group 40 and the facing distance h of the sub pad surface 511 of the sub bearing pad 51 of the second bearing pad group 50 are the same. As a result, the force received from the thrust collar 20 is evenly distributed on both the main pad surface 411 and the sub pad surface 511, and the thrust collar 20 is received on both the closest bearing pad group 40 and the second bearing pad group 50. Will be supported.

  According to the bearing device 3 as described above, when the force received by the main bearing pad 41 of the closest bearing pad group 40 from the thrust collar 20 is small, such as when the amount of movement of the rotor 2 in the axis O direction is small, the closest The thrust collar 20 can be supported only by the main bearing pad 41 of the bearing pad group 40. Therefore, the pad surface facing the thrust collar 20 is only the main pad surface 411, and the pressure receiving area A of the pad surface facing the thrust collar 20 when the rotor 2 rotates can be reduced. The rotor 2 can reduce friction loss caused by the bearing pads. As a result, while the force received from the thrust collar 20 is small, the friction loss caused by the bearing pad can be suppressed and the rotor 2 can be efficiently rotated.

When the force received by the main bearing pad 41 of the closest bearing pad group 40 from the thrust collar 20 exceeds a preset load L _set which is a predetermined threshold value, the relief valve 424b of the valve portion 424 which is the reverse drive portion 42 is activated. By doing so, the main bearing pad 41 of the closest bearing pad group 40 is retracted, and the thrust collar 20 can be supported by the sub-bearing pad 51 of the second bearing pad group 50 which is the other bearing pad group 30. Therefore, when the force received by the main bearing pad 41 from the thrust collar 20 exceeds the set load L _{set due} to an increase in the amount of movement of the rotor 2 in the axis O direction, etc., according to the force received from the thrust collar 20. The number of bearing pads that support the thrust collar 20 can be increased from the main bearing pad 41 to the main bearing pad 41 and the sub bearing pad 51. By supporting the thrust collar 20 with the main bearing pad 41 and the sub-bearing pad 51, the size of the bearing pad that supports the rotor 2 can be increased as the entire bearing device 3 and the pressure receiving area A can be increased. That is, the pad surface facing the thrust collar 20 becomes the main pad surface 411 and the sub pad surface 511, and the pad surface as the bearing device 3 can be enlarged.

Here, as shown in FIG. 2 (a), in a general thrust bearing, when the pressure receiving area A of the bearing pad is constant, the bearing pad of the bearing device 3 receives through the thrust collar 20. The thrust force F, which is a force that can be applied, is proportional to the bearing surface pressure P, which is the force received by the bearing pad of the bearing device 3. Therefore, when the bearing surface pressure P of the bearing pad reaches a limit surface pressure that is a limit value, the thrust force F reaches an allowable thrust force that is an allowable load that can be received by the bearing pad.
Therefore, in the present embodiment, when the set surface pressure P _set is reached, the bearing pad that supports the thrust collar 20 becomes the main bearing pad 41 and the sub bearing pad 51 from the main bearing pad 41 alone, thereby increasing the pressure receiving area A. I am letting. Therefore, as shown in FIG. 2B, when the set surface pressure P _set is exceeded, the gradient of the graph showing the relationship between the thrust force F and the bearing surface pressure P is reduced by the amount by which the pressure receiving area A is increased. The allowable thrust load can be improved only in the area a to the area b.

  Therefore, by increasing the pressure receiving area A of the pad surface facing the thrust collar 20 from the middle according to the force received from the thrust collar 20, an allowable thrust force that is an allowable thrust force F for the bearing device 3 is obtained from the thrust collar 20. It can be increased according to the force received. As a result, even if the force received from the thrust collar 20 increases, the bearing device 3 has the allowable thrust force necessary to support the rotor 2, and the rotor 2 can be stably supported. That is, by increasing the bearing pad group 30 that supports the thrust collar 20 according to the force received by the main bearing pad 41 of the closest bearing pad group 40 from the thrust collar 20, while efficiently rotating the rotor 2, The allowable thrust force can be increased as necessary, and the rotor 2 can be stably supported.

  Further, the closest bearing pad group 40 is arranged on the innermost side in the radial direction of the axis O and is brought closer to the rotor 2, so that the second bearing pad group 50, which is another bearing pad group 30, is separated from the rotor 2. The distance can be reduced, and the peripheral speed can be suppressed as compared with the second bearing pad group 50. Since the force related to the bearing pad increases as the peripheral speed increases, the force received by the main bearing pad 41 of the closest bearing pad group 40 can be reduced by suppressing the peripheral speed. As a result, the force received by the closest bearing pad group 40 is reduced, whereby the friction loss generated in the rotor 2 can be further reduced and the rotor 2 can be rotated more efficiently.

Further, the relief valve 424b, which is the valve portion 424, detects that the pressure received by the working fluid f exceeds the _set surface pressure Pset and discharges the working fluid f, whereby the main bearing pad 41 of the closest bearing pad group 40 is discharged. Can be retreated. That is, the reverse drive unit 42 converts the force received by the main bearing pad 41 of the closest bearing pad group 40 from the thrust collar 20 into the pressure received by the working fluid f filled in the cylinder unit 422 via the piston unit 421. can do. Then, the fact that the force received by the main bearing pad 41 from the thrust collar 20 exceeds a preset load L _set which is a predetermined threshold is detected by the relief valve 424b which is the valve portion 424 via the working fluid f, and the working fluid f As a structure for retracting the main bearing pad 41 of the closest bearing pad group 40, the backward drive portion 42 can be formed. Accordingly, it is possible to easily provide the reverse drive unit 42 for moving the main bearing pad 41 backward when the force received by the main bearing pad 41 from the thrust collar 20 exceeds a preset load L _set which is a predetermined threshold value.

  Further, according to the steam turbine 1 that is a rotating machine using the bearing device 3 as described above, the rotor 2 can be efficiently rotated, and the efficiency of the steam turbine 1 that is a rotating machine can be improved. Become.

Next, the bearing device 3 of the second embodiment will be described with reference to FIG.
In the second embodiment, the same components as those in the first embodiment are given the same reference numerals, and detailed description thereof is omitted. The bearing device 3 of the second embodiment is different from the first embodiment in that the position of the main bearing pad 41 is adjusted by the facing distance h in the closest bearing pad group 40.

  That is, as shown in FIG. 3, in the second embodiment, the position measuring unit 301 that measures the facing distance h between the main bearing pad 41 and the thrust collar 20 of the closest bearing pad group 40 and the position measuring unit 301 measure the distance. And a position control unit 302 that controls the size of the flow path cross section of the discharge pipe 424a in the relief valve 424b that is the valve unit 424 based on the value of the facing distance h. In FIG. 3, illustration of the left side portion of the paper, which is the other side in the direction of the axis O, is omitted, and only one side in the direction of the axis O is illustrated, but both sides in the direction of the axis O through the thrust collar 20. A similar structure is provided.

The position measuring unit 301 is a gap sensor installed from the inner peripheral surface of the bearing housing 60, measures the size of the distance between the thrust collar 20 and the gap sensor, and outputs the measured distance to the position control unit 302.
The position control unit 302 is a relief valve 424b that is the valve unit 424 when the distance between the position sensor 302 and the gap sensor that is input from the position measurement unit 301 deviates from a predetermined clearance h _set that is a predetermined threshold value. Is adjusted to reduce the size of the flow path cross section of the discharge pipe 424a.

Next, the operation of the bearing device 3 of the second embodiment will be described.
According to the bearing device 3 of the second embodiment, when the rotor 2 slightly moves in the direction of the axis O while the thrust collar 20 is supported only by the closest bearing pad group 40, the position measuring unit 301 is used. The gap sensor measures the size of the opposing distance between the thrust collar 20 and the gap sensor as the position measuring unit 301. Measuring the distance between the thrust collar 20 and the gap sensor as the position measuring unit 301 is to measure the distance h between the thrust collar 20 and the main pad surface 411 of the closest bearing pad group 40. It becomes. Therefore, if the value measured by the position measuring unit 301 is deviated from the predetermined clearance h _set which is a predetermined threshold value, the facing distance h between the thrust collar 20 and the main pad surface 411 of the closest bearing pad group 40. Will be out of magnitude. Therefore, the amount of the working fluid f discharged by closing the relief valve 424b, which is the valve portion 424, is adjusted to fill the cylinder portion 422 with the working fluid f. That is, when the amount of movement of the rotor 2 in the direction of the axis O is such that the force received by the main bearing pad 41 of the closest bearing pad group 40 from the thrust collar 20 does not reach the set load L _set. When the measured value output from the unit 301 is smaller than the predetermined clearance h _set which is a predetermined threshold, the relief valve 424b which is the valve unit 424 is completely closed, and the operation supplied from the pump unit 423 is performed. The fluid f is filled in the cylinder portion 422. As a result, the piston portion 421 is pushed by the working fluid f, so that the main bearing pad 41 moves forward along the axis O toward the thrust collar 20. Then, by pushing back the thrust collar 20 by the main bearing pad 41, the position of the rotor 2 is moved to a desired position, and the specified clearance h _set is maintained again.

  According to the bearing device 3 as described above, the main portions of the thrust collar 20 and the closest bearing pad group 40 measured through the distance between the thrust collar 20 measured by the gap sensor as the position measuring unit 301 and the gap sensor are opposed to each other. The position of the rotor 2 can be returned to a desired position by moving the main bearing pad 41 with respect to the thrust collar 20 based on the facing distance h with respect to the pad surface 411. For example, in the case of the steam turbine 1 as in the present embodiment, the position of the rotor 2 is adjusted to a desired position by the main bearing pad 41, and the moving blades provided on the rotor 2 in the steam turbine 1 are illustrated. The position of the stationary blade provided in the casing that is not adjusted is adjusted, the positional relationship between the moving blade and the stationary blade can be kept optimal, and the performance of the steam turbine 1 can be prevented from deteriorating. Thereby, the position of the rotor 2 is adjusted to a desired position, so that the rotor 2 can be rotated while the position in the direction of the axis O is maintained at the optimum position.

Next, the bearing device 3 of the third embodiment will be described with reference to FIG.
In the third embodiment, the same components as those in the first embodiment are given the same reference numerals, and detailed description thereof is omitted. The bearing device 3 of the third embodiment is different from the first embodiment in that the amount of lubricating oil supplied to the sub bearing pad 51 is controlled.

  That is, in the third embodiment, as shown in FIG. 4, lubricating oil is supplied between the sub pad surface 511 of the second bearing pad group 50 and the thrust collar 20 instead of the lubricating oil supply source in the first embodiment. And a lubricant control unit 305 that adjusts the amount of lubricant supplied from the lubricant supply unit 304.

  The lubricating oil supply unit 304 includes a lubricating oil pump 304a that is a supply source of the lubricating oil, and a supply nozzle 304b that supplies the lubricating oil to the sub pad surface 511 of the second bearing pad group 50 from the lubricating oil pump 304a. The lubricating oil supply unit 304 supplies the lubricating oil supplied from the lubricating oil pump 304a to the sub pad surface 511 via the supply nozzle 304b.

The lubricating oil control unit 305 receives the output from the opening detection unit 305a that detects that the valve unit 424 is opened, the lubricating oil valve 305b that is provided in the supply nozzle 304b, and the opening detection unit 305a. And a lubricating oil valve driving unit 305c to be opened.
The opening detection unit 305a detects that the relief valve 424b of the valve unit 424 has been completely opened and outputs a trigger signal TS.
The lubricating oil valve 305b is an electromagnetic valve that is provided in the supply nozzle 304b and closes the supply nozzle 304b, and allows the lubricating oil to flow through the supply nozzle 304b by opening the electromagnetic valve.
When detecting that the relief valve 424b of the valve unit 424 is opened from the opening detection unit 305a, the lubricating oil valve drive unit 305c inputs a signal to the electromagnetic valve that is the lubricating oil valve 305b to energize the electromagnetic valve. Open.

Next, the operation of the bearing device 3 of the third embodiment will be described.
According to the bearing device 3 of the third embodiment, in a state where the thrust collar 20 is supported only by the closest bearing pad group 40, it is between the main pad surface 411 of the closest bearing pad group 40 and the thrust collar 20. Lubricating oil is supplied to the space by a lubricating oil supply source (not shown). On the other hand, in a state where the thrust collar 20 is supported only by the closest bearing pad group 40, the relief valve 424b of the valve portion 424 is not completely opened, so that the lubricating oil valve 305b remains closed. Therefore, no lubricating oil is supplied between the sub pad surface 511 of the second bearing pad surface and the thrust collar 20.

Thereafter, when the force received by the nearest bearing pad group 40 from the thrust collar 20 increases and exceeds the set load L _set and the pressure of the working fluid f also exceeds the set surface pressure P _set , the relief valve 424b of the valve portion 424 is completely opened. Then, the nearest bearing pad group 40 moves backward. When the opening detection unit 305a detects that the relief valve 424b of the valve unit 424 is completely opened and outputs the trigger signal TS to the lubricating oil valve driving unit 305c, a signal is output from the lubricating oil valve driving unit 305c and the lubricating oil A signal is input to the valve 305b. When a signal is input, the electromagnetic valve that is the lubricating oil valve 305b is energized and opened, and the lubricating oil flows through the supply nozzle 304b. The lubricating oil is supplied from the lubricating oil supply unit 304 to the sub pad surface 511 through the supply nozzle 304b.

  When the lubricating oil is supplied to the sub pad surface 511 and the nearest bearing pad group 40 moves backward, the facing distance h1 becomes the same as the facing distance h2 of the second bearing pad group 50, so that the second bearing pad The group 50 can receive a force from the thrust collar 20 via the lubricating oil, and supports the thrust collar 20 together with the closest bearing pad group 40.

According to the bearing device 3 as described above, the lubricating oil between the sub pad surface 511 of the second bearing pad group 50 and the thrust collar 20 has a greater force applied to the nearest bearing pad group 40, and the relief valve of the valve portion 424. It will not be supplied until 424b is fully opened and the main bearing pad 41 is retracted. That is, in a state where the thrust collar 20 is supported only by the closest bearing pad group 40, the space between the thrust collar 20 and the second bearing pad group 50 is a gap where no lubricating oil intervenes. Therefore, until the closest bearing pad group 40 moves backward, the gap between the sub bearing pad 51 and the thrust collar 20 of the second bearing pad group 50, which is another bearing pad group other than the closest bearing pad group 40, is wide. As a result, the thrust collar 20 is not supported by the sub-bearing pads 51 of the second bearing pad group 50. Therefore, the friction loss to the rotor 2 by the sub bearing pad 51 of the second bearing pad group 50 can be reduced.
Until the closest bearing pad group 40 moves backward, the second bearing pad group 50 does not support the thrust collar 20, and lubricating oil is applied to the sub-bearing pad 51 that does not support the thrust collar 20. Since there is no need to supply, the supply amount of lubricating oil can be reduced.

Next, the bearing device 3 of the fourth embodiment will be described with reference to FIGS. 5 (a) and 5 (b).
In the fourth embodiment, the same components as those in the first embodiment are given the same reference numerals, and detailed description thereof is omitted. The bearing device 3 according to the fourth embodiment is different from the first embodiment in that a throttle portion 306 is provided in the cylinder portion 422.

That is, in the fourth embodiment, as shown in FIGS. 5A and 5B, a plurality of throttle portions 306 that divide the space in the cylinder portion 422 into a plurality of portions in the circumferential direction are provided.
The restricting portion 306 is disposed at 120 ° intervals and equally spaced in the circumferential direction so as to divide the ring-shaped space in the cylinder portion 422 into a plurality of portions in the circumferential direction. The throttle portion 306 is a rectangular orifice, and a space smaller than the radial sectional area of the cylinder portion 422 is opened.

Next, the operation of the bearing device 3 according to the fourth embodiment will be described.
According to the bearing device 3 of the fourth embodiment, the space in the cylinder portion 422 is partitioned into a plurality of small spaces by the throttle portion 306, and each small space is passed through the opening portion of the throttle portion 306. In other words, the working fluid f filled in the cylinder part 422 can move through the small spaces divided through the throttle part 306.

According to the bearing device 3 as described above, the working fluid f moves in the cylinder defined by the throttle portion 306 in accordance with the force received by the piston portion 421 from the main bearing pad 41, so that the operation is performed for each small space. The amount of fluid f can be automatically changed. Here, when the rotor 2 is tilted with respect to the axis O, the thrust collar 20 is also tilted with respect to the closest bearing pad group 40, and the force received by the main bearing pad 41 from the thrust collar 20 varies depending on the circumferential position. . However, since the working fluid f moves and the amount of the working fluid f can be changed for each small space, the piston portion 421 itself can be tilted to follow the thrust collar 20. As a result, the rotor 2 can flexibly cope with the inclination with respect to the axis O, and the rotor 2 can be rotated efficiently.
Further, since the working fluid f can move in the cylinder, the cylinder portion 422 and the piston portion 421 that are the backward drive portions 42 can function as dampers via the working fluid f. As a result, even if the rotor 2 is tilted and vibrates with respect to the axis O, the vibration can be attenuated and reduced.

Next, the bearing device 3 of the fifth embodiment will be described with reference to FIG.
In the fifth embodiment, the same components as those in the first embodiment are given the same reference numerals, and detailed description thereof is omitted. The bearing device 3 of the fifth embodiment is different from the first embodiment in that the reverse drive unit 42 is controlled by the temperature of the closest bearing pad group 40.

That is, in the fifth embodiment, as shown in FIG. 6, the temperature monitoring unit 307 that measures the temperature of the main pad surface 411 of the main bearing pad 41, and the temperature measured by the temperature monitoring unit 307 are predetermined temperatures. having a specified temperature T _set determining whether it exceeds the temperature determination unit 308, and a temperature control unit 309 to completely retract the retraction driving section 42 when it is determined to exceed the predetermined temperature T _set.

The temperature monitoring unit 307 is a temperature sensor provided on the main pad surface 411 of the closest bearing pad group 40, measures the temperature of the main pad surface 411, and outputs the measured temperature information to the temperature determination unit 308. . As the temperature monitoring unit 307, a known temperature sensor may be used, and for example, a thermocouple is used.
When the temperature information measured and output by the temperature monitoring unit 307 is input, the temperature determination unit 308 compares the predetermined temperature T _set determined in advance with the input temperature information, and the measured temperature is the specified temperature. If it is determined that T _set is exceeded, a signal is output to the temperature control unit 309. The specified temperature _Tset is set to a temperature at which it is determined that an abnormality has occurred in the main bearing pad 41, such as a temperature when the main bearing pad 41 is burned out.
When a signal is input from the temperature determination unit 308 based on the determination result, the temperature control unit 309 completely opens the relief valve 424b, which is the valve unit 424, and stops the pump 423b of the pump unit 423.

Next, the operation of the bearing device 3 of the fifth embodiment will be described.
According to the bearing device 3 of the fifth embodiment, the temperature monitoring unit 307 measures the temperature of the main pad surface 411 of the closest bearing pad surface by the temperature sensor, and constantly monitors the temperature of the main pad surface 411. Then, information on the temperature measured by the temperature monitoring unit 307 is input to the temperature determination unit 308, and the temperature determination unit 308 compares the measured temperature information with the specified temperature T _set so that the temperature determination unit 308 has the specified temperature T on the main pad surface 411. _Judge whether the temperature exceeding _set does not work. When the temperature determination unit 308 determines that the temperature of the main pad surface 411 exceeds the specified temperature T _set , the temperature determination unit 308 sends a signal to the temperature control unit 309. When the temperature control unit 309 receives a signal from the temperature determination unit 308, the release valve 424 b of the valve unit 424 is completely opened to widen the flow path of the discharge pipe 424 a, discharge the working fluid f, and retract the main bearing pad 41. The distance between the thrust collar 20 and the main bearing pad 41 is increased. The temperature control unit 309 also stops the supply of the working fluid f into the cylinder unit 422 by stopping the pump 423b which is the pump unit 423, and the cylinder unit 422 is emptied. As a result, the piston portion 421 is retracted so as to be completely separated from the thrust collar in the cylinder portion 422, and the main bearing pad 41 is retracted from the sub-bearing pad 51 which is the second bearing pad group 50.

  According to the bearing device 3 as described above, when some abnormality occurs in the main bearing pad 41 which is the closest bearing pad group 40 and the main pad surface 411 is at a high temperature, the temperature of the main pad surface 411 is increased. Therefore, the abnormality of the main bearing pad 41 can be detected and retracted. In general, when the steam turbine 1 or the like is operated and the rotor 2 is rotating, foreign matter or the like enters and is caught between the main bearing pad 41 and the thrust collar 20 of the closest bearing pad group 40. As a result, the friction between the main pad surface 411 of the main bearing pad 41 and the thrust collar 20 becomes abnormally large. As a result, the frictional heat increases and the temperature of the main pad surface 411 increases rapidly, and the thrust collar 20 and the rotor 2 may be damaged. However, based on the temperature of the main pad surface 411, the main bearing pad 41 and the thrust collar 20 are moved backward by moving the main bearing pad 41 from the sub-bearing pad 51 by opening the valve portion 424 that is the backward driving portion 42. Thus, the frictional heat generated on the main pad surface 411 is eliminated by supporting the thrust collar 20 only by the sub bearing pad 51. That is, the thrust collar 20 is not supported by the nearest bearing pad group 40 in which an abnormality has occurred, but is supported only by the second bearing pad group 50. Accordingly, the rotor 2 can be protected from the nearest bearing pad group 40 in which an abnormality has occurred even if the rotor 2 is continuously rotated without performing an emergency stop or the like, and the highly reliable bearing device 3 can be easily obtained. It becomes possible to form.

The present invention is not limited to the present embodiment, and various modifications are allowed without departing from the scope of the present invention. For example, the bearing apparatus 3 which does not have the pump part 423 in 1st embodiment as a 1st modification of this embodiment is mentioned.
That is, the first modification does not have the pump part 423, and the cylinder part 422 is filled with the working fluid f in a predetermined amount in advance. And the relief valve 424b which is the valve part 424 is open | released only when it becomes a regulation pressure, and when not satisfy | filling the setting surface pressure _Pset , it is obstruct | occluded completely.

In the bearing device 3 of the first modification as described above, when the pressure received by the working fluid f in the cylinder part 422 exceeds the set surface pressure P _set , the relief valve 424b which is the valve part 424 is opened and the working fluid f is received. The main bearing pad 41 is discharged and retracted. By adopting such a structure, the nearest bearing pad group 40 can be moved backward only by the working fluid f filled in the cylinder portion 422 in advance without using the pump portion 423, and the drive is driven backward with a simpler structure. The part 42 can be formed.

As a second modification of the present embodiment, there is a bearing device 3 in which the position control unit 302 in the second embodiment controls not only the relief valve 424b of the valve unit 424 but also the pump unit 423.
That is, the second modified example has a second pump unit 425 having the same configuration as the pump unit 423 in which the cylinder portion 422 is filled with a predetermined amount of the working fluid f in advance as in the first modified example. However, unlike the pump unit 423, the second pump unit 425 supplies the working fluid f to the cylinder unit 422 only when a signal from the position control unit 302 is input.

In the bearing device 3 according to the second modification as described above, when the position control unit 302 deviates from the specified clearance h _set which is a predetermined threshold value, the magnitude of the facing distance h input from the position measurement unit 301 is. A signal for closing the relief valve 424b which is the valve part 424 is output to the valve part 424 of the reverse drive part 42, or a signal for supplying the working fluid f to the second pump part 425 is output. That is, when the rotor 2 approaches the main bearing pad 41, the second pump part 425 is operated to supply the working fluid f into the cylinder part 422, and the main bearing pad 41 is advanced along the axis O direction. Then, the rotor 2 is pushed back to return the position. On the contrary, when the rotor 2 moves away from the main bearing pad 41, the relief valve 424b of the valve part 424 which is the reverse drive part 42 is opened, the working fluid f in the cylinder part 422 is discharged, and the main bearing pad 41 is discharged. Is retracted along the direction of the axis O to weaken the force to support the rotor 2 and return the rotor 2 to the return position. Therefore, if the position measuring unit 301 and the position control unit 302 are provided only in the closest bearing pad group 40 on the one side of the axis O direction with respect to the thrust collar 20, the rotor can be adjusted by adjusting the position of the main bearing pad 41. The position 2 can be returned to the optimum position. Accordingly, it is possible to suppress the supply amount of the working fluid f to the minimum necessary while forming the backward drive unit 42 with a simpler structure.

  Although the embodiments of the present invention have been described in detail with reference to the drawings, the configurations and combinations of the embodiments in the embodiments are examples, and the addition and omission of configurations are within the scope not departing from the gist of the present invention. , Substitutions, and other changes are possible. Further, the present invention is not limited by the embodiments, and is limited only by the scope of the claims.

In addition, the several bearing pad group 30 in this embodiment is not necessarily restricted to two of the closest bearing pad group 40 and the 2nd bearing pad group 50, but is called the 3rd, 4th bearing pad group 30. In this manner, more bearing pad groups 30 may be provided.
Further, the backward drive unit 42 is not limited to being provided only in the closest bearing pad group 40, and may be included in the second bearing pad group 50, for example. In addition, when it has the 3rd and 4th bearing pad group 30, they may have the backward drive part 42. FIG.
Furthermore, the bearing pads of the different bearing pad groups 30 are not limited to those that are equally spaced in the circumferential direction. For example, the main bearing pad 41 and the second bearing of the closest bearing pad group 40 The sub bearing pads 51 of the pad group 50 may be arranged on the same radius.
Further, the shape of the bearing pad is not limited to a disk shape, and may be an arc shape or a rectangular shape.
Furthermore, the rotary machine in which the bearing device 3 of the present invention is used is not limited to the steam turbine 1, but for example, from a large rotary machine such as a gas turbine or a nuclear turbine to a medium or small rotary machine such as a compressor. Up to a machine, it can be used for various rotating machines that require the bearing device 3.

O ... axis 1 ... steam turbine 2 ... rotor 10 ... turbine body 3 ... bearing device 20 ... thrust collar 30 ... bearing pad group 40 ... closest bearing pad group 41 ... main bearing pad 411 ... main pad surface 42 ... reverse drive part 421 ... Piston part 421a ... Piston body part 421b ... Piston connection part 421c ... Seal ring 422 ... Cylinder part 422a ... Stopper 423 ... Pump part 423a ... Supply pipe 423b ... Pump 424 ... Valve part 424a ... Drain pipe 424b ... Release valve f ... Activation Fluid 50 ... second bearing pad group 51 ... sub-bearing pad 511 ... sub-pad surface 52 ... bearing pad support 60 ... bearing box L _set ... set load P _set ... set surface pressure h ... opposed distance 301 ... position measuring unit 302 ... position The control unit h _{set ...} provisions clearance 304 ... lubricating oil supply Section 304a ... Lubricating oil pump 304b ... Supply nozzle 305 ... Lubricating oil control section 305a ... Opening detection section 305b ... Lubricating oil valve 305c ... Lubricating oil valve drive section 306 ... Restriction section 307 ... Temperature monitoring section 308 ... Temperature determination section 309 ... Temperature Control part T _set ... Specified temperature 425 ... Second pump part TS ... Trigger signal P ... Bearing surface pressure F ... Thrust

Claims (8)

A thrust collar provided so as to protrude from the outer peripheral surface of the rotor extending along the axis;
A plurality of bearing pad groups in which the pad surface is disposed opposite to the axial direction with respect to the thrust collar;
The plurality of bearing pad groups are arranged such that the distance to the thrust collar is different between the bearing pad groups,
The nearest bearing pad group which is the bearing pad group closest to the thrust collar among the bearing pad group includes a backward drive unit configured to retract from the thrust collar,
The retraction drive unit retreats the bearing pad group when the force received from the thrust collar by the bearing pad group exceeds a predetermined threshold value.   2. The bearing device according to claim 1, wherein the closest bearing pad group is disposed on the innermost side in the radial direction of the axis among the plurality of bearing pad groups. The backward drive unit includes a piston unit that supports the bearing pad group from a back surface facing the pad surface;
A cylinder portion for accommodating the piston portion so as to be slidable in the axial direction;
A working fluid filled to support the piston portion within the cylinder portion;
A valve part for discharging the working fluid from the cylinder part when a force received from the thrust collar by the bearing pad group exceeds a predetermined threshold value;
The bearing device according to claim 1, wherein the piston part retreats along an axial direction when the working fluid is discharged.   The bearing device according to claim 3, wherein the cylinder part has at least one throttle part that divides the cylinder part into a plurality of parts. A position measuring unit for measuring the facing distance;
And a position control unit that adjusts an amount by which the reverse drive unit moves the bearing pad group so that the size of the facing distance measured by the position measurement unit becomes a predetermined size. The bearing apparatus as described in any one of Claim 1 to 4. A lubricating oil supply section that supplies lubricating oil between the bearing pad group and the thrust collar;
A lubricating oil control unit that adjusts the amount of lubricating oil supplied from the lubricating oil supply unit to a bearing pad group other than the retreated bearing pad group by retreating the bearing pad group by the retreat drive unit; The bearing device according to claim 1, wherein the bearing device is provided. A temperature monitoring unit for measuring a temperature of a surface of the nearest bearing pad group facing the thrust collar of the bearing pads;
A temperature determination unit for determining whether the temperature measured by the temperature monitoring unit exceeds a predetermined temperature; and
7. The bearing device according to claim 1, further comprising: a temperature control unit configured to cause the reverse drive unit to retract the bearing pad group based on a determination result in the temperature determination unit.   A rotary machine comprising the bearing device according to any one of claims 1 to 6.

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