WO2023063043A1 - Roulement à rouleaux cylindriques - Google Patents

Roulement à rouleaux cylindriques Download PDF

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Publication number
WO2023063043A1
WO2023063043A1 PCT/JP2022/035232 JP2022035232W WO2023063043A1 WO 2023063043 A1 WO2023063043 A1 WO 2023063043A1 JP 2022035232 W JP2022035232 W JP 2022035232W WO 2023063043 A1 WO2023063043 A1 WO 2023063043A1
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WO
WIPO (PCT)
Prior art keywords
roller
pocket
parallel
column
cylindrical
Prior art date
Application number
PCT/JP2022/035232
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English (en)
Japanese (ja)
Inventor
和気 陰山
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 WO2023063043A1 publication Critical patent/WO2023063043A1/fr

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Classifications

    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly 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

Definitions

  • the present invention relates to cylindrical roller bearings.
  • the retainer used in the bearing has the role of holding the rolling elements at equal intervals in the bearing, preventing contact between the rolling elements and helping high-speed rotation.
  • the retainer includes a pressed retainer (pressed retainer), a machined retainer (machined retainer), and a molded retainer by injection molding or the like.
  • This machined retainer As a machined retainer, the one described in Patent Document 1 is known.
  • This machined retainer as shown in FIG. 10, consists of two concentric ring portions 1, 1 and a post portion 2 connecting these ring portions. Cylindrical rollers 4 as rolling elements are accommodated in pockets 3 formed between adjacent column portions 2 . In addition, a relief portion 5 is formed at each corner of the pocket 3 .
  • the recessed portion of the machined retainer was formed by turning such as drilling.
  • the side surface of the circular arc-shaped column portion is cut into, and the strength of the column portion is reduced. That is, in the one-piece machined retainer, the recessed portion 5 is formed by drilling, so it takes the form of a straight hole parallel to the center line of the pocket toward the center of the retainer. For this reason, it is necessary to cut the relief portion 5 beyond the side surface of the circular arc-shaped column portion 2 toward the column portion 2 side.
  • the strength of the pillar 2 is determined by the narrowest portion, that is, the cross section passing through the bottom of the pillar 2, so the cross-sectional area is small and the strength is inferior.
  • the present invention seeks to provide a cylindrical roller bearing using a machined cage that is excellent in strength and durability without reducing bearing life.
  • a cylindrical roller bearing according to the present invention comprises a pair of bearing rings, cylindrical rollers as a plurality of rolling elements interposed between the raceway surfaces of the pair of bearing rings, a pair of annular portions, and the pair of rollers extending in the axial direction. and pockets formed between the adjacent pillars to accommodate the cylindrical rollers. Recessed portions are provided at the four corners of the pockets so that the cylindrical rollers are arranged in the circumferential direction.
  • the roller diameter of the cylindrical roller is Dw
  • the ratio of the radial displacement of the pocket center to the roller center and the roller diameter is ⁇ 1.
  • ⁇ 1 (the amount of radial movement of the pocket center relative to the roller center/Dw) is 3% to 10%.
  • the gap between the roller diameter and the pocket diameter is evaluated, making it possible to limit the maximum movement of the cage.
  • the pocket openings on the outer diameter side of the cage are smaller than the pocket openings on the inner diameter side of the cage, and both openings are smaller than the roller diameters. I'm in.
  • the value of the radial distance when the roller center and the pocket center are aligned and the outer diameter side of the cage is moved until it contacts the rollers, and the radial distance value when the inner diameter side of the cage is moved until it contacts the rollers. are compared, and the larger value is evaluated as the amount of radial movement of the pocket center relative to the roller center.
  • the same evaluation method is used for cages in which the pocket opening on the inner diameter side of the cage is smaller than the pocket opening on the outer diameter side of the cage.
  • the side surface of the column portion excluding the recessed portion is a straight portion extending in the axial direction, and the ratio of the axial length to the roller length when the axial length of this straight portion is H2 and the roller length is H1.
  • the side surface of the column is arcuate, the relief portion is parallel to the side surface of the column, and the shape of the relief portion is aligned with the side surface of the column.
  • a first parallel portion parallel to the side surface of the column connected via one sloped portion, and a second parallel portion parallel to the inner wall surface of the annular portion connected to the inner wall surface of the annular portion via the second sloped portion.
  • a curved surface portion that is in contact with the first parallel portion and the second parallel portion, connects the first parallel portion and the second parallel portion, and does not interfere with the chamfered portion of the cylindrical roller, and the first inclined surface portion and the side surface of the column is ⁇ 1, and the inclination angle between the second slope portion and the inner wall surface of the annular portion is ⁇ 2, ⁇ 1> ⁇ 2 and 30° ⁇ 1 ⁇ 45° , 2° ⁇ 2 ⁇ 15°.
  • ⁇ 1 can be made relatively large, and the spatial cross-sectional area of the recessed portion in the circumferential direction becomes large, which is advantageous for the supply of lubricant.
  • the cylindrical roller rotates in the circumferential direction, it is advantageous for lubrication if the relief portion in the direction of the column portion is large.
  • .theta.2 can be made smaller than .theta.1, and the spatial cross-sectional area can also be made relatively small. Since the annular portion with which the roller end face contacts is thinner than the column portion, providing a large relief portion reduces the strength.
  • the present invention can limit the maximum movement of the cylindrical rollers, it has excellent vibration resistance, improves durability, and effectively prevents a reduction in service life.
  • FIG. 1 is a cross-sectional view of a cylindrical roller bearing of the present invention
  • FIG. FIG. 2 is a perspective view of a main portion of a machined retainer used in a cylindrical roller bearing
  • FIG. 4 is a cross-sectional view showing a column portion of the machined retainer
  • FIG. 4 is a cross-sectional view showing a surface corresponding to the roller end face of the machined retainer
  • FIG. 4 is an exploded view of the main part of the machined retainer
  • FIG. 6 is an enlarged view of a main portion of FIG. 5
  • It is a simplified sectional view showing the relationship with the pocket roller.
  • It is a simplified cross-sectional view showing the relationship between the column portion and the side rollers.
  • FIG. 4 is a simplified simplified diagram showing the relationship between the rollers and the inner wall surface of the annular portion
  • FIG. 2 is a cross-sectional view of a machined retainer used in a conventional cylindrical roller bearing
  • FIG. 4 is a cross-
  • FIG. 1 shows a cross-sectional view of a cylindrical roller bearing of the present invention, which comprises a pair of bearing rings, a plurality of rolling elements interposed between the raceway surfaces of the pair of bearing rings, and the rolling elements.
  • a retainer is provided to hold the elements at predetermined intervals in the circumferential direction.
  • the inner ring 11 constituting one bearing ring, the outer ring 12 constituting the other bearing ring, and the rolling elements interposed between the raceway surface 11a of the inner ring 11 and the raceway surface 12a of the outer ring 12 It comprises cylindrical rollers 20 and retainers 14 that are held at predetermined intervals in the circumferential direction.
  • the outer ring has flanges 12b, 12b at both ends in the axial direction, and the inner ring 11 does not have flanges at both ends in the axial direction.
  • a so-called single-row NU type is used.
  • the inner ring 11 and outer ring 12 are made of, for example, high-carbon chromium bearing steel such as JIS SUJ2, machine structural alloy such as SCM420, or machine structural carbon steel such as S53C.
  • the cylindrical rollers 20 as rolling elements may be made of an iron-based metal material, ceramics, or the like. Examples of iron-based metal materials include bearing steel used for rolling bearings, carburized steel, carbon steel for machine structural use, cold-rolled steel, hot-rolled steel, and the like. Carbon steel for machine structural use and high-strength brass castings are often used as materials for the retainer 14, and aluminum alloys and the like are also used.
  • the retainer 14 includes a pair of annular portions 21, 21, a plurality of pillars 23 extending in the axial direction and connecting the pair of annular portions 21, 21, and adjacent
  • a pocket 24 is formed between the mating pillars 23 and 23 and accommodates the cylindrical roller 20 .
  • relief portions 25 are formed at the four corners of the pocket 24 .
  • the side surface of the column portion 23 is arc-shaped in a cross section perpendicular to the axis of the retainer, and the relief portion 25 extends parallel to the side surface of the column portion 23 .
  • parallel simply refers to the relationship between straight lines, planes and planes, or straight lines and planes, but just like the mathematical term parallel curves, the term “parallel” is also used for curves.
  • Parallel curves are defined as two curves that have a common normal at every point. Concentric circles (parts of) belong to this parallel curve.
  • the term "parallel" in the specification and claims is also used in this sense.
  • the recessed portion is also arc-shaped.
  • the side surface of the column portion 23 and the recessed portion 25 are arcuate with a common center and different radii of curvature, and form a part of concentric circles. .
  • the outline of the relief portion 25 is composed of a first slope portion 31 formed by a slope forming an acute angle with the side surface 23 a of the column portion 23 and a slope forming an acute angle with the inner wall surface (side surface) of the annular portion (side plate) 21 .
  • a first parallel portion 34 circumferentially offset by a1 from the side surface 23a of the column portion 23 toward the opposite pocket side; and a second parallel portion 35 offset by a2 to the side opposite the pocket.
  • the first parallel portion 34 and the second parallel portion 35 are connected by the curved surface portion 33 .
  • the relief portion 25 extends from the side surface 23a of the column portion 23 to the first slope portion 31, the first parallel portion 34, the curved surface portion 33, the second parallel portion 35, and the second slope portion 32 as an annular portion (side plate). 21 is continuously connected to the inner wall surface 21a.
  • the relief portion 25 is reliably formed outside the side surface 21a (opposite side of the pocket) and outside the side surface 23a of the column portion 23 (opposite side of the pocket). It becomes possible to The first and second parallel portions 34 , 35 are tangent to the curved portion 33 .
  • R indicates the radius of curvature of the curved surface portion 33
  • r indicates the radius of curvature of the corner radius portion 24c of the pocket 24 when the relief portion 25 is not formed.
  • the allowable range of the dimensions a1, a2 and R is a range that does not interfere with the chamfered portion of the cylindrical roller 20.
  • the relationship between ⁇ 1 and ⁇ 2 is ⁇ 1> ⁇ 2. Further, ⁇ 1 was set to 30° ⁇ 1 ⁇ 55°, and ⁇ 2 was set to 2° ⁇ 2 ⁇ 15°.
  • FIG. 7 shows the relationship between the pocket 24 of the retainer and the cylindrical rollers 20 housed in this pocket 24.
  • the cylindrical rollers 20 in FIG. 7 are in contact with the outer diameter edges 24b, 24b of the pocket 24.
  • the pocket center O2 is the bearing P. C. D. It is located above.
  • FIG. 8 shows the relationship between the side surface of the column portion 23 and the cylindrical roller 20.
  • the side surface 23a of the column portion 23 without the relief portion 25 is a straight portion extending in the axial direction.
  • FIG. 9 shows the relationship between the cylindrical rollers 20 and the inner wall surface of the annular portion 21.
  • FIG. When the ratio of the diameter of the ring portion to the roller diameter of the inner wall surface 21a of the annular portion 21 corresponding to the roller end surface 20a of the pocket 24 is Dx and the roller diameter is Dw is ⁇ 3.
  • ⁇ 3 (Dx/Dw) is from 55% to 75%.
  • the clearance generated between the roller diameter and the pocket diameter is evaluated regarding the amount of radial movement of the pocket center O2 with respect to the roller center O1, and it is possible to limit the maximum movement of the cage.
  • the pocket openings on the outer diameter side of the cage are smaller than the pocket openings on the inner diameter side of the cage, and both openings are smaller than the roller diameters. I'm winning.
  • the larger value is evaluated as the amount of radial movement of the pocket center O2 with respect to the roller center O1.
  • the same evaluation method is used for cages in which the pocket opening on the inner diameter side of the cage is smaller than the pocket opening on the outer diameter side of the cage.
  • the cylindrical roller bearing can limit the maximum movement of the cylindrical rollers 20, so that it has excellent vibration resistance, improves durability, and effectively prevents a reduction in service life.
  • the relief portion 25 can be parallel to the side surface 23a of the column portion 23, and has the same size in any cross section of the column portion 23 in the thickness direction. Therefore, the degree to which the cross-sectional area of the base of the column portion 23 is reduced is minimized. Moreover, the area of the relief portion 25 that bites into the base of the column portion 23 can be reduced, and stress concentration can be alleviated as compared with the conventional case.
  • the degree of reduction in the cross-sectional area of the base of the column portion 23 can be minimized, and the reduction in strength due to the provision of the recessed portion 25 can be suppressed. It is excellent in durability and can effectively prevent a decrease in service life.
  • the side surface 23a of the column portion 23 without the relief portion 25 is a straight portion extending in the axial direction.
  • ⁇ 2 is the length ratio
  • a ratio of the diameters of the ring portion middle height circles when the ring portion middle height circle diameter of the surface corresponding to the roller end surface 20a of the pocket 24 corresponding to the roller end surface 20a of the pocket 24, which is the inner wall surface 21a of the annular portions 21, 21a, is Dx and the roller diameter is Dw. is ⁇ 3, ⁇ 3 (Dx/Dw) is preferably 55% to 75%.
  • the dimension a1 becomes larger than the dimension a2.
  • the cylindrical roller 20 rotates in the circumferential direction.
  • the retainer having the relief portion 25 shown in FIG. 6 was evaluated using evaluation functions of ⁇ 1, ⁇ 2, and ⁇ 2.
  • Table 1 below shows the evaluation by the evaluation function of ⁇ 1.
  • ⁇ 1 15% or more, the space inside the pocket becomes too wide, the amount of movement between the rollers 20 and the cage 14 inside the pocket 24 increases, and the amount of vibration increases.
  • the cylindrical rollers 20 are incorporated into the bearing, first, the cylindrical rollers 20 are inserted into the pockets 24 of the retainer 14 from the inner diameter side, and then incorporated into the inner ring 11 . Therefore, if the inner pocket space becomes too large, the cylindrical rollers 20 may fall from the inner diameter side of the cage. Conversely, if ⁇ 1 is 2% or less, the space in the pocket becomes too narrow, and the flow path for the lubricant (oil, grease, etc.) cannot be secured, and the cylindrical rollers 20 may be locked.
  • ⁇ indicates the case where the pocket space is neither too narrow nor too wide and the above problems do not occur, and ⁇ indicates that the pocket space is too wide (15% or more), It shows a case where the above problem may occur, and when the space inside the pocket is too narrow (2% or less), the above problem may occur. That is, ⁇ indicates superiority, and ⁇ indicates that superiority is not recognized.
  • ⁇ 1 is set from 3% to 10%.
  • the present retainer can ensure a sufficient flow path for the lubricating oil, is excellent in vibration resistance, and is resistant to wear.
  • Table 2 shows the evaluation by the evaluation function of ⁇ 2.
  • ⁇ indicates a case where a sufficient flow path for the lubricating oil can be secured and the contact portion between the cylindrical roller 20 and the column portion does not decrease and the above-described problems do not occur
  • x indicates a case where the lubricating oil ( ⁇ 2 is 95% or more), the above problem may occur, and the contact portion between the cylindrical roller 20 and the column portion 23 is reduced ( ⁇ 2 is 55% or less), causing the above problem. Indicates when there is a risk. Therefore, also in this case, ⁇ indicates superiority, and x indicates that superiority is not recognized.
  • ⁇ 2 is set from 60% to 90%. Even if it is set in this way, it is possible to secure a sufficient flow path for the lubricating oil, and furthermore, it is excellent in vibration resistance and wear-resistant.
  • Table 3 shows the evaluation by the evaluation function of ⁇ 3.
  • ⁇ 3 is 80% or more, the lubricating oil flow path cannot be sufficiently secured, and it is difficult to stably obtain smooth rotation for a long period of time. If ⁇ 3 is 50% or less, the contact portion between the roller end surface 20a and the annular portion 21 is reduced, resulting in poor vibration resistance and easy wear. Moreover, the strength of the annular portion 21 or the strength of the cage as a whole may be insufficient.
  • ⁇ indicates a case where a sufficient lubricating oil flow path can be secured and the contact portion between the cylindrical roller 20 and the annular portion 21 is not reduced, and the above-described problems do not occur, and x indicates lubrication. A sufficient oil flow path cannot be secured ( ⁇ 3 is 80% or more), and the above problem may occur. Indicates a case where there is a risk of occurrence. Therefore, also in this case, ⁇ indicates superiority, and x indicates that superiority is not recognized.
  • ⁇ 3 is set from 55% to 75%. Even if it is set in this way, it is possible to secure a sufficient flow path for the lubricating oil, and furthermore, it is excellent in vibration resistance and wear-resistant.
  • the cylindrical roller bearing of the present invention uses the retainer 14 described above. For this reason, the cylindrical roller bearing can suppress a decrease in strength, has excellent vibration resistance, improves durability, and can constitute a bearing that can effectively prevent a decrease in life.
  • NUP type N type, NF type, NH type, etc.
  • the NJ type has a rib on one side of the inner ring and both sides of the outer ring.
  • the NUP type has a rib on one side of the inner ring and both sides of the outer ring.
  • the N type has ribs on both sides of the inner ring and no outer ring.
  • the NF type has ribs on both sides of the inner ring and one side of the outer ring.
  • the NH type is a combination of an L-shaped collar ring on the inner ring side of the NU or NJ type.
  • an outer ring guide system refers to positioning of the cage by bringing the cage into contact with the outer ring, and the outer surface serves as a guide surface and contacts the inner circumference of the outer ring.
  • an inner ring guide system may be used.
  • the inner ring guide means positioning of the cage by bringing the cage into contact with the inner ring, and the inner diameter surface serves as a guide surface and contacts the outer circumference of the inner ring.
  • the bearing As a cylindrical roller bearing, it can be used for applications involving vibration such as gearboxes, and can be used for various devices and structures such as general machinery, electrical machinery, and transportation machinery. Moreover, the bearing is not limited to a single-row type, and may be a double-row type.
  • Raceway ring 11a Raceway surface
  • Raceway ring (outer ring) 12a raceway surface
  • cylindrical roller 20a end surface 21 annular portion 21a inner wall surface 21a inner wall surface 23 column portion 23a side surface 24 pocket 25 relief portion 31 first slope portion 32 second slope portion 33 curved surface portion 34 first parallel portion 35 second parallel portion
  • O1 Roller center O2 Pocket center

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

Abstract

L'invention concerne une cage usinée intégrée comprenant une paire de parties en forme d'anneau, une pluralité de parties en colonne qui s'étendent dans la direction axiale et qui relient la paire de parties en forme d'anneau, et des poches qui sont formées entre des parties en colonne adjacentes et qui logent des rouleaux cylindriques. Les quatre coins de chaque poche sont pourvus de parties évidées. La quantité mobile radiale du centre de chaque poche par rapport au centre d'un rouleau cylindrique respectif (Dw) est de 3 à 10 %, Dw étant le diamètre de rouleau des rouleaux cylindriques.
PCT/JP2022/035232 2021-10-12 2022-09-21 Roulement à rouleaux cylindriques WO2023063043A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021167554A JP2023057850A (ja) 2021-10-12 2021-10-12 円筒ころ軸受
JP2021-167554 2021-10-12

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WO2023063043A1 true WO2023063043A1 (fr) 2023-04-20

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CN (2) CN115962226A (fr)
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH053644U (ja) * 1991-07-04 1993-01-19 光洋精工株式会社 円筒ころ軸受用合成樹脂製保持器
JPH09177793A (ja) * 1995-12-28 1997-07-11 Ntn Corp 円筒ころ軸受用樹脂保持器
JPH11108065A (ja) * 1997-08-06 1999-04-20 Ntn Corp 針状ころ軸受
JP2001012477A (ja) * 1999-04-28 2001-01-16 Nsk Ltd 転がり軸受用保持器
JP2001323936A (ja) * 2000-05-18 2001-11-22 Nsk Ltd ころ軸受
JP2006118644A (ja) * 2004-10-22 2006-05-11 Ntn Corp 円筒ころ軸受用もみ抜き保持器

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH053644U (ja) * 1991-07-04 1993-01-19 光洋精工株式会社 円筒ころ軸受用合成樹脂製保持器
JPH09177793A (ja) * 1995-12-28 1997-07-11 Ntn Corp 円筒ころ軸受用樹脂保持器
JPH11108065A (ja) * 1997-08-06 1999-04-20 Ntn Corp 針状ころ軸受
JP2001012477A (ja) * 1999-04-28 2001-01-16 Nsk Ltd 転がり軸受用保持器
JP2001323936A (ja) * 2000-05-18 2001-11-22 Nsk Ltd ころ軸受
JP2006118644A (ja) * 2004-10-22 2006-05-11 Ntn Corp 円筒ころ軸受用もみ抜き保持器

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CN115962226A (zh) 2023-04-14
CN218440256U (zh) 2023-02-03

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