WO2024111363A1 - Palier à rouleaux - Google Patents

Palier à rouleaux Download PDF

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Publication number
WO2024111363A1
WO2024111363A1 PCT/JP2023/039156 JP2023039156W WO2024111363A1 WO 2024111363 A1 WO2024111363 A1 WO 2024111363A1 JP 2023039156 W JP2023039156 W JP 2023039156W WO 2024111363 A1 WO2024111363 A1 WO 2024111363A1
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WO
WIPO (PCT)
Prior art keywords
inner ring
region
diameter side
arc
roller bearing
Prior art date
Application number
PCT/JP2023/039156
Other languages
English (en)
Japanese (ja)
Inventor
翔吾 福留
径生 堀
雄太 西田
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 WO2024111363A1 publication Critical patent/WO2024111363A1/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
    • F16C33/50—Cages for rollers or needles formed of interconnected members, e.g. chains
    • 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
    • F16C33/51—Cages for rollers or needles formed of unconnected members
    • 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
    • F16C33/56—Selection of substances

Definitions

  • the present invention relates to a roller bearing.
  • tapered roller bearing 100 is composed of inner ring 101, outer ring 102 arranged concentrically around the inner ring, tapered rollers 103 arranged between inner ring 101 and outer ring 102, and retainer 104 that holds tapered rollers 103 at regular intervals in the circumferential direction.
  • Tapered roller bearing 100 is assembled by assembling inner ring 101, tapered rollers 103, and retainer 104 together to form what is called an inner ring assembly, and then assembling outer ring 102 into the inner ring assembly.
  • the retainer 104 of the tapered roller bearing 100 is generally made of steel plate.
  • the tapered rollers 103 are also large and many are used, so the steel plate retainer 104 may deform due to its own weight or the weight of the tapered rollers 103 it holds.
  • the steel plate retainer 104 is usually manufactured by pressing, but when it becomes a large one with an outer diameter exceeding 1 m, processing becomes difficult due to equipment problems.
  • the strength of the steel plate retainer 104 can be ensured by increasing its plate thickness, generally, large parts are difficult to press due to problems in manufacturing equipment, and there is a limit to the plate thickness that can be pressed due to processing constraints.
  • the retainer 104 is manufactured by cutting, the cost increases significantly compared to a pressed product, and there is also a lot of material waste.
  • segment cage in which the cage 104 is divided into multiple segments 104A as shown in FIG. 25, and the segments 104A are assembled in an annular shape
  • the segments 104A are mainly made of resin.
  • Conventional segment cages assembled with segments 104A use a rolling element guide system, and are configured such that pockets with outer diameter side guide claws 105 that contact the tapered rollers 103 on the outer diameter side and pockets with inner diameter side guide claws 106 that contact the tapered rollers 103 on the inner diameter side are arranged alternately in the circumferential direction, and the tapered rollers 103 are inserted into the pockets of the segments 104A from the inner diameter side and the outer diameter side.
  • the cage When trying to ensure the rigidity required to ensure the strength of a segment cage, the cage will occupy a larger space inside the bearing. This reduces the fluidity of the grease between the rollers and the inner surface of the cage pocket, making it difficult to maintain good lubrication. In addition, the weight of the cage increases, and the impact and inertial forces applied to the cage during bearing operation increase, causing abnormal noise and vibration. To increase strength, it is preferable to use a material such as PEEK as the material for the segment cage, but PEEK is expensive, so it is necessary to reduce the weight used in order to reduce manufacturing costs.
  • the present invention aims to provide a roller bearing that combines lubrication in the pockets with cage strength.
  • the present invention provides a roller bearing comprising an inner ring having a raceway surface, an outer ring having a raceway surface, a plurality of rollers interposed between the raceway surface of the inner ring and the raceway surface of the outer ring, and a cage having a plurality of pockets for accommodating the rollers, the cage being formed by arranging a plurality of resin segments in the circumferential direction of the bearing, the segment integrally comprising a first arc-shaped portion extending in the circumferential direction of the bearing, a second arc-shaped portion spaced apart from the first arc-shaped portion in the axial direction of the rollers and extending in the circumferential direction of the bearing, and a plurality of columnar portions interposed between the first arc-shaped portion and the second arc-shaped portion, the pocket being a space surrounded by the first arc-shaped portion, the second arc-shaped portion, and two adjacent columnar portions, the columnar portions forming the pocket being provided with claw portions on the outer diameter
  • the second column section's contribution to the strength of the segment is small. Therefore, by providing a recess on the inner diameter surface of the second column section, the strength required for the segment can be ensured even if the second column section is thinned.
  • providing a recess increases the flow of grease (particularly in the circumferential direction of the bearing), which improves lubrication between the inner surface of the pocket and the rollers. This makes it possible to achieve both lubrication in the pocket and strength of the cage.
  • the weight of the segment can be reduced, which reduces the impact force and inertia force applied to the cage during bearing operation and reduces the frequency of abnormal noise and vibration.
  • the two regions of the first arc-shaped portion that face the column portions at both circumferential ends of the bearing are defined as a first region, and the region located between the two first regions is defined as a second region, and a thin-walled portion that has a smaller radial thickness than the first region can be provided in the second region.
  • the first arc-shaped portion By providing a thin-walled portion in this way in the first arc-shaped portion, it is possible to increase the flowability of grease (particularly the flowability in the axial direction of the rollers). This makes it possible to further improve lubrication in the pockets. It also makes it possible to further reduce the weight of the segments. Because the second region, which has a thin-walled portion, makes a small contribution to the strength of the segment, it is possible to avoid a decrease in the strength of the segment even if a thin-walled portion is provided. This makes it possible to achieve both lubrication in the pockets and strength of the cage.
  • the two regions of the second arc-shaped portion that face the columnar portions at both circumferential ends of the bearing may be defined as a third region, and the region located between the two third regions may be defined as a fourth region, and a thin-walled portion having a smaller radial thickness than the third region may be provided in the fourth region.
  • the two regions of the first arc-shaped portion that face the columnar portions at both circumferential ends of the bearing can be defined as a first region, and the region located between the two first regions can be defined as a second region, with a thin-walled portion having a smaller radial thickness than the first region being provided in the second region, and the two regions of the second arc-shaped portion that face the columnar portions at both circumferential ends of the bearing can be defined as a third region, and the region located between the two third regions can be defined as a fourth region, with a thin-walled portion having a smaller radial thickness than the third region being provided in the fourth region.
  • the resin that forms the segments can be polyetheretherketone mixed with carbon fiber or polyetheretherketone mixed with glass fiber.
  • the rollers are tapered rollers
  • the first arc-shaped portion is a small diameter side arc-shaped portion
  • the second arc-shaped portion is a large diameter side arc-shaped portion with a larger radius of curvature than the small diameter side arc-shaped portion
  • the segments can be provided with engaging portions that can engage with a flexible connecting member that extends circumferentially around the bearing.
  • the engagement portion can be provided on the large diameter side surface of the large diameter arc portion of each segment.
  • a protrusion having the engagement portion can be provided on both ends of the large diameter side surface of the large diameter arc-shaped portion of the segment.
  • a wing portion that protrudes toward the small diameter side can be provided on the small diameter side surface of the small diameter side arc-shaped portion.
  • the angle between the large rib portion of the inner ring, which contacts the large diameter end face of the tapered roller, and a line perpendicular to the central axis of the inner ring, is I
  • the chamfer width of the tip of the large rib portion is H
  • the distance from the central axis of the inner ring to the center of gravity of the tapered roller is y1
  • the diameter of the large rib portion is J
  • the diameter of the large rib portion should satisfy the following condition. (J/2)-H cos I>y1
  • the diameter of the small rib portion of the inner ring is M
  • the angle between the small rib portion of the inner ring that contacts the small diameter end face of the tapered roller and a line perpendicular to the central axis of the inner ring is L
  • the chamfer width of the tip of the small rib portion is K
  • the tapered roller is rotated around the tip of the large rib portion of the inner ring, the distance from contact point C where the side of the small rib portion and the small diameter end face of the tapered roller come into contact with the central axis is y3, the height of the small rib portion should satisfy the following condition. (M/2)-K cos L>y3
  • the roller bearing described above can be used in wind power generation equipment.
  • the outer diameter of the roller bearing is 1m or more.
  • the ends of the connecting members may be connected to each other by fastening parts provided on the connecting members themselves, or by fastening members such as turnbuckles or cable ties.
  • each annularly arranged segment When connecting the large diameter sides of each annularly arranged segment with a connecting member, it is preferable to fit an annular jig into the wing portion on the small diameter side of each annularly arranged segment.
  • the annular jig can be removed before the inner ring assembly, which integrates the inner ring, tapered rollers, and cage, is assembled into the outer ring.
  • the connecting member can be removed after the inner ring assembly is assembled into the outer ring.
  • the connecting member may be divided into a plurality of pieces, and the ends of each divided connecting member may be connected to each other by the fastening portion or fastening member.
  • the multiple fastening portions or fastening members are preferably arranged equally in a circular pattern.
  • a small diameter side connecting member and a small diameter side engaging portion that engages with the small diameter side connecting member may be provided on the small diameter side surface of the small diameter side arc-shaped portion, and the small diameter side connecting member may be detachably engaged with the small diameter side engaging portion to connect the segments arranged in a circular pattern.
  • the present invention provides a roller bearing that combines good lubrication in the pockets with strong cage strength.
  • FIG. 1 is a cross-sectional view showing an embodiment of a tapered roller bearing according to the present invention.
  • FIG. 2 is a perspective view of a segment of a segmented retainer used in the tapered roller bearing of FIG. 1, as viewed from the outer diameter side.
  • FIG. 3 is a side view of the segment of FIG. 2 as viewed from direction III.
  • FIG. 2 is a perspective view of a segment of a segmented retainer used in the tapered roller bearing of FIG. 1, as viewed from the inner diameter side.
  • 4 is a cross-sectional view showing the VV cross section in FIG. 3.
  • 13 is a table showing evaluation test results. 13 is a table showing evaluation test results.
  • FIG. 13 is a perspective view showing another example of a segment.
  • FIG. 9 is a cross-sectional view showing a state in which tapered rollers are inserted into the segment of FIG. 8 .
  • FIG. 2 is a perspective view of the tapered roller bearing with the outer ring removed.
  • FIG. 2 is a front view of the tapered roller bearing with the outer ring removed.
  • FIG. 2 is a perspective view showing an assembly procedure for the tapered roller bearing.
  • 13 is a perspective view showing the assembly procedure of FIG. 12 from a different angle.
  • FIG. 4 is a schematic diagram showing the relationship between the tapered rollers and the large rib portion of the inner ring when the tapered rollers are arranged on the inner ring with the large end face of the inner ring facing down.
  • FIG. 2 is a perspective view showing a state in the middle of assembling the tapered roller bearing.
  • FIG. 2 is a perspective view showing a state in the middle of assembling the tapered roller bearing.
  • FIG. 17 is a cross-sectional view of FIG.
  • FIG. 17 is a cross-sectional view showing the state shown in FIG. 16 with the annular jig removed.
  • 11 is a cross-sectional view showing the state in which the inner ring assembly is turned over and assembled into the outer ring.
  • FIG. 4 is a cross-sectional view showing the state in which the inner ring assembly is assembled into the outer ring.
  • FIG. FIG. 4 is a schematic diagram showing the rotating state of tapered rollers arranged on the raceway surface of the inner ring.
  • FIG. 4 is a schematic diagram showing the relationship between the height of a small rib portion of an inner ring and a tapered roller when the tapered roller arranged on a raceway surface of an inner ring is rotated.
  • FIG. FIG. 4 is a cross-sectional view showing another example of a tapered roller bearing.
  • FIG. 1 is a cross-sectional view of a conventional tapered roller bearing.
  • FIG. 1 is a perspective view showing a state in which tapered rollers are inserted into segments that constitute a retainer segment used in a conventional tapered roller bearing.
  • the roller bearing 1 has an inner ring 11 having a raceway surface 13 on its outer circumference, an outer ring 12 having a raceway surface 14 on its inner circumference and arranged concentrically with the inner ring 11 on the outer diameter side of the inner ring 11, rollers 15 as multiple rolling elements arranged between the raceway surface 13 of the inner ring 11 and the raceway surface 14 of the outer ring 12, and a cage 17 with multiple pockets 16 to accommodate the rollers 15.
  • the roller bearing of this embodiment is a tapered roller bearing that uses tapered rollers 15 as the rolling elements.
  • the rolling surfaces of the tapered rollers 15 and the apexes of the cone angles of the raceway surface 13 of the inner ring 11 and the raceway surface 14 of the outer ring 12 coincide at a point on the central axis of the tapered roller bearing.
  • a small rib portion 18 and a large rib portion 19 are formed in the areas on both sides of the axial direction sandwiching the raceway surface 13 of the inner ring 11, which protrude in the outer diameter direction and come into contact with the end faces of the tapered rollers 15.
  • the average diameter of the tapered rollers 15 is 40 mm or more, and the outer diameter of the bearing is 1 m or more.
  • the retainer 17 used is a segment retainer formed by arranging a plurality of resin segments 20 shown in Fig. 2 in the circumferential direction X of the bearing.
  • the resin material forming the segments 20 preferably has a linear expansion coefficient of 1.7 x 10-5 °C or less.
  • polyetheretherketone containing carbon fiber or polyetheretherketone containing glass fiber is suitable as the resin material.
  • the segments 20 are formed by injection molding the above-mentioned resin material.
  • the circumferential dimension of the gap is smaller than 0.12% of the circumference of a circle passing through the center of the cage segment.
  • the first segment refers to the segment that is arranged first when multiple segments are arranged in a circumferentially consecutive order
  • the last segment refers to the segment that is arranged last when adjacent segments are abutted and arranged in a circumferentially consecutive order.
  • Multiple cage segments are arranged in a circumferential order and assembled into a tapered roller bearing to form a single annular cage.
  • the filling ratio of the filler in the resin material By setting the filling ratio of the filler in the resin material to 20% by weight or more and 40% by weight or less and keeping the circumferential gap between the segments within the above range, it is possible to prevent strength problems caused by collisions between the segments and deformations caused by the segments pushing against each other in the circumferential direction.
  • each segment 20 is integrally provided with a first arc-shaped portion 21 extending in the bearing circumferential direction X, a second arc-shaped portion 22 spaced from the first arc-shaped portion in the roller axial direction Y and extending in the bearing circumferential direction X, and a plurality of columnar portions 23 interposed between the first arc-shaped portion 21 and the second arc-shaped portion 22.
  • one end of the retainer 17 in the roller axial direction Y has a larger diameter than the other end, so that the radius of curvature of one of the pair of arc-shaped portions 21, 22 is larger than the radius of curvature of the other arc-shaped portion.
  • the first arc-shaped portion 21 is referred to as the small diameter side arc-shaped portion
  • the second arc-shaped portion 22 is referred to as the large diameter side arc-shaped portion.
  • the radius of curvature of the large diameter side arc-shaped portion 22 is larger than the radius of curvature of the small diameter side arc-shaped portion.
  • protrusions 26 having engagement portions 27 are provided so as to protrude in the roller axial direction.
  • wing portions 28 are provided which protrude in the bearing axial direction (small diameter side). The roles and functions of the protrusions 26, engagement portions 27, and wing portions 28 will be described later.
  • the column portion 23 extends in the roller axial direction Y.
  • the space surrounded by the small diameter side portion 21, the large diameter side arc portion 22, and the two adjacent column portions 23 forms a pocket 16 that accommodates the tapered roller 15.
  • Each segment 20 has multiple pockets 16, and in this embodiment, a segment 20 with five pockets 16 is exemplified.
  • a claw portion 24 is formed that protrudes into the area on the outer diameter side of the pocket 16.
  • the claw portion 24 is capable of contacting the outer peripheral surface (rolling surface) of the tapered roller 15.
  • the claw portion 24 restricts the movement of the tapered roller 15 toward the outer diameter side in all pockets 16 (all pockets 16 of the cage 17).
  • an outer ring guide type cage 17 which guides the cage 17 by contacting it with the inner peripheral surface of the outer ring 12.
  • guide protrusions 29 capable of contacting the inner diameter surface of the outer ring 12 are provided on the outer diameter sides of the pillar portions 23 (23 1 ) that form the pockets 16 at both ends in the circumferential direction X of the bearing.
  • the guide type of the cage 17 is not limited to the outer ring guide type, and may be a rolling element guide type or an inner ring guide type.
  • the two columnar portions 23 located at both ends in the bearing circumferential direction X are defined as first columnar portions 231
  • the columnar portion located between the two first columnar portions 231 is defined as second columnar portion 232
  • a recess 40 is provided on the inner diameter surface of each second columnar portion 232.
  • the recess 40 is formed by retracting the inner diameter surface of the second columnar portion 232 toward the outer diameter side from the inner diameter surface 21a of the small diameter side arcuate portion 21 and the inner diameter surface 22a of the large diameter side arcuate portion 22.
  • the recess 40 is provided so as to penetrate the second columnar portion 232 in the bearing circumferential direction. Therefore, the grease sealed inside the bearing can flow between the adjacent pockets 16 through the space formed by this recess 40.
  • Tapered surfaces are formed on both ends of the recess 40 in the roller axial direction. Through this tapered surface, the recess 40 is connected to an inner diameter surface having no recess of the second columnar portion 23 2. The tapered surface may be directly connected to the inner diameter surface 21 a of the small diameter side arcuate portion 21 or the inner diameter surface 22 a of the large diameter side arcuate portion 22.
  • the contribution of the second columnar portion 232 to the strength of the segment 20 is small. Therefore, even if the second columnar portion 232 is thinned by providing the recess 40 on the inner diameter surface of the second columnar portion 232 , the strength required for the segment 20 can be ensured.
  • the provision of the recess 40 increases the flowability of grease (particularly the flowability in the circumferential direction of the bearing), so that the lubrication between the inner surface of the pocket and the tapered roller 15 can be improved. Therefore, it is possible to achieve both the lubrication in the pocket 16 and the strength of the segment 20.
  • the weight of the segment 20 can be reduced, so that the impact force and inertia force applied to the cage during the operation of the bearing are reduced, and the frequency of occurrence of abnormal noise and vibration can be reduced.
  • a thin-walled portion 41 having a smaller radial thickness than both ends in the bearing circumferential direction is formed in the center of either one or both of the small-diameter-side arcuate portion 21 and the large-diameter-side arcuate portion 22 in the bearing circumferential direction.
  • the thin-walled portion 41 is provided in the large-diameter-side arcuate portion 22, as shown in FIG.
  • a region of the large-diameter-side arcuate portion 22 facing the first column portion 23 1 at both ends in the bearing circumferential direction X is defined as a first region, and a region located between the two first regions is defined as a second region, and the thin-walled portion 41 having a smaller radial thickness than the first region is provided in the second region.
  • the thin-walled portion 41 is formed by providing recesses 42 on the inner diameter surface 22a and the outer diameter surface 22b of the large-diameter-side arcuate portion 22.
  • the thin-walled portion 41 may be formed by providing the recesses 42 on both the inner diameter surface 22a and the outer diameter surface 22b, or by providing the recesses 42 on only one of them.
  • the number of pockets 16 provided in the segment 20 is three or more.
  • the thin-walled portion 41 is formed in an area larger than the width of at least one pocket 16 in the circumferential direction X of the bearing.
  • the thin-walled portion 41 described above may be provided only in the large-diameter-side arcuate portion 22, or may be provided only in the small-diameter-side arcuate portion 21.
  • the region of the small-diameter-side arcuate portion 21 facing the first columnar portions 23-1 at both ends in the circumferential direction X of the bearing is defined as a third region, and the region located between the two third regions is defined as a fourth region, and the thin-walled portion 41 having a smaller radial thickness than the third region is provided in the fourth region.
  • the thin-walled portion 41 may be provided in both the large-diameter-side arcuate portion 22 and the small-diameter-side arcuate portion 21.
  • the provision of the thin-walled portion 41 in either or both of the small-diameter-side arc-shaped portion 21 and the large-diameter-side arc-shaped portion 22 can improve the flowability of grease (particularly the flowability in the roller axial direction).
  • the lubrication in the pocket can be further improved.
  • the weight of the segment 20 can be further reduced. Since the area in which the thin-walled portion 41 is provided has a small contribution to the strength of the segment 20, a decrease in the strength of the segment 20 can be avoided even if the thin-walled portion 41 is provided. Therefore, it is possible to achieve both lubrication in the pocket 16 and strength of the segment 20.
  • Figure 7 shows the results of evaluating the lubricity and strength of the segment 20 by changing the depths t1 , t2 (see Figure 3) of the recesses 42 provided on the inner diameter surface 22a and the outer diameter surface 22b of the large diameter side arcuate portion 22.
  • the depth t1 of the recess provided on the inner diameter surface of the small diameter side arcuate portion 21 and the depth t2 of the recess provided on the outer diameter surface are preferably in the range of 5% ⁇ t1 /T ⁇ 15% and 5% ⁇ t2 /T ⁇ 15%, respectively.
  • the tapered roller bearing 1 As shown in FIG. 1, the tapered roller bearing 1 according to this embodiment comprises an inner ring 11, an outer ring 12 arranged concentrically around the inner ring 11, a number of tapered rollers 15 arranged between the inner ring 11 and the outer ring 12, and a cage 17 having pockets 16 that hold the tapered rollers 15 at regular intervals.
  • the outer ring 12 has a raceway 14 on its inner circumference along which each tapered roller 15 rolls.
  • the inner ring 11 has a raceway 13 on its outer circumference along which the tapered rollers 15 roll, and a large rib portion 19 and a small rib portion 18 on either side of the raceway 13 in the axial direction with which the end faces of the tapered rollers 15 come into contact.
  • the average diameter of the tapered rollers 15 is 40 mm or more, and the outer diameter of the bearing is 1 m or more.
  • the retainer 17 is a segment retainer consisting of multiple segments 20.
  • the segment 20 has a pair of small diameter side arcuate portions 21 and large diameter side arcuate portions 22 that face each other with a specified distance between them, and a number of pillar portions 23 that are installed between the small diameter side arcuate portions 21 and the large diameter side arcuate portions 22.
  • the space surrounded by the two adjacent pillar portions 23, the small diameter side arcuate portions 21, and the large diameter side arcuate portions 22 forms a pocket 16 that houses the tapered rollers 15.
  • the cage 17, which is formed by arranging the segments 20 in an annular shape, is an outer ring guide type, and arc-shaped guide protrusions 29 are provided on the outer surfaces of both axial ends of the column sections 23.
  • the guide protrusions 29 may be provided only on any of the column sections 23, including the column sections 23 at both ends.
  • the segment 20 is arranged in a ring shape with the end faces of the small diameter side arcuate portion 21 and the large diameter side arcuate portion 22 butted against each other.
  • protrusions 26 having engagement portions 27 for the connecting members 25 arranged on the large diameter side of each annularly arranged segment 20 are provided so as to protrude in the axial direction. It is preferable that the protrusions 26 on both ends of the large diameter side surface of the large diameter side arcuate portion 22 of the segment 20 are provided so as to avoid contact between the protrusions 26 of adjacent segments 20.
  • the annular jig 31 consists of a ring portion 31a that abuts against the small diameter end face of the inner ring 11, and an L-shaped engagement portion 31b that protrudes from the axial end of the ring portion 31a toward the outer diameter side. With the ring portion 31a abutting against the small diameter end face of the inner ring 11, the L-shaped engagement portion 31b is fitted into the wing portion 28 of the segment 20.
  • the connecting members 25 wound around the large diameter side of each segment 20 are fastened by a fastening member 30 such as a turnbuckle.
  • a fastening member 30 such as a turnbuckle
  • the fastening member 30 has a body with a female thread, and the ends of the connecting members 25 can be connected to each other by screwing the male thread provided at the end of the connecting member 25 into the body of the turnbuckle.
  • Tension can be applied to the connecting members 25 by rotating the body, and the fastening at both ends of the connecting members 25 can be released by rotating the body in the opposite direction to the tightening direction.
  • the ends of the connecting members 25 can be connected to each other by providing a fastening portion at the end of the connecting members 25 and wrapping the connecting members 25 around each other, or by using a cable tie.
  • the connecting member 25 may be a long or endless member having flexibility, such as a wire or a belt.
  • a detachable hook or turnbuckle may be used as the fastening member 30.
  • Turnbuckles are most preferable because they are detachable, the fastening force does not loosen, and the fastening force is adjustable.
  • a detachable buckle is preferable as the fastening member 30 because the fastening force does not loosen.
  • the segment 20 is made of resin or steel.
  • the resin that can be used to form the segment 20 is polyetheretherketone mixed with carbon fiber or polyetheretherketone mixed with glass fiber.
  • the tapered roller bearing 1 using the segments 20 is assembled as follows.
  • the inner ring assembly is assembled by integrating the inner ring 11, tapered rollers 15, and cage 17 as shown in Figures 10 and 11.
  • the tapered rollers 15 are placed on the raceway surface 13 with the large end face of the inner ring 11 facing down, there is a possibility that the tapered rollers 15 may fall off the inner ring 11 due to their own weight.
  • the distance from the central axis of the inner ring 11 to the tip of the large rib portion 19 is made greater than the distance from the central axis of the inner ring 11 to the center of gravity of the tapered rollers 15, and the diameter J of the large rib portion 19 satisfies the following formula.
  • D indicates the diameter of the large end face of the tapered roller
  • G indicates the diameter of the small end face of the tapered roller
  • F indicates the length of the tapered roller
  • E indicates the distance from the central axis to the end of the raceway surface 13 on the large rib portion 19 side.
  • each segment 20 After lining up the tapered rollers 15 on the raceway surface 13 of the inner ring 11, as shown in Figure 15, each segment 20 is placed on top of it from the outer diameter side, and the tapered rollers 15 are inserted into the pockets 16 from the inner diameter side of each segment 20.
  • an annular jig 31 is fitted onto the wing portions 28 protruding from the small diameter side of the annularly arranged segments 20, a connecting member 25 is passed through the engagement portion 27 of the protrusion 26 protruding from the large diameter side, the ends of the connecting member 25 wound around the outer diameter side of the segments 20 are bound together with fastening members 30, and the connecting member 25 is tightened with the fastening members 30 to integrate the multiple annularly arranged segments 20.
  • the fastening member 30 is located between the protrusions 26 that protrude from both ends of the large diameter side of the large diameter arc-shaped portion 22, and the space between the protrusions 26 on both ends serves as a housing for the fastening member 30.
  • the connecting member 25 may be a single continuous piece in the circumferential direction, or may be divided into multiple pieces in the circumferential direction, with the ends of each divided connecting member 25 being connected to each other by fastening members 30.
  • the fastening members 30 are arranged in equal circumferential portions.
  • the annular jig 31 is placed axially over the wing portions 28 of the small-diameter arc-shaped portions 21 of the segments 20 arranged in an annular shape, and can be removed by moving it along the central axis after the inner ring assembly is assembled (Figure 18).
  • the inner race assembly is attached to the outer race 12 by turning it over so that the small diameter side of the inner race assembly faces downwards, as shown in Figure 19.
  • the tapered rollers 15 inserted into the pockets 16 of each segment 20 are prevented from slipping out of the pockets 16 by the claws 24 provided on the outer diameter side of the column portions 23 that form the pockets 16.
  • the annular jig 31 used when assembling the inner ring assembly should be removed when assembling it into the outer ring 12.
  • the segments 20 connected by the connecting member 25 have tapered rollers 15 inserted and held in the pockets 16 of each segment 20 that fit between the large rib portion 19 and the small rib portion 18 located on both axial sides of the raceway surface 13 of the inner ring 11, and the tapered rollers 15 are hooked onto the small rib portion 18 of the inner ring 11, preventing the segments 20 from falling off.
  • Point C on the side of the small rib portion 18 where the tapered roller 15 catches is the intersection point between the spline curve that traces the trajectory of the corner of the small end face of the tapered roller 15 when the tapered roller 15 rotates and the side of the small rib portion 18, as shown in Figure 22.
  • the diameter M of the small rib portion 18 of the inner ring 11 satisfies the following condition.
  • M is the diameter of the small rib portion 18 of the inner ring 11
  • L is the angle that the side surface of the small rib portion 18 of the inner ring 11 on the point C side makes with a line perpendicular to the central axis of the inner ring 11
  • K is the chamfer width of the tip of the small rib portion 18
  • y3 is the distance from the contact point C where the side surface of the small rib portion 18 and the small diameter end face of the tapered roller 15 come into contact with each other to the central axis when the tapered roller 15 is rotated around point B at the tip of the large rib portion 19 of the inner ring 11.
  • the tapered roller bearing 1 can be assembled as shown in Figure 21.
  • the connecting members 25 that fasten the outer periphery of each segment 20 can be loosened and removed with the fastening members 30 without causing the segments 20 to come apart, so the connecting members 25 can be removed after the tapered roller bearing 1 is installed in the device.
  • a wing portion 28 protruding toward the small diameter side is provided on the small diameter side surface of the small diameter side arcuate portion 21, and when the large diameter side of each segment 20 arranged in a ring is bound with a connecting member 25, an annular jig 31 is fitted into the wing portion on the small diameter side of each segment 20 arranged in a ring.
  • a connecting member 25 when the large diameter side of each segment 20 arranged in a ring is bound with a connecting member 25, an annular jig 31 is fitted into the wing portion on the small diameter side of each segment 20 arranged in a ring.
  • a small diameter side engaging portion 32 is provided on the small diameter side surface of the small diameter side arcuate portion 21
  • a connecting member 33 wound around the small diameter side of each segment arranged in a ring is passed through this small diameter side engaging portion 32, and the ends of this connecting member 25 are detachably bound to each other with a fastening member (not shown), so that the annular jig 31 is not used.
  • the tapered roller will not fall out of the pocket even if the inner ring assembly is turned over.
  • annular jig When connecting the large diameter sides of each annularly arranged segment with a connecting member, an annular jig can be fitted into the wing portion of the small diameter side of each annularly arranged segment to prevent the small diameter sides of each segment from opening apart.
  • each annularly arranged segment The ends of the connecting members on the large diameter side of each annularly arranged segment are connected to each other by fastening parts or fastening members, so after the inner ring assembly is installed in the outer ring, the connecting members can be removed by removing the fastening parts or fastening members, preventing the connecting members from coming loose and causing breakdowns during operation.
  • a tapered roller bearing is used as an example, but the present invention can be widely applied to roller bearings such as cylindrical roller bearings.

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

Abstract

Un élément de retenue (17) est formé par agencement d'une pluralité de segments de résine (20) dans une direction circonférentielle de palier. Chaque segment 20 est pourvu d'une seule pièce : d'une première partie arquée 21 s'étendant dans la direction circonférentielle de palier; d'une seconde partie arquée 22 qui est espacée de la première partie arquée dans une direction axiale de rouleaux et qui s'étend dans la direction circonférentielle de palier; et d'une pluralité de parties colonnes 23 interposées entre la première partie arquée 21 et la seconde partie arquée 22. Des parties griffes (24) qui entrent en contact avec les rouleaux et qui limitent le mouvement radial extérieur des rouleaux sont disposées sur un côté radialement externe des parties colonnes (23) qui forment des poches (16). Parmi la pluralité de parties colonnes 23 de chaque segment 20, les deux parties colonnes positionnées aux deux extrémités dans la direction circonférentielle sont définies en tant que premières parties colonnes 231, et les parties colonnes positionnées entre les deux premières parties colonnes sont définies en tant que secondes parties colonnes 232, et des parties évidées 40 sont disposées sur des surfaces de diamètre interne des secondes parties colonnes 232.
PCT/JP2023/039156 2022-11-21 2023-10-30 Palier à rouleaux WO2024111363A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022-185666 2022-11-21
JP2022185666A JP2024074487A (ja) 2022-11-21 2022-11-21 ころ軸受

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WO2024111363A1 true WO2024111363A1 (fr) 2024-05-30

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007024294A (ja) * 2005-07-21 2007-02-01 Ntn Corp 円錐ころ軸受および風力発電機の主軸支持構造
JP2007078090A (ja) * 2005-09-14 2007-03-29 Ntn Corp 針状ころ軸受
JP2007247819A (ja) * 2006-03-16 2007-09-27 Ntn Corp ころ軸受、保持器セグメントおよび風力発電機の主軸支持構造
JP2015117767A (ja) * 2013-12-18 2015-06-25 株式会社ジェイテクト ころ軸受
JP2016153674A (ja) * 2015-02-20 2016-08-25 日本精工株式会社 転がり軸受用セグメント保持器及びころ軸受
JP2018080747A (ja) * 2016-11-16 2018-05-24 Ntn株式会社 円すいころ軸受の保持器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007024294A (ja) * 2005-07-21 2007-02-01 Ntn Corp 円錐ころ軸受および風力発電機の主軸支持構造
JP2007078090A (ja) * 2005-09-14 2007-03-29 Ntn Corp 針状ころ軸受
JP2007247819A (ja) * 2006-03-16 2007-09-27 Ntn Corp ころ軸受、保持器セグメントおよび風力発電機の主軸支持構造
JP2015117767A (ja) * 2013-12-18 2015-06-25 株式会社ジェイテクト ころ軸受
JP2016153674A (ja) * 2015-02-20 2016-08-25 日本精工株式会社 転がり軸受用セグメント保持器及びころ軸受
JP2018080747A (ja) * 2016-11-16 2018-05-24 Ntn株式会社 円すいころ軸受の保持器

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