Rotating machines, control devices

Abstract

Provided is a technology making it possible to adjust the force with which a tilting pad, which is on a tilting pad-type radial bearing built into a rotating machine, is pressed against a rotating shaft. A rotating machine 1 is provided with: a rotating shaft 20; a bearing device 30 for supporting a radial load of the rotating shaft 20; and an enclosure 10 accommodating the constituent elements of the rotating machine 1. The bearing device 30 comprises: a bearing support member 31; a tilting pad 32A that radially faces the rotating shaft 20, between the bearing support member 31 and the rotating shaft 20; a pivot 32B arranged so as to abut against the outside in the radial direction of the tilting pad 32A; an elastic body 32C for pushing the tilting pad 32A toward the rotating shaft 20, via the pivot 32B; and an adjustment unit 32D attached to the bearing support member 31 so as to enable adjustment of the urging force of the elastic body 32C.

Description

[Technical Field]

[0001] The present disclosure relates to rotary machines and the like. [Background technology]

[0002] BACKGROUND ART Conventionally, a rotary machine is known in which a radial load of a rotating shaft is supported by a tilting pad type radial bearing (see Patent Document 1).

[0003] In Patent Document 1, a tilting pad type radial bearing is applied to an expansion turbine. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Utility Model Application Publication No. 60-140876 Summary of the Invention [Problem to be solved by the invention]

[0005] In a tilting pad type radial bearing, an elastic body presses the tilting pad against the rotating shaft via a pivot, generating a film pressure of gas or liquid between the rotating shaft and the tilting pad, thereby supporting the radial load of the rotating shaft.

[0006] However, for example, in order to properly form a gas or liquid film pressure between the tilting pad and the rotating shaft, the force (hereinafter referred to as "preload") that the elastic body applies to press the tilting pad against the rotating shaft via the pivot must be appropriate.

[0007] In view of the above problems, an object of the present invention is to provide a technology that makes it possible to adjust the force (preload) that presses a tilting pad against a rotating shaft in a tilting pad type radial bearing built into a rotating machine. [Means for solving the problem]

[0008] In order to achieve the above object, in one embodiment of the present disclosure, A rotation axis; a bearing device that supports a radial load of the rotating shaft; a housing that houses components of a rotary machine including the rotating shaft and the bearing device, The bearing device is a fixed portion disposed radially outward from the rotation axis; a tilting pad disposed between the fixed portion and the rotation shaft so as to face the rotation shaft in the radial direction; a pivot disposed to abut against the outer side of the tilting pad in the radial direction; an elastic body that is disposed so as to abut against the outer side of the pivot in the radial direction and presses the tilting pad toward the rotation shaft via the pivot; an adjustment unit attached to the fixed part so as to adjust the biasing force of the elastic body, Rotating Machinery And, a drive mechanism that drives the adjustment unit; an actuator that drives the drive mechanism; a control device that controls the actuator in accordance with a rotation speed of a rotary machine, the control device controls the actuator so that the biasing force increases as the rotation speed increases. Rotating Machinery is provided.

[0009] In another embodiment of the present disclosure, A rotation axis; a bearing device that supports a radial load of the rotating shaft; a housing that houses components of a rotary machine including the rotating shaft and the bearing device, The bearing device is a fixed portion disposed radially outward from the rotation axis; a tilting pad disposed between the fixed portion and the rotation shaft so as to face the rotation shaft in the radial direction; a pivot disposed to abut against the outer side of the tilting pad in the radial direction; an elastic body that is disposed so as to abut against the outer side of the pivot in the radial direction and presses the tilting pad toward the rotation shaft via the pivot; an adjustment unit attached to the fixed part so as to be able to adjust the biasing force of the elastic body; a drive mechanism that drives the adjustment unit; an actuator that drives the drive mechanism; include, Rotating Machinery About and controlling the actuator in accordance with the rotation speed of the A control device, The actuator is controlled so that the biasing force increases as the rotation speed of the rotary machine increases. , A control device is provided. [Effects of the Invention]

[0010] According to the above-described embodiment, it is possible to adjust the force (preload) that presses the tilting pads against the rotating shaft in the tilting pad type radial bearing built into the rotary machine. [Brief explanation of the drawings]

[0011] [Figure 1] 1 is a cross-sectional view showing the structure of a first example of a rotary machine. [Figure 2] 1 is a vertical cross-sectional view showing the structure of a first example of a rotary machine. [Figure 3] FIG. 2 is a cross-sectional view showing the structure of a second example of a rotary machine. [Figure 4] FIG. 2 is a diagram illustrating a functional configuration of an example of a control system of a rotary machine. [Figure 5] 1 is a longitudinal cross-sectional view showing an expansion turbine as an example of a rotary machine. [Figure 6] FIG. 1 is a diagram illustrating an example of a hydrogen gas filling system. DETAILED DESCRIPTION OF THE INVENTION

[0012] Hereinafter, an embodiment will be described with reference to the drawings.

[0013] [First example of a rotating machine] A first example of a rotary machine 1 according to this embodiment will be described with reference to FIGS.

[0014] In addition, FIG. 1 shows a state in which the rotary machine 1 rotates counterclockwise.

[0015] Hereinafter, the axial direction, radial direction, and circumferential direction based on the rotating shaft 20 of the rotary machine 1 may be simply referred to as the "axial direction," the "radial direction," and the "circumferential direction."

[0016] Fig. 1 is a cross-sectional view showing the structure of a first example of a rotating machine 1. Specifically, Fig. 1 is a cross-sectional view taken along a plane perpendicular to a rotating shaft 20 of the first example of the rotating machine 1. Fig. 2 is a longitudinal cross-sectional view showing the structure of the first example of the rotating machine 1. Specifically, Fig. 2 is a cross-sectional view taken along a plane passing through the axis of a rotating shaft 20 of the first example of the rotating machine 1 and parallel to the rotating shaft 20.

[0017] In the drawing, only some of the components of the rotary machine 1 (the housing body 11, the flange 12, the seal member 13, the rotating shaft 20, and the bearing support member 31) are depicted as cross-sectional views. Also, in the drawing, a radial space is depicted between the housing body 11 and the bearing support member 31, and this space schematically represents that the housing body 11 and the bearing support member 31 exist as separate bodies. For example, the space between the housing body 11 and the bearing support member 31 is an extremely small gap in the entire axial direction or in part, and the housing body 11 and the bearing support member 31 are fixed so that they do not move relative to each other (i.e., so that the bearing support member 31 does not rotate with respect to the housing body 11) by abutting against each other with a seal member or the like interposed therebetween.

[0018] In addition, in addition to the above-mentioned sealing member, various configurations such as screws can be used to fix the housing main body 11 and the bearing support member 31 so that they do not move relative to each other, and the housing main body 11 and the bearing support member 31 may be fixed using any configuration.

[0019] As shown in FIG. 1, in this example, the rotary machine 1 includes a housing 10, a rotary shaft 20, and a bearing device 30.

[0020] The rotary machine 1 is, for example, an expansion turbine 1A (see FIG. 5) described below. The rotary machine 1 may also be a jet engine, a gas turbine, a supercharger, a compressor, a pump, a water wheel, or the like.

[0021] The housing 10 accommodates components of the rotary machine 1, including the rotating shaft 20 and the bearing device 30, in its internal space. The housing 10 includes a housing body 11, a flange 12, and a seal member 13.

[0022] The rotating shaft 20 is a member corresponding to the axis of the center of rotation of the rotating body of the rotary machine 1.

[0023] The bearing device 30 rotatably supports the rotating shaft 20. In this example, the bearing device 30 supports the radial load of the rotating shaft 20. The bearing device 30 may also support the thrust load of the rotating shaft 20 (see FIG. 5).

[0024] The bearing device 30 includes a bearing support member 31 and a radial bearing 32 .

[0025] The bearing support member 31 supports the radial bearing 32. The bearing support member 31 is disposed radially outward as viewed from the rotating shaft 20, surrounding the entire circumference of the rotating shaft 20. The bearing support member 31 is disposed radially spaced apart from the inner surface of the housing 10 (housing main body 11), and may be fixed to the housing 10 (housing main body 11) at both axial ends. This allows the bearing support member 31 to support the radial bearing 32 as a fixed part.

[0026] The radial bearing 32 supports the radial load of the rotating shaft 20. In this example, the radial bearing 32 is a tilting pad type radial bearing.

[0027] The radial bearing 32 includes a tilting pad 32A, a pivot 32B, an elastic body 32C, and an adjustment portion 32D.

[0028] The tilting pad 32A is arranged so as to face the rotating shaft 20 in the radial space between the rotating shaft 20 and the bearing support member 31. A plurality of tilting pads 32A (three in this example) are arranged in the circumferential direction. For example, the tilting pads 32A are arranged at angular positions set at approximately equal intervals in the circumferential direction. The outer peripheral surface of the tilting pad 32A is formed into a curved shape, such as a spherical shape. For example, a special coating is applied to the inner and outer peripheral surfaces of the tilting pad 32A to increase hardness.

[0029] The pivot 32B is disposed so as to abut against the radially outer side of the tilting pad 32A. One pivot 32B is provided for each tilting pad 32A. That is, the same number of pivots 32B as the number of tilting pads 32A (three in this example) are provided, and the multiple pivots 32B are disposed at circumferential positions (angular positions) where they can abut against the outer circumferential surfaces of the corresponding tilting pads 32A. The contact portion of the pivot 32B with the tilting pad 32A is formed into a curved surface, such as a spherical surface. This allows the curved tilting pad 32A to move freely while abutting against the pivot 32B. The contact portion of the pivot 32B with the tilting pad 32A is, for example, coated with a special coating to increase hardness.

[0030] The elastic body 32C abuts against the outer side of the pivot 32B in the radial direction, and generates a biasing force for pressing the tilting pad 32A toward the rotation shaft 20 via the pivot 32B. The elastic body 32C is, for example, a coil spring. An elastic body 32C is provided for each pivot 32B. That is, the same number of elastic bodies 32C as the number of pivots 32B (three in this example) are provided.

[0031] The elastic body 32C may be provided on only some of the pivots 32B (for example, one pivot 32B) among the plurality of pivots 32B (three in this example).

[0032] The pivot 32B and the elastic body 32C are disposed in radially extending through holes provided in the bearing support member 31. The bearing support member 31 is provided with the same number of through holes as the pivots 32B and the elastic bodies 32C (three in this example), and the multiple through holes are formed at circumferential positions (angular positions) corresponding to the angular positions at which the multiple tilting pads 32A are disposed.

[0033] The adjustment portion 32D is disposed so as to abut against the radially outer side of the elastic body 32C. An adjustment portion 32D is provided for each combination of pivot 32B and elastic body 32C. That is, the same number of adjustment portions 32D (three in this example) as the number of pivots 32B and elastic bodies 32C are provided. The adjustment portions 32D are attached to the bearing support member 31 so as to be able to adjust the radially outer end positions of the elastic bodies 32C. This makes it possible to adjust the expansion / contraction state of the elastic body 32C and adjust the biasing force with which the elastic body 32C presses the tilting pad 32A against the rotation shaft 20 via the pivot 32B.

[0034] For example, the adjustment portion 32D is a male screw member that can be screwed from the radial outside into a female screw portion formed on the radial inner surface of a through hole in the bearing support member 31 that accommodates the pivot 32B and the elastic body 32C. This makes it possible to adjust the radial outer end position of the elastic body 32C by adjusting the amount of screwing of the adjustment portion 32D (male screw member). The drive portion 32D1 of the adjustment portion 32D (male screw member) is exposed so as to be visible from the radial outside opening of the through hole in the bearing support member 31. This makes it possible to operate the adjustment portion 32D with a tool from the radial outside of the bearing support member 31 and adjust the amount of screwing of the adjustment portion 32D (male screw member).

[0035] The housing 10 is provided with through holes 11A that penetrate between the outer surface and the inner surface. One through hole 11A is provided for each radial bearing 32 (adjustment portion 32D). That is, the same number of through holes 11A as the number of adjustment portions 32D (three in this example) are provided.

[0036] The through-hole 11A is formed radially and linearly from the outer surface of the housing body 11 toward the drive unit 32D1 of the adjustment unit 32D. The cross-sectional shape and size of the through-hole 11A are appropriately set so that a tool (for example, a Phillips head screwdriver or a flat head screwdriver) for engaging the drive unit 32D1 can be inserted therethrough. This allows the tool to reach the adjustment unit 32D (drive unit 32D1) from outside the housing 10 to operate the adjustment unit 32D, thereby adjusting the biasing force with which the elastic body 32C presses the tilting pad 32A against the rotation shaft 20 via the pivot 32B.

[0037] The outer opening of the through hole 11A is closed by a flange 12 fixed to the housing body 11 with a screw or the like. A flange 12 is provided for each through hole 11A. That is, the same number of flanges 12 as the number of through holes 11A (three in this example) are provided.

[0038] A recess for accommodating a seal member 13 is provided on the mating surface of the flange 12 with the outer surface of the housing body 11. The seal member 13 is, for example, an O-ring. This ensures that the housing 10 of the rotating machine 1 is airtight and liquid-tight (oil-tight).

[0039] If airtightness or liquid tightness of the housing 10 is not required, the flange 12 and the seal member 13 may be omitted. Also, the link mechanism connected to the adjustment unit 32D (drive unit 32D1) may be installed so as to be exposed to the outside of the housing 10 (housing body 11) through the through-hole 11A. This allows the adjustment unit 32D to be operated simply by operating the link mechanism without inserting a tool through the through-hole 11A. Also, if the outer end of the adjustment unit 32D in the radial direction is The adjustment portion 32D may be configured to be exposed to the outside of the housing 10 (housing main body 11) through the through-hole 11A by extending outside the housing 10. This makes it easier to operate the adjustment portion 32D exposed to the outside of the housing 10.

[0040] [Second example of a rotating machine] Next, a second example of the rotary machine 1 according to this embodiment will be described with reference to FIG.

[0041] In addition, FIG. 3 shows a state in which the rotary machine 1 rotates clockwise.

[0042] Hereinafter, the same reference numerals will be used to designate the same or corresponding configurations as those in the first example described above, and the explanation will focus on the parts that differ from the first example, and explanations of the same or corresponding content as in the first example may be omitted.

[0043] <Structure of rotating machines> 3 is a cross-sectional view showing the structure of a second example of the rotary machine 1. Specifically, FIG. 3 is a cross-sectional view taken along a plane perpendicular to the rotary shaft 20 of the second example of the rotary machine 1.

[0044] In the drawing, the housing 10 of the rotary machine 1 is omitted, and only some of the components of the rotary machine 1 (the rotating shaft 20, the bearing support member 31, and the cylinder 35B) are depicted as cross-sectional views.

[0045] As shown in FIG. 3, in this example, the rotary machine 1 includes a housing 10, a rotary shaft 20, and a bearing device 30 (not shown), similar to the first example described above.

[0046] The bearing device 30 includes a bearing support member 31 and a radial bearing 32, similar to the first example described above.

[0047] In this example, the radial bearing 32 is a tilting pad type radial bearing, similar to the first example described above.

[0048] As in the first example described above, the radial bearing 32 includes a tilting pad 32A, a pivot 32B, an elastic body 32C, and an adjustment portion 32D.

[0049] Similar to the first example described above, a plurality of pivots 32B (three in this example) are arranged in the circumferential direction. Similar to the first example described above, the pivots 32B are arranged in through holes extending in the radial direction that are provided in the bearing support member 31.

[0050] The elastic body 32C is provided for only some of the pivots 32B (in this example, one pivot 32B) among the multiple pivots 32B. For example, as shown in Fig. 3, the elastic body 32C is a coil spring. In this example, the elastic body 32C is housed in a recess provided from the outer end of the pivot 32B in the radial direction toward the inner side in the radial direction.

[0051] Incidentally, the elastic bodies 32C may be provided for all of the plurality of pivots 32B, similarly to the first example described above.

[0052] Similar to the first example described above, the adjustment portion 32D is disposed so as to abut against the radially outer side of the elastic body 32C. Similar to the first example described above, the adjustment portion 32D is attached to the bearing support member 31 so as to be able to adjust the radially outer end position of the elastic body 32C. Specifically, similar to the first example described above, the adjustment portion 32D may be a male screw member that is able to adjust the amount of threading into the female screw portion of the through hole.

[0053] The drive mechanism 35 drives the adjustment unit 32D in response to the operation of the micro-displacement actuator 36, and adjusts the radial outer end position of the adjustment unit 32D. This allows the drive mechanism 35 to adjust the biasing force of the elastic body 32C, i.e., the preload of the radial bearing 32. The drive mechanism 35 includes a linear cam 35A, a cylinder 35B, and an elastic body 35C.

[0054] The linear cam 35A is attached to the radially outer end of the adjustment unit 32D. The outer peripheral surface of the linear cam 35A around the central axis of the through hole in which the adjustment unit 32D is disposed comes into contact with and slides against the tip of the movable unit 36B of the micro-displacement actuator 36, and converts the linear movement of the movable unit 36B into the rotational movement of the adjustment unit 32D. Specifically, when the movable unit 36B of the micro-displacement actuator 36 moves linearly in a direction approaching the linear cam 35A, the linear cam 35A can rotate the adjustment unit 32D in a direction that increases the amount of threading into the female thread portion of the through hole.

[0055] The cylinder 35B accommodates the linear cam 35A.

[0056] The elastic body 35C is disposed inside the cylinder 35B so as to abut against both the inner surface and the linear cam 35A. For example, the elastic body 35C abuts and slides against the outer circumferential surface of the linear cam 35A at a position substantially opposite the micro-displacement actuator 36 in the circumferential direction based on the central axis of the through-hole in which the adjustment unit 32D is disposed. The shape of the sliding surface of the linear cam 35A that contacts the elastic body 35C is defined so that the elastic body 35C contracts when the movable part 36B of the micro-displacement actuator 36 is displaced toward the linear cam 35A and the linear cam 35A rotates in a direction that increases the amount of screwing of the adjustment unit 32D. Therefore, when the movable part 36B of the micro-displacement actuator 36 is displaced away from the linear cam 35A, the restoring force of the elastic body 35C can rotate the linear cam 35A in a direction that decreases the amount of screwing of the adjustment unit 32D. Therefore, the elastic body 35C can reduce the screwing amount of the adjustment part 32D in accordance with the displacement of the movable part 36B of the minute displacement actuator 36 in the direction away from the linear cam 35A.

[0057] The micro-displacement actuator 36 drives the adjustment unit 32D. The micro-displacement actuator 36 is an actuator capable of outputting a micro-displacement corresponding to a micro-adjustment range of the screw-in amount of the adjustment unit 32D. The micro-displacement actuator 36 is, for example, a piezo-electric actuator that employs a piezo-electric element. The micro-displacement actuator 36 includes a main body 36A and a movable part 36B that protrudes from the main body 36A toward the sliding surface of the linear cam 35A. Under the control of the control device 60, the micro-displacement actuator 36 can adjust the biasing force of the elastic body 32C via the adjustment unit 32D by adjusting the amount of displacement of the movable part 36B.

[0058] For example, as shown in FIG. 3 , the drive mechanism 35 is disposed adjacent to the bearing support member 31 and the adjustment unit 32D, and the drive mechanism 35 and the micro-displacement actuator 36 are housed inside the housing body 11. Specifically, the cylinder 35B of the drive mechanism 35 may be fixed to the bearing support member 31, and the linear cam 35A of the drive mechanism 35 may be rotatably connected to the adjustment unit 32D as a unit through a through-hole provided in the cylinder 35B. In this case, a space capable of housing the bearing device 30 including the drive mechanism 35 and the micro-displacement actuator 36 and including a workspace for assembling the bearing device 30 therein is formed inside the housing body 11. Alternatively, the drive mechanism 35 and the micro-displacement actuator 36 may be disposed outside the housing body 11. For example, the cylinder 35B of the drive mechanism 35 and the micro-displacement actuator 36 are attached to the outer surface of the housing body 11. The housing body 11 may be provided with a through hole 11A similar to that of the first example described above, and the adjustment section 32D inside the housing body 11 and the linear cam 35A of the drive mechanism 35 outside the housing body 11 may be rotatably connected as a single unit through the through hole 11A.

[0059] <Rotating machine control system> FIG. 4 is a diagram showing an example of a functional configuration of a control system of the rotating machine 1. As shown in FIG.

[0060] As shown in FIGS. 3 and 4, the control system of the rotary machine 1 includes a control device 60 and a rotation speed sensor 70.

[0061] The control device 60 performs control related to the rotating machine 1. The control device 60 may be mounted on the rotating machine 1, or may be provided outside the rotating machine 1 and perform control related to the rotating machine 1 by outputting control commands to devices to be controlled by the rotating machine 1 via a predetermined communication line.

[0062] The functions of the control device 60 are realized by any hardware or any combination of hardware and software. For example, the control device 60 is mainly configured with a computer including a central processing unit (CPU), a memory device, an auxiliary storage device, and an interface device. The memory device is, for example, a static random access memory (SRAM). The auxiliary storage device is, for example, an electrically erasable programmable read-only memory (EEPROM) or a flash memory. The interface device includes a communication interface for communicating with other devices such as the micro-displacement actuator 36 and the rotation speed sensor 70. The interface device may also include an external interface for connecting to an external storage medium. This allows the control device 60 to read data and programs required for processing from an external storage medium through the external interface and install them in the auxiliary storage device, for example, on a factory production line.

[0063] The data and programs required for the processing of the control device 60 may be downloaded from an external device via a communication interface and installed in the auxiliary storage device.

[0064] The rotation speed sensor 70 acquires information relating to the rotation speed (rotational speed) of the rotating machine 1. The rotation speed sensor 70 is, for example, an encoder mounted on the rotating machine 1.

[0065] For example, the controller 60 controls the micro-displacement actuator 36 .

[0066] 4, the control device 60 includes, as functional units, a startup preload target value setting unit 601, a post-startup preload target value setting unit 602, and an operation amount conversion unit 603. These functions are realized, for example, by loading a program installed in an auxiliary storage device into a memory device and executing it on a CPU.

[0067] The startup preload target value setting unit 601 sets a target value (hereinafter referred to as "preload target value") N of the preload of the radial bearing 32 when the rotating machine 1 is started up. The preload at the start of the rotating machine 1 corresponds to the preload of the radial bearing 32 when the rotating machine 1 starts to rotate from a state where the rotation speed is zero. The preload target value N of the radial bearing 32 when the rotating machine 1 is started up is registered in advance in an auxiliary storage device or the like as the minimum value Nmin of the preload target value N of the radial bearing 32. For example, the startup preload target value setting unit 601 sets the preload target value N to the minimum value Nmin when the measured value of the rotation speed X of the rotating machine 1 is in an extremely low speed region that is equal to or less than a predetermined threshold value Xth1.

[0068] The post-startup preload target value setting unit 602 sets a target value (preload target value N) for the preload of the radial bearing 32 after startup of the rotating machine 1. The post-startup preload target value N of the rotating machine 1 is varied according to the rotation speed X of the rotating machine 1. Specifically, the preload target value N may be varied so that it increases as the rotation speed X of the rotating machine 1 increases. For example, information (e.g., a function such as a conversion formula) defining the correlation between the measured value of the rotation speed X of the rotating machine 1, acquired based on the output of the rotation speed sensor 70, and the preload target value N is registered in advance in the auxiliary storage device of the control device 60. As a result, the post-startup preload target value setting unit 602 can set the preload target value N corresponding to the rotation speed X of the rotating machine 1, based on the output of the rotation speed sensor 70, using the information defining the correlation loaded from the auxiliary storage device to the memory device. For example, when the measured value of the rotation speed X of the rotating machine 1 exceeds a threshold value Xth1, the post-startup preload target value setting unit 602 sets a preload target value N according to the rotation speed X of the rotating machine 1. The threshold value Xth1 is, for example, defined in advance as an upper limit value of the rotation speed when the rotating machine 1 is rotating at an extremely low speed at startup.

[0069] The manipulated variable converter 603 converts the preload target value N, set by the startup preload target value setting unit 601 or the post-startup preload target value setting unit 602, into a manipulated variable of the micro-displacement actuator 36 to be controlled. The manipulated variable converter 603 then energizes and drives the micro-displacement actuator 36 so as to realize the acquired manipulated variable. The manipulated variable of the micro-displacement actuator 36 is, for example, the displacement of the movable part 36B of the micro-displacement actuator 36 toward the linear cam 35A. That is, the manipulated variable converter 603 may convert the set preload target value N into the displacement of the micro-displacement actuator 36 required to generate, in the elastic body 32C, a biasing force equivalent to the preload target value N. For example, information (e.g., a function such as a conversion formula) defining the correlation between the preload target value N and the manipulated variable (displacement) of the micro-displacement actuator 36 is registered in advance in the auxiliary storage device of the control device 60. This allows the operation amount conversion unit 603 to convert the set preload target value N into an operation amount (displacement amount) of the micro-displacement actuator 36 using information specifying the correlation loaded from the auxiliary storage device to the memory device.

[0070] In this way, the control device 60 can control the micro-displacement actuator 36 and adjust the preload of the radial bearing 32 so that the preload of the radial bearing 32 increases as the rotation speed of the rotary machine 1 increases.

[0071] For example, if the preload of the radial bearing 32 is fixed to a relatively large value, it is possible to suppress vibrations in a region where the rotation speed of the rotary machine 1 is relatively high (especially in a high-speed rotation region). On the other hand, if the preload of the radial bearing 32 is fixed to a relatively high value, friction loss at the start of the rotary machine 1 and shaft loss (viscous resistance) during steady rotation may become relatively large, which may lead to an increase in energy consumption.

[0072] Conversely, if the preload of the radial bearing 32 is fixed to a relatively small value, it is possible to reduce friction loss at the start of the rotary machine 1 and shaft loss during steady rotation, thereby reducing energy consumption. On the other hand, if the preload of the radial bearing 32 is fixed to a relatively small value, there is a possibility that vibrations cannot be adequately suppressed in the range where the rotation speed of the rotary machine 1 is relatively high (especially in the high-speed rotation range).

[0073] In contrast to this, in this example, the control device 60 can vary the preload of the radial bearing 32 according to the rotation speed of the rotary machine 1. Specifically, the control device 60 can adjust the preload of the radial bearing 32 so that when the rotation speed of the rotary machine 1 is relatively low, the preload of the radial bearing 32 is relatively small, and when the rotation speed of the rotary machine 1 is relatively high, the preload of the radial bearing 32 is relatively large. Therefore, the control device 60 can reduce friction loss at the start of the rotary machine 1 and shaft loss during steady rotation, thereby reducing energy consumption and appropriately suppressing vibration of the rotary machine 1 in a range where the rotation speed is relatively high (especially in a high-speed rotation range).

[0074] [Examples of rotating machinery] Next, a specific example (expansion turbine 1A) of the rotary machine 1 according to this embodiment will be described with reference to FIG.

[0075] The following description will focus on the content common to the rotary machines 1 according to the first and second examples described above, and the content specific to the expansion turbine 1A.

[0076] Fig. 5 is a vertical cross-sectional view showing an expansion turbine 1A as an example of the rotary machine 1. Specifically, Fig. 5 is a diagram for explaining the contents common to the rotary machines 1 according to the first and second examples described above.

[0077] In this example, the up-down direction in the drawing corresponds to the vertical direction. Also, the casing 10 is omitted from Fig. 5. Also, in the drawing, only some of the components of the expansion turbine 1A (the bearing support member 31 and the thrust bearing 34) are shown as cross-sectional views.

[0078] The expansion turbine 1A includes a housing 10, a rotary shaft 20, a bearing device 30, an impeller 40, and an energy consuming section 50.

[0079] The bearing device 30 supports the radial load and thrust load on the rotating shaft 20 rotating at high speed.

[0080] For example, as shown in Fig. 5, the rotation shaft 20 is installed so as to extend in the vertical direction. Alternatively, the rotation shaft 20 may be arranged so as to extend in the horizontal direction.

[0081] An impeller 40 for expanding a process gas is attached to one end (the lower end in this example) of the rotating shaft 20. The process gas is, for example, hydrogen gas (see FIG. 6). Alternatively, the process gas may be helium gas, nitrogen gas, or air.

[0082] An energy consuming unit 50 is attached to the other end (the upper end in this example) of the rotating shaft 20. The energy consuming unit 50 can consume the rotational energy of the rotating shaft 20 driven by the process gas. The energy consuming unit 50 is, for example, an impeller of a compressor (see FIG. 6). The energy consuming unit 50 may also be a brake fan for braking or a generator.

[0083] The rotation axis 20 may be upside down in the vertical direction.

[0084] The bearing device 30 includes a bearing support member 31, a radial bearing 32, a collar 33, and a thrust bearing .

[0085] The bearing support member 31 supports a radial bearing 32, a collar 33, and a thrust bearing 34. The rotating shaft 20 passes through the bearing support member 31 in the vertical direction. An impeller 40 is attached to one end (lower end) of the rotating shaft 20 that is exposed from one end (lower end) of the bearing support member 31, and an energy consuming unit 50 is attached to the other end (upper end) of the rotating shaft 20 that is exposed from the other end (upper end) of the bearing support member 31.

[0086] The radial bearing 32 supports a radial load on the rotating shaft 20. Specifically, the radial bearing 32 is a tilting pad type radial bearing as described above.

[0087] In this example, two radial bearings 32 are provided, one at each end in the axial direction inside the bearing support member 31.

[0088] The collar 33 is attached to the rotary shaft 20 and has a disk shape centered on the rotary shaft 20. The collar 33 is provided inside the bearing support member 31 at the center in the axial direction.

[0089] The collar 33 is configured to be able to receive a reaction force (hereinafter referred to as a "thrust reaction force") generated by the thrust bearing 34 in response to the thrust load of the rotary shaft 20.

[0090] The thrust bearing 34 supports a thrust load on the rotary shaft 20. Specifically, the thrust bearing 34 generates a thrust reaction force on the collar 33.

[0091] The thrust bearing 34 is disposed so as to face the collar 33 in the axial direction. For example, as shown in Fig. 5, two thrust bearings 34 are provided, and each is disposed so as to be adjacent to both one end (lower end) side and the other end (upper end) side of the rotating shaft 20 when viewed from the collar 33.

[0092] For example, as shown in FIG. 5 , the thrust bearing 34 is a hydrostatic gas bearing. Specifically, the thrust bearing 34 has injection holes 34A that inject a predetermined gas toward the collar 33. For example, the injection holes 34A are provided at predetermined intervals in the circumferential direction. The injection holes 34A communicate with a gas supply path 34B that leads to the bearing support member 31 or the outside of the housing 10, and the predetermined gas is supplied to the injection holes 34A from the outside. The predetermined gas is, for example, the same gas as the process gas introduced into the expansion turbine 1A (impeller 40). In this case, the process gas before being introduced into the expansion turbine 1A including the impeller 40 is branched and introduced into the gas supply path 34B. Alternatively, the predetermined gas may be a gas dedicated to the thrust bearing 34 that is different from the process gas introduced into the expansion turbine 1A including the impeller 40. Alternatively, the thrust bearing 34 may be a hydrodynamic gas bearing that supports the thrust load of the rotating shaft 20 by gas film pressure between the thrust bearing 34 and the collar 33. In this case, the injection holes 34A are omitted. Furthermore, the thrust bearing 34 may be a combination of both a dynamic pressure type and a static pressure type.

[0093] The injection holes 34A are provided on the surface of the thrust bearing 34 facing the collar 33, and are formed so that the injection direction of the predetermined gas is in the axial direction. As a result, the predetermined gas injected from the injection holes 34A can generate a thrust reaction force in the collar 33. Furthermore, even if the rotating shaft 20 tilts due to runout or vibration of the rotating shaft 20, causing the collar 33 to approach the thrust bearing 34, the action of the injected predetermined gas can suppress abnormal approach due to an increase in the tilt of the rotating shaft 20. As a result, contact between the collar 33 and the thrust bearing 34 can be suppressed.

[0094] The gas injected from the injection holes 34A may be released to the atmosphere or may be recovered. In the latter case, the recovered gas may be returned to the same path as the gas before being introduced into the expansion turbine 1A.

[0095] [Application example of rotary machinery (expansion turbine)] Next, an application example of the rotary machine 1 (expansion turbine 1A) according to this embodiment will be described with reference to FIG.

[0096] Fig. 6 is a diagram showing an application example of the rotary machine 1 (expansion turbine 1A) Specifically, Fig. 6 is a diagram showing an example of a hydrogen gas filling system SYS.

[0097] The hydrogen gas filling system SYS is installed, for example, in a hydrogen station for filling a vehicle VCL with hydrogen gas.

[0098] As shown in FIG. 6, the system includes a hydrogen gas compression facility 100, an expansion valve 200, a hydrogen gas line 300, and a pre-cooling system 400.

[0099] The hydrogen gas compression equipment 100 compresses hydrogen gas supplied from a tank, boosts the pressure to a predetermined level, and outputs the compressed hydrogen gas.

[0100] The expansion valve 200 adiabatically expands (isenthalpic expands) the hydrogen gas output from the hydrogen gas compression equipment 100. At this time, since the temperature of the hydrogen gas before expansion is higher than the inversion temperature (-58°C), the temperature of the hydrogen gas after expansion rises due to the Joule-Thomson effect.

[0101] The hydrogen gas line 300 supplies the expanded hydrogen gas output from the expansion valve 200 to the pre-cooling system 400 .

[0102] The pre-cooling system 400 cools the hydrogen gas supplied from the hydrogen gas line 300 and supplies it to the dispenser 500 .

[0103] The pre-cooling system 400 includes a compressor 410 , a chiller 420 , a cold source 430 , and an expansion section 440 .

[0104] The compressor 410 compresses the hydrogen gas supplied from the hydrogen gas line 300 .

[0105] The cooler 420 exchanges heat between a refrigerant supplied from a cold heat source 430 and the hydrogen gas compressed by the compressor 410, thereby cooling the hydrogen gas.

[0106] The cold heat source 430 supplies a refrigerant having a temperature lower than that of the hydrogen gas output from the compressor 410 to the cooler 420 and circulates it.

[0107] A cooler similar to the cooler 420 may be provided upstream of the compressor 410, and the hydrogen gas in the hydrogen gas line 300 may be introduced into the compressor 410 after being cooled by the cooler.

[0108] The expansion section 440 expands the hydrogen gas cooled by the cooler 420. This allows the hydrogen gas to expand and lower its temperature. Furthermore, by expanding the hydrogen gas compressed by the compressor 410, the expansion ratio becomes relatively large, and as a result, the temperature of the hydrogen gas can be lowered more significantly. Therefore, the temperature of the hydrogen gas can be lowered to an appropriate level without requiring a pre-cooling system that requires a refrigerator equipment including, for example, a compressor, a condenser, an expansion valve, an evaporator, an accumulator, and the like.

[0109] In this example, the compressor 410 and the expansion section 440 are realized by the expansion turbine 1A. Specifically, the expansion turbine 1A realizes the function of the expansion section 440 by expanding hydrogen gas with the impeller 40 at one end of the rotary shaft 20, and realizes the function of the compressor 410 by compressing the hydrogen gas with the impeller serving as the energy consumption section 50 at the other end of the rotary shaft 20.

[0110] The dispenser 500 fills the hydrogen tank TNK of the vehicle VCL with high-pressure hydrogen gas supplied from the pre-cooling system 400. The vehicle VCL is, for example, a fuel cell vehicle equipped with a fuel cell capable of generating electricity using hydrogen gas as fuel.

[0111] In this way, the expansion turbine 1A can be applied to the pre-cooling system 400 of the hydrogen gas filling system SYS.

[0112] [Effect] Next, the operation of the rotary machine and the control device according to this embodiment will be described.

[0113] In this embodiment, the rotating machine includes a rotating shaft, a bearing device that supports a radial load of the rotating shaft, and a housing that accommodates components of the rotating machine including the rotating shaft and the bearing device. The rotating machine is, for example, the rotating machine 1 described above. The rotating shaft is, for example, the rotating shaft 20 described above. The bearing device is, for example, the bearing device 30 described above. The housing is, for example, the housing 10 described above. Specifically, the bearing device includes a fixed portion, a tilting pad, a pivot, an elastic body, and an adjustment portion. The fixed portion is, for example, the bearing support member 31 described above. The tilting pad is, for example, the tilting pad 32A described above. The pivot is, for example, the pivot 32B described above. The elastic body is, for example, the elastic body 32C described above. The adjustment portion is, for example, the adjustment portion 32D described above. More specifically, the fixed portion is disposed radially outward from the rotating shaft. Furthermore, the tilting pad is disposed between the fixed portion and the rotating shaft so as to face the rotating shaft in the radial direction. The pivot is disposed so as to abut against the radially outer side of the tilting pad. The elastic body is disposed so as to abut against the radially outer side of the pivot and presses the tilting pad toward the rotation axis via the pivot. The adjustment part is attached to the fixed part so as to be able to adjust the biasing force of the elastic body.

[0114] This makes it possible to adjust the force (preload) with which the elastic body presses the tilting pad against the rotation shaft via the pivot by adjusting the biasing force of the elastic body.

[0115] Furthermore, for example, in a tilting pad radial bearing, the force with which the elastic body presses the tilting pad against the rotating shaft via the pivot must be delicately adjusted to properly form the film pressure of gas or liquid between the tilting pad and the rotating shaft. Therefore, for example, after assembling the rotating machine, a rotation test may be performed, and depending on the test results, the rotating machine may need to be disassembled, the force with which the tilting pad is pressed against the rotating shaft may be adjusted, and then the rotating machine may be reassembled and subjected to a rotation test, which may require repeated work. Furthermore, repeated disassembly and reassembly of the rotating machine may accelerate the aging (deterioration) of the components.

[0116] In contrast to this, in this embodiment, the rotary machine has a structure in which the biasing force can be adjusted by operating the adjustment unit from outside the housing.

[0117] This makes it possible to easily adjust the force pressing the tilting pad against the rotating shaft from outside the housing of the rotating machine without disassembling the rotating machine.

[0118] In this embodiment, the housing may be provided with a through-hole that allows access to the adjustment unit from outside the housing. The through-hole is, for example, through-hole 11A.

[0119] This allows, for example, a tool to reach the adjustment unit through the through hole 11A and operate the adjustment unit.

[0120] In this embodiment, the rotating machine may also include a drive mechanism and an actuator. The drive mechanism is, for example, the drive mechanism 35 described above. The actuator is, for example, the micro-displacement actuator 36 described above. Specifically, the drive mechanism drives the adjustment unit. And the actuator drives the drive mechanism.

[0121] This allows the rotating machine to automatically operate the adjustment unit using the actuator and automatically adjust the force (preload) with which the elastic body presses the tilting pad against the rotating shaft via the pivot.As a result, the rotating machine can appropriately adjust the force (preload) with which the elastic body presses the tilting pad against the rotating shaft via the pivot in accordance with its operating state.

[0122] In this embodiment, the control device may control the actuator in accordance with the rotation speed of the rotary machine. The control device is, for example, the control device 60 described above.

[0123] This allows the control device to appropriately adjust the force (preload) with which the elastic body presses the tilting pad against the rotation shaft via the pivot, in accordance with the rotation speed of the rotating machine.

[0124] In addition, in this embodiment, the control device may control the actuator so that the biasing force of the elastic body increases as the rotation speed of the rotary machine increases.

[0125] As a result, the control device can, for example, reduce the force (preload) with which the elastic body presses the tilting pad via the pivot in a region where the rotational speed of the rotating machine is relatively low, thereby suppressing sliding loss at the start of the rotating machine and shaft loss during steady rotation. Furthermore, the control device can reduce the force with which the elastic body presses the tilting pad via the pivot in a region where the rotational speed is relatively high, thereby appropriately suppressing vibration of the rotating machine. Therefore, the control device can suppress sliding loss and shaft loss of the rotating machine in a region where the rotational speed is relatively low, while suppressing vibration of the rotating machine in a region where the rotational speed is relatively high. Therefore, the control device can simultaneously reduce the energy consumption of the rotating machine and suppress vibration of the rotating machine.

[0126] Although the embodiments have been described in detail above, the present disclosure is not limited to such specific embodiments, and various modifications and variations are possible within the scope of the gist described in the claims.

[0127] Finally, this application claims priority based on Japanese Patent Application No. 2022-111546, filed on July 12, 2022, the entire contents of which are incorporated herein by reference. [Explanation of symbols]

[0128] 1 Rotating Machinery 1A expansion turbine 10. Cabinet 11. Main body 11A through hole 12 flange 13 Sealing material 20 Rotation axis 30 Bearing device 31 Bearing support member 32 Radial bearing 32A Tilting Pad 32B Pivot 32C Elastic body 32D adjustment section 32D1 Drive unit 33 Color 34 Thrust bearing 35 Drive mechanism 36 Micro-displacement actuator 40 impeller 50 Energy consumption unit 60 Control device 70 RPM sensor 100 Hydrogen gas compression equipment 200 Expansion valve 300 Hydrogen gas line 400 Pre-cool System 500 dispensers SYS Hydrogen Gas Filling System TNK hydrogen tank VCL vehicle

Claims

1. A rotation axis; a bearing device that supports a radial load of the rotating shaft; a housing that houses components of a rotary machine including the rotating shaft and the bearing device, The bearing device is a fixed portion disposed radially outward from the rotation axis; a tilting pad disposed between the fixed portion and the rotation shaft so as to face the rotation shaft in the radial direction; a pivot disposed to abut against the outer side of the tilting pad in the radial direction; an elastic body that is disposed so as to abut against the outer side of the pivot in the radial direction and presses the tilting pad toward the rotation shaft via the pivot; an adjustment unit attached to the fixed part so as to adjust the biasing force of the elastic body, A rotating machine, a drive mechanism that drives the adjustment unit; an actuator that drives the drive mechanism; a control device that controls the actuator in accordance with a rotation speed of a rotary machine, the control device controls the actuator so that the biasing force increases as the rotation speed increases. Rotating machinery.

2. A rotating shaft, a bearing device that supports a radial load of the rotating shaft; a housing that houses components of a rotary machine including the rotating shaft and the bearing device, The bearing device is a fixed portion disposed radially outward from the rotation axis; a tilting pad disposed between the fixed portion and the rotation shaft so as to face the rotation shaft in the radial direction; a pivot disposed to abut against the outer side of the tilting pad in the radial direction; an elastic body that is disposed so as to abut against the outer side of the pivot in the radial direction and presses the tilting pad toward the rotation shaft via the pivot; an adjustment unit attached to the fixed part so as to be able to adjust the biasing force of the elastic body; a drive mechanism that drives the adjustment unit; an actuator that drives the drive mechanism; A control device for a rotary machine that controls the actuator in accordance with a rotation speed of the rotary machine, controlling the actuator so that the biasing force increases as the rotation speed of the rotary machine increases; Control device.

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