JP2018004016A - Bearing structure, rotary machine, and compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing structure which can inhibit deterioration of bearing performance and inhibit leakage of a lubrication oil, and to provide a rotary machine and a compressor.SOLUTION: A bearing structure includes: a side seal 110 formed with an insertion hole 110c; a pad 101 having a bearing surface 101a; a detection member 150 which is inserted into the insertion hole and has a tip inserted into an insertion hole 101e of the pad; and a holding member 201 which is held by the detection member and has a facing surface 201a facing the insertion hole.SELECTED DRAWING: Figure 3

Description

  The present disclosure relates to a bearing structure that supports a rotating shaft, and a rotary machine and a compressor that include the bearing structure.

  In a rotating machine such as a compressor, a bearing that supports a rotating shaft is provided. Since self-excited vibration occurs when the rotating shaft rotates at high speed, a bearing capable of suppressing self-excited vibration is employed particularly in a high-speed rotating machine. As a bearing capable of suppressing self-excited vibration, for example, a tilting pad bearing (tilted pad bearing) shown in Patent Document 1 is known. The tilting pad bearing includes a plurality of pads (inclined pads) divided in the rotation direction of the rotation shaft. Each pad is tiltably held in the casing. In the tilting pad bearing, when the pad is tilted, the amount of gap between the rotating shaft and the rotating shaft becomes variable, and self-excited vibration is suppressed.

  Further, when the rotating machine is operated, the temperature of the bearing rises. An excessive temperature rise of the bearing causes seizure of the rotating shaft and wear of the bearing itself. Therefore, in the tilting pad bearing disclosed in Patent Document 1, a thermocouple sheath is attached to the pad in order to monitor the temperature of the pad.

JP 2014-163467 A

  Like the thermocouple described above, the bearing may be provided with a detection member for measuring the temperature, pressure, and the like in and around the bearing. In order to reduce leakage of lubricating oil supplied to the bearing surface, the bearing may be housed in a casing or the like. In this case, it is necessary to insert the detection member through the insertion hole formed in the casing.

  At this time, if the clearance between the insertion hole and the detection member is reduced, the detection member is restrained and the bearing performance may be deteriorated. For example, in the tilting pad bearing described above, when the movement of the sheath is restricted, the movement of the pad is restricted. As a result, the bearing performance decreases, for example, the temperature of the pad increases or the vibration suppressing effect decreases. On the other hand, when the clearance is increased, the leakage of lubricating oil from the casing increases.

  An object of the present disclosure is to provide a bearing structure, a rotating machine, and a compressor that cover at least a part of the insertion hole and can suppress leakage of lubricating oil through the insertion hole.

  In order to solve the above problems, a bearing structure of the present disclosure includes a housing member in which an insertion portion is formed, a bearing portion provided in the housing member, and the insertion portion, and a part of the bearing structure is located in the housing member. And a holding member having an opposing surface that faces the insertion portion in the insertion direction of the detection member.

  The bearing portion may be a pad that is tiltably held in the housing member, and the detection member may include a contact portion that contacts the pad.

  The housing member may include a side seal that faces the bearing portion in the axial direction of the rotation shaft that is pivotally supported by the bearing portion, and the insertion portion may be formed in the side seal.

  The detection member may be a thermocouple.

  In order to solve the above problems, a bearing structure of the present disclosure is provided in a housing portion into which a rotating shaft is inserted, a bearing portion that is provided in the housing portion and supports the rotating shaft that is inserted into the housing portion, and a housing portion. An insertion portion communicating between the inside and the outside of the storage portion, a seal surface provided in the insertion portion on the inside of the storage portion, a detection portion in the storage portion, and the detection portion, and passing the insertion portion from the detection portion to the outside of the storage portion And a holding member through which the detection member is inserted and can come into contact with the seal surface.

  In order to solve the above-described problem, a rotating machine according to the present disclosure includes a housing member in which an insertion portion is formed, a bearing portion provided in the housing member, and the insertion portion, and a part thereof is positioned in the storage member. And a holding member having an opposing surface that faces the insertion portion in the insertion direction of the detection member.

  In order to solve the above-described problem, a compressor according to the present disclosure includes a housing member in which an insertion portion is formed, a bearing portion provided in the housing member, and the insertion portion. And a holding member having an opposing surface that faces the insertion portion in the insertion direction of the detection member.

  According to the present disclosure, it is possible to cover at least a part of the insertion hole and suppress leakage of the lubricating oil through the insertion hole.

It is a schematic sectional drawing of a compressor. It is the schematic of a tilting pad bearing. It is a figure which expands and shows the surrounding part of the dashed-dotted line in FIG. It is a figure explaining the effect | action of a bearing structure. It is a figure explaining the bearing structure of a modification.

  Hereinafter, embodiments will be described in detail with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiments are merely examples for facilitating understanding, and are not limited unless otherwise specified. In the present specification and the drawings, elements having substantially the same function and configuration are denoted by the same reference numerals, and redundant description is omitted, and elements not directly related are omitted.

  The bearing structure described below can be applied to various machines and devices including rotating machines such as compressors. Here, as an example, a bearing structure applied to a compressor will be described. In the following, the configuration of the compressor will be described first, and then the bearing structure applied to the compressor will be described.

  FIG. 1 is a schematic cross-sectional view of the compressor 1. The compressor 1 includes an input shaft 2 connected to a drive shaft of a motor (not shown). The input shaft 2 is provided with a large-diameter gear 3. When the motor is driven, the input shaft 2 and the large-diameter gear 3 rotate integrally. The compressor 1 includes a gear case 4 in which a gear chamber 4a is formed. The large diameter gear 3 is disposed in the gear chamber 4a. In the gear case 4, two ball bearings 5 are arranged apart from each other in the axial direction of the input shaft 2. The input shaft 2 is rotatably supported by these two ball bearings 5. The large-diameter gear 3 is located between the two ball bearings 5.

  A first rotating shaft 10 is rotatably supported on the gear case 4. The first rotating shaft 10 is parallel to the input shaft 2 and is spaced apart from the input shaft 2 in the radial direction. The first rotation shaft 10 is provided with a first gear 11 having a smaller diameter than the large diameter gear 3. The first gear 11 is engaged with the large-diameter gear 3 in the gear case 4 and rotates integrally with the first rotating shaft 10. Therefore, when the motor is driven, the input shaft 2, the large diameter gear 3, the first gear 11, and the first rotating shaft 10 are integrally rotated.

  One end 10a of the first rotating shaft 10 protrudes on the opposite side of the motor with the gear chamber 4a interposed therebetween. A first impeller 12 is provided at one end 10 a protruding from the side surface 4 b of the gear case 4. A first partition wall 13 is attached to the gear case 4 in the vicinity of the first impeller 12. An annular first scroll passage 14 is formed by the first partition wall 13 on the radially outer side of the first impeller 12. An annular first diffuser 15 is formed by a gap formed between the first partition wall 13 and the side surface 4b. Further, a first intake space 16 is formed in the first partition wall 13 in front of the first impeller 12. The first diffuser 15 communicates with the first intake space 16 via the first impeller 12 on the radially inner side. Further, the outer side of the first diffuser 15 in the radial direction communicates with the first scroll flow path 14.

  The first rotary shaft 10, the first gear 11, the first impeller 12, the first scroll flow path 14, the first diffuser 15, and the first intake space 16 constitute a first stage compression portion A.

  The gear case 4 is rotatably supported by a second rotating shaft 20. The second rotating shaft 20 is parallel to the input shaft 2 and is spaced apart from the input shaft 2 in the radial direction. The second rotating shaft 20 is provided at a position that is 180 ° out of phase with the first rotating shaft 10 around the input shaft 2. The second rotating shaft 20 is provided with a second gear 21 having a smaller diameter than that of the large diameter gear 3. The second gear 21 is engaged with the large-diameter gear 3 in the gear case 4 and rotates integrally with the second rotating shaft 20. Therefore, when the motor is driven, the input shaft 2, the large-diameter gear 3, the second gear 21, and the second rotating shaft 20 are integrally rotated.

  One end 20a of the second rotating shaft 20 protrudes on the opposite side of the motor with the gear chamber 4a interposed therebetween. A second impeller 22 is provided at one end 20 a protruding from the side surface 4 c of the gear case 4. The second impeller 22 is smaller in the radial and axial dimensions than the first impeller 12. A second partition wall 23 is attached to the gear case 4 in the vicinity of the second impeller 22. An annular second scroll passage 24 is formed by the second partition wall 23 on the radially outer side of the second impeller 22. An annular second diffuser 25 is formed by a gap formed between the second partition wall 23 and the side surface 4c.

  The second partition wall 23 is formed with a second intake space 26 in front of the second impeller 22. The second diffuser 25 communicates with the second intake space 26 via the second impeller 22 on the radially inner side. Further, the radially outer side of the second diffuser 25 communicates with the second scroll channel 24. The second scroll channel 24 and the second diffuser 25 have a channel cross-sectional area smaller than that of the first scroll channel 14 and the first diffuser 15, respectively. A plate 27 that closes the second intake space 26 is fixed to the gear case 4.

  The second rotary shaft 20, the second gear 21, the second impeller 22, the second scroll flow path 24, the second diffuser 25, and the second intake space 26 constitute a second stage compression portion B.

  The first scroll passage 14 is connected to the second intake space 26 via a passage (not shown). An intercooler is provided in a passage connecting the first scroll flow path 14 and the second intake space 26. That is, the second stage compression unit B is connected to the first stage compression unit A via the intercooler. In addition, an external pipe is connected to the second scroll flow path 24 via an unshown aftercooler.

  Next, the operation of the compressor 1 having the above configuration will be described. When the input shaft 2 rotates by driving the motor, the first rotating shaft 10 and the second rotating shaft 20 rotate. When the first rotating shaft 10 rotates, the first impeller 12 rotates, and when the second rotating shaft 20 rotates, the second impeller 22 rotates. That is, when the compressor 1 is in operation, the first impeller 12 and the second impeller 22 rotate simultaneously.

  When the first impeller 12 rotates, air is sucked from the first intake space 16. The air sucked from the first intake space 16 is accelerated by the action of centrifugal force in the process of flowing between the blades of the first impeller 12. The increased air is pressurized by the first diffuser 15 and the first scroll flow path 14. Thus, the air pressurized by the first stage compression section A is cooled by the intercooler and then introduced into the second intake space 26 of the second stage compression section B.

  The air introduced into the second intake space 26 is accelerated by the action of centrifugal force in the process of flowing between the blades of the second impeller 22. The increased air is pressurized by the second diffuser 25 and the second scroll passage 24. Thus, the air pressurized by the second stage compression section B is cooled by the aftercooler and then discharged to the external pipe.

  In the compressor 1, the input shaft 2, the first rotating shaft 10, and the second rotating shaft 20 are rotatably supported by the gear case 4. A large-diameter gear 3 is provided on the input shaft 2 on the drive force input side. On the other hand, the first rotating shaft 10 and the second rotating shaft 20 on the output side of the driving force are provided with a first gear 11 and a second gear 21 having a smaller diameter than the large diameter gear 3. Therefore, the first rotating shaft 10 and the second rotating shaft 20 rotate at a higher speed than the input shaft 2. As described above, the first rotary shaft 10 and the second rotary shaft 20 that rotate at high speed may cause self-excited vibration. Therefore, in the compressor 1, the first rotary shaft 10 and the second rotary shaft 20 are pivotally supported by a tilting pad bearing T that is effective for suppressing self-excited vibration.

  FIG. 2 is a schematic view of the tilting pad bearing T. 2A shows a plan view of the tilting pad bearing T, and FIG. 2B shows a cross section taken along the line bb of FIG. The tilting pad bearing T includes a housing 100 (accommodating member, accommodating portion) having a circular planar shape. The housing 100 has a predetermined thickness in the axial direction of the first rotating shaft 10 or the second rotating shaft 20 (hereinafter simply referred to as “rotating shaft”). A through-hole 100a through which the rotation shaft passes is formed at the center of the housing 100. The inner diameter of the through hole 100a is larger than the diameter of the rotating shaft.

  A plurality (here, five) of pads 101 (bearing portions) are provided on the inner peripheral surface of the through hole 100a. The pad 101 has a shape in which an annular member that can be accommodated in the through hole 100a is divided into a plurality of parts in the rotation direction of the rotation shaft. The bearing surface 101a provided on the pad 101 faces the rotating shaft while maintaining a clearance. That is, the rotating shaft is rotatably supported by the bearing surface 101a. The pad 101 is provided with an outer surface 101b that faces the inner peripheral surface of the through hole 100a. The outer surface 101b has a slightly larger curvature than the inner peripheral surface of the through hole 100a. A support groove 101c is formed on the outer surface 101b. The support groove 101c is located in the center of the outer surface 101b in the rotation direction of the rotation shaft and the center of the rotation shaft in the axial direction. However, the position where the support groove 101c is provided is not limited to this, and may be located, for example, shifted from the center in the rotational direction or the axial direction.

  The housing 100 is formed with a plurality (here, five) of retainer holding holes 100b extending in the radial direction of the rotating shaft. The retainer holding hole 100 b penetrates from the through hole 100 a to the outer peripheral surface of the housing 100. In the retainer holding hole 100 b, the opening on the through hole 100 a side faces the support groove 101 c of the pad 101. The retainer holding hole 100b accommodates a retainer pin 102 indicated by cross hatching in FIG. 2B and a biasing member 103 that biases the retainer pin 102 toward the center of the housing 100. The tip 102 a of the retainer pin 102 protrudes from the retainer holding hole 100 b (the inner peripheral surface of the through hole 100 a) by the biasing force of the biasing member 103 and enters the support groove 101 c of the pad 101. Thus, the pad 101 is held in the housing 100 so as to be tiltable with the tip 102a of the retainer pin 102 as a fulcrum.

  Further, as shown in FIG. 2A, a gap is held between the pads 101 adjacent in the rotation direction. The housing 100 is formed with a plurality (here, five) of oil inlet holes 100 c that open in the gaps between the pads 101. The oil inlet hole 100c extends in the radial direction from the opening on the through hole 100a side. A lubricating oil supply source is connected to the oil inlet hole 100c. Lubricating oil is supplied to the bearing surface 101a of the pad 101 from the outside of the housing 100 through the oil inlet hole 100c.

  Further, as shown in FIG. 2B, on the both sides in the axial direction of the rotating shaft of the housing 100, fixing surfaces 100d extending radially outward from the through holes 100a are respectively provided. Further, a side surface 100e extending to the outer peripheral surface of the housing 100 is provided on the outer side in the radial direction from the fixed surface 100d. A step portion 100f extending in the axial direction of the rotating shaft is formed between the fixed surface 100d and the side surface 100e. The fixed surface 100d is positioned on the inner side in the axial direction of the housing 100 from the side surface 100e by the height of the stepped portion 100f.

  The housing 100 is provided with a side seal 110 (accommodating member) so as to come into surface contact with the fixed surface 100d. The side seal 110 is fixed to the fixing surface 100 d of the housing 100 with screws 111. A plurality (six in this case) of screws 111 are provided in the circumferential direction. The side seal 110 is an annular plate member and has a thickness comparable to the height of the stepped portion 100f. Further, the side seal 110 is formed with a shaft hole 110a through which the rotation shaft is inserted. The inner peripheral surface of the shaft hole 110a is substantially flush with the bearing surface 101a of the pad 101, or is slightly shifted in the radial direction from the bearing surface 101a.

  Therefore, the inner diameter of the shaft hole 110 a is smaller than the inner diameter of the through hole 100 a of the housing 100. Here, a portion of the side seal 110 that protrudes radially inward from the through hole 100a of the housing 100 is referred to as a protruding portion 110b. The protrusion 110b faces the side surface 101d of the pad 101 in the axial direction of the rotation axis. At this time, a slight gap is provided between the protruding portion 110b and the side surface 101d so as not to hinder the tilting operation of the pad 101. As described above, the pad 101 is held in the housing 100 by the side seal 110. Further, the side seal 110 has a function of suppressing leakage of the lubricating oil supplied to the bearing surface 101a of the pad 101 to the outside.

  According to the tilting pad bearing T described above, when the pad 101 is tilted, the amount of the gap with the rotating shaft becomes variable, and self-excited vibration is suppressed. However, when the compressor 1 is operated, the temperature of the tilting pad bearing T, more strictly, the pad 101 is increased. An excessive temperature rise of the pad 101 causes seizure of the rotating shaft and wear of the tilting pad bearing T. Therefore, the tilting pad bearing T is provided with a detection member 150 as shown in FIG. 2B in order to monitor the temperature. Here, a thermocouple is provided as the detection member 150.

  As shown in FIG. 1, two tilting pad bearings T are provided on each of the first rotating shaft 10 and the second rotating shaft 20. The detection member 150 may be provided for each tilting pad bearing T. Here, one detection member 150 is provided on the first rotation shaft 10 and one detection member 150 is provided on the second rotation shaft 20. Further, the detection member 150 is provided on one of the plurality of pads 101 in one tilting pad bearing T. Below, the bearing structure 200 provided with the tilting pad bearing T with which the detection member 150 is provided is demonstrated.

  FIG. 3 is an enlarged view of the encircled portion of the alternate long and short dash line in FIG. In this bearing structure 200, an insertion hole 101 e is formed in the side surface 101 d of the pad 101. The insertion hole 101e is provided on the bearing surface 101a side of the side surface 101d of the pad 101. A gap is provided between the protrusion 110 b of the side seal 110 and the side surface 101 d of the pad 101. The protruding portion 110b is formed with an insertion hole 110c (insertion portion) that faces the insertion hole 101e. The insertion hole 110c has a larger diameter than the insertion hole 101e.

  The detection member 150 made of a thermocouple includes a sheath 150a. The sheath 150a is inserted into the insertion hole 110c of the side seal 110. Further, a contact portion 150b (detection portion) to be inserted into the insertion hole 101e is provided at the distal end of the sheath 150a. The sheath 150a is attached to the pad 101 by inserting the contact portion 150b into the insertion hole 101e. That is, the detection member 150 is attached to the pad 101. The detection member 150 is fixed to the gear case 4 in a state where the distal end of the sheath 150a is pressed in the insertion direction into the insertion hole 101e.

  Here, the inner diameter of the insertion hole 110c is formed larger than the diameter of the sheath 150a. Accordingly, a gap is formed between the sheath 150a and the insertion hole 110c. Although the sheath 150a operates, the inner diameter of the insertion hole 110c is dimensioned so that it does not come into contact even when the sheath 150a is operated to the maximum.

  Here, the lubricating oil is supplied to the bearing surface 101a of the pad 101 from the oil inlet hole 100c. When the inner diameter of the insertion hole 110c is increased, the leakage of the lubricating oil from the tilting pad bearing T and further from the gear case 4 increases.

  Therefore, in the bearing structure 200, the holding member 201 is provided inside the side seal 110. In other words, the holding member 201 is provided in a housing member including the housing 100 and the side seal 110. The holding member 201 is a thin plate-like member having a thickness smaller than that of the side seal 110. In addition, the holding member 201 includes a facing surface 201a that faces the protruding portion 110b. That is, the holding member 201 can abut on a seal surface provided on the outer periphery of the insertion hole 110c. The facing surface 201a is larger than the opening area of the insertion hole 110c. The planar shape of the holding member 201 is not particularly limited, and may be circular or rectangular. However, it is desirable that the holding member 201 has such a dimension that the opposing surface 201a completely covers the insertion hole 110c even when the pad 101 (detection member 150) is operated to the maximum. That is, it is desirable that the holding member 201 has a spread that is greater than or equal to the difference between the radius of the insertion hole 110c and the radius of the sheath 150a, with the inserted sheath 150a as the center. However, even when the insertion hole 110c is not completely covered and only a part is covered, there is an effect of suppressing leakage of the lubricating oil.

  The holding member 201 is held by the detection member 150 in the housing member, that is, in the gap between the pad 101 and the side seal 110. More specifically, the holding member 201 has a holding hole 201b. The holding member 201 is held by the detection member 150 when the detection member 150 (sheath 150a) is inserted through the holding hole 201b. The inner diameter of the holding hole 201b is substantially equal to the diameter of the sheath 150a. Therefore, pressure input does not act so much between the holding hole 201b and the sheath 150a, and almost no gap is interposed. That is, the holding member 201 is movably inserted into the detection member 150.

  Then, the internal pressure of the lubricating oil in the tilting pad bearing T acts on the holding member 201. The holding member 201 is pressed against the side seal 110 by the internal pressure. As a result, the facing surface 201a of the holding member 201 comes into surface contact with the protruding portion 110b of the side seal 110 and comes into contact with the outer peripheral sealing surface of the insertion hole 110c.

  Thus, according to the bearing structure 200, the inner diameter of the insertion hole 110c is formed larger than the diameter of the sheath 150a. Therefore, the tilting operation of the pad 101 is not restrained. Further, since the insertion hole 110c is blocked by the holding member 201, leakage of the lubricating oil to the outside can be suppressed.

  FIG. 4 is a diagram for explaining the operation of the bearing structure 200. The pad 101 tilts in the direction indicated by the double arrow in the figure with the tip 102a of the retainer pin 102 as a fulcrum. Therefore, in the pad 101, the operation range is narrow on the center side of the rotation direction of the rotation shaft (indicated by the arrow in the figure), and the operation range becomes wider as the distance from the center side increases. Further, it is known that the bearing surface 101a of the pad 101 has a higher temperature on the front side in the rotation direction of the rotation shaft than on the rear side in the rotation direction. Therefore, in order to appropriately monitor the temperature of the tilting pad bearing T, it is desirable to provide the detection member 150 at the point a in FIG.

  However, in the conventional bearing structure, the inner diameter of the insertion hole 110c is formed small in order to prevent leakage of the lubricating oil. Therefore, in the conventional bearing structure, the insertion hole 110 c interferes with the detection member 150. Therefore, in the conventional bearing structure, as shown by a point b in FIG. 4, it is common to provide the detection member 150 on the center side in the rotation direction of the rotation shaft in the bearing surface 101a. That is, in the conventional bearing structure, since the position where the detection member 150 is provided is restricted, it is difficult to monitor the temperature appropriately.

  On the other hand, according to the bearing structure 200 described above, the insertion hole 110 c does not interfere with the detection member 150. Therefore, the position where the detection member 150 is provided is not restricted. Therefore, the detection member 150 can be provided on the front side in the rotation direction of the rotation shaft, and the temperature monitoring accuracy can be improved as compared with the conventional case.

  FIG. 5 is a diagram for explaining a bearing structure 300 according to a modification. In the bearing structure 200 described above, only one detection member 150 is provided on the pad 101. However, a plurality of detection members 150 may be provided on one pad 101. For example, in the bearing structure 300, it is assumed that three insertion holes 101e (not shown in FIG. 5) into which the detection member 150 is inserted are formed on the side surface 101d of the pad 101 so as to be spaced apart in the circumferential direction. In this case, the side seal 310 is formed with an insertion hole 310c (insertion portion) extending in the circumferential direction. The insertion hole 310 c faces three insertion holes 101 e formed in the pad 101. The bearing structure 300 includes a holding member 301 having a facing surface 301a facing the insertion hole 310c. The holding member 301 has three holding holes 301b through which the detection member 150 is inserted. As described above, according to the bearing structure 300, even if a plurality of detection members 150 are provided, it is possible to achieve the same operational effects as the above-described bearing structure 200.

  As mentioned above, although embodiment of this indication was described referring an accompanying drawing, it cannot be overemphasized that this indication is not limited to this embodiment. It will be apparent to those skilled in the art that various changes and modifications can be made in the scope described in the claims, and these are naturally within the technical scope of the present disclosure. Is done.

  In the above embodiment, the insertion hole 110 c is formed in the side seal 110 fixed to the housing 100. However, the insertion hole 110 c may be formed in the housing 100. Moreover, in the said embodiment, the penetration hole 110c is provided as an insertion part by which the detection member 150 is penetrated. However, the insertion portion only needs to be inserted through the detection member 150, and may be constituted by a groove or a notch, for example.

  Moreover, in the said embodiment, the sealing surface is provided in the outer periphery of the insertion hole 110c. However, for example, if the insertion hole 110c is a tapered shape that expands toward the inside of the housing 100, a sealing surface can be formed on the inner periphery of the insertion hole 110c. In this case, the holding member 201 has a smaller area than the opening of the insertion hole 110 c inside the housing 100. Alternatively, if the portion of the holding member 201 facing the insertion hole 110c is reduced toward the insertion hole 110c, the periphery of the opening of the insertion hole 110c can also be a sealing surface.

  In the above embodiment, the bearing included in the bearing structure 200 is configured by the tilting pad bearing T. However, the bearing included in the bearing structure is not limited to the tilting pad bearing T. For example, a so-called semi-floating bearing or ball bearing in which a bearing portion having a bearing surface does not operate may be used. Furthermore, in a bearing structure including a bearing portion and an oil film damper as a bearing constituent member, the detection member 150 can be attached to the oil film damper. Generally, vibration is generated in a bearing component including a bearing portion by rotation of a rotary shaft. When vibration occurs, if the detection member 150 is restrained by the insertion portion, the bearing performance may be deteriorated. Therefore, the insertion part may be enlarged. Even in this case, it is possible to suppress leakage of the lubricating oil by adopting the above-described bearing structure.

  Moreover, in the said embodiment, the detection member 150 is attached to the axial direction of the rotating shaft with respect to the bearing part. However, the detection member 150 may be attached to the bearing portion in the radial direction of the rotation shaft.

  In any case, the bearing structure includes a housing member in which an insertion portion is formed, a bearing portion provided in the housing member, a detection member that is inserted through the insertion portion and is partially located in the housing member, and a housing. A holding member that is held by the detection member within the member and has a facing surface that faces the insertion portion in the insertion direction of the detection member may be provided.

  In the above embodiment, the detection member 150 is a thermocouple. However, the detection member is not limited to a thermocouple, and may be a member that detects pressure, displacement, or the like in the housing member. In any case, the detection members widely include those that output the state in the housing member as a signal to the outside.

  Further, in the above-described embodiment, the case has been described in which the opposing surface 201a of the holding member 201 contacts the seal surface on the outer periphery of the insertion hole 110c due to the internal pressure of the lubricating oil. However, the holding member 201 can suppress leakage of the lubricating oil due to resistance without completely contacting the seal surface. However, when the holding member 201 abuts on the seal surface with the internal pressure, leakage of the lubricating oil can be more effectively suppressed.

  In the above embodiment, the case where the bearing structure 200 is applied to the compressor 1 has been described. However, the bearing structure 200 is not limited to the compressor, and can be applied to any rotating machine including a rotating shaft such as a speed increaser and a speed reducer.

  The present disclosure can be used for a bearing structure that supports a rotating shaft, a rotating machine including the bearing structure, and a compressor.

1 Compressor 10 First Rotating Shaft (Rotating Shaft)
20 Second rotation axis (rotation axis)
100 Housing (accommodating member, accommodating part)
101 Pad (bearing part)
110 Side seal (accommodating member, accommodating part)
110c Insertion hole (insertion part)
150 detection member 150b contact part (detection part)
200 Bearing structure 201 Holding member 201a facing surface 300 Bearing structure 301 Holding member 301a facing surface 310 Side seal 310c Insertion hole (insertion part)

Claims (7)

A housing member formed with an insertion portion;
A bearing provided in the housing member;
A detection member that is inserted through the insertion portion and a part of which is located in the housing member;
A holding member having an opposing surface opposite to the insertion portion in the insertion direction of the detection member;
Bearing structure. The bearing is a pad that is tiltably held in the housing member,
The bearing structure according to claim 1, wherein the detection member includes a contact portion that contacts the pad. The housing member includes a side seal opposed to the bearing portion in the axial direction of a rotating shaft pivotally supported by the bearing portion,
The bearing structure according to claim 1, wherein the insertion portion is formed in the side seal.   The bearing structure according to claim 1, wherein the detection member is a thermocouple. A receiving portion into which the rotating shaft is inserted;
A bearing portion provided in the housing portion and supporting a rotating shaft inserted into the housing portion;
An insertion portion provided in the housing portion and communicating between the inside and the outside of the housing portion;
Inside the housing portion, a sealing surface provided in the insertion portion;
A detection unit in the housing unit;
From the detection part, through the insertion part, the detection member extended to the outside of the storage part,
A bearing structure comprising: a holding member through which the detection member is inserted and capable of coming into contact with the seal surface inside the housing portion.   A rotating machine comprising the bearing structure according to any one of claims 1 to 5.   A compressor provided with the bearing structure according to any one of claims 1 to 5.

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