WO2024038492A1 - Structure d'étanchéité de compresseur de suralimentation et compresseur de suralimentation - Google Patents

Structure d'étanchéité de compresseur de suralimentation et compresseur de suralimentation Download PDF

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Publication number
WO2024038492A1
WO2024038492A1 PCT/JP2022/030894 JP2022030894W WO2024038492A1 WO 2024038492 A1 WO2024038492 A1 WO 2024038492A1 JP 2022030894 W JP2022030894 W JP 2022030894W WO 2024038492 A1 WO2024038492 A1 WO 2024038492A1
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WIPO (PCT)
Prior art keywords
seal
midpoint
supercharger
seal member
wheel
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PCT/JP2022/030894
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English (en)
Japanese (ja)
Inventor
拓弥 江花
裕二 木下
Original Assignee
三菱重工エンジン＆ターボチャージャ株式会社
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Priority to PCT/JP2022/030894 priority Critical patent/WO2024038492A1/fr
Publication of WO2024038492A1 publication Critical patent/WO2024038492A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings

Definitions

  • the present disclosure relates to a seal structure for a supercharger and a supercharger provided with the seal structure for the supercharger.
  • a supercharger includes a rotor (rotating body) including a rotating shaft, a turbine impeller attached to one side of the rotating shaft, and a compressor impeller attached to the other side of the rotating shaft, and a turbine impeller and a compressor on the rotating shaft. It includes a bearing rotatably supported between the rotor and the impeller, and a casing (stationary body) that houses the rotor and the bearing.
  • the bearings of a supercharger support a rotating shaft that rotates at high speed, so they easily become hot, and if lubrication is insufficient, there is a risk of seizure. For this reason, the bearings are lubricated or cooled by supplying lubricating oil to the bearings.
  • a seal ring is installed in a turbocharger to seal between the outer surface of a rotating body such as a rotor and the inner surface of a stationary body such as a casing in order to prevent lubricating oil supplied to the bearing from leaking to the compressor or turbine side.
  • At least one embodiment of the present disclosure provides a seal structure for a supercharger and a supercharger that can suppress the inflow and outflow of fluid through a seal gap formed between a rotating body and a stationary body.
  • the purpose is to provide.
  • a seal structure for a supercharger includes: A seal structure of a supercharger, a rotating member including at least a rotating shaft of the supercharger and a rotating wheel provided on one end side of the rotating shaft; a stationary member that includes at least a housing that accommodates the rotating member; a bearing that rotatably supports the rotating shaft; A seal gap formed between the rotating member and the stationary member, the seal gap communicating between a wheel housing space in which the rotating wheel is housed and a bearing housing space in which the bearing is housed.
  • Each of the plurality of seal members is formed in an arc shape extending along the circumferential direction of the rotating shaft, and has a pair of arc end faces facing each other to form an abutment gap;
  • the plurality of seal members include a first seal member and a second seal member disposed closer to the wheel accommodation space than the first seal member, In the case where the angular position is defined such that the vertically upward direction with respect to the axis of the rotating shaft is 0° and the angle increases toward the rotation direction of the rotating shaft,
  • the first seal member is arranged such that the first midpoint, which is the midpoint of the abutment gap of the first seal member, is located within the range of the angular position from -90° to 90°,
  • the second seal member is configured such that the difference in angular position between the second midpoint, which is the midpoint of the abutment gap of the second seal member, and the first midpoint is within a range of 90° or more and 180° or less. It was arranged so that
  • a supercharger according to at least one embodiment of the present disclosure includes the supercharger seal structure.
  • a seal structure for a supercharger and a supercharger that can suppress the inflow and outflow of fluid through a seal gap formed between a rotating body and a stationary body are provided.
  • FIG. 1 is a schematic cross-sectional view along the axis of a supercharger including a seal structure for a supercharger according to an embodiment.
  • FIG. 1 is a schematic cross-sectional view along the axis of a seal structure of a supercharger according to an embodiment. It is a schematic diagram showing the state where the 1st seal member in the seal structure of the supercharger concerning one embodiment was seen from one side (compressor side) of an axial direction. It is a schematic diagram showing the state where the 2nd seal member in the seal structure of the supercharger concerning one embodiment was seen from one side (compressor side) of an axial direction.
  • FIG. 1 is a schematic cross-sectional view along the axis of a supercharger including a seal structure for a supercharger according to an embodiment.
  • FIG. 1 is a schematic cross-sectional view along the axis of a seal structure of a supercharger according to an embodiment. It is a schematic diagram showing the state where the 1st seal
  • FIG. 1 is a schematic cross-sectional view along the axis of a seal structure of a supercharger according to an embodiment. It is a schematic diagram showing the state where the third seal member in the seal structure of the supercharger concerning one embodiment was seen from one side (compressor side) of an axial direction.
  • FIG. 1 is a schematic cross-sectional view of a supercharger 1 along an axis LA including a seal structure 2 for a supercharger 1 according to an embodiment.
  • the seal structure 2 according to the present disclosure can be installed, for example, in a supercharger (turbocharger) 1 for automobiles, ships, or industries (for example, for land-based power generation).
  • the supercharger 1 is driven by the energy of exhaust gas discharged from an engine (internal combustion engine), not shown, and is configured to compress fluid (for example, air).
  • the supercharger (turbocharger) 1 includes a rotating shaft 11, a compressor wheel 12A connected to one end of the rotating shaft 11, and a turbine connected to the other end of the rotating shaft 11. It includes a wheel 12B, a bearing 13 that rotatably supports the rotating shaft 11, and a housing 14 that supports the bearing 13.
  • the housing 14 accommodates the rotating shaft 11, the compressor wheel 12A, the turbine wheel 12B, and the bearing 13.
  • the rotating shaft 11 is rotatable about the axis LA of the rotating shaft 11 by being supported by a bearing 13 arranged between the compressor wheel 12A and the turbine wheel 12B.
  • the direction in which the axis LA of the rotating shaft 11 extends is defined as the axial direction of the rotating shaft 11 (supercharger 1), and the direction perpendicular to the axis LA is defined as the radial direction of the rotating shaft 11 (supercharger 1).
  • the circumferential direction around the axis LA is defined as the circumferential direction of the rotating shaft 11 (supercharger 1).
  • the side where the compressor wheel 12A is located relative to the turbine wheel 12B is referred to as the compressor side
  • the side where the turbine wheel 12B is located relative to the compressor wheel 12A is referred to as the turbine side. do.
  • the turbine wheel 12B is configured to rotate by the energy of exhaust gas discharged from an engine (not shown) and guided to the turbine wheel 12B. Since the compressor wheel 12A is coaxially connected to the turbine wheel 12B via the rotating shaft 11, it rotates together with the rotating shaft 11 in conjunction with the rotation of the turbine wheel 12B.
  • the supercharger 1 compresses gas (e.g., air) guided to the compressor wheel 12A by rotation of the compressor wheel 12A, increases the density of the gas, and sends the gas to the gas supply destination (e.g., the engine). configured.
  • the compressor wheel 12A is configured to guide air introduced along the axial direction of the supercharger 1 (i.e., the direction in which the axis LA extends) to the outside of the supercharger 1 in the radial direction. It is composed of The turbine wheel 12B is configured to guide exhaust gas introduced from the outside in the radial direction of the supercharger 1 along the axial direction of the supercharger 1.
  • Each of the compressor wheel 12A and the turbine wheel 12B does not include an annular member surrounding the outer periphery of the blade.
  • FIG. 2 and FIG. 5 are schematic cross-sectional views along the axis LA of the seal structure 2 of the supercharger 1 according to one embodiment.
  • the seal structure 2 of the supercharger 1 according to some embodiments is a seal structure that is provided in the supercharger 1 to suppress leakage of lubricating oil in the supercharger 1. As shown in FIG. 1, FIG. 2, and FIG. At least a plurality of seal members 5 provided in a seal gap 21 formed in the seal gap 21 are provided.
  • the rotating member 3 is configured to rotate when the supercharger 1 is driven.
  • the rotating member 3 includes at least a rotating shaft 11 and a rotating wheel 12 provided at one end of the rotating shaft 11.
  • the stationary member 4 is configured to remain stationary (do not rotate) even if the rotating member 3 rotates when the supercharger 1 is driven.
  • Stationary member 4 includes at least a housing 14 .
  • the housing 14 (stationary member 4) accommodates the rotating member 3 and the bearing 13. Inside the housing 14 (stationary member 4), the above-mentioned seal gap 21, a wheel accommodation space 22 in which the rotating wheel 12 is accommodated, and a bearing accommodation space 23 in which the bearing 13 is accommodated are formed.
  • the seal gap 21 is provided between the wheel housing space 22 and the bearing housing space 23 in the axial direction of the rotating shaft 11, and communicates the wheel housing space 22 and the bearing housing space 23.
  • the rotating member 3 has a rotating side outer circumferential surface 31 that defines a seal gap 21.
  • the stationary member 4 has a stationary inner circumferential surface 41 that defines a seal gap 21 .
  • Each of the rotating side outer circumferential surface 31 and the stationary side inner circumferential surface 41 is formed into an annular shape extending along the circumferential direction of the supercharger 1 .
  • the stationary inner circumferential surface 41 is provided on the outer side in the radial direction of the rotating shaft 11 than the rotating outer circumferential surface 31, and faces the rotating outer circumferential surface 31 with the seal gap 21 formed in an annular shape in between.
  • FIG. 3 is a schematic diagram showing the first seal member 5A in the seal structure 2 of the supercharger 1 according to one embodiment, viewed from one side in the axial direction (compressor side).
  • FIG. 4 is a schematic diagram showing the second seal member 5B in the seal structure 2 of the supercharger 1 according to one embodiment, viewed from one side in the axial direction (compressor side).
  • FIG. 6 is a schematic diagram showing a third seal member 5C in the seal structure 2 of the supercharger 1 according to one embodiment, viewed from one side in the axial direction (compressor side). 3, 4, and 6, for reference, a vertical line VL passing through the axis LA and extending in the vertical direction, and a horizontal line HL passing through the axis LA and extending in the horizontal direction are shown.
  • Each of the plurality of seal members (seal rings) 5 is configured to seal between the stationary side inner peripheral surface 41 and the rotating side outer peripheral surface 31.
  • each of the plurality of seal members 5 is formed in an arc shape extending along the circumferential direction of the rotating shaft 11, and is a pair of seal members facing each other to form an abutment gap 51. It has circular arc end faces 52 and 53.
  • each of the plurality of seal members 5 is made of a metal material and has the same shape (the inner diameter, outer diameter, thickness, and abutment gap size are the same).
  • Each of the plurality of seal members 5 is arranged in a compressed state along the circumferential direction between the stationary side inner circumferential surface 41 and the rotating side outer circumferential surface 31 so as to narrow the abutment gap, and the stationary side inner circumference Its outer peripheral surface abuts against the surface 41.
  • a plurality of annular grooves 32 (32A, 32B, 32C) are formed in the rotation-side outer circumferential surface 31, into which portions (inner circumferential portions) of the seal member 5 are respectively fitted.
  • Each of the plurality of annular grooves 32 is formed in an annular shape extending along the circumferential direction of the rotating shaft 11, and is provided at intervals in the axial direction of the rotating shaft 11. A portion (outer peripheral portion) of each of the plurality of seal members 5 fitted into the annular groove 32 protrudes outward in the radial direction of the rotating shaft 11 beyond the rotation-side outer peripheral surface 31 .
  • each of the plurality of seal members 5 is brought into contact with the outer circumferential surface 31 of the rotating side without forming the plurality of annular grooves 32 on the outer circumferential surface 31 of the rotating side. It may be .
  • a plurality of annular grooves are formed on the stationary side inner circumferential surface 41 at intervals in the axial direction of the rotating shaft 11, and a plurality of seal members are formed in each of the plurality of annular grooves. The outer periphery of each of the parts 5 may be fitted.
  • the supercharger 1 is configured such that lubricating oil flows into the bearing 13 and a space in which the bearing 13 is accommodated (bearing accommodation space 23).
  • the housing 14 includes a lubricating oil inlet 24 for introducing lubricating oil into its interior, and a lubricating oil supply path 25 for guiding lubricating oil from the lubricating oil inlet 24 to the bearing 13 . and a lubricating oil discharge port 26 for discharging lubricating oil to the outside of the housing 14.
  • the lubricating oil supply path 25 is a flow path defined by the inner wall surface of the housing 14 that communicates the lubricating oil inlet 24 with the bearing housing space 23 .
  • the lubricating oil discharge port 26 is provided below the bearing housing space 23 and communicates with the lower part of the bearing housing space 23 .
  • the lubricating oil introduced into the housing 14 through the lubricating oil inlet 24 is guided to the bearing 13 through the lubricating oil supply path 25. Most of the lubricating oil guided to the bearing 13 flows downward in the bearing housing space 23 and is discharged to the outside of the housing 14 via the lubricating oil outlet 26 . A portion of the lubricating oil guided to the bearing 13 may flow into the seal gap 21.
  • the seal structure 2 of the supercharger 1 includes the above-mentioned rotating member 3, the above-mentioned stationary member 4, the above-mentioned bearing 13, and a plurality of seal members provided in the above-mentioned seal gap 21. 5.
  • the plurality of seal members 5 include a first seal member 5A and a second seal member 5B disposed closer to the wheel accommodation space 22 than the first seal member 5A.
  • the plurality of annular grooves 32 include a first annular groove 32A into which the inner circumference of the first seal member 5A is fitted, and a second annular groove into which the inner circumference of the second seal member 5B is fitted. Including groove portion 32B.
  • the second annular groove 32B is formed closer to the wheel accommodation space 22 than the first annular groove 32A.
  • the angular position ⁇ is defined such that the vertically upward direction with respect to the axis LA of the rotating shaft 11 is 0°, and the angle increases toward the rotation direction of the rotating shaft 11. do.
  • the angular range in which the abutment gap 51 is formed is preferably 10° or less.
  • the midpoint of the abutment gap 51A (51) formed between the pair of arcuate end surfaces 52A, 53A (52, 53) of the first seal member 5A is defined as a first midpoint MP1.
  • the first seal member 5A is arranged such that the first midpoint MP1 is located within the range of the angular position ⁇ ( ⁇ 1) from ⁇ 90° to 90°. In other words, the first seal member 5A is arranged such that the first midpoint MP1 is higher than the horizontal line HL.
  • the midpoint (intermediate position) between the radial center positions of each of the pair of arcuate end surfaces 52 and 53 is abutment. It is set as the midpoint of the gap.
  • the abutment gap 51 of the seal member 5 is preferably provided above in the vertical direction in order to suppress leakage of lubricating oil through the abutment gap 51.
  • the first midpoint MP1 is located within a range where the angular position ⁇ ( ⁇ 1) is -60° or more and 60° or less, and the angular position ⁇ ( ⁇ 1) is -30° or more and 30° or less. It is more preferable that the first midpoint MP1 is located within the following range.
  • the midpoint of the abutment gap 51B (51) formed between the pair of arcuate end surfaces 52B, 53B (52, 53) of the second seal member 5B is defined as a second midpoint MP2.
  • the second seal member 5B is arranged such that the difference ⁇ in the angular position ⁇ between the second midpoint MP2 and the first midpoint MP1 is within the range of 90° or more and 180° or less.
  • the difference ⁇ is the difference between the angular position ⁇ 1 of the first midpoint MP1 and the angular position ⁇ 2 of the second midpoint MP2.
  • the difference ⁇ is a first imaginary straight line extending from the axis LA and passing through the first midpoint MP1 when the seal members 5 (5A, 5B) are viewed from one side in the axial direction of the rotating shaft 11. It means the smaller angle between the angle L1 (see FIG. 3) and the second virtual straight line L2 extending from the axis LA and passing through the second midpoint MP2.
  • the difference ⁇ is preferably in the range of 120° or more and 180° or less, and more preferably the difference ⁇ is in the range of 150° or more and 180° or less.
  • the first sealing member 5A is arranged such that the first midpoint MP1 is located within the range of -90° or more and 90° or less at the angular position ⁇ ( ⁇ 1). Leakage of lubricating oil through the abutment gap 51A of the seal member 5A can be suppressed.
  • the second seal member 5B is arranged such that the difference ⁇ in the angular position ⁇ between the second midpoint MP2 and the first midpoint MP1 is within the range of 90° or more and 180° or less. Leakage of lubricating oil through the abutment gap 51B of the second seal member 5B can be suppressed.
  • the seal structure 2 of the supercharger 1 not only prevents fluid (for example, lubricating oil) from flowing out from the bearing accommodation space 23 to the wheel accommodation space 22 via the seal gap 21, but also prevents the sealing. It is also possible to suppress the inflow of fluid (for example, air, exhaust gas, etc.) from the wheel housing space 22 to the bearing housing space 23 via the gap 21.
  • fluid for example, lubricating oil
  • the plurality of seal members 5, as shown in FIG. It includes a third seal member 5C disposed on the 22 side.
  • the plurality of annular grooves 32 include the above-mentioned first annular groove 32A, the above-mentioned second annular groove 32B, and a third annular groove 32C into which the inner circumference of the third seal member 5C is fitted. including.
  • the third annular groove 32C is formed closer to the wheel accommodation space 22 than the second annular groove 32B.
  • the midpoint of the abutment gap 51C (51) formed between the pair of arc end faces 52C, 53C (52, 53) of the third seal member 5C is defined as a third midpoint MP3.
  • the third seal member 5C is arranged such that the difference ⁇ in the angular position ⁇ between the third midpoint MP3 and the second midpoint MP2 is within the range of 90° or more and 180° or less.
  • the difference ⁇ is the difference between the angular position ⁇ 2 of the second midpoint MP2 and the angular position ⁇ 3 of the third midpoint MP3.
  • the difference ⁇ is determined by a second virtual straight line extending from the axis LA and passing through the second midpoint MP2 when the seal members 5 (5B, 5C) are viewed from one side in the axial direction of the rotating shaft 11. It means the smaller angle between the angle L2 (see FIG. 4) and the third virtual straight line L3 extending from the axis LA and passing through the third midpoint MP3.
  • the difference ⁇ is preferably in the range of 120° or more and 180° or less, and more preferably the difference ⁇ is in the range of 150° or more and 180° or less.
  • the third seal member 5C is arranged such that the difference ⁇ in the angular position ⁇ between the third midpoint MP3 and the second midpoint MP2 is within the range of 90° or more and 180° or less. By doing so, leakage of lubricating oil through the abutment gap 51C of the third seal member 5C can be suppressed.
  • the second seal member 5B is arranged such that the second midpoint MP2 is located within a range where the angular position ⁇ ( ⁇ 2) is 90° or more and 270° or less, as shown in FIG. has been done.
  • the third seal member 5C is arranged such that the third midpoint MP3 is located within the range of the angular position ⁇ ( ⁇ 3) from ⁇ 90° to 90°.
  • the second seal member 5B is arranged so that the second midpoint MP2 is below the horizontal line HL
  • the third seal member 5C is arranged so that the third midpoint MP3 is above the horizontal line HL. .
  • the second seal member 5B by providing a vertical difference (height difference) between the abutment gap 51B of the second seal member 5B and the abutment gap 51C of the third seal member 5C, the second seal member 5B
  • the lubricating oil that has passed through the abutment gap 51B becomes difficult to pass through the abutment gap 51C of the third seal member 5C.
  • leakage of lubricating oil via the abutment gap 51C of the third seal member 5C can be suppressed.
  • the second seal member 5B is arranged such that the second midpoint MP2 is below the horizontal line HL, but in some other embodiments, the second midpoint MP2 is It may be located above the horizontal line HL.
  • the third seal member 5C is arranged such that the third midpoint MP3 is equal to or higher than the horizontal line HL, but in some other embodiments, the third midpoint MP3 is It may be located below the horizontal line HL.
  • the plurality of seal members 5 (5A, 5B, 5C) may be arranged such that the first midpoint MP1, the second midpoint MP2, and the third midpoint MP3 are all higher than the horizontal line HL.
  • differences may be provided in the intervals between the abutment gaps 51 of the plurality of seal members 5.
  • the abutment gap 51 of the seal member 5 (5B in the illustrated example) whose midpoint is disposed below the horizontal line HL is set to the abutment gap 51 of the seal member 5 (5A, 5C in the illustrated example) whose midpoint is disposed above the horizontal line HL.
  • the gap may be smaller than the abutment gap 51. In this case, leakage of the lubricating oil through the abutment gap 51 can be suppressed by narrowing the abutment gap 51 located below where the lubricant oil accumulates.
  • the wheel accommodation space 22 described above includes a compressor wheel accommodation space 22A in which a compressor wheel 12A is accommodated.
  • the seal structure 2 (2A) of the supercharger 1 is for suppressing leakage of lubricating oil from the bearing accommodation space 23 to the compressor wheel accommodation space 22A.
  • the rotating wheel 12 of the supercharger seal structure 2A includes the compressor wheel 12A described above.
  • the compressor wheel accommodating space 22A or the seal gap 21A (21) arranged between the compressor wheel accommodating space 22A and the bearing accommodating space 23 is closer to the bearing accommodating space 23 in which the bearing 13 is accommodated. is also provided on the compressor side in the axial direction of the rotating shaft 11.
  • the rotation-side outer circumferential surface 31A (31) may be, for example, the outer circumferential surface of an annular sleeve 15 included in the supercharger 1, as shown in FIG.
  • the sleeve 15 is attached to the rotary shaft 11 between the compressor wheel 12A (rotary wheel 12) and the bearing 13 in the axial direction of the rotary shaft 11 so as to cover the outer periphery of the rotary shaft 11.
  • the rotating member 3 may further include a sleeve 15.
  • the stationary side inner circumferential surface 41A (41) may be an inner wall surface of the housing 14 that faces the outer circumferential surface of the sleeve 15 with the seal gap 21A in between.
  • the rotation-side outer peripheral surface 31 may be the outer peripheral surface of the rotation shaft 11.
  • the seal structure 2 (2A) of the supercharger 1 can suppress leakage of lubricating oil into the compressor wheel housing space 22A via the seal gap 21A. Furthermore, the seal structure 2 (2A) of the supercharger 1 can suppress air, which is the working fluid that operates the compressor wheel 12A, from flowing into the bearing housing space 23 through the seal gap 21A.
  • the wheel accommodation space 22 described above includes a turbine wheel accommodation space 22B in which the turbine wheel 12B is accommodated.
  • the seal structure 2B(2) of the supercharger is for suppressing leakage of lubricating oil from the bearing housing space 23 to the turbine wheel housing space 22B. be.
  • the rotating wheel 12 of the supercharger seal structure 2B includes the turbine wheel 12B described above.
  • the seal gap 21B (21) arranged between the turbine wheel housing space 22B and the turbine wheel housing space 22B and the bearing housing space 23 is closer to the bearing housing space 23 in which the bearing 13 is housed. is also provided on the turbine side in the axial direction of the rotating shaft 11.
  • the rotation side outer circumferential surface 31B (31) may be, for example, the outer circumferential surface of a boss portion protruding from the back surface of the turbine wheel 12B, as shown in FIG.
  • the stationary side inner circumferential surface 41B (41) may be an inner wall surface of the housing 14 that faces the outer circumferential surface of the boss portion of the turbine wheel 12B with the seal gap 21B in between.
  • the seal structure 2B(2) of the supercharger 1 can suppress leakage of lubricating oil into the turbine wheel housing space 22B via the seal gap 21B. Further, the seal structure 2B(2) of the supercharger 1 can suppress the exhaust gas, which is the working fluid that operates the turbine wheel 12B, from flowing into the bearing accommodation space 23 through the seal gap 21B.
  • the supercharger 1 may include both the seal structures 2A and 2B of the supercharger 1. That is, the present disclosure may be applied to each of the plurality of seal members 5 arranged in the seal gap 21A described above and the plurality of seal members 5 arranged in the seal gap 21B described above.
  • the supercharger 1 includes at least one of the seal structures 2A and 2B described above.
  • the seal structure 2 (2A, 2B) of the supercharger 1 can suppress leakage of fluid such as lubricating oil through the seal gap 21.
  • the seal structure 2 (2A, 2B) of the supercharger 1 described above not only prevents lubricating oil from leaking through the seal gap 21, but also prevents lubricant oil from leaking from the wheel housing space 22 to the bearing housing space 23 through the seal gap 21. Leakage of gas (exhaust gas and air) can also be suppressed.
  • expressions expressing shapes such as a square shape or a cylindrical shape do not only mean shapes such as a square shape or a cylindrical shape in a strict geometric sense, but also within the range where the same effect can be obtained. , shall also represent shapes including uneven parts, chamfered parts, etc.
  • the expressions "comprising,””including,” or “having" one component are not exclusive expressions that exclude the presence of other components.
  • the seal structure (2) of the supercharger (1) includes: A seal structure (2) for a supercharger (1), a rotating member (3) including at least a rotating shaft (11) of the supercharger (1) and a rotating wheel (12) provided at one end of the rotating shaft (11); a stationary member (4) comprising at least a housing (14) housing the rotating member (3); a bearing (13) rotatably supporting the rotating shaft (11); A sealing gap (21) formed between the rotating member (3) and the stationary member (4), which is a sealing gap (21) formed between the wheel housing space (22) in which the rotating wheel (12) is accommodated and the bearing (13).
  • Each of the plurality of seal members (5) is formed in an arc shape extending along the circumferential direction of the rotating shaft (11), and has a pair of arc end faces () facing each other to form an abutment gap (51).
  • the plurality of seal members (5) include a first seal member (5A), a second seal member (5B) disposed closer to the wheel accommodation space (22) than the first seal member (5A), including;
  • the angular position ( ⁇ ) is defined such that the vertically upward direction with respect to the axis (LA) of the rotary shaft (11) is 0° and the angle increases toward the rotation direction of the rotary shaft (11)
  • the first seal member (5A) has a first seal member (5A) whose angular position ( ⁇ ) is at the midpoint of the abutment gap (51A) of the first seal member (5A) within a range of ⁇ 90° or more and 90° or less.
  • the second seal member (5B) is located between the second midpoint (MP2), which is the midpoint of the abutment gap (51B) of the second seal member (5B), and the first midpoint (MP1). They were arranged so that the difference ( ⁇ ) in the angular position was within a range of 90° or more and 180° or less.
  • the first sealing member (5A) is arranged such that the first midpoint (MP1) is located within the range of the angular position ( ⁇ ) from ⁇ 90° to 90°. This makes it possible to suppress leakage of lubricating oil through the abutment gap (51A) of the first seal member (5A).
  • the second seal member (5B) has a difference ( ⁇ ) in angular position ( ⁇ ) between the second midpoint (MP2) and the first midpoint (MP1) within a range of 90° or more and 180° or less.
  • the seal structure (2) of the supercharger (1) allows fluid to flow from the bearing accommodation space (23) to the wheel accommodation space (22) via the seal gap (21). Not only the outflow but also the inflow of fluid from the wheel housing space (22) to the bearing housing space (23) via the seal gap (21) can be suppressed.
  • the plurality of seal members (5) further include a third seal member (5C) disposed closer to the wheel accommodation space (22) than the second seal member (5B),
  • the third seal member (5C) is located between the third midpoint (MP3), which is the midpoint of the abutment gap (51C) of the third seal member (5C), and the second midpoint (MP2).
  • the arrangement was such that the difference ( ⁇ ) in the angular position was within a range of 90° or more and 180° or less.
  • the third seal member (5C) has a difference ( ⁇ ) in angular position ( ⁇ ) of 90° between the third midpoint (MP3) and the second midpoint (MP2).
  • the seal structure (2) of the supercharger (1) described in 2) above is arranged such that the second midpoint (MP2) is located within a range of the angular position ( ⁇ ) of 90° or more and 270° or less,
  • the third seal member (5C) was arranged such that the third midpoint (MP3) was located within the range of the angular position ( ⁇ ) from ⁇ 90° to 90°.
  • the wheel housing space (22) includes a compressor wheel housing space (22A) in which a compressor wheel (12A) is housed.
  • the seal structure (2) of the supercharger (1) can suppress leakage of lubricating oil into the compressor wheel housing space (22A) via the seal gap (21). Furthermore, the seal structure (2) of the supercharger (1) can suppress air, which is the working fluid that operates the compressor wheel (12A), from flowing into the bearing housing space (23) through the seal gap (21). .
  • the wheel housing space (22) includes a turbine wheel housing space (22B) in which a turbine wheel (12B) is housed.
  • the seal structure (2) of the supercharger (1) can suppress leakage of lubricating oil into the turbine wheel housing space (22B) via the seal gap (21). Furthermore, the seal structure (2) of the supercharger (1) can suppress the exhaust gas, which is the working fluid that operates the turbine wheel (12B), from flowing into the bearing housing space (23) through the seal gap (21). .
  • a supercharger (1) according to at least one embodiment of the present disclosure The seal structure (2) of the supercharger (1) according to any one of 1) to 5) above is provided.
  • the seal structure (2) of the supercharger (1) can suppress the inflow and outflow of fluid such as lubricating oil through the seal gap (21).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)

Abstract

La structure d'étanchéité de compresseur de suralimentation de l'invention comprend au moins une pluralité d'éléments d'étanchéité disposés sur un espace d'étanchéité formé entre un élément rotatif, qui comprend un arbre rotatif et une roue folle, et un élément fixe, qui comprend un boîtier qui reçoit l'élément rotatif, l'espace d'étanchéité permettant une communication entre un espace de réception de roue dans lequel la roue folle est logée et un espace de réception de palier dans lequel un palier est logé. La pluralité d'éléments d'étanchéité comprend un premier élément d'étanchéité et un second élément d'étanchéité qui est disposé plus près de l'espace de réception de roue que ne l'est le premier élément d'étanchéité. Si une position angulaire est définie de telle sorte que la verticale au-dessus de l'axe de l'arbre rotatif est de 0° et que l'angle augmente le long de la direction de rotation de l'arbre rotatif, le premier élément d'étanchéité est disposé de telle sorte que le point médian d'un espace de butée (premier point médian) est positionné dans la plage de positions angulaires de -90° à 90°, et le second élément d'étanchéité est disposé de telle sorte que la différence de position angulaire entre le point médian d'un espace de butée (second point médian) et le premier point médian est comprise dans la plage de 90° à 180°.
PCT/JP2022/030894 2022-08-15 2022-08-15 Structure d'étanchéité de compresseur de suralimentation et compresseur de suralimentation WO2024038492A1 (fr)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008106823A (ja) * 2006-10-24 2008-05-08 Toyota Motor Corp シール構造
JP2012057507A (ja) * 2010-09-07 2012-03-22 Ihi Corp シール構造及び過給機
WO2015128935A1 (fr) * 2014-02-25 2015-09-03 三菱重工業株式会社 Structure d'étanchéité et compresseur de suralimentation pourvu de ladite structure d'étanchéité
JP2021095983A (ja) * 2019-12-19 2021-06-24 いすゞ自動車株式会社 シール構造
JP2022054670A (ja) * 2020-09-28 2022-04-07 いすゞ自動車株式会社 配管構造

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008106823A (ja) * 2006-10-24 2008-05-08 Toyota Motor Corp シール構造
JP2012057507A (ja) * 2010-09-07 2012-03-22 Ihi Corp シール構造及び過給機
WO2015128935A1 (fr) * 2014-02-25 2015-09-03 三菱重工業株式会社 Structure d'étanchéité et compresseur de suralimentation pourvu de ladite structure d'étanchéité
JP2021095983A (ja) * 2019-12-19 2021-06-24 いすゞ自動車株式会社 シール構造
JP2022054670A (ja) * 2020-09-28 2022-04-07 いすゞ自動車株式会社 配管構造

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