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WO2018181113A1 - Roulement à rouleaux à auto-alignement - Google Patents

Roulement à rouleaux à auto-alignement Download PDF

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Publication number
WO2018181113A1
WO2018181113A1 PCT/JP2018/012008 JP2018012008W WO2018181113A1 WO 2018181113 A1 WO2018181113 A1 WO 2018181113A1 JP 2018012008 W JP2018012008 W JP 2018012008W WO 2018181113 A1 WO2018181113 A1 WO 2018181113A1
Authority
WO
WIPO (PCT)
Prior art keywords
self
roller bearing
cage
aligning roller
rollers
Prior art date
Application number
PCT/JP2018/012008
Other languages
English (en)
Japanese (ja)
Inventor
常智 相賀
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
Priority claimed from JP2018052581A external-priority patent/JP7170408B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2018181113A1 publication Critical patent/WO2018181113A1/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
    • F16C19/34—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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • 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
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip

Definitions

  • the present invention relates to a self-aligning roller bearing suitable for use in a rotation support portion of an elevator hoisting machine.
  • the rotation support part of the elevator hoisting machine is loaded with the weight of the elevator car and the weight of the transported goods mounted on the car, and the shaft and housing are easily bent. Therefore, the deflection of the shaft and housing is absorbed. Possible spherical roller bearings are often used.
  • a general self-aligning roller bearing has an outer ring having a spherically recessed raceway surface on an inner diameter surface, and an inner ring having a spherically recessed raceway surface facing the outer raceway surface on the outer diameter surface, respectively.
  • the raceway surface of the inner and outer rings is recessed in a spherical shape, and the rollers swell in a spherical shape to complement this, so when the shaft or housing is bent, the inner ring and the outer ring are relatively inclined to align. It is a mechanism that absorbs deflection.
  • this type of conventional self-aligning roller bearing has a problem of contact noise caused by collision or sliding between the cage and other parts, that is, rollers, race rings, or guide wheels, or collision or sliding between the cages. May be.
  • the problem to be solved by the present invention is to reduce the contact noise caused by the cage coming into contact with the roller and the raceway in the self-aligning roller bearing.
  • a self-aligning roller bearing according to the present invention includes an outer ring having a raceway surface that is recessed in a spherical shape on an inner diameter surface, and a spherical shape that is opposed to the raceway surface of the outer ring on the outer diameter surface.
  • An inner ring having raceway surfaces in two rows in the width direction, and a plurality of rollers arranged in two rows between each raceway surface of the inner ring facing the raceway surface of the outer ring, and a rolling surface swelled in a spherical shape,
  • a single annular portion that is incorporated between the inner diameter surface of the outer ring and the outer diameter surface of the inner ring and is positioned between the two rows of rollers, and the annular portion toward each row of the rollers
  • a plurality of pillars extending from the annular part and arranged in parallel in the circumferential direction of the annular part, and having a cage that holds the rollers so as to be rollable by rolling element guides between the pillars adjacent in the circumferential direction; It was.
  • that the cage is guided to the rolling element means that the cage contacts only the roller and is guided to rotate by the roller.
  • the cage is a rolling element guide rather than a bearing ring guide
  • the cage does not come into contact with any parts other than the rollers, and the cage, the bearing ring and the guide ring found in the conventional self-aligning roller bearing No contact sound is generated.
  • the rolling element guide retainer can suppress the behavior of the rollers in the non-load region, so that the contact noise can be further reduced.
  • the comb cage can be designed with a wider pocket inner surface shape than the press cage cage, so that it suppresses the behavior of the rollers and consequently the behavior of the rolling element guide cage itself. be able to.
  • the comb cage can be assembled by inserting the rollers into the pocket in the axial direction, so unlike the cage cage that requires the rollers to be press-fitted from the outside diameter side of the pocket, This is because the inner shape of the pocket can be designed widely. Further, widening the shape of the inner surface of the pocket increases the amount of lubricant interposed between the roller and the pocket, and has the advantage of improving the damper effect by the lubricant. Since a configuration in which two rows of rollers are held by a single cage is adopted, the cages do not come into contact with each other compared to the case of using two cages that respectively hold the rollers in each row. Further reduction can be achieved.
  • the inner shape of the pocket of the cage is a concave shape straddling the diameter of the roller pitch along the outer diameter surface of the roller, and the pocket and the maximum diameter Dw of the roller are It is preferable to adopt a configuration in which 0.01 ⁇ Dw ⁇ C ⁇ 0.02 ⁇ Dw is established for the minimum clearance C of the above.
  • the minimum clearance C the smaller the rotational noise of the self-aligning roller bearing.
  • an excessively small clearance prevents smooth rotation of the roller, so the minimum clearance C is set to 0.01 ⁇ Dw ⁇ C ⁇ 0.
  • the range By setting the range to 02 ⁇ Dw, smooth rotation of the bearing and reduction of rotational noise can be achieved at a high level.
  • the cage when the load load area is on the lower side in the gravitational direction, the cage restrains the roller on the outer diameter side, and the load load area is on the upper side opposite to the gravity direction. In this case, it is preferable to restrain the roller on the inner diameter side. In this case, the cage further suppresses the behavior of the rollers in the non-load region, so that the contact sound can be further reduced.
  • the self-aligning roller bearing it is preferable to employ a configuration further including a seal member for sealing a bearing space formed between the inner ring and the outer ring. If it does in this way, since the contact sound which generate
  • the seal member preferably employs a configuration having a cored bar and a soundproof sheet attached to the cored bar.
  • the soundproof sheet blocks or absorbs the contact sound, the diffusion of the contact sound is further suppressed.
  • the self-aligning roller bearing according to the invention further includes grease sealed in the bearing space, and the grease occupies 60 to 80% (volume ratio) of the static space volume in the bearing space.
  • the grease occupies 60 to 80% (volume ratio) of the static space volume in the bearing space.
  • the amount of grease filled is 60% or more of the static space volume in the bearing space, the grease exhibits a good damper effect, and the contact noise can be further reduced.
  • the amount of grease enclosed is 80% or less of the static space volume in the bearing space, the stirring noise of the grease can be reduced.
  • the self-aligning roller bearing according to the invention preferably employs a configuration in which no parts other than the cage are provided between the rows of the two rollers. If it does in this way, it will be prevented reliably that a holder
  • the self-aligning roller bearing according to the invention may employ a configuration in which the cage is made of resin. If it does in this way, the contact sound at the time of contacting a roller or a bearing ring will be reduced more compared with the case where a cage is metal.
  • the self-aligning roller bearing according to the present invention is suitably used for a rotation support portion of an elevator hoisting machine that is required to reduce annoying collision noise.
  • the self-aligning roller bearing according to the invention is configured as described above, it is possible to reduce the contact noise caused when the cage comes into contact with the roller or the raceway.
  • Sectional view of the self-aligning roller bearing of the first embodiment Plan view of the cage of the self-aligning roller bearing of the first embodiment 2A is a cross-sectional view of the arrow Partially enlarged sectional view of the self-aligning roller bearing of the second embodiment
  • a self-aligning roller bearing 10 according to the first embodiment shown in FIG. 1 includes an outer ring 11, an inner ring 12, a plurality of rollers 13, and a cage 14, and is preferably used for an elevator hoisting machine. The contact noise during rotation is reduced.
  • the entire outer ring 11 has a substantially cylindrical shape, and a single raceway surface 11a is formed on the inner diameter surface thereof.
  • the entire track surface 11a is recessed in a spherical shape.
  • An oil hole 11b penetrating in the radial direction is formed in the central portion of the outer ring 11 in the width direction, and lubricating oil can be supplied into the self-aligning roller bearing 10 through the oil hole 11b.
  • the outer ring 11 is not provided with a hook.
  • the outer ring 11 is attached to a housing of an elevator hoist, for example.
  • wheel 11 is not specifically limited, It can illustrate that it is metal.
  • the inner ring 12 as a whole has a substantially cylindrical shape, and its diameter is smaller than that of the outer ring 11 and is arranged coaxially with the outer ring 11.
  • a raceway surface 12 a is formed on the outer diameter surface of the inner ring 12.
  • the raceway surface 12a is formed in two rows in the width direction of the inner ring 12, and the whole is recessed in a spherical shape.
  • a pair of flanges 12b protruding in the outer diameter direction are provided at both ends in the width direction of the outer diameter surface of the inner ring 12, and the rollers 13 are prevented from falling off.
  • the inner ring 12 is attached to a shaft that supports a sheave of an elevator hoist, for example.
  • wheel 12 is not specifically limited, It can illustrate that it is metal.
  • each roller 13 has a barrel shape as a whole, and its rolling surface swells in a spherical shape.
  • the rollers 13 are positioned between the raceway surface 11 a of the outer ring 11 and the raceway surface 12 a of the inner ring 12, and are arranged in two rows in the width direction of the self-aligning roller bearing 10 corresponding to the two rows of raceway surfaces 12 a of the inner ring 12. Is arranged.
  • the rollers 13 are arranged in parallel at equal intervals in the circumferential direction of the self-aligning roller bearing 10.
  • the material of the roller 13 is not specifically limited, It can illustrate that it is metal.
  • the cage 14 has a single annular portion 14 a and a plurality of pillar portions 14 b, and is assembled between the inner diameter surface of the outer ring 11 and the outer diameter surface of the inner ring 12. It is.
  • the substantially ring-shaped annular portion 14 a is disposed between the rows of the two rollers 13 and faces the boundary of the two raceways 12 a of the inner ring 12.
  • Each of the substantially square columnar portions 14b extends from the annular portion 14a in both directions in the width direction of the self-aligning roller bearing 10 and reaches each row of the rollers 13 in two rows.
  • the column portions 14 b are arranged in parallel at equal intervals in the circumferential direction of the self-aligning roller bearing 10. Further, as shown in FIGS. 2A and 2B, the column portion 14b located on one row and the column portion 14b located on the other row of the rollers 13 in two rows are circumferentially arranged along the annular portion 14a. Are arranged in a phase shifted state. That is, as viewed from the annular portion 14a, the column portions 14b on one side and the column portions 14b on the other side in the width direction of the self-aligning roller bearing 10 are alternately arranged.
  • the tip of the pillar portion 14b of the cage 14, that is, the end opposite to the end connected to the annular portion 14a is a free end that is not connected to other members. This free end terminates on the raceway surface 12 a of the inner ring 12 and does not reach the flange 12 b of the inner ring 12.
  • a space serving as a pocket is formed between the column portions 14b adjacent to each other in the circumferential direction of the self-aligning roller bearing 10, and each roller 13 is rotatably held in each pocket P.
  • the inner surface shape of the pocket P (the shape of the opposing surface facing the circumferential direction of the cage 14 of the column portion 14b) is a concave shape straddling the roller pitch circle diameter along the outer diameter surface of the roller 13 held in the pocket P. ing.
  • the concave shape in the present embodiment is composed of a partial conical surface 14d that accepts the smaller diameter side of the roller 13 and a partial cylindrical surface 14c that accepts the maximum diameter of the roller 13.
  • the partial cylindrical surface 14c is a roller.
  • a minimum clearance is formed between the 13 maximum diameters.
  • the columnar portion 14b on one side and the columnar portion 14b on the other side in the width direction of the self-aligning roller bearing 10 are alternately arranged when viewed from the annular portion 14a.
  • the load applied from the roller 13 to the annular portion 14a and the load applied from the roller 13 in the other row to the annular portion 14a are distributed in the circumferential direction of the annular portion 14a, and concentration of the load is prevented.
  • the diameter of the pocket P of the cage 14 is set to be smaller than the diameter of the pocket P of the conventional general comb cage, that is, the clearance with the roller 13 is set small. Specifically, when the maximum diameter of the roller 13 is Dw and the minimum clearance is C, 0.01 ⁇ Dw ⁇ C ⁇ 0.02 ⁇ Dw is established. Further, the annular portion 14 a and the column portion 14 b of the cage 14 are in contact with only the roller 13 in a stationary state, and are not in contact with the outer ring 11 and the inner ring 12. As a result, the retainer 14 is not rotationally guided (tracked ring guide) by the outer ring 11 and the inner ring 12, but is rotationally guided (rolling body guide) by the roller 13.
  • the inner ring 12 does not have a center collar, so the cage 14 and the center collar do not come into contact with each other, but the distance (gap) between the cage and the cage is set large after providing a center collar and a guide ring. By doing so, rolling element guidance may be realized.
  • the cage 14 as a whole is made of high-strength brass. Although the manufacturing method of the holder
  • retainer 14 is not specifically limited, A shaving (boring) can be illustrated.
  • the configuration of the self-aligning roller bearing 10 according to the embodiment is as described above, and the cage 14 is rotationally guided by the roller 13 and is not in contact with the outer ring 11 or the inner ring 12. Generation of contact sound due to contact is prevented. Since the inner ring 12 does not have a center collar, the generation of contact sound due to the contact with the center collar of the retainer 14 is prevented. Compared with the case where the cage 14 is guided to the outer ring 11 and the inner ring 12, the sliding contact area is reduced, so that the contact sound as a whole is reduced.
  • the cages are compared to the case where two cages are incorporated in the self-aligning roller bearing to hold the rollers 13 of each row.
  • the contact sound is reduced by the amount that no contact sound is generated.
  • a single retainer 14 comprising an annular portion 14a and column portions 14b extending on both sides of the annular portion 14a is used, so that each row of rollers is held.
  • the annular portion 14a is made thicker than a case where two pairs of cages each composed of an annular portion and a column portion extending only on one side of the annular portion are assembled with the annular portions back to back between rows of rollers. be able to.
  • the strength of the annular portion 14a is ensured to be resistant to damage or the like in the use state normally assumed for the rotation support portion of the elevator hoisting machine. can do. Since the pocket diameter of the cage 14 is set smaller than before, the clearance between the pocket P and the place 13 is made as small as possible, and the inner surface shape of the pocket P is a concave shape along the roller outer diameter surface. The posture of the roller 13 and thus the posture of the cage 14 are stable, no abnormal contact occurs, and the contact sound is further reduced.
  • FIG. 3 shows a self-aligning roller bearing 10 according to the second embodiment.
  • the outer ring 11, the inner ring 12, the roller 13 and the retainer 14 have substantially the same configuration as that of the first embodiment, but a pair of seal members 15 are provided on both width surfaces. The configuration is different from that of the first embodiment.
  • each seal member 15 has an annular core 15a, an annular elastic portion 15b covering the outer surface of the core 15a, and a soundproof sheet 15c attached to the inner surface of the core 15a.
  • a fitting portion is provided at the outer end in the radial direction of the seal member 15, and this fitting portion is fitted into seal grooves 11 c formed at both ends in the width direction of the inner diameter surface of the outer ring 11.
  • a lip formed of an elastic portion 15 b is provided at the radially inner end of the seal member 15, and this lip is in contact with the flange 12 b at both ends in the width direction of the outer diameter surface of the inner ring 12.
  • the bearing space of the self-aligning roller bearing 10 formed between the outer ring 11 and the inner ring 12 is sealed. Since the bearing space of the self-aligning roller bearing 10 is sealed with the seal member 15, the contact sound generated by the contact of the cage 14 and 13 or the like is prevented from diffusing to the outside of the self-aligning roller bearing 10. Has been. Therefore, for example, it is difficult for an elevator passenger or the like to hear the contact sound.
  • the inner surface of the cored bar 15a is not covered with the elastic portion 15b, and a soundproof sheet 15c is attached by appropriate means such as sticking. Moreover, the thickness of the metal core 15a is formed larger than the thickness of the metal core in a general sealing member. Due to the soundproofing or sound absorbing effect of the soundproofing sheet 15c and the soundproofing effect of the thick cored bar 15a, the diffusion of contact sound to the outside of the self-aligning roller bearing 10 is further suppressed. The material, type, etc.
  • the soundproof sheet 15c are not particularly limited, but nitrile rubber, woven or non-woven fabric of polyester fiber or polyethylene fiber, a laminate of these, or a laminate of inorganic layers on both sides or one side thereof Can be illustrated.
  • a material having a large surface density and thickness is preferable as a material that provides a significant soundproofing or sound absorption effect.
  • the self-aligning roller bearing 10 of the second embodiment grease (not shown) is sealed in the bearing space, and the lubricity is improved.
  • the amount of grease filled is 60 to 80% (volume ratio) of the static space volume in the bearing space (the volume of the space where the grease can rest), and the contact noise is further reduced by the damper effect of the grease. Yes.
  • the amount of grease filled is less than 60% of the static space volume in the bearing space, a significant damper effect cannot be obtained, and when it exceeds 80% of the static space volume, the agitation sound of the grease during rotation of the self-aligning roller bearing 10 Will become bigger.
  • the comb cage can easily enclose and retain grease on the inner diameter side of the cage and improve the grease damper effect.
  • Types of base oil, thickener, additive, etc. contained in the grease are not particularly limited.
  • the soundproof sheet 15c is attached to the inner surface of the cored bar 15a in the seal member 15, but the manner of mounting is not limited to this, and may be mounted on both the inner and outer surfaces of the cored bar 15a. Further, the soundproof sheet 15c may be attached to the cored bar 15a and covered with the elastic part 15b from above, or the elastic part 15b may be interposed between the cored bar 15a and the soundproofed sheet 15c.
  • the retainer 14 may be configured to constrain the roller 13 on the outer diameter side or may be configured to constrain the roller 13 on the inner diameter side.
  • the cage further suppresses the behavior of the roller in the non-load region, so that the contact noise is further reduced.
  • the cage 14 is made of high-strength brass, but the material of the cage is not limited to this, and can be made of metal other than high-strength brass or resin.
  • the contact noise when the roller contacts the raceway is reduced, and therefore the contact noise can be further reduced.
  • resin is generally lighter than metal, the weight of the whole self-aligning roller bearing can be reduced by making the cage made of resin.
  • the kind of resin is not specifically limited, As a resin excellent in durability, a polyamide resin, a polyether ether ketone resin, and a polyphenylene sulfide resin can be exemplified.
  • the shape of the cage 14 is not limited to the embodiment.

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

Abstract

L'invention concerne un roulement à rouleaux à auto-alignement (10) comprenant un dispositif de retenue (14) possédant : une section annulaire (14a) unique située entre des rangées de rouleaux (13) ; et plusieurs sections de colonne (14b) qui s'étendent à partir de la section annulaire (14a) vers chacune des rangées de rouleaux (13) et qui sont disposées en parallèle dans la direction circonférentielle de la section annulaire (14a). La rotation du dispositif de retenue (14) est guidée par les rouleaux (13) maintenus entre les sections de colonne (14b) adjacentes l'une à l'autre dans la direction circonférentielle. Étant donné que le dispositif de retenue (14) est guidé par un corps de roulement, le dispositif de retenue (14) évite le contact avec des éléments autres que les rouleaux (13), ce qui permet de réduire davantage le son de contact. En outre, le dispositif de retenue (14) est conçu sous la forme d'une unité unique, il n'y a donc pas de contact entre des dispositifs de retenue par comparaison à l'utilisation de deux dispositifs de retenue qui maintiennent respectivement les rouleaux (13) de rangées respectives, ce qui permet de réduire le son de contact.
PCT/JP2018/012008 2017-03-29 2018-03-26 Roulement à rouleaux à auto-alignement WO2018181113A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2017065021 2017-03-29
JP2017-065021 2017-03-29
JP2018052581A JP7170408B2 (ja) 2017-03-29 2018-03-20 自動調心ころ軸受
JP2018-052581 2018-03-20

Publications (1)

Publication Number Publication Date
WO2018181113A1 true WO2018181113A1 (fr) 2018-10-04

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PCT/JP2018/012008 WO2018181113A1 (fr) 2017-03-29 2018-03-26 Roulement à rouleaux à auto-alignement

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111823774A (zh) * 2020-08-21 2020-10-27 浙江四和机械有限公司 带静音式高载荷组件的一体化重型汽车轮毂单元及方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007127167A (ja) * 2005-11-02 2007-05-24 Nsk Ltd 保持器付自動調心ころ軸受
JP2007303608A (ja) * 2006-05-12 2007-11-22 Nsk Ltd 保持器付複列ころ軸受
JP2010190241A (ja) * 2009-02-16 2010-09-02 Nsk Ltd 自動調心ころ軸受
JP2012086954A (ja) * 2010-10-20 2012-05-10 Mitsubishi Electric Building Techno Service Co Ltd 乗客コンベアの回転支持装置
US20150336658A1 (en) * 2007-12-06 2015-11-26 Roller Bearing Company Of America, Inc. Bearing installed on an aircraft structure
JP2016102525A (ja) * 2014-11-27 2016-06-02 日本精工株式会社 自動調心ころ軸受

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007127167A (ja) * 2005-11-02 2007-05-24 Nsk Ltd 保持器付自動調心ころ軸受
JP2007303608A (ja) * 2006-05-12 2007-11-22 Nsk Ltd 保持器付複列ころ軸受
US20150336658A1 (en) * 2007-12-06 2015-11-26 Roller Bearing Company Of America, Inc. Bearing installed on an aircraft structure
JP2010190241A (ja) * 2009-02-16 2010-09-02 Nsk Ltd 自動調心ころ軸受
JP2012086954A (ja) * 2010-10-20 2012-05-10 Mitsubishi Electric Building Techno Service Co Ltd 乗客コンベアの回転支持装置
JP2016102525A (ja) * 2014-11-27 2016-06-02 日本精工株式会社 自動調心ころ軸受

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111823774A (zh) * 2020-08-21 2020-10-27 浙江四和机械有限公司 带静音式高载荷组件的一体化重型汽车轮毂单元及方法
CN111823774B (zh) * 2020-08-21 2024-05-07 浙江四和机械有限公司 带静音式高载荷组件的一体化重型汽车轮毂单元及方法

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