JP2017106330A - Turbomachine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a turbomachine having high durability.SOLUTION: A turbomachine (100a) is equipped with a rotary shaft (1); a bearing (4); a partition wall (8); and a disc wheel (2). The bearing (4) has a bearing surface (4a) facing an outer peripheral surface of the rotary shaft (1) while a liquid refrigerant in interposed therebetween. The partition wall (8) faces an end surface (1e) of the bearing (1) in an axial direction of the bearing (1) while a discharge space (6) collecting a liquid refrigerant discharged from the bearing (4) with a gas phase refrigerant is interposed therebetween, and has a through-hole (8a) in which the rotary shaft (1) is inserted. The disc wheel (2) has a front surface (2a) facing the partition wall (8) while a suction space (5) sucking the gas phase refrigerant therein is interposed. The partition wall (8) and the rotary shaft (1) are form a throttle (9) filled with the gas phase refrigerant supplied from the discharge space (6) between a surface forming the through-hole (8a) and the outer peripheral surface of the rotary shaft.SELECTED DRAWING: Figure 1

Description

  The present disclosure relates to turbomachines.

  Conventionally, as a turbomachine, a compressor having a rotating shaft and having a rotating body that compresses water vapor as a refrigerant gas is known, and a technique for supplying water as a lubricant to a bearing that supports the rotating shaft. It has been known.

  For example, Patent Literature 1 describes a refrigerator 300 in which water is used as a refrigerant, as shown in FIG. 4, and the refrigerator 300 includes a compressor 304. The compressor 304 includes a housing 322, a rotating body 324, a plurality of bearings 326, a motor 328, a seal portion 330, a lubricating water supply line 332, and a lubricating water discharge line 334. A rotating body 324, a plurality of bearings 326, and a seal portion 330 are provided inside the housing 322. A compression chamber 322a for compressing the refrigerant gas is provided inside the housing 322. The pressure on the inlet side of the compression chamber 322a is set to, for example, a saturated vapor pressure of water of about 7 ° C. so that water vapor as the refrigerant gas introduced into the compression chamber 322a does not condense. The rotating body 324 has a plurality of impellers 324a and a rotating shaft 324b, and rotates by receiving the driving force of the motor 328 to compress water vapor as refrigerant gas in the compression chamber 322a. The rotation shaft 324b is disposed inside the housing 322 so as to extend in the axial direction of the housing 322. The rotation shaft 324b is rotatably supported by a plurality of bearings 326.

  One of the plurality of bearings 326 is disposed on the opposite side of the motor 328 with respect to the compression chamber 322a. Each bearing 326 is a sliding bearing, and water (lubricating water) as a lubricant is supplied to each bearing 326 through a lubricating water supply line 332. A slight gap is formed between the inner peripheral surface of the bearing 326 and the outer peripheral surface of the rotary shaft 324b. The lubricating water supplied to the bearing 326 is introduced into the gap to form a water film, and then flows out from the gap to both ends in the axial direction. The lubricating water that has flowed out accumulates in a space 326 a around the bearing 326 inside the housing 22 and is discharged through the lubricating water discharge line 334. The pressure in the space 326a in which the bearing 326 is provided in the housing 322 is about 1 atmosphere or more.

  The seal portion 330 separates the space 326a and the compression chamber 322a inside the housing 322. Since the compression chamber 322a has a negative pressure with respect to the space 326a, part of the lubricating water in the space 326a is sucked into the compression chamber 322a side through the gap between the seal portion 330 and the rotation shaft 324b. At this time, the seal portion 330 prevents a large amount of lubricating water from being rapidly sucked into the compression chamber 322a.

International Publication No. 2010/010925

  The compressor described in Patent Document 1 has room for improving durability. Therefore, the present disclosure provides a turbo machine having high durability.

This disclosure
A rotation axis;
A bearing that supports the rotating shaft, and has a bearing surface facing the outer peripheral surface of the rotating shaft in a state where a liquid refrigerant is interposed;
The liquid refrigerant discharged from the bearing faces the end surface of the bearing in the axial direction of the bearing with a discharge space in which the liquid refrigerant is stored together with the gas-phase refrigerant, and has a through hole into which the rotating shaft is inserted. A partition,
An impeller fixed to the rotating shaft, having a front surface facing the partition wall in a state where a suction space for sucking a gas-phase refrigerant is interposed on the opposite side of the bearing as viewed from the partition wall in the axial direction of the rotating shaft. An impeller for sucking the gas-phase refrigerant from the suction space by rotating together with the rotating shaft,
The partition and the rotary shaft form a throttle filled with the gas-phase refrigerant supplied from the discharge space between a surface forming the through hole and an outer peripheral surface of the rotary shaft.
Provide turbomachinery.

  The above turbomachine has high durability.

Sectional drawing which shows the turbomachine which concerns on embodiment of this indication Sectional drawing which shows the turbomachine which concerns on a modification Sectional drawing which shows the turbomachine which concerns on another modification The block diagram which shows the conventional refrigerator provided with the compressor as a turbo machine

  In the compressor 304 described in Patent Literature 1, a part of the lubricating water accumulated in the space 326a is sucked into the compression chamber 322a side through a gap between the seal portion 330 and the rotating shaft 324b. Since the pressure at the negative pressure inside the compression chamber 322a is set to the saturated vapor pressure, the lubricating water sucked into the compression chamber 322a seems to evaporate immediately. However, although part of the lubricating water sucked into the compression chamber 322a evaporates, the water vapor cooled by the latent heat of evaporation condenses into water droplets, which may collide with the impeller 324a. For this reason, there is a possibility that the impeller 324a may be damaged by a water droplet colliding with the impeller 324a. Thus, the compressor 304 has room for improving durability.

  From the viewpoint of improving the durability of the compressor 304, the pressure of the space 326a is set to the temperature of the lubricating water so that the level of the lubricating water is formed below the gap between the seal portion 330 and the rotating shaft 324b. On the other hand, it is conceivable to keep the saturated vapor pressure determined. Thereby, it can prevent that the lubricating water which is a liquid phase is sucked into the compression chamber 322a side. However, when the temperature of water in the space 326a is low, the saturated vapor pressure of water at that temperature is also low, so the pressure in the space 326a is low. For this reason, since the pressure at the end surface of the bearing 326 in the axial direction of the bearing 326 decreases, the gap between the inner peripheral surface of the bearing 326 and the outer peripheral surface of the rotary shaft 324b is near the end surface of the bearing 326 in contact with the space 326a. The subcool degree of the formed water film is reduced. As a result, cavitation tends to occur inside the water film. As a result, the cooling capacity by the mixed lubrication in the bearing 326 is not sufficient, and the seizure load capacity is reduced, making it difficult to sufficiently enhance the durability of the compressor 304. Here, the “seizure load capacity” means a load at which seizure occurs when the load to be supported by the sliding bearing in the mixed lubrication state is increased. As described above, when the durability of the compressor 304 is improved, the pressure in the space 326a needs to be appropriately maintained, but Patent Literature 1 does not suggest any such knowledge. The turbomachine of the present disclosure has been devised based on such knowledge. In addition, the knowledge regarding the deformation | transformation of the compressor 304 was obtained as a result of consideration of the present inventors, and this knowledge is not a prior art.

The first aspect of the present disclosure is:
A rotation axis;
A bearing that supports the rotating shaft, and has a bearing surface facing the outer peripheral surface of the rotating shaft in a state where a liquid refrigerant is interposed;
The liquid refrigerant discharged from the bearing faces the end surface of the bearing in the axial direction of the bearing with a discharge space in which the liquid refrigerant is stored together with the gas-phase refrigerant, and has a through hole into which the rotating shaft is inserted. A partition,
An impeller fixed to the rotating shaft, having a front surface facing the partition wall in a state where a suction space for sucking a gas-phase refrigerant is interposed on the opposite side of the bearing as viewed from the partition wall in the axial direction of the rotating shaft. An impeller for sucking the gas-phase refrigerant from the suction space by rotating together with the rotating shaft,
The partition and the rotary shaft form a throttle filled with the gas-phase refrigerant supplied from the discharge space between a surface forming the through hole and an outer peripheral surface of the rotary shaft.
Provide turbomachinery.

  According to the first aspect, the gas phase refrigerant is stored in the discharge space in addition to the liquid refrigerant, and the throttle is filled with the gas phase refrigerant supplied from the discharge space. Thereby, the liquid refrigerant stored in the discharge space is prevented from leaking into the suction space, and the liquid refrigerant can be prevented from colliding with the impeller and damaging the impeller. In addition, heat generated from a heat-generating component such as an impeller is transmitted through the rotating shaft, whereby the discharge space is heated and the saturated vapor pressure of the refrigerant stored in the discharge space is appropriately maintained. In addition, due to the restriction, an appropriate pressure difference is generated between the discharge space and the suction space. For this reason, the pressure at the end face of the bearing in the axial direction of the rotating shaft is appropriately maintained, and the occurrence of cavitation is suppressed in the liquid film formed by the liquid refrigerant interposed between the outer peripheral surface of the rotating shaft and the bearing surface. As a result, the durability of the bearing can be increased. Thus, the turbomachine of the first aspect has high durability.

  According to a second aspect of the present disclosure, in addition to the first aspect, the rotating shaft is attached to the rotating shaft adjacent to the impeller on the side opposite to the partition wall when viewed from the impeller in the axial direction of the rotating shaft, A turbomachine is provided, further comprising a motor for rotating the motor. According to the second aspect, since the motor is attached to the rotating shaft adjacent to the impeller, the motor which is a heat generating component in addition to the impeller is disposed at a relatively close position in the discharge space. For this reason, the amount of heat transmitted to the discharge space by the rotating shaft is relatively large, and it is easy to increase the saturated vapor pressure of the refrigerant stored in the discharge space.

  According to a third aspect of the present disclosure, in addition to the first aspect or the second aspect, the third aspect of the present disclosure is formed in an annular shape while extending from the outer peripheral surface of the rotation shaft to the outer side in the radial direction of the rotation shaft. A turbomachine is further provided, further comprising an annular body arranged. According to the third aspect, even when the liquid refrigerant level in the discharge space rises and the liquid refrigerant approaches the throttle, the liquid refrigerant is kept away from the throttle by the centrifugal action that occurs when the annular body rotates together with the rotating shaft. It is done. Thereby, it is possible to prevent the liquid refrigerant stored in the discharge space from leaking into the suction space.

  According to a fourth aspect of the present disclosure, in addition to any one of the first to third aspects, the partition includes a turbomachine having a heat insulating structure inside the partition. According to the 4th aspect, it is suppressed by the heat insulation structure that the temperature and pressure of discharge space fall. As a result, the subcooling of the liquid film formed by the liquid refrigerant interposed between the outer peripheral surface of the rotating shaft and the bearing surface becomes sufficiently large near the end face of the bearing in contact with the discharge space, and cavitation occurs inside the liquid film. Is easily suppressed.

  Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. The following description relates to an example of the present invention, and the present invention is not limited to these.

  As shown in FIG. 1, the turbo machine 100 a of the present disclosure includes a rotating shaft 1, a bearing 4, a partition wall 8, and an impeller 2. The turbo machine 100a is, for example, a turbo compressor. For example, the turbo machine 100a compresses a predetermined gas phase refrigerant such as water vapor. The rotating shaft 1 extends in the horizontal direction, for example. The bearing 4 has a bearing surface 4 a that faces the outer peripheral surface of the rotating shaft 1 in a state where the liquid refrigerant is interposed, and supports the rotating shaft 1. The bearing 4 is a sliding bearing lubricated with a liquid refrigerant. The solid arrows in FIG. 1 conceptually show the flow of the liquid refrigerant that lubricates the bearing 4. The partition wall 8 faces the end surface 4e of the bearing 4 in the axial direction of the bearing 4 with the discharge space 6 interposed therebetween. That is, a discharge space 6 is formed between the partition wall 8 and the bearing 4 in the axial direction of the bearing 4. In the discharge space 6, the liquid refrigerant discharged from the bearing 4 is stored together with the gas phase refrigerant. The partition wall 8 has a through hole 8a. The impeller 2 has a front surface 2a that faces the partition wall 8 with a suction space 5 through which a gas-phase refrigerant is sucked on the opposite side of the bearing 4 from the partition wall 8 in the axial direction of the rotary shaft 1. The impeller 2 is fixed to the rotary shaft 1. The impeller 2 sucks the gas phase refrigerant from the suction space 5 by rotating together with the rotating shaft 1. The partition wall 8 and the rotary shaft 1 form a diaphragm 9 between the surface that forms the through hole 8 a and the outer peripheral surface of the rotary shaft 1. The throttle 9 is filled with a gas phase refrigerant supplied from the discharge space 6.

  The refrigerant used in the turbo machine 100a is, for example, a fluid having a saturated vapor pressure at an ordinary temperature (Japanese Industrial Standard: 20 ° C. ± 15 ° C./JIS Z 8703) and lower than the atmospheric pressure. The refrigerant of the turbo machine 100a is water, for example. A gas phase refrigerant is supplied to the suction space 5. The pressure of the gas phase refrigerant in the suction space 5 is kept lower than the atmospheric pressure. The pressure of the refrigerant in the suction space 5 is, for example, 0.5 to 5 kPaA. When the impeller 2 rotates with the rotary shaft 1, the gas-phase refrigerant sucked from the suction space 5 passes through the impeller 2 and is compressed.

  As shown in FIG. 1, the turbo machine 100a further includes, for example, a discharge path 10, a storage space 15, and a supply path 16. The discharge path 10 is a flow path for discharging the liquid refrigerant stored in the discharge space 6 to the outside of the turbo machine 100a. The storage space 15 is formed on the opposite side of the discharge space 6 when viewed from the bearing 4 in the axial direction of the rotary shaft 1. In the storage space 15, liquid refrigerant supplied between the bearing surface 4 a and the outer peripheral surface of the rotary shaft 1 is stored. The supply path 16 is a flow path for supplying the liquid refrigerant to the storage space 15. The end of the rotating shaft 1 is immersed in the liquid refrigerant stored in the storage space 15. Inside the rotating shaft 1, a first flow path extending in the axial direction of the rotating shaft 1 from the end of the rotating shaft 1, and extending radially outward of the rotating shaft 1 from the first flow path to the outer peripheral surface of the rotating shaft 1. The second flow path is formed. The liquid refrigerant stored in the storage space 15 passes through the first flow path and the second flow path inside the rotation shaft 1 by the centrifugal action caused by the rotation of the rotation shaft 1, and the bearing surface 4 a and the outer peripheral surface of the rotation shaft 1. Supplied during. The supplied liquid refrigerant forms a liquid film between the bearing surface 4a and the outer peripheral surface of the rotating shaft 1, and lubricates and cools the rotating shaft 1 and the bearing 4. Thereafter, a part of the liquid refrigerant is discharged from the bearing 4 to the discharge space 6. The impeller 2 generates heat due to fluid loss due to rotation, and the generated heat is transmitted to the discharge space 6 by the rotating shaft 1. Thereby, a part of the liquid refrigerant discharged into the discharge space 6 evaporates and changes to a gas-phase refrigerant, so that the refrigerant in the discharge space 6 becomes saturated (gas-liquid equilibrium state). For this reason, the discharge space 6 is maintained at the saturated vapor pressure of the liquid refrigerant, and the liquid refrigerant is stored together with the gas-phase refrigerant in the discharge space 6. The liquid level of the liquid refrigerant in the discharge space 6 is lower than that of the restriction 9.

  Since the refrigerant stored in the discharge space 6 receives the heat accompanying the viscous loss in the bearing 4 in addition to the heat generated in the impeller 2, it is at a relatively high temperature. For example, the refrigerant stored in the discharge space 6 has a temperature higher than the temperature of the gas-phase refrigerant in the suction space 5. The gas-phase refrigerant in the suction space 5 is also close to saturation, and the refrigerant pressure (saturated vapor pressure) in the discharge space 6 is higher than the pressure in the suction space 5. In this way, a pressure difference is generated between the discharge space 6 and the suction space 5. Due to this pressure difference, the gas-phase refrigerant generated by the evaporation of the liquid refrigerant in the discharge space 6 flows into the suction space 5 through the throttle 9. Since the heat of the refrigerant in the discharge space 6 is lost as evaporation heat by the flow of the gas-phase refrigerant, if the flow rate of the gas-phase refrigerant flowing into the suction space 5 is large, the temperature of the refrigerant and the saturated vapor pressure in the discharge space 6 Will fall. However, in the turbo machine 100a, the flow rate of the gas-phase refrigerant flowing into the suction space 5 is restricted by the throttle 9, so that the saturated vapor pressure of the refrigerant stored in the discharge space 6 is appropriately maintained. That is, the pressure in the discharge space 6 does not become too low, and an appropriate pressure difference is generated between the discharge space 6 and the suction space 5. The throttle 9 is formed from such a viewpoint. For example, the rotary shaft 1 and the partition wall 8 are arranged so that a pressure difference of 1 kPa to 10 kPa is generated between the discharge space 6 and the suction space 5. Forming. When the size of the average gap between the outer peripheral surface of the rotating shaft 1 and the surface forming the through hole 8a is defined as G, and the diameter of the portion of the rotating shaft 1 inserted into the through hole 8a is defined as D, G / D is, for example, 0.003 to 0.01.

  The liquid refrigerant level in the discharge space 6 is lower than that of the restriction 9, and the restriction 9 is filled with the gas-phase refrigerant. That is, the liquid refrigerant level in the discharge space 6 is lower than the height of the lowest portion of the throttle 9. For this reason, the liquid refrigerant stored in the discharge space 6 is prevented from leaking into the suction space 5. Thereby, it can prevent that a liquid refrigerant collides with the impeller 2 and the impeller 2 is damaged. Further, the throttle 9 generates an appropriate pressure difference between the discharge space 6 and the suction space 5. For this reason, the pressure at the end surface 4e of the bearing 4 in the axial direction of the rotating shaft 1 is appropriately maintained, and cavitation occurs in the liquid film formed by the liquid refrigerant interposed between the outer peripheral surface of the rotating shaft 1 and the bearing surface 4a. Is suppressed. As a result, the wear resistance of the bearing 4 can be improved, and the turbo machine 100a has high durability.

  As shown in FIG. 1, the turbo machine 100 a further includes, for example, a motor 3 that rotates the rotating shaft 1. The motor 3 is attached to the rotating shaft 1 adjacent to the impeller 2 on the side opposite to the partition wall 8 when viewed from the impeller 2 in the axial direction of the rotating shaft 1. The motor 3 includes a rotor 3 a and a stator 3 b, and the rotor 3 a is fixed to the rotating shaft 1. When electric power is supplied to the motor 3, the rotor 3a rotates. At this time, the motor 3 generates heat. The heat generated by the motor 3 is transmitted to the discharge space 6 through the rotating shaft 1. Since the motor 3 is located on the rotary shaft 1 adjacent to the impeller 2, the motor 3 and the impeller 2, which are heat generating components, are arranged relatively close to the discharge space 6. For this reason, the amount of heat transmitted to the discharge space 6 through the rotary shaft 1 is relatively large, and the saturated vapor pressure of the refrigerant stored in the discharge space 6 tends to increase.

  The turbo machine 100a can be changed from various viewpoints. The turbo machine 100a may be changed to a turbo machine 100b illustrated in FIG. 2, for example. The turbo machine 100b has the same configuration as that of the turbo machine 100a unless otherwise described. Components that are the same as or correspond to components of the turbo machine 100a are assigned the same reference numerals, and detailed descriptions thereof are omitted. The description regarding the turbo machine 100a also applies to the turbo machine 100b unless there is a technical contradiction.

  The turbo machine 100 b further includes an annular body 11. The annular body 11 is formed in an annular shape while extending from the outer peripheral surface of the rotating shaft 1 to the radially outer side of the rotating shaft 1, and is disposed adjacent to the partition wall 8 in the discharge space 6. The annular body 11 has, for example, a tapered surface whose diameter decreases toward the partition wall 8 in the axial direction of the rotating shaft 1. For example, the annular body 11 is a member manufactured as a separate member from the rotating shaft 1, and the annular body 11 is fitted and fixed to the rotating shaft 1. The annular body 11 may be formed integrally with the rotary shaft 1.

  When the heating amount of the refrigerant in the discharge space 6 decreases for some reason, the dryness of the saturated refrigerant in the discharge space 6 may decrease, and the liquid level of the refrigerant liquid in the discharge space 6 may increase. If the liquid level of the refrigerant liquid in the discharge space 6 exceeds the height of the lowest part of the throttle 9, a part of the refrigerant liquid may pass through the throttle 9 and leak into the suction space 5. According to the turbo machine 100b, even if the liquid refrigerant level in the discharge space 6 rises and the liquid refrigerant approaches the throttle 9, the centrifugal action generated by the rotation of the annular body 11 together with the rotary shaft 1 causes the liquid refrigerant. Is moved away from the aperture 9. Thereby, it is possible to prevent the liquid refrigerant stored in the discharge space 6 from leaking into the suction space 5. Further, in order to increase the dryness of the discharge space 6, it is not necessary to reduce the pressure loss due to the restriction 9 and to reduce the pressure in the discharge space 6. For this reason, in the vicinity of the end surface 4e of the bearing 4 in contact with the discharge space 6, the subcool of the liquid film formed by the liquid refrigerant interposed between the outer peripheral surface of the rotating shaft 1 and the bearing surface 4a becomes sufficiently large. Occurrence of internal cavitation is likely to be suppressed. As a result, the wear resistance of the bearing 4 can be improved, and the turbo machine 100b has high durability.

  The turbo machine 100a may be changed to a turbo machine 100c illustrated in FIG. 3, for example. The turbo machine 100c has the same configuration as that of the turbo machine 100a unless otherwise specified. Components that are the same as or correspond to components of the turbo machine 100a are assigned the same reference numerals, and detailed descriptions thereof are omitted. The description regarding the turbo machine 100a also applies to the turbo machine 100c as long as there is no technical contradiction.

  In the turbo machine 100 c, the partition wall 8 has a heat insulating structure 12 inside the partition wall 8. The turbo machine 100c includes an annular body 11 as in the turbo machine 100b. In the turbo machine 100c, the annular body 11 may be omitted. The heat insulating structure 12 forms a vacuum space, for example. The heat insulating structure 12 may be formed of a heat insulating material such as glass wool.

  Part of the heat of the refrigerant stored in the discharge space 6 is transmitted to the suction space 5 not only as evaporation heat due to the flow of the gas-phase refrigerant passing through the throttle 9 but also due to heat conduction in the partition wall 8. According to the turbo machine 100c, the heat insulation structure 12 suppresses the temperature of the discharge space 6 and the decrease in the saturated vapor pressure of the refrigerant in the discharge space 6. For this reason, in the vicinity of the end surface 4e of the bearing 4 in contact with the discharge space 6, the subcool of the liquid film formed by the liquid refrigerant interposed between the outer peripheral surface of the rotating shaft 1 and the bearing surface 4a becomes sufficiently large. Occurrence of internal cavitation is likely to be suppressed. Thereby, the abrasion resistance of the bearing 4 can be improved, and the turbo machine 100c has high durability.

  The turbo machine of the present disclosure is useful for a compressor of a refrigeration cycle apparatus that can be used for air-conditioning products such as a turbo refrigerator and a commercial air conditioner.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Impeller 2a Front surface 3 Motor 4 Bearing 4a Bearing surface 4e End surface 5 Suction space 6 Discharge space 8 Partition 8a Through-hole 9 Restriction 11 Annulus 100a, 100b, 100c Turbomachine

Claims (4)

A rotation axis;
A bearing that supports the rotating shaft, and has a bearing surface facing the outer peripheral surface of the rotating shaft in a state where a liquid refrigerant is interposed;
The liquid refrigerant discharged from the bearing faces the end surface of the bearing in the axial direction of the bearing with a discharge space in which the liquid refrigerant is stored together with the gas-phase refrigerant, and has a through hole into which the rotating shaft is inserted. A partition,
An impeller fixed to the rotating shaft, having a front surface facing the partition wall in a state where a suction space for sucking a gas-phase refrigerant is interposed on the opposite side of the bearing as viewed from the partition wall in the axial direction of the rotating shaft. An impeller for sucking the gas-phase refrigerant from the suction space by rotating together with the rotating shaft,
The partition and the rotary shaft form a throttle filled with the gas-phase refrigerant supplied from the discharge space between a surface forming the through hole and an outer peripheral surface of the rotary shaft.
Turbo machine.   2. The motor according to claim 1, further comprising a motor that is attached to the rotating shaft adjacent to the impeller on the side opposite to the partition wall when viewed from the impeller in the axial direction of the rotating shaft and rotates the rotating shaft. Turbomachine.   3. The apparatus according to claim 1, further comprising an annular body that is formed in an annular shape while extending radially outward of the rotating shaft from an outer peripheral surface of the rotating shaft, and is disposed adjacent to the partition wall in the discharge space. The listed turbomachine.   The turbomachine according to claim 1, wherein the partition wall has a heat insulating structure inside the partition wall.

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