WO2023090208A1 - Roulement à rouleaux coniques - Google Patents

Roulement à rouleaux coniques Download PDF

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Publication number
WO2023090208A1
WO2023090208A1 PCT/JP2022/041610 JP2022041610W WO2023090208A1 WO 2023090208 A1 WO2023090208 A1 WO 2023090208A1 JP 2022041610 W JP2022041610 W JP 2022041610W WO 2023090208 A1 WO2023090208 A1 WO 2023090208A1
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WO
WIPO (PCT)
Prior art keywords
tapered roller
oil
diameter side
roller bearing
wall surface
Prior art date
Application number
PCT/JP2022/041610
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English (en)
Japanese (ja)
Inventor
誠 前佛
啓陽 山中
Original Assignee
日本精工株式会社
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
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Publication of WO2023090208A1 publication Critical patent/WO2023090208A1/fr

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    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • 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
    • F16C33/46—Cages for rollers or needles
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N31/00—Means for collecting, retaining, or draining-off lubricant in or on machines or apparatus
    • 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
    • F16N—LUBRICATING
    • F16N9/00—Arrangements for supplying oil or unspecified lubricant from a moving reservoir or the equivalent
    • F16N9/02—Arrangements for supplying oil or unspecified lubricant from a moving reservoir or the equivalent with reservoir on or in a rotary member

Definitions

  • the present invention relates to a tapered roller bearing, and more particularly to a tapered roller bearing in which lubricating oil is supplied inside the bearing.
  • hybrid vehicles have a mode in which the electric motor is used while the engine is stopped.
  • this mode in a structure with only a lubricating oil pump directly connected to the engine, the vehicle runs without lubricating oil to the bearings.
  • the vehicle runs without oil for several minutes, but the bearing must not seize during this period.
  • the centrifugal force CF acts on the retainer 114 during rotation of the bearing, making it difficult for the lubricating oil L to reach the acute-angled portion 125 formed at the shaft end on the inner peripheral side.
  • the lubricating oil L added to the oil groove 120 remains at the bottom of the groove, and there is a possibility that the lubricating oil L cannot be supplied to the large-diameter side end faces 113b of the tapered rollers 113 .
  • the entire oil retaining groove does not face the large-diameter end face of the tapered roller, and when the bearing is rotated at high speed, it faces the large-diameter end face.
  • Lubricating oil may splash due to centrifugal force from the circumferential ends of the oil retaining grooves that are not in contact with each other.
  • the present invention has been made in view of the problems described above, and an object of the present invention is to retain lubricating oil or grease in oil retaining grooves and to supply the oil or grease to the large-diameter side end faces of tapered rollers.
  • an object of the present invention is to retain lubricating oil or grease in oil retaining grooves and to supply the oil or grease to the large-diameter side end faces of tapered rollers.
  • the retainer includes a large-diameter side annular portion, a small-diameter side annular portion arranged coaxially with the large-diameter side annular portion, and the large-diameter side annular portion and the small-diameter side annular portion.
  • An oil retaining groove for retaining the lubricating oil or grease is formed in at least the axial inner end surface of the large diameter side annular portion so as to extend along the circumferential direction,
  • the oil retaining groove has a shape such that both ends in the circumferential direction of the oil retaining groove overlap the large-diameter side end surfaces of the tapered roller when viewed from the longitudinal direction of the tapered roller, At least one of both circumferential end portions of the oil retaining groove, which can contact the large-diameter side end surface of the tapered roller, is located at the boundary between the outer circumferential wall surface and the circumferential wall surface of the oil retaining groove.
  • a tangent line at the boundary portion and a tangent line at the circumferential wall surface or the boundary portion thereof form an acute angle, Tapered roller bearing.
  • the oil retention grooves are provided on at least the axial inner end surface of the large-diameter side annular portion, the outer peripheral side wall surface, the inner peripheral side wall surface, and a pair of connecting the outer peripheral side wall surface and the inner peripheral side wall surface, respectively. comprising the circumferential wall surface, A tapered roller bearing according to (1).
  • the radial width of the oil retaining groove is 0.35 mm or less.
  • a plurality of the oil retaining grooves extending along the circumferential direction are formed in the axial inner end surface of the large-diameter side annular portion so as to be aligned in the radial direction.
  • the plurality of oil retention grooves are connected at a circumferential intermediate portion,
  • the oil retaining groove is formed from the axially inner end surface to the inner peripheral surface of the large diameter side annular portion.
  • the retainer is made of resin.
  • Lubricating oil is intermittently supplied to the inside of the bearing, or used in a lubricating environment where the amount of lubricating oil inside the bearing is very small.
  • lubricating oil or grease can be retained in the oil retaining grooves, and lubricating oil or grease can be supplied to the large-diameter side end face of the tapered rollers. Damage such as seizure and galling can be suppressed even when the oil supply is stopped.
  • FIG. 2 is a perspective view of the retainer shown in FIG. 1 as viewed from the longitudinal direction of tapered rollers;
  • FIG. 2 is a partial cross-sectional view showing a state in which the retainer shown in FIG. 1 is in contact with the large-diameter side end surfaces of tapered rollers and a centrifugal force is generated due to rotation of the retainer;
  • FIG. 11 is a perspective view of a retainer according to a first modified example of the present invention as seen from the longitudinal direction of tapered rollers;
  • FIG. 11 is a perspective view of a retainer according to a second modification of the present invention, viewed from the longitudinal direction of tapered rollers;
  • FIG. 11 is a perspective view of a retainer according to a third modified example of the present invention as seen from the longitudinal direction of tapered rollers;
  • FIG. 11 is a perspective view of a retainer according to a fourth modified example of the present invention as seen from the longitudinal direction of tapered rollers;
  • FIG. 11 is a perspective view of a retainer according to a fifth modified example of the present invention as viewed from the longitudinal direction of tapered rollers;
  • FIG. 11 is a perspective view of a retainer according to a sixth modification of the present invention, viewed from the longitudinal direction of tapered rollers;
  • FIG. 11 is a perspective view of a retainer according to a second modification of the present invention, viewed from the longitudinal direction of tapered rollers;
  • FIG. 11 is a perspective view of a retainer according to a third modified example of the present invention as
  • FIG. 4 is a cross-sectional view for explaining oil supply to bearings by a lubricating oil pump
  • FIG. 5 is a cross-sectional view for explaining oil supply to a bearing by splashing of a gear
  • It is the perspective view which looked at the conventional retainer from the diameter direction inner side.
  • FIG. 13 is a partial cross-sectional view showing a state in which the cage shown in FIG. 12 is in contact with the large-diameter side end surfaces of the tapered rollers and a centrifugal force is generated due to the rotation of the cage;
  • the tapered roller bearing 10 of this embodiment includes an outer ring 11 having an outer ring raceway surface 11a on its inner peripheral surface, an inner ring 12 having an inner ring raceway surface 12a on its outer peripheral surface, an outer ring raceway surface 11a and an inner ring. It includes a plurality of tapered rollers 13 that are rotatably provided between them and the raceway surface 12a, and a retainer 14 that holds the plurality of tapered rollers 13 at substantially equal intervals in the circumferential direction.
  • lubricating oil is appropriately supplied to the inside of the bearing by a lubricating oil pump P (see FIG. 10) or the like.
  • the inner ring 12 has a large flange portion 12b provided at the large diameter side end of the inner ring 12 and a small flange portion 12c provided at the small diameter side end of the inner ring 12.
  • the outer peripheral surface of the inner ring 12 is formed in a substantially conical shape.
  • the tapered rollers 13 have a rolling surface 13a provided on the peripheral surface of the tapered roller 13, a large diameter side end surface 13b provided on the large diameter side end of the tapered roller 13, and a small diameter side end of the tapered roller 13. and a small diameter side end face 13c provided.
  • the retainer 14 includes a large diameter side annular portion 14a, a small diameter side annular portion 14c arranged coaxially with the large diameter side annular portion 14a, and the large diameter side annular portion 14a and the small diameter side annular portion 14c. and a plurality of pillars 14e (see FIG. 2) that are connected in the axial direction and provided at substantially equal intervals in the circumferential direction.
  • a space surrounded by the large-diameter annular portion 14a and the small-diameter annular portion 14c forms a pocket 14f between the pillars 14e adjacent to each other in the circumferential direction, and holds the tapered rollers 13 rollably. .
  • the axial inner end surface 14b of the large-diameter annular portion 14a and the axial inner end surface 14d of the small-diameter annular portion 14c are parallel to the large-diameter end surface 13b and the small-diameter end surface 13c of the tapered rollers 13, respectively. and perpendicular to the central axis C of the tapered rollers 13 .
  • the retainer 14 can move relative to the tapered roller 13 within a predetermined range along the axial direction.
  • the gap between the axial inner end surface 14b of the large-diameter annular portion 14a of the retainer 14 and the large-diameter end surface 13b of the tapered roller 13 is
  • the tapered rollers 13 are designed so that the large-diameter end faces 13b of the tapered rollers 13 cover the later-described oil retention grooves 20 of the retainer 14 so that the oil or grease retained in the oil retention grooves 20 does not scatter.
  • the axial inner end surface 14b of the large-diameter side annular portion 14a of the retainer 14 is provided with an oil retaining groove 20 for retaining the lubricating oil L by grooving or the like in the circumferential direction. formed to extend along the
  • the oil retention groove 20 includes an arc-shaped outer peripheral side wall surface 21, an arc-shaped inner peripheral side wall surface 22, and a pair of straight circumferential wall surfaces 23 connecting the outer peripheral side wall surface 21 and the inner peripheral side wall surface 22, respectively.
  • 23 is a bottomed groove.
  • the outer peripheral side wall surface 21, the inner peripheral side wall surface 22, and the circumferential wall surfaces 23, 23 each extend axially from the axial inner end surface 14b.
  • both ends of the oil retaining groove 20 in the circumferential direction correspond to the large-diameter side end surfaces of the tapered rollers 13 . It has a shape and length overlapping with 13b. Therefore, the entire oil retaining groove 20 is covered with the large-diameter side end surface 13b of the tapered roller 13, and the lubricating oil retained in the oil retaining groove 20 scatters regardless of whether the tapered roller bearing 10 is in a stationary state or a rotating state. can be prevented.
  • both circumferential ends of the oil retaining groove 20, which can contact the large-diameter end faces 13b of the tapered rollers 13, are located at the outer boundary 24 between the outer circumferential wall face 21 and the circumferential wall face 23.
  • a tangential line 21a at a boundary portion 24 of the rim and the circumferential wall surface 23 form an acute angle ⁇ .
  • the lubricating oil L can be retained by the capillary force at the boundary portion 24 between the outer peripheral side wall surface 21 and the circumferential wall surface 23 of the oil retaining groove 20, and the oil retaining ability of the retainer 14 can be enhanced.
  • the axial inner end surface 14b of the large diameter annular portion 14a and the large diameter end surface 13b of the tapered roller 13 can contact each other.
  • the axial inner end surface 14b of the large-diameter annular portion 14a and the large-diameter end surface 13b of the tapered roller 13 come into contact with each other at the circumferential end portion of the oil retaining groove 20, oil is trapped inside the groove 20 by capillary force.
  • the stored lubricating oil can be supplied to the large-diameter side end face 13b of the tapered roller 13 by the action of capillary force with the roller surface.
  • the capillary force mentioned in this explanation is the force by which a solid tries to attract a liquid.
  • Capillary forces occur when the surface tension of the solid (retainer) is greater than the surface tension of the liquid (lubricant) and the liquid is attracted to the solid surface.
  • Liquids also try to reduce the surface area in contact with air due to surface tension. That is, the lubricating oil tries to increase the area in contact with the cage while reducing the area in contact with the air. Therefore, the oil retaining groove 20 of the retainer has a high capillary force at the fine and narrow boundary portion 24 .
  • the centrifugal force acting on the cage 14 due to the rotation of the cage 14 makes it easier for the lubricating oil L to reach the boundary 24 on the outer peripheral side formed at the acute angle ⁇ , and the lubricating oil L flows inward in the axial direction due to capillary force.
  • Oil is drawn to the end face 14b and can be lubricated by capillary force to the large-diameter side end face 13b of the tapered roller 13, which is in contact with the axial inner end face 14b.
  • the acute angle ⁇ may be less than 90°, but is preferably 70° or less, more preferably 60° or less, in order to exert the capillary force more effectively.
  • the material of the retainer 14 is not particularly limited, but a synthetic resin material having high surface tension against the lubricating oil used and lipophilicity that produces a capillary force is preferable. cage resin material.
  • the synthetic resin of the retainer 14 may contain fibers as a reinforcing agent. A resin material having low lipophilicity can also be used, but in this case, it is preferable to apply lipophilic treatment.
  • the depth of the oil retaining groove 20 is arbitrarily designed in consideration of the oil retaining property of the lubricating oil, the strength of the retainer 14, the accuracy of general injection molding, and the like.
  • the oil retention groove 20 formed by axial draw extends in the same direction (axial direction) as the central axis of the retainer 14, which is the direction in which the mold moves (releases) during injection molding. .
  • the retainer 14 has the oil retaining groove 20 for retaining lubricating oil formed in the axial inner end surface 14b of the large diameter side annular portion 14a.
  • the oil retaining groove 20 is formed so as to extend along the circumferential direction, and when viewed from the longitudinal direction of the tapered roller 13 , both circumferential ends of the oil retaining groove 20 overlap the large-diameter side end surfaces 13 b of the tapered roller 13 .
  • the lubricating oil L can be retained in the oil retaining grooves 20, and the lubricating oil L can be supplied to the large-diameter side end surfaces 13b of the tapered rollers 13, so that the lubricating oil L can be lubricated in a poor lubrication environment or when the lubrication is temporarily stopped. It is possible to suppress damage such as seizing and galling even in a state.
  • the amount of lubricating oil can be greatly reduced, so the stirring resistance of the lubricating oil can be reduced.
  • a structure see FIG. 11
  • the tapered roller bearing 10 of the present embodiment can be suitably used for a mechanism that temporarily stops the lubricating oil pump when the engine is stopped, such as the transmission of some hybrid vehicles. This makes it possible to cope with situations such as when the lubricating oil pump does not operate when the vehicle is being towed, making it difficult to supply a sufficient amount of lubricating oil.
  • FIG. 4 is a perspective view of a retainer 14A according to a first modified example of the present invention, viewed from the longitudinal direction of tapered rollers.
  • the retainers 14A to 14F shown in FIGS. 4 to 9 are different in the shape of the oil retaining grooves 20a to 20f from those of the retainer 14 shown in FIG. .
  • one end in the circumferential direction of the oil retaining groove 20a, which can contact the large-diameter end face 13b of the tapered rollers 13, forms an acute angle ⁇ is formed to form
  • the other circumferential end of the oil retaining groove 20a is formed to form an acute angle at the boundary 25 between the inner peripheral wall surface 22 and the circumferential wall surface 23 .
  • the centrifugal force acting on the retainer 14A causes the lubricating oil L to be stored in the boundary portion 24 on the outer peripheral side of one end of the oil retention groove 20a in the circumferential direction, and the boundary portion 24 forms an acute angle ⁇ so that the capillary Oil is drawn to the axial inner end surface 14b by the force, and the large-diameter end surface 13b of the tapered roller 13, which is in contact with the axial inner end surface 14b, can be lubricated by capillary force.
  • FIG. 5 is a perspective view of a retainer 14B according to a second modification of the invention, viewed from the longitudinal direction of the tapered rollers.
  • the oil retaining groove 20b connects the boundary portion between the inner peripheral side wall surface 22 and the circumferential wall surface 23 smoothly by a curved line without corners.
  • the lubricating oil L adhering to the inner peripheral wall surface 22 is easily moved to the boundary portion 24 via the circumferential wall surface 23 by the centrifugal force acting on the retainer 14B.
  • lubricating oil L is stored in the boundary portions 24 between the outer peripheral side wall surface 21 and the circumferential wall surface 23 at both circumferential end portions of the oil retention groove 20b.
  • the oil is drawn to the axial inner end surface 14b by capillary force, and the large-diameter end surface 13b of the tapered roller 13 in contact with the axial inner end surface 14b can be lubricated by the capillary force.
  • FIG. 6 is a perspective view of a retainer 14C according to a third modification of the present invention, viewed from the longitudinal direction of the tapered rollers.
  • the radial width W of the oil retaining groove 20c (the width in the direction orthogonal to the extending direction of the oil retaining groove 20) extends in the circumferential direction due to the outer peripheral side wall surface 21 and the inner peripheral side wall surface 22.
  • the oil retaining groove 20c is narrower than the oil retaining groove 20 of FIG. 2 and has an elongated shape along the circumferential direction.
  • the boundary portion 24 is formed at an acute angle.
  • ⁇ oil is drawn to the axial inner end surface 14b by capillary force, and the large diameter side end surface 13b of the tapered roller 13 in contact with the axial inner end surface 14b can be lubricated by the capillary force.
  • the radial width W of the oil retaining groove 20c is sufficient as long as it can exert a capillary force that prevents the lubricating oil L from leaking out of the oil retaining groove 20c due to centrifugal force due to rotation.
  • the design of the radial width W of the oil-retaining groove 20c is affected by the peripheral speed acting on the oil-retaining groove 20c, the interfacial tension due to physical properties, and the viscosity of the lubricating oil L. In the case of automobile applications with a rotation speed of about 4,000 rpm, the radial width W must be 0.35 mm or less to prevent the lubricant L from leaking out.
  • lubricating oil with low viscosity (approximately 20 cSt) has been used in some applications for the purpose of improving fuel efficiency. Further, in order to further reduce the viscosity (about 10 cSt) and increase the speed in the future, setting the radial width W to 0.15 mm or less can be applied to most applications.
  • FIG. 7 is a perspective view of a retainer 14D according to a fourth modification of the present invention, viewed from the longitudinal direction of the tapered rollers.
  • this retainer 14D a plurality (in this embodiment, two) of oil retaining grooves 20d1 and 20d2 extending along the circumferential direction are formed in the axial direction inner end face 14b of the large diameter side annular portion 14a in parallel with each other. are formed in the same direction.
  • the oil retaining grooves 20d1 and 20d2 are designed to have a radial width large enough to exert a capillary force that prevents the lubricant L from leaking from the oil retaining groove 20c due to centrifugal force due to rotation. ing.
  • the oil retaining volume can be increased compared to the third modification.
  • the boundary portion 24 forming the acute angle ⁇ that allows oil to be supplied to the large-diameter end face 13b of the tapered roller 13 can be increased compared to the third modification, and the lubrication performance can be further improved.
  • the oil retaining groove 20d1 on the outer peripheral side is formed longer than the oil retaining groove 20d2 on the inner peripheral side.
  • FIG. 8 is a perspective view of a retainer 14E according to a fifth modification of the present invention, viewed from the longitudinal direction of the tapered rollers.
  • this retainer 14E two oil retaining grooves 20e1 and 20e2 formed side by side in the axial direction on the axial inner end surface 14b of the large diameter side annular portion 14a are connected at a circumferential intermediate portion by an oil retaining groove 20e3. It is As a result, even if the amount of the lubricating oil L is uneven in the oil retaining grooves 20e1 and 20e2, the lubricating oil L can flow between the oil retaining grooves 20e1 and 20e2, thereby improving the efficiency of oil retention and oil supply. be able to.
  • FIG. 9 is a perspective view of a retainer 14F according to a sixth modification of the invention, viewed from the longitudinal direction of the tapered rollers.
  • the oil retaining groove 20f is formed from the axial inner end surface 14b of the large diameter side annular portion 14a to the inner peripheral surface 14g.
  • the oil retaining groove 20f can be supplemented with oil during rotation, and the amount of lubricating oil L in the oil retaining groove 20f can be increased.
  • FIG. 1 A structure in which an oil supply passage R communicating with the tapered roller bearing 10 is provided in H and a lubricating oil pump P is connected to the oil supply passage R is generally known.
  • the lubricating oil pressure-fed from the lubricating oil pump P is supplied to the tapered roller bearing 10 through the oil supply passage R.
  • the outer ring 11 of the tapered roller bearing 10 is fitted inside the housing H, and the inner ring 12 is fitted around the rotating shaft A.
  • a structure in which a gear G is provided adjacent to an inner ring 12 on an axis A is generally known. In the case of this structure, lubricating oil adhering to the gear G scatters due to the centrifugal force associated with shaft rotation, and the splattered lubricating oil adheres to the tapered roller bearing 10 and is supplied.
  • lubricating oil is supplied at a rate of about 50cc/min to 1000cc/min in order to prevent seizure of the bearing.
  • the amount of lubricating oil is less than 10 cc/min, heat generation and seizure tend to occur due to insufficient oil film due to insufficient lubricating oil, and seizure occurs at 0 cc/min (no lubrication).
  • the present invention deals with a thin lubrication state rather than a non-lubricating state, and a large effect is obtained in a lubricating environment in which the amount of lubricating oil is very small, specifically in a thin lubrication state of about 0.01 cc / min to 10 cc / min. demonstrate.
  • the lubricating oil stored in the oil retaining groove can be used in the present invention. Since the bearing can be lubricated until it runs out of lubricating oil, seizure resistance can be greatly improved.
  • the present invention is not limited to the examples illustrated in the above embodiments, and can be modified as appropriate without departing from the gist of the present invention.
  • the tapered roller bearing is lubricated with lubricating oil, but the present invention can also be applied when the tapered roller bearing is lubricated with grease.
  • the oil retaining groove of the present invention does not necessarily have to be entirely covered with the large-diameter side end faces of the tapered rollers.
  • the entire oil retention groove with the large-diameter side end face of the tapered roller, it is also possible to have a scattering prevention effect.
  • the outer peripheral side wall surface and the inner peripheral side wall surface of the oil retaining groove are formed in a curved shape along the shape of the axial inner end surface of the large diameter side annular portion.
  • the outer peripheral side wall surface and the inner peripheral side wall surface of the oil groove may be formed linearly.
  • the circumferential wall surface of the oil retaining groove may be formed linearly or curvedly. That is, in the present invention, at the boundary between the outer peripheral wall surface and the circumferential wall surface of the oil retaining groove, the tangent to the outer peripheral wall surface or the boundary thereof forms an acute angle with the tangent to the circumferential wall surface or the boundary. Any configuration may be used as long as it is formed.
  • tapered roller bearing 11 outer ring 11a outer ring raceway surface 12 inner ring 12a inner ring raceway surface 12b large flange portion 12c small flange portion 13 tapered roller 13a rolling surface 13b large diameter side end face 13c small diameter side end face 14, 14A, 14B, 14C, 14D, 14E, 14F retainer 14a large diameter annular portion 14b axial inner end surface 14c small diameter annular portion 14d axial inner end surface 14e column portion 14f pocket 14g inner peripheral surface 20, 20a, 20b, 20c, 20d1, 20d2, 20e1 , 20e2, 20f Plural grooves (oil holding portion) 21 outer peripheral side wall surface 22 inner peripheral side wall surface 23 circumferential wall surface 24 boundary portion L lubricating oil

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un roulement à rouleaux coniques, un élément de retenue ayant une partie annulaire côté grand diamètre, une partie annulaire côté petit diamètre et une pluralité de parties en colonne qui relient la partie annulaire côté grand diamètre et la partie annulaire côté petit diamètre dans la direction axiale. Au moins dans la surface d'extrémité interne axiale de la partie annulaire côté grand diamètre, une rainure de retenue d'huile est formée le long de la direction circonférentielle. Au moins une des parties d'extrémité circonférentielles de la rainure de retenue d'huile, qui peut entrer en contact avec la surface d'extrémité côté grand diamètre d'un rouleau conique, est formée de telle sorte que, au niveau de la partie limite entre la surface de paroi côté circonférence extérieure et la surface de paroi circonférentielle de la rainure de retenue d'huile, un angle aigu soit formé entre la surface de paroi côté circonférence extérieure ou une tangente au niveau de la partie limite de celle-ci et la surface de paroi circonférentielle ou une tangente au niveau de la partie limite de celle-ci.
PCT/JP2022/041610 2021-11-17 2022-11-08 Roulement à rouleaux coniques WO2023090208A1 (fr)

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JP2021187277A JP2023074356A (ja) 2021-11-17 2021-11-17 円すいころ軸受
JP2021-187277 2021-11-17

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021025656A (ja) * 2019-07-31 2021-02-22 Ntn株式会社 円すいころ軸受
JP2021032353A (ja) * 2019-08-26 2021-03-01 日本精工株式会社 円すいころ軸受
JP2021032360A (ja) * 2019-08-26 2021-03-01 日本精工株式会社 ラジアル型ころ軸受
JP2021060071A (ja) * 2019-10-04 2021-04-15 日本精工株式会社 円すいころ軸受

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2021025656A (ja) * 2019-07-31 2021-02-22 Ntn株式会社 円すいころ軸受
JP2021032353A (ja) * 2019-08-26 2021-03-01 日本精工株式会社 円すいころ軸受
JP2021032360A (ja) * 2019-08-26 2021-03-01 日本精工株式会社 ラジアル型ころ軸受
JP2021060071A (ja) * 2019-10-04 2021-04-15 日本精工株式会社 円すいころ軸受

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