JP5050619B2 - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
JP5050619B2
JP5050619B2 JP2007106020A JP2007106020A JP5050619B2 JP 5050619 B2 JP5050619 B2 JP 5050619B2 JP 2007106020 A JP2007106020 A JP 2007106020A JP 2007106020 A JP2007106020 A JP 2007106020A JP 5050619 B2 JP5050619 B2 JP 5050619B2
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outer ring
raceway surface
ring raceway
tapered roller
crowning
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JP2008261458A (en
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健一 柴崎
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NSK Ltd
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NSK Ltd
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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
    • 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
    • F16C23/088—Ball or roller bearings self-adjusting by means of crowning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • 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
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/50—Crowning, e.g. crowning height or crowning radius

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

Description

本発明は、円すいころ軸受に関し、特に、外輪軌道面及び円すいころの外周面にクラウニングが施される円すいころ軸受に関する。   The present invention relates to a tapered roller bearing, and more particularly to a tapered roller bearing in which crowning is performed on the outer ring raceway surface and the outer peripheral surface of the tapered roller.

円すいころ軸受は、コンパクトで、大きなラジアル荷重及びアキシャル荷重を支持することができ、しかも、高速回転で使用することができるため、広く使用されている。   Tapered roller bearings are widely used because they are compact, can support large radial loads and axial loads, and can be used at high speeds.

従来の円すいころ軸受としては、例えば、図３に示す円すいころ軸受３０が知られている。この円すいころ軸受３０は、内周面に円すい状の外輪軌道面１１ａを有する外輪１１と、外周面に円すい状の内輪軌道面１２ａを有する内輪１２と、外輪軌道面１１ａと内輪軌道面１２ａとの間に転動自在に配設される複数の円すいころ１３と、円すいころ１３を円周方向に等間隔に保持する保持器１４と、を備える。   As a conventional tapered roller bearing, for example, a tapered roller bearing 30 shown in FIG. 3 is known. The tapered roller bearing 30 includes an outer ring 11 having a conical outer ring raceway surface 11a on an inner peripheral surface, an inner ring 12 having a conical inner ring raceway surface 12a on an outer peripheral surface, an outer ring raceway surface 11a and an inner ring raceway surface 12a. And a plurality of tapered rollers 13 disposed so as to be freely rotatable, and a retainer 14 that holds the tapered rollers 13 at equal intervals in the circumferential direction.

ところで、ころ軸受のころの外周面及び軌道面には、エッジロード発生による寿命低下を防止する目的で、一般に、図４に示すように、クラウニング（図では誇張して表現されている）が施されている（例えば、特許文献１及び２参照）。   Incidentally, crowning (exaggerated in the figure) is generally applied to the outer peripheral surface and raceway surface of the roller bearing, as shown in FIG. (For example, see Patent Documents 1 and 2).

図４に示す例では、外輪軌道面１１ａ及び円すいころ１３の外周面（転動面）のクラウニングの曲線形状は、いずれもクラウニングの中心Ｃ１に対して左右対称とされ、また、クラウニングの中心Ｃ１は、外輪軌道面１１ａの幅方向の中心Ｃ２及び円すいころ１３の軸方向長さの中心Ｃ３に一致している。また、外輪軌道面１１ａの大径側端縁から円すいころ１３の大径側端面までの寸法（大径側外輪余裕代）Ｘ１は、外輪軌道面１１ａの小径側端縁から円すいころ１３の小径側端面までの寸法（小径側外輪余裕代）Ｘ２と等しくなっている。   In the example shown in FIG. 4, the crowning curve shapes of the outer ring raceway surface 11a and the outer peripheral surface (rolling surface) of the tapered roller 13 are both symmetrical with respect to the center C1 of the crowning, and the center C1 of the crowning Is coincident with the center C2 in the width direction of the outer ring raceway surface 11a and the center C3 in the axial length of the tapered rollers 13. The dimension (large diameter side outer ring allowance) X1 from the large diameter side edge of the outer ring raceway surface 11a to the large diameter side end surface of the tapered roller 13 is the small diameter of the tapered roller 13 from the small diameter side edge of the outer ring raceway surface 11a. It is equal to the dimension (small diameter side outer ring allowance) X2 to the side end face.

特開２００１−３９４１号公報Japanese Patent Laid-Open No. 2001-3941 実開平３−１２０１５号公報Japanese Utility Model Publication No. 3-12015

しかしながら、上記従来の円すいころ軸受の場合、外輪１１の肉厚が外輪軌道面１１ａの大径側で薄く、小径側で厚いため、荷重を支持したときの外輪１１の変形が外輪軌道面１１ａの小径側より大径側で大きくなり、結果として、外輪軌道面１１ａの小径側の接触面圧は大径側の接触面圧よりも大きくなる。この面圧分布の偏りは、軸受寿命を短くする原因となり、また、外輪軌道面１１ａの小径側でエッジロードが発生した場合は、軸受寿命を極端に短くしてしまう可能性がある。   However, in the case of the conventional tapered roller bearing described above, the outer ring 11 is thin on the large diameter side of the outer ring raceway surface 11a and thick on the small diameter side, so that the deformation of the outer ring 11 when the load is supported deforms the outer ring raceway surface 11a. As a result, the contact surface pressure on the small diameter side of the outer ring raceway surface 11a becomes larger than the contact surface pressure on the large diameter side. This uneven surface pressure distribution causes the bearing life to be shortened, and when an edge load occurs on the small diameter side of the outer ring raceway surface 11a, the bearing life may be extremely shortened.

本発明は、このような不都合を解消するためになされたものであり、その目的は、外輪軌道面の接触面圧分布の偏りを抑制して、軸受寿命を向上することができる円すいころ軸受を提供することにある。   The present invention has been made in order to eliminate such inconveniences, and an object of the present invention is to provide a tapered roller bearing capable of improving the bearing life by suppressing the uneven contact surface pressure distribution on the outer ring raceway surface. It is to provide.

本発明の上記目的は、内周面に円すい状の外輪軌道面を有する外輪と、外周面に円すい状の内輪軌道面を有する内輪と、外輪軌道面と内輪軌道面との間に転動自在に配設される複数の円すいころと、を備え、外輪軌道面及び円すいころの外周面にそれぞれクラウニングが施される円すいころ軸受であって、クラウニングの曲線が、単一の円弧、又は複数の円弧の組合せにより形成され、外輪軌道面に施されるクラウニングの中心が、外輪軌道面の幅方向の中心よりも外輪軌道面の大径側に位置すると共に、外輪軌道面の大径側端縁から円すいころの大径側端面までの寸法が、外輪軌道面の小径側端縁から円すいころの小径側端面までの寸法よりも長くされて、外輪軌道面に施されるクラウニングの中心が、円すいころの外周面に施されるクラウニングの中心よりも外輪軌道面の大径側に位置することにより、外輪軌道面の大径側における、円すいころに施されるクラウニングの落ち量と外輪軌道面に施されるクラウニングの落ち量との和が、外輪軌道面の小径側における、円すいころに施されるクラウニングの落ち量と外輪軌道面に施されるクラウニングの落ち量との和よりも小さくなるように設定し、これにより、荷重が加えられた場合の、外輪軌道面の接触面圧分布の偏りを抑制することを特徴とする円すいころ軸受により達成される。 The object of the present invention is to roll freely between an outer ring having a conical outer ring raceway surface on the inner peripheral surface, an inner ring having a conical inner ring raceway surface on the outer peripheral surface, and the outer ring raceway surface and the inner ring raceway surface. A tapered roller bearing, wherein the outer ring raceway surface and the outer peripheral surface of the tapered roller are respectively crowned, wherein the crowning curve has a single arc or a plurality of tapered rollers. The center of the crowning formed by the combination of the circular arcs and applied to the outer ring raceway surface is located on the larger diameter side of the outer ring raceway surface than the center in the width direction of the outer ring raceway surface, and the outer diameter side edge of the outer ring raceway surface To the large diameter end surface of the tapered roller is made longer than the small diameter end edge of the outer ring raceway surface to the small diameter end surface of the tapered roller, and the center of the crowning applied to the outer ring raceway surface is the cone. Claw applied to the outer peripheral surface of the roller By positioning on the large diameter side of the outer ring raceway surface from the centering of the outer ring, the amount of crowning drop applied to the tapered roller and the amount of crowning drop applied to the outer ring raceway surface on the large diameter side of the outer ring raceway surface Is set to be smaller than the sum of the amount of crowning drop applied to the tapered roller and the amount of crowning drop applied to the outer ring raceway surface on the small diameter side of the outer ring raceway surface. This is achieved by a tapered roller bearing that suppresses the uneven distribution of the contact surface pressure distribution on the outer ring raceway surface.

本発明の円すいころ軸受によれば、外輪軌道面に施されるクラウニングの中心が、円すいころの外周面に施されるクラウニングの中心よりも外輪軌道面の大径側に位置するため、外輪軌道面の接触面圧分布の偏りを抑制することができるので、軸受寿命を向上することができる。   According to the tapered roller bearing of the present invention, the center of the crowning applied to the outer ring raceway surface is located on the larger diameter side of the outer ring raceway surface than the center of the crowning applied to the outer peripheral surface of the tapered roller. Since the uneven contact surface pressure distribution of the surface can be suppressed, the bearing life can be improved.

以下、本発明に係る円すいころ軸受の各実施形態について、図面を参照して詳細に説明する。なお、円すいころ軸受の基本的構造については、図３及び図４に示す従来の円すいころ軸受３０と同様であるため、従来構造と同等部分に関する図示並びに説明は、省略或いは簡略化し、以下、各実施形態の特徴部分を中心に説明する。   Hereinafter, each embodiment of the tapered roller bearing according to the present invention will be described in detail with reference to the drawings. Since the basic structure of the tapered roller bearing is the same as that of the conventional tapered roller bearing 30 shown in FIGS. 3 and 4, illustrations and explanations regarding the same parts as the conventional structure are omitted or simplified. The description will focus on the features of the embodiment.

（第１実施形態）
まず、図１を参照して、本発明に係る円すいころ軸受の第１実施形態について説明する。
図１は本発明に係る円すいころ軸受の第１実施形態を説明するための要部断面図である。 (First embodiment)
First, a first embodiment of a tapered roller bearing according to the present invention will be described with reference to FIG.
FIG. 1 is a sectional view of an essential part for explaining a tapered roller bearing according to a first embodiment of the present invention.

本実施形態の円すいころ軸受１０では、図１に示すように、外輪１１の外輪軌道面１１ａに施されるクラウニングの中心Ｃ１１が、外輪軌道面１１ａの幅方向の中心Ｃ２よりも外輪軌道面１１ａの大径側に位置し、円すいころ１３の外周面に施されるクラウニングの中心Ｃ１２が、外輪軌道面１１ａの幅方向の中心Ｃ２及び円すいころ１３の軸方向長さの中心Ｃ３に一致している。これにより、外輪軌道面１１ａのクラウニングの中心Ｃ１１が、円すいころ１３のクラウニングの中心Ｃ１２よりも外輪軌道面１１ａの大径側に位置している。なお、外輪軌道面１１ａ及び円すいころ１３のクラウニングの曲線形状については、単一の円弧、又は複数の円弧の組合せであってもよい。   In the tapered roller bearing 10 of this embodiment, as shown in FIG. 1, the center C11 of the crowning applied to the outer ring raceway surface 11a of the outer ring 11 is more than the center C2 in the width direction of the outer ring raceway surface 11a. The center C12 of the crowning applied to the outer peripheral surface of the tapered roller 13 coincides with the center C2 in the width direction of the outer ring raceway surface 11a and the center C3 of the axial length of the tapered roller 13 on the large diameter side. Yes. Thus, the crowning center C11 of the outer ring raceway surface 11a is positioned on the larger diameter side of the outer ring raceway surface 11a than the crowning center C12 of the tapered roller 13 is. In addition, about the curve shape of the crowning of the outer ring raceway surface 11a and the tapered roller 13, a single circular arc or a combination of a plurality of circular arcs may be used.

以上説明したように、本実施形態の円すいころ軸受１０によれば、外輪軌道面１１ａに施されるクラウニングの中心Ｃ１１が、円すいころ１３の外周面に施されるクラウニングの中心Ｃ１２よりも外輪軌道面１１ａの大径側に位置するため、外輪軌道面１１ａの大径側における、円すいころ１３のクラウニングの落ち量＋外輪軌道面１１ａのクラウニングの落ち量を、外輪軌道面１１ａの小径側における、円すいころ１３のクラウニングの落ち量＋外輪軌道面１１ａのクラウニングの落ち量よりも小さくすることができる。   As described above, according to the tapered roller bearing 10 of the present embodiment, the center C11 of the crowning applied to the outer ring raceway surface 11a is more than the center C12 of the crowning applied to the outer peripheral surface of the tapered roller 13. Since it is located on the large diameter side of the surface 11a, the amount of crowning drop of the tapered roller 13 + the amount of crowning drop of the outer ring raceway surface 11a on the large diameter side of the outer ring raceway surface 11a is set on the small diameter side of the outer ring raceway surface 11a. The amount of crowning drop of the tapered roller 13 can be made smaller than the amount of crowning fall of the outer ring raceway surface 11a.

そのため、荷重を支持し、外輪１１の外輪軌道面１１ａの大径側が小径側より大きく変形したときの、円すいころ１３のクラウニングの落ち量＋外輪軌道面１１ａのクラウニングの落ち量＋外輪１１の変形による落ち量を、外輪軌道面１１ａの大径側と小径側とで同程度に近づけることができる。これにより、外輪軌道面１１ａの接触面圧分布の偏りを抑制することができるので、均一な分布に近づけることが可能となり、軸受寿命を向上することができる。   Therefore, when the load is supported and the large diameter side of the outer ring raceway surface 11a of the outer ring 11 is deformed larger than the small diameter side, the amount of crowning fall of the tapered roller 13 + the amount of crowning fall of the outer ring raceway surface 11a + deformation of the outer ring 11 The amount of fall due to can be made close to the same degree on the large diameter side and the small diameter side of the outer ring raceway surface 11a. Thereby, since the bias of the contact surface pressure distribution of the outer ring raceway surface 11a can be suppressed, it becomes possible to approach the uniform distribution, and the bearing life can be improved.

（第２実施形態）
次に、図２を参照して、本発明に係る円すいころ軸受の第２実施形態について説明する。
図２は本発明に係る円すいころ軸受の第２実施形態を説明するための要部断面図である。 (Second Embodiment)
Next, a second embodiment of the tapered roller bearing according to the present invention will be described with reference to FIG.
FIG. 2 is a cross-sectional view of a main part for explaining a second embodiment of the tapered roller bearing according to the present invention.

本実施形態の円すいころ軸受２０では、図２に示すように、外輪軌道面１１ａの大径側端縁から円すいころ１３の大径側端面までの寸法（大径側外輪余裕代）Ｘ１が、外輪軌道面１１ａの小径側端縁から円すいころ１３の小径側端面までの寸法（小径側外輪余裕代）Ｘ２よりも長く、且つ外輪１１の外輪軌道面１１ａに施されるクラウニングの中心Ｃ１１が、外輪軌道面１１ａの幅方向の中心Ｃ２に一致していると共に、円すいころ１３の外周面に施されるクラウニングの中心Ｃ１２が、円すいころ１３の軸方向長さの中心Ｃ３に一致している。これにより、外輪軌道面１１ａのクラウニングの中心Ｃ１１が、円すいころ１３のクラウニングの中心Ｃ１２よりも外輪軌道面１１ａの大径側に位置している。なお、外輪軌道面１１ａ及び円すいころ１３のクラウニングの曲線形状については、単一の円弧、又は複数の円弧の組合せであってもよい。
その他の作用効果については、上記第１実施形態と同様である。 In the tapered roller bearing 20 of the present embodiment, as shown in FIG. 2, the dimension (large diameter side outer ring allowance) X1 from the large diameter side edge of the outer ring raceway surface 11a to the large diameter side end surface of the tapered roller 13 is A dimension C2 of the outer ring raceway surface 11a that is longer than the dimension (small diameter side outer ring allowance) X2 from the small diameter side edge of the outer ring raceway surface 11a to the small diameter side end surface of the tapered roller 13, Along with the center C2 in the width direction of the outer ring raceway surface 11a, the center C12 of the crowning applied to the outer peripheral surface of the tapered roller 13 matches the center C3 of the axial length of the tapered roller 13. Thus, the crowning center C11 of the outer ring raceway surface 11a is positioned on the larger diameter side of the outer ring raceway surface 11a than the crowning center C12 of the tapered roller 13 is. In addition, about the curve shape of the crowning of the outer ring raceway surface 11a and the tapered roller 13, a single circular arc or a combination of a plurality of circular arcs may be used.
Other functions and effects are the same as those in the first embodiment.

なお、本発明の外輪、外輪軌道面、内輪、内輪軌道面、円すいころ、クラウニング等の構成は、上記各実施形態に例示したものに限定されるものではなく、本発明の要旨を逸脱しない範囲において適宜変更可能である。   The configurations of the outer ring, outer ring raceway surface, inner ring, inner ring raceway surface, tapered roller, crowning and the like of the present invention are not limited to those illustrated in the above embodiments, and do not depart from the spirit of the present invention. In FIG.

本発明に係る円すいころ軸受の第１実施形態を説明するための要部断面図である。It is principal part sectional drawing for demonstrating 1st Embodiment of the tapered roller bearing which concerns on this invention. 本発明に係る円すいころ軸受の第２実施形態を説明するための要部断面図である。It is principal part sectional drawing for demonstrating 2nd Embodiment of the tapered roller bearing which concerns on this invention. 従来の円すいころ軸受を説明するための要部断面図である。It is principal part sectional drawing for demonstrating the conventional tapered roller bearing. 従来の円すいころ軸受の外輪軌道面及び円すいころのクラウニングの中心と外輪軌道面の幅方向の中心及び円すいころの軸方向長さの中心との関係を説明するための要部断面図である。It is principal part sectional drawing for demonstrating the relationship between the center of the outer ring raceway surface of a conventional tapered roller bearing, and the crowning of a tapered roller, the center of the width direction of an outer ring raceway surface, and the center of the axial direction length of a tapered roller.

符号の説明Explanation of symbols

１０，２０ 円すいころ軸受
１１ 外輪
１１ａ 外輪軌道面
１２ 内輪
１２ａ 内輪軌道面
１３ 円すいころ 10, 20 Tapered roller bearing 11 Outer ring 11a Outer ring raceway surface 12 Inner ring 12a Inner ring raceway surface 13 Tapered roller

Claims (1)

内周面に円すい状の外輪軌道面を有する外輪と、外周面に円すい状の内輪軌道面を有する内輪と、前記外輪軌道面と前記内輪軌道面との間に転動自在に配設される複数の円すいころと、を備え、前記外輪軌道面及び前記円すいころの外周面にそれぞれクラウニングが施される円すいころ軸受であって、
前記クラウニングの曲線が、単一の円弧、又は複数の円弧の組合せにより形成され、
前記外輪軌道面に施されるクラウニングの中心が、前記外輪軌道面の幅方向の中心よりも前記外輪軌道面の大径側に位置すると共に、
前記外輪軌道面の大径側端縁から前記円すいころの大径側端面までの寸法が、前記外輪軌道面の小径側端縁から前記円すいころの小径側端面までの寸法よりも長くされて、
前記外輪軌道面に施されるクラウニングの中心が、前記円すいころの外周面に施されるクラウニングの中心よりも前記外輪軌道面の大径側に位置することにより、
前記外輪軌道面の大径側における、前記円すいころに施されるクラウニングの落ち量と前記外輪軌道面に施されるクラウニングの落ち量との和が、前記外輪軌道面の小径側における、前記円すいころに施されるクラウニングの落ち量と前記外輪軌道面に施されるクラウニングの落ち量との和よりも小さくなるように設定し、
これにより、荷重が加えられた場合の、前記外輪軌道面の接触面圧分布の偏りを抑制することを特徴とする円すいころ軸受。 An outer ring having a conical outer ring raceway surface on the inner peripheral surface, an inner ring having a conical inner ring raceway surface on the outer peripheral surface, and a rollable arrangement between the outer ring raceway surface and the inner ring raceway surface. comprising a plurality of tapered rollers, and a tapered roller bearing crowned respectively applied before Kigairin raceway surface and the outer peripheral surface of the tapered rollers,
The crowning curve is formed by a single arc or a combination of arcs;
The center of the crowning applied to the outer ring raceway surface is located on the larger diameter side of the outer ring raceway surface than the center in the width direction of the outer ring raceway surface, and
The dimension from the large diameter side edge of the outer ring raceway surface to the large diameter side end surface of the tapered roller is longer than the dimension from the small diameter side edge of the outer ring raceway surface to the small diameter side end surface of the tapered roller,
The center of the crowning applied to the outer ring raceway surface is located on the larger diameter side of the outer ring raceway surface than the center of the crowning applied to the outer peripheral surface of the tapered roller ,
The sum of the amount of crowning drop applied to the tapered roller on the large diameter side of the outer ring raceway surface and the amount of crowning drop applied to the outer ring raceway surface is the cone on the small diameter side of the outer ring raceway surface. Set to be smaller than the sum of the amount of crowning dropped on the rollers and the amount of crowning dropped on the outer raceway surface,
Accordingly, the tapered roller bearing is characterized in that it suppresses the deviation of the contact surface pressure distribution on the outer ring raceway surface when a load is applied .
JP2007106020A 2007-04-13 2007-04-13 Tapered roller bearing Expired - Fee Related JP5050619B2 (en)

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