JP2014105830A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP2014105830A
JP2014105830A JP2012261075A JP2012261075A JP2014105830A JP 2014105830 A JP2014105830 A JP 2014105830A JP 2012261075 A JP2012261075 A JP 2012261075A JP 2012261075 A JP2012261075 A JP 2012261075A JP 2014105830 A JP2014105830 A JP 2014105830A
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Prior art keywords
outer ring
inner ring
rolling bearing
rows
raceway
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Japanese (ja)
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Toshiya Kakizaki
敬也 柿崎
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JTEKT Corp
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JTEKT Corp
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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
    • F16C19/34—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
    • F16C19/383—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • 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
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing which is operated under low torque, has superior reliability and is easily assembled.SOLUTION: There is provided a rolling bearing 1 including: an outer ring member 2 having two rows of outer ring raceways 2a; an inner ring 3 having an inner ring raceway 3a at the outer periphery center of the inner ring; two rows of a plurality of conical rollers 4 arranged in a freely rollable manner between the outer ring raceway 2a and the inner ring raceway 3a; and two cages 5 in which a plurality of pockets 5a for holding the plurality of conical rollers 4 are formed. The conical roller 4 has a cone-shaped rolling surface 4a. The outer ring member 2 has: two rows of outer ring raceways 2a of cone shape whose large diameters are along an axial center direction of the outer ring member 2; and two rib surfaces 2b which are diametrically reduced from large diameter ends of both outer ring raceways 2a toward a diametrical inside and are in contact with the large diameter-side end surfaces of the rolling surface. The inner ring 3 is formed into such a spherical shape that the inner ring raceway 3a are in internal contact with the rolling surfaces 4a of the two rows of the plurality of conical rollers 4.

Description

本発明は転がり軸受に係わり、より詳しくは、内外輪間に調心機能を有する転がり軸受に関する。   The present invention relates to a rolling bearing, and more particularly to a rolling bearing having a centering function between inner and outer rings.

風力発電装置の主軸を支持する軸受としては、構造上、調心性が求められるため、外輪軌道が球面に形成され、樽型のころを有する自動調心ころ軸受が使用されている。風力発電装置に使用される軸受は、発電の効率化のため、低い摩擦力が求められる。又、風力発電装置に使用される軸受は、塔の最上部の発電装置に組込まれており、保守や交換が困難なため、高い信頼性が求められる。   As a bearing for supporting the main shaft of the wind power generator, since alignment is required for the structure, a self-aligning roller bearing having a barrel-shaped roller and having an outer ring raceway formed on a spherical surface is used. Bearings used in wind power generators are required to have a low frictional force in order to improve power generation efficiency. Moreover, since the bearing used for a wind power generator is incorporated in the power generator of the uppermost part of a tower, and maintenance and replacement | exchange are difficult, high reliability is calculated | required.

自動調心ころ軸受においては、ころ軸線方向のころの直径の変化と、ころとの接触位置における外輪軌道、内輪軌道の直径の変化とが比例していないため、ころ軸線方向の接触位置でのころの公転速度に差が生じ、差動滑りが発生する。この差動滑りにより、ころの軸線が軸受の軸線に対して、円周方向に傾く、いわゆるころのスキューが発生する。   In self-aligning roller bearings, the change in the diameter of the roller in the roller axis direction is not proportional to the change in the diameter of the outer ring raceway and the inner ring raceway at the contact position with the roller. A difference occurs in the revolution speed of the rollers, and differential slip occurs. This differential slip causes a so-called roller skew in which the roller axis is inclined in the circumferential direction with respect to the bearing axis.

ころのスキューは内輪に設けられた鍔面で抑制されるが、鍔面ところの端面は滑り接触であり、大きな摩擦力が発生する。また、軸受が軸心を水平に配置された場合、内輪に設けられた鍔面には潤滑剤が到達しにくく、摩擦力がさらに増大する。さらに、大きな摩擦力によって鍔面ところの端面の温度が上昇し、スメアリング等の不具合が発生しやすくなる。   The skew of the rollers is suppressed by the flange surface provided on the inner ring, but the end surface of the flange surface is a sliding contact, and a large frictional force is generated. Further, when the bearing is arranged horizontally with the shaft center, the lubricant is difficult to reach the collar surface provided on the inner ring, and the frictional force further increases. Furthermore, the temperature of the end surface at the heel surface increases due to a large frictional force, and problems such as smearing tend to occur.

調心機能を有し、かつ、鍔面へ潤滑剤が到達しやすい軸受として、外輪に鍔面を有し、内輪軌道が球形状に形成され、鼓型の転動体を有する転がり軸受がある。（特許文献１の図１２参照）   As a bearing having a centering function and allowing the lubricant to easily reach the flange surface, there is a rolling bearing having a flange surface on the outer ring, an inner ring raceway formed in a spherical shape, and a drum-shaped rolling element. (See FIG. 12 of Patent Document 1)

特開平７−２５９８６４号公報JP-A-7-259864

しかしながら、特許文献１の転がり軸受においても、ころ軸線方向のころの直径の変化と、接触位置における外輪軌道、内輪軌道の直径の変化とが比例していないため、差動滑りによるころのスキューが発生する。さらに、ころの転動面の軸線方向の曲率半径が前述の樽型のころより小さいことから、特に、内輪軌道と、ころの転動面との接触においては、その傾向はさらに強くなる。この結果、ころのスキューはより大きく、外輪軌道、内輪軌道と、ころの転動面との間の摩擦力も大きい。   However, even in the rolling bearing of Patent Document 1, the change in the diameter of the roller in the roller axis direction is not proportional to the change in the diameter of the outer ring raceway and the inner ring raceway at the contact position. Occur. Furthermore, since the radius of curvature of the rolling surface of the roller in the axial direction is smaller than that of the barrel-shaped roller described above, the tendency becomes even stronger especially in the contact between the inner ring raceway and the rolling surface of the roller. As a result, the roller skew is larger, and the frictional force between the outer ring raceway, the inner ring raceway, and the rolling surface of the roller is also greater.

この発明の目的は、差動滑りを防止し、低トルクで、かつ、信頼性に優れた転がり軸受を提供することにある。   An object of the present invention is to provide a rolling bearing that prevents differential slip, has low torque, and is excellent in reliability.

前記の課題を解決するため、請求項１に係る発明の構成上の特徴は、内周面に２列の外輪軌道を有する外輪部材と、外周中央に前記外輪軌道に対向する内輪軌道、を有する内輪と、前記外輪軌道と前記内輪軌道との間に転動自在に配置された２列の複数の円すいころと、前記複数の円すいころを保持する複数のポケットが形成された保持器とを有する転がり軸受であって、前記円すいころは円すい形状の転動面を有し、前記外輪部材は前記外輪部材の軸方向中央方向を大径とする円すい形状の複列の外輪軌道と、前記両外輪軌道の大径側端部から径方向内方に縮径しかつ前記円すいころの転動面の大径側端面に接する２つの鍔面を有し、前記内輪は前記内輪軌道が前記２列の複数のころに内接する球形状に形成されていることである。   In order to solve the above problems, the structural features of the invention according to claim 1 include an outer ring member having two rows of outer ring raceways on the inner peripheral surface, and an inner ring raceway facing the outer ring raceway at the outer peripheral center. An inner ring; a plurality of tapered rollers arranged in two rows between the outer ring raceway and the inner ring raceway; and a cage formed with a plurality of pockets for holding the plurality of tapered rollers. A rolling bearing, wherein the tapered roller has a conical rolling surface, the outer ring member is a conical double row outer ring raceway having a large diameter in the axial direction central direction of the outer ring member, and both the outer rings. The inner ring has two flange surfaces that are radially inwardly reduced from the large-diameter end of the raceway and in contact with the large-diameter end surface of the rolling surface of the tapered roller. It is formed in a spherical shape inscribed in the plurality of rollers.

本発明の構成によると、前記円すいころが前記外輪軌道に接して公転する場合、前記円すいころの軸線方向の直径の変化と、円すいころとの接触位置における前記外輪軌道の直径の変化とは比例しており、前記円すいころの軸線方向全ての位置において、前記円すいころの公転回転数が等しくなる。この結果、差動滑りによる円すいころのスキューが生じることがなく、円すいころの端面と前記外輪部材の鍔面の間の摩擦力は従来の調心性を有する転がり軸受に比べ小さい。   According to the configuration of the present invention, when the tapered roller revolves in contact with the outer ring raceway, the change in the axial diameter of the tapered roller is proportional to the change in the diameter of the outer ring raceway at the contact position with the tapered roller. Thus, the revolution speed of the tapered roller becomes equal at all positions in the axial direction of the tapered roller. As a result, the skew of the tapered roller due to differential slip does not occur, and the frictional force between the end surface of the tapered roller and the flange surface of the outer ring member is smaller than that of a rolling bearing having a conventional aligning property.

また、前記円すいころと前記内輪軌道は点接触となり、回転時の摩擦力は線接触にくらべ小さい。さらに前記鍔面が外輪に形成されていることにより前記鍔面の潤滑性能は、鍔面が内輪に形成されている場合にくらべ優れている。   Further, the tapered roller and the inner ring raceway are in point contact, and the frictional force during rotation is smaller than that in line contact. Further, since the flange surface is formed on the outer ring, the lubricating performance of the flange surface is superior to that when the flange surface is formed on the inner ring.

前記の課題を解決するため、請求項２に係る発明の構成上の特徴は前記内輪の最大直径が、前記外輪部材および前記保持器の最小直径より小さいことである。   In order to solve the above-mentioned problem, the structural feature of the invention according to claim 2 is that the maximum diameter of the inner ring is smaller than the minimum diameters of the outer ring member and the cage.

本発明の構成によると、前記転がり軸受の組立工程において、前記外輪部材と前記保持器の内方に、前記内輪の軸線を、前記外輪および前記保持器の軸線に対し９０°傾けて前記内輪を挿入した状態で、前記外輪部材と前記保持器の内周から前記複数の円すいころを挿入することにより、容易に組立ることができる。   According to the configuration of the present invention, in the assembly process of the rolling bearing, the inner ring is inclined by 90 ° with respect to the outer ring and the cage inwardly of the outer ring member and the cage. By inserting the plurality of tapered rollers from the inner periphery of the outer ring member and the cage in the inserted state, the assembly can be easily performed.

前記の課題を解決するため、請求項３に係る発明の構成上の特徴は、前記外輪部材は、１列の外輪軌道を有する２個の外輪からなることである。   In order to solve the above-mentioned problem, the structural feature of the invention according to claim 3 is that the outer ring member is composed of two outer rings having one row of outer ring raceways.

本発明の構成によると、前記転がり軸受の組立工程において、前記外輪、前記保持器および１列の複数の円すいころ、との組立品２組を、前記内輪の軸方向両側側方から装着することにより、容易に組立ることができる。   According to the configuration of the present invention, in the assembly process of the rolling bearing, two sets of assemblies including the outer ring, the cage, and a plurality of tapered rollers in a row are mounted from both sides in the axial direction of the inner ring. Therefore, it can be assembled easily.

この発明によれば、差動滑りを防止することにより、低トルクで、信頼性に優れ、かつ組立が容易な転がり軸受を提供することができる。   According to the present invention, it is possible to provide a rolling bearing that is low in torque, excellent in reliability, and easy to assemble by preventing differential slip.

本発明の実施形態の転がり軸受の断面図である。It is sectional drawing of the rolling bearing of embodiment of this invention. 本発明の実施形態の転がり軸受の部品の寸法諸元を説明する説明図である。It is explanatory drawing explaining the dimension specification of the components of the rolling bearing of embodiment of this invention. 本発明の実施形態の転がり軸受の作用を説明する説明図である。It is explanatory drawing explaining the effect | action of the rolling bearing of embodiment of this invention.

この発明の実施の形態を、以下図面を参照して説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１は本発明の実施形態の転がり軸受の断面図である。
図２は本発明の実施形態の転がり軸受の部品の寸法諸元を説明する説明図である。
転がり軸受１は外輪部材としての外輪２と、内輪３と、複数の円すいころ４と、２個の保持器５を備えている。 FIG. 1 is a sectional view of a rolling bearing according to an embodiment of the present invention.
FIG. 2 is an explanatory view for explaining dimensions of the components of the rolling bearing according to the embodiment of the present invention.
The rolling bearing 1 includes an outer ring 2 as an outer ring member, an inner ring 3, a plurality of tapered rollers 4, and two cages 5.

外輪２は軸受鋼等の鋼材からなり、内周軸方向中央に径方向内方に凸状の鍔２ｃを有し、両端部から前記鍔２ｃの方向に拡径する２列の円すい形状の外輪軌道２ａが形成されている。前記両外輪軌道２ａの大径側端部、鍔２ｃとの交点から径方向内方に縮径し、内方に凹状の円すい形状の鍔面２ｂが形成されている。また、鍔面２ｂの断面形状は直線または、直線に近い軸方向端面側が凹状の円弧に形成されている。   The outer ring 2 is made of a steel material such as bearing steel, and has two rows of conical outer rings each having a radially inwardly convex flange 2c at the center in the inner circumferential axis direction and expanding in the direction of the flange 2c from both ends. A track 2a is formed. A diameter of the outer ring raceway 2a is reduced radially inward from the intersection of the outer diameter raceway 2a with the flange 2c, and a concave conical flange surface 2b is formed inward. Further, the cross-sectional shape of the flange surface 2b is a straight arc or a concave arc on the axial end face side close to the straight line.

ここで、２列円すい形状の外輪軌道２ａは転がり軸受１の軸線上に頂点Ｏを有している。
また、外輪２の最小直径ｄｏは外輪２の軸方向両端部となっている。 Here, the outer ring raceway 2 a having a two-row cone shape has an apex O on the axis of the rolling bearing 1.
Further, the minimum diameter do of the outer ring 2 is at both axial ends of the outer ring 2.

内輪３は、軸受鋼等の鋼材からなる環体で、内周面３ｂは円筒形状で、外周面に球面の内輪軌道３ａを有する環体である。内輪軌道３ａの球面の半径はＲｉで、球面の中心は内輪３の軸線の軸方向中央にある。すなわち内輪３の最大径位置は内輪３の軸方向中央であり、その直径はＤｉは球面の半径Ｒｉの２倍に等しい。また、最大径位置の直径Ｄｉは外輪２の最小直径ｄｏより小さく形成されている。   The inner ring 3 is a ring made of a steel material such as bearing steel, the inner peripheral surface 3b is a cylindrical shape, and has a spherical inner ring raceway 3a on the outer peripheral surface. The radius of the spherical surface of the inner ring raceway 3 a is Ri, and the center of the spherical surface is at the center in the axial direction of the axis of the inner ring 3. That is, the maximum diameter position of the inner ring 3 is the center in the axial direction of the inner ring 3, and its diameter Di is equal to twice the radius Ri of the spherical surface. Further, the diameter Di at the maximum diameter position is formed smaller than the minimum diameter do of the outer ring 2.

円すいころ４は軸受鋼等の鋼材からなる、円すい台形状で、転動面４ａ、大端面４ｂ、小端面４ｃを有する。ここで転動面４ａは頂点Ｏｒを有する円すい面形状であり、大端面４ｂは、円すい面の頂点Ｏｒから大端面４ｂまでの距離Ｌｒに略等しい曲率半径Ｒｒを持つ球面に形成されている。   The tapered roller 4 has a conical trapezoidal shape made of a steel material such as bearing steel, and has a rolling surface 4a, a large end surface 4b, and a small end surface 4c. Here, the rolling surface 4a has a conical surface shape having a vertex Or, and the large end surface 4b is formed in a spherical surface having a curvature radius Rr substantially equal to a distance Lr from the vertex Or of the conical surface to the large end surface 4b.

保持器５は、炭素鋼等の金属材料を削り加工にてリング状に形成され、軸方向一方側端部に円環部５ｂを有している。また、円環部５ｂから軸方向他方側に複数の柱５ｃを有し、円環部５ｂの他方側側面と２個の柱５ｃの円周方向側面で複数のころ４を転動可能に保持する複数のポケット５ａを区画形成する。ここで、保持器５の最小直径ｄｃは内輪３の最大径位置Ｄｉより大きく形成されている。２個の保持器５は円環部５ｂを対峙して、外輪軌道２ａの内方に配置されている。   The cage 5 is formed in a ring shape by cutting a metal material such as carbon steel, and has an annular portion 5b at one end in the axial direction. In addition, a plurality of columns 5c are provided on the other side in the axial direction from the annular portion 5b, and a plurality of rollers 4 are rotatably held on the other side surface of the annular portion 5b and the circumferential side surfaces of the two columns 5c. A plurality of pockets 5a are formed. Here, the minimum diameter dc of the cage 5 is formed larger than the maximum diameter position Di of the inner ring 3. The two cages 5 are arranged inside the outer ring raceway 2a so as to face the annular portion 5b.

図１および図２に示すように、２列の複数の円すいころ４は、それぞれ外輪２の２列の外輪軌道面２ａと、対向する内輪３の球面の内輪軌道３ａに、転動面４ａを接し、鍔面２ｂに大端面４ｂを接して、２個の保持器５の複数のポケット５ａに所定の間隔に保持され、転動自在に配置されている。このとき、各円すいころ４の転動面４ａの円すいの頂点Ｏｒは外輪軌道２ａの円すいの頂点Ｏと略一致している。   As shown in FIG. 1 and FIG. 2, the plurality of tapered rollers 4 in two rows each have rolling surfaces 4 a on two rows of outer ring raceway surfaces 2 a of the outer ring 2 and spherical inner ring raceways 3 a of the opposed inner rings 3. The large end surface 4b is in contact with the flange surface 2b, is held at a predetermined interval in the plurality of pockets 5a of the two cages 5, and is arranged to be freely rollable. At this time, the vertex Or of the cone of the rolling surface 4a of each tapered roller 4 is substantially coincident with the vertex O of the cone of the outer ring raceway 2a.

このため、ころ４のころ軸線方向全長にわたり、ころ４のテーパ角γと、外輪軌道２ａのテーパ角２αの比率は等しい。すなわち、ころ軸線方向全長にわたり、ころ４の直径Ｄｒｌと、ころ４との接触位置における外輪軌道２ａの直径ｄｏｌとの比率は等しい。   For this reason, the ratio of the taper angle γ of the roller 4 and the taper angle 2α of the outer ring raceway 2a is equal over the entire length in the roller axial direction of the roller 4. That is, the ratio between the diameter Drl of the roller 4 and the diameter dol of the outer ring raceway 2a at the contact position with the roller 4 is equal over the entire length in the roller axial direction.

以下、本発明の実施形態の転がり軸受１の作用および効果について説明する。   Hereinafter, the operation and effect of the rolling bearing 1 according to the embodiment of the present invention will be described.

一般的に、ころ軸線方向のころの直径の変化と、ころとの接触位置における外輪軌道、内輪軌道の直径の変化とが比例していない場合、ころ軸線方向の接触位置でのころの公転速度に差が生じ、差動滑りが発生する。この差動滑りにより、ころ軸線が軸受の軸線に対して、円周方向に傾く、いわゆるころのスキューが発生する。   Generally, when the change in the diameter of the roller in the roller axis direction is not proportional to the change in the diameter of the outer ring raceway and the inner ring raceway at the contact position with the roller, the revolution speed of the roller at the contact position in the roller axis direction A difference occurs between the two and differential slip occurs. This differential slip causes a so-called roller skew in which the roller axis is inclined in the circumferential direction with respect to the bearing axis.

本発明の実施形態の転がり軸受１においては、複数の円すいころ４が外輪軌道２ａに接して公転する場合、円すいころ４のころ軸線方向の直径Ｄｒｌの変化と、円すいころ４と外輪軌道２ａの接触位置における外輪軌道２ａの直径Ｄｏｌの変化とは比例しており、円すいころ４のころ軸線方向全ての位置において、円すいころ４の公転回転数が等しくなる。この結果、差動滑りによる円すいころ４のスキューが生じることはない。   In the rolling bearing 1 according to the embodiment of the present invention, when the plurality of tapered rollers 4 revolve in contact with the outer ring raceway 2a, the change in the diameter Drl of the tapered roller 4 in the roller axial direction, and the tapered roller 4 and the outer ring raceway 2a The change in the diameter Dol of the outer ring raceway 2a at the contact position is proportional, and the revolution speed of the tapered roller 4 is equal at all positions in the roller axial direction of the tapered roller 4. As a result, the skew of the tapered roller 4 due to differential slip does not occur.

また、本発明の実施形態の転がり軸受１においては、内輪軌道３ａは球面に形成されているため、複数の円すいころ４の転動面４ａと内輪軌道３ａとの接触は点接触となり、線接触にくらべ、回転時の摩擦力が小さい。さらに、転がり軸受１が軸線を水平に配置された場合、鍔面２ｂが外輪２に形成されていることにより、鍔面２ｂには潤滑剤が到達し易く、鍔面２ｂの潤滑性能は、鍔面が内輪に形成されている場合くらべ優れている。   Further, in the rolling bearing 1 of the embodiment of the present invention, the inner ring raceway 3a is formed into a spherical surface. Therefore, the contact between the rolling surfaces 4a of the plurality of tapered rollers 4 and the inner ring raceway 3a is a point contact and a line contact. The frictional force during rotation is small compared to Further, when the rolling bearing 1 is arranged with its axis line horizontally, the flange surface 2b is formed on the outer ring 2, so that the lubricant can easily reach the flange surface 2b, and the lubrication performance of the flange surface 2b is It is superior to the case where the surface is formed on the inner ring.

このように、本発明の実施形態の転がり軸受１は、差動滑りによる円すいころ４のスキューによって大きな摩擦力が発生することがなく、さらに潤滑性能が優れていることによって、鍔面ところの端面の温度が上昇による、スミアリング等の不具合が防止でき、低トルクで、かつ信頼性に優れている。   As described above, the rolling bearing 1 according to the embodiment of the present invention does not generate a large frictional force due to the skew of the tapered roller 4 due to the differential slip, and further has excellent lubrication performance. It is possible to prevent problems such as smearing due to the temperature rise, low torque and excellent reliability.

また、本発明の実施形態の転がり軸受１において、内輪３の最大直径Ｄｉは、外輪２の最小直径ｄｏおよび保持器５の最小直径ｄｃより小さい。このため、組立工程において、外輪２と保持器５の内方に、内輪３の軸線を、前記外輪および前記保持器の軸線に対し９０°傾けて内輪を挿入することができる。この状態から、内輪３を外輪２の円周方向に回転させながら、外輪２と保持器５の内周から残りの複数の円すいころ４を挿入することにより、容易に組立ることができる。   In the rolling bearing 1 according to the embodiment of the present invention, the maximum diameter Di of the inner ring 3 is smaller than the minimum diameter do of the outer ring 2 and the minimum diameter dc of the cage 5. Therefore, in the assembly process, the inner ring can be inserted inside the outer ring 2 and the cage 5 with the axis of the inner ring 3 inclined by 90 ° with respect to the axis of the outer ring and the cage. From this state, the inner ring 3 can be easily assembled by inserting the remaining plurality of tapered rollers 4 from the inner circumference of the outer ring 2 and the cage 5 while rotating the inner ring 3 in the circumferential direction of the outer ring 2.

上述の実施形態の転がり軸受１において、外輪部材としての外輪２は、１個の外輪２に２列の外輪軌道２ａが形成されているが、本発明においては、外輪部材は図３に示す転がり軸受２０のように、単列の外輪軌道２２ａを有する２個の外輪２２で構成されていてもよい。   In the rolling bearing 1 of the above-described embodiment, the outer ring 2 as the outer ring member has two rows of outer ring raceways 2a formed on one outer ring 2, but in the present invention, the outer ring member is the rolling ring shown in FIG. Like the bearing 20, you may be comprised by the two outer rings 22 which have the single row outer ring track 22a.

上述の実施形態の転がり軸受において、外輪は外輪軌道の大径側端部のみに鍔が形成されているが、本発明においては、外輪は外輪軌道の大径側端部、および小径側端部の両方に鍔が形成されていてもよい。   In the rolling bearing of the above-described embodiment, the outer ring has a flange formed only at the large-diameter side end of the outer ring raceway. However, in the present invention, the outer ring is the large-diameter side end and the small-diameter side end of the outer ring raceway. A wrinkle may be formed on both.

上述の実施形態の転がり軸受において、保持器は炭素鋼等の金属材料を削り加工にてリング状に形成されたものが２個で構成されているが、本発明においては、保持器は、鋼板をプレス成型されたもの、樹脂で形成されたもの、２列の複数のポケットを１個の保持器に形成されたもの等、他のさまざまな形式のものであってもよい。   In the rolling bearing of the above-described embodiment, the cage is composed of two pieces formed by ringing a metal material such as carbon steel into a ring shape. In the present invention, the cage is a steel plate. Other various types such as those formed by press molding, formed by resin, and formed by two rows of a plurality of pockets in one cage may be used.

１ ‥転がり軸受
２ ‥外輪（外輪部材）
２ａ ‥外輪軌道
２ｂ ‥鍔面
３ ‥内輪
３ａ ‥内輪軌道
４ ‥円すいころ
４ａ ‥転動面
５ ‥保持器
５ａ ‥ポケット 1 ... Rolling bearing 2 ... Outer ring (outer ring member)
2a ··· Outer ring raceway 2b ··· Surface 3 ··· Inner ring 3a · · · Inner ring raceway 4 · Tapered roller 4a · Rolling surface 5 · Cage 5a · Pocket

Claims (3)

内周面に２列の外輪軌道を有する外輪部材と、外周中央に前記外輪軌道に対向する内輪軌道、を有する内輪と、前記外輪軌道と前記内輪軌道との間に転動自在に配置された２列の複数の円すいころと、前記複数の円すいころを保持する複数のポケットが形成された２個の保持器とを有する転がり軸受であって、
前記円すいころは円すい形状の転動面を有し、前記外輪部材は前記外輪部材の軸方向中央方向を大径とする円すい形状の２列の外輪軌道と、前記両外輪軌道の大径側端部から径方向内方に縮径しかつ前記転動面の大径側端面に接する２つの鍔面を有し、前記内輪は前記内輪軌道が前記２列の複数の円すいころの前記転動面に内接する球形状に形成されていることを特徴とする転がり軸受。 An inner ring having an outer ring member having two rows of outer ring raceways on the inner peripheral surface, an inner ring raceway facing the outer ring raceway in the center of the outer periphery, and a rollable arrangement between the outer ring raceway and the inner ring raceway. A rolling bearing having a plurality of tapered rollers in two rows and two cages formed with a plurality of pockets for holding the plurality of tapered rollers,
The tapered roller has a conical rolling surface, and the outer ring member has two rows of tapered outer ring raceways having a large diameter in the axial center direction of the outer ring member, and large diameter side ends of the two outer ring raceways. The inner ring has two flange surfaces that are radially inwardly reduced from the portion and are in contact with the large-diameter end surface of the rolling surface, and the inner ring raceway is the rolling surface of the plurality of tapered rollers in the two rows. A rolling bearing characterized in that it is formed in a spherical shape inscribed in the ball. 前記内輪の最大直径が、前記外輪部材および前記保持器の最小直径より小さいことを特徴とする請求項１に記載の転がり軸受。   The rolling bearing according to claim 1, wherein a maximum diameter of the inner ring is smaller than a minimum diameter of the outer ring member and the cage. 前記外輪部材は、１列の外輪軌道を有する２個の外輪からなることを特徴とする請求項１に記載の転がり軸受。   The rolling bearing according to claim 1, wherein the outer ring member includes two outer rings having a row of outer ring raceways.
JP2012261075A 2012-11-29 2012-11-29 Rolling bearing Pending JP2014105830A (en)

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US1356326A (en) * 1920-03-18 1920-10-19 Svenka Kullagerfabriken Ab Roller-bearing
US1697493A (en) * 1921-07-19 1929-01-01 Wilhelm B Bronander Roller bearing
US2089048A (en) * 1931-02-02 1937-08-03 American Steel Foundries Roller bearing
JPH0177134U (en) * 1987-11-13 1989-05-24
JPH04351314A (en) * 1991-05-28 1992-12-07 Koyo Seiko Co Ltd Conical roller bearing
JPH07259864A (en) * 1994-03-16 1995-10-09 Koyo Seiko Co Ltd Roller bearing, tapered roller bearing and self-aligning roller bearing
JP2003343552A (en) * 2002-05-27 2003-12-03 Koyo Seiko Co Ltd Cone roller bearing
JP2004508511A (en) * 2000-09-05 2004-03-18 レックスノード　コーポレイション Roller bearing for perturbation without retainer
JP2005030461A (en) * 2003-07-09 2005-02-03 Nsk Ltd Conical roller bearing
WO2008152921A1 (en) * 2007-06-15 2008-12-18 Ntn Corporation Tapered roller bearing
JP2011074929A (en) * 2009-09-29 2011-04-14 Ntn Corp Tapered roller bearing

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1356326A (en) * 1920-03-18 1920-10-19 Svenka Kullagerfabriken Ab Roller-bearing
US1697493A (en) * 1921-07-19 1929-01-01 Wilhelm B Bronander Roller bearing
US2089048A (en) * 1931-02-02 1937-08-03 American Steel Foundries Roller bearing
JPH0177134U (en) * 1987-11-13 1989-05-24
JPH04351314A (en) * 1991-05-28 1992-12-07 Koyo Seiko Co Ltd Conical roller bearing
JPH07259864A (en) * 1994-03-16 1995-10-09 Koyo Seiko Co Ltd Roller bearing, tapered roller bearing and self-aligning roller bearing
JP2004508511A (en) * 2000-09-05 2004-03-18 レックスノード　コーポレイション Roller bearing for perturbation without retainer
JP2003343552A (en) * 2002-05-27 2003-12-03 Koyo Seiko Co Ltd Cone roller bearing
JP2005030461A (en) * 2003-07-09 2005-02-03 Nsk Ltd Conical roller bearing
WO2008152921A1 (en) * 2007-06-15 2008-12-18 Ntn Corporation Tapered roller bearing
JP2011074929A (en) * 2009-09-29 2011-04-14 Ntn Corp Tapered roller bearing

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