WO2022004175A1 - ローラ軸受 - Google Patents

ローラ軸受 Download PDF

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Publication number
WO2022004175A1
WO2022004175A1 PCT/JP2021/019104 JP2021019104W WO2022004175A1 WO 2022004175 A1 WO2022004175 A1 WO 2022004175A1 JP 2021019104 W JP2021019104 W JP 2021019104W WO 2022004175 A1 WO2022004175 A1 WO 2022004175A1
Authority
WO
WIPO (PCT)
Prior art keywords
spacer
roller
roller bearing
rollers
view
Prior art date
Application number
PCT/JP2021/019104
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
敏和 伴
Original Assignee
Thk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 Thk株式会社 filed Critical Thk株式会社
Publication of WO2022004175A1 publication Critical patent/WO2022004175A1/ja

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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
    • F16C19/34—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
    • 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
    • F16C19/38—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 two or more rows 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
    • 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
    • F16C19/40—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 with loose spacing bodies between the 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
    • F16C33/37—Loose spacing bodies

Definitions

  • the present invention relates to a roller bearing in which a plurality of rollers are arranged between raceway grooves having a V-shaped cross section formed in each of the inner ring and the outer ring, and spacers are arranged between adjacent rollers.
  • roller bearings are known as bearings that can support complex loads that combine radial load, thrust load, and moment load.
  • the roller bearing includes an inner ring, an outer ring, a plurality of rollers arranged in a raceway groove having a V-shaped cross section formed on the surfaces of the inner ring and the outer ring facing each other, and a spacer arranged between adjacent rollers. Be prepared.
  • the spacer is formed with a pocket for storing a lubricant such as grease applied to the roller.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a roller bearing capable of improving the rated load and rigidity even if a spacer is arranged between adjacent rollers.
  • one aspect of the present invention is a roller bearing in which a plurality of rollers are arranged between raceway grooves having a V-shaped cross section formed in each of the inner ring and the outer ring, and spacers are arranged between adjacent rollers.
  • the thickness (t) of the spacers that determines the distance between adjacent rollers is set thin to 20% or less of the roller diameter (D w ), and in order to prevent the spacers from collapsing, a pair of the spacers in a side view.
  • a roller bearing whose angular dimension (D) is set to be larger than the roller diameter (D w).
  • the rated load and rigidity of the roller bearing can be improved by thinning the spacer and increasing the number of rollers. If the spacer is made thinner, the spacer tends to fall between the rolling surfaces of the raceway grooves of the inner ring and the outer ring, but the diagonal dimension (D) of the spacer in the side view is the roller diameter (D w ) (roller diameter D w is the rolling surface). Since it is set to be larger than the distance between them), it is possible to prevent the spacer from collapsing between the rolling surfaces.
  • FIG. 1A is a perspective view of a roller bearing according to the first embodiment of the present invention
  • FIG. 1B is a perspective view of a roller bearing according to the prior art. It is sectional drawing of the roller bearing of this embodiment. It is a perspective view of the spacer of the roller bearing of this embodiment.
  • a detailed view of the spacer (FIG. 4 (a) is a front view
  • FIG. 4 (b) is a sectional view taken along line bb of FIG. 4 (a)
  • FIG. 4 (c) is a line cc of FIG. 4 (a).
  • 5 (a) is a diagram showing the pitch circle diameter of the roller bearing of the present embodiment
  • FIG. 6A is a front view
  • FIG. 6B is a sectional view taken along line bb of FIG. 6A, showing another example of the spacer of the roller bearing of the present embodiment.
  • FIG. 7 is an enlarged view of part VII of FIG.
  • FIG. 9 (a) is a front view
  • FIG. 9 (b) is a sectional view taken along line bb of FIG. 9 (a)
  • FIG. 9 (c) 9 (a) is a cross-sectional view taken along the line cc of FIG. 9 (a).
  • roller bearing according to the embodiment of the present invention will be described with reference to the accompanying drawings.
  • the roller bearing of the present invention can be embodied in various forms, and is not limited to the embodiments described in the present specification.
  • the present embodiment is provided with the intention of allowing those skilled in the art to fully understand the invention by adequately disclosing the specification. (First Embodiment)
  • FIG. 1A is a perspective view of the roller bearing 5 according to the first embodiment of the present invention.
  • FIG. 1B is a perspective view of the roller bearing 25 of the prior art.
  • 1 is an inner ring
  • 2 is an outer ring
  • 3 is a roller
  • 4 is a spacer.
  • a part of the outer ring 2 is cut out in order to show the roller 3 and the spacer 4 arranged between the inner ring 1 and the outer ring 2.
  • the spacer 4 is made thinner than the spacer 24 of the prior art, the distance between the adjacent rollers 3 is narrowed, and the number of rollers 3 arranged between the inner ring 1 and the outer ring 2 is increased. This improves the rated load and rigidity.
  • the thickness t (see FIG. 4B) of the spacer 4 that determines the distance between the adjacent rollers 3 is set to 20% or less of the roller diameter D w , preferably 15% or less, and more preferably 10% or less. ..
  • a raceway groove 6 having a V-shaped cross section extending in the circumferential direction and having a right-angled apex angle is formed on the outer peripheral surface of the inner ring 1.
  • the track groove 6 includes a first rolling surface 6a and a second rolling surface 6b.
  • a raceway groove 7 having a V-shaped cross section extending in the circumferential direction and having a right-angled apex angle is formed on the inner peripheral surface of the outer ring 2.
  • the track groove 7 includes a first rolling surface 7a and a second rolling surface 7b.
  • the outer ring 2 is divided into upper and lower parts.
  • the raceway groove 6 of the inner ring 1 and the raceway groove 7 of the outer ring 2 face each other.
  • the track groove 6 and the track groove 7 form a circulation path 8 having a substantially square cross section.
  • a plurality of rollers 3 are cross-arranged so that the axes of the adjacent rollers 3 are substantially at right angles.
  • the roller 3 has a cylindrical shape.
  • the roller diameter Dw is set to be slightly larger than the axial length L of the roller 3.
  • the roller bearing 5 of this embodiment is a cross roller bearing.
  • the roller 3 is classified into an upward roller 3a and a downward roller 3b.
  • the upward roller 3a revolves between the second rolling surface 6b of the inner ring 1 and the second rolling surface 7b of the outer ring 2 with the line passing through the virtual center point P1 located above as the axis.
  • the downward roller 3b revolves between the first rolling surface 6a of the inner ring 1 and the first rolling surface 7a of the outer ring 2 with the line passing through the virtual center point P2 located below as the axis.
  • FIG. 3 is a perspective view of the spacer 4
  • FIG. 4 is a detailed view of the spacer 4.
  • the configuration of the spacer 4 will be described using the direction when the spacer 4 is viewed from the traveling direction, that is, the vertical, horizontal, and front-rear directions of FIG.
  • the spacer 4 is formed in a substantially square shape (see FIG. 4A).
  • An arcuate chamfer 9 is formed at the corner of the spacer 4.
  • semi-cylindrical concave surfaces 10 and 11 for receiving the rollers 3 are formed at both ends of the spacer 4 in the front-rear direction.
  • the extending directions of the concave surface 10 and the concave surface 11 are at right angles.
  • the cross sections of the concave surfaces 10 and 11 are arcuate in which the radius is slightly larger than the radius of the roller 3.
  • the concave surfaces 10 and 11 and the roller 3 come into contact with each other at the central portion of the concave surfaces 10 and 11.
  • Chamfers 12 are formed on both edges of the concave surfaces 10 and 11.
  • An arcuate pocket 13 for storing a lubricant such as grease is formed in the central portion of the concave surface 10.
  • a similar pocket (not shown) is also formed in the central portion of the concave surface 11.
  • the pocket 13 of the concave surface 10 and the pocket of the concave surface 11 are communicated with each other by a through hole 14 so that the lubricant can move between them.
  • Constrictions 23 having an arc-shaped cross section are formed on the upper surface, the left and right side surfaces, and the lower surface of the spacer 4. Lubricant is stored in the constriction 23.
  • the width of the spacer 4 is A in front view.
  • the height of the spacer 4 is B.
  • the thickness of the spacer 4 that determines the distance between the adjacent rollers 3 is t.
  • the length of the spacer 4 in the traveling direction in the side view is C.
  • the diagonal dimension D of the spacer 4 in the side view> the roller diameter D w is set to prevent the spacer 4 from collapsing.
  • the roller diameter D w is equal to the distance between the first rolling surface 6a of the inner ring 1 and the first rolling surface 7a of the outer ring 2.
  • B and C are set so as to satisfy the following equation (1).
  • a and C are used in order to prevent the spacer 4 from falling between the second rolling surface 6b of the inner ring 1 and the second rolling surface 7b of the outer ring 2. It is set to satisfy the following equation (2).
  • equations (1) and (2) mean that A and B are enlarged to prevent the spacer 4 from collapsing. However, if A and B are increased, the spacer 4 interferes with the raceway grooves 6 and 7. In order to prevent interference, it is necessary to set the upper limits of A and B as follows.
  • FIG. 5A is a diagram showing the pitch circle diameter of the roller bearing 5.
  • 3 is a roller
  • D pw is a pitch circle diameter.
  • the pitch circle diameter D pw is the diameter of a circle connecting the centers of the rollers 3 arranged in the circulation path 8.
  • FIG. 5B is from a direction at an angle of 45 degrees (the direction of the arrow V in FIG. 5A, which is parallel to the first rolling surface 6a of the inner ring 1 and the first rolling surface 7a of the outer ring 2). It is an enlarged view of the circulation path 8 seen.
  • the spacer 4 contacts the first rolling surface 6a of the inner ring 1 at one point N1 and contacts the first rolling surface 7a of the outer ring 2 at two points N2 and N3. do.
  • the first rolling surface 6a of the inner ring 1 and the first rolling surface 7a of the outer ring 2 are both elliptical, so that the point M1 is used.
  • AB max which is the distance between points M2, can be obtained from the following equation (3).
  • roller bearing 5 of this embodiment has been described above. According to the roller bearing 5 of the present embodiment, the following effects are obtained.
  • the thickness t of the spacer 4 that determines the distance between the adjacent rollers 3 is set thin to 20% or less of the roller diameter D w , the rated load and rigidity of the roller bearing 5 can be improved.
  • the spacer 4 When the spacer 4 is made thin, the spacer 4 tends to fall between the first rolling surfaces 6a and 7a and the second rolling surfaces 6b and 7b of the inner ring 1 and the outer ring 2, but the diagonal dimension D of the spacer 4 in the side view. Can be set to be larger than the roller diameter D w to prevent the spacer 4 from collapsing.
  • concave surfaces 10 and 11 for receiving the rollers 3 are formed at both ends of the spacer 4 in the traveling direction, C can be increased even if the thickness t of the spacer 4 is reduced, and the diagonal dimension D of the spacer 4 is increased. be able to.
  • the thickness t of the spacer 4 is set thin to 15% or less of the roller diameter D w , the number of rollers 3 can be increased in the roller bearings 5 of many model numbers.
  • the spacer 4 of the present embodiment is suitable for improving the rated load and rigidity of the cross roller bearing in which the roller 3 is classified into the upward roller 3a and the downward roller 3b.
  • the spacer 4 is made of a molded body obtained by mixing a resin such as nylon with a reinforcing fiber such as glass fiber. By doing so, sufficient strength can be secured even if the spacer 4 is made thin.
  • the thickness a between the central portion of the lower end edge of the concave surface 10 and the central portion of the lower end edge of the concave surface 11 and the upper end edge of the concave surface 10 are formed.
  • FIG. 6 shows another example of the spacer 4.
  • b is set to a ⁇ b.
  • the concave surface 10 and the concave surface 11 are inclined by an angle ⁇ .
  • the axis of the upward roller 3a tends to face the virtual center point P1
  • the axis of the downward roller 3b tends to point to the virtual center point P2.
  • Other configurations of the spacer 4 are the same as the spacer 4 shown in FIG.
  • the thickness t of the spacer 4 that determines the distance between the adjacent rollers 3 is the thickness between the central portion of the concave surface 10 and the central portion of the concave surface 11. ..
  • the diagonal dimension D is the shorter diagonal dimension of the two diagonal dimensions.
  • roller bearing 15 is a cross roller bearing
  • roller bearing 15 of the second embodiment is a parallel roller bearing
  • the axes of the adjacent rollers 3 are arranged in parallel so as to be substantially parallel to each other.
  • the roller 3 is classified into an upward roller 3a and a downward roller 3b.
  • two upper and lower rolling grooves 18 and 19 are formed on the outer peripheral surface of the inner ring 16.
  • Two upper and lower rolling grooves 20 and 21 facing the rolling grooves 18 and 19 are formed on the inner peripheral surface of the outer ring 17.
  • the downward rollers 3b are arranged in parallel between the upper rolling groove 18 and the upper rolling groove 20.
  • the upward rollers 3a are arranged in parallel between the lower rolling groove 19 and the lower rolling groove 21.
  • the upward roller 3a revolves between the rolling surface 19a of the inner ring 16 and the rolling surface 21a of the outer ring 17 with the line passing through the virtual center point P1 located above as the axis.
  • the downward roller 3b revolves around the rolling surface 18a of the inner ring 16 and the rolling surface 20a of the outer ring 17 with the line passing through the virtual center point P2 located below as the axis.
  • FIG. 9 shows the spacer 22 used in the roller bearing 15 of the second embodiment.
  • the structure of the spacer 22 is the same as that of the spacer 4 of the first embodiment, except that the concave surfaces 10 and 11 are formed in parallel in the extending direction.
  • the thickness t of the spacer 22 that determines the distance between adjacent rollers 3 is 20% or less, preferably 15% or less, and more preferably 10% or less of the diameter of the rollers 3. It is set thinly to.
  • the diagonal dimension D of the spacer 22 in the side view is set to be larger than the roller diameter Dw.
  • the spacer 22 is prevented from falling between the rolling surface 19a of the inner ring 16 and the rolling surface 21a of the outer ring 17 and between the rolling surface 18a of the inner ring 16 and the rolling surface 20a of the outer ring 17. can do.
  • the concave surface 10 and the concave surface 11 may be tilted symmetrically by ⁇ .
  • the present invention is not limited to being embodied in the above embodiment, and can be embodied in other embodiments without changing the gist of the present invention.
  • a tapered roller can be used as the roller instead of the cylindrical roller.
  • the tapered rollers may be cross-arranged so that the axes of adjacent tapered rollers are substantially perpendicular to each other, or may be arranged in parallel so that the axes of adjacent tapered rollers are substantially parallel to each other.
  • the diameter of the central portion in the axial direction of the tapered roller is regarded as the diameter of the tapered roller, and the thickness t of the central portion of the spacer and the diagonal dimension D of the central portion of the spacer may be set in the same manner as in the spacer of the above embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
PCT/JP2021/019104 2020-07-02 2021-05-20 ローラ軸受 WO2022004175A1 (ja)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020-114816 2020-07-02
JP2020114816A JP7245808B2 (ja) 2020-07-02 2020-07-02 ローラ軸受

Publications (1)

Publication Number Publication Date
WO2022004175A1 true WO2022004175A1 (ja) 2022-01-06

Family

ID=79315958

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2021/019104 WO2022004175A1 (ja) 2020-07-02 2021-05-20 ローラ軸受

Country Status (3)

Country Link
JP (1) JP7245808B2 (zh)
TW (1) TW202223257A (zh)
WO (1) WO2022004175A1 (zh)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10252748A (ja) * 1997-03-12 1998-09-22 Antetsukusu:Kk 旋回座軸受
JP2013160309A (ja) * 2012-02-06 2013-08-19 Nippon Thompson Co Ltd セパレータを備えた旋回軸受
US20140301684A1 (en) * 2011-09-02 2014-10-09 Cyril Bouron Spacer for rolling bearing, notably used in a wind turbine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0625704Y2 (ja) * 1988-04-21 1994-07-06 博 寺町 旋回ベアリング

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10252748A (ja) * 1997-03-12 1998-09-22 Antetsukusu:Kk 旋回座軸受
US20140301684A1 (en) * 2011-09-02 2014-10-09 Cyril Bouron Spacer for rolling bearing, notably used in a wind turbine
JP2013160309A (ja) * 2012-02-06 2013-08-19 Nippon Thompson Co Ltd セパレータを備えた旋回軸受

Also Published As

Publication number Publication date
JP2022012756A (ja) 2022-01-17
TW202223257A (zh) 2022-06-16
JP7245808B2 (ja) 2023-03-24

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