JP7824038B2 - tapered roller bearings - Google Patents
tapered roller bearingsInfo
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- JP7824038B2 JP7824038B2 JP2021129950A JP2021129950A JP7824038B2 JP 7824038 B2 JP7824038 B2 JP 7824038B2 JP 2021129950 A JP2021129950 A JP 2021129950A JP 2021129950 A JP2021129950 A JP 2021129950A JP 7824038 B2 JP7824038 B2 JP 7824038B2
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Description
この発明は、円すいころ軸受に関する。 This invention relates to a tapered roller bearing.
自動車のトランスミッション（マニュアルトランスミッション（ＭＴ）、オートマチックトランスミッション（ＡＴ）、デュアルクラッチトランスミッション（ＤＣＴ）、連続可変トランスミッション（ＣＶＴ）、ハイブリッド自動車（ＨＥＶ）のトランスミッション）、電気自動車（ＥＶ）の減速機、自動車のディファレンシャル機構などには、ラジアル荷重とアキシアル荷重を同時に支持することが可能な軸受である円すいころ軸受が多く用いられる（例えば、特許文献１）。 Tapered roller bearings, which are capable of supporting radial and axial loads simultaneously, are widely used in automobile transmissions (manual transmissions (MT), automatic transmissions (AT), dual clutch transmissions (DCT), continuously variable transmissions (CVT), and hybrid electric vehicle (HEV) transmissions), reducers for electric vehicles (EV), and automobile differential mechanisms (see, for example, Patent Document 1).
円すいころ軸受は、外輪と、外輪の径方向内側に同軸に配置された内輪と、外輪と内輪の間に周方向に間隔をおいて組み込まれた複数の円すいころとを有する。内輪の外周には、複数の円すいころが転がり接触する円すい状の内輪軌道面と、内輪軌道面の大径側端部から径方向外方に突出して形成された大つばとが設けられている。軸受回転時、内輪の大つばは、アキシアル荷重の一部を受けながら円すいころの大端面と滑り接触する。そのため、円すいころ軸受においては、円すいころの大端面と内輪の大つばとの間の潤滑を確保することが重要である。 A tapered roller bearing has an outer ring, an inner ring arranged coaxially radially inward of the outer ring, and multiple tapered rollers spaced circumferentially between the outer and inner rings. The outer circumference of the inner ring is provided with a conical inner ring raceway surface with which the multiple tapered rollers roll, and a large rib formed to protrude radially outward from the large diameter end of the inner ring raceway surface. When the bearing rotates, the large rib of the inner ring comes into sliding contact with the large end faces of the tapered rollers while bearing part of the axial load. For this reason, it is important in tapered roller bearings to ensure lubrication between the large end faces of the tapered rollers and the large rib of the inner ring.
ここで、本願の出願人は、円すいころの大端面と内輪の大つばとの間の潤滑性を向上することが可能な円すいころ軸受として、特許文献２のものをすでに提案している。特許文献２の円すいころ軸受は、内輪の大つばが、円すいころの大端面に接触する直線の断面をもつ大つば面と、大つば面の径方向外側に滑らかに連なり、円すいころの大端面から遠ざかる方向に湾曲した凸円弧状の断面をもつ逃げＲ部とを有する。逃げＲ部の径方向の外端は、大つばの外径面から円すいころに向かって径方向内側に傾斜する面取り部と交差している。 The applicant of the present application has already proposed a tapered roller bearing capable of improving lubrication between the large end faces of the tapered rollers and the large rib of the inner ring, as disclosed in Patent Document 2. In the tapered roller bearing of Patent Document 2, the large rib of the inner ring has a large rib surface with a linear cross section that contacts the large end faces of the tapered rollers, and a relief R portion that smoothly connects to the radially outer side of the large rib surface and has a convex arc-shaped cross section that curves away from the large end faces of the tapered rollers. The radial outer end of the relief R portion intersects with a chamfer that slopes radially inward from the outer diameter surface of the large rib toward the tapered rollers.
特許文献２の円すいころ軸受は、円すいころの大端面と内輪の大つばの逃げＲ部との間に、くさび状の隙間が形成されるので、そのくさび状の隙間に潤滑油が引き込まれやすく、円すいころの大端面と内輪の大つばとの間の潤滑性に優れる。 The tapered roller bearing of Patent Document 2 has a wedge-shaped gap formed between the large end face of the tapered roller and the relief R portion of the large rib of the inner ring. This makes it easy for lubricating oil to be drawn into this wedge-shaped gap, resulting in excellent lubrication between the large end face of the tapered roller and the large rib of the inner ring.
ところで近年、自動車の室内空間を大きくするために、自動車の駆動ユニットの小型化が求められる傾向がある。また、自動車の駆動ユニットが高出力化される傾向もあり、さらに、自動車の燃費向上を目的として、従来よりも低粘度の潤滑油が使用される傾向がある。そのため、自動車に使用される軸受は、小型のものが求められ、一方、軸受に負荷される荷重は増大し、さらに、軸受内部の油膜形成が難しくなる傾向がある。 In recent years, there has been a trend toward smaller automobile drive units in order to increase the interior space of automobiles. There is also a trend toward higher output from automobile drive units, and a trend toward using lubricating oils with lower viscosities than before in order to improve automobile fuel economy. This has led to a demand for smaller bearings for use in automobiles, but at the same time, the loads placed on the bearings are increasing, and it is becoming more difficult to form an oil film inside the bearings.
特に、円すいころ軸受は、円すいころの大端面と内輪の大つばとが滑り接触することから、円すいころの大端面と内輪の大つばの間の潤滑を確保することが重要であるが、低粘度の潤滑油が使用される場合、円すいころの大端面と内輪の大つばの間に十分な油膜を形成することが難しくなる。 In particular, with tapered roller bearings, the large end faces of the tapered rollers and the large rib of the inner ring are in sliding contact, so it is important to ensure lubrication between the large end faces of the tapered rollers and the large rib of the inner ring. However, if a low-viscosity lubricant is used, it becomes difficult to form a sufficient oil film between the large end faces of the tapered rollers and the large rib of the inner ring.
そこで、本願の発明者らは、低粘度の潤滑油に円すいころ軸受を対応させるために、特許文献２の円すいころ軸受を更に改良することで、円すいころの大端面と内輪の大つばとの間の潤滑性を更に高めることができないかを検討した。 The inventors of the present application therefore investigated whether it would be possible to further improve the lubrication between the large end faces of the tapered rollers and the large rib of the inner ring by further improving the tapered roller bearing of Patent Document 2, in order to make the tapered roller bearing compatible with low-viscosity lubricating oil.
一方、軸受は低コストが求められることから、軸受の構成部品は、短時間で加工することができる形状とすることが好ましい。 On the other hand, since bearings must be low cost, it is preferable that the components of the bearing have a shape that can be machined in a short amount of time.
この発明が解決しようとする課題は、低粘度の潤滑油が使用される場合にも、円すいころの大端面と内輪の大つばの間に十分な油膜を形成することができ、かつ、低コストな円すいころ軸受を提供することである。 The problem this invention aims to solve is to provide a low-cost tapered roller bearing that can form a sufficient oil film between the large end face of the tapered roller and the large rib of the inner ring, even when low-viscosity lubricating oil is used.
上記の課題を解決するため、この発明では、以下の構成の円すいころ軸受を提供する。
外輪と、
前記外輪の径方向内側に同軸に配置された内輪と、
前記外輪と前記内輪の間に周方向に間隔をおいて組み込まれた複数の円すいころと、を備え、
前記内輪の外周に、前記複数の円すいころが転がり接触する円すい状の内輪軌道面と、前記内輪軌道面の大径側端部から径方向外方に突出して形成された大つばとが設けられている円すいころ軸受において、
前記大つばは、大つばの外径面から前記円すいころに向かって径方向内側に傾斜する面取り部と、前記円すいころの大端面に接触する断面の大つば面と、前記大つば面の径方向外側に滑らかに連なり、前記円すいころの大端面から遠ざかる方向に湾曲した凸円弧状の断面をもつ逃げＲ部と、前記逃げＲ部の接線をなすように前記逃げＲ部の径方向外側に滑らかに連なり、前記面取り部に交差する直線の断面をもつ逃げストレート部とを有することを特徴とする円すいころ軸受。
In order to solve the above problems, the present invention provides a tapered roller bearing having the following configuration.
The outer ring and
an inner ring arranged coaxially radially inside the outer ring;
a plurality of tapered rollers assembled at intervals in the circumferential direction between the outer ring and the inner ring,
A tapered roller bearing in which the outer periphery of the inner ring is provided with a conical inner ring raceway surface with which the plurality of tapered rollers come into rolling contact, and a large rib formed to protrude radially outward from a large diameter side end of the inner ring raceway surface,
a large rib surface in cross section that contacts the large end face of the tapered roller; a relief R portion that continues smoothly to the radially outward side of the large rib surface and has a convex arc-shaped cross section that curves in a direction away from the large end face of the tapered roller; and a relief straight portion that continues smoothly to the radially outward side of the relief R portion so as to form a tangent to the relief R portion and has a straight cross section that intersects the chamfered portion.
このようにすると、直線の断面をもつ逃げストレート部は、凸円弧状の断面をもつ逃げＲ部よりも、潤滑油の接触角ヒステリシスが大きく、表面張力により潤滑油を保持する能力が高い。そのため、逃げストレート部を設けずに、大つば面から面取り部までをすべて逃げＲ部としたものよりも、円すいころの大端面と内輪の大つばとの間の潤滑性に優れる。また、逃げストレート部を設けずに、大つば面から面取り部までをすべて逃げＲ部としたものよりも、大つばの研削加工時間を短縮することが可能であり、低コストである。 In this way, the straight relief section, which has a linear cross section, has a larger contact angle hysteresis of the lubricant than the rounded relief section, which has a convex arc cross section, and is therefore more capable of retaining lubricant due to surface tension. This results in better lubrication between the large end face of the tapered roller and the large rib of the inner ring than in a case where there is no straight relief section and the entire area from the large rib surface to the chamfer is rounded. Furthermore, it is possible to reduce the grinding time of the large rib, resulting in lower costs, compared to a case where there is no straight relief section and the entire area from the large rib surface to the chamfer is rounded.
前記大つば面と平行な方向に測ったときの前記逃げＲ部の幅寸法と前記逃げストレート部の幅寸法の比は、９：１～３．５：６．５の範囲に設定することができる。 The ratio of the width of the relief curved portion to the width of the relief straight portion when measured in a direction parallel to the large flange surface can be set within the range of 9:1 to 3.5:6.5.
前記逃げストレート部は、前記大つば面に対して２°～１５°の角度をなすように形成すると好ましい。 It is preferable that the straight relief portion be formed at an angle of 2° to 15° relative to the large flange surface.
逃げストレート部が大つば面に対してなす角度を２°以上とすることにより、円すいころがスキューした場合にも、円すいころの大端面が前記逃げストレート部と前記面取り部との境界に接触するのを回避し、円すいころの大端面と逃げストレート部との間に油膜切れが生じるのを防止することができる。また、逃げストレート部が大つば面に対してなす角度を１５°以下とすることにより、逃げストレート部および逃げＲ部を研削加工で形成する場合の研削深さを効果的に抑えることができ、大つばの研削加工時間を効果的に短縮することができる。 By making the angle that the straight relief portion makes with respect to the large rib surface 2° or more, even if the tapered roller is skewed, the large end face of the tapered roller can be prevented from coming into contact with the boundary between the straight relief portion and the chamfered portion, preventing oil film breakdown between the large end face of the tapered roller and the straight relief portion. Furthermore, by making the angle that the straight relief portion makes with respect to the large rib surface 15° or less, the grinding depth when forming the straight relief portion and the R relief portion by grinding can be effectively reduced, effectively shortening the grinding time for the large rib.
前記円すいころは、前記円すいころの大端面の中央を円形に凹ませたヌスミ部を有する場合、前記円すいころの大端面と前記ヌスミ部との境界が、前記大つば面の径方向外端よりも径方向内側に位置するようにヌスミ部を形成すると好ましい。 When the tapered roller has a recessed portion formed by circularly recessing the center of the large end face of the tapered roller, it is preferable that the recessed portion be formed so that the boundary between the large end face of the tapered roller and the recessed portion is located radially inward of the radial outer end of the large rib surface.
このようにすると、軸受の潤滑条件が悪くなり、円すいころの大端面が大つば面との接触により摩耗した場合にも、円すいころの安定した挙動を確保することができる。すなわち、仮に、円すいころの大端面とヌスミ部との境界が、大つば面の径方向外端よりも径方向内側ではなく、径方向外側に位置するようにヌスミ部を形成した場合、円すいころの大端面に、大つば面と非接触となって摩耗を生じない領域が残ることとなることから、円すいころの大端面が大つば面との接触により摩耗したときに、特にスキュー等が発生すると、円すいころの大端面と大つばとの接触状態が不安定となり、円すいころの挙動が不安定になるおそれがあるのに対し、円すいころの大端面とヌスミ部との境界が、大つば面の径方向外端よりも径方向内側に位置するようにヌスミ部を形成すると、円すいころの大端面の全面が大つば面と接触し、円すいころの大端面が全面で摩耗することから、円すいころの大端面が大つば面との接触により摩耗したときにも、円すいころの大端面と大つばとの接触状態が面当たりとなって安定し、円すいころの安定した挙動を確保することができる。 In this way, stable behavior of the tapered roller can be ensured even if the lubrication conditions of the bearing deteriorate and the large end face of the tapered roller wears due to contact with the large rib surface. In other words, if the recessed portion were formed so that the boundary between the large end face of the tapered roller and the recessed portion was located radially outward rather than radially inward from the radial outer end of the large rib surface, an area would remain on the large end face of the tapered roller that was not in contact with the large rib surface and would not wear. Therefore, when the large end face of the tapered roller wears due to contact with the large rib surface, particularly if skew or the like occurs, the contact state between the large end face of the tapered roller and the large rib becomes unstable, and the behavior of the tapered roller becomes unstable. However, if the recessed portion is formed so that the boundary between the large end face of the tapered roller and the recessed portion is located radially inward of the radial outer end of the large rib surface, the entire surface of the large end face of the tapered roller will come into contact with the large rib surface and the large end face of the tapered roller will wear across its entire surface. Therefore, even when the large end face of the tapered roller wears due to contact with the large rib surface, the contact state between the large end face of the tapered roller and the large rib will be surface contact, which will be stable and ensure stable behavior of the tapered roller.
前記逃げストレート部と前記面取り部の交点から、前記大つば面までの距離は、１０μｍ～１５０μｍの範囲に設定すると好ましい。 The distance from the intersection of the straight relief portion and the chamfered portion to the large flange surface is preferably set in the range of 10 μm to 150 μm.
前記逃げストレート部と前記面取り部の交点から、前記大つば面までの距離を１０μｍ以上とすることにより、円すいころがスキューした場合にも、円すいころの大端面が、前記逃げストレート部と前記面取り部の交点に当たるのを回避し、円すいころの大端面に局所的な強い当たりが生じるのを防止することができる。また、前記逃げストレート部と前記面取り部の交点から、前記大つば面までの距離を、１５０μｍ以下とすることにより、逃げストレート部と逃げＲ部と大つば面とを研削加工で形成する場合の研削深さを効果的に抑えることができ、大つばの研削加工時間を効果的に短縮することができる。 By making the distance from the intersection of the relief straight portion and the chamfered portion to the large rib surface 10 μm or more, even if the tapered roller is skewed, the large end face of the tapered roller can be prevented from hitting the intersection of the relief straight portion and the chamfered portion, preventing localized strong contact with the large end face of the tapered roller. Furthermore, by making the distance from the intersection of the relief straight portion and the chamfered portion to the large rib surface 150 μm or less, the grinding depth can be effectively reduced when forming the relief straight portion, relief R portion, and large rib surface by grinding, effectively shortening the grinding time for the large rib.
前記大つば面の幅寸法は１．５ｍｍ以上とすると好ましい。 It is preferable that the width of the large flange surface be 1.5 mm or more.
このようにすると、大つば面の幅寸法が大きいので、大つば面を超仕上げ加工するときに、大きいサイズの超仕上げ砥石を使用することが可能であり、大つば面の傾斜角度の精度を高めることができる。 By doing this, the width dimension of the rib surface is large, so when superfinishing the rib surface, it is possible to use a large-sized superfinishing grinding stone, which can improve the accuracy of the inclination angle of the rib surface.
前記大つば面の面粗さは０．０８μｍＲａ以下とすると好ましい。 It is preferable that the surface roughness of the large flange surface be 0.08 μm Ra or less.
このようにすると、大つば面の面粗さが小さいので、円すいころのスキューを小さく抑えることができる。 By doing this, the surface roughness of the large rib surface is small, which helps keep the skew of the tapered rollers small.
この発明の円すいころ軸受は、逃げＲ部の径方向外側に滑らかに連なる逃げストレート部を有し、直線の断面をもつ逃げストレート部は、凸円弧状の断面をもつ逃げＲ部よりも、潤滑油の接触角ヒステリシスが大きく、表面張力により潤滑油を保持する能力が高い。そのため、逃げストレート部を設けずに、大つば面から面取り部までをすべて逃げＲ部としたものよりも、円すいころの大端面と内輪の大つばとの間の潤滑性に優れる。また、逃げストレート部を設けずに、大つば面から面取り部までをすべて逃げＲ部としたものよりも、大つばの研削加工時間を短縮することが可能であり、低コストである。 The tapered roller bearing of this invention has a straight relief portion that smoothly connects to the radially outer side of the relief radius portion. A straight relief portion with a linear cross section has a larger contact angle hysteresis for lubricating oil than a relief radius portion with a convex arc cross section, and is more capable of retaining lubricating oil through surface tension. This results in better lubrication between the large end face of the tapered roller and the large rib of the inner ring than a bearing that does not have a straight relief portion and has a relief radius from the large rib surface to the chamfered portion. Furthermore, it is possible to reduce the grinding time for the large rib, resulting in lower costs, compared to a bearing that does not have a straight relief portion and has a relief radius from the large rib surface to the chamfered portion.
図１に、この発明の実施形態の円すいころ軸受を示す。この円すいころ軸受は、外輪１と、外輪１の径方向内側に同軸に配置された内輪２と、外輪１と内輪２の間に周方向に間隔をおいて組み込まれた複数の円すいころ３と、その複数の円すいころ３の周方向の間隔を保持する保持器４とを有する。 Figure 1 shows a tapered roller bearing according to an embodiment of the present invention. This tapered roller bearing has an outer ring 1, an inner ring 2 arranged coaxially radially inside the outer ring 1, a plurality of tapered rollers 3 assembled between the outer ring 1 and the inner ring 2 at intervals in the circumferential direction, and a cage 4 that maintains the circumferential spacing of the tapered rollers 3.
外輪１の内周には、円すいころ３が転がり接触する円すい状の外輪軌道面５が形成されている。内輪２の外周には、円すいころ３が転がり接触する円すい状の内輪軌道面６と、内輪軌道面６の小径側端部から径方向外方に突出する小つば７と、内輪軌道面６の大径側端部から径方向外方に突出する大つば８とが形成されている。 The inner circumference of the outer ring 1 is formed with a conical outer ring raceway surface 5 against which the tapered rollers 3 roll. The outer circumference of the inner ring 2 is formed with a conical inner ring raceway surface 6 against which the tapered rollers 3 roll, a small rib 7 protruding radially outward from the small diameter end of the inner ring raceway surface 6, and a large rib 8 protruding radially outward from the large diameter end of the inner ring raceway surface 6.
内輪軌道面６と外輪軌道面５は、円すいころ３を間に挟んで径方向に対向している。外輪軌道面５と内輪軌道面６は、内輪２の中心線上に位置する共通の一点（図５に示すコーンセンタＯ）で交わる円すい面である。軸受回転時、各円すいころ３は外輪軌道面５と内輪軌道面６の間で内輪２の中心線まわりに公転しながら自転する。大つば８は、軸受回転時、円すいころ３の大端面９と滑りを伴って接触し、アキシアル荷重の一部を支持する。 The inner ring raceway surface 6 and the outer ring raceway surface 5 face each other radially, sandwiching a tapered roller 3 between them. The outer ring raceway surface 5 and the inner ring raceway surface 6 are conical surfaces that intersect at a common point (cone center O shown in Figure 5) located on the centerline of the inner ring 2. When the bearing rotates, each tapered roller 3 rotates while revolving around the centerline of the inner ring 2 between the outer ring raceway surface 5 and the inner ring raceway surface 6. When the bearing rotates, the large rib 8 comes into sliding contact with the large end face 9 of the tapered roller 3, supporting part of the axial load.
円すいころ３は、内輪２の小つば７と対向する小端面１０と、内輪２の大つば８と対向する大端面９と、外輪軌道面５および内輪軌道面６に転がり接触する円すい状のころ転動面１１と、ころ転動面１１と小端面１０の間をつなぐ小径側ころ面取り部１２と、ころ転動面１１と大端面９の間をつなぐ大径側ころ面取り部１３と、円すいころ３の大端面９の中央を円形に凹ませたヌスミ部１４（図２参照）とを有する。 The tapered roller 3 has a small end face 10 facing the small rib 7 of the inner ring 2, a large end face 9 facing the large rib 8 of the inner ring 2, a tapered roller rolling surface 11 that is in rolling contact with the outer ring raceway surface 5 and the inner ring raceway surface 6, a small diameter side roller chamfer 12 connecting the roller rolling surface 11 and the small end face 10, a large diameter side roller chamfer 13 connecting the roller rolling surface 11 and the large end face 9, and a recessed portion 14 (see Figure 2) formed by a circular recess in the centre of the large end face 9 of the tapered roller 3.
図２に示すように、大つば８は、円すいころ３の大端面９に接触する直線の断面をもつ大つば面１５と、円筒状の外径面１６と、外径面１６から円すいころ３に向かって径方向内側に傾斜する面取り部１７とを有する。大つば面１５と内輪軌道面６の交差部には、凹円弧状の断面をもつ盗み溝１８が形成されている。 As shown in Figure 2, the large rib 8 has a large rib surface 15 with a linear cross section that contacts the large end face 9 of the tapered roller 3, a cylindrical outer diameter surface 16, and a chamfered portion 17 that slopes radially inward from the outer diameter surface 16 toward the tapered roller 3. At the intersection of the large rib surface 15 and the inner ring raceway surface 6, a relief groove 18 with a concave arc cross section is formed.
大つば面１５の幅寸法ａは、１．５ｍｍ以上（好ましくは１．６ｍｍ以上、より好ましくは１．７ｍｍ以上）、３．０ｍｍ以下に設定されている。大つば面１５は、超仕上げ加工が施された超仕上げ面であり、その面粗さは０．００５μｍＲａ以上、０．０８０μｍＲａ以下（好ましくは０．０５０μｍＲａ以下）とされている。面取り部１７は、凸円弧状の断面をもつ形状とされている。面取り部１７の大つば面１５と平行な方向に測ったときの幅寸法は、０．２ｍｍ以上（好ましくは０．４ｍｍ以上）、１．２ｍｍ以下とされている。面取り部１７の幅寸法を０．２ｍｍ以上（好ましくは０．４ｍｍ以上）とすると、打ち疵などを予防することができ、面取り部１７の幅寸法を１．２ｍｍ以下とすると、面取り部１７を形成するときの旋削加工時間を短く抑えることができる。 The width dimension a of the large flange surface 15 is set to 1.5 mm or more (preferably 1.6 mm or more, more preferably 1.7 mm or more) and 3.0 mm or less. The large flange surface 15 is a superfinished surface that has been subjected to superfinishing, and its surface roughness is set to 0.005 μm Ra or more and 0.080 μm Ra or less (preferably 0.050 μm Ra or less). The chamfered portion 17 has a convex arc-shaped cross section. The width dimension of the chamfered portion 17, measured in a direction parallel to the large flange surface 15, is set to 0.2 mm or more (preferably 0.4 mm or more) and 1.2 mm or less. Setting the width dimension of the chamfered portion 17 to 0.2 mm or more (preferably 0.4 mm or more) can prevent dents and other damage, while setting the width dimension of the chamfered portion 17 to 1.2 mm or less can shorten the turning processing time required to form the chamfered portion 17.
図３に示すように、大つば８は、大つば面１５の径方向外側に滑らかに連なり、円すいころ３の大端面９（図２参照）から遠ざかる方向に湾曲した凸円弧状の断面をもつ逃げＲ部２０と、逃げＲ部２０の接線をなすように逃げＲ部２０の径方向外側に滑らかに連なる直線の断面をもつ逃げストレート部２１とを有する。逃げＲ部２０の断面の曲率半径Ｒは、面取り部１７の断面の曲率半径よりも大きい。図４に示すように、逃げストレート部２１の断面の直線は、面取り部１７の接線をなすように滑らかに面取り部１７に連なるのではなく、面取り部１７と交点を形成するように交差している。 As shown in Figure 3, the large rib 8 has a relief R portion 20 that smoothly connects to the radially outer side of the large rib surface 15 and has a convex arc-shaped cross section that curves away from the large end face 9 (see Figure 2) of the tapered roller 3, and a relief straight portion 21 that has a straight cross section that smoothly connects to the radially outer side of the relief R portion 20 so as to form a tangent to the relief R portion 20. The radius of curvature R of the cross section of the relief R portion 20 is larger than the radius of curvature of the cross section of the chamfered portion 17. As shown in Figure 4, the straight line of the cross section of the relief straight portion 21 does not smoothly connect to the chamfered portion 17 so as to form a tangent to the chamfered portion 17, but rather intersects with the chamfered portion 17 to form an intersection.
図２に示すように、円すいころ３の大端面９の中央を円形に凹ませたヌスミ部１４の直径ｅは、大端面９とヌスミ部１４との境界（図では直径ｅの下端位置）が、大つば面１５の径方向外端（大つば面１５と逃げＲ部２０の境界。図では、大つば面１５の幅寸法ａの上端位置）よりも径方向内側（図では下側）に位置するように設定されている。 As shown in Figure 2, the diameter e of the recessed portion 14, which is a circular recess in the center of the large end face 9 of the tapered roller 3, is set so that the boundary between the large end face 9 and the recessed portion 14 (the lower end position of diameter e in the figure) is located radially inward (lower in the figure) than the radial outer end of the large rib surface 15 (the boundary between the large rib surface 15 and the relief R portion 20; in the figure, the upper end position of the width dimension a of the large rib surface 15).
図３に示すように、逃げストレート部２１と面取り部１７の交点から、大つば面１５までの距離ｄ（以下「逃げドロップ量ｄ」という）は、１０μｍ以上（好ましくは１５μｍ以上、より好ましくは２０μｍ以上）、１５０μｍ以下の範囲に設定されている。大つば面１５と平行な方向に測ったときの逃げＲ部２０の幅寸法ｂと逃げストレート部２１の幅寸法ｃの比は、９：１～３．５：６．５の範囲に設定されている。大つば面１５と平行な方向に測ったときの逃げＲ部２０と逃げストレート部２１を合わせた領域の幅寸法ｂ＋ｃ（以下「逃げ幅ｂ＋ｃ」という）は、大つば面１５の幅寸法ａの１５～６０％の範囲に設定されている。 As shown in Figure 3, the distance d from the intersection of the relief straight portion 21 and the chamfered portion 17 to the large flange surface 15 (hereinafter referred to as the "relief drop amount d") is set to a range of 10 μm or more (preferably 15 μm or more, more preferably 20 μm or more) and 150 μm or less. The ratio of the width dimension b of the relief R portion 20 to the width dimension c of the relief straight portion 21 when measured in a direction parallel to the large flange surface 15 is set to a range of 9:1 to 3.5:6.5. The width dimension b + c of the combined region of the relief R portion 20 and the relief straight portion 21 when measured in a direction parallel to the large flange surface 15 (hereinafter referred to as the "relief width b + c") is set to a range of 15 to 60% of the width dimension a of the large flange surface 15.
図４に示すように、逃げストレート部２１と大つば面１５のなす角度θは、２°～１５°の範囲に設定されている。 As shown in Figure 4, the angle θ between the straight relief portion 21 and the large flange surface 15 is set in the range of 2° to 15°.
図５に示すように、大つば面１５の傾斜角度（大つば面１５が軸直角方向に対してなす角度）αは、大つば面１５と円すいころ３の大端面９の接点位置とコーンセンタＯとを結ぶ直線に直交するように設定されている。前記直線が内輪軌道面６に対してなす角度ρは、円すいころ３の中心角βに対して、β／８以上、β／５以下の大きさとなるように設定されている。角度ρがβ／８以上の大きさであると、円すいころ３の大端面９を大つば面１５に安定して接触させることができ、角度ρがβ／５以下の大きさであると、円すいころ３の大端面９と大つば面１５との接触による昇温を抑制することが可能となる。 As shown in Figure 5, the inclination angle α of the large rib surface 15 (the angle the large rib surface 15 makes with respect to the axis-perpendicular direction) is set so that it is perpendicular to the line connecting the contact point between the large rib surface 15 and the large end face 9 of the tapered roller 3 and the cone center O. The angle ρ that this line makes with the inner ring raceway surface 6 is set so that it is greater than or equal to β/8 and less than or equal to β/5, relative to the central angle β of the tapered roller 3. When the angle ρ is β/8 or greater, the large end face 9 of the tapered roller 3 can be brought into stable contact with the large rib surface 15, and when the angle ρ is β/5 or less, it is possible to suppress temperature increases due to contact between the large end face 9 of the tapered roller 3 and the large rib surface 15.
上記の円すいころ軸受の内輪２は、例えば、次のようにして製造することができる。まず、鍛造加工で大つば８を有する素形材を形成する。次に、その素形材の大つば８を旋削加工することで、図６に示す外径面１６および面取り部１７を形成する。その後、図６に示すように、大つば８に、逃げストレート部２１と逃げＲ部２０と大つば面１５とに対応する形状をもつ研削砥石Ｇ１を押し当てることで、逃げストレート部２１と逃げＲ部２０と大つば面１５とを形成する。その後、大つば面１５の部分に超仕上げ砥石を押し当てることで、大つば面１５の面粗さを高める。 The inner ring 2 of the tapered roller bearing described above can be manufactured, for example, as follows. First, a base material having a large rib 8 is formed by forging. Next, the large rib 8 of this base material is turned to form the outer diameter surface 16 and chamfered portion 17 shown in Figure 6. Then, as shown in Figure 6, a grinding wheel G1 having a shape corresponding to the straight relief portion 21, the round relief portion 20, and the large rib surface 15 is pressed against the large rib 8 to form the straight relief portion 21, the round relief portion 20, and the large rib surface 15. Then, a superfinishing wheel is pressed against the large rib surface 15 to increase the surface roughness of the large rib surface 15.
この円すいころ軸受は、図３に示すように、逃げＲ部２０の径方向外側に滑らかに連なる逃げストレート部２１を有し、直線の断面をもつ逃げストレート部２１は、凸円弧状の断面をもつ逃げＲ部２０よりも、潤滑油の接触角ヒステリシスが大きく、表面張力により潤滑油を保持する能力が高い。そのため、図８に示すように、逃げストレート部２１を設けずに、大つば面１５から面取り部１７までをすべて逃げＲ部２０としたものよりも、円すいころ３の大端面９と内輪２の大つば８との間の潤滑性に優れ、低粘度の潤滑油が使用される場合にも、円すいころ３の大端面９と内輪２の大つば８の間に十分な油膜を形成することができる。ここでいう低粘度の潤滑油は、１００℃の油温条件で３～６ｍｍ２／秒（従来の潤滑油の粘度は、１００℃の油温条件で６～１２ｍｍ２／秒）である。 As shown in Figure 3, this tapered roller bearing has a straight relief portion 21 that smoothly connects to the radially outward side of the relief radius portion 20, and the straight relief portion 21, which has a straight cross section, has a larger contact angle hysteresis of the lubricating oil and is more capable of retaining lubricating oil due to surface tension than the relief radius portion 20, which has a convex arc cross section. Therefore, as shown in Figure 8, this tapered roller bearing has better lubrication between the large end faces 9 of the tapered rollers 3 and the large rib 8 of the inner ring 2 than a bearing in which the entire area from the large rib surface 15 to the chamfered portion 17 is formed as a relief radius portion 20 without the straight relief portion 21, and is able to form a sufficient oil film between the large end faces 9 of the tapered rollers 3 and the large rib 8 of the inner ring 2, even when a low-viscosity lubricating oil is used. The low-viscosity lubricating oil referred to here has a viscosity of 3 to 6 mm 2 /sec at an oil temperature of 100°C (the viscosity of conventional lubricating oil is 6 to 12 mm 2 /sec at an oil temperature of 100°C).
また、この円すいころ軸受は、図３に示すように、逃げＲ部２０の径方向外側に滑らかに連なる逃げストレート部２１を有するので、図８に示すように、逃げストレート部２１を設けずに、大つば面１５から面取り部１７までをすべて逃げＲ部２０としたものよりも、大つば８の研削加工時間を短縮することが可能である。 In addition, as shown in Figure 3, this tapered roller bearing has a straight relief portion 21 that smoothly connects to the radially outer side of the relief radius portion 20. This makes it possible to shorten the grinding time for the large rib 8 compared to a bearing that does not have a straight relief portion 21 and has a relief radius portion 20 throughout from the large rib surface 15 to the chamfered portion 17, as shown in Figure 8.
図６と図７を参照して説明する。図６は、図３に示すように逃げＲ部２０の径方向外側に滑らかに連なる逃げストレート部２１を有する大つば８の研削加工を説明する図である。図６において、研削砥石Ｇ１は、図３に示す逃げストレート部２１と逃げＲ部２０と大つば面１５とに対応する形状を有し、この研削砥石Ｇ１を大つば８に押し当てることで、逃げストレート部２１（図３参照）に対応する部分から研削加工が開始し、最終的に図の斜線部分が研削砥石Ｇ１で削り取られることで、図３に示す逃げストレート部２１と逃げＲ部２０と大つば面１５とが形成される。図６の寸法ｓは、研削砥石Ｇ１から大つば８の加工開始点までの距離であり、図６の寸法ｔ１は、研削砥石Ｇ１の大つば面１５に対応する部分から大つば８までの距離である。 Referring to Figures 6 and 7, the following explanation will be given. Figure 6 illustrates the grinding process of the large flange 8, which has a straight relief portion 21 that smoothly connects to the radially outer side of the rounded relief portion 20, as shown in Figure 3. In Figure 6, the grinding wheel G1 has a shape corresponding to the straight relief portion 21, rounded relief portion 20, and large flange surface 15 shown in Figure 3. By pressing this grinding wheel G1 against the large flange 8, grinding begins from the portion corresponding to the straight relief portion 21 (see Figure 3). Finally, the hatched portion in the figure is removed by the grinding wheel G1, forming the straight relief portion 21, rounded relief portion 20, and large flange surface 15 shown in Figure 3. Dimension s in Figure 6 is the distance from the grinding wheel G1 to the starting point of the large flange 8, and dimension t1 in Figure 6 is the distance from the portion of the grinding wheel G1 corresponding to the large flange surface 15 to the large flange 8.
これに対し、図７は、図８に示すように逃げストレート部２１を設けずに、大つば面１５から面取り部１７までをすべて逃げＲ部２０とした大つば８の研削加工を説明する図である。図７において、研削砥石Ｇ２は、逃げＲ部２０と大つば面１５とに対応する形状を有し、この研削砥石Ｇ２を大つば８に押し当てることで、逃げＲ部２０から研削加工が開始し、最終的に図の斜線部分が研削砥石Ｇ２で削り取られることで、逃げＲ部２０と大つば面１５とが形成される。図７の寸法ｓは、研削砥石Ｇ２から大つば８の加工開始点までの距離であり、図７の寸法ｔ２は、研削砥石Ｇ２の大つば面１５に対応する部分から大つば８までの距離である。図６における寸法ｓと、図７における寸法ｓは同じ大きさである。 In contrast, Figure 7 illustrates the grinding of a large flange 8 in which the entire area from the large flange surface 15 to the chamfered portion 17 is formed as a relief radius 20 without providing a relief straight portion 21, as shown in Figure 8. In Figure 7, the grinding wheel G2 has a shape corresponding to the relief radius 20 and the large flange surface 15. By pressing the grinding wheel G2 against the large flange 8, grinding begins at the relief radius 20. The shaded area in the figure is ultimately removed by the grinding wheel G2, forming the relief radius 20 and the large flange surface 15. Dimension s in Figure 7 is the distance from the grinding wheel G2 to the starting point of machining the large flange 8, and dimension t2 in Figure 7 is the distance from the portion of the grinding wheel G2 corresponding to the large flange surface 15 to the large flange 8. Dimension s in Figure 6 and dimension s in Figure 7 are the same size.
図６と図７を比較すると、図６および図７の寸法ｓと、図６の寸法ｔ１と、図７の寸法ｔ２とには、ｓ＜ｔ１＜ｔ２の関係が成立する。すなわち、図６における研削の加工距離（研削深さ）は、図７における研削の加工距離（研削深さ）よりも小さい。そのため、図３に示すように、逃げＲ部２０の径方向外側に滑らかに連なる逃げストレート部２１を設けた場合の大つば８の研削加工時間は、図８に示すように、逃げストレート部２１を設けずに、大つば面１５から面取り部１７までをすべて逃げＲ部２０とした場合の大つば８の研削加工時間よりも短縮することが可能である。 Comparing Figures 6 and 7, the dimension s in Figures 6 and 7, the dimension t1 in Figure 6, and the dimension t2 in Figure 7 satisfy the relationship s < t1 < t2. In other words, the grinding distance (grinding depth) in Figure 6 is smaller than the grinding distance (grinding depth) in Figure 7. Therefore, as shown in Figure 3, the grinding time for a large flange 8 with a straight relief portion 21 that smoothly connects to the radially outer side of the relief radius 20 can be shorter than the grinding time for a large flange 8 with no straight relief portion 21 and the entire flange surface 15 to the chamfered portion 17 formed as a relief radius 20, as shown in Figure 8.
この円すいころ軸受は、図４に示すように、逃げストレート部２１が大つば面１５に対してなす角度θを２°以上としているので、円すいころ３がスキューした場合にも、円すいころ３の大端面９が逃げストレート部２１と面取り部１７との境界に接触するのを回避し、円すいころ３の大端面９と逃げストレート部２１との間に油膜切れが生じるのを防止することができる。また、逃げストレート部２１が大つば面１５に対してなす角度θを１５°以下としているので、逃げストレート部２１と逃げＲ部２０と大つば面１５とを研削加工で形成する場合の研削深さを効果的に抑えることができ、大つば８の研削加工時間を効果的に短縮することができる。 As shown in Figure 4, in this tapered roller bearing, the angle θ that the relief straight portion 21 makes with respect to the large rib surface 15 is 2° or more. This prevents the large end face 9 of the tapered roller 3 from coming into contact with the boundary between the relief straight portion 21 and the chamfered portion 17, even when the tapered roller 3 is skewed, preventing oil film breakdown between the large end face 9 of the tapered roller 3 and the relief straight portion 21. Furthermore, because the angle θ that the relief straight portion 21 makes with respect to the large rib surface 15 is 15° or less, the grinding depth when forming the relief straight portion 21, relief R portion 20, and large rib surface 15 by grinding can be effectively reduced, effectively shortening the grinding time for the large rib 8.
また、この円すいころ軸受は、図２に示すように、円すいころ３の大端面９とヌスミ部１４との境界が、大つば面１５の径方向外端よりも径方向内側に位置するようにヌスミ部１４を形成しているので、軸受の潤滑条件が悪くなり、円すいころ３の大端面９が大つば面１５との接触により摩耗した場合にも、円すいころ３の安定した挙動を確保することができる。 Furthermore, as shown in Figure 2, this tapered roller bearing forms the recessed portion 14 so that the boundary between the large end face 9 of the tapered roller 3 and the recessed portion 14 is located radially inward of the radial outer end of the large rib surface 15.This ensures stable behavior of the tapered roller 3 even if the lubrication conditions of the bearing deteriorate and the large end face 9 of the tapered roller 3 wears due to contact with the large rib surface 15.
すなわち、仮に、円すいころ３の大端面９とヌスミ部１４との境界が、大つば面１５の径方向外端よりも径方向内側ではなく、径方向外側に位置するようにヌスミ部１４を形成した場合、円すいころ３の大端面９に、大つば面１５と非接触となって摩耗を生じない領域が残ることとなることから、円すいころ３の大端面９が大つば面１５との接触により摩耗したときに、特にスキュー等が発生すると、円すいころ３の大端面９と大つば８との接触状態が不安定となり、円すいころ３の挙動が不安定になるおそれがあるのに対し、円すいころ３の大端面９とヌスミ部１４との境界が、大つば面１５の径方向外端よりも径方向内側に位置するようにヌスミ部１４を形成すると、円すいころ３の大端面９の全面が大つば面１５と接触し、円すいころ３の大端面９が全面で摩耗することから、円すいころ３の大端面９が大つば面１５との接触により摩耗したときにも、円すいころ３の大端面９と大つば８との接触状態が面当たりとなって安定し、円すいころ３の安定した挙動を確保することができる。 In other words, if the recessed portion 14 were formed so that the boundary between the large end face 9 of the tapered roller 3 and the recessed portion 14 was located radially outward rather than radially inward from the radially outer end of the large rib surface 15, an area would remain on the large end face 9 of the tapered roller 3 that would not come into contact with the large rib surface 15 and would not experience wear. Therefore, when the large end face 9 of the tapered roller 3 wears due to contact with the large rib surface 15, and especially if skew or the like occurs, the contact state between the large end face 9 of the tapered roller 3 and the large rib 8 becomes unstable, and the behavior of the tapered roller 3 becomes unstable. However, if the recessed portion 14 is formed so that the boundary between the large end face 9 of the tapered roller 3 and the recessed portion 14 is located radially inward of the radial outer end of the large rib surface 15, the entire surface of the large end face 9 of the tapered roller 3 will come into contact with the large rib surface 15, and the entire large end face 9 of the tapered roller 3 will wear. Therefore, even when the large end face 9 of the tapered roller 3 wears due to contact with the large rib surface 15, the contact state between the large end face 9 of the tapered roller 3 and the large rib 8 will be surface contact, which will be stable, and stable behavior of the tapered roller 3 can be ensured.
また、この円すいころ軸受は、図３に示すように、逃げドロップ量ｄを１０μｍ以上としているので、円すいころ３がスキューした場合にも、円すいころ３の大端面９が、逃げストレート部２１と面取り部１７の交点に当たるのを回避し、円すいころ３の大端面９に局所的な強い当たりが生じるのを防止することができる。また、逃げドロップ量ｄを、１５０μｍ以下としているので、逃げストレート部２１と逃げＲ部２０と大つば面１５とを研削加工で形成する場合の研削深さを効果的に抑えることができ、大つば８の研削加工時間を効果的に短縮することができる。 In addition, as shown in Figure 3, this tapered roller bearing has a relief drop amount d of 10 μm or more. This prevents the large end face 9 of the tapered roller 3 from hitting the intersection of the relief straight portion 21 and the chamfered portion 17 even when the tapered roller 3 is skewed, preventing localized strong contact on the large end face 9 of the tapered roller 3. Furthermore, because the relief drop amount d is 150 μm or less, the grinding depth when forming the relief straight portion 21, relief R portion 20, and large rib surface 15 by grinding can be effectively reduced, effectively shortening the grinding time for the large rib 8.
また、この円すいころ軸受は、図３に示す大つば面１５の幅寸法ａを１．５ｍｍ以上（好ましくは１．６ｍｍ以上、より好ましくは１．７ｍｍ以上）としており、大つば面１５の幅寸法ａが大きいので、大つば面１５を超仕上げ加工するときに、大きいサイズの超仕上げ砥石を使用することが可能であり、大つば面１５の傾斜角度α（図５参照）の精度を高めることが可能となっている。具体的には、大つば面１５の傾斜角度αを、大つば面１５と直交する円すいころ３の大端面９の接点位置とコーンセンタＯとを結ぶ直線が内輪軌道面６に対してなす角度ρが、円すいころ３の中心角βに対して、β／８以上、β／５以下の大きさとなるように設定した設計値に対して±１５′（好ましくは±１０′、より好ましくは±７′）の範囲に収まるように大つば面１５を超仕上げ加工することが可能となる。これにより、円すいころ３の大端面９と大つば面１５との接触状態が安定したものとなり、低粘度の潤滑油を使用した場合にも、円すいころ３のスキュー量を安定して抑制することが可能となる。大つば面１５の幅寸法ａと、大つば面１５の傾斜角度αの関係を表１に示す。 In addition, this tapered roller bearing has a width dimension a of the large rib surface 15 shown in Figure 3 that is 1.5 mm or more (preferably 1.6 mm or more, more preferably 1.7 mm or more). Because the width dimension a of the large rib surface 15 is large, it is possible to use a large-sized superfinishing grinding stone when superfinishing the large rib surface 15, thereby improving the accuracy of the inclination angle α (see Figure 5). Specifically, the inclination angle α of the large rib surface 15 can be superfinished so that it falls within a range of ±15' (preferably ±10', more preferably ±7') of the design value set so that the angle ρ, which is the angle formed by the line connecting the contact point of the large end face 9 of the tapered roller 3 perpendicular to the large rib surface 15 and the cone center O with the inner ring raceway surface 6, is β/8 or more and β/5 or less with respect to the central angle β of the tapered roller 3. This stabilizes the contact state between the large end face 9 of the tapered roller 3 and the large rib surface 15, making it possible to stably suppress the amount of skew of the tapered roller 3 even when using a low-viscosity lubricant. The relationship between the width dimension a of the large rib surface 15 and the inclination angle α of the large rib surface 15 is shown in Table 1.
また、この円すいころ軸受は、大つば面１５の面粗さを０．０８μｍＲａ以下としており、大つば面１５の面粗さが小さいので、円すいころ３のスキューを小さく抑えることが可能となっている。大つば面１５の面粗さと円すいころ３のスキュー量の関係を表２に示す。 In addition, this tapered roller bearing has a surface roughness of 0.08 μm Ra or less on the large rib surface 15, and because the surface roughness of the large rib surface 15 is small, it is possible to keep the skew of the tapered rollers 3 small. The relationship between the surface roughness of the large rib surface 15 and the amount of skew of the tapered rollers 3 is shown in Table 2.
上記実施形態の円すいころ軸受のサンプル品を製作し、その評価試験を行なった。このとき用いた円すいころ軸受の構成は、以下のとおりである。
・軸受サイズ：内輪内径７０ｍｍ、外輪外径１５０ｍｍ、軸受幅４０ｍｍ
・大つば面１５の幅寸法ａ：３．５ｍｍ
・大つば面１５の面粗さ：０．０７８μｍＲａ
・逃げドロップ量ｄ：６０ｍｍ
・面取り部の幅寸法ａ：０．８ｍｍ
・逃げ幅ｂ＋ｃ：０．６９ｍｍ
A sample of the tapered roller bearing according to the above embodiment was manufactured and subjected to an evaluation test. The tapered roller bearing used had the following configuration.
- Bearing size: inner ring inner diameter 70 mm, outer ring outer diameter 150 mm, bearing width 40 mm
Width dimension a of the large flange surface 15: 3.5 mm
Surface roughness of the large flange surface 15: 0.078 μm Ra
Relief drop amount d: 60 mm
Width dimension of chamfered part a: 0.8 mm
Relief width b + c: 0.69 mm
また、試験条件は、以下のとおりである。
・試験アキシアル荷重：Ｐ／Ｃ＝０．１１
・試験回転速度：３０００ｒ／ｍｉｎ
・潤滑条件：円すいころ軸受を潤滑油（デフ油）に浸漬して取り出した後、３０分放置し、その後、無給油で円すいころ軸受を運転。
The test conditions are as follows:
Test axial load: P/C = 0.11
Test rotation speed: 3000 r/min
Lubrication conditions: The tapered roller bearing was immersed in lubricating oil (differential oil), removed, and left for 30 minutes, after which the tapered roller bearing was operated without oiling.
上記試験の結果、円すいころ軸受の運転を開始してから４００秒を経過した時点で、円すいころ３の大端面９と大つば８の間に焼付きが発生した。一方、逃げＲ部２０と逃げストレート部２１を設けない円すいころ軸受についても同様の評価試験を行なったところ、円すいころ軸受の運転を開始してから７５秒が経過した時点で焼付きが発生した。この結果より、逃げＲ部２０と逃げストレート部２１を大つば８に設けた円すいころ軸受は、逃げＲ部２０と逃げストレート部２１を大つば８に設けない円すいころ軸受と比較して、約５倍の寿命を有することが分かる。 As a result of the above test, seizure occurred between the large end face 9 of the tapered roller 3 and the large rib 8 400 seconds after the tapered roller bearing began operation. Meanwhile, when a similar evaluation test was conducted on a tapered roller bearing without the relief radius 20 and straight relief portion 21, seizure occurred 75 seconds after the tapered roller bearing began operation. These results show that a tapered roller bearing with the relief radius 20 and straight relief portion 21 on the large rib 8 has a lifespan approximately five times longer than a tapered roller bearing without the relief radius 20 and straight relief portion 21 on the large rib 8.
今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。 The embodiments disclosed herein should be considered in all respects to be illustrative and not restrictive. The scope of the present invention is indicated by the claims, not the above description, and is intended to include all modifications that are equivalent in meaning to and within the scope of the claims.
１ 外輪
２ 内輪
３ 円すいころ
６ 内輪軌道面
８ 大つば
９ 大端面
１４ ヌスミ部
１５ 大つば面
１６ 外径面
１７ 面取り部
２０ 逃げＲ部
２１ 逃げストレート部
ａ 大つば面の幅寸法
ｄ 逃げドロップ量
θ 逃げストレート部が大つば面に対してなす角度
1 Outer ring 2 Inner ring 3 Tapered roller 6 Inner ring raceway surface 8 Large rib 9 Large end face 14 Recessed portion 15 Large rib surface 16 Outer diameter surface 17 Chamfered portion 20 Relief R portion 21 Relief straight portion a Width dimension d of large rib surface Relief drop amount θ Angle formed by the relief straight portion with respect to the large rib surface
Claims (6)
前記外輪（１）の径方向内側に同軸に配置された内輪（２）と、
前記外輪（１）と前記内輪（２）の間に周方向に間隔をおいて組み込まれた複数の円すいころ（３）と、を備え、
前記内輪（２）の外周に、前記複数の円すいころ（３）が転がり接触する円すい状の内輪軌道面（６）と、前記内輪軌道面（６）の大径側端部から径方向外方に突出して形成された大つば（８）とが設けられている円すいころ軸受において、
前記大つば（８）は、大つば（８）の外径面（１６）から前記円すいころ（３）に向かって径方向内側に傾斜する面取り部（１７）と、前記円すいころ（３）の大端面（９）に接触する断面の大つば面（１５）と、前記大つば面（１５）の径方向外側に滑らかに連なり、前記円すいころ（３）の大端面（９）から遠ざかる方向に湾曲した凸円弧状の断面をもつ逃げＲ部（２０）と、前記逃げＲ部（２０）の接線をなすように前記逃げＲ部（２０）の径方向外側に滑らかに連なり、前記面取り部（１７）に交差する直線の断面をもつ逃げストレート部（２１）とを有し、
前記円すいころ（３）は、前記円すいころ（３）の大端面（９）の中央を円形に凹ませたヌスミ部（１４）を有し、
前記円すいころ（３）の大端面（９）と前記ヌスミ部（１４）との境界が、前記大つば面（１５）の径方向外端よりも径方向内側に位置することを特徴とする円すいころ軸受。 The outer ring (1) and
an inner ring (2) arranged coaxially on the radially inner side of the outer ring (1);
a plurality of tapered rollers (3) assembled at intervals in the circumferential direction between the outer ring (1) and the inner ring (2),
In this tapered roller bearing, a conical inner ring raceway surface (6) with which the plurality of tapered rollers (3) roll and contact is provided on the outer periphery of the inner ring (2), and a large rib (8) formed to protrude radially outward from a large diameter side end of the inner ring raceway surface (6),
The large rib (8) has a chamfered portion (17) that slopes radially inward from the outer diameter surface (16) of the large rib (8) toward the tapered roller (3), a large rib surface (15) in cross section that contacts the large end face (9) of the tapered roller (3), a relief R portion (20) that smoothly connects to the radially outer side of the large rib surface (15) and has a convex arc-shaped cross section that curves in a direction away from the large end face (9) of the tapered roller (3), and a relief straight portion (21) that smoothly connects to the radially outer side of the relief R portion (20) so as to form a tangent to the relief R portion (20) and has a straight cross section that intersects the chamfered portion (17),
The tapered roller (3) has a recessed portion (14) formed by circularly recessing the center of the large end face (9) of the tapered roller (3),
A tapered roller bearing characterized in that the boundary between the large end face (9) of the tapered roller (3) and the recessed portion (14) is located radially inward of the radial outer end of the large rib surface (15).
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| JP2007100934A (en) | 2005-10-07 | 2007-04-19 | Ntn Corp | Self-aligning roller bearing |
| JP2019173854A (en) | 2018-03-28 | 2019-10-10 | Ntn株式会社 | Tapered roller bearing |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007100934A (en) | 2005-10-07 | 2007-04-19 | Ntn Corp | Self-aligning roller bearing |
| JP2019173854A (en) | 2018-03-28 | 2019-10-10 | Ntn株式会社 | Tapered roller bearing |
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