WO2024161750A1 - 過給機 - Google Patents

過給機 Download PDF

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Publication number
WO2024161750A1
WO2024161750A1 PCT/JP2023/040784 JP2023040784W WO2024161750A1 WO 2024161750 A1 WO2024161750 A1 WO 2024161750A1 JP 2023040784 W JP2023040784 W JP 2023040784W WO 2024161750 A1 WO2024161750 A1 WO 2024161750A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
retaining plate
oil
side wall
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2023/040784
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
貴大 田中
朗弘 上田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHI Corp
Original Assignee
IHI Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by IHI Corp filed Critical IHI Corp
Priority to CN202380074692.1A priority Critical patent/CN120092124A/zh
Priority to DE112023004071.0T priority patent/DE112023004071T5/de
Priority to JP2024574276A priority patent/JP7810289B2/ja
Publication of WO2024161750A1 publication Critical patent/WO2024161750A1/ja
Priority to US19/189,575 priority patent/US20250250910A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F01D25/162—Bearing supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/54—Radial bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/30—Arrangement of components
    • F05D2250/36—Arrangement of components in inner-outer relationship, e.g. shaft-bearing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/98—Lubrication

Definitions

  • the turbocharger may include a rolling bearing that supports the shaft.
  • the turbocharger of Patent Document 1 includes a pair of rolling bearings.
  • the outer ring of one rolling bearing is positioned by a side wall of the housing, and the outer ring of the other rolling bearing is positioned by a wall separate from the housing. Oil is supplied to the rolling bearings for lubrication.
  • the objective of this disclosure is to provide a turbocharger that can efficiently guide oil in the discharge direction.
  • a turbocharger includes a housing including a rolling bearing including a shaft, an inner ring attached to the shaft, and an outer ring arranged around the inner ring, a bearing hole that houses the rolling bearing, and a side wall that intersects the bearing hole, and a bearing retaining plate that is attached to the side wall and faces the side of the outer ring, the lower part of the bearing retaining plate including a small radius region, the distance from the central axis of the shaft to the outer edge of the small radius region being shorter than the distance from the central axis to the outer edge of other regions of the bearing retaining plate, the above-mentioned distance of the small radius region being greater than the radius of the bearing hole and less than or equal to the distance from the central axis to the outer edge of the portion of the side wall that faces the small radius region.
  • a portion of the outer edge of the bearing retaining plate may be pressed into the housing, and the small radius area may be formed in an area of the bearing retaining plate that is not pressed into the housing.
  • the small radius region may include a tapered surface in which the radius from the central axis decreases from a first end face facing the side surface of the outer ring to a second end face opposite the first end face.
  • oil can be efficiently guided in the direction of discharge.
  • FIG. 1 is a schematic cross-sectional view showing a turbocharger according to an embodiment.
  • FIG. 2 shows the second side wall and the bearing retaining plate of the bearing housing as viewed axially.
  • FIG. 3 is a schematic enlarged cross-sectional view of a portion A in FIG.
  • FIG. 4 is a schematic plan view showing the bearing retaining plate.
  • FIG. 5 is a schematic enlarged cross-sectional view of part B in FIG.
  • FIG. 1 is a schematic cross-sectional view showing a turbocharger TC according to an embodiment.
  • the turbocharger TC is applied to an engine.
  • the turbocharger TC includes a housing 1, a shaft 7, a turbine impeller 8, and a compressor impeller 9.
  • the shaft 7, turbine impeller 8, and compressor impeller 9 rotate integrally with one another. Therefore, in this disclosure, the axial, radial, and circumferential directions of the shaft 7, turbine impeller 8, and compressor impeller 9 may be referred to simply as the "axial direction,” the “radial direction,” and the “circumferential direction,” respectively, unless otherwise specified. Also, in this disclosure, the central axes of the shaft 7, turbine impeller 8, and compressor impeller 9 may be referred to simply as the "central axis.”
  • the housing 1 includes a bearing housing 2, a turbine housing 3, and a compressor housing 4.
  • One end of the bearing housing 2 in the axial direction is connected to the turbine housing 3 by a fastening mechanism 21a such as a G coupling.
  • the other end of the bearing housing 2 in the axial direction is connected to the compressor housing 4 by a fastening mechanism 21b such as a fastening bolt.
  • the bearing housing 2 includes a bearing hole 22.
  • the bearing hole 22 extends axially within the bearing housing 2.
  • the bearing hole 22 has a cylindrical shape.
  • first side wall 23 of the bearing housing 2 One end of the bearing hole 22 in the axial direction is defined by the first side wall 23 of the bearing housing 2.
  • the first side wall 23 is located between the turbine impeller 8 and the bearing hole 22 in the axial direction.
  • the first side wall 23 is integral with the bearing housing 2.
  • the first side wall 23 may be separate from the bearing housing 2 or may be attached to the bearing housing 2.
  • the other end of the bearing hole 22 in the axial direction is defined by a bearing retaining plate 40.
  • the bearing retaining plate 40 is located between the compressor impeller 9 and the bearing hole 22 in the axial direction.
  • the bearing retaining plate 40 is separate from the bearing housing 2 and is attached to the bearing housing 2.
  • the bearing housing 2 includes a second side wall 24.
  • a seal plate 30 is disposed adjacent to the second side wall 24.
  • a groove 25 is formed in the second side wall 24.
  • the bearing retaining plate 40 is press-fitted into the groove 25.
  • FIG. 2 shows the second side wall 24 and bearing retaining plate 40 of the bearing housing 2 viewed in the axial direction, with the second side wall 24 and bearing retaining plate 40 viewed from the right side in FIG. 1.
  • the second side wall 24 is hatched for better understanding.
  • the second side wall 24 is formed with a groove 25.
  • the groove 25 has an arc shape of greater than 180 degrees when viewed in the axial direction.
  • An oil drain space 26 is formed below the groove 25.
  • the groove 25 and the oil drain space 26 are continuous with each other in the radial direction. Therefore, a portion of the outer edge 42 of the bearing retaining plate 40 is pressed into the groove 25, and the remainder of the outer edge 42 is not pressed into the groove 25 and is exposed to the oil drain space 26.
  • FIG. 3 is a schematic enlarged cross-sectional view of part A in FIG. 1.
  • the groove 25 includes a third side wall 27.
  • the third side wall 27 corresponds to the bottom surface of the groove 25.
  • the third side wall 27 extends in the radial direction.
  • the third side wall 27 intersects with the bearing hole 22. Specifically, the third side wall 27 may be perpendicular to the bearing hole 22.
  • the bearing retaining plate 40 is disposed adjacent to the third side wall 27. For example, the bearing retaining plate 40 contacts the third side wall 27. The bearing retaining plate 40 will be described in more detail below.
  • the bearing hole 22 accommodates a pair of rolling bearings 50, 60.
  • the rolling bearings 50, 60 rotatably support the shaft 7.
  • the pair of rolling bearings 50, 60 are spaced apart from each other in the axial direction.
  • the rolling bearing adjacent to the first side wall 23 may be referred to as the first rolling bearing 50.
  • the rolling bearing adjacent to the bearing retaining plate 40 may be referred to as the second rolling bearing 60.
  • a turbine impeller 8 is provided at a first end (the left end in FIG. 1) of the shaft 7 in the axial direction.
  • the turbine impeller 8 is located outside the bearing hole 22 in the axial direction.
  • the turbine impeller 8 is rotatably accommodated in the turbine housing 3.
  • the turbine impeller 8 rotates integrally with the shaft 7.
  • a compressor impeller 9 is provided at a second axial end of the shaft 7 (the right end in FIG. 1).
  • the compressor impeller 9 is located outside the bearing hole 22 in the axial direction.
  • the compressor impeller 9 is rotatably housed in the compressor housing 4.
  • the compressor impeller 9 rotates integrally with the shaft 7.
  • the compressor housing 4 includes an intake port 10 at the end opposite the bearing housing 2 in the axial direction.
  • the intake port 10 is connected to an air cleaner (not shown).
  • the bearing housing 2 and the compressor housing 4 define a diffuser passage 11 therebetween.
  • the diffuser passage 11 expands in the radial direction.
  • the diffuser passage 11 has a generally annular shape.
  • the diffuser passage 11 communicates with the intake port 10 via the compressor impeller 9.
  • the compressor housing 4 includes a compressor scroll passage 12.
  • the compressor scroll passage 12 is located radially outward from the compressor impeller 9.
  • the compressor scroll passage 12 communicates with the diffuser passage 11.
  • the compressor scroll passage 12 also communicates with an intake port of an engine (not shown).
  • the turbine housing 3 includes a discharge port 13 at the end opposite the bearing housing 2 in the axial direction.
  • the discharge port 13 is connected to an exhaust gas purification device (not shown).
  • the turbine housing 3 includes a flow path 14 and a turbine scroll flow path 15.
  • the turbine scroll flow path 15 is located radially outward from the turbine impeller 8.
  • the flow path 14 is located between the turbine impeller 8 and the turbine scroll flow path 15.
  • the turbine scroll flow path 15 communicates with the flow path 14.
  • the flow path 14 communicates with the discharge port 13 via the turbine impeller 8.
  • the turbine scroll passage 15 communicates with a gas inlet (not shown).
  • the gas inlet receives exhaust gas discharged from an exhaust manifold (not shown) of the engine.
  • the exhaust gas is guided from the gas inlet to the turbine scroll passage 15, and is further guided to the discharge port 13 via the passage 14 and the turbine impeller 8.
  • the exhaust gas rotates the turbine impeller 8 as it passes through the blades of the turbine impeller 8.
  • the rotational force of the turbine impeller 8 is transmitted to the compressor impeller 9 via the shaft 7.
  • the air from the intake port 10 is pressurized as described above. In this way, the pressurized air is guided to the intake port of the engine.
  • the bearing housing 2 includes a main oil passage 71.
  • the main oil passage 71 extends in the axial direction.
  • the main oil passage 71 extends parallel to the bearing hole 22.
  • the main oil passage 71 is located above the bearing hole 22.
  • the bearing hole 22 and the main oil passage 71 open into the third side wall 27. As described above, the bearing retaining plate 40 contacts the third side wall 27. The bearing retaining plate 40 blocks the opening of the main oil passage 71.
  • the bearing housing 2 includes a through hole 72.
  • the through hole 72 extends from the outer wall of the bearing housing 2 to the main oil passage 71.
  • the through hole 72 communicates with the main oil passage 71. Oil is supplied to the main oil passage 71 from an oil pump (not shown) through the through hole 72.
  • the bearing housing 2 includes a first oil passage 73 and a second oil passage 74.
  • the first oil passage 73 and the second oil passage 74 each open to the main oil passage 71.
  • the first oil passage 73 and the second oil passage 74 each open to the bearing hole 22.
  • the first oil passage 73 and the second oil passage 74 each connect the main oil passage 71 and the bearing hole 22.
  • the first oil passage 73 is provided at a position corresponding to the first rolling bearing 50 in the axial direction and opens toward the first rolling bearing 50.
  • the second oil passage 74 is provided at a position corresponding to the second rolling bearing 60 in the axial direction and opens toward the second rolling bearing 60.
  • the bearing housing 2 includes a bottom wall 28.
  • the bottom wall 28 defines a lower portion of the bearing hole 22 in the radial direction.
  • the bottom wall 28 includes an oil drain hole 28a.
  • the oil drain hole 28a penetrates the bottom wall 28 in the vertical direction.
  • the oil drain hole 28a is located between the first oil passage 73 and the second oil passage 74 in the axial direction.
  • the oil drain hole 28a is located between the first rolling bearing 50 and the second rolling bearing 60 in the axial direction.
  • the bearing housing 2 includes an oil outlet 29 below the oil drain hole 28a.
  • the oil outlet 29 directs oil to the outside of the bearing housing 2.
  • the bearing hole 22 accommodates a portion of the shaft 7.
  • the shaft 7 includes a large diameter portion 7a, a medium diameter portion 7b, and a small diameter portion 7c.
  • the medium diameter portion 7b is located between the first side wall 23 and the bearing retaining plate 40.
  • the large diameter portion 7a is located between the first end of the shaft 7 and the medium diameter portion 7b.
  • the small diameter portion 7c is located between the second end of the shaft 7 and the medium diameter portion 7b.
  • the diameter of the medium diameter portion 7b is smaller than the diameter of the large diameter portion 7a.
  • the diameter of the small diameter portion 7c is smaller than the diameter of the medium diameter portion 7b.
  • the shaft 7 includes a first step surface 7d and a second step surface 7e.
  • the first step surface 7d is located between the large diameter portion 7a and the medium diameter portion 7b.
  • the first step surface 7d extends radially from the outer surface of the large diameter portion 7a to the outer surface of the medium diameter portion 7b.
  • the second step surface 7e is located between the medium diameter portion 7b and the small diameter portion 7c.
  • the second step surface 7e extends radially from the outer surface of the medium diameter portion 7b to the outer surface of the small diameter portion 7c.
  • the first rolling bearing 50 includes an inner ring 51, an outer ring 52, multiple rolling elements 53, and a retainer 54.
  • the inner ring 51 is attached to the outer surface of the medium diameter portion 7b of the shaft 7.
  • the inner ring 51 rotates integrally with the shaft 7.
  • the outer ring 52 is disposed radially outward from the inner ring 51.
  • the outer surface of the outer ring 52 faces the inner surface of the bearing hole 22.
  • Multiple rolling elements 53 are disposed between the inner ring 51 and the outer ring 52.
  • the retainer 54 holds the multiple rolling elements 53.
  • the second rolling bearing 60 includes an inner ring 61, an outer ring 62, multiple rolling elements 63, and a retainer 64.
  • the inner ring 61 is attached to the outer surface of the medium diameter portion 7b of the shaft 7.
  • the inner ring 61 rotates integrally with the shaft 7.
  • the outer ring 62 is disposed radially outward from the inner ring 61.
  • the outer surface of the outer ring 62 faces the inner surface of the bearing hole 22.
  • Multiple rolling elements 63 are disposed between the inner ring 61 and the outer ring 62.
  • the retainer 64 holds the multiple rolling elements 63.
  • the side surfaces 51a, 51b and 61a, 61b of the inner ring 51 of the first rolling bearing 50 and the inner ring 61 of the second rolling bearing 60 the side surfaces 51b, 61b that face each other in the axial direction may be referred to as the "inner surface”, and the side surfaces 51a, 61a opposite the inner surfaces 51b, 61b may be referred to as the "outer surface”.
  • the side surfaces 52a, 52b and 62a, 62b of the outer ring 52 of the first rolling bearing 50 and the outer ring 62 of the second rolling bearing 60 may be referred to as the "inner surface”, and the side surfaces 52a, 62a opposite the inner surfaces 52b, 62b may be referred to as the "outer surface”.
  • the outer surface 51a of the inner ring 51 of the first rolling bearing 50 contacts the first step surface 7d of the shaft 7 in the axial direction.
  • the outer surface 52a of the outer ring 52 of the first rolling bearing 50 faces the first side wall 23 of the bearing housing 2 in the axial direction.
  • a spacer 80 is disposed between the inner ring 51 and the inner ring 61 in the medium diameter portion 7b of the shaft 7.
  • the spacer 80 has a generally cylindrical shape.
  • the shaft 7 is inserted into the spacer 80.
  • a spring and a spring support may be provided instead of the spacer 80.
  • the inner surface 51b of the inner ring 51 of the first rolling bearing 50 contacts one end of the spacer 80 in the axial direction.
  • the inner surface 61b of the inner ring 61 of the second rolling bearing 60 contacts the other end of the spacer 80 in the axial direction.
  • An oil-slinger 90 is attached to the small diameter portion 7c of the shaft 7.
  • the oil-slinger 90 scatters oil radially outward.
  • the oil-slinger 90 is positioned radially inward of the bearing retaining plate 40.
  • the oil-slinger 90 and the bearing retaining plate 40 are spaced apart radially.
  • the outer surface 61a of the inner ring 61 of the second rolling bearing 60 contacts the oil thrower member 90 in the axial direction.
  • the outer surface 62a of the outer ring 62 of the second rolling bearing 60 faces the bearing retaining plate 40 in the axial direction.
  • the first rolling bearing 50, the spacer 80, the second rolling bearing 60, and the oil thrower 90 are mounted on the shaft 7 in this order from the second end of the shaft 7 (the right end in FIG. 1).
  • the bearing retainer plate 40 and the seal plate 30 are assembled to the bearing housing 2.
  • the compressor impeller 9 is mounted on the shaft 7. Axial compressive stress is applied to the inner ring 51 of the first rolling bearing 50, the spacer 80, the inner ring 61 of the second rolling bearing 60, the oil thrower 90, and the compressor impeller 9 by the fastening bolt attached to the second end of the shaft 7, thereby fixing these members to the shaft 7.
  • the inner ring 51 of the first rolling bearing 50, the spacer 80, the inner ring 61 of the second rolling bearing 60, the oil thrower 90, and the compressor impeller 9 rotate integrally with the shaft 7.
  • the turbocharger TC does not have a rotation stopper for the outer rings 52, 62.
  • the outer ring 52 When the outer ring 52 is not pressed against the first side wall 23, the outer ring 52 is rotatable in the circumferential direction relative to the bearing housing 2.
  • the outer ring 62 When the outer ring 62 is not pressed against the bearing retaining plate 40, the outer ring 62 is rotatable in the circumferential direction relative to the bearing housing 2.
  • the inner rings 51, 61 rotate integrally with the shaft 7.
  • the rolling elements 53, 63 rotate in conjunction with the rotation of the inner rings 51, 61.
  • the rolling elements 53, 63 move in the circumferential direction.
  • the outer rings 52, 62 rotate in the circumferential direction in conjunction with the rotation and movement of the rolling elements 53, 63, or in conjunction with the flow of oil.
  • the rotational speed of the outer ring 52 is slower than the rotational speed of the inner ring 51.
  • the pair of rolling bearings 50, 60 are face-to-face assembled. Therefore, no spacer is required between the outer ring 52 and the outer ring 62. Therefore, no preload is applied to the outer rings 52 and 62. Therefore, the outer rings 52 and 62 are easy to rotate relative to the bearing housing 2.
  • FIG. 4 is a schematic plan view showing the bearing retaining plate 40, as viewed axially from the left side in FIG. 1.
  • the bearing retaining plate 40 has a generally annular or disc shape.
  • the bearing retaining plate 40 is arranged concentrically with the shaft 7 (not shown in FIG. 4).
  • the bearing retaining plate 40 includes an inner edge 41 and an outer edge 42.
  • the inner edge 41 has a circular shape when viewed axially.
  • the outer edge 42 has a generally circular shape when viewed axially.
  • the lower portion of the outer edge 42 has a non-circular shape (described in more detail below).
  • Figure 5 is a schematic enlarged cross-sectional view of part B in Figure 3.
  • the diameter of the inner edge 41 is smaller than the innermost diameter of the outer ring 62 of the second rolling bearing 60 and is larger than the outer diameter of the oil thrower member 90.
  • the diameter of the outer edge 42 is larger than the inner diameter of the bearing hole 22.
  • the bearing retaining plate 40 includes a first end face 43 and a second end face 44 in the axial direction.
  • the first end face 43 defines the end of the bearing hole 22 in the axial direction.
  • the first end face 43 contacts the third side wall 27 of the bearing housing 2.
  • the oil drain surface 48 (described later) is spaced axially from the third side wall 27.
  • the first end face 43 directly faces the outer surface 62a of the outer ring 62 of the second rolling bearing 60 in the axial direction. In other words, no other members are disposed between the first end face 43 and the outer surface 62a in the axial direction.
  • the second end face 44 is located opposite the first end face 43 in the axial direction.
  • the lower part of the bearing retaining plate 40 includes a small radius region 45.
  • the distance r1 from the central axis to the outer edge 42 in the small radius region 45 is shorter than the distance r2 from the central axis to the outer edge 42 in other regions of the bearing retaining plate 40.
  • the outer edge 42 in the small radius region 45 has a horizontal straight line shape when viewed in the axial direction.
  • the outer edge 42 in the small radius region 45 may have other shapes, such as a curved shape, when viewed in the axial direction.
  • the distance r1 of the small radius region 45 is greater than the radius of the bearing hole 22. Furthermore, the distance r1 is equal to or less than the distance r3 from the central axis to the outer edge of the portion of the third side wall 27 that faces the small radius region 45 in the axial direction. In this embodiment, the distance r1 is equal to the distance r3. In other embodiments, the distance r1 may be less than the distance r3.
  • the groove 25 of the housing 2 has an arc shape. Therefore, a portion of the outer edge 42 of the bearing retaining plate 40 is pressed into the groove 25, and the remainder of the outer edge 42 is not pressed into the groove 25.
  • the small radius region 45 is formed in an area of the bearing retaining plate 40 that is not pressed into the housing 2. In other words, the small radius region 45 is formed in an area of the bearing retaining plate 40 that does not overlap with the groove 25 in the circumferential direction.
  • the small radius region 45 includes a tapered surface 46.
  • the tapered surface 46 is formed on the outer peripheral surface of the bearing retaining plate 40.
  • the tapered surface 46 is inclined with respect to the axial direction.
  • the radius of the tapered surface 46 from the central axis decreases from the first end surface 43 toward the second end surface 44.
  • the tapered surface 46 is a flat surface. In other embodiments, the tapered surface 46 may be a curved surface.
  • the small radius region 45 and tapered surface 46 may be formed by cutting out the lower portion of the annular bearing retaining plate 40.
  • the small radius region 45 and tapered surface 46 are not limited to this and may be formed by other methods.
  • the small radius region 45 and tapered surface 46 may be formed together with other portions of the bearing retaining plate 40.
  • an oil groove 47 and an oil drain surface 48 are formed in the first end face 43.
  • the oil groove 47 is formed continuously with respect to the inner edge 41.
  • the oil groove 47 is formed with a predetermined width in the radial direction from the inner edge 41.
  • the oil groove 47 extends along the circumferential direction.
  • the oil groove 47 is continuous in the entire circumferential direction and has an annular shape. At the lower part, the oil groove 47 is formed integrally with the oil drain surface 48.
  • the oil drain surface 48 is provided in the lower region of the first end face 43. When viewed in the axial direction, the oil drain surface 48 has a sector shape that is concentric with the shaft 7.
  • oil is supplied from an oil pump (not shown) to a main oil passage 71 via a through hole 72. A portion of the oil is supplied to the first rolling bearing 50 via a first oil passage 73, and the remainder of the oil is supplied to the second rolling bearing 60 via a second oil passage 74.
  • the oil supplied to the second rolling bearing 60 is used to lubricate the gap between the inner ring 61 and the rolling elements 63, and between the outer ring 62 and the rolling elements 63.
  • the oil is also used to lubricate the gap between the outer ring 62 and the inner surface of the bearing hole 22.
  • the oil is guided to the oil groove 47 and the oil drain surface 48 from the gap between the outer ring 62 and the bearing retaining plate 40, and the gap between the outer ring 62 and the inner ring 61.
  • a portion of the oil in the oil groove 47 is guided in the circumferential direction by the oil groove 47.
  • the oil is guided from the oil groove 47 to the oil drain surface 48.
  • the oil drain surface 48 further guides the oil downward. The oil falls into the oil drain space 26.
  • the remaining oil in the oil groove 47 is guided through the gap between the bearing retaining plate 40 and the oil thrower member 90 to the second end face 44.
  • the second end face 44 further guides the oil downward.
  • the oil falls into the oil drain space 26.
  • the oil in the oil drain space 26 is collected in the oil outlet 29 (not shown in FIG. 5) and discharged to the outside.
  • the turbocharger TC as described above includes a shaft 7, a second rolling bearing 60 including an inner ring 61 attached to the shaft 7 and an outer ring 62 arranged around the inner ring 61, a bearing housing 2 including a bearing hole 22 that accommodates the second rolling bearing 60 and a third side wall 27 that intersects with the bearing hole 22, and a bearing retaining plate 40 that is attached to the third side wall 27 and directly faces the outer surface 62a of the outer ring 62.
  • the lower part of the bearing retaining plate 40 includes a small radius region 45. The distance r1 from the central axis to the outer edge 42 in the small radius region 45 is shorter than the distance r2 from the central axis to the outer edge 42 in other regions of the bearing retaining plate 40.
  • the distance r1 of the small radius region 45 is greater than the radius of the bearing hole 22 and is equal to or less than the distance r3 from the central axis to the outer edge of the third side wall 27 that faces the small radius region 45.
  • the distance r1 of the small radius region 45 is equal to or less than the distance r3 from the central axis to the outer edge of the third side wall 27, so the bearing retaining plate 40 does not protrude downward from the third side wall 27.
  • a large oil drain space 26 is ensured, and the oil flowing through the second end face 44 can easily pass through the oil drain space 26. Therefore, the oil can be efficiently guided in the discharge direction.
  • the distance r1 of the small radius region 45 is greater than the radius of the bearing hole 22. Therefore, the small radius region 45 can block the gap between the bearing hole 22 and the outer ring 62 from the axial direction while ensuring a large oil discharge space 26. If the small radius region 45 is too short and the gap is not blocked by the small radius region 45, oil will splash from the gap in the axial direction. This oil will interfere with the downward flow of oil flowing through the second end face 44. However, according to the above configuration, the oil splashing from the gap between the bearing hole 22 and the outer ring 62 in the axial direction is received by the bearing retaining plate 40. Therefore, the downward flow of oil flowing through the second end face 44 is not interfered with. As a result, the oil can be guided more efficiently in the discharge direction.
  • the small radius region 45 is positioned vertically downward. Therefore, when assembling the bearing retaining plate 40 to the bearing housing 2, the small radius region 45 can be used as a marker for positioning in the circumferential direction. As a result, no additional marker is required on the bearing retaining plate 40.
  • the turbocharger TC a portion of the outer edge 42 of the bearing retaining plate 40 is pressed into the bearing housing 2, and the small radius region 45 is formed in an area of the bearing retaining plate 40 that is not pressed into the bearing housing 2.
  • the small radius region 45 includes a tapered surface 46 in which the radius from the central axis decreases from a first end face 43 that faces the outer surface 62a of the outer ring 62 to a second end face 44 opposite the first end face 43.
  • the oil guided to the second end face 44 flows along the tapered surface 46.
  • the oil flowing along the tapered surface 46 smoothly merges with the oil flowing along the oil discharge surface 48. Therefore, the oil can be guided in the discharge direction even more efficiently.
  • the bearing retaining plate 40 is press-fitted into the groove 25 of the bearing housing 2.
  • the bearing retaining plate 40 may be fixed to the third side wall 27 of the bearing housing 2 by a bolt or the like.
  • the bearing retaining plate 40 has a tapered surface 46.
  • the tapered surface 46 is not essential.
  • the bearing retaining plate 40 is applied to the second rolling bearing 60 close to the compressor impeller 9. In other embodiments, the bearing retaining plate 40 may be applied to the first rolling bearing 50 close to the turbine impeller 8.
  • the turbocharger TC includes two rolling bearings 50, 60. In other embodiments, the turbocharger TC may include three or more rolling bearings.
  • the outer rings 52, 62 are rotatable relative to the bearing housing 2. In other embodiments, the outer rings 52, 62 may be rotationally fixed relative to the bearing housing 2.
  • the pair of rolling bearings 50, 60 are angular bearings.
  • the rolling bearings may be rolling bearings other than angular bearings (e.g., deep groove ball bearings or self-aligning ball bearings).
  • the pair of rolling bearings 50, 60 are face-to-face assembled. In other embodiments, the pair of rolling bearings 50, 60 may be back-to-back assembled.
  • This disclosure can reduce oil leakage into the intake air and promote the purification of exhaust gases, making it possible to contribute to Goal 13 of the United Nations-led Sustainable Development Goals (SDGs), which states, "Take urgent action to combat climate change and its impacts.”
  • SDGs Sustainable Development Goals

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rolling Contact Bearings (AREA)
  • Supercharger (AREA)
PCT/JP2023/040784 2023-02-03 2023-11-13 過給機 Ceased WO2024161750A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CN202380074692.1A CN120092124A (zh) 2023-02-03 2023-11-13 增压器
DE112023004071.0T DE112023004071T5 (de) 2023-02-03 2023-11-13 Turbolader
JP2024574276A JP7810289B2 (ja) 2023-02-03 2023-11-13 過給機
US19/189,575 US20250250910A1 (en) 2023-02-03 2025-04-25 Turbocharger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2023015246 2023-02-03
JP2023-015246 2023-02-03

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US19/189,575 Continuation US20250250910A1 (en) 2023-02-03 2025-04-25 Turbocharger

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WO2024161750A1 true WO2024161750A1 (ja) 2024-08-08

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US (1) US20250250910A1 (https=)
JP (1) JP7810289B2 (https=)
CN (1) CN120092124A (https=)
DE (1) DE112023004071T5 (https=)
WO (1) WO2024161750A1 (https=)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6043137U (ja) * 1983-09-01 1985-03-27 石川島播磨重工業株式会社 過給機軸受の給油装置
US20170328273A1 (en) * 2016-05-13 2017-11-16 Honeywell International Inc. Turbocharger assembly
JP2022502598A (ja) * 2018-09-24 2022-01-11 エービービー スウィッツァーランド リミテッドABB Switzerland Ltd 軸受アセンブリモジュールを有する排気タービン過給機
WO2022224492A1 (ja) * 2021-04-23 2022-10-27 株式会社Ihi 過給機

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009125452A1 (ja) * 2008-04-08 2009-10-15 株式会社Ihi ターボチャージャ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6043137U (ja) * 1983-09-01 1985-03-27 石川島播磨重工業株式会社 過給機軸受の給油装置
US20170328273A1 (en) * 2016-05-13 2017-11-16 Honeywell International Inc. Turbocharger assembly
JP2022502598A (ja) * 2018-09-24 2022-01-11 エービービー スウィッツァーランド リミテッドABB Switzerland Ltd 軸受アセンブリモジュールを有する排気タービン過給機
WO2022224492A1 (ja) * 2021-04-23 2022-10-27 株式会社Ihi 過給機

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JP7810289B2 (ja) 2026-02-03
US20250250910A1 (en) 2025-08-07
CN120092124A (zh) 2025-06-03
JPWO2024161750A1 (https=) 2024-08-08
DE112023004071T5 (de) 2025-07-31

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