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WO2018105162A1 - Patin oscillant, dispositif palier à gaz et compresseur - Google Patents

Patin oscillant, dispositif palier à gaz et compresseur Download PDF

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Publication number
WO2018105162A1
WO2018105162A1 PCT/JP2017/025265 JP2017025265W WO2018105162A1 WO 2018105162 A1 WO2018105162 A1 WO 2018105162A1 JP 2017025265 W JP2017025265 W JP 2017025265W WO 2018105162 A1 WO2018105162 A1 WO 2018105162A1
Authority
WO
WIPO (PCT)
Prior art keywords
pad
vibration damping
axis
tilting pad
damping member
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/025265
Other languages
English (en)
Japanese (ja)
Inventor
拓造 鴫原
秀一 諫山
直之 長井
英樹 永尾
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
Original Assignee
Mitsubishi Heavy Industries Ltd
Mitsubishi Heavy Industries Compressor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd, Mitsubishi Heavy Industries Compressor Corp filed Critical Mitsubishi Heavy Industries Ltd
Publication of WO2018105162A1 publication Critical patent/WO2018105162A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings

Definitions

  • the present invention relates to a tilting pad, a gas bearing device, and a compressor.
  • This application claims priority on the basis of Japanese Patent Application No. 2016-236853 for which it applied to Japan on December 6, 2016, and uses the content here.
  • a bearing device is used to rotatably support the rotor.
  • a gas bearing device provided with a tilting pad is known as a bearing device.
  • This tilting pad is configured by swingably supporting a bearing pad having a pad surface that is in sliding contact with the rotor.
  • the gas existing around the rotor is drawn between the outer peripheral surface of the rotor and the inner surface of the bearing pad as the rotor rotates to form a film (gas film) made of this gas.
  • the rotor is supported rotatably.
  • the gas is compressed by being drawn between the outer peripheral surface of the rotor and the inner peripheral surface of the bearing pad, and dynamic pressure is generated. Due to this dynamic pressure, the rotor is supported without directly contacting the bearing pads.
  • the lubricating fluid is a gas
  • the viscosity of the lubricating fluid is lower than that of the oil lubricated bearing device. If the viscosity of the lubricating fluid is low, shaft unbalance, external force, and the like may cause shaft vibration to increase, and the shaft and the tilting pad may come into contact with each other. For this reason, it is difficult to commercialize a gas bearing device having a tilting pad.
  • Patent Document 1 in an oil lubricated bearing device provided with a tilting pad, a vibration reducing function is imparted to the tilting pad by providing an O-ring, a throttle mechanism, or a labyrinth seal around the tilting pad.
  • Technology has been proposed.
  • Gas bearing device has weaker force to change tilting pad posture than oil lubricated bearing device. Therefore, if an O-ring, a throttle mechanism, or a labyrinth seal is provided so as to surround the tilting pad so as to attenuate the shaft vibration as in the bearing device described in Patent Document 1, the tilting pad does not move. There is a possibility that. Thus, if the tilting pad does not move, contact between the shaft and the tilting pad may occur.
  • This invention provides a tilting pad, a gas bearing device, and a compressor that can improve stability and prevent contact with a rotating shaft.
  • the tilting pad is supported via the pivot on the inner surface of the housing that surrounds the rotating shaft that rotates about the axis from the outer peripheral side, and the tilt direction, the roll direction, and the yaw direction are supported by the pivot.
  • the tilting pad is supported so as to be swingable in a direction and can support the rotating shaft via a gas film.
  • the tilting pad includes a pad main body and a vibration damping member.
  • an outer peripheral surface facing outward in the radial direction centered on the axis is a support surface supported by the pivot, and an inner peripheral surface facing inward in the radial direction is connected to the rotating shaft via a gas film.
  • the pad surface is supported.
  • the vibration damping member is disposed only between the two side surfaces of the pad main body facing the axial direction and the inner surface of the housing facing the side surface to attenuate the vibration of the pad main body. Since the pad main body is supported by the pivot, it can move in the tilt direction, the roll direction, and the yaw direction, respectively.
  • the movement in the tilt direction of the pad body here refers to a movement in which the both ends of the pad body are inclined toward and away from the rotation axis with the pivot position as a fulcrum when the pad body is viewed from the axial direction. is there.
  • the movement of the pad body in the roll direction is a movement in which the pad surface is inclined in the axial direction.
  • the movement of the pad body in the yaw direction is a movement of the pad body rotating in the circumferential direction around the pivot.
  • the vibration damping member is disposed only between the side surface of the pad main body and the inner surface of the housing, it is possible to suppress the movement of the pad main body in the tilt direction and the yaw direction.
  • the vibration of the pad main body in the yaw direction that is most likely to vibrate can be attenuated by the vibration damping member. Therefore, stability can be improved and it can control that a tilting pad and a rotating shaft contact.
  • the vibration damping member according to the first aspect is formed so as to extend in the circumferential direction around the axis, and is provided in a plurality of rows in the radial direction around the axis. Also good. Since a plurality of vibration damping members extending in the circumferential direction are provided in this way, the size of each vibration damping member can be reduced. Therefore, the vibration damping member can be disposed even when the gap formed between the side surface of the pad main body and the inner surface of the housing is small. Furthermore, even if the vibration damping performance per vibration damping member is reduced, a plurality of vibration damping members are provided, so that a sufficient vibration damping effect can be obtained.
  • a plurality of vibration damping members according to the first aspect may be provided at intervals in the circumferential direction around the axis of the pad body.
  • the vibration damping member according to the first aspect may be disposed only at both ends in the circumferential direction centering on the axis. By doing in this way, the vibration attenuation performance to the yaw direction by a vibration attenuation member can be exhibited efficiently.
  • the pad main body according to the first aspect may include an inclined surface that is inclined so as to gradually decrease the thickness of the pad main body in a direction away from the pivot on the outer peripheral surface thereof. Good. Between the pad body and the rotating shaft, the pressure near the pivot is highest, and the pressure decreases as the distance from the pivot increases. Therefore, in the fifth aspect, the thickness of the pad main body is gradually reduced in the direction away from the pivot. By doing in this way, a pad main body can be reduced in weight and the inertial force of a pad main body can be reduced. Therefore, the followability of the pad main body with respect to the rotating shaft can be improved, and the stability can be improved.
  • the gas bearing device includes the vibration damping member according to any one of the first to fifth aspects. By doing in this way, the reliability of the gas bearing device using a tilting pad can be improved.
  • the gas bearing device includes a rotating shaft, a housing, a pivot, a tilting pad, and a vibration damping member.
  • the rotation axis rotates around the axis.
  • the housing surrounds the rotating shaft from the outer peripheral side.
  • the pivot is attached to the inner surface of the housing.
  • the tilting pad is supported by the pivot so as to be swingable in the tilt direction, the roll direction, and the yaw direction.
  • an outer peripheral surface facing outward in a radial direction centering on the axis is a support surface supported by the pivot.
  • an inner peripheral surface facing inward in the radial direction supports the rotating shaft via a gas film.
  • the vibration damping member attenuates the vibration of the tilting pad.
  • the vibration damping member is disposed only between the two side surfaces of the tilting pad facing in the axial direction and the inner surface of the housing facing the side surface. By doing so, since the vibration damping member is disposed only between the side surface of the tilting pad and the inner surface of the housing, it is possible to suppress the movement of the tilting pad in the tilt direction and the yaw direction from being restricted. . Further, the vibration of the tilting pad in the yaw direction that is most likely to vibrate can be damped by the vibration damping member. Therefore, stability can be improved and it can control that a tilting pad and a rotating shaft contact.
  • the vibration damping member according to the seventh aspect is formed so as to extend in the circumferential direction around the axis, and is provided in a plurality of rows in the radial direction around the axis. Also good. By doing in this way, even if the clearance gap formed between the side surface of a tilting pad and the inner surface of a housing is small, a vibration damping member can be arrange
  • a plurality of vibration damping members according to the seventh or eighth aspect may be provided at intervals in the circumferential direction around the axis of the tilting pad.
  • the vibration damping member according to the eighth or ninth aspect may be disposed only at both ends in the circumferential direction of the tilting pad.
  • positioned can be made in the circumferential direction centering on an axis line. Therefore, by adjusting the vibration damping performance in the yaw direction, for example, it is possible to suppress the movement of the tilting pad in the yaw direction more than necessary.
  • the thickness of the tilting pad gradually decreases in the direction away from the pivot on the outer peripheral surface thereof. You may provide the inclined surface which inclines so that it may make. By doing in this way, a tilting pad can be reduced in weight and the inertia force of a pad main body can be reduced. Therefore, the followability of the tilting pad with respect to the rotating shaft can be improved, and the stability can be improved.
  • the compressor includes the gas bearing device according to any one of the sixth to eleventh aspects.
  • the rotating shaft of a compressor can be stably supported by a gas bearing device.
  • the compressor structure can be suppressed from being complicated as compared with the case of using the oil lubricated bearing device.
  • the stability can be improved.
  • FIG. 8 is a sectional view taken along line VIII-VIII in FIG. 7.
  • FIG. 1 is a configuration diagram showing a schematic configuration of a compressor in the first embodiment of the present invention.
  • the compressor 100 according to the first embodiment includes a rotating shaft 2, an impeller 3, a casing 4, and a bearing device 5.
  • the rotating shaft 2 is formed in a cylindrical shape extending in the direction of the axis O. Both ends of the rotating shaft 2 in the direction of the axis O are rotatably supported by the bearing device 5.
  • the impeller 3 is attached to the outer peripheral surface 2 a of the rotary shaft 2.
  • the impeller 3 rotates around the axis O together with the rotary shaft 2.
  • the impeller 3 includes a disk 6 and a blade 7.
  • the disk 6 is formed in a disk shape, and the blade 7 is provided on one surface of the disk 6 in the direction of the axis O.
  • the rotating shaft 2 is illustrated with a plurality of impellers 3 arranged in the direction of the axis O, but only one impeller 3 may be provided.
  • Casing 4 accommodates rotating shaft 2 and impeller 3 inside.
  • the casing 4 further forms a fluid flow path 8 for circulating a fluid.
  • the casing 4 includes an inlet 9 for introducing a fluid from the outside on the first side in the direction of the axis O.
  • the casing 4 includes a discharge port 10 that discharges the fluid pressure-fed through the fluid flow path 8 on the second side in the direction of the axis O.
  • the bearing device 5 includes a tilting pad gas bearing device (gas bearing device) 5a and a thrust bearing device 5b.
  • the tilting pad gas bearing device 5a is a so-called journal bearing that supports the radial load of the rotating shaft 2 at both ends of the casing 4 in the axis O direction.
  • the thrust bearing device 5b supports a load in the direction of the axis O of the rotary shaft 2.
  • FIG. 2 is a diagram showing an overall configuration of the tilting pad gas bearing device according to the first embodiment of the present invention.
  • the tilting pad gas bearing device 5a includes a housing 11, a pivot 12, and a tilting pad 13A.
  • the tilting pad gas bearing device 5a in this embodiment supports the rotating shaft 2 using a part of the gas G, which is the fluid discharged from the discharge port 10 described above, as a lubricating fluid.
  • the housing 11 covers the rotary shaft 2 from the outer peripheral side. This housing 11 forms a space with a circular cross section that continues in the direction of the axis O inside.
  • the housing 11 is formed integrally with the casing 4, but the casing 4 and the housing 11 of the tilting pad gas bearing device 5a may be formed separately.
  • the pivot 12 is attached to the inner surface 11 a of the housing 11.
  • a plurality of pivots 12 (four in the example of FIG. 1) are provided at intervals in the circumferential direction about the axis O.
  • One pivot 12 supports one tilting pad 13A. These pivots 12 support the tilting pad 13A so as to be swingable in the tilt direction, the roll direction and the yaw direction, respectively.
  • the swing in the tilt direction is a movement in which both ends of the tilting pad 13A are inclined toward and away from the rotary shaft 2 with the position of the pivot 12 as a fulcrum when viewed from the direction of the axis O.
  • the movement in the roll direction is a movement in which the tilting pad 13A is inclined in the direction of the axis O.
  • the movement in the yaw direction is a movement in which the tilting pad 13A rotates in the circumferential direction around the axis of the pivot 12.
  • the tilting pad 13A is accommodated in a cylindrical internal space 14 formed by the inner surface 11a of the housing 11 and the outer peripheral surface 2a of the rotary shaft 2.
  • the tilting pad 13A is supported by the pivot 12 so as to be swingable in the tilt direction, the roll direction, and the yaw direction. That is, as with the pivot 12, the tilting pads 13A are provided in a plurality (four in the example of FIG. 1) at intervals in the circumferential direction centered on the axis O.
  • These tilting pads 13A include those having a pad main body 15A and a vibration damping member 16A, and those having only the pad main body 15A.
  • the pad main body 15A is formed in a plate shape curved in a circular arc shape that is concave toward the axis O.
  • the inner peripheral surface (in other words, the surface facing the inner side in the radial direction centering on the axis O) of the pad main body 15 ⁇ / b> A is a pad surface 17 that supports the rotating shaft 2.
  • the pad surface 17 has a radius of curvature that is slightly larger than the radius of curvature of the outer peripheral surface 2 a of the rotating shaft 2.
  • the outer peripheral surface of the pad main body 15 ⁇ / b> A on the outer side in the bending direction is a support surface 18 supported by the pivot 12.
  • the pad surface 17 supports the rotating shaft 2 through a gas film formed by the gas G existing around the rotating shaft 2.
  • the gas G existing around the rotating shaft 2 is drawn between the outer peripheral surface 2a of the rotating shaft 2 and the pad surface 17 of the pad main body 15A as the rotating shaft 2 rotates, so that the film (gas) Film).
  • the pad surface 17 may be provided with a synthetic resin layer such as PEEK (polyetheretherketone) or a metal layer for bearings. Further, high pressure gas may be supplied between the outer peripheral surface 2 a and the pad surface 17 via the pivot 12.
  • FIG. 3 is a sectional view of the tilting pad taken along line III-III in the first embodiment of the present invention.
  • the vibration damping member 16A attenuates the vibration of the pad main body 15A. More specifically, the vibration damping member 16A is provided for the purpose of mainly attenuating vibration in the yaw direction of the pad main body 15A. As shown in FIGS. 2 and 3, the vibration damping member 16 ⁇ / b> A is attached to the two side surfaces 19 a and 19 b of the pad main body 15 ⁇ / b> A facing the direction of the axis O. In other words, the vibration damping member 16A is disposed only between the side surfaces 19a and 19b and the inner surface 11a of the housing 11 facing the side surfaces 19a and 19b. Furthermore, in other words, the vibration damping member 16A is not provided on the end surface 20 (see FIG. 2) of the pad main body 15A facing the circumferential direction with the axis O as the center.
  • the vibration attenuating member 16A may be any member that can attenuate the vibration of the pad main body 15A, and various vibration attenuating elements can be used.
  • a vibration damping member 16A for example, a vibration damping member 16A formed of an elastically deformable material can be used.
  • the elastically deformable material include materials such as rubber and gel (silicon).
  • the vibration damping member 16A in the first embodiment is formed so as to extend in the circumferential direction about the axis O.
  • the vibration damping member 16A is formed in a columnar shape with a circular cross section.
  • Grooves 21 for accommodating the vibration damping member 16A are formed in the side surfaces 19a and 19b of the pad main body 15A described above.
  • the vibration damping member 16A is fixed inside the groove 21.
  • the vibration damping member 16A has, for example, a wire diameter of about 10% of the thickness dimension of the pad main body 15A in the radial direction around the axis O. Further, the groove 21 of the pad main body 15A is formed in such a size that an appropriate crushing allowance (for example, 20%) corresponding to the hardness (for example, about 70 degrees) of the vibration damping member 16A is obtained.
  • the tilting pad 13A includes the vibration damping member 16A described above on the side surface 19a and the side surface 19b.
  • the vibration damping member 16 ⁇ / b> A is arranged in an arc shape extending in parallel with the pad surface 17 when viewed from the axis O direction.
  • the vibration damping member 16A in this embodiment is illustrated as being disposed at the center of the pad body 15A in the thickness direction with respect to the pad body 15A.
  • the arrangement of the vibration damping member is not limited to the above position.
  • the four tilting pads 13A are arranged two above and below, with a horizontal line H passing through the axis O as a boundary.
  • the vibration damping member 16A is provided only on the two tilting pads 13A disposed below the horizontal line H, that is, below the axis O. This is because the lower two tilting pads 13A receive a larger load from the rotating shaft 2 than the two upper tilting pads 13A, and the vibration of the pad main body 15A increases. It is.
  • the vibration damping member 16A may be provided on all the tilting pads 13A.
  • the vibration damping member is disposed only between the side surfaces 19a, 19b of the pad main body 15A and the inner surface 11a of the housing 11, the pad main body 15A in the tilt direction or the yaw direction is provided. It can suppress that movement of is restricted. Furthermore, the vibration of the pad main body 15A in the yaw direction that most easily vibrates can be damped by the vibration damping member 16A. As a result, the stability of the tilting pad 13A can be improved, and the tilting pad 13A and the rotating shaft 2 can be prevented from contacting each other.
  • FIG. 4 is a side view of the pad body in the first modification of the first embodiment of the present invention as viewed from the axial direction.
  • the vibration damping members 16A are provided in a row on the side surfaces 19a and 19b.
  • a plurality of rows (for example, two rows) of vibration damping members 16B may be provided as in the tilting pad 13B shown in FIG.
  • These vibration damping members 16B extend parallel to the pad surface 17 when viewed from the direction of the axis O, and are spaced from the adjacent vibration damping members 16B in the vertical direction.
  • This interval is formed so that the vibration damping members 16B adjacent in the vertical direction do not contact each other, and may be larger than the wire diameter of the vibration damping member 16B, for example.
  • the wire diameter of the vibration damping member 16B is smaller than that of the vibration damping member 16A of the first embodiment.
  • each vibration damping member 16B can be reduced, so that the space between the side surfaces 19a, 19b of the pad main body 15A and the inner surface 11a of the housing 11 can be reduced. Even when the gap formed is small, the vibration damping member 16B can be disposed. Furthermore, even if the vibration damping performance per vibration damping member 16B is reduced, the vibration damping members 16B are provided in a plurality of rows, so that a sufficient vibration damping effect can be obtained. Three or more vibration damping members 16B may be provided. In FIG. 4, only the side surface 19a is shown, but the same applies to the side surface 19b (hereinafter the same applies to the second and third modified examples).
  • FIG. 5 is a side view corresponding to FIG. 4 in a second modification of the first embodiment of the present invention.
  • the vibration damping member 16A is continuous from the position of the first end face 20 to the position of the second end face 20 in the circumferential direction around the axis O. The case where it is formed is described.
  • a plurality of vibration damping members 16C may be provided on the side surface 19a at intervals in the circumferential direction (the same applies to the side surface 19b).
  • the vibration damping member 16C of the second modification is disposed only at the end portions 22a and 22b (both end portions) of the side surfaces 19a and 19b in the circumferential direction with the axis O as the center.
  • the circumferential lengths of these vibration damping members 16C may be determined according to the required vibration damping performance, the ease of movement of the pad main body 15A in the tilt direction and the roll direction, and the like.
  • the vibration damping member 16C in the second modification is different from the vibration damping member 16A in the first embodiment only in length, and the wire diameter and the arrangement in the thickness direction of the pad main body 15A are different from those in the first embodiment. The same can be applied (hereinafter the same applies to the third modification).
  • the vibration damping member 16C is disposed only on the end portions 22a and 22b of the tilting pad 13C that have a large movement in the yaw direction around the pivot 12. Therefore, vibration damping performance in the yaw direction can be efficiently exhibited.
  • the case where the two vibration damping members 16C are arranged at intervals in the circumferential direction around the axis O has been described.
  • the number of vibration damping members 16 ⁇ / b> C arranged at intervals in the circumferential direction is not limited to two. For example, three or more may be used.
  • FIG. 6 is a side view corresponding to FIG. 4 in a third modification of the first embodiment of the present invention.
  • the vibration damping member 16D may be provided only in the central part of the side surfaces 19a, 19b in the circumferential direction around the axis O.
  • the arrangement of the vibration damping member in the circumferential direction around the axis O is not limited to the arrangement of the vibration damping member 16C and the vibration damping member 16D of the second and third modifications.
  • FIG. 7 is a view of the pad main body in the second embodiment of the present invention as seen from the axial direction.
  • FIG. 8 is a sectional view taken along line VIII-VIII in FIG.
  • the pad body 15B of the tilting pad 13E according to the second embodiment has an inclined surface 23 that is inclined so as to gradually decrease the thickness of the pad body 15B in the direction away from the pivot 12. It has.
  • the 7 and 8 indicate the pressure distribution between the pad surface 17 of the pad main body 15B and the outer peripheral surface 2a of the rotating shaft 2 (see FIG. 2).
  • the pressure is higher as the two-dot chain line is farther from the pad surface 17. That is, the pressure between the pad surface 17 and the outer peripheral surface 2a of the rotary shaft 2 is highest near the pivot 12 of the pad body 15B.
  • the pressure between the pad surface 17 and the outer peripheral surface 2 a gradually decreases in the vicinity of the outer edge of the pad surface 17 far from the pivot 12 as the distance from the pivot 12 increases.
  • the thickness of the pad main body 15B in the radial direction around the axis O corresponds to the pressure between the pad surface 17 disposed inside the radial direction and the outer peripheral surface 2a of the rotary shaft 2. It is said to be thick.
  • the pad main body 15B is formed such that the thickness near the outer edge of the pad main body 15B where the pressure between the pad surface 17 and the outer peripheral surface 2a of the rotating shaft 2 is small is smaller than the thickness near the pivot 12. .
  • the inclined surface 23 in the second embodiment is formed at an inclination angle corresponding to the pressure distribution between the pad surface 17 and the outer peripheral surface 2a of the rotating shaft 2. That is, when the pressure suddenly decreases in the vicinity of the outer edge of the pad main body 15B, the inclination angle of the inclined surface 23 becomes abrupt. On the other hand, when the pressure decreases gradually, the inclination angle of the inclined surface 23 is increased. Has become moderate.
  • the inclined surface 23 is formed as a plane has been described.
  • the inclined surface 23 may be formed in a stepped shape, a curved surface shape, a combination thereof, or the like.
  • the vibration damping member 16A is provided only between the side surfaces 19a, 19b of the pad main body 15A and the outer peripheral surface 2a of the rotating shaft 2 as in the first embodiment described above. Yes.
  • the vibration damping member 16A of the second embodiment is not limited to the vibration damping member 16A of the first embodiment.
  • the vibration damping members 16B, 16C, and 16D of the first modification to the third modification of the first embodiment are used. It may be used.
  • the pad main body 15B can be reduced in weight by partially reducing the thickness. Therefore, the inertia force of the pad main body 15B can be reduced. As a result, it is possible to improve the followability of the pad main body 15B with respect to the rotating shaft 2 and to improve the stability while attenuating vibration in the yaw direction of the pad main body 15B by the vibration damping members 16A to 16D.
  • the present invention is not limited to the configurations of the above-described embodiments and modifications, and can be changed in design without departing from the scope of the invention.
  • the vibration damping members 16A, 16B, 16C, and 16D may be provided in the housing 11, for example.
  • the gas bearing device 1 of the compressor 100 has been described as an example.
  • the gas bearing device 1 is not limited to that used for the compressor 100. That is, it can also be used as a bearing device for a rotary machine other than the compressor 100.
  • a vibration damping member made of a material such as rubber or silicon is exemplified.
  • the vibration damping member of the present invention is not limited to the above structure as long as it can attenuate the vibration in the yaw direction of the pad main bodies 15A and 15B.
  • an oil damper or the like may be used as the vibration damping member.
  • the vibration damping members 16A, 16B, 16C, and 16D formed in a columnar shape having a circular cross section are exemplified.
  • the shape of the vibration damping members 16A, 16B, 16C, and 16D is not limited to a circular cross section or a column shape.
  • a cross-section formed in a polygonal or elliptical columnar shape, or a spherical or polyhedral vibration damping member may be used.
  • the present invention can be applied to a tilting pad, a gas bearing device, and a compressor. According to this invention, it becomes possible to improve stability.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Selon l'invention, un patin oscillant (13A) comprend un corps de patin (15A) et un élément d'amortissement de vibrations (16A). Le corps de patin (15A) comporte une face circonférentielle extérieure orientée vers l'extérieur dans la direction radiale autour de l'axe (O) servant de face de support (18) supportée par un pivot, et une face intérieure orientée vers l'intérieur dans la direction radiale servant de face de patin (17) supportant un arbre rotatif (2) par l'intermédiaire d'un film de gaz. L'élément d'amortissement de vibrations (16A) est disposé uniquement entre les deux faces latérales du corps de patin (15A) orientées dans la direction d'axe (O) et la face intérieure (11a) d'un carter (11) opposée à ces faces latérales et amortit les vibrations du corps de patin (15A).
PCT/JP2017/025265 2016-12-06 2017-07-11 Patin oscillant, dispositif palier à gaz et compresseur Ceased WO2018105162A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016236853A JP2018091453A (ja) 2016-12-06 2016-12-06 ティルティングパッド、ガス軸受装置及び圧縮機
JP2016-236853 2016-12-06

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WO2018105162A1 true WO2018105162A1 (fr) 2018-06-14

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PCT/JP2017/025265 Ceased WO2018105162A1 (fr) 2016-12-06 2017-07-11 Patin oscillant, dispositif palier à gaz et compresseur

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WO (1) WO2018105162A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112682345A (zh) * 2020-12-24 2021-04-20 北京理工大学 一种用于氢燃料电池系统的空气压缩机
CN112727927A (zh) * 2020-12-28 2021-04-30 北京理工大学 一种用于燃料电池系统空气压缩机的空气轴承
CN113586245A (zh) * 2021-08-31 2021-11-02 中国联合重型燃气轮机技术有限公司 一种燃气轮机的支撑装置及燃气轮机

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Publication number Priority date Publication date Assignee Title
CN112682345A (zh) * 2020-12-24 2021-04-20 北京理工大学 一种用于氢燃料电池系统的空气压缩机
CN112727927A (zh) * 2020-12-28 2021-04-30 北京理工大学 一种用于燃料电池系统空气压缩机的空气轴承
CN112727927B (zh) * 2020-12-28 2021-11-02 北京理工大学 一种用于燃料电池系统空气压缩机的空气轴承
CN113586245A (zh) * 2021-08-31 2021-11-02 中国联合重型燃气轮机技术有限公司 一种燃气轮机的支撑装置及燃气轮机
CN113586245B (zh) * 2021-08-31 2022-04-26 中国联合重型燃气轮机技术有限公司 一种燃气轮机的支撑装置及燃气轮机

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