[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

WO2018070311A1 - Bearing device for supercharger - Google Patents

Bearing device for supercharger Download PDF

Info

Publication number
WO2018070311A1
WO2018070311A1 PCT/JP2017/036058 JP2017036058W WO2018070311A1 WO 2018070311 A1 WO2018070311 A1 WO 2018070311A1 JP 2017036058 W JP2017036058 W JP 2017036058W WO 2018070311 A1 WO2018070311 A1 WO 2018070311A1
Authority
WO
WIPO (PCT)
Prior art keywords
axial direction
holder
bearing
outer ring
axial
Prior art date
Application number
PCT/JP2017/036058
Other languages
French (fr)
Japanese (ja)
Inventor
井筒　智善
Original Assignee
Ntn株式会社
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 Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2018070311A1 publication Critical patent/WO2018070311A1/en

Links

Images

Classifications

    • 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
    • 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
    • F02B39/14—Lubrication of pumps; Safety measures therefor
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • 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

Definitions

  • the present invention relates to a bearing device for a supercharger used for an internal combustion engine or the like.
  • an elastic member such as a coil spring is disposed between outer rings of a pair of rolling bearings fitted to a rotating shaft, and a preload is applied to the rolling bearing by the repulsive force of the elastic member.
  • Bearing devices that support an outer ring with an oil film damper are known (for example, Patent Documents 1 to 4).
  • spacers are arranged between the inner rings and the outer rings of a pair of rolling bearings to keep the distance between the bearings constant, while the end surface on the outer side in the axial direction of the outer ring is contacted on the housing side.
  • a bearing device is also known in which the outer ring is restrained in the axial direction by contacting the contact portion.
  • Patent Document 6 discloses a bearing device for a supercharger in which the durability of the bearing is not impaired due to such a disadvantage that the outer ring is displaced.
  • the bearing device for a supercharger disclosed in Patent Document 6 has a structure shown in FIGS.
  • FIG. 7 shows a supercharger 101 in which the bearing device 110 having the structure shown in Patent Document 6 is incorporated.
  • the supercharger 101 includes a turbine rotor 102 provided in an exhaust passage of the internal combustion engine, a compressor impeller 103 provided in an intake passage of the internal combustion engine, and a turbine shaft 104 as a rotary shaft that couples them so as to be integrally rotatable. It is configured as a turbocharger.
  • the turbine rotor 102 and the turbine shaft 104 are integrally formed on the same axis.
  • the turbine shaft 104 is a stepped shaft in which a large diameter portion 104a, an intermediate portion 104b, and a small diameter portion 104c are sequentially provided from the turbine rotor 102 side toward the compressor impeller 103.
  • the intermediate portion 104b is inserted into the bearing housing 105 of the supercharger 101, and the small diameter portion 104c is inserted through the bearing housing 105 into a compressor housing (not shown).
  • the bearing housing 105 has a retainer 105B coupled to one end of the housing body 105A using a fixing means such as a bolt.
  • a pair of rolling bearings 111 and 112 are fitted on the outer periphery of the intermediate portion 104b.
  • the rolling bearings 111 and 112 are ball bearings including inner rings 111a and 112a, outer rings 111b and 112b, and a large number of balls 111c and 112c as rolling elements disposed therebetween. More specifically, the rolling bearings 111 and 112 are angular contact ball bearings that apply a radial load and an axial load in one direction.
  • the inner rings 111 a and 112 a of the rolling bearings 111 and 112 are fitted on the turbine shaft 104.
  • the rolling bearing 111 is loaded with an axial load in the direction toward the turbine rotor 102, and the rolling bearing 112 is mounted in such a direction as to load an axial load in the direction toward the compressor impeller 103.
  • a slinger 113 is provided between the inner ring 111a and the large-diameter portion 104a of the rolling bearing 111, and a sleeve 114 as an inner ring spacer is provided between the inner rings 111a and 112a.
  • the collars 115 and 116 and the compressor impeller 103 are sequentially fitted on the outer periphery of the small diameter portion 104c. From the compressor impeller 103, a male screw portion 104d at the tip of the small diameter portion 104c protrudes.
  • the slinger 113, the inner ring 111a, the sleeve 114, the inner ring 112a, the collars 115 and 116, and the compressor impeller 103 are sandwiched between the large-diameter portion 104a and the nut 117. They are constrained to a fixed position in the axial direction.
  • the compressor impeller 103, the inner ring 111 a, the sleeve 114, and the inner ring 112 a are sandwiched between the step between the large diameter portion 104 a and the intermediate portion 104 b of the turbine shaft 104 and the end surface of the compressor impeller 103. Restrained at a fixed position in the direction. Thereby, the turbine rotor 102, the turbine shaft 104, the slinger 113, the inner ring 111 a, the sleeve 114, the inner ring 112 a, the collars 115 and 116, the compressor impeller 103, and the nut 117 can be integrally rotated around the center line CL of the turbine shaft 104.
  • the rotating body assembly 106 is assembled.
  • the outer rings 111 b and 112 b of the rolling bearings 111 and 112 are fitted into the holder 120.
  • the holder 120 is fitted into the holder accommodating portion 105 a of the housing main body 105 A of the bearing housing 105.
  • the retainer 105 ⁇ / b> B of the bearing housing 105 is attached to the opening end portion (end portion on the compressor impeller 103 side) of the holder housing portion 105 a, so that the holder 120 is a protrusion of the bearing housing 105 with respect to the axial direction of the turbine shaft 104. It is held between 105b and the retainer 105B.
  • Each of the sleeve 114 and the holder 120 is configured as a separate part from the rolling bearings 111 and 112.
  • the holder 120 has a cylindrical case portion 122 as a holding member disposed on the outer periphery of the outer rings 111b and 112b, and an outer ring spacer that protrudes on the inner peripheral side of the case portion 122 and is interposed between the outer rings 111b and 112b.
  • the spacer part 123 is integrated. Both end surfaces 122a and 122b in the axial direction of the case portion 122 are in positions protruding outward in the axial direction from the outer rings 111b and 112b.
  • the outer rings 111b and 112b are fitted to the holder 120 so as to recede inward in the axial direction from the axial end surfaces 122a and 122b of the case portion 122.
  • Outer rings 111b and 112b are abutted against both ends of the spacer portion 123. Accordingly, the outer rings 111b and 112b are positioned in the axial direction, and the axial distance between the outer rings 111b and 112b is kept constant.
  • each of the inner rings 111a and 112a and the outer rings 111b and 112b The displacement in the direction is minimized, and the position is maintained at a position where the preload is not substantially applied.
  • the play in the axial direction of the turbine shaft 4 can be suppressed to a minimum, and the clearances between the turbine rotor 2 and the compressor impeller 3 and their housings can be set small to improve the supercharging performance.
  • the member which restrains outer ring 111b, 112b from those axial direction outer sides is not provided in the axial direction outer side of outer rings 111b, 112b. That is, the outer rings 111b and 112b are fitted to the holder 120 in an unconstrained state outward in the axial direction. Further, an elastic member such as a spring that pushes them in the axial direction and applies a preload is not provided between the outer rings 111b and 112b. By assembling the rolling bearings 111 and 112 without preload, friction loss inside the rolling bearings 111 and 112 can be suppressed.
  • a very small gap 125 is provided between the holder 120 and the bearing housing 105.
  • the gap 125 includes a radial gap 125 a located on the outer peripheral side of the holder 120 and axial gaps 125 b and 125 c located at both axial ends of the holder 120.
  • the radial gap 125 a exists over the entire outer peripheral surface of the holder 120, and the axial gaps 125 b and 125 c exist over the entire end surfaces 122 a and 122 b of the holder 120.
  • the holder 120 in a state where an oil film described later is not formed, can move in the radial direction by an amount corresponding to the radial gap 125a with respect to the bearing housing 105, and corresponds to the axial gaps 125b and 125c. It can move in the axial direction by an amount.
  • an oil supply path (not shown) is formed from its lower surface toward the radial gap 125a.
  • the gap 125 is filled with the lubricating oil, and an oil film is formed between the holder 120 and the bearing housing 105.
  • the oil film, the holder 120 and the bearing housing 105 constitute an oil film damper 108, and the oil film damper 108 supports the outer rings 111b and 112b.
  • the oil film damper 108 By providing the oil film damper 108 in this way, it is possible to efficiently absorb the vibration of the bearing assembly. Therefore, the adaptability of the supercharger 1 with respect to a high-speed rotation region exceeding 100,000 rotations per minute can be improved. Since the gaps 125 a, 125 b, and 125 c exist in the radial direction and the axial direction of the holder 120, the holder 120 can smoothly move in the radial direction and the axial direction with respect to the bearing housing 105. For this reason, the vibration absorption effect by the oil film damper 108 is enhanced.
  • the axial deflection of the bearing assembly is limited when the end surfaces 122a and 122b of the holder 120 are in contact with the protrusion 105b or the retainer 105B of the bearing housing 105. Since the outer rings 111 b and 112 b are retracted inward in the axial direction from both end faces 122 a and 122 b of the holder 120, there is no possibility that the outer rings 111 b and 112 b directly hit the bearing housing 105. Moreover, the holder 120 and the outer rings 111b and 112b are separate parts, and the outer rings 111b and 112b are fitted to the holder 120 in an unconstrained state outward in the axial direction.
  • the outer rings 111b and 112b are displaced only by the axial force transmitted from the inner rings 111a and 112a via the balls 111c and 112c, and an unnatural axial external force does not act on the rolling bearings 111 and 112.
  • the outer periphery of the holder 120 is provided with two annular grooves 130 so as to go around the holder 120.
  • each annular groove 130 is provided with an oil jet hole 131 for supplying lubricating oil to the rolling bearings 111 and 112 side.
  • the oil jet hole 131 is provided so that the center line thereof faces the inner rings 111a and 112a. Thereby, a part of the lubricating oil forming the oil film is supplied from the oil jet hole 131 to the inner rings 111a and 112a (black arrow in FIG. 8). Therefore, compared with the case where the lubricating oil is directly sprayed toward the balls 111c and 112c, the stirring loss of the lubricating oil can be reduced and the supercharging efficiency can be increased.
  • Lubricating oil supplied from the oil jet hole 131 toward the inner rings 111a and 112a is blown off to the outer periphery by centrifugal force, and is discharged from the inner surface side of the outer rings 111b and 112b to the outside in the axial direction of the rolling bearings 111 and 112 ( FIG. 8 black arrow).
  • gaps 125 a, 125 b, and 125 c exist between the outer peripheral surface in the radial direction and the end surface in the axial direction of the holder 120 and the bearing housing 105, respectively.
  • 125a, 125b, 125c is supplied with lubricating oil in order to provide the oil film damper 108, and this lubricating oil is more axial than the two end faces 122a, 122b of the holder 120, as indicated by white arrows in FIG. It is discharged to the outer side portion in the axial direction of the outer rings 111b and 112b retracted inward.
  • a part of the lubricating oil forming the oil film is supplied from the oil jet hole 131 toward the inner ring 111a as shown by the black arrow in FIG. 8, and the supplied lubricating oil is the axis of the rolling bearings 111 and 112. It is discharged outward.
  • the rolling bearings 111 and 112 Since the lubricating oil discharged to the outside in the axial direction of the rolling bearings 111 and 112 and the lubricating oil discharged from the both end faces 122a and 122b of the holder 120 are discharged in directions orthogonal to each other, the rolling bearings 111 and 112 The lubricating oil discharged at the outer portion in the axial direction collides and the lubricating oil stays. As a result, the lubricating oil is not discharged smoothly, and the friction loss of the rolling bearing may increase.
  • the present invention supports the outer ring of the rolling bearing by the oil film damper through the holder with respect to the bearing housing, and the discharge path of the lubricating oil supplied to the oil film damper passes through the rolling bearing in the axial direction.
  • a bearing device having a path discharged to the outside and a path discharged from both end faces of the holder, lubricating oil discharged through the rolling bearing to the outside in the axial direction and lubrication discharged from both end faces of the holder It is intended to prevent the oil from staying in the axially outer portion of the rolling bearing by preventing the oil from colliding with the axially outer portion of the rolling bearing.
  • the present invention is configured as a pair of rolling bearings disposed on a rotating shaft of a supercharger and the pair of rolling bearings as separate parts, and the outer ring of the pair of bearings A holding member to which each is fitted, a bearing housing combined with the holding member so as to form an oil film damper that supports the outer ring, and an axial direction between the inner rings arranged between the inner rings of the pair of bearings An inner ring spacer that maintains a constant distance; and an outer ring spacer that is disposed between the outer rings and that maintains a constant axial distance between the outer rings.
  • the outer ring is in an unconstrained state outward in the axial direction.
  • a turbocharger bearing in which a discharge path for lubricating oil supplied to the film damper includes a path that passes through the rolling bearing and is discharged to the outside in the axial direction, and a path that is discharged from both axial end surfaces of the holding member.
  • a flow direction changing portion for changing the flow direction of the lubricating oil discharged from the path of both end surfaces in the axial direction of the holding member toward the outer side in the axial direction of the outer ring is provided on the outer side in the axial direction of the outer ring. It is characterized by.
  • the flow direction changing portion can be constituted by steps formed integrally on both end surfaces in the axial direction of the holding member.
  • the flow direction changing portion may be formed on a ring member separate from the outer ring, provided on the outer surface in the axial direction of the outer ring.
  • the flow direction changing portion can be constituted by a step formed integrally on the outer side surface in the axial direction of the outer ring.
  • the bearing device of the supercharger according to the present invention has a flow direction changing portion that changes the flow direction of the lubricating oil discharged from the path on both end surfaces in the axial direction of the holding member toward the outside in the axial direction of the outer ring. Therefore, the lubricating oil discharged to the outside in the axial direction through the rolling bearing and the lubricating oil discharged from the both end faces of the holder are parallel to each other on the outer side in the axial direction of the rolling bearing, and do not collide with each other. Further, it is possible to prevent the lubricating oil from staying at the outer side portion in the axial direction of the rolling bearing.
  • FIG. 1 shows a supercharger 1 in which a bearing device 10 according to a first embodiment of the present invention is incorporated.
  • the supercharger 1 includes a turbine rotor 2 provided in an exhaust passage of the internal combustion engine, a compressor impeller 3 provided in an intake passage of the internal combustion engine, and a turbine shaft 4 as a rotary shaft that couples them so as to be integrally rotatable. It is configured as a turbocharger.
  • the turbine rotor 2 and the turbine shaft 4 are integrally formed on the same axis.
  • the turbine shaft 4 is a stepped shaft in which a large diameter portion 4 a, an intermediate portion 4 b, and a small diameter portion 4 c are sequentially provided from the turbine rotor 2 side toward the compressor impeller 3.
  • the intermediate portion 4b is inserted into the bearing housing 5 of the supercharger 1, and the small diameter portion 4c is inserted into the compressor housing (not shown) through the bearing housing 5.
  • a retainer 5 ⁇ / b> B is coupled to one end of the housing body 5 ⁇ / b> A using a fixing means such as a bolt.
  • a pair of rolling bearings 11 and 12 are fitted on the outer periphery of the intermediate portion 4b.
  • the rolling bearings 11 and 12 are ball bearings including inner rings 11a and 12a, outer rings 11b and 12b, and a large number of balls 11c and 12c as rolling elements disposed therebetween. More specifically, the rolling bearings 11 and 12 are angular contact ball bearings that apply a radial load and one axial load.
  • Each of the inner rings 11 a and 12 a of the rolling bearings 11 and 12 is fitted onto the turbine shaft 4.
  • the rolling bearing 11 is loaded with an axial load in the direction toward the turbine rotor 2, and the rolling bearing 12 is mounted in such a direction as to load an axial load in the direction toward the compressor impeller 3.
  • a sleeve 14 as an inner ring spacer is provided between the inner rings 11a and 12a of the rolling bearing 11.
  • the outer surface in the axial direction of the inner ring 11 a of the rolling bearing 11 is in contact with a stepped portion 13 formed between the large diameter portion 4 a and the intermediate portion 4 b of the turbine shaft 4.
  • the outer surface in the axial direction of the inner ring 12 a of the rolling bearing 12 is in contact with the end surface portion 15 of the compressor impeller 3 fitted to the small diameter portion 4 c of the turbine shaft 4.
  • the compressor impeller 3 By fitting the compressor impeller 3 into the small diameter portion 4 c of the turbine shaft 4, the inner ring 11 a, the sleeve 14, and the inner ring 12 a are stepped between the large diameter portion 4 a and the intermediate portion 4 b of the turbine shaft 4 and the compressor impeller 3. Is sandwiched between the end face portions 15 and is constrained to a fixed position in the axial direction.
  • the turbine rotor 2, the turbine shaft 4, the inner ring 11 a, the sleeve 14, the inner ring 12 a, and the compressor impeller 3 are assembled as a rotating body assembly 6 that can rotate integrally around the center line CL of the turbine shaft 4.
  • the outer rings 11b and 12b of the rolling bearings 11 and 12 are fitted into a holder 20 as a holding member.
  • the holder 20 is fitted into the holder accommodating portion 5 a of the housing main body 5 ⁇ / b> A of the bearing housing 5.
  • the retainer 5 ⁇ / b> B of the bearing housing 5 is attached to the opening end portion (end portion on the compressor impeller 3 side) of the holder housing portion 5 a, so that the holder 20 is a protrusion of the bearing housing 5 with respect to the axial direction of the turbine shaft 4. It is held between 5b and the retainer 5B.
  • Each of the sleeve 14 and the holder 20 is configured as a separate part from the rolling bearings 11 and 12.
  • the holder 20 is a cylindrical case portion 22 as a holding member disposed on the outer periphery of the outer rings 11b and 12b, and an outer ring spacer that protrudes on the inner peripheral side of the case portion 22 and is interposed between the outer rings 11b and 12b.
  • the spacer part 23 is integrated.
  • Both end surfaces 22a and 22b in the axial direction of the case portion 22 are in positions protruding outward in the axial direction from the outer rings 11b and 12b.
  • the outer rings 11b and 12b are fitted into the holder 20 so as to recede inward in the axial direction from the axial end faces 22a and 22b of the case portion 22.
  • a flow direction changing portion 40 that changes the oil flow direction toward the outside in the axial direction is formed by a step.
  • Outer rings 11b and 12b are abutted against both ends of the spacer portion 23. Accordingly, the outer rings 11b and 12b are positioned in the axial direction, and the axial distance between the outer rings 11b and 12b is kept constant. Then, the rolling bearings 11 and 12, the sleeve 14 and the holder 20 are assembled with each other, whereby the bearing assembly 7 is formed.
  • each of the inner rings 11a, 12a and the outer rings 11b, 12b has a minimum positional deviation in the axial direction, and the preload Is held in a position that is substantially not provided.
  • the play in the axial direction of the turbine shaft 4 can be suppressed to a minimum, and the clearances between the turbine rotor 2 and the compressor impeller 3 and their housings can be set small to improve the supercharging performance.
  • wheel 11b, 12b from those axial direction outer sides is not provided in the axial direction outer side of outer ring
  • a very small gap 25 is provided between the holder 20 and the bearing housing 5.
  • the gap 25 includes a radial gap 25 a located on the outer peripheral side of the holder 20, and axial gaps 25 b and 25 c located at both axial ends of the holder 20.
  • the radial gap 25 a exists on the outer peripheral surface of the holder 20, and the axial gaps 25 b and 25 c exist on the end faces 22 a and 22 b of the holder 20. That is, in a state where an oil film to be described later is not formed, the holder 20 can move in the radial direction by an amount corresponding to the radial gap 25a with respect to the bearing housing 5, and corresponds to the axial gaps 25b and 25c. It can move in the axial direction by an amount.
  • the bearing housing 5 is provided with an oil supply passage 41 for supplying lubricating oil to the radial gap 25a.
  • an oil film is formed between the holder 20 and the bearing housing 5.
  • the oil film, the holder 20 and the bearing housing 5 constitute an oil film damper 8, and the oil film damper 8 supports the outer rings 11 b and 12 b.
  • the holder 20 can smoothly move in the radial direction and the axial direction with respect to the bearing housing 5. For this reason, the vibration absorption effect by the oil film damper 8 increases.
  • the axial deflection of the bearing assembly 7 is limited when the end surfaces 22a and 22b of the holder 20 are in contact with the protrusion 5b or the retainer 5B of the bearing housing 5. Since the outer rings 11 b and 12 b are retracted inward in the axial direction from both end faces 22 a and 22 b of the holder 20, there is no possibility that the outer rings 11 b and 12 b directly hit the bearing housing 5. Moreover, the holder 20 and the outer rings 11b and 12b are separate parts, and the outer rings 11b and 12b are fitted to the holder 20 in an unconstrained state outward in the axial direction. Therefore, the outer rings 11b and 12b are displaced only by the axial force transmitted from the inner rings 11a and 12a via the balls 11c and 12c, and an unnatural axial external force does not act on the rolling bearings 11 and 12.
  • the holder 20 is provided with two oil supply portions 42.
  • Each oil supply portion 42 is provided with an oil jet hole 43 for supplying lubricating oil to the rolling bearings 11 and 12 side.
  • 2 shows only the oil jet hole 43 on the rolling bearing 11 side, the same oil jet hole 43 is also provided on the rolling bearing 12 side.
  • the oil jet hole 43 is provided so that the center line thereof faces the inner ring 11a. As a result, a part of the lubricating oil forming the oil film is supplied from the oil jet hole 43 to the inner ring 11a and the periphery thereof. Therefore, the stirring loss of the lubricating oil can be reduced and the supercharging efficiency can be increased as compared with the case where the lubricating oil is directly sprayed toward the ball 11c.
  • the heat transmitted from the turbine rotor 2 to the rolling bearing 11 and the sleeve 14 via the turbine shaft 4 is transmitted from the oil jet hole 43. Therefore, the cooling efficiency of the supercharger 1 can be improved.
  • Lubricating oil supplied from the oil jet hole 43 to the inner surface of the inner ring 11a is blown off to the inner surface of the outer ring 11b by centrifugal force and discharged toward the outer side in the axial direction of the outer ring 11b (black arrow in FIG. 2).
  • clearances 25a, 25b, and 25c exist between the outer peripheral surface in the radial direction and the end surface in the axial direction of the holder 20 and the bearing housing 5, and the oil film damper 8 is provided in the clearances 25a, 25b, and 25c.
  • lubricating oil is supplied, and this lubricating oil is discharged
  • the discharge path for the lubricating oil supplied to the oil film damper 8 is a path that passes through the rolling bearings 11, 12 and is discharged to the outside in the axial direction, and both end faces in the axial direction of the holder 20. 22a and 22b, and a route discharged from 22a and 22b.
  • Lubricating oil discharged from the both end faces 22a, 22b of the holder 20 toward the inner diameter side is a flow direction comprising steps provided so as to protrude outward from the inner diameter parts of the axial end faces 22a, 22b of the case section 22.
  • the flow direction is changed outward in the axial direction.
  • the flow direction of the lubricating oil discharged from the axial end faces 22a and 22b of the case portion 22 and the flow direction of the lubricating oil discharged through the rolling bearing 11 are shown by white arrows and black arrows in FIG.
  • the oil is parallel to the outside, and it is possible to prevent the lubricating oil from staying in the outer portion of the rolling bearing 11 in the axial direction.
  • 3 and 4 show the supercharger 1 in which the bearing device 10 according to the second embodiment of the present invention is incorporated.
  • the flow direction changing portion 40 formed of a step formed on the inner diameter portion of the axial end surfaces 22a and 22b of the case portion 22 is the second embodiment.
  • the ring members 44 are provided separately from the outer rings 11b and 12b. Since other configurations are the same as those of the first embodiment, detailed description thereof is omitted.
  • the flow direction changing portion 40 formed of a step formed on the inner diameter portion of the axial end faces 22a and 22b of the case portion 22 is replaced with the second embodiment. Then, the outer rings 11b and 12b are extended to the outside of the axial end faces 22a and 22b of the case portion 22, and a flow direction changing portion 40 having a step is provided in the extended portion. Since other configurations are the same as those of the first embodiment, detailed description thereof is omitted.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)
  • Supercharger (AREA)

Abstract

The present invention addresses the problem of providing a bearing device (10) for a supercharger (1) in which a discharging path for a lubrication oil supplied to an oil film damper (8) has a path in which the lubrication oil passes through rolling bearings (11, 12) and is discharged to the outside in the axial direction, and a path in which the lubrication oil is discharged from both end surfaces of a holder (20), and the lubrication oil passing through the rolling bearings (11, 12) and discharged to the outside in the axial direction, and the lubrication oil discharged from both end surfaces of the holder (20) are prevented from colliding with each other in an outside portion in the axial direction. By providing, outside the outer races (11b, 12b) in the axial direction, a flow direction changing part (40), which changes the flow direction of lubrication oil discharged from the path of both end surfaces of the holder (20) in the axial direction toward the outside of outer races (11b, 12b) in the axial direction, and thus the lubrication oil discharged from both end surfaces of the holder (20) has been prevented from colliding together in the outside portion of the rolling bearings (11, 12) in the axial direction.

Description

過給機の軸受装置Supercharger bearing device
　この発明は、内燃機関等に用いられる過給機の軸受装置に関する。 The present invention relates to a bearing device for a supercharger used for an internal combustion engine or the like.
　過給機の軸受装置として、回転軸に嵌め合わされた一対の転がり軸受の外輪間にコイルばね等の弾性部材を配置し、その弾性部材の反発力で転がり軸受に予圧を与えるとともに、転がり軸受の外輪をオイルフィルムダンパにて支持する軸受装置が知られている（例えば特許文献１～４）。 As a bearing device for a supercharger, an elastic member such as a coil spring is disposed between outer rings of a pair of rolling bearings fitted to a rotating shaft, and a preload is applied to the rolling bearing by the repulsive force of the elastic member. Bearing devices that support an outer ring with an oil film damper are known (for example, Patent Documents 1 to 4).
　これら特許文献１～４のように、外輪間に嵌め合わされた弾性部材にて一対の転がり軸受に予圧を与える軸受装置では、外輪を弾性部材の力で転動体に押し付けることから、その外輪を押し出す方向、つまり軸線方向外側へは外輪を非拘束状態としておくことが必須である。 As in these Patent Documents 1 to 4, in a bearing device that applies a preload to a pair of rolling bearings with an elastic member fitted between outer rings, the outer ring is pushed out against the rolling element by the force of the elastic member, and thus the outer ring is pushed out. It is essential to keep the outer ring in an unconstrained state in the direction, that is, the outside in the axial direction.
　一方、特許文献５のように、一対の転がり軸受の内輪間、及び外輪間にそれぞれスペーサを配置して軸受間の距離を一定に保持しつつ、外輪の軸線方向外側の端面をハウジング側の当接部に当接させて外輪を軸線方向に拘束する軸受装置も知られている。 On the other hand, as in Patent Document 5, spacers are arranged between the inner rings and the outer rings of a pair of rolling bearings to keep the distance between the bearings constant, while the end surface on the outer side in the axial direction of the outer ring is contacted on the housing side. A bearing device is also known in which the outer ring is restrained in the axial direction by contacting the contact portion.
　ところで、回転軸の高速回転化を図るには転がり軸受の摩擦損失を低減させることが望ましいが、予圧を与えれば摩擦損失が大きくなる。一方、毎分１０万回転を超えるような高速回転領域では、転がり軸受をオイルフィルムダンパにて支持することが必要不可欠となる。両者の要求を満たすには、上述した特許文献５のように外輪間にばね等の弾性部材を設けない構成の軸受装置において、転がり軸受の外輪が嵌め合わされる保持部材を軸受ハウジングと別に設け、その保持部材と軸受ハウジングとの隙間にオイルフィルムを形成する構成が一案として考えられる。 By the way, it is desirable to reduce the friction loss of the rolling bearing in order to increase the rotation speed of the rotating shaft. However, if preload is applied, the friction loss increases. On the other hand, in a high-speed rotation region exceeding 100,000 rotations per minute, it is essential to support the rolling bearing with an oil film damper. In order to satisfy both requirements, in the bearing device having a configuration in which no elastic member such as a spring is provided between the outer rings as in Patent Document 5 described above, a holding member to which the outer ring of the rolling bearing is fitted is provided separately from the bearing housing. A configuration in which an oil film is formed in the gap between the holding member and the bearing housing is considered as one proposal.
　しかしながら、特許文献５の装置のように、外輪の軸線方向外側の端面を軸受ハウジングに当接させて外輪を拘束した場合、オイルフィルムダンパの振動吸収作用で外輪が軸線方向に変位したときに、軸受ハウジングから軸受の外輪へと軸線方向の力が入力される。そのため、内輪から転動体を介して外輪に伝わる軸線方向の力と軸受ハウジング側から外輪に加わる力とが競合して軸受に無理な軸線方向の力が作用し、外輪の位置がずれるといった不都合が発生し、軸受の耐久性が損なわれるおそれがある。 However, as in the device of Patent Document 5, when the outer ring is restrained by contacting the axially outer end face of the outer ring to the bearing housing, when the outer ring is displaced in the axial direction by the vibration absorbing action of the oil film damper, An axial force is input from the bearing housing to the outer ring of the bearing. For this reason, the axial force transmitted from the inner ring to the outer ring via the rolling element competes with the force applied to the outer ring from the bearing housing side, so that an unreasonable axial force acts on the bearing and the position of the outer ring is displaced. And the durability of the bearing may be impaired.
　特許文献６には、このような外輪の位置ずれという不都合によって軸受の耐久性が損なわれないようにした過給機の軸受装置が開示されている。 Patent Document 6 discloses a bearing device for a supercharger in which the durability of the bearing is not impaired due to such a disadvantage that the outer ring is displaced.
　この特許文献６に開示された過給機の軸受装置は、図７及び図８に示す構造を備えている。 The bearing device for a supercharger disclosed in Patent Document 6 has a structure shown in FIGS.
　図７は、特許文献６に示す構造の軸受装置１１０が組み込まれた過給機１０１を示している。過給機１０１は、内燃機関の排気通路に設けられるタービンロータ１０２と、内燃機関の吸気通路に設けられるコンプレッサインペラ１０３と、それらを一体回転可能に連結する回転軸としてのタービン軸１０４とを備えたターボチャージャとして構成されている。タービンロータ１０２とタービン軸１０４とは同軸上に一体形成されている。タービン軸１０４には、タービンロータ１０２側からコンプレッサインペラ１０３に向かって、大径部１０４ａ、中間部１０４ｂ及び小径部１０４ｃが順次設けられた段付きシャフトである。 FIG. 7 shows a supercharger 101 in which the bearing device 110 having the structure shown in Patent Document 6 is incorporated. The supercharger 101 includes a turbine rotor 102 provided in an exhaust passage of the internal combustion engine, a compressor impeller 103 provided in an intake passage of the internal combustion engine, and a turbine shaft 104 as a rotary shaft that couples them so as to be integrally rotatable. It is configured as a turbocharger. The turbine rotor 102 and the turbine shaft 104 are integrally formed on the same axis. The turbine shaft 104 is a stepped shaft in which a large diameter portion 104a, an intermediate portion 104b, and a small diameter portion 104c are sequentially provided from the turbine rotor 102 side toward the compressor impeller 103.
　中間部１０４ｂは、過給機１０１の軸受ハウジング１０５内に挿入され、小径部１０４ｃは軸受ハウジング１０５を貫いてコンプレッサハウジング（図示しない）内に挿入されている。 The intermediate portion 104b is inserted into the bearing housing 105 of the supercharger 101, and the small diameter portion 104c is inserted through the bearing housing 105 into a compressor housing (not shown).
　軸受ハウジング１０５は、ハウジング本体１０５Ａの一端に、リテーナ１０５Ｂがボルト等の固定手段を用いて結合されている。中間部１０４ｂの外周には一対の転がり軸受１１１、１１２が嵌め合わされている。転がり軸受１１１、１１２は、内輪１１１ａ、１１２ａと、外輪１１１ｂ、１１２ｂと、それらの間に配置される転動体としての多数のボール１１１ｃ、１１２ｃとを備えた玉軸受である。より具体的には、転がり軸受１１１、１１２は、径方向荷重と一方向の軸線方向荷重とを負荷するアンギュラコンタクト玉軸受である。転がり軸受１１１、１１２の内輪１１１ａ、１１２ａのそれぞれはタービン軸１０４上に嵌め合わされる。転がり軸受１１１はタービンロータ１０２に向かう方向の軸線方向荷重を負荷し、転がり軸受１１２はコンプレッサインペラ１０３に向かう方向の軸線方向荷重を負荷する向きでそれぞれ取り付けられている。 The bearing housing 105 has a retainer 105B coupled to one end of the housing body 105A using a fixing means such as a bolt. A pair of rolling bearings 111 and 112 are fitted on the outer periphery of the intermediate portion 104b. The rolling bearings 111 and 112 are ball bearings including inner rings 111a and 112a, outer rings 111b and 112b, and a large number of balls 111c and 112c as rolling elements disposed therebetween. More specifically, the rolling bearings 111 and 112 are angular contact ball bearings that apply a radial load and an axial load in one direction. The inner rings 111 a and 112 a of the rolling bearings 111 and 112 are fitted on the turbine shaft 104. The rolling bearing 111 is loaded with an axial load in the direction toward the turbine rotor 102, and the rolling bearing 112 is mounted in such a direction as to load an axial load in the direction toward the compressor impeller 103.
　転がり軸受１１１の内輪１１１ａと大径部１０４ａの間にはスリンガ１１３が設けられ、内輪１１１ａ、１１２ａの間には内輪スペーサとしてのスリーブ１１４が設けられている。小径部１０４ｃの外周には、カラー１１５、１１６、コンプレッサインペラ１０３が順次嵌め合わされている。コンプレッサインペラ１０３からは小径部１０４ｃの先端の雄ねじ部１０４ｄが突出する。その雄ねじ部１０４ｄにナット１１７を装着してこれを締め付けることにより、スリンガ１１３、内輪１１１ａ、スリーブ１１４、内輪１１２ａ、カラー１１５、１１６及びコンプレッサインペラ１０３が大径部１０４ａとナット１１７との間に挟み込まれてそれらが軸線方向の定位置に拘束される。 A slinger 113 is provided between the inner ring 111a and the large-diameter portion 104a of the rolling bearing 111, and a sleeve 114 as an inner ring spacer is provided between the inner rings 111a and 112a. The collars 115 and 116 and the compressor impeller 103 are sequentially fitted on the outer periphery of the small diameter portion 104c. From the compressor impeller 103, a male screw portion 104d at the tip of the small diameter portion 104c protrudes. By attaching and tightening the nut 117 to the male threaded portion 104d, the slinger 113, the inner ring 111a, the sleeve 114, the inner ring 112a, the collars 115 and 116, and the compressor impeller 103 are sandwiched between the large-diameter portion 104a and the nut 117. They are constrained to a fixed position in the axial direction.
　コンプレッサインペラ１０３を嵌め合わせることにより、内輪１１１ａ、スリーブ１１４及び内輪１１２ａが、タービン軸１０４の大径部１０４ａと中間部１０４ｂとの間の段差、及びコンプレッサインペラ１０３の端面の間に挟み込まれて軸線方向の定位置に拘束される。これにより、タービンロータ１０２、タービン軸１０４、スリンガ１１３、内輪１１１ａ、スリーブ１１４、内輪１１２ａ、カラー１１５、１１６、コンプレッサインペラ１０３及びナット１１７は、タービン軸１０４の中心線ＣＬの回りに一体回転可能な回転体アッセンブリ１０６として組み立てられる。 By fitting the compressor impeller 103, the inner ring 111 a, the sleeve 114, and the inner ring 112 a are sandwiched between the step between the large diameter portion 104 a and the intermediate portion 104 b of the turbine shaft 104 and the end surface of the compressor impeller 103. Restrained at a fixed position in the direction. Thereby, the turbine rotor 102, the turbine shaft 104, the slinger 113, the inner ring 111 a, the sleeve 114, the inner ring 112 a, the collars 115 and 116, the compressor impeller 103, and the nut 117 can be integrally rotated around the center line CL of the turbine shaft 104. The rotating body assembly 106 is assembled.
　転がり軸受１１１、１１２のそれぞれの外輪１１１ｂ、１１２ｂは、ホルダ１２０に嵌め合わされている。そのホルダ１２０は、軸受ハウジング１０５のハウジング本体１０５Ａのホルダ収容部１０５ａに嵌め合わされている。軸受ハウジング１０５のリテーナ１０５Ｂは、ホルダ収容部１０５ａの開口端部（コンプレッサインペラ１０３側の端部）に取り付けられ、それにより、ホルダ１２０は、タービン軸１０４の軸線方向に関して、軸受ハウジング１０５の突起部１０５ｂとリテーナ１０５Ｂとの間に保持される。なお、スリーブ１１４及びホルダ１２０のそれぞれは転がり軸受１１１、１１２とは別部品として構成されている。 The outer rings 111 b and 112 b of the rolling bearings 111 and 112 are fitted into the holder 120. The holder 120 is fitted into the holder accommodating portion 105 a of the housing main body 105 A of the bearing housing 105. The retainer 105 </ b> B of the bearing housing 105 is attached to the opening end portion (end portion on the compressor impeller 103 side) of the holder housing portion 105 a, so that the holder 120 is a protrusion of the bearing housing 105 with respect to the axial direction of the turbine shaft 104. It is held between 105b and the retainer 105B. Each of the sleeve 114 and the holder 120 is configured as a separate part from the rolling bearings 111 and 112.
　ホルダ１２０は、外輪１１１ｂ、１１２ｂの外周に配置される保持部材としての円筒状のケース部１２２と、そのケース部１２２の内周側に突出して外輪１１１ｂ、１１２ｂの間に介在する外輪スペーサとしてのスペーサ部１２３とが一体化された構成を備えている。ケース部１２２の軸線方向両端面１２２ａ、１２２ｂは、外輪１１１ｂ、１１２ｂよりも軸線方向外側に突出した位置にある。言い換えれば、外輪１１１ｂ、１１２ｂは、ケース部１２２の軸線方向端面１２２ａ、１２２ｂよりも軸線方向内側に後退するようにしてホルダ１２０に嵌め合わされている。 The holder 120 has a cylindrical case portion 122 as a holding member disposed on the outer periphery of the outer rings 111b and 112b, and an outer ring spacer that protrudes on the inner peripheral side of the case portion 122 and is interposed between the outer rings 111b and 112b. The spacer part 123 is integrated. Both end surfaces 122a and 122b in the axial direction of the case portion 122 are in positions protruding outward in the axial direction from the outer rings 111b and 112b. In other words, the outer rings 111b and 112b are fitted to the holder 120 so as to recede inward in the axial direction from the axial end surfaces 122a and 122b of the case portion 122.
　スペーサ部１２３の両端には外輪１１１ｂ、１１２ｂが突き当てられている。それにより、外輪１１１ｂ、１１２ｂが軸線方向に位置決めされて外輪１１１ｂ、１１２ｂ間の軸線方向の距離が一定に保持される。 Outer rings 111b and 112b are abutted against both ends of the spacer portion 123. Accordingly, the outer rings 111b and 112b are positioned in the axial direction, and the axial distance between the outer rings 111b and 112b is kept constant.
　図８に示すように、スペーサ部１２３の軸線方向の寸法Ａと、スリーブ１１４の軸線方向の寸法Ｂとをそれぞれ正確に管理することにより、内輪１１１ａ、１１２ａ及び外輪１１１ｂ、１１２ｂのそれぞれは、軸線方向の位置ずれが最小となり、予圧が実質的に与えられない位置に保持される。これにより、タービン軸４の軸線方向の遊びを最小に抑え、タービンロータ２及びコンプレッサインペラ３とそれらのハウジングとの間の隙間を小さく設定して過給性能を向上させることができる。なお、外輪１１１ｂ、１１２ｂの軸線方向外側には、外輪１１１ｂ、１１２ｂをそれらの軸線方向外側から拘束する部材が設けられていない。すなわち、外輪１１１ｂ、１１２ｂは軸線方向外側へは非拘束の状態でホルダ１２０に嵌め合わされている。また、外輪１１１ｂ、１１２ｂの間には、これらを軸線方向に押し出して予圧を付加するばね等の弾性部材は設けられていない。転がり軸受１１１、１１２を予圧なしで組み付けることにより、転がり軸受１１１、１１２の内部における摩擦損失を抑えることができる。 As shown in FIG. 8, by accurately managing the dimension A in the axial direction of the spacer portion 123 and the dimension B in the axial direction of the sleeve 114, each of the inner rings 111a and 112a and the outer rings 111b and 112b The displacement in the direction is minimized, and the position is maintained at a position where the preload is not substantially applied. Thereby, the play in the axial direction of the turbine shaft 4 can be suppressed to a minimum, and the clearances between the turbine rotor 2 and the compressor impeller 3 and their housings can be set small to improve the supercharging performance. In addition, the member which restrains outer ring 111b, 112b from those axial direction outer sides is not provided in the axial direction outer side of outer rings 111b, 112b. That is, the outer rings 111b and 112b are fitted to the holder 120 in an unconstrained state outward in the axial direction. Further, an elastic member such as a spring that pushes them in the axial direction and applies a preload is not provided between the outer rings 111b and 112b. By assembling the rolling bearings 111 and 112 without preload, friction loss inside the rolling bearings 111 and 112 can be suppressed.
　ホルダ１２０と軸受ハウジング１０５との間には微小量の隙間１２５が設けられている。隙間１２５は、ホルダ１２０の外周側に位置する半径方向隙間１２５ａと、ホルダ１２０の軸線方向両端に位置する軸線方向隙間１２５ｂ、１２５ｃとを含む。半径方向隙間１２５ａはホルダ１２０の外周面の全面に亘って存在し、軸線方向隙間１２５ｂ、１２５ｃはホルダ１２０の端面１２２ａ、１２２ｂの全面に亘って存在する。つまり、後述するオイルフィルムが形成されていない状態において、ホルダ１２０は、軸受ハウジング１０５に対して半径方向隙間１２５ａに相当する量だけ半径方向に移動可能であり、軸線方向隙間１２５ｂ、１２５ｃに相当する量だけ軸線方向に移動可能である。 A very small gap 125 is provided between the holder 120 and the bearing housing 105. The gap 125 includes a radial gap 125 a located on the outer peripheral side of the holder 120 and axial gaps 125 b and 125 c located at both axial ends of the holder 120. The radial gap 125 a exists over the entire outer peripheral surface of the holder 120, and the axial gaps 125 b and 125 c exist over the entire end surfaces 122 a and 122 b of the holder 120. That is, in a state where an oil film described later is not formed, the holder 120 can move in the radial direction by an amount corresponding to the radial gap 125a with respect to the bearing housing 105, and corresponds to the axial gaps 125b and 125c. It can move in the axial direction by an amount.
　軸受ハウジング１０５には、その下面から半径方向隙間１２５ａに向かって給油路（図示省略）が形成されている。給油路を介して半径方向隙間１２５ａに潤滑油が供給されることにより、隙間１２５が潤滑油で満たされてホルダ１２０と軸受ハウジング１０５との間にオイルフィルムが形成される。そのオイルフィルムと、ホルダ１２０及び軸受ハウジング１０５とによってオイルフィルムダンパ１０８が構成され、そのオイルフィルムダンパ１０８により外輪１１１ｂ、１１２ｂが支持される。 In the bearing housing 105, an oil supply path (not shown) is formed from its lower surface toward the radial gap 125a. By supplying the lubricating oil to the radial gap 125 a through the oil supply passage, the gap 125 is filled with the lubricating oil, and an oil film is formed between the holder 120 and the bearing housing 105. The oil film, the holder 120 and the bearing housing 105 constitute an oil film damper 108, and the oil film damper 108 supports the outer rings 111b and 112b.
　このようにオイルフィルムダンパ１０８を設けることにより、軸受アッセンブリの振動を効率よく吸収することが可能となる。よって、毎分１０万回転を超える高速回転領域に対する過給機１の適応性を高めることができる。ホルダ１２０の半径方向及び軸線方向にそれぞれ隙間１２５ａ、１２５ｂ、１２５ｃが存在するため、ホルダ１２０が軸受ハウジング１０５に対して半径方向及び軸線方向に円滑に動くことができる。このため、オイルフィルムダンパ１０８による振動吸収効果が高まる。 By providing the oil film damper 108 in this way, it is possible to efficiently absorb the vibration of the bearing assembly. Therefore, the adaptability of the supercharger 1 with respect to a high-speed rotation region exceeding 100,000 rotations per minute can be improved. Since the gaps 125 a, 125 b, and 125 c exist in the radial direction and the axial direction of the holder 120, the holder 120 can smoothly move in the radial direction and the axial direction with respect to the bearing housing 105. For this reason, the vibration absorption effect by the oil film damper 108 is enhanced.
　軸受アッセンブリの軸線方向の振れは、ホルダ１２０の端面１２２ａ、１２２ｂが軸受ハウジング１０５の突起部１０５ｂ又はリテーナ１０５Ｂに接することにより制限される。ホルダ１２０の両端面１２２ａ、１２２ｂよりも外輪１１１ｂ、１１２ｂが軸線方向内側に後退しているため、外輪１１１ｂ、１１２ｂが軸受ハウジング１０５に直接突き当たるおそれはない。しかも、ホルダ１２０と外輪１１１ｂ、１１２ｂとは別部品であり、さらに外輪１１１ｂ、１１２ｂは軸線方向外側へは非拘束の状態でホルダ１２０に嵌め合わされている。よって、外輪１１１ｂ、１１２ｂは内輪１１１ａ、１１２ａからボール１１１ｃ、１１２ｃを介して伝わる軸線方向の力のみで変位し、転がり軸受１１１、１１２に不自然な軸線方向の外力が作用しない。 The axial deflection of the bearing assembly is limited when the end surfaces 122a and 122b of the holder 120 are in contact with the protrusion 105b or the retainer 105B of the bearing housing 105. Since the outer rings 111 b and 112 b are retracted inward in the axial direction from both end faces 122 a and 122 b of the holder 120, there is no possibility that the outer rings 111 b and 112 b directly hit the bearing housing 105. Moreover, the holder 120 and the outer rings 111b and 112b are separate parts, and the outer rings 111b and 112b are fitted to the holder 120 in an unconstrained state outward in the axial direction. Therefore, the outer rings 111b and 112b are displaced only by the axial force transmitted from the inner rings 111a and 112a via the balls 111c and 112c, and an unnatural axial external force does not act on the rolling bearings 111 and 112.
　ホルダ１２０の外周には、２本の環状溝１３０がホルダ１２０を一周するように設けられている。各環状溝１３０には、図８に示すように、転がり軸受１１１、１１２側に潤滑油を供給するためのオイルジェット孔１３１が設けられている。オイルジェット孔１３１は、その中心線が内輪１１１ａ、１１２ａに向かうように設けられている。これにより、オイルフィルムを形成した潤滑油の一部がオイルジェット孔１３１から内輪１１１ａ、１１２ａに給油される（図８黒色矢印）。従って、ボール１１１ｃ、１１２ｃに向かって潤滑油を直接吹き付けた場合と比較して潤滑油の撹拌損失を低減させ、過給効率を高めることができる。 The outer periphery of the holder 120 is provided with two annular grooves 130 so as to go around the holder 120. As shown in FIG. 8, each annular groove 130 is provided with an oil jet hole 131 for supplying lubricating oil to the rolling bearings 111 and 112 side. The oil jet hole 131 is provided so that the center line thereof faces the inner rings 111a and 112a. Thereby, a part of the lubricating oil forming the oil film is supplied from the oil jet hole 131 to the inner rings 111a and 112a (black arrow in FIG. 8). Therefore, compared with the case where the lubricating oil is directly sprayed toward the balls 111c and 112c, the stirring loss of the lubricating oil can be reduced and the supercharging efficiency can be increased.
　オイルジェット孔１３１から内輪１１１ａ、１１２ａに向かって給油された潤滑油は、遠心力によって外周へ吹き飛ばされ、外輪１１１ｂ、１１２ｂの内面側から転がり軸受１１１、１１２の軸線方向の外側に排出される（図８黒色矢印）。 Lubricating oil supplied from the oil jet hole 131 toward the inner rings 111a and 112a is blown off to the outer periphery by centrifugal force, and is discharged from the inner surface side of the outer rings 111b and 112b to the outside in the axial direction of the rolling bearings 111 and 112 ( FIG. 8 black arrow).
実開昭６２－３５１９５号公報Japanese Utility Model Publication No. 62-35195 特開平４－７２４２４号公報Japanese Patent Laid-Open No. 4-72424 特開平４－８８２５号公報Japanese Patent Laid-Open No. 4-8825 実公平６－４０９０８号公報No. 6-40908 特開２００２－３６９４７４号公報JP 2002-369474 A 特許第５０７５０００号公報Japanese Patent No. 5075000
　ところで、図７及び図８に示す軸受装置１１０においては、ホルダ１２０の半径方向の外周面及び軸線方向の端面と軸受ハウジング１０５との間に、それぞれ隙間１２５ａ、１２５ｂ、１２５ｃが存在し、この隙間１２５ａ、１２５ｂ、１２５ｃには、オイルフィルムダンパ１０８を設けるために、潤滑油が供給され、この潤滑油は図８に白抜き矢印で示すように、ホルダ１２０の両端面１２２ａ、１２２ｂよりも軸線方向内側に後退した外輪１１１ｂ、１１２ｂの軸線方向外側部分に排出される。 Incidentally, in the bearing device 110 shown in FIGS. 7 and 8, gaps 125 a, 125 b, and 125 c exist between the outer peripheral surface in the radial direction and the end surface in the axial direction of the holder 120 and the bearing housing 105, respectively. 125a, 125b, 125c is supplied with lubricating oil in order to provide the oil film damper 108, and this lubricating oil is more axial than the two end faces 122a, 122b of the holder 120, as indicated by white arrows in FIG. It is discharged to the outer side portion in the axial direction of the outer rings 111b and 112b retracted inward.
　また、オイルフィルムを形成した潤滑油の一部は、図８に黒色矢印で示すように、オイルジェット孔１３１から内輪１１１ａに向かって給油され、給油された潤滑油は転がり軸受１１１、１１２の軸線方向外側に排出される。 Further, a part of the lubricating oil forming the oil film is supplied from the oil jet hole 131 toward the inner ring 111a as shown by the black arrow in FIG. 8, and the supplied lubricating oil is the axis of the rolling bearings 111 and 112. It is discharged outward.
　この転がり軸受１１１、１１２の軸線方向外側に排出される潤滑油と、ホルダ１２０の両端面１２２ａ、１２２ｂから排出される潤滑油は、互いに直交する方向に排出されるため、転がり軸受１１１、１１２の軸線方向外側部分で排出される潤滑油がぶつかり合って潤滑油が滞留し、その結果、潤滑油の排出が円滑に行われず、転がり軸受の摩擦損失が大きくなるおそれがある。 Since the lubricating oil discharged to the outside in the axial direction of the rolling bearings 111 and 112 and the lubricating oil discharged from the both end faces 122a and 122b of the holder 120 are discharged in directions orthogonal to each other, the rolling bearings 111 and 112 The lubricating oil discharged at the outer portion in the axial direction collides and the lubricating oil stays. As a result, the lubricating oil is not discharged smoothly, and the friction loss of the rolling bearing may increase.
　そこで、この発明は、転がり軸受の外輪を、軸受ハウジングに対してホルダを介してオイルフィルムダンパによって支持し、オイルフィルムダンパに供給される潤滑油の排出経路が、転がり軸受を通過して軸線方向外側に排出される経路と、ホルダの両端面から排出される経路とを有する軸受装置において、転がり軸受を通過して軸線方向外側に排出される潤滑油と、ホルダの両端面から排出される潤滑油とが転がり軸受の軸線方向外側部分でぶつかり合わないようにして、転がり軸受の軸線方向外側部分での潤滑油の滞留を防止しようとするものである。 Therefore, the present invention supports the outer ring of the rolling bearing by the oil film damper through the holder with respect to the bearing housing, and the discharge path of the lubricating oil supplied to the oil film damper passes through the rolling bearing in the axial direction. In a bearing device having a path discharged to the outside and a path discharged from both end faces of the holder, lubricating oil discharged through the rolling bearing to the outside in the axial direction and lubrication discharged from both end faces of the holder It is intended to prevent the oil from staying in the axially outer portion of the rolling bearing by preventing the oil from colliding with the axially outer portion of the rolling bearing.
　前記の課題を解決するために、この発明は、過給機の回転軸上に配置される一対の転がり軸受と、前記一対の転がり軸受とは別部品として構成され、該一対の軸受の外輪のそれぞれが嵌め合わされる保持部材と、前記外輪を支持するオイルフィルムダンパが形成されるように前記保持部材と組み合わされる軸受ハウジングと、前記一対の軸受の内輪間に配置されて内輪間の軸線方向の距離を一定に保持する内輪スペーサと、前記外輪間に配置されて外輪間の軸線方向の距離を一定に保持する外輪スペーサとを具備し、前記外輪は、軸線方向外側へは非拘束の状態で前記保持部材に嵌め合わされ、前記保持部材の外周及び軸線方向両端面のそれぞれと前記軸受ハウジングとが前記オイルフィルムを形成するための隙間を介して対向し、オイルフィルムダンパに供給される潤滑油の排出経路が、転がり軸受を通過して軸線方向外側に排出される経路と、前記保持部材の軸線方向両端面から排出される経路とを有する、過給機の軸受装置において、前記保持部材の軸線方向両端面の経路から排出される潤滑油の流れ方向を前記外輪の軸線方向外側に向かって変更する流れ方向変更部を、前記外輪の軸線方向外側に設けたことを特徴とする。 In order to solve the above-described problems, the present invention is configured as a pair of rolling bearings disposed on a rotating shaft of a supercharger and the pair of rolling bearings as separate parts, and the outer ring of the pair of bearings A holding member to which each is fitted, a bearing housing combined with the holding member so as to form an oil film damper that supports the outer ring, and an axial direction between the inner rings arranged between the inner rings of the pair of bearings An inner ring spacer that maintains a constant distance; and an outer ring spacer that is disposed between the outer rings and that maintains a constant axial distance between the outer rings. The outer ring is in an unconstrained state outward in the axial direction. The bearing member is fitted into the holding member, and the bearing housing and each of the outer periphery and the axial end faces of the holding member are opposed to each other through a gap for forming the oil film. A turbocharger bearing in which a discharge path for lubricating oil supplied to the film damper includes a path that passes through the rolling bearing and is discharged to the outside in the axial direction, and a path that is discharged from both axial end surfaces of the holding member. In the apparatus, a flow direction changing portion for changing the flow direction of the lubricating oil discharged from the path of both end surfaces in the axial direction of the holding member toward the outer side in the axial direction of the outer ring is provided on the outer side in the axial direction of the outer ring. It is characterized by.
　前記流れ方向変更部は、前記保持部材の軸線方向両端面に一体に形成された段差によって構成することができる。 The flow direction changing portion can be constituted by steps formed integrally on both end surfaces in the axial direction of the holding member.
　また、前記流れ方向変更部は、前記外輪の軸線方向外側面に設けられた、外輪と別体のリング部材に形成してもよい。 Further, the flow direction changing portion may be formed on a ring member separate from the outer ring, provided on the outer surface in the axial direction of the outer ring.
　また、前記流れ方向変更部は、前記外輪の軸線方向外側面に一体に形成した段差によって構成することもできる。 Further, the flow direction changing portion can be constituted by a step formed integrally on the outer side surface in the axial direction of the outer ring.
　以上のように、この発明の過給機の軸受装置は、保持部材の軸線方向両端面の経路から排出される潤滑油の流れ方向を、外輪の軸線方向外側に向かって変更する流れ方向変更部を有するので、転がり軸受を通過して軸線方向外側に排出される潤滑油と、ホルダの両端面から排出される潤滑油とが転がり軸受の軸線方向外側部分で平行になって、ぶつかり合わないため、転がり軸受の軸線方向外側部分での潤滑油の滞留を防止することができる。 As described above, the bearing device of the supercharger according to the present invention has a flow direction changing portion that changes the flow direction of the lubricating oil discharged from the path on both end surfaces in the axial direction of the holding member toward the outside in the axial direction of the outer ring. Therefore, the lubricating oil discharged to the outside in the axial direction through the rolling bearing and the lubricating oil discharged from the both end faces of the holder are parallel to each other on the outer side in the axial direction of the rolling bearing, and do not collide with each other. Further, it is possible to prevent the lubricating oil from staying at the outer side portion in the axial direction of the rolling bearing.
この発明の一形態に係る軸受装置が組み込まれた過給機の軸線方向の断面図である。It is sectional drawing of the axial direction of the supercharger in which the bearing apparatus which concerns on one form of this invention was integrated. 図１の左側の転がり軸受部分の拡大断面図である。It is an expanded sectional view of the rolling bearing part on the left side of FIG. この発明の別の形態に係る軸受装置が組み込まれた過給機の軸線方向の断面図である。It is sectional drawing of the axial direction of the supercharger in which the bearing apparatus which concerns on another form of this invention was integrated. 図３の左側の転がり軸受部分の拡大断面図である。It is an expanded sectional view of the rolling bearing part of the left side of FIG. この発明の別の形態に係る軸受装置が組み込まれた過給機の軸線方向の断面図である。It is sectional drawing of the axial direction of the supercharger in which the bearing apparatus which concerns on another form of this invention was integrated. 図５の左側の転がり軸受部分の拡大断面図である。It is an expanded sectional view of the rolling bearing part of the left side of FIG. 従来の軸受装置が組み込まれた過給機の軸線方向の断面図である。It is sectional drawing of the axial direction of the supercharger in which the conventional bearing apparatus was integrated. 図７の軸受装置の部分拡大図である。It is the elements on larger scale of the bearing apparatus of FIG.
　以下、この発明の実施形態を添付図面に基づいて説明する。 Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
　図１は、この発明の第１の実施形態に係る軸受装置１０が組み込まれた過給機１を示している。 FIG. 1 shows a supercharger 1 in which a bearing device 10 according to a first embodiment of the present invention is incorporated.
　過給機１は、内燃機関の排気通路に設けられるタービンロータ２と、内燃機関の吸気通路に設けられるコンプレッサインペラ３と、それらを一体回転可能に連結する回転軸としてのタービン軸４とを備えたターボチャージャとして構成されている。 The supercharger 1 includes a turbine rotor 2 provided in an exhaust passage of the internal combustion engine, a compressor impeller 3 provided in an intake passage of the internal combustion engine, and a turbine shaft 4 as a rotary shaft that couples them so as to be integrally rotatable. It is configured as a turbocharger.
　タービンロータ２とタービン軸４とは同軸上に一体形成されている。タービン軸４には、タービンロータ２側からコンプレッサインペラ３に向かって、大径部４ａ、中間部４ｂ及び小径部４ｃが順次設けられた段付きシャフトである。 The turbine rotor 2 and the turbine shaft 4 are integrally formed on the same axis. The turbine shaft 4 is a stepped shaft in which a large diameter portion 4 a, an intermediate portion 4 b, and a small diameter portion 4 c are sequentially provided from the turbine rotor 2 side toward the compressor impeller 3.
　中間部４ｂは過給機１の軸受ハウジング５内に挿入され、小径部４ｃは軸受ハウジング５を貫いてコンプレッサハウジング（図示しない）内に挿入されている。軸受ハウジング５は、ハウジング本体５Ａの一端に、リテーナ５Ｂがボルト等の固定手段を用いて結合されている。 The intermediate portion 4b is inserted into the bearing housing 5 of the supercharger 1, and the small diameter portion 4c is inserted into the compressor housing (not shown) through the bearing housing 5. In the bearing housing 5, a retainer 5 </ b> B is coupled to one end of the housing body 5 </ b> A using a fixing means such as a bolt.
　中間部４ｂの外周には一対の転がり軸受１１、１２が嵌め合わされている。転がり軸受１１、１２は、内輪１１ａ、１２ａと、外輪１１ｂ、１２ｂと、それらの間に配置される転動体としての多数のボール１１ｃ、１２ｃとを備えた玉軸受である。より具体的には、転がり軸受１１、１２は、径方向荷重と一方向の軸線方向荷重とを負荷するアンギュラコンタクト玉軸受である。転がり軸受１１、１２の内輪１１ａ、１２ａのそれぞれはタービン軸４上に嵌め合わされる。転がり軸受１１はタービンロータ２に向かう方向の軸線方向荷重を負荷し、転がり軸受１２はコンプレッサインペラ３に向かう方向の軸線方向荷重を負荷する向きでそれぞれ取り付けられている。 A pair of rolling bearings 11 and 12 are fitted on the outer periphery of the intermediate portion 4b. The rolling bearings 11 and 12 are ball bearings including inner rings 11a and 12a, outer rings 11b and 12b, and a large number of balls 11c and 12c as rolling elements disposed therebetween. More specifically, the rolling bearings 11 and 12 are angular contact ball bearings that apply a radial load and one axial load. Each of the inner rings 11 a and 12 a of the rolling bearings 11 and 12 is fitted onto the turbine shaft 4. The rolling bearing 11 is loaded with an axial load in the direction toward the turbine rotor 2, and the rolling bearing 12 is mounted in such a direction as to load an axial load in the direction toward the compressor impeller 3.
　転がり軸受１１の内輪１１ａ、１２ａの間には内輪スペーサとしてのスリーブ１４が設けられている。転がり軸受１１の内輪１１ａの軸線方向の外面は、タービン軸４の大径部４ａと中間部４ｂとの間に形成された段差部１３に当接している。一方、転がり軸受１２の内輪１２ａの軸線方向の外面は、タービン軸４の小径部４ｃに嵌められたコンプレッサインペラ３の端面部１５に当接している。タービン軸４の小径部４ｃにコンプレッサインペラ３を嵌め込むことにより、内輪１１ａ、スリーブ１４及び内輪１２ａが、タービン軸４の大径部４ａと中間部４ｂとの間の段差部１３及びコンプレッサインペラ３の端面部１５の間に挟み込まれて軸線方向の定位置に拘束される。これにより、タービンロータ２、タービン軸４、内輪１１ａ、スリーブ１４、内輪１２ａ、コンプレッサインペラ３は、タービン軸４の中心線ＣＬの回りに一体回転可能な回転体アッセンブリ６として組み立てられる。 Between the inner rings 11a and 12a of the rolling bearing 11, a sleeve 14 as an inner ring spacer is provided. The outer surface in the axial direction of the inner ring 11 a of the rolling bearing 11 is in contact with a stepped portion 13 formed between the large diameter portion 4 a and the intermediate portion 4 b of the turbine shaft 4. On the other hand, the outer surface in the axial direction of the inner ring 12 a of the rolling bearing 12 is in contact with the end surface portion 15 of the compressor impeller 3 fitted to the small diameter portion 4 c of the turbine shaft 4. By fitting the compressor impeller 3 into the small diameter portion 4 c of the turbine shaft 4, the inner ring 11 a, the sleeve 14, and the inner ring 12 a are stepped between the large diameter portion 4 a and the intermediate portion 4 b of the turbine shaft 4 and the compressor impeller 3. Is sandwiched between the end face portions 15 and is constrained to a fixed position in the axial direction. Thus, the turbine rotor 2, the turbine shaft 4, the inner ring 11 a, the sleeve 14, the inner ring 12 a, and the compressor impeller 3 are assembled as a rotating body assembly 6 that can rotate integrally around the center line CL of the turbine shaft 4.
　転がり軸受１１、１２のそれぞれの外輪１１ｂ、１２ｂは、保持部材としてのホルダ２０に嵌め合わされている。そのホルダ２０は、軸受ハウジング５のハウジング本体５Ａのホルダ収容部５ａに嵌め合わされている。軸受ハウジング５のリテーナ５Ｂは、ホルダ収容部５ａの開口端部（コンプレッサインペラ３側の端部）に取り付けられ、それにより、ホルダ２０は、タービン軸４の軸線方向に関して、軸受ハウジング５の突起部５ｂとリテーナ５Ｂとの間に保持される。なお、スリーブ１４及びホルダ２０のそれぞれは転がり軸受１１、１２とは別部品として構成されている。 The outer rings 11b and 12b of the rolling bearings 11 and 12 are fitted into a holder 20 as a holding member. The holder 20 is fitted into the holder accommodating portion 5 a of the housing main body 5 </ b> A of the bearing housing 5. The retainer 5 </ b> B of the bearing housing 5 is attached to the opening end portion (end portion on the compressor impeller 3 side) of the holder housing portion 5 a, so that the holder 20 is a protrusion of the bearing housing 5 with respect to the axial direction of the turbine shaft 4. It is held between 5b and the retainer 5B. Each of the sleeve 14 and the holder 20 is configured as a separate part from the rolling bearings 11 and 12.
　ホルダ２０は、外輪１１ｂ、１２ｂの外周に配置される保持部材としての円筒状のケース部２２と、そのケース部２２の内周側に突出して外輪１１ｂ、１２ｂの間に介在する外輪スペーサとしてのスペーサ部２３とが一体化された構成を備えている。ケース部２２の軸線方向両端面２２ａ、２２ｂは、外輪１１ｂ、１２ｂよりも軸線方向外側に突出した位置にある。言い換えれば、外輪１１ｂ、１２ｂは、ケース部２２の軸線方向端面２２ａ、２２ｂよりも軸線方向内側に後退するようにしてホルダ２０に嵌め合わされている。 The holder 20 is a cylindrical case portion 22 as a holding member disposed on the outer periphery of the outer rings 11b and 12b, and an outer ring spacer that protrudes on the inner peripheral side of the case portion 22 and is interposed between the outer rings 11b and 12b. The spacer part 23 is integrated. Both end surfaces 22a and 22b in the axial direction of the case portion 22 are in positions protruding outward in the axial direction from the outer rings 11b and 12b. In other words, the outer rings 11b and 12b are fitted into the holder 20 so as to recede inward in the axial direction from the axial end faces 22a and 22b of the case portion 22.
　また、ケース部２２の軸線方向端面２２ａ、２２ｂの内径部には、軸受ハウジング５とリテーナ５Ｂと隙間を空けて、ケース部２２の軸線方向端面２２ａ、２２ｂから内径側に向かって排出される潤滑油の流れ方向を軸線方向外側に向かうように変更する流れ方向変更部４０が段差によって形成されている。 In addition, a gap is formed between the bearing housing 5 and the retainer 5B in the inner diameter portions of the axial end surfaces 22a and 22b of the case portion 22, and the lubricant is discharged from the axial end surfaces 22a and 22b of the case portion 22 toward the inner diameter side. A flow direction changing portion 40 that changes the oil flow direction toward the outside in the axial direction is formed by a step.
　スペーサ部２３の両端には外輪１１ｂ、１２ｂが突き当てられている。それにより、外輪１１ｂ、１２ｂが軸線方向に位置決めされて外輪１１ｂ、１２ｂ間の軸線方向の距離が一定に保持される。そして、転がり軸受１１、１２、スリーブ１４及びホルダ２０が相互に組み立てられることにより、軸受アッセンブリ７が形成される。スペーサ部２３の軸線方向の寸法と、スリーブ１４の軸線方向の寸法とをそれぞれ正確に管理することにより、内輪１１ａ、１２ａ及び外輪１１ｂ、１２ｂのそれぞれは、軸線方向の位置ずれが最小となり、予圧が実質的に与えられない位置に保持される。これにより、タービン軸４の軸線方向の遊びを最小に抑え、タービンロータ２及びコンプレッサインペラ３とそれらのハウジングとの間の隙間を小さく設定して過給性能を向上させることができる。なお、外輪１１ｂ、１２ｂの軸線方向外側には、外輪１１ｂ、１２ｂをそれらの軸線方向外側から拘束する部材が設けられていない。すなわち、外輪１１ｂ、１２ｂは軸線方向外側へは非拘束の状態でホルダ２０に嵌め合わされている。また、外輪１１ｂ、１２ｂの間には、これらを軸線方向に押し出して予圧を付加するばね等の弾性部材は設けられていない。転がり軸受１１、１２を予圧なしで組み付けることにより、転がり軸受１１、１２の内部における摩擦損失を抑えることができる。 Outer rings 11b and 12b are abutted against both ends of the spacer portion 23. Accordingly, the outer rings 11b and 12b are positioned in the axial direction, and the axial distance between the outer rings 11b and 12b is kept constant. Then, the rolling bearings 11 and 12, the sleeve 14 and the holder 20 are assembled with each other, whereby the bearing assembly 7 is formed. By accurately managing the dimension of the spacer portion 23 in the axial direction and the dimension of the sleeve 14 in the axial direction, each of the inner rings 11a, 12a and the outer rings 11b, 12b has a minimum positional deviation in the axial direction, and the preload Is held in a position that is substantially not provided. Thereby, the play in the axial direction of the turbine shaft 4 can be suppressed to a minimum, and the clearances between the turbine rotor 2 and the compressor impeller 3 and their housings can be set small to improve the supercharging performance. In addition, the member which restrains outer ring | wheel 11b, 12b from those axial direction outer sides is not provided in the axial direction outer side of outer ring | wheel 11b, 12b. That is, the outer rings 11b and 12b are fitted to the holder 20 in an unconstrained state toward the outside in the axial direction. Further, an elastic member such as a spring that pushes them in the axial direction and applies a preload is not provided between the outer rings 11b and 12b. By assembling the rolling bearings 11 and 12 without preload, friction loss inside the rolling bearings 11 and 12 can be suppressed.
　ホルダ２０と軸受ハウジング５との間には微小量の隙間２５が設けられている。隙間２５は、ホルダ２０の外周側に位置する半径方向隙間２５ａと、ホルダ２０の軸線方向両端に位置する軸線方向隙間２５ｂ、２５ｃとを含む。半径方向隙間２５ａはホルダ２０の外周面に存在し、軸線方向隙間２５ｂ、２５ｃはホルダ２０の端面２２ａ、２２ｂに存在する。つまり、後述するオイルフィルムが形成されていない状態において、ホルダ２０は、軸受ハウジング５に対して半径方向隙間２５ａに相当する量だけ半径方向に移動可能であり、軸線方向隙間２５ｂ、２５ｃに相当する量だけ軸線方向に移動可能である。 A very small gap 25 is provided between the holder 20 and the bearing housing 5. The gap 25 includes a radial gap 25 a located on the outer peripheral side of the holder 20, and axial gaps 25 b and 25 c located at both axial ends of the holder 20. The radial gap 25 a exists on the outer peripheral surface of the holder 20, and the axial gaps 25 b and 25 c exist on the end faces 22 a and 22 b of the holder 20. That is, in a state where an oil film to be described later is not formed, the holder 20 can move in the radial direction by an amount corresponding to the radial gap 25a with respect to the bearing housing 5, and corresponds to the axial gaps 25b and 25c. It can move in the axial direction by an amount.
　軸受ハウジング５には、半径方向隙間２５ａに対して潤滑油を供給する給油路４１が形成されている。給油路４１を介して半径方向隙間２５ａに潤滑油が供給されることにより、隙間２５が潤滑油で満たされてホルダ２０と軸受ハウジング５との間にオイルフィルムが形成される。そのオイルフィルムと、ホルダ２０及び軸受ハウジング５とによってオイルフィルムダンパ８が構成され、そのオイルフィルムダンパ８により外輪１１ｂ、１２ｂが支持される。このようにオイルフィルムダンパ８を設けることにより、軸受アッセンブリ７の振動を効率よく吸収することが可能となる。よって、毎分１０万回転を超える高速回転領域に対する過給機１の適応性を高めることができる。ホルダ２０の半径方向及び軸線方向にそれぞれ隙間２５ａ、２５ｂ、２５ｃが存在するため、ホルダ２０が軸受ハウジング５に対して半径方向及び軸線方向に円滑に動くことができる。このため、オイルフィルムダンパ８による振動吸収効果が高まる。 The bearing housing 5 is provided with an oil supply passage 41 for supplying lubricating oil to the radial gap 25a. By supplying the lubricating oil to the radial gap 25 a via the oil supply passage 41, the gap 25 is filled with the lubricating oil, and an oil film is formed between the holder 20 and the bearing housing 5. The oil film, the holder 20 and the bearing housing 5 constitute an oil film damper 8, and the oil film damper 8 supports the outer rings 11 b and 12 b. By providing the oil film damper 8 in this way, it is possible to efficiently absorb the vibration of the bearing assembly 7. Therefore, the adaptability of the supercharger 1 with respect to a high-speed rotation region exceeding 100,000 rotations per minute can be improved. Since the gaps 25 a, 25 b, and 25 c exist in the radial direction and the axial direction of the holder 20, the holder 20 can smoothly move in the radial direction and the axial direction with respect to the bearing housing 5. For this reason, the vibration absorption effect by the oil film damper 8 increases.
　軸受アッセンブリ７の軸線方向の振れは、ホルダ２０の端面２２ａ、２２ｂが軸受ハウジング５の突起部５ｂ又はリテーナ５Ｂに接することにより制限される。ホルダ２０の両端面２２ａ、２２ｂよりも外輪１１ｂ、１２ｂが軸線方向内側に後退しているため、外輪１１ｂ、１２ｂが軸受ハウジング５に直接突き当たるおそれはない。しかも、ホルダ２０と外輪１１ｂ、１２ｂとは別部品であり、さらに外輪１１ｂ、１２ｂは軸線方向外側へは非拘束の状態でホルダ２０に嵌め合わされている。よって、外輪１１ｂ、１２ｂは内輪１１ａ、１２ａからボール１１ｃ、１２ｃを介して伝わる軸線方向の力のみで変位し、転がり軸受１１、１２に不自然な軸線方向の外力が作用しない。 The axial deflection of the bearing assembly 7 is limited when the end surfaces 22a and 22b of the holder 20 are in contact with the protrusion 5b or the retainer 5B of the bearing housing 5. Since the outer rings 11 b and 12 b are retracted inward in the axial direction from both end faces 22 a and 22 b of the holder 20, there is no possibility that the outer rings 11 b and 12 b directly hit the bearing housing 5. Moreover, the holder 20 and the outer rings 11b and 12b are separate parts, and the outer rings 11b and 12b are fitted to the holder 20 in an unconstrained state outward in the axial direction. Therefore, the outer rings 11b and 12b are displaced only by the axial force transmitted from the inner rings 11a and 12a via the balls 11c and 12c, and an unnatural axial external force does not act on the rolling bearings 11 and 12.
　ホルダ２０には、２本の給油部４２が設けられている。各給油部４２には、転がり軸受１１、１２側に潤滑油を供給するためのオイルジェット孔４３が設けられている。なお、図２では転がり軸受１１側のオイルジェット孔４３のみが図示されているが、転がり軸受１２側にも同様のオイルジェット孔４３が設けられている。オイルジェット孔４３は、その中心線が内輪１１ａに向かうように設けられている。これにより、オイルフィルムを形成した潤滑油の一部がオイルジェット孔４３から内輪１１ａ及びその周囲に給油される。従って、ボール１１ｃに向かって潤滑油を直接吹き付けた場合と比較して潤滑油の撹拌損失を低減させ、過給効率を高めることができる。転がり軸受１２側に関しても同様である。また、特にタービンロータ２側のオイルジェット孔４３を上記の通りに形成した場合には、タービンロータ２からタービン軸４を介して転がり軸受１１及びスリーブ１４に伝達される熱をオイルジェット孔４３からの潤滑油で吸収して過給機１の冷却効率を改善することができる。 The holder 20 is provided with two oil supply portions 42. Each oil supply portion 42 is provided with an oil jet hole 43 for supplying lubricating oil to the rolling bearings 11 and 12 side. 2 shows only the oil jet hole 43 on the rolling bearing 11 side, the same oil jet hole 43 is also provided on the rolling bearing 12 side. The oil jet hole 43 is provided so that the center line thereof faces the inner ring 11a. As a result, a part of the lubricating oil forming the oil film is supplied from the oil jet hole 43 to the inner ring 11a and the periphery thereof. Therefore, the stirring loss of the lubricating oil can be reduced and the supercharging efficiency can be increased as compared with the case where the lubricating oil is directly sprayed toward the ball 11c. The same applies to the rolling bearing 12 side. In particular, when the oil jet hole 43 on the turbine rotor 2 side is formed as described above, the heat transmitted from the turbine rotor 2 to the rolling bearing 11 and the sleeve 14 via the turbine shaft 4 is transmitted from the oil jet hole 43. Therefore, the cooling efficiency of the supercharger 1 can be improved.
　オイルジェット孔４３から内輪１１ａの内面に供給された潤滑油は、遠心力により、外輪１１ｂの内面へ吹き飛ばされ、外輪１１ｂの軸線方向の外側に向かって排出される（図２の黒色矢印）。 Lubricating oil supplied from the oil jet hole 43 to the inner surface of the inner ring 11a is blown off to the inner surface of the outer ring 11b by centrifugal force and discharged toward the outer side in the axial direction of the outer ring 11b (black arrow in FIG. 2).
　一方、ホルダ２０の半径方向の外周面及び軸線方向の端面と軸受ハウジング５との間に、それぞれ隙間２５ａ、２５ｂ、２５ｃが存在し、この隙間２５ａ、２５ｂ、２５ｃには、オイルフィルムダンパ８を設けるために、潤滑油が供給され、この潤滑油は、図２に白抜き矢印で示すように、ホルダ２０の両端面２２ａ、２２ｂより内径側に向かって排出される。このように、軸受装置１０では、オイルフィルムダンパ８に供給される潤滑油の排出経路は、転がり軸受１１、１２を通過して軸線方向外側に排出される経路と、ホルダ２０の軸線方向両端面２２ａ、２２ｂから排出される経路とを有する。 On the other hand, clearances 25a, 25b, and 25c exist between the outer peripheral surface in the radial direction and the end surface in the axial direction of the holder 20 and the bearing housing 5, and the oil film damper 8 is provided in the clearances 25a, 25b, and 25c. In order to provide, lubricating oil is supplied, and this lubricating oil is discharged | emitted from the both end surfaces 22a and 22b of the holder 20 toward an internal diameter side, as shown by the white arrow in FIG. Thus, in the bearing device 10, the discharge path for the lubricating oil supplied to the oil film damper 8 is a path that passes through the rolling bearings 11, 12 and is discharged to the outside in the axial direction, and both end faces in the axial direction of the holder 20. 22a and 22b, and a route discharged from 22a and 22b.
　ホルダ２０の両端面２２ａ、２２ｂより内径側に向かって排出される潤滑油は、ケース部２２の軸線方向端面２２ａ、２２ｂの内径部に外側に向かって突き出すように設けられた段差からなる流れ方向変更部４０に当たり、流れ方向が軸線方向の外向きに変えられる。 Lubricating oil discharged from the both end faces 22a, 22b of the holder 20 toward the inner diameter side is a flow direction comprising steps provided so as to protrude outward from the inner diameter parts of the axial end faces 22a, 22b of the case section 22. When hitting the change unit 40, the flow direction is changed outward in the axial direction.
　したがって、ケース部２２の軸線方向端面２２ａ、２２ｂから排出される潤滑油の流れ方向と、転がり軸受１１内を通過して排出される潤滑油の流れ方向が、図２に白抜き矢印と黒色矢印に示すように、外側に向かって平行になり、転がり軸受１１の軸線方向の外側部分に潤滑油が滞留するということを防止することができる。 Therefore, the flow direction of the lubricating oil discharged from the axial end faces 22a and 22b of the case portion 22 and the flow direction of the lubricating oil discharged through the rolling bearing 11 are shown by white arrows and black arrows in FIG. As shown in FIG. 4, the oil is parallel to the outside, and it is possible to prevent the lubricating oil from staying in the outer portion of the rolling bearing 11 in the axial direction.
　図３及び図４は、この発明に係る第２の実施形態に係る軸受装置１０が組み込まれた過給機１を示している。 3 and 4 show the supercharger 1 in which the bearing device 10 according to the second embodiment of the present invention is incorporated.
　この第２の実施形態の軸受装置１０は、第１の実施形態において、ケース部２２の軸線方向端面２２ａ、２２ｂの内径部に形成した段差からなる流れ方向変更部４０を、第２の実施形態では、外輪１１ｂ、１２ｂと別体のリング部材４４に設けている。その他の構成は、第１の実施形態と同様であるので、詳細な説明は省略する。 In the bearing device 10 of the second embodiment, in the first embodiment, the flow direction changing portion 40 formed of a step formed on the inner diameter portion of the axial end surfaces 22a and 22b of the case portion 22 is the second embodiment. Then, the ring members 44 are provided separately from the outer rings 11b and 12b. Since other configurations are the same as those of the first embodiment, detailed description thereof is omitted.
　図５及び図６は、この発明に係る第３の実施形態に係る軸受装置１０が組み込まれた過給機１を示している。 5 and 6 show the supercharger 1 in which the bearing device 10 according to the third embodiment of the present invention is incorporated.
　この第３の実施形態の軸受装置１０は、第１の実施形態において、ケース部２２の軸線方向端面２２ａ、２２ｂの内径部に形成した段差からなる流れ方向変更部４０を、第２の実施形態では、外輪１１ｂ、１２ｂを、ケース部２２の軸線方向端面２２ａ、２２ｂの外側に延長させ、この延長部分に段差からなる流れ方向変更部４０を設けている。その他の構成は、第１の実施形態と同様であるので、詳細な説明は省略する。 In the bearing device 10 of the third embodiment, in the first embodiment, the flow direction changing portion 40 formed of a step formed on the inner diameter portion of the axial end faces 22a and 22b of the case portion 22 is replaced with the second embodiment. Then, the outer rings 11b and 12b are extended to the outside of the axial end faces 22a and 22b of the case portion 22, and a flow direction changing portion 40 having a step is provided in the extended portion. Since other configurations are the same as those of the first embodiment, detailed description thereof is omitted.
１　　　　：過給機
２　　　　：タービンロータ
３　　　　：コンプレッサインペラ
４　　　　：タービン軸
４ａ　　　：大径部
４ｂ　　　：中間部
４ｃ　　　：小径部
５　　　　：軸受ハウジング
５Ａ　　　：ハウジング本体
５Ｂ　　　：リテーナ
５ａ　　　：ホルダ収容部
５ｂ　　　：突起部
６　　　　：回転体アッセンブリ
７　　　　：軸受アッセンブリ
８　　　　：オイルフィルムダンパ
１０　　　：軸受装置
１１　　　：転がり軸受
１１ａ　　：内輪
１１ｂ　　：外輪
１１ｃ　　：ボール
１２　　　：転がり軸受
１２ａ　　：内輪
１２ｂ　　：外輪
１２ｃ　　：ボール
１３　　　：段差部
１４　　　：スリーブ
１５　　　：端面部
２０　　　：ホルダ
２２　　　：ケース部
２２ａ、２２ｂ　　：端面
２３　　　：スペーサ部
２５ａ　　：半径方向隙間
２５ｂ、２５ｃ　　：軸線方向隙間
４０　　　：流れ方向変更部
４１　　　：給油路
４２　　　：給油部
４３　　　：オイルジェット孔
４４　　　：リング部材
ＣＬ　　　：中心線 1: Supercharger 2: Turbine rotor 3: Compressor impeller 4: Turbine shaft 4a: Large diameter part 4b: Intermediate part 4c: Small diameter part 5: Bearing housing 5A: Housing body 5B: Retainer 5a: Holder accommodating part 5b: Protrusion part 6: Rotating body assembly 7: Bearing assembly 8: Oil film damper 10: Bearing device 11: Rolling bearing 11a: Inner ring 11b: Outer ring 11c: Ball 12: Rolling bearing 12a: Inner ring 12b: Outer ring 12c: Ball 13: Step 14: Sleeve 15: End surface portion 20: Holder 22: Case portions 22a, 22b: End surface 23: Spacer portion 25a: Radial clearance 25b, 25c: Axial clearance 40: Flow direction changing portion 41: Oil supply passage 42: Oil supply portion 43: Oil Jet hole 44 Ring member CL: centerline

Claims (4)

  1. 　過給機の回転軸上に配置される一対の転がり軸受と、前記一対の転がり軸受とは別部品として構成され、該一対の軸受の外輪のそれぞれが嵌め合わされる保持部材と、前記外輪を支持するオイルフィルムダンパが形成されるように前記保持部材と組み合わされる軸受ハウジングと、前記一対の軸受の内輪間に配置されて内輪間の軸線方向の距離を一定に保持する内輪スペーサと、前記外輪間に配置されて外輪間の軸線方向の距離を一定に保持する外輪スペーサとを具備し、前記外輪は、軸線方向外側へは非拘束の状態で前記保持部材に嵌め合わされ、前記保持部材の外周及び軸線方向両端面のそれぞれと前記軸受ハウジングとがオイルフィルムを形成するための隙間を介して対向し、オイルフィルムダンパに供給される潤滑油の排出経路が、前記転がり軸受を通過して軸線方向外側に排出される経路と、前記保持部材の軸線方向両端面から排出される経路とを有する、過給機の軸受装置において、前記保持部材の軸線方向両端面の経路から排出される潤滑油の流れ方向を、前記外輪の軸線方向外側に向かって変更する流れ方向変更部を、前記外輪の軸線方向外側に設けたことを特徴とする過給機の軸受装置。 A pair of rolling bearings disposed on the rotating shaft of the supercharger, a holding member that is configured as a separate part from the pair of rolling bearings, and in which the outer rings of the pair of bearings are fitted, and supports the outer ring A bearing housing combined with the holding member so as to form an oil film damper, an inner ring spacer disposed between the inner rings of the pair of bearings to maintain a constant axial distance between the inner rings, and between the outer rings And an outer ring spacer that maintains a constant axial distance between the outer rings, and the outer ring is fitted to the holding member in an unconstrained state outward in the axial direction, and the outer circumference of the holding member and Each of the axial end faces faces the bearing housing via a gap for forming an oil film, and a discharge path for lubricating oil supplied to the oil film damper is provided. In the bearing device for a supercharger, the axially opposite end surfaces of the holding member have a path that passes through the rolling bearing and is discharged outward in the axial direction, and a path that is discharged from the axially opposite end surfaces of the holding member. A turbocharger bearing device comprising: a flow direction changing portion for changing a flow direction of lubricating oil discharged from the path of the outer ring toward an outer side in the axial direction of the outer ring; .
  2. 　前記流れ方向変更部が、前記保持部材の軸線方向両端面に一体に形成された段差からなることを特徴とする請求項１記載の過給機の軸受装置。 2. The bearing device for a supercharger according to claim 1, wherein the flow direction changing portion comprises a step formed integrally on both end surfaces in the axial direction of the holding member.
  3. 　前記流れ方向変更部が、前記外輪の軸線方向外側面に設けられた、外輪と別体のリング部材からことを特徴とする請求項１記載の過給機の軸受装置。 The bearing device for a supercharger according to claim 1, wherein the flow direction changing portion is a ring member provided separately from the outer ring, provided on the outer surface in the axial direction of the outer ring.
  4. 　前記流れ方向変更部を、前記外輪の軸線方向外側面に一体に形成した段差からなることを特徴とする請求項１記載の過給機の軸受装置。 2. The bearing device for a supercharger according to claim 1, wherein the flow direction changing portion is formed by a step formed integrally with an outer surface in the axial direction of the outer ring.
PCT/JP2017/036058 2016-10-14 2017-10-04 Bearing device for supercharger WO2018070311A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-202395 2016-10-14
JP2016202395A JP2018063018A (en) 2016-10-14 2016-10-14 Bearing device of supercharger

Publications (1)

Publication Number Publication Date
WO2018070311A1 true WO2018070311A1 (en) 2018-04-19

Family

ID=61905673

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/036058 WO2018070311A1 (en) 2016-10-14 2017-10-04 Bearing device for supercharger

Country Status (2)

Country Link
JP (1) JP2018063018A (en)
WO (1) WO2018070311A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020170376A1 (en) * 2019-02-21 2020-08-27 三菱重工エンジン＆ターボチャージャ株式会社 Turbocharger
CN115103954A (en) * 2020-02-20 2022-09-23 三菱重工发动机和增压器株式会社 Turbocharger
CN117469194A (en) * 2023-12-28 2024-01-30 诺顿风机(潍坊)有限公司 Novel intelligent monitoring's special bearing box of axial fan
WO2024166345A1 (en) * 2023-02-10 2024-08-15 三菱重工エンジン＆ターボチャージャ株式会社 Rotary machine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009270613A (en) * 2008-05-07 2009-11-19 Toyota Motor Corp Bearing structure of turbocharger
JP2013217436A (en) * 2012-04-09 2013-10-24 Jtekt Corp Rolling bearing device for turbocharger
JP2014043920A (en) * 2012-08-28 2014-03-13 Jtekt Corp Rolling bearing device for turbocharger
JP2015081542A (en) * 2013-10-22 2015-04-27 Ntn株式会社 Turbocharger bearing device and turbocharger bearing device manufacturing method
US20150233382A1 (en) * 2011-08-18 2015-08-20 Thanh-Hung Nguyen-Schaefer Rolling bearing assembly of an exhaust gas turbocharger

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009270613A (en) * 2008-05-07 2009-11-19 Toyota Motor Corp Bearing structure of turbocharger
US20150233382A1 (en) * 2011-08-18 2015-08-20 Thanh-Hung Nguyen-Schaefer Rolling bearing assembly of an exhaust gas turbocharger
JP2013217436A (en) * 2012-04-09 2013-10-24 Jtekt Corp Rolling bearing device for turbocharger
JP2014043920A (en) * 2012-08-28 2014-03-13 Jtekt Corp Rolling bearing device for turbocharger
JP2015081542A (en) * 2013-10-22 2015-04-27 Ntn株式会社 Turbocharger bearing device and turbocharger bearing device manufacturing method

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020170376A1 (en) * 2019-02-21 2020-08-27 三菱重工エンジン＆ターボチャージャ株式会社 Turbocharger
CN113423963A (en) * 2019-02-21 2021-09-21 三菱重工发动机和增压器株式会社 Turbocharger
CN115103954A (en) * 2020-02-20 2022-09-23 三菱重工发动机和增压器株式会社 Turbocharger
US20230053136A1 (en) * 2020-02-20 2023-02-16 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbocharger
CN115103954B (en) * 2020-02-20 2024-02-09 三菱重工发动机和增压器株式会社 Turbocharger with a variable-speed control valve
US11982199B2 (en) * 2020-02-20 2024-05-14 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Turbocharger
WO2024166345A1 (en) * 2023-02-10 2024-08-15 三菱重工エンジン＆ターボチャージャ株式会社 Rotary machine
CN117469194A (en) * 2023-12-28 2024-01-30 诺顿风机(潍坊)有限公司 Novel intelligent monitoring's special bearing box of axial fan
CN117469194B (en) * 2023-12-28 2024-03-08 诺顿风机(潍坊)有限公司 Bearing box special for intelligent monitoring axial flow fan

Also Published As

Publication number Publication date
JP2018063018A (en) 2018-04-19

Similar Documents

Publication Publication Date Title
JP5075000B2 (en) Supercharger bearing device
CN104220706B (en) Bearing unit of turbocharger
WO2018070311A1 (en) Bearing device for supercharger
US9784315B2 (en) Bearing assembly for a turbocharger, and a method for manufacturing a bearing assembly for a turbocharger
US20090196743A1 (en) Turbocharger
JP5071150B2 (en) Bearing device for turbocharger
JPH1054208A (en) Bearing support member for high speed rotation
WO2006088144A1 (en) Shaft device
WO2011055630A1 (en) Camshaft apparatus
US7828485B2 (en) Roller bearing
JP2010138753A (en) Bearing device for supercharger
JP2005172099A (en) Turbocharger bearing device
KR20020015302A (en) Turbocharger rotor with low-cost ball bearing
JP2010133266A (en) Bearing device for supercharger
JP7050818B2 (en) Plain bearings with hydrodynamic axial fixing means
JP2009203846A (en) Ball bearing arrangement for turbocharger
JP2018123780A (en) Bearing device for turbocharger
JPH0710037Y2 (en) Supercharger bearing device
JP2006226184A (en) Camshaft device and its assembling method
JP2008232311A (en) Roller bearing
US12146523B2 (en) Tilting pad bearing
JP2014105732A (en) Rolling bearing
US20230184287A1 (en) Tilting pad bearing
WO2022209417A1 (en) Ball bearing
JP2007327609A (en) Divided type roller bearing

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17861040

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17861040

Country of ref document: EP

Kind code of ref document: A1