WO2022210339A1 - Roulement à rouleaux et engrenage réducteur de vitesse planétaire - Google Patents

Roulement à rouleaux et engrenage réducteur de vitesse planétaire Download PDF

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Publication number
WO2022210339A1
WO2022210339A1 PCT/JP2022/014327 JP2022014327W WO2022210339A1 WO 2022210339 A1 WO2022210339 A1 WO 2022210339A1 JP 2022014327 W JP2022014327 W JP 2022014327W WO 2022210339 A1 WO2022210339 A1 WO 2022210339A1
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WO
WIPO (PCT)
Prior art keywords
roller
rollers
planetary
roller bearing
diameter
Prior art date
Application number
PCT/JP2022/014327
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English (en)
Japanese (ja)
Inventor
友紀 角
貴之 中村
Original Assignee
ミネベアミツミ株式会社
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 ミネベアミツミ株式会社 filed Critical ミネベアミツミ株式会社
Publication of WO2022210339A1 publication Critical patent/WO2022210339A1/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
    • F16C19/24—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
    • F16C33/34—Rollers; 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
    • F16C33/58—Raceways; Race rings
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion

Definitions

  • the present invention relates to roller bearings and planetary reduction gears.
  • Full complement bearings are known to be used in planetary gear reduction gears, etc., when ball bearings or roller bearings with cages are insufficient in durability or when downsizing is difficult. .
  • An object of one aspect is to provide a roller bearing and a planetary reduction gear that can improve rotational efficiency.
  • the roller bearing includes first rollers and second rollers arranged between the inner ring and the outer ring and extending in the axial direction.
  • the diameter of the second roller is smaller than the diameter of the first roller.
  • the rotation efficiency can be improved.
  • FIG. 1 is a perspective view of a planetary reduction gear in an embodiment.
  • FIG. 2 is a side cross-sectional view showing an example of the planetary reduction gear in the embodiment.
  • FIG. 3 is a front cross-sectional view showing an example of the planetary reduction gear in the embodiment.
  • FIG. 4 is a front cross-sectional view showing an example of a planetary gear having roller bearings in the embodiment.
  • FIG. 5 is a side cross-sectional view showing an example of a planetary gear having roller bearings in the embodiment.
  • FIG. 6 is a perspective view showing an example of first rollers and second rollers in the embodiment.
  • FIG. 7 is an enlarged cross-sectional view showing an example of a roller bearing in the embodiment.
  • FIG. 8 is an enlarged cross-sectional view showing an example of a roller bearing in the background art.
  • roller bearing and planetary reduction gear disclosed in the present application will be described below with reference to the drawings. Note that the dimensional relationship of each element in the drawings, the ratio of each element, and the like may differ from reality. Even between the drawings, there are cases where portions with different dimensional relationships and ratios are included.
  • FIG. 1 is a perspective view of a planetary speed reducer according to an embodiment
  • FIG. 2 is a side sectional view showing an example of a planetary speed reducer according to an embodiment
  • FIG. 3 is a front sectional view showing an example of a planetary speed reducer according to an embodiment.
  • the planetary reduction gear 1 in the embodiment can be used for general purposes, for example, joints of robots.
  • the planetary reduction gear 1 in the embodiment includes a housing 10, an internal gear mechanism 70 formed in the housing 10, a carrier 30, a plurality of planetary gear mechanisms 40, and a sun gear 60.
  • the sun gear 60 is held by an adapter 20 fixed to the rotating shaft (not shown) of the motor, and the sun gear 60 rotates as the motor rotates.
  • the three planetary gear mechanisms 40 can rotate around the planetary shaft 43 and revolve around the sun gear 60 while meshing with the internal gear mechanism 70 as the sun gear 60 rotates.
  • the planetary shaft 43 is connected to the carrier 30, and the carrier 30 rotates as the planetary gear mechanism 40 revolves.
  • the sun gear 60 may be directly used as the rotating shaft of the motor without using the adapter 20 .
  • the housing 10 and the internal gear mechanism 70 may be separate bodies.
  • the carrier 30 is an example of an output member, and the output member is connected to a drive target (not shown) such as a joint of a robot.
  • the output member transmits the driving force transmitted from the internal gear mechanism 70 to the driven object.
  • the planetary gear mechanism 40 has a planetary gear 41 and a planetary shaft 43 .
  • FIG. 4 is a front cross-sectional view showing an example of a planetary gear having roller bearings in the embodiment. As shown in FIG. 4, the planetary gear 41 rotates in conjunction with the planetary shaft 43 as a rotation axis. The planetary gear 41 is connected to the internal gear mechanism 70 .
  • the planetary gear 41 corresponds to the outer ring of a general bearing, and the planetary shaft 43 corresponds to the inner ring.
  • the planetary reduction gear 1 in the embodiment is a known planetary reduction gear, and by fixing any one of the internal gear mechanism 70, the planetary gear 41 and the sun gear 60, the input destination from the drive source and the driven object You can change the output source of As a result, the planetary reduction gear 1 can obtain an arbitrary speed reduction ratio.
  • the planetary gear 41 is rotatably supported by the planetary shaft 43 via the first roller 44 and the second roller 45 .
  • the first rollers 44 and the second rollers 45 are accommodated without using a retainer. That is, in the planetary gear mechanism 40 according to the embodiment, the first rollers 44 and the second rollers 45 constitute the roller bearing 50 which is a full roller bearing.
  • the first roller 44 and the second roller 45 are made of bearing steel such as SUJ2.
  • the second rollers 45 are made of the same material as the first rollers 44 .
  • the first rollers 44 and the second rollers 45 extend, for example, in the axial direction so as to support the planetary gear 41 in the radial direction.
  • FIG. 5 is a side cross-sectional view showing an example of a planetary gear having roller bearings in the embodiment.
  • FIG. 5 shows a cross section taken along line CC of FIG.
  • the length of the first roller 44 and the second roller 45 is approximately 11 mm. Both axial ends of the first roller 44 and the second roller 45 are covered with, for example, a cover (not shown).
  • the sum of the axial lengths of the first rollers 44 and the second rollers 45 and the axial thickness of the cover portions disposed at both ends in the axial direction is approximately the axial length of the planetary gear 41. are identical.
  • FIG. 6 is a perspective view showing an example of first rollers and second rollers in the embodiment.
  • the first roller 44 is formed in a cylindrical shape, that is, when the cross-sectional shape is circular, the diameter da near the end of the first roller 44 on the positive axial direction side
  • the diameter db of the end portion near the direction center and the diameter dc near the end portion on the negative axial direction side are substantially the same as the diameter r1.
  • the diameter dp near the end of the second roller 45 on the positive axial direction, the diameter dq near the center in the axial direction, and the diameter dr near the end on the negative axial direction are equal to the diameter It is substantially the same as r2.
  • FIG. 8 is an enlarged cross-sectional view showing an example of a roller bearing in the background art.
  • the first roller 94 and the second roller 95a engage with each other at the point of contact Ca.
  • the first roller 94 and the second roller 95b engage with each other at the point of contact Cb. Therefore, a torque loss is generated due to friction between the first roller 94 and the second rollers 95a and 95b.
  • FIG. 7 is an enlarged cross-sectional view showing an example of a roller bearing in the embodiment.
  • FIG. 7 is an enlarged view of the portion indicated by the frame F1 in FIG.
  • the diameter r1 of the first roller 44 is " ⁇ 1.18”
  • the diameter r2 of the second roller 45 is " ⁇ 1.17”.
  • the diameter r1 of the first roller 44 substantially matches the interval I1 between the outer circumference of the planetary shaft 43 and the inner circumference 46 of the planetary gear 41. That is, when the first roller 44 is inserted into the planetary gear 41 , the first roller 44 is in contact with the planetary shaft 43 and also in contact with the inner periphery 46 .
  • the diameter r2 of the second roller 45 is slightly smaller than the interval I1 as described above.
  • the second rollers 45 are not in contact with both the planetary shaft 43 and the inner periphery 46 at the same time when they are inserted into the planetary gear 41 .
  • the second roller 45 is formed with a gap G1 corresponding to the difference between the diameter r2 and the interval I1 between the second roller 45a and the planetary shaft 43 in the radial direction.
  • a radial gap G2 may be formed between the second roller 45b and the inner circumference 46.
  • the second roller 45 is arranged movably between the planetary shaft 43 and the inner circumference 46 in the radial direction. In this case, the second roller 45 bears no radial load between the planetary shaft 43 and the inner circumference 46 of the planetary gear 41 .
  • the second roller 45a shown in FIG. Since it does not completely interlock with the movement of the gear 41 and can rotate freely, it does not interfere with the first roller 44 .
  • the roller bearing 50 in the embodiment includes the first rollers 44 and the second rollers 45 arranged between the inner ring 43 and the outer ring 41 and extending in the axial direction. Also, the diameter r2 of the second roller 45 is smaller than the diameter r1 of the first roller 44 . According to such a configuration, it is possible to improve the rotation efficiency.
  • first roller 44 and the second roller 45 have substantially the same length in the axial direction and are made of the same material. Furthermore, each cross-sectional shape of the first roller 44 and the second roller 45 may be constant regardless of the position in the axial direction. Thereby, the manufacturing cost of the first roller 44 and the second roller 45 can be reduced.
  • the second roller 45 is arranged between two adjacent first rollers 44 in the circumferential direction, and the first roller 44 is arranged between the two adjacent second rollers 45 in the circumferential direction. placed in That is, the first rollers 44 and the second rollers 45 are arranged alternately in the circumferential direction. Further, the second rollers 45 are arranged movably between the outer peripheral side of the inner ring 43 and the inner peripheral side of the outer ring 41 in the radial direction. As a result, the second rollers 45 do not bear a radial load, so that they can be prevented from colliding with the first rollers 44 .
  • the embodiment is not limited to this.
  • the first roller 44 and the second roller 45 are made of the same material
  • the embodiment is not limited to this.
  • the second rollers 45 may be made of a highly slidable material having self-lubricating properties, such as resin.
  • the diameter r1 of the first roller 44 and the diameter r2 of the second roller 45 shown in each embodiment are merely examples, and are within a range in which rattling of the first roller 44 does not occur in the circumferential and radial directions.
  • the diameter r2 of the second roller 45 may be reduced.
  • the diameter r2 of the second roller 45 may be larger if the friction between the second roller 45 and the first roller 44 can be sufficiently reduced, such as when the second roller 45 has self-lubricating properties.
  • the lengths of the rollers may differ from each other. At least one of the first roller and the second roller may be a crowned roller.

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

Abstract

Un roulement à rouleaux (50) comprend un premier rouleau (44) et un second rouleau (45) disposés entre une bague interne (43) et une bague externe (41) et s'étendant dans la direction axiale. Dans le roulement à rouleaux (50), le diamètre du second rouleau (45) est inférieur au diamètre du premier rouleau (44).
PCT/JP2022/014327 2021-03-31 2022-03-25 Roulement à rouleaux et engrenage réducteur de vitesse planétaire WO2022210339A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021061755A JP2022157496A (ja) 2021-03-31 2021-03-31 ころ軸受け及び遊星減速機
JP2021-061755 2021-03-31

Publications (1)

Publication Number Publication Date
WO2022210339A1 true WO2022210339A1 (fr) 2022-10-06

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PCT/JP2022/014327 WO2022210339A1 (fr) 2021-03-31 2022-03-25 Roulement à rouleaux et engrenage réducteur de vitesse planétaire

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JP (1) JP2022157496A (fr)
WO (1) WO2022210339A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0673448U (ja) * 1993-03-31 1994-10-18 エヌティエヌ株式会社 固体潤滑転がり軸受
US20040101225A1 (en) * 2002-11-27 2004-05-27 Del Rio Eddy H. Needle/roller bearing
JP2006071031A (ja) * 2004-09-03 2006-03-16 Ntn Corp 自動調心ころ軸受
JP2007292163A (ja) * 2006-04-24 2007-11-08 Nsk Ltd 分割型ころ軸受
US20160076585A1 (en) * 2013-05-10 2016-03-17 Roller Bearing Company Of America, Inc. Double row preloaded ball bearing with spacer balls
JP2016109253A (ja) * 2014-12-09 2016-06-20 日本精工株式会社 転がり軸受

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0673448U (ja) * 1993-03-31 1994-10-18 エヌティエヌ株式会社 固体潤滑転がり軸受
US20040101225A1 (en) * 2002-11-27 2004-05-27 Del Rio Eddy H. Needle/roller bearing
JP2006071031A (ja) * 2004-09-03 2006-03-16 Ntn Corp 自動調心ころ軸受
JP2007292163A (ja) * 2006-04-24 2007-11-08 Nsk Ltd 分割型ころ軸受
US20160076585A1 (en) * 2013-05-10 2016-03-17 Roller Bearing Company Of America, Inc. Double row preloaded ball bearing with spacer balls
JP2016109253A (ja) * 2014-12-09 2016-06-20 日本精工株式会社 転がり軸受

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