WO2015064480A1 - Roulement à deux rangées de rouleaux cylindriques - Google Patents

Roulement à deux rangées de rouleaux cylindriques Download PDF

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Publication number
WO2015064480A1
WO2015064480A1 PCT/JP2014/078277 JP2014078277W WO2015064480A1 WO 2015064480 A1 WO2015064480 A1 WO 2015064480A1 JP 2014078277 W JP2014078277 W JP 2014078277W WO 2015064480 A1 WO2015064480 A1 WO 2015064480A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer ring
notch
roller bearing
cylindrical
double row
Prior art date
Application number
PCT/JP2014/078277
Other languages
English (en)
Japanese (ja)
Inventor
敬介 鳥井
省吾 望月
Original Assignee
日本精工株式会社
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 日本精工株式会社 filed Critical 日本精工株式会社
Priority to DE212014000206.0U priority Critical patent/DE212014000206U1/de
Priority to CN201490001138.7U priority patent/CN206000871U/zh
Priority to JP2015544962A priority patent/JPWO2015064480A1/ja
Publication of WO2015064480A1 publication Critical patent/WO2015064480A1/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
    • F16C19/28—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 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
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring

Definitions

  • the present invention relates to a double row roller bearing.
  • Sintered pallet carts are designed to circulate on the rails as the wheels roll on the rails.
  • This sinter pallet truck transports the sintered powder when traveling on the straight part located vertically above the rail, and then engages the sprocket with the outer surface of the bearing, It runs on the straight part located in the lower part of the vertical direction. Subsequently, the sintered pallet carriage is engaged with a sprocket on the outer surface of the bearing, and is lifted vertically upward by this sprocket to travel on the other curved portion, and thereafter, the linear portion located above the vertical direction is moved. It is going to run again.
  • the rolling bearing 100 described in Patent Document 1 includes an outer ring 140, a first inner ring member 141, a second inner ring member 142, a plurality of first cylindrical rollers 143, and a plurality of second cylinders. It has a roller 144 and a substantially cylindrical inner ring collar 145.
  • the inner ring saddle wheel 145 is located between the first inner ring member 141 and the second inner ring member 142, and the end face on one side in the axial direction of the inner ring saddle ring 145 is the end face in the axial direction of the first inner ring member 141. It is in contact. Further, the end surface on the other axial side of the inner ring saddle wheel 145 is in contact with the end surface of the second inner ring member 142 in the axial direction.
  • the outer ring 140 includes an inner peripheral cylindrical portion 139, a first inner flange portion 153, and a second inner flange portion 154.
  • the inner peripheral cylindrical portion 139 includes the first cylindrical inner peripheral raceway surface 150 and the second cylinder. It consists of an inner circumferential track surface 151 and an inner circumferential cylindrical portion 152.
  • the first inner flange 153 is located on one side in the axial direction of the inner peripheral cylindrical portion 139, while the second inner flange 154 is located on the other side in the axial direction of the inner peripheral cylindrical portion 139. ing.
  • the first inner ring member 141 has a cylindrical outer raceway surface 160 and a first outer flange portion 163.
  • the first outer flange portion 163 is located on the opposite side to the inner ring flange 145 side in the axial direction of the cylindrical outer raceway surface 160.
  • the second inner ring member 142 has a cylindrical outer raceway surface 161 and a second outer flange portion 164.
  • the second outer flange portion 164 is located on the opposite side to the inner ring flange 145 side in the axial direction of the cylindrical outer raceway surface 161.
  • the outer diameter of the cylindrical outer raceway surface 160 is equal to the outer diameter of the cylindrical outer raceway surface 161.
  • the outer diameter of the outer peripheral surface of the inner ring saddle wheel 145 is larger than the outer diameter of the cylindrical outer peripheral raceway surface 160.
  • the inner diameter of the inner circumferential cylindrical portion 152 is the same as the inner diameter of the first cylindrical inner circumferential raceway surface 150 and the same as the inner diameter of the second cylindrical inner circumferential raceway surface 151.
  • the plurality of first cylindrical rollers 143 are disposed between the first cylindrical inner raceway surface 150 of the outer ring 140 and the cylindrical outer raceway surface 160 of the first inner ring member 141.
  • the plurality of second cylindrical rollers 144 are disposed between the second cylindrical inner circumferential raceway surface 151 of the outer ring 140 and the cylindrical outer circumferential raceway surface 161 of the second inner ring member 142.
  • the outer ring 140 has a shape in which the inner collar portion does not exist between the first cylinder inner circumferential raceway surface 150 and the second cylinder inner circumferential raceway surface 151 of the outer ring 140 as described above. .
  • the outer ring 140 if there is an inner flange portion in the periphery of the outer ring 140 between the first cylindrical inner peripheral raceway surface 150 and the second cylinder inner peripheral raceway surface 151 during the engagement of the sprocket, It is possible to prevent the outer ring 140 from being damaged and to increase the life of the outer ring 140 without causing a large stress concentration that would have occurred due to the contact between the collar and the cylindrical rollers 143 and 144. Can do.
  • Patent Document 1 describes that the service life can be extended as compared with a conventional rolling bearing for a sintered pallet truck.
  • some conventional double row roller bearings with seals used in a sintered pallet carriage have chamfers 170 and 171 provided on the outer peripheral surfaces of both ends in the axial direction of the outer ring 140.
  • the chamfers 170 and 171 provided in the conventional double row roller bearing with seal are formed to have an axial width substantially the same as the axial width of the seals 173 and 174.
  • the chamfers 170 and 171 are designed so that the outer ring seal attachment portions 175 and 176 thinner than the wall thickness of the outer ring 140 are not subjected to a radial load.
  • the chamfers 170 and 171 are the end faces of the inner and outer ring flanges that are generated as a result of the inclination of the outer ring due to the moment of the load generated by the movement of the sprocket when the double row roller bearing with seal is used for the sintered pallet carriage. It is not provided as a measure against galling damage. Therefore, even if the chamfers 170 and 171 are provided on the outer ring 140, there is a possibility that damage is caused by galling of the outer ring, the collar part of the inner ring, and the roller end face.
  • An object of the present invention is to solve the above-mentioned problems, and is to provide a double row rolling bearing capable of reducing local damage and suppressing a reduction in rolling fatigue life.
  • a double row roller bearing comprising an outer ring, an inner ring, and rollers that are freely rollable between the outer ring and the inner ring and are arranged in a plurality of rows in the axial direction.
  • the outer peripheral surface of the outer ring has a cylindrical part having a uniform diameter, and a notch part having a radial dimension shorter than the cylindrical part and extending from both sides of the cylindrical part to the outer ring end face,
  • the double row roller bearing wherein an axial width of the notch is equal to or greater than an axial distance from the outer ring end face to the roller outer end face.
  • the double row roller according to (1) wherein an axial width of the notch portion is equal to or less than a distance from the outer ring end face to a third of the roller length from the roller outer end face. bearing.
  • the notch portion is a virtual conical surface formed by a straight line having a radial dimension at an arbitrary position that extends from a notch start line intersecting the cylindrical portion to a notch end line intersecting the outer ring end surface.
  • notches having an axial width equal to or greater than the axial distance from the outer ring end surface to the roller outer end surface are formed at both axial ends of the outer peripheral surface of the outer ring. Therefore, even when an offset load acts on the outer peripheral surface of the outer ring and misalignment occurs in the bearing, there is no contact with the outer ring engaging member such as a sprocket on the outer peripheral surface of the outer ring near the bearing end surface. No load is applied. As a result, the occurrence of a moment due to the load on the bearing can be suppressed.
  • the double-row cylindrical roller bearing 1 of the present embodiment is freely rollable between an outer ring 10, an inner ring 20, and between the outer ring 10 and the inner ring 20, and in a plurality of rows in the axial direction.
  • an outer ring middle flange portion 11 protrudes on the inner diameter side at the center of the cylindrical inner peripheral surface in the axial direction, one side of the outer ring middle collar portion 11 is a first outer ring raceway surface 12, and the other side is A second outer ring raceway surface 13 is formed.
  • the inner ring 20 is provided with a first inner ring intermediate collar portion 21 projecting on the outer diameter side at the axial center of the cylindrical outer peripheral surface, and ends on one side and the other side in the axial direction of the first inner ring intermediate collar portion 21.
  • a second inner ring outer flange portion 22 and a third inner ring outer flange portion 23 project from the outer diameter side.
  • the first inner ring middle collar portion 21 is opposed to the outer ring middle collar portion 11 of the outer ring 10 in the radial direction, and has a wider axial width than the outer ring middle collar portion 11.
  • the first inner ring intermediate flange 21 has a radial dimension substantially equal to that of the second inner ring outer flange 22 and the third inner ring outer flange 23.
  • a space between the first inner ring intermediate flange 21 and the second inner ring outer flange 22 is a first inner ring raceway surface 25 that faces the first outer ring raceway surface 12, and the first inner ring intermediate flange 21 and the third inner ring.
  • a space between the outer flange portions 23 is a second inner ring raceway surface 26 that faces the second outer ring raceway surface 13.
  • the plurality of cylindrical rollers 30 are provided between the first outer ring raceway surface 12 of the outer ring 10 and the first inner ring raceway surface 25 of the inner ring 20, the second outer ring raceway surface 13 of the outer ring 10, and the second inner ring raceway surface 26 of the inner ring 20.
  • a sealing member (not shown) is attached.
  • the thickness (diameter thickness) of the outer ring 10 in the portion where the cylindrical roller 30 is disposed is configured to be thicker than the thickness of the inner ring 20.
  • the outer circumferential surface of the outer ring 10 has a cylindrical portion 15 having a uniform diameter (same radial dimension), and a cutout having a radial dimension shorter than the cylindrical portion 15 and extending from both sides of the cylindrical portion 15 to the outer ring end surface 16. Part 17.
  • the notch 17 is formed by inclining a region having an axial width (axial distance) L from the outer ring end surface 16 over the entire circumference in the circumferential direction by ⁇ ° with respect to the axial direction. That is, the outer ring 10 has an outer ring formed from a notch start line P1 (a line formed by connecting points indicated by P1 in the cross-sectional view of FIG. 2 in the circumferential direction) where both ends of the outer peripheral surface intersect with the cylindrical part 15. This is an inclined surface 41 that connects up to a notch end line P2 (a line formed by connecting points indicated by P2 in the cross-sectional view of FIG. 2 in the circumferential direction) located on the end face 16.
  • a notch start line P1 a line formed by connecting points indicated by P1 in the cross-sectional view of FIG. 2 in the circumferential direction
  • P2 a line formed by connecting points indicated by P2 in the cross-sectional view of FIG. 2 in the circumferential direction
  • the axial width L of the notch 17 is equal to or greater than the distance L1 from the outer ring end face 16 to the roller outer end face 31 of the cylindrical roller 30, and preferably 1 / of the roller length from the outer ring end face 16 to the roller outer end face 31.
  • the distance up to 3 is less than L2. That is, the axial width L of the notch 17 preferably satisfies the relationship L1 ⁇ L ⁇ L2, as shown in FIG.
  • the cylindrical roller 30 is positioned correctly between the first outer ring raceway surface 12 and the first inner ring raceway surface 25 or between the second outer ring raceway surface 13 and the second inner ring raceway surface 26.
  • the position (neutral position) in the set state is used as a reference.
  • the outer ring 10 is deformed because the shaft and the carriage are bent according to the rigidity of the carriage and the shaft due to the weight of the carriage loaded with the sintered powder. There may be a large tilt with respect to the sprocket.
  • the contact point is a position that is separated from the outer ring end surface 16 on the outer peripheral surface of the outer ring 10 by L1 or more. Since this contact point is on the inner side of the roller pressure receiving width (roller length) of the cylindrical roller 30, generation of a moment due to the load can be suppressed more than on the outer side.
  • the contact point is inside the roller pressure receiving width (roller length) of the cylindrical roller 30, that is, inside the roller outer end surface 31, it is positioned as close as possible to the roller outer end surface 31 of the cylindrical roller 30. Therefore, the area of the outer peripheral surface that receives the load can be secured widely. Therefore, by increasing the axial width L of the notch 17 to the distance L2 or less, the surface pressure of the outer peripheral surface of the outer ring 10 is increased. Can be suppressed.
  • the inclination angle ⁇ of the inclined surface 41 of the notch 17 is preferably 5 ° to 35 °, and more preferably 10 ° to 30 °. If the inclination angle ⁇ of the inclined surface 41 is smaller than 5 °, the outer ring 10 may come into contact with an outer ring engaging member such as a sprocket. If it is larger than 35 °, the outer ring of the seal mounting portion to which the seal member is attached. There is a risk that the strength will be insufficient.
  • the details of the notch portion 17 are shown in FIG. 2 only for the right end portion in the drawing, but the same applies to the left end portion in the drawing (hereinafter the same applies to FIGS. 3 and 4).
  • the notch portion 17 is configured by the inclined surface 41.
  • the notch portion 17 is not limited to this, and the notch portion 17 has a radial dimension at an arbitrary position from the notch start line P1 that intersects the cylindrical portion 15.
  • the virtual conical surface A formed by a straight line connecting up to the notch end line P2 that intersects the end face 16 may be equal to or smaller than the radial distance at that position and greater than or equal to the radial distance of the notch end line P2.
  • the said embodiment is an example which made the notch part 17 the inclined surface 41 along the virtual conical surface A, and is not restricted to this, For example, a notch part like the 1st and 2nd modification demonstrated below 17 may be configured.
  • the notch 17 is cut out by a depth (radial distance) T from the outer ring end face 16 in the axial width L over the entire circumference in the circumferential direction.
  • the outer ring 10 is a cylinder in which both end portions of the outer peripheral surface extend in the axial direction from a vertical surface S1 extending radially inward from a notch start line P1 intersecting the cylindrical portion 15 and a notch end line P2 positioned on the outer ring end surface 16.
  • a step 42 is formed by the surface S2.
  • the notch portion 17 is notched so as to bend a region having an axial width L from the outer ring end surface 16 over the entire circumference in the circumferential direction.
  • the outer ring 10 has a concave curved surface 43 in which both end portions of the outer peripheral surface are connected to a notch start line P1 located on the outer peripheral surface of the outer ring 10 and intersecting the cylindrical portion 15 to a notch end line P2 located on the outer ring end surface 16. It has become.
  • the concave curved surface 43 has a radial distance at an arbitrary position that is equal to or smaller than the radial distance on the virtual conical surface A at that position.
  • the axial width L of the notch 17 in the first and second modifications is equal to or greater than the distance L1 from the outer ring end surface 16 to the roller outer end surface 31 of the cylindrical roller 30 as in the above embodiment, preferably the outer ring.
  • the inclination angle ⁇ of the virtual conical surface A of the notch 17 is preferably 5 ° to 35 °, more preferably 10 ° to 30 °.
  • the axial width L is equal to or greater than the axial distance L1 from the outer ring end surface 16 to the roller outer end surface 31 at both axial ends of the outer peripheral surface of the outer ring 10. Since the notch 17 (sloping structure) is formed, even if an offset load acts on the outer circumferential surface of the outer ring 10 and misalignment occurs in the bearing, the outer circumferential surface of the outer ring 10 near the bearing end surface Since there is no contact with an outer ring engaging member such as a sprocket and no load is applied, it is possible to suppress the occurrence of a moment due to the load in the bearing.
  • the outer ring 10 the flange of the inner ring 20 (the outer ring intermediate flange 11, the first inner ring intermediate flange 21, the second inner ring outer flange 22, the third inner ring outer flange 23) and the roller end surface (roller outer end surface 31). It is possible to suppress the occurrence of local damage (galling) on the roller inner end face. Further, the surface pressure generated between the cylindrical roller 30 and the inner and outer ring raceway surfaces (the first outer ring raceway surface 12, the second outer ring raceway surface 13, the first inner ring raceway surface 25, and the second inner ring raceway surface 26) is locally localized. It becomes difficult to generate a high part, and a decrease in rolling fatigue life can be suppressed.
  • the axial width L of the notch portion 17 is equal to or less than the distance L2 from the outer ring end surface 16 to the roller outer end surface 31 to 1/3 of the roller length, the area of the outer peripheral surface receiving the load can be increased widely. Since it can ensure, the raise of the surface pressure of the outer peripheral surface of the outer ring
  • the present invention is not limited to the embodiments described above, and modifications, improvements, and the like can be made as appropriate.
  • the double-row cylindrical roller bearing is exemplified as the double-row rolling bearing.
  • the present invention is not limited to this and can be applied to a double-row tapered roller bearing or the like.
  • the shape of the notch portion 17 is an imaginary conical surface A in which a radial dimension at an arbitrary position is formed by a straight line connecting from a notch start line P1 intersecting with the cylindrical portion 15 to a notch end line P2 intersecting with the outer ring end surface 16.
  • the inner ring 20 may be composed of two or more inner ring members.
  • the outer ring 10 and the inner ring 20 are combined with one or more intermediate flanges, and as long as two or more outer flanges are provided at both ends (left and right sides with respect to the bearing center line),
  • the number of outer casings can be set as appropriate.
  • only one of the outer ring 10 and the inner ring 20 may be provided with a center collar, two outer collars may be provided at both ends of the outer ring 10 and the inner ring 20, and one middle collar and four outer collars may be combined. .
  • the present invention is based on Japanese Patent Application No. 2013-223649 filed on Oct. 28, 2013, the contents of which are incorporated herein by reference.
  • Double row cylindrical roller bearing Double row roller bearing
  • DESCRIPTION OF SYMBOLS 10 Outer ring 15 Cylindrical part 16 Outer ring end surface 17 Notch part 20
  • Inner ring 30
  • Cylindrical roller (roller) 31
  • Roller outer end surface 41 Inclined surface
  • a Virtual conical surface L Axial width L1 of the notch
  • P1 Notch start line P2 Notch end line

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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 deux rangées de rouleaux cylindriques comportant une bague extérieure, une bague intérieure, et des rouleaux cylindriques en mesure de rouler entre les bagues extérieure et intérieure et disposés en rangées dans le sens axial. La surface périphérique extérieure de la bague extérieure a une partie cylindrique ayant un diamètre uniforme, et des parties à entailles ayant une dimension radiale plus courte que celle de la partie cylindrique et s'étendant depuis les deux côtés de la partie cylindrique jusqu'aux faces d'extrémité de la bague extérieure. La largeur axiale de chaque partie à entailles est supérieure ou égale à la distance axiale entre la face d'extrémité de bague extérieure correspondante et la face d'extrémité extérieure du rouleau correspondant.
PCT/JP2014/078277 2013-10-28 2014-10-23 Roulement à deux rangées de rouleaux cylindriques WO2015064480A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE212014000206.0U DE212014000206U1 (de) 2013-10-28 2014-10-23 Zweireihiges Wälzlager
CN201490001138.7U CN206000871U (zh) 2013-10-28 2014-10-23 多列滚子轴承
JP2015544962A JPWO2015064480A1 (ja) 2013-10-28 2014-10-23 複列ころ軸受

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-223649 2013-10-28
JP2013223649 2013-10-28

Publications (1)

Publication Number Publication Date
WO2015064480A1 true WO2015064480A1 (fr) 2015-05-07

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PCT/JP2014/078277 WO2015064480A1 (fr) 2013-10-28 2014-10-23 Roulement à deux rangées de rouleaux cylindriques

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JP (1) JPWO2015064480A1 (fr)
CN (1) CN206000871U (fr)
DE (1) DE212014000206U1 (fr)
WO (1) WO2015064480A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017008877A1 (de) * 2017-09-21 2019-03-21 Imo Holding Gmbh Schrägrollenlager
KR102295186B1 (ko) * 2019-09-24 2021-09-01 (주)세고스 베어링 조립체
CN218118333U (zh) * 2022-08-25 2022-12-23 瓦房店轴承集团有限责任公司 一种台阶式外径自密封双列圆锥滚子轴承

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63180102U (fr) * 1987-05-15 1988-11-21
JPH11303863A (ja) * 1998-04-15 1999-11-02 Nippon Seiko Kk シェル型ころ軸受
JP2010019367A (ja) * 2008-07-11 2010-01-28 Jtekt Corp 焼結パレット台車用転がり軸受
JP2012072818A (ja) * 2010-09-28 2012-04-12 Ntn Corp 車輪用軸受
JP2014163481A (ja) * 2013-02-27 2014-09-08 Nsk Ltd 焼結パレット台車用複列式円筒ころ軸受

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013223649A (ja) 2012-04-23 2013-10-31 Rends Co Ltd マッサージ器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63180102U (fr) * 1987-05-15 1988-11-21
JPH11303863A (ja) * 1998-04-15 1999-11-02 Nippon Seiko Kk シェル型ころ軸受
JP2010019367A (ja) * 2008-07-11 2010-01-28 Jtekt Corp 焼結パレット台車用転がり軸受
JP2012072818A (ja) * 2010-09-28 2012-04-12 Ntn Corp 車輪用軸受
JP2014163481A (ja) * 2013-02-27 2014-09-08 Nsk Ltd 焼結パレット台車用複列式円筒ころ軸受

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Publication number Publication date
CN206000871U (zh) 2017-03-08
JPWO2015064480A1 (ja) 2017-03-09
DE212014000206U1 (de) 2016-06-01

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