JP2018189165A - Bearing device and turbo machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing device that can exhibit high damping performance without applying voltage to liquid of a squeeze film damper.SOLUTION: A bearing device (10) comprises a bearing (11), a bearing box (12), a squeeze film damper (15), and a flow passage (16). The squeeze film damper (15) comprises a plurality of elastic seal members (13), and liquid (14). The plurality of elastic seal members (13) are arranged separately in a direction of an axis of the baring (11) between an outer surface (11a) of the bearing and an inner surface (12a) of the bearing box in a direction perpendicular to the axis of the bearing (11). A space surrounded by the outer surface (11a) of the bearing, the inner surface (12a) of the bearing box, and the plurality of elastic seal members (13) is filled with the liquid (14). The flow passage (16) passes through the bearing (11) or the bearing box (12) in the direction of the axis of the bearing (11).SELECTED DRAWING: Figure 1

Description

  The present disclosure relates to a bearing device and a turbomachine.

  Conventionally, a squeeze film damper bearing is known as a bearing that supports a shaft that rotates at high speed in a centrifugal compressor.

  For example, Patent Document 1 describes a squeeze film damper bearing 300 as shown in FIG. The squeeze film damper bearing 300 includes a rotating shaft 301, a bearing metal 302, a bearing housing 303, and an O-ring 310. The bearing metal 302 supports the rotating shaft 301. The bearing housing 303 is in contact with the bearing installation portion 304 outside the bearing metal 302. The O-ring 310 is made of an insulating material for sealing a gap formed between the outer peripheral surface of the bearing metal 302 and the inner peripheral surface of the bearing housing 303. In this sealed space, a liquid 309 forming a squeeze film is sealed. The liquid 309 is a liquid whose viscosity changes with voltage. An oil supply passage 307 for supplying lubricating oil is provided in a gap between the rotary shaft 301 and the bearing metal 302.

  In order to apply a voltage to the liquid 309, an electric circuit for supplying a voltage is formed. In this electric circuit, a DC power supply 305 and a switch 308 are coupled in series, one end is connected to the ground 306, and the other end is connected to the bearing housing 303. Further, the bearing metal 302 is grounded by a ground 306.

  By turning on the switch 308 of the electric circuit, a voltage is applied to the liquid 309 and the viscosity of the liquid 309 changes. When voltage is applied to the liquid 309, the viscosity of the liquid 309 increases. When the vibration frequency becomes so high that the squeeze film breaks down, the switch 308 is turned on to apply a voltage to the liquid 309 in the sealed space forming the squeeze film to increase its viscosity, thereby reducing the squeeze film damping performance. To improve. As a result, the oil film in the squeeze film is prevented from being cut, the swing of the rotating shaft 301 is suppressed, and the reliability of the squeeze film damper bearing 300 is ensured.

JP 2000-145768 A

  In the technique described in Patent Document 1, it is not considered that the temperature of the liquid 309 rises due to the frictional heat in the bearing and the heat generated by the motor being transmitted to the squeeze film. For this reason, when the temperature of the liquid 309 rises, it is not certain whether the attenuation performance can be sufficiently improved by applying a voltage to the liquid 309. Further, according to the technique described in Patent Document 1, it is necessary to apply a voltage to the liquid 309 in order to increase the viscosity of the liquid 309.

  Therefore, the present disclosure provides a bearing device that can exhibit high damping performance without applying voltage to the liquid forming the squeeze film in the squeeze film damper.

This disclosure
A bearing for rotatably supporting the rotating shaft;
A bearing box surrounding the bearing around an axis of the bearing;
A plurality of elastic seal members arranged in the axial direction of the bearing between the outer surface of the bearing and the inner surface of the bearing box in a direction perpendicular to the axis of the bearing; the outer surface of the bearing; and the bearing box A squeeze film damper having a liquid filling the space surrounded by the inner surface and the plurality of elastic seal members;
A flow path penetrating the bearing or the bearing housing in the axial direction of the bearing,
A bearing device is provided.

  The above bearing device can exhibit high damping performance without applying a voltage to the liquid of the squeeze film damper.

FIG. 1 is a cross-sectional view illustrating an example of the bearing device of the present disclosure. FIG. 2 is a sectional view of the bearing device taken along line II-II in FIG. FIG. 3 is a cross-sectional view illustrating an example of the turbo machine of the present disclosure. FIG. 4 is a configuration diagram illustrating an example of the refrigeration cycle apparatus of the present disclosure. FIG. 5 is a configuration diagram illustrating another example of the refrigeration cycle apparatus of the present disclosure. FIG. 6 is a cross-sectional view showing a conventional squeeze film damper bearing.

<Knowledge based on studies by the present inventors>
In a bearing device having a squeeze film damper, heat generated in equipment near the bearing device such as a motor and frictional heat in the bearing may be transferred to the liquid forming the squeeze film. In this case, the temperature of the liquid rises and the viscosity is lowered, and the damping performance of the bearing device may be lowered. For this reason, it is considered that a high damping performance can be exhibited by appropriately cooling the parts in contact with the squeeze film damper and maintaining the liquid forming the squeeze film at a desired temperature. According to the technique described in Patent Document 1, the lubricating oil is supplied to the gap between the rotating shaft 301 and the bearing metal 302 through the oil supply passage 307. The oil supply path 307 is connected to a gap between the rotating shaft 301 and the bearing metal 302, and the size of the gap is considered to be usually very narrow for fluid lubrication. For this reason, it is difficult to increase the flow rate of the lubricating oil in the oil supply passage 307, and it is difficult to think that the bearing metal 302 is efficiently cooled by the oil supply passage 307 from the viewpoint of keeping the liquid forming the squeeze film at a desired temperature.

  Therefore, the present inventors have conducted day and night studies on a bearing device that can appropriately cool a part in contact with the squeeze film damper and exhibit high damping performance. As a result, the present inventors have newly found that the bearing device can have a flow path penetrating the bearing or the bearing housing, thereby efficiently cooling the bearing or the bearing housing and exhibiting high damping performance. I found it. The present inventors have devised the bearing device of the present disclosure based on such new knowledge. In addition, said knowledge is knowledge based on examination of the present inventors, and does not admit as prior art.

The first aspect of the present disclosure is:
A bearing for rotatably supporting the rotating shaft;
A bearing box surrounding the bearing around an axis of the bearing;
A plurality of elastic seal members arranged in the axial direction of the bearing between the outer surface of the bearing and the inner surface of the bearing box in a direction perpendicular to the axis of the bearing; the outer surface of the bearing; and the bearing box A squeeze film damper having a liquid filling the space surrounded by the inner surface and the plurality of elastic seal members;
A flow path penetrating the bearing or the bearing housing in the axial direction of the bearing,
A bearing device is provided.

  According to the first aspect, since the flow path penetrates the bearing or the bearing box, the flow rate of the cooling liquid in the flow path tends to increase when the cooling liquid flows in the flow path. For this reason, a bearing or a bearing box can be cooled efficiently, and the temperature rise of the liquid of a squeeze film damper can be prevented. Thereby, it can prevent that the viscosity of the liquid of a squeeze film damper falls, and the bearing apparatus which concerns on a 1st aspect can exhibit high damping performance, without applying a voltage to the liquid of a squeeze film damper.

  According to a second aspect of the present disclosure, in addition to the first aspect, the flow path provides a bearing device that passes through the bearing. When the rotating shaft is driven by the motor, the heat generated by the motor is transmitted to the bearing through the rotating shaft. For this reason, the temperature of a bearing tends to rise compared with the temperature of a bearing box. According to the 2nd aspect, since the flow path has penetrated the bearing, the bearing which is easy to rise in temperature can be cooled efficiently. As a result, the bearing device according to the second aspect can exhibit high damping performance.

  According to a third aspect of the present disclosure, in addition to the first aspect, the flow path provides a bearing device that penetrates the bearing box. According to the third aspect, since the bearing box surrounds the bearing around the axis of the bearing, it is easy to increase the cross-sectional area of the flow path perpendicular to the axis of the bearing. For this reason, it is easy to increase the flow rate of the coolant in the flow path. Thereby, the bearing apparatus which concerns on a 3rd aspect can cool a bearing housing efficiently, and can exhibit high damping performance.

  According to a fourth aspect of the present disclosure, in addition to the first to third aspects, the flow path includes an inner flow path that penetrates the bearing and an outer flow path that penetrates the bearing box. A bearing device is provided. According to the 4th aspect, a bearing and a bearing housing can be cooled efficiently. As a result, the bearing device according to the fourth aspect can exhibit high damping performance more reliably.

  A fifth aspect of the present disclosure provides the bearing device, in addition to any one of the first to fourth aspects, the flow path has a plurality of through holes arranged around the axis of the bearing. . According to the fifth aspect, since the cooling flow path flows through the plurality of through holes, the bearing or the bearing box can be cooled more efficiently. As a result, the bearing device according to the fifth aspect can exhibit high damping performance more reliably.

  In a sixth aspect of the present disclosure, in addition to the third aspect, the bearing box has a first protrusion that protrudes inward in a direction perpendicular to the axis of the bearing and is in contact with the liquid. The flow path provides a bearing device that penetrates the first protrusion. According to the sixth aspect, since the flow path passes through the first protrusion that is in contact with the liquid, the length of the flow path in the axial direction of the bearing can be shortened, and the flow path is formed in the bearing box. The time required for processing can be shortened. In addition, since the first protrusion is in contact with the liquid, the flow path is located near the liquid of the squeeze film damper. For this reason, the temperature rise of the liquid of a squeeze film damper can be prevented more reliably.

  According to a seventh aspect of the present disclosure, in addition to the sixth aspect, the bearing is adjacent to the first protrusion in the axial direction of the bearing and the first protrusion in a direction perpendicular to the axis of the bearing. There is provided a bearing device having a second projecting portion that projects outward and inward of the flow path penetrating the shaft. According to the seventh aspect, the bearing and the bearing box can be aligned in the axial direction of the bearing by the first protrusion and the second protrusion. In addition, the space between the second protrusion and the inner surface of the bearing box can be used to guide the coolant to the flow path penetrating the first protrusion.

The eighth aspect of the present disclosure is:
A rotation axis;
An impeller attached to the rotating shaft;
The bearing device according to any one of the first to seventh aspects, which is disposed around the axis of the rotating shaft,
Provide turbomachinery.

  According to the eighth aspect, since the bearing device can exhibit high damping performance, the turbo machine has high reliability.

  Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. In addition, the following embodiment is only an illustration and this invention is not limited by these.

<Bearing device>
As shown in FIG. 1, the bearing device 10 includes a bearing 11, a bearing box 12, a squeeze film damper 15, and a flow path 16. The bearing 11 supports the rotating shaft 35 in a rotatable manner. The bearing housing 12 surrounds the bearing 11 around the axis of the bearing 11. The squeeze film damper 15 includes a plurality of elastic seal members 13 and a liquid 14. The plurality of elastic seal members 13 are arranged apart in the axial direction of the bearing 11 between the outer surface 11 a of the bearing and the inner surface 12 a of the bearing housing 12 in a direction perpendicular to the axis of the bearing 11. The liquid 14 fills a space surrounded by the plurality of elastic seal members 13, the outer surface 11 a of the bearing 11, and the inner surface 12 a of the bearing box 12. The flow path 16 penetrates the bearing 11 or the bearing housing 12 in the axial direction of the bearing 11.

  The bearing 11 is typically a slide bearing. When the bearing device 10 is used, a lubricating space 65 that is a cylindrical space exists between the bearing 11 and the rotating shaft 35, and the lubricating liquid is supplied to the lubricating space 65 from the outside of the bearing device 10. The size of the gap in the radial direction of the rotating shaft 35 is set to, for example, several tens of μm so that fluid lubrication can be performed.

  The elastic seal member 13 is, for example, an O-ring.

  The space filled with the liquid 14 in the squeeze film damper 15 is typically a cylindrical space. The dimension of the squeeze film damper 15 in the direction perpendicular to the axis of the bearing 11 is, for example, 10 μm to 200 μm. Due to the viscosity of the liquid 14 in the squeeze film damper 15, vibration due to unbalance of the rotating shaft 35 and self-excited vibration can be suppressed. For this reason, it is desirable that the liquid 14 of the squeeze film damper 15 has a desired viscosity.

  As the predetermined coolant flows through the flow path 16, the bearing 11 or the bearing box 12 is cooled. Since the flow path 16 penetrates the bearing 11 or the bearing box 12, the flow rate of the coolant in the flow path 16 tends to increase, and the bearing 11 or the bearing box 12 is efficiently cooled. Thereby, the temperature rise of the liquid 14 of the squeeze film damper 15 is prevented. As a result, the liquid 14 tends to have a desired viscosity in the squeeze film damper 15, and the bearing device 10 can exhibit high damping performance.

  As shown in FIG. 1, the flow path 16 penetrates the bearing 11, for example. For example, when the rotating shaft 35 is driven by a motor, heat generated by the motor may be transmitted to the bearing 11 through the rotating shaft 35. For this reason, the temperature of the bearing 11 may be likely to rise as compared with the temperature of the bearing housing 12. If the flow path 16 penetrates the bearing 11, the bearing 11 can be efficiently cooled even when the temperature of the bearing 11 is likely to rise. As a result, the bearing device 10 can exhibit high damping performance.

  As shown in FIG. 1, the flow path 16 penetrates the bearing box 12, for example. Since the bearing housing 12 surrounds the bearing 11 around the axis of the bearing 11, it is easy to increase the cross-sectional area of the flow path 16 perpendicular to the axis of the bearing 12. This is advantageous from the viewpoint of increasing the flow rate of the coolant in the flow path 16. According to the bearing device 10, the bearing housing 12 can be efficiently cooled and high damping performance can be exhibited.

  As shown in FIG. 1, the channel 16 includes, for example, an inner channel 16 a and an outer channel 16 b. The inner flow path 16 a passes through the bearing 11. The outer flow path 16b penetrates the bearing box 12. In this case, the bearing 11 and the bearing housing 12 can be efficiently cooled, and the bearing device 10 can exhibit high damping performance more reliably.

  As shown in FIG. 2, the flow path 16 has, for example, a plurality of through holes arranged around the axis of the bearing 11. In this case, the amount of the coolant flowing through the flow path 16 increases, and the bearing 11 or the bearing box 12 can be cooled more efficiently.

  As long as the flow path 16 penetrates the bearing 11 or the bearing housing 12, the flow path 16 may extend parallel to the axis of the bearing 11, or may extend while being inclined with respect to the axis of the bearing 11. For example, the flow path 16 extends without being connected to the squeeze film damper 15.

  As shown in FIG. 1, the bearing box 12 has, for example, a first protrusion 12p. The first protrusion 12 p protrudes inward in a direction perpendicular to the axis of the bearing 11 and is in contact with the liquid 14. For example, the flow path 16 penetrates the first protrusion 12p. In this case, the length of the flow path 16 in the axial direction of the bearing 11 can be shortened, and the period required for processing to form the flow path 16 in the bearing box 12 can be shortened. In addition, since the first protrusion 12 p is in contact with the liquid 14, the flow path 16 is located near the liquid 14 of the squeeze film damper 15. For this reason, the temperature rise of the liquid 14 of the squeeze film damper 15 can be prevented more reliably.

  As illustrated in FIG. 1, the bearing 11 includes, for example, a second protrusion 11p. The second protrusion 11p is adjacent to the first protrusion 12p in the axial direction of the bearing 11. In addition, the second protruding portion 11p protrudes outward on the inner side than the flow path 16 passing through the first protruding portion 12p in the direction perpendicular to the axis of the bearing 11. In this case, the bearing 11 and the bearing housing 12 can be aligned in the axial direction of the bearing 11 by the first projecting portion 12p and the second projecting portion 11p. In addition, there is a cylindrical space between the second protrusion 11p and the inner surface 12a of the bearing box 12, and this space is used to guide the coolant to the flow path 16 penetrating the first protrusion 12p. Available.

  For example, in the axial direction of the bearing 11, one end surface of the bearing 11 and one end surface of the bearing housing 12 are aligned. The bearing housing 12 has a longer dimension than the bearing 11 in the axial direction of the bearing 11. The bearing box 12 includes, for example, a partition wall 12 w at a position away from the squeeze film damper 15 in the axial direction of the bearing 11. The partition wall 12w has a through hole having an inner diameter slightly larger than the diameter of the rotary shaft 35, and the rotary shaft 35 is disposed in the through hole. When the bearing device 10 supports the rotating shaft 35, an annular space is defined between the squeeze film damper 15 and the partition wall 12 w in the axial direction of the bearing 11 by the inner surface of the bearing housing 12 and the outer surface of the rotating shaft 35. It is done.

<Turbo machine>
Next, an example of the use of the bearing device 10 will be described. As shown in FIG. 3, the turbo machine 30 includes a rotating shaft 35, an impeller 38, and the bearing device 10. The impeller 38 is attached to the rotation shaft 35. The bearing device 10 is disposed around the axis of the rotation shaft 35. As described above, since the bearing device 10 can exhibit high damping performance, the turbo machine 30 has high reliability.

  The impeller 38 is fixed to the rotating shaft 35 by shrink fitting, for example. The bearing 11 of the bearing device 10 supports, for example, one end portion in the axial direction of the rotary shaft 35 in front of the impeller 38. For example, the bearing housing 12 is adjacent to the front end of the impeller 38 in the axial direction of the rotating shaft 35.

  As shown in FIG. 3, the turbo machine 30 further includes, for example, a bearing device 10b, a casing 31a, a casing 31b, a motor 32, a bearing retainer 39a, and a bearing retainer 39b.

  The bearing device 10 b is configured in the same manner as the bearing device 10, for example, and supports the other end of the rotating shaft 35 in the axial direction.

  An impeller 38 is disposed inside the casing 31a. The turbo machine 30 operates as a centrifugal compressor, for example. A compression space 61 exists inside the casing 31a. The compression space 61 is a space in contact with the impeller 38 on the radially outer side of the impeller 38. A compression space inlet 62 is formed at the front end of the impeller 38. The inner surface of the casing 31 a defines a vortex chamber 63 on the radially outer side of the impeller 38, and the compression space outlet 64 is in contact with the vortex chamber 63.

  When the motor 32 operates during the operation period of the turbo machine 30, the impeller 38 rotates together with the rotating shaft 35. Thereby, the compressive fluid is sucked into the compression space 61 and compressed. The compressed fluid is discharged from the compressed space outlet 64 to the outside of the turbo machine 30.

  The casing 31b is disposed adjacent to the casing 31a in the axial direction of the rotary shaft 35, and the casing 31b is fixed to the casing 31a. The motor 32 is disposed inside the casing 31b. The motor 32 includes a stator 33 and a rotor 34. The stator 33 is fixed to the casing 31b by shrink fitting, and the rotor 34 is fixed to the rotating shaft 35 by shrink fitting. A gap of a predetermined size is formed between the inner surface of the stator 33 and the outer surface of the rotor 34. The rotating shaft 35 extends outward in the axial direction from the end surface of the rotor 34 in the axial direction of the rotating shaft 35.

  The bearing retainer 39 a is disposed adjacent to the bearing device 10 in the axial direction of the rotating shaft 35. A storage space 71a for storing the lubricant is present inside the bearing retainer 39a. A pipe is connected to the bearing retainer 39 a, and this pipe defines a part of the lubricating liquid supply path 71. The lubricating liquid supply path 71 is connected to the storage space 71a. The storage space 71a is located on the outer side in the axial direction with respect to the rotation shaft 35, and the end surface of the rotation shaft 35 faces the storage space 71a. As shown in FIG. 1, the rotating shaft 35 has a communication path 73 including an inlet and an outlet therein. The inlet of the communication path 73 is located on the end surface of the rotating shaft 35. The outlet of the communication path 73 is located on the outer surface extending in the axial direction of the rotating shaft 35 and faces the lubricating space 65 between the bearing 11 and the rotating shaft 35. As a result, the storage space 71 a communicates with the lubrication space 65. A part of the communication path 73 extends in the radial direction of the rotation shaft 35.

  A discharge space 72 a that is an annular space is defined between the squeeze film damper 15 and the partition wall 12 w in the axial direction of the bearing 11 by the inner surface of the bearing box 12 and the outer surface of the rotating shaft 35. A pipe is connected to the bearing box 12, and this pipe defines a part of the lubricating liquid discharge path 72. The lubricant discharge path 72 is connected to the discharge space 72a. The discharge space 72 a communicates with the lubrication space 65.

  The lubricating liquid is stored in the storage space 71 a through the lubricating liquid supply path 71. The lubricating liquid stored in the storage space 71 a is supplied to the lubricating space 65 through the communication path 73. Centrifugal force accompanying the rotation of the rotating shaft 35 acts on the lubricating liquid in the portion of the communication path 73 extending in the radial direction of the rotating shaft 35, and the lubricating liquid is pumped toward the bearing space 65. Thereafter, the lubricating liquid is guided to the discharge space 72 a and is discharged to the outside of the turbo machine 30 through the lubricating liquid discharge path 72.

  The channel 16 communicates with the storage space 71a and the discharge space 72a. For this reason, a part of the lubricating liquid stored in the storage space 71 a through the lubricating liquid supply path 71 is supplied to the flow path 16 as a cooling liquid. Thereafter, the cooling liquid is guided to the discharge space 72a. As described above, in the turbo machine 30, a part of the lubricating liquid for lubricating the rotating shaft 35 and the bearing 11 is used as a cooling liquid to be supplied to the flow path 16. Note that the cooling liquid to be supplied to the flow path 16 may be a liquid of a different type from the lubricating liquid, and separately from the lubricating liquid for lubricating the rotating shaft 35 and the bearing 11, the outside of the bearing device 10. May be supplied from

  The bearing retainer 39b is disposed adjacent to the bearing device 10b in the axial direction of the rotary shaft 35. The bearing retainer 39b is configured in the same manner as the bearing retainer 39a.

<Refrigeration cycle equipment>
The turbo machine 30 is incorporated in the refrigeration cycle apparatus 1a, for example. As shown in FIG. 4, the refrigeration cycle apparatus 1 a includes, for example, a main circuit 21, a first circulation circuit 22, a second circulation circuit 23, and a turbo machine 30. The refrigeration cycle apparatus 1a functions as an air conditioner dedicated to cooling, for example. The refrigerant used in the refrigeration cycle apparatus 1a contains, for example, a substance having a saturated vapor pressure lower than atmospheric pressure as a main component at room temperature (Japanese Industrial Standard: 20 ° C. ± 15 ° C. JIS Z 8703). The main component of the refrigerant is not particularly limited as long as it is a substance having a saturated vapor pressure lower than atmospheric pressure at normal temperature, and is, for example, water, alcohol, or ether. In the present specification, the “main component” means a component that is contained most in mass.

  In the refrigeration cycle apparatus 1a, the turbo machine 30 functions as a compressor. The main circuit 21 is a circuit in which the first storage tank 24, the turbo machine 30, and the second storage tank 25 are connected in this order. In the main circuit 21, the internal space of the first storage tank 24 and the space in which the impeller 38 of the turbo machine 30 is disposed communicate with each other through the flow path 21a. In the main circuit 21, the spiral chamber 63 of the turbo machine 30 and the internal space of the second storage tank 25 are communicated with each other by a flow path 21c. In the main circuit 21, the internal space of the first storage tank 24 and the internal space of the second storage tank 25 communicate with each other through the flow path 21d.

  The first circulation circuit 22 includes a first pump 26 and a first heat exchanger 27. Liquid refrigerant is stored in the first storage tank 24. In the first circulation circuit 22, the liquid refrigerant stored in the first storage tank 24 is supplied to the first heat exchanger 27 by the first pump 26, and the refrigerant that has absorbed heat in the first heat exchanger 27 is the first storage tank 24. Is configured to return. In the 1st circulation circuit 22, the 1st storage tank 24 and the inlet_port | entrance of the 1st pump 26 are connected by the flow path 22a. The outlet of the first pump 26 and the inlet of the first heat exchanger 27 are connected by a flow path 22b. The outlet of the first heat exchanger 27 and the first storage tank 24 are connected by a flow path 22c.

  The second circulation circuit 23 includes a second pump 28 and a second heat exchanger 29. Liquid refrigerant is stored in the second storage tank 25. In the second circulation circuit 23, the liquid refrigerant stored in the second storage tank 25 is supplied to the second heat exchanger 29 by the second pump 28, and the refrigerant radiated by the second heat exchanger 29 is the second storage tank 25. Is configured to return. In the second circulation circuit 23, the second storage tank 25 and the inlet of the second pump 28 are connected by a flow path 23a. The outlet of the second pump 28 and the inlet of the second heat exchanger 29 are connected by a flow path 23b. The outlet of the second heat exchanger 29 and the second storage tank 25 are connected by a flow path 23c.

  In the main circuit 21, the second storage tank 25 stores low-temperature and high-pressure refrigerant in the refrigeration cycle. The low-temperature and high-pressure working fluid is sent to the first storage tank 24 through the channel 21d, and expands or evaporates in the first storage tank 24 to become a low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant in the first storage tank 24 is sent to the turbo machine 30 through the flow path 21a and is compressed by the turbo machine 30 to become a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant is discharged from the turbo machine 30 to the flow path 21 c and supplied to the second storage tank 25. The high-temperature and high-pressure refrigerant that has flowed into the second storage tank 25 is cooled in the second storage tank 25 and becomes a low-temperature and high-pressure refrigerant.

  The low-temperature and high-pressure refrigerant in the first storage tank 24 becomes a low-temperature and low-pressure refrigerant by cooling the fluid for heat transport filled in the first circulation circuit 22. The fluid for heat transport is sent to the first heat exchanger 27 through the flow path 22a and the flow path 22b by the first pump 26. For example, after the indoor air is cooled in the first heat exchanger 27, the first heat exchanger 27 Return to the storage tank 24.

  The high-temperature and high-pressure refrigerant flowing into the second storage tank 25 dissipates heat to the heat transport fluid filled in the second circulation circuit 23 to become a low-temperature and high-pressure working fluid. The fluid for heat transport is sent to the second heat exchanger 29 through the flow path 23a and the flow path 23b by the second pump 28, radiates heat to the outdoor air, and then returns to the second storage tank 25. In this way, the refrigeration cycle apparatus 1a functions as an air conditioner dedicated to cooling.

  For example, the liquid refrigerant stored in the first storage tank 24 is supplied to the lubricating space 65 as a lubricating liquid. The first storage tank 24 communicates with the storage space 71 a through the lubricating liquid supply path 71. Further, the discharge space 72 a communicates with the first storage tank 24 through the lubricant discharge path 72. For example, a pump 76 a is disposed in the lubricating liquid supply path 71, and the liquid refrigerant stored in the first storage tank 24 is supplied to the lubricating space 65 by the action of the pump 76 a. Thereafter, the liquid refrigerant is returned to the first storage tank 24 through the discharge space 72 a and the lubricating liquid discharge path 72. In this case, for example, the liquid refrigerant flows through the flow path 16 as a cooling liquid.

  The liquid refrigerant stored in the first storage tank 24 is supplied into the bearing device 10b by the action of the pump 76b, and then returned to the first storage tank 24.

(Modification)
The refrigeration cycle apparatus 1a can be changed from various viewpoints. For example, the lubricating space 65 may be supplied with a different type of lubricating liquid from the refrigerant of the refrigeration cycle. For example, oil may be supplied to the lubricating space 65 as the lubricating liquid. In this case, for example, a liquid incompatible with oil such as water may be supplied to the flow path 16 as a cooling liquid. In this case, the liquid refrigerant may be supplied to the flow path 16 as a cooling liquid, or a liquid other than the liquid refrigerant may be supplied to the flow path 16 as a cooling liquid.

  The refrigeration cycle apparatus 1a may be modified like the refrigeration cycle apparatus 1b shown in FIG. The refrigeration cycle apparatus 1b is configured in the same manner as the refrigeration cycle apparatus 1a unless otherwise described. The same or corresponding components of the refrigeration cycle apparatus 1b as those of the refrigeration cycle apparatus 1a are denoted by the same reference numerals, and detailed description thereof is omitted. The description regarding the refrigeration cycle apparatus 1a also applies to the refrigeration cycle 1b as long as there is no technical contradiction.

  The refrigeration cycle apparatus 1b includes a first heat exchanger 24a instead of the first storage tank 24, and includes a second heat exchanger 25a instead of the second storage tank 25. The first heat exchanger 24a is, for example, a shell and tube heat exchanger. The heat transport fluid filled in the first circulation circuit 22 indirectly exchanges heat with the refrigerant in the refrigeration cycle in the first heat exchanger 24a. Moreover, the 2nd heat exchanger 25a is a shell and tube type heat exchanger, for example. The heat transport fluid filled in the second circulation circuit 23 indirectly exchanges heat with the refrigerant of the refrigeration cycle in the second heat exchanger 25a.

  The bearing device of the present disclosure is particularly useful for home or business use air conditioners, chillers, and hot water supply heat pumps. The bearing device of the present disclosure is particularly useful for a heat pump using a refrigerant containing water as a main component. The bearing device of the present disclosure is a large refrigeration cycle device such as an industrial ice making device or a freezing / refrigeration device, a power source for pneumatic equipment used in a plant, a cleaning device using compressed air used in a clean room, etc. The present invention is also applicable to compressed air supply sources, thermal power generation, hydroelectric power generation, wind power generation, tidal power generation, turbines and pumps for various types of power generation such as nuclear power generation, and aircraft jet engines.

DESCRIPTION OF SYMBOLS 10 Bearing apparatus 11 Bearing 11a Outer surface 11p Second protrusion 12 Bearing box 12a Inner surface 12p First protrusion 13 Elastic seal member 15 Squeeze film damper 16 Flow path 16a Inner flow path 16b Outer flow path 30 Turbo machine 35 Rotating shaft 38 Impeller

Claims (8)

A bearing for rotatably supporting the rotating shaft;
A bearing box surrounding the bearing around an axis of the bearing;
A plurality of elastic seal members arranged in the axial direction of the bearing between the outer surface of the bearing and the inner surface of the bearing box in a direction perpendicular to the axis of the bearing; the outer surface of the bearing; and the bearing box A squeeze film damper having a liquid filling the space surrounded by the inner surface and the plurality of elastic seal members;
A flow path penetrating the bearing or the bearing housing in the axial direction of the bearing,
Bearing device.   The bearing device according to claim 1, wherein the flow path passes through the bearing.   The bearing device according to claim 1, wherein the flow path penetrates the bearing box.   The bearing device according to claim 1, wherein the flow path includes an inner flow path that passes through the bearing and an outer flow path that passes through the bearing box.   The bearing device according to any one of claims 1 to 4, wherein the flow path has a plurality of through holes arranged around an axis of the bearing. The bearing housing has a first protrusion that protrudes inward in a direction perpendicular to the axis of the bearing and is in contact with the liquid;
The bearing device according to claim 3, wherein the flow path passes through the first protrusion.   The bearing is adjacent to the first protrusion in the axial direction of the bearing and protrudes outside and inside the flow path passing through the first protrusion in a direction perpendicular to the axis of the bearing. The bearing device according to claim 6, further comprising a second projecting portion. A rotation axis;
An impeller attached to the rotating shaft;
The bearing device according to any one of claims 1 to 7, which is disposed around an axis of the rotating shaft.
Turbo machine.

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