WO2015064480A1 - Double-row roller bearing - Google Patents

Double-row roller bearing 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
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WO
WIPO (PCT)
Prior art keywords
outer ring
notch
roller bearing
cylindrical
double row
Prior art date
Application number
PCT/JP2014/078277
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French (fr)
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 CN201490001138.7U priority Critical patent/CN206000871U/en
Priority to DE212014000206.0U priority patent/DE212014000206U1/en
Priority to JP2015544962A priority patent/JPWO2015064480A1/en
Publication of WO2015064480A1 publication Critical patent/WO2015064480A1/en

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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
    • F16C19/28—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

Abstract

A double-row cylindrical roller bearing is provided with an outer race, an inner race, and cylindrical rollers rollable between the outer and inner races and axially disposed in rows. The outer peripheral surface of the outer race has a cylindrical portion having a uniform diameter, and notched portions having a radial dimension shorter than that of the cylindrical portion and extending from both sides of the cylindrical portion to the outer race end faces. The axial width of each notched portion is greater than or equal to the axial distance between the corresponding outer race end face and the outer end face of the corresponding roller.

Description

複列ころ軸受Double row roller bearing
　本発明は、複列ころ軸受に関する。 The present invention relates to a double row roller bearing.
　焼結パレット台車は、車輪がレール上を転動することによって、レール上を循環するようになっている。この焼結パレット台車は、レールの鉛直方向上方に位置する直線部分を走行している際に焼結粉体を運搬し、その後、軸受の外面にスプロケットを係合させて、一方の曲線部を介して鉛直方向下方に位置する直線部分を走行する。続いて、焼結パレット台車は、軸受の外面にスプロケットを係合させて、このスプロケットによって、鉛直方向上方に持ち上げられて他方の曲線部を走行し、その後、鉛直方向上方に位置する直線部を再度走行するようになっている。 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.
　このような焼結パレット台車に用いられる転がり軸受として、特許文献１に記載の複列円筒転がり軸受が知られている。特許文献１に記載の転がり軸受１００は、図５に示すように、外輪１４０と、第１内輪部材１４１と、第２内輪部材１４２と、複数の第１円筒ころ１４３と、複数の第２円筒ころ１４４と、略円筒状の内輪鍔輪１４５とを有する。内輪鍔輪１４５は、第１内輪部材１４１と第２内輪部材１４２との間に位置し、内輪鍔輪１４５の軸方向の一方の側の端面は、第１内輪部材１４１の軸方向の端面に当接している。また、内輪鍔輪１４５の軸方向の他方の側の端面は、第２内輪部材１４２の軸方向の端面に当接している。 As a rolling bearing used for such a sintered pallet truck, a double-row cylindrical rolling bearing described in Patent Document 1 is known. As shown in FIG. 5, 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.
　外輪１４０は、内周円筒部１３９と、第１内鍔部１５３と、第２内鍔部１５４とを有し、内周円筒部１３９は、第１円筒内周軌道面１５０と、第２円筒内周軌道面１５１と、内周円筒部１５２とからなっている。第１内鍔部１５３は、内周円筒部１３９の軸方向の一方の側に位置している一方、第２内鍔部１５４は、内周円筒部１３９の軸方向の他方の側に位置している。 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.
　第１内輪部材１４１は、円筒外周軌道面１６０と、第１外鍔部１６３とを有する。第１外鍔部１６３は、円筒外周軌道面１６０の軸方向の内輪鍔輪１４５側とは反対側に位置している。また、第２内輪部材１４２は、円筒外周軌道面１６１と、第２外鍔部１６４とを有する。第２外鍔部１６４は、円筒外周軌道面１６１の軸方向の内輪鍔輪１４５側とは反対側に位置している。円筒外周軌道面１６０の外径は、円筒外周軌道面１６１の外径と等しくなっている。また、内輪鍔輪１４５の外周面の外径は、円筒外周軌道面１６０の外径よりも大きくなっている。 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. Further, 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. Further, 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.
　内周円筒部１５２の内径は、第１円筒内周軌道面１５０の内径と同一であり、第２円筒内周軌道面１５１の内径と同一になっている。 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.
　複数の第１円筒ころ１４３は、外輪１４０の第１円筒内周軌道面１５０と、第１内輪部材１４１の円筒外周軌道面１６０との間に、配置されている。また、複数の第２円筒ころ１４４は、外輪１４０の第２円筒内周軌道面１５１と、第２内輪部材１４２の円筒外周軌道面１６１との間に、配置されている。 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.
　特許文献１によれば、このように外輪１４０は、外輪１４０の第１円筒内周軌道面１５０と第２円筒内周軌道面１５１との間に、内鍔部が存在しない形状とされている。これにより、スプロケットの係合時において、外輪１４０における第１円筒内周軌道面１５０と第２円筒内周軌道面１５１との間の周辺に、内鍔部が存在していたならば、その内鍔部と円筒ころ１４３、１４４との接触に起因して発生したであろう大きな応力集中が発生することがなく、外輪１４０の損傷を抑制することができて、外輪１４０の寿命を長くすることができる。その結果、従来の焼結パレット台車用転がり軸受と比較して寿命を長くすることができることが特許文献１に記載されている。 According to Patent Document 1, 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. . As a result, 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. As a result, Patent Document 1 describes that the service life can be extended as compared with a conventional rolling bearing for a sintered pallet truck.
　また、図６に示すように、焼結パレット台車に用いられる従来のシール付き複列ころ軸受には、外輪１４０の軸方向両端部の外周面に面取り１７０，１７１を設けたものがある。 Further, as shown in FIG. 6, 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.
日本国特開２０１０－１９３６７号公報Japanese Unexamined Patent Publication No. 2010-19367
　しかしながら、特許文献１に記載の転がり軸受では、外輪の外周面にオフセット荷重が作用し、軸受にミスアライメントが発生した場合、外輪、内輪の鍔部及びころ端面が、局部的な接触により損傷（かじりが発生）する虞があった。また、ころ転動面と内外輪軌道面の接触が均一ではなくなるため、ころと内外輪軌道面の間に発生する面圧が局部的に高くなる箇所が発生し、転がり疲れ寿命が低下する虞があった。 However, in the rolling bearing described in Patent Document 1, when an offset load is applied to the outer peripheral surface of the outer ring and misalignment occurs in the bearing, the outer ring, the inner ring flange and the roller end surface are damaged due to local contact ( There was a risk of galling. In addition, since the contact between the roller rolling surface and the inner and outer ring raceway surfaces is not uniform, there is a possibility that the surface pressure generated between the roller and the inner and outer ring raceway surfaces is locally increased, and the rolling fatigue life may be reduced. was there.
　また、上記従来のシール付き複列ころ軸受に設けた面取り１７０，１７１は、シール１７３，１７４の軸方向幅とほぼ同じ程度の軸方向幅に形成されている。この面取り１７０，１７１は、外輪１４０の軌道輪位置の肉厚より薄い外輪のシール取り付け部１７５，１７６に、ラジアル荷重を受けさせないように設計したものである。つまり、面取り１７０，１７１は、シール付き複列ころ軸受を焼結パレット台車に用いた場合に、スプロケットの運動で発生した荷重のモーメントにより外輪が傾き、その結果として発生する内外輪鍔部ところ端面のかじり損傷の対策として設けたものではない。したがって、面取り１７０，１７１を外輪１４０に設けても、上記した外輪、内輪の鍔部及びころ端面のかじりによる損傷が発生する虞がある。 Further, 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. In other words, 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.
　本発明の目的は、上記課題を解消するためになされたものであり、局部的な損傷を低減するとともに、転がり疲れ寿命の低下を抑制可能な複列転がり軸受を提供することにある。 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.
　上記目的は以下の構成により達成される。
（１）　外輪と、内輪と、前記外輪と前記内輪との間に転動自在とされ、且つ、軸方向に複数列に配置されたころと、を備えた複列ころ軸受において、
　前記外輪の外周面は、一様径を有する円筒部と、該円筒部よりも短い径方向寸法を有し該円筒部の両側から外輪端面まで延びる切り欠き部と、を有し、
　該切り欠き部の軸方向幅は、前記外輪端面からころ外側端面までの軸方向距離以上であることを特徴とする複列ころ軸受。
（２）　該切り欠き部の軸方向幅は、前記外輪端面から、前記ころ外側端面からころ長さの１／３までの距離以下であることを特徴とする（１）に記載の複列ころ軸受。
（３）　前記切り欠き部は、任意の位置における径方向寸法が、前記円筒部と交わる切り欠き開始線から前記外輪端面と交わる切り欠き終了線までを結ぶ直線によって形成される仮想円錐面のその位置における径方向距離以下、かつ、前記切り欠き終了線の径方向距離以上であることを特徴とする（１）又は（２）に記載の複列ころ軸受。
（４）　前記仮想円錐面は、軸方向に対する傾斜角度が５°～３５°の範囲内であることを特徴とする（３）に記載の複列ころ軸受。
（５）　該切り欠き部は、前記仮想円錐面に沿う傾斜面であることを特徴とする（３）又は（４）に記載の複列ころ軸受。
（６）　前記ころは円筒ころであることを特徴とする（１）～（５）のいずれかに記載の複列ころ軸受。
（７）　焼結パレット台車に用いられることを特徴とする（１）～（６）のいずれかに記載の複列ころ軸受。 The above object is achieved by the following configuration.
(1) In 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.
(2) 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.
(3) 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. The double row roller bearing according to (1) or (2), wherein the double row roller bearing is not more than a radial distance at a position and not less than a radial distance of the notch end line.
(4) The double row roller bearing according to (3), wherein the virtual conical surface has an inclination angle with respect to an axial direction in a range of 5 ° to 35 °.
(5) The double row roller bearing according to (3) or (4), wherein the notch is an inclined surface along the virtual conical surface.
(6) The double row roller bearing according to any one of (1) to (5), wherein the roller is a cylindrical roller.
(7) The double row roller bearing according to any one of (1) to (6), which is used for a sintered pallet carriage.
　本発明の複列ころ軸受によれば、外輪の外周面の軸方向両端部に、外輪端面からころ外側端面までの軸方向距離以上の軸方向幅を有する切り欠き部が形成される。そのため、外輪の外周面にオフセット荷重が作用し、軸受にミスアライメントが発生した場合であっても、軸受端面付近の外輪の外周面において、スプロケットのような外輪係合部材との接触がなく、荷重がかからない。その結果、軸受に荷重によるモーメントが発生することが抑えられる。これにより、外輪、内輪の鍔部及びころ端面に、局部的な損傷（かじり）が発生するのを抑制できる。また、ころと内外輪軌道面の間に発生する面圧が局部的に高くなる箇所が発生しづらくなり、転がり疲れ寿命の低下を抑制できる。 According to the double row roller bearing of the present invention, 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. Thereby, it can suppress that local damage (galling) generate | occur | produces in the outer ring | wheel, the collar part of an inner ring | wheel, and a roller end surface. Further, it is difficult to generate a portion where the surface pressure generated between the rollers and the inner and outer ring raceway surfaces is locally increased, and a reduction in rolling fatigue life can be suppressed.
本発明の複列転がり軸受の一実施形態の断面図である。It is sectional drawing of one Embodiment of the double row rolling bearing of this invention. 外輪の切り欠き部を説明するための図１の複列転がり軸受の部分断面図である。It is a fragmentary sectional view of the double row rolling bearing of Drawing 1 for explaining a notch part of an outer ring. 本発明の第２実施形態の複列転がり軸受の部分断面図である。It is a fragmentary sectional view of the double row rolling bearing of a 2nd embodiment of the present invention. 本発明の第３実施形態の複列転がり軸受の部分断面図である。It is a fragmentary sectional view of the double row rolling bearing of a 3rd embodiment of the present invention. 特許文献１に記載の転がり軸受の断面図である。It is sectional drawing of the rolling bearing of patent document 1. 他の従来の転がり軸受の断面図である。It is sectional drawing of the other conventional rolling bearing.
　以下、本発明の複列転がり軸受の一実施形態について図面に基づいて詳しく説明する。なお、以下の説明では、複列転がり軸受として複列円筒ころ軸受を例示する。 Hereinafter, an embodiment of the double row rolling bearing of the present invention will be described in detail with reference to the drawings. In the following description, a double-row cylindrical roller bearing is exemplified as the double-row rolling bearing.
　本実施形態の複列円筒ころ軸受１は、図１に示すように、外輪１０と、内輪２０と、外輪１０と内輪２０との間に転動自在とされ、且つ、軸方向に複数列に配置された複数の円筒ころ３０と、を備える。 As shown in FIG. 1, 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. A plurality of cylindrical rollers 30 arranged.
　外輪１０には、円筒状の内周面の軸方向中央に外輪中鍔部１１が内径側に突設され、外輪中鍔部１１の一方側が第１外輪軌道面１２となっており、他方側が第２外輪軌道面１３となっている。 In the outer ring 10, 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.
　内輪２０には、円筒状の外周面の軸方向中央に第１内輪中鍔部２１が外径側に突設され、第１内輪中鍔部２１の軸方向で一方側と他方側の端部に、第２内輪外鍔部２２と第３内輪外鍔部２３がそれぞれ外径側に突設されている。第１内輪中鍔部２１は、外輪１０の外輪中鍔部１１に径方向で対向し、外輪中鍔部１１よりも軸方向幅が広く形成されている。第１内輪中鍔部２１は、第２内輪外鍔部２２と第３内輪外鍔部２３と略等しい径方向寸法を有している。第１内輪中鍔部２１と第２内輪外鍔部２２の間は、第１外輪軌道面１２と対向する第１内輪軌道面２５となっており、第１内輪中鍔部２１と第３内輪外鍔部２３の間は、第２外輪軌道面１３と対向する第２内輪軌道面２６となっている。 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. In addition, 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.
　複数の円筒ころ３０は、外輪１０の第１外輪軌道面１２と内輪２０の第１内輪軌道面２５との間と、外輪１０の第２外輪軌道面１３と内輪２０の第２内輪軌道面２６との間の、２列に配置されている。外輪１０の軸方向両端部には、外部の水等の異物が複列円筒ころ軸受１の内部空間に浸入することを防止し、複列円筒ころ軸受１内に充填されている潤滑剤を保持するシール部材（不図示）が取り付けられている。円筒ころ３０が配置される部分における外輪１０の厚み（径方向の厚み）は、内輪２０の厚みよりも厚くなるよう構成されている。 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. Are arranged in two rows. At both ends in the axial direction of the outer ring 10, foreign substances such as external water are prevented from entering the internal space of the double row cylindrical roller bearing 1, and the lubricant filled in the double row cylindrical roller bearing 1 is retained. 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.
　続いて、本発明の特徴部分である複列円筒ころ軸受１の外輪１０の外周面の形状について図２を参照しながら詳細に説明する。
　外輪１０の外周面は、一様径（同一の径方向寸法）を有する円筒部１５と、該円筒部１５よりも短い径方向寸法を有し円筒部１５の両側から外輪端面１６まで延びる切り欠き部１７と、を有する。 Next, the shape of the outer peripheral surface of the outer ring 10 of the double row cylindrical roller bearing 1 which is a characteristic part of the present invention will be described in detail with reference to FIG.
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.
　切り欠き部１７は、周方向全周に亘って、外輪端面１６から軸方向幅（軸方向距離）Ｌの領域を軸方向に対しθ°傾斜させることで形成される。即ち、外輪１０は、外周面の両端部が、円筒部１５と交わる切り欠き開始線Ｐ１（図２の断面視においてＰ１で示された点が周方向に連なることで形成される線）から外輪端面１６に位置する切り欠き終了線Ｐ２（図２の断面視においてＰ２で示された点が周方向に連なることで形成される線）までを結ぶ傾斜面４１となっている。 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 θ ° 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.
　切り欠き部１７の軸方向幅Ｌは、外輪端面１６から円筒ころ３０のころ外側端面３１までの距離Ｌ１以上であり、好ましくは、外輪端面１６から、ころ外側端面３１からころ長さの１／３までの距離Ｌ２以下である。即ち、切り欠き部１７の軸方向幅Ｌは、図２に示すように、Ｌ１≦Ｌ≦Ｌ２の関係を満たすことが好ましい。円筒ころ３０の位置は、円筒ころ３０が第１外輪軌道面１２と第１内輪軌道面２５との間、または、第２外輪軌道面１３と第２内輪軌道面２６の軌道面間に正しく配置された状態における位置（中立位置）を基準とする。 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.
　これにより、外輪１０の外周面にオフセット荷重が作用し、軸受にミスアライメントが発生した場合でも、軸受端面付近の外輪１０の外周面において、外輪係合部材との接触がなく、荷重がかからない。そのため、軸受に荷重によるモーメントが発生することを抑えられる。 Therefore, even when an offset load acts on the outer peripheral surface of the outer ring 10 and misalignment occurs in the bearing, the outer peripheral surface of the outer ring 10 near the bearing end surface is not in contact with the outer ring engaging member, and no load is applied. For this reason, it is possible to suppress the occurrence of a moment due to the load on the bearing.
　例えば、複列円筒ころ軸受１が焼結パレット台車に用いられた場合、焼結粉体を積載した台車の重量により、軸や台車の剛性に応じて軸や台車が撓むため、外輪１０はスプロケットに対して大きく傾く場合がある。外輪１０とスプロケットに角度がついた状態で両者が接触した場合、その接触点は、外輪１０の外周面における外輪端面１６からＬ１以上離れた箇所となる。この接触点が、円筒ころ３０のころ受圧幅（ころ長さ）よりも内側にあるので、外側にあるよりも荷重によるモーメントの発生が抑えられる。接触点が円筒ころ３０の端面より外側に有る場合、即ち、切り欠き部１７の軸方向幅Ｌが、ころ外側端面３１までの距離Ｌ１より短い場合は、軸受に発生するモーメントの抑制効果が低く、かじり損傷を防止できない場合が生じ得る。 For example, when the double-row cylindrical roller bearing 1 is used in a sintered pallet truck, 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. When the outer ring 10 and the sprocket are in contact with each other at an angle, 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. When the contact point is outside the end surface of the cylindrical roller 30, that is, when the axial width L of the notch 17 is shorter than the distance L1 to the roller outer end surface 31, the effect of suppressing the moment generated in the bearing is low. In some cases, galling damage cannot be prevented.
　また、上記接触点が円筒ころ３０のころ受圧幅（ころ長さ）よりも内側、即ち、ころ外側端面３１よりも内側にある場合でも、できるだけ円筒ころ３０のころ外側端面３１に近い箇所に位置する方が、荷重を受ける外周面の面積をよく広く確保することができるので、切り欠き部１７の軸方向幅Ｌを距離Ｌ２以下とすることで、外輪１０の外周面の面圧の上昇を抑えることができる。 Further, even when 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.
　切り欠き部１７の傾斜面４１の傾斜角度θは、５°～３５°が好ましく、１０°～３０°がさらに好ましい。傾斜面４１の傾斜角度θが５°より小さい場合、外輪１０はスプロケットのような外輪係合部材と接触してしまう可能性があり、３５°より大きい場合、シール部材を取り付けるシール取付部の外輪強度が足りなくなる虞がある。切り欠き部１７の詳細について、図２では、図中右側端部についてのみ記載したが、図中左側端部についても同様である（以下、図３、４についても同様）。 The inclination angle θ of the inclined surface 41 of the notch 17 is preferably 5 ° to 35 °, and more preferably 10 ° to 30 °. If the inclination angle θ 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).
　上記実施形態では、切り欠き部１７を傾斜面４１により構成したが、これに限らず、切り欠き部１７は、任意の位置における径方向寸法が、円筒部１５と交わる切り欠き開始線Ｐ１から外輪端面１６と交わる切り欠き終了線Ｐ２までを結ぶ直線によって形成される仮想円錐面Ａのその位置における径方向距離以下、かつ、切り欠き終了線Ｐ２の径方向距離以上であればよい。上記実施形態は、切り欠き部１７を仮想円錐面Ａに沿った傾斜面４１とした例であり、これに限らず、例えば、以下で説明する第１及び第２変形例のように切り欠き部１７を構成してもよい。 In the above-described embodiment, the notch portion 17 is configured by the inclined surface 41. However, 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.
　第１変形例は、切り欠き部１７を、図３に示すように、周方向全周に亘って、外輪端面１６から軸方向幅Ｌの領域を深さ（径方向距離）Ｔだけ切り欠くことで形成した例である。即ち、外輪１０は、外周面の両端部が、円筒部１５と交わる切り欠き開始線Ｐ１から径方向内側に延びる鉛直面Ｓ１と外輪端面１６に位置する切り欠き終了線Ｐ２から軸方向に延びる円筒面Ｓ２とによって形成される段部４２となっている。 In the first modified example, as shown in FIG. 3, 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. It is an example formed by. That is, 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.
　また、第２変形例は、切り欠き部１７を、図４に示すように、周方向全周に亘って、外輪端面１６から軸方向幅Ｌの領域を凹状に湾曲するように切り欠くことで形成した例である。即ち、外輪１０は、外周面の両端部が、外輪１０の外周面に位置し円筒部１５と交わる切り欠き開始線Ｐ１から外輪端面１６に位置する切り欠き終了線Ｐ２までを結ぶ凹状湾曲面４３となっている。なお、凹状湾曲面４３は、任意の位置における径方向距離がその位置における仮想円錐面Ａ上の径方向距離以下となっている。 Further, in the second modified example, as shown in FIG. 4, 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. This is an example of formation. That is, 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.
　第１及び第２変形例における切り欠き部１７の軸方向幅Ｌは、上記実施形態と同様に、外輪端面１６から円筒ころ３０のころ外側端面３１までの距離Ｌ１以上であり、好ましくは、外輪端面１６から、ころ外側端面３１からころ長さの１／３までの距離Ｌ２以下である。また、切り欠き部１７の仮想円錐面Ａの傾斜角度θは、５°～３５°が好ましく、１０°～３０°がさらに好ましい。 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. A distance L2 or less from the end face 16 to the roller outer end face 31 to 1/3 of the roller length. Further, the inclination angle θ of the virtual conical surface A of the notch 17 is preferably 5 ° to 35 °, more preferably 10 ° to 30 °.
　以上説明したように、上記実施形態及び変形例によれば、外輪１０の外周面の軸方向両端部に、外輪端面１６からころ外側端面３１までの軸方向距離Ｌ１以上の軸方向幅Ｌを有する切り欠き部１７（だらし構造）が形成されるので、外輪１０の外周面にオフセット荷重が作用し、軸受にミスアライメントが発生した場合であっても、軸受端面付近の外輪１０の外周面において、スプロケットのような外輪係合部材との接触がなく、荷重がかからないため、軸受に荷重によるモーメントが発生することを抑えられる。これにより、外輪１０、内輪２０の鍔部（外輪中鍔部１１、第１内輪中鍔部２１、第２内輪外鍔部２２、第３内輪外鍔部２３）及びころ端面（ころ外側端面３１、ころ内側端面）に、局部的な損傷（かじり）が発生するのを抑制できる。また、円筒ころ３０と内外輪軌道面（第１外輪軌道面１２、第２外輪軌道面１３、第１内輪軌道面２５、第２内輪軌道面２６）の間に発生する面圧が局部的に高くなる箇所が発生しづらくなり、転がり疲れ寿命の低下を抑制できる。 As described above, according to the embodiment and the modification, 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. As a result, 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.
　また、切り欠き部１７の軸方向幅Ｌを、外輪端面１６から、ころ外側端面３１からころ長さの１／３までの距離Ｌ２以下とすることで、荷重を受ける外周面の面積をよく広く確保することができるので、外輪１０の外周面の面圧の上昇を抑えることができる。 Further, by setting the axial width L of the notch portion 17 to be 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 | wheel 10 can be suppressed.
　本発明は、前述した各実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。
　上記実施形態では、複列転がり軸受として複列円筒ころ軸受を例示したが、これに限定されるものではなく複列円錐ころ軸受等にも適用可能である。
　切り欠き部１７の形状は、任意の位置における径方向寸法が、円筒部１５と交わる切り欠き開始線Ｐ１から外輪端面１６と交わる切り欠き終了線Ｐ２までを結ぶ直線によって形成される仮想円錐面Ａのその位置における径方向距離以下、かつ、切り欠き終了線Ｐ２の径方向距離以上であれば、任意の形状とすることができる。
　また、内輪２０は、２つ以上の内輪部材から構成されてもよい。
　外輪１０と内輪２０にはあわせて、一つ以上の中鍔と、両端部（軸受の中心線に対して左右両側）に二つ以上の外鍔と、が設けられている限り、中鍔と外鍔の数は適宜設定することができる。例えば、外輪１０と内輪２０のいずれか一方にのみ中鍔を設け、外輪１０と内輪２０の両方の両端部に二つの外鍔を設け、あわせて一つの中鍔と四つの外鍔としてもよい。 The present invention is not limited to the embodiments described above, and modifications, improvements, and the like can be made as appropriate.
In the above-described embodiment, the double-row cylindrical roller bearing is exemplified as the double-row rolling bearing. However, 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. Any shape can be used as long as it is not more than the radial distance at that position and not less than the radial distance of the notch end line P2.
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. For example, 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. .
　本発明は、２０１３年１０月２８日出願の日本国特許出願２０１３－２２３６４９号に基づき、その内容は参照としてここに取り込まれる。 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.
１　　　複列円筒ころ軸受（複列ころ軸受）
１０　　外輪
１５　　円筒部
１６　　外輪端面
１７　　切り欠き部
２０　　内輪
３０　　円筒ころ（ころ）
３１　　ころ外側端面
４１　　傾斜面
Ａ　　　仮想円錐面
Ｌ　　　切り欠き部の軸方向幅
Ｌ１　　外輪端面からころ外側端面までの軸方向距離
Ｌ２　　外輪端面から、ころ外側端面からころ長さの１／３までの距離
Ｐ１　　切り欠き開始線
Ｐ２　　切り欠き終了線
θ　　　傾斜角度 1 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 Axial distance L2 from the outer ring end surface to the roller outer end surface Distance from the outer ring end surface to 1/3 of the roller length from the roller outer end surface P1 Notch start line P2 Notch end line θ Inclination angle

Claims (7)

  1. 　外輪と、内輪と、前記外輪と前記内輪との間に転動自在とされ、且つ、軸方向に複数列に配置されたころと、を備えた複列ころ軸受において、
    　前記外輪の外周面は、一様径を有する円筒部と、該円筒部よりも短い径方向寸法を有し該円筒部の両側から外輪端面まで延びる切り欠き部と、を有し、
    　該切り欠き部の軸方向幅は、前記外輪端面からころ外側端面までの軸方向距離以上であることを特徴とする複列ころ軸受。     In 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 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.
  2. 　該切り欠き部の軸方向幅は、前記外輪端面から、前記ころ外側端面からころ長さの１／３までの距離以下であることを特徴とする請求項１に記載の複列ころ軸受。 The double row roller bearing according to claim 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.
  3. 　前記切り欠き部は、任意の位置における径方向寸法が、前記円筒部と交わる切り欠き開始線から前記外輪端面と交わる切り欠き終了線までを結ぶ直線によって形成される仮想円錐面のその位置における径方向距離以下、かつ、前記切り欠き終了線の径方向距離以上であることを特徴とする請求項１又は２に記載の複列ころ軸受。 The notch portion has a radial dimension at an arbitrary position at a position of a virtual conical surface formed by a straight line connecting a notch start line intersecting the cylindrical portion to a notch end line intersecting the outer ring end surface. The double row roller bearing according to claim 1, wherein the double row roller bearing is not more than a directional distance and not less than a radial distance of the notch end line.
  4. 　前記仮想円錐面は、軸方向に対する傾斜角度が５°～３５°の範囲内であることを特徴とする請求項３に記載の複列ころ軸受。 The double-row roller bearing according to claim 3, wherein the virtual conical surface has an inclination angle with respect to an axial direction in a range of 5 ° to 35 °.
  5. 　該切り欠き部は、前記仮想円錐面に沿う傾斜面であることを特徴とする請求項３又は４に記載の複列ころ軸受。 The double row roller bearing according to claim 3 or 4, wherein the notch is an inclined surface along the virtual conical surface.
  6. 　前記ころは円筒ころであることを特徴とする請求項１～５のいずれか１項に記載の複列ころ軸受。 The double row roller bearing according to any one of claims 1 to 5, wherein the roller is a cylindrical roller.
  7. 　焼結パレット台車に用いられることを特徴とする請求項１～６のいずれか１項に記載の複列ころ軸受。 The double row roller bearing according to any one of claims 1 to 6, wherein the double row roller bearing is used in a sintered pallet carriage.
PCT/JP2014/078277 2013-10-28 2014-10-23 Double-row roller bearing WO2015064480A1 (en)

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DE212014000206.0U DE212014000206U1 (en) 2013-10-28 2014-10-23 Double row rolling bearing
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DE102017008877A1 (en) * 2017-09-21 2019-03-21 Imo Holding Gmbh Tapered roller bearings
KR102295186B1 (en) * 2019-09-24 2021-09-01 (주)세고스 Bearing assembly
CN218118333U (en) * 2022-08-25 2022-12-23 瓦房店轴承集团有限责任公司 Step type outer diameter self-sealing double-row tapered roller bearing

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JPS63180102U (en) * 1987-05-15 1988-11-21
JPH11303863A (en) * 1998-04-15 1999-11-02 Nippon Seiko Kk Shell type roller bearing
JP2010019367A (en) * 2008-07-11 2010-01-28 Jtekt Corp Rolling bearing for sintering pallet carriage
JP2012072818A (en) * 2010-09-28 2012-04-12 Ntn Corp Wheel bearing
JP2014163481A (en) * 2013-02-27 2014-09-08 Nsk Ltd Double row type cylindrical roller bearing for sintering pallet truck

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JP2013223649A (en) 2012-04-23 2013-10-31 Rends Co Ltd Massage machine

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JPS63180102U (en) * 1987-05-15 1988-11-21
JPH11303863A (en) * 1998-04-15 1999-11-02 Nippon Seiko Kk Shell type roller bearing
JP2010019367A (en) * 2008-07-11 2010-01-28 Jtekt Corp Rolling bearing for sintering pallet carriage
JP2012072818A (en) * 2010-09-28 2012-04-12 Ntn Corp Wheel bearing
JP2014163481A (en) * 2013-02-27 2014-09-08 Nsk Ltd Double row type cylindrical roller bearing for sintering pallet truck

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