JP2012112517A - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
JP2012112517A
JP2012112517A JP2011071727A JP2011071727A JP2012112517A JP 2012112517 A JP2012112517 A JP 2012112517A JP 2011071727 A JP2011071727 A JP 2011071727A JP 2011071727 A JP2011071727 A JP 2011071727A JP 2012112517 A JP2012112517 A JP 2012112517A
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Prior art keywords
tapered roller
inner ring
roller bearing
main body
diameter surface
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JP2011071727A
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Japanese (ja)
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Takanobu Asai
孝宜 浅井
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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
    • F16C19/36—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
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings

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

Abstract

PROBLEM TO BE SOLVED: To provide a tapered roller bearing having superior collar strength and an increased bearing life by eliminating stress concentration in an intersection between a collar face and a raceway of an inner race.SOLUTION: The tapered roller bearing includes an outer race 2, an inner race 3, and a plurality of tapered rollers 4 disposed between the outer race 2 and the inner race 3. The inner race 3 is separated into an inner race body 31 having an inner diameter face 31d on an inner periphery and a raceway face 31a and an outer diameter face 31b on an outer circumference, and a collar 32 to be in contact with a large end face 4b of the tapered roller 4. The collar 32 is disposed as circumscribed to the inner race body 31. An inner diameter face 32b of the collar 32 and the outer diameter face 31b of the inner race body 31 are formed into cylindrical faces concentric to the inner diameter face 31d of the inner race body 31, and thereby, the collar 32 and the inner race body 31 can be relatively moved in the axial direction.

Description

本発明は円すいころ軸受に係り、より詳しくは、自動車の終減速機、その他に使用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 used for a final reduction gear of an automobile and the like.

自動車の終減速機のようなスラスト荷重の大きな用途には、通常、外輪と、内輪と、外輪と内輪の間に配置された複数の円すいころと、内輪に前記円すいころの大端に接する鍔面を有する鍔部とを備える円すいころ軸受が使用される。前述の構成において、鍔面には円すいころの端面から軸方向の負荷が作用し、鍔面と内輪の軌道部の交差部には大きな応力の集中が発生するので、鍔部の強度が低下し、内輪の寿命が低下する。   For applications with large thrust loads such as final reduction gears for automobiles, the outer ring, the inner ring, a plurality of tapered rollers arranged between the outer ring and the inner ring, and the inner ring are in contact with the large end of the tapered roller. Tapered roller bearings having a flange with a surface are used. In the above-described configuration, an axial load acts on the flange surface from the end surface of the tapered roller, and a large stress concentration occurs at the intersection of the flange surface and the raceway portion of the inner ring, so the strength of the flange portion decreases. The life of the inner ring is reduced.

この対応として、鍔部の軸方向の幅を拡大することが考えられるが、鍔部の軸方向の幅の拡大には、軸受の組幅の拡大か、内輪の軌道部の幅の縮小が必要である。しかし、通常は軸受の組幅は制限されており、軸受の組幅の拡大は困難である。又軌道部の幅の縮小は軸受の負荷容量の減少すなわち軸受寿命の減少をもたらす。   To cope with this, it is conceivable to increase the axial width of the flange, but to increase the axial width of the flange, it is necessary to increase the bearing assembly width or to reduce the inner ring raceway width. It is. However, the bearing group width is usually limited, and it is difficult to increase the bearing group width. Further, the reduction in the width of the raceway portion causes a reduction in the load capacity of the bearing, that is, a reduction in the bearing life.

また、図８に示す円すいころ軸受２１のように、内輪２３の鍔面２３ｆと軌道部２３ａの交差部２３ｄに切削加工による逃げＡを形成し、応力集中を緩和するやり方もある。
また、他の応力集中の対応として、図９に示す円すいころ軸受３１のように、内輪３３の鍔面３３ｆと軌道部３３ａとの交差部２２ｄは逃げを廃止し、断面円弧状の隅部Ｂとしたもの（特許文献１参照）等がある。 In addition, as in the tapered roller bearing 21 shown in FIG. 8, there is a method of reducing stress concentration by forming a clearance A by cutting at the intersecting portion 23d of the flange surface 23f of the inner ring 23 and the raceway portion 23a.
Further, as another countermeasure for stress concentration, as in the tapered roller bearing 31 shown in FIG. 9, the intersection 22d between the flange surface 33f of the inner ring 33 and the raceway 33a eliminates the relief, and the corner B having the arcuate cross section is eliminated. (See Patent Document 1).

特開２００７―３３３０４７号公報JP 2007-333047 A

しかしながら、上述の鍔部の幅の拡大や、前記交差部の研削仕上げ等の鍔部強度向上手段は、交差部の応力集中を緩和することはできるが、いずれの対策案も交差部が最弱部であることは変わらず、根本的な鍔部強度向上策とはなっていない。また、前記いずれの対策案も鍔部の軸方向外方側面と軸肩部端面の間に隙間が存在する場合、前記交差部の応力はさらに増大し鍔部強度は低下する。   However, the means for improving the strength of the heel such as the expansion of the width of the heel and the grinding finish of the intersection described above can alleviate the stress concentration at the intersection, but in any of the countermeasures, the intersection is weakest. This is not a fundamental measure for improving the strength of the buttocks. In any of the above countermeasures, when there is a gap between the axially outer side surface of the heel and the end face of the shoulder portion, the stress at the intersecting portion further increases and the heel strength decreases.

この発明の目的は、鍔面と内輪の軌道部との交差部の応力集中を排除することで、鍔部強度がすぐれ、かつ軸受寿命を向上できる円すいころ軸受を提供することにある。   SUMMARY OF THE INVENTION An object of the present invention is to provide a tapered roller bearing that has excellent flange strength and can improve bearing life by eliminating stress concentration at the intersection between the flange surface and the raceway portion of the inner ring.

上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、外輪と内輪と前記外輪と前記内輪の間に配置された複数の円すいころとを備える円すいころ軸受において、前記内輪は内周に内径面、外周に軌道面および、外径面を有する内輪本体部と、前記円すいころの大端面に接する鍔部とに分離され、前記鍔部は前記内輪本体部に外接して配置され、前記鍔部の内径面および前記内輪本体部の外径面は前記内輪本体部の内径面と同心の円筒面に形成することにより、前記鍔部と前記内輪本体部は軸方向に相対移動が可能であることである。   In order to solve the above-described problem, the structural feature of the invention according to claim 1 is that in the tapered roller bearing including an outer ring, an inner ring, and a plurality of tapered rollers disposed between the outer ring and the inner ring, the inner ring Is separated into an inner ring body portion having an inner diameter surface on the inner periphery, a raceway surface and an outer diameter surface on the outer periphery, and a flange portion that contacts the large end surface of the tapered roller, and the flange portion circumscribes the inner ring body portion. The inner diameter surface of the flange portion and the outer diameter surface of the inner ring main body portion are formed on a cylindrical surface concentric with the inner diameter surface of the inner ring main body portion, so that the flange portion and the inner ring main body portion are axially relative to each other. It is possible to move.

円すいころ軸受が荷重を受けると、前記鍔面には前記ころの大端面より軸方向の負荷が作用するが、本発明においては、前記鍔部はあらかじめ内輪本体部と分離しているため、前記大鍔面と前記内輪本体部の軌道面の交差部に応力の集中が発生することはない。さらに、前記鍔部は軸方向に移動が可能であり、組付け状態において、軸肩部端面と前記鍔部の外方側面との間に隙間が存在していても、前記ころの大端面よりの軸方向の負荷によって、前記鍔部は、前記外方側面が前記軸肩部端面に接触するまで移動し安定した位置関係を保ち通常の組付け状態と同等の鍔部の強度が確保できる。   When the tapered roller bearing receives a load, an axial load acts on the flange surface from the large end surface of the roller, but in the present invention, the flange portion is separated from the inner ring main body portion in advance. Stress concentration does not occur at the intersection of the large collar surface and the raceway surface of the inner ring main body. Further, the flange portion is movable in the axial direction, and in the assembled state, even if there is a gap between the shaft shoulder end surface and the outer side surface of the flange portion, it is more than the large end surface of the roller. Due to the axial load, the collar moves until the outer side surface comes into contact with the end face of the shaft shoulder, maintains a stable positional relationship, and can ensure the strength of the collar equivalent to that in a normal assembled state.

上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、前記鍔部の内径面の直径および前記内輪本体部の外径面の直径は前記複数の円すいころの最大内接円径に略等しく形成されたことである。   In order to solve the above-described problem, the structural feature of the invention according to claim 2 is that the diameter of the inner diameter surface of the flange portion and the diameter of the outer diameter surface of the inner ring main body portion are the maximum inscribed in the plurality of tapered rollers. It is formed substantially equal to the diameter of the circle.

前記円すいころの最大内接円径とは前記ころが軸受に組み込まれた状態で前記ころの転動面が前記内輪本体の軌道面に接する最大径である。上記構成によれば前記ころの転動面と前記内輪本体の軌道面との有効接触長さが確保されるため、軸受負荷容量を保つ範囲で前記鍔部の前記外方側面の面積は最大となり、鍔部の軸方向圧縮応力を軽減することができる。   The maximum inscribed circle diameter of the tapered roller is the maximum diameter where the rolling surface of the roller contacts the raceway surface of the inner ring main body in a state where the roller is incorporated in a bearing. According to the above configuration, since the effective contact length between the rolling surface of the roller and the raceway surface of the inner ring main body is ensured, the area of the outer side surface of the flange is maximized within a range in which the bearing load capacity is maintained. The axial compressive stress of the buttocks can be reduced.

上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、前記鍔部の内径面と前記内輪本体部の外径面は締め代を持った嵌めあいで係合されたことである。上記構成によれば、運搬時や組付け時における前記鍔部と前記内輪本体部の分離による不具合を防止できる。   In order to solve the above-described problem, the structural feature of the invention according to claim 3 is that the inner diameter surface of the flange portion and the outer diameter surface of the inner ring main body portion are engaged with each other with a fit. It is. According to the said structure, the malfunction by the separation | separation of the said collar part and the said inner ring main-body part at the time of conveyance or an assembly | attachment can be prevented.

上記の課題を解決するため、請求項４に係る発明の構成上の特徴は、前記鍔部の内径面と前記内輪本体部の外径面の間に保持リングが介在され、前記保持リングによって前記内輪本体部と前記鍔部が係止されたことである。上記構成によれば、運搬時や組付け時における前記鍔部と前記内輪本体部の分離による不具合を防止でき、かつ前記鍔部の内径面と前記内輪本体部の外径面をすきまを持った嵌めあいで係合することにより、前記軸方向の負荷による前記鍔部の移動は容易に行え、常に安定した位置関係を保ち通常の組付け状態と同等の鍔部の強度が確保できる。   In order to solve the above-described problem, a structural feature of the invention according to claim 4 is that a holding ring is interposed between the inner diameter surface of the flange portion and the outer diameter surface of the inner ring main body portion, and the holding ring causes the That is, the inner ring main body portion and the collar portion are locked. According to the above configuration, problems due to separation of the flange part and the inner ring main body part during transportation and assembly can be prevented, and a gap is provided between the inner diameter surface of the flange part and the outer diameter surface of the inner ring main body part. By engaging by fitting, the collar part can be easily moved by the load in the axial direction, and a stable positional relationship is always maintained and the strength of the collar part equivalent to that in a normal assembled state can be secured.

上記の課題を解決するため、請求項５に係る発明の構成上の特徴は、前記保持リングは弾性材料で形成されたことである。前記保持リングを弾性材料で形成することにより、上記の前記鍔部と前記内輪本体部とは容易に係止可能となる。   In order to solve the above problem, a structural feature of the invention according to claim 5 is that the retaining ring is made of an elastic material. By forming the holding ring from an elastic material, the hook part and the inner ring main body part can be easily locked.

本発明によれば、鍔面と内輪の軌道部との交差部の応力集中排除することで、鍔部の強度にすぐれ、かつ軸受寿命を向上できる円すいころ軸受を提供することができる。   According to the present invention, it is possible to provide a tapered roller bearing that is excellent in strength of the flange portion and can improve the bearing life by eliminating stress concentration at the intersection of the flange surface and the raceway portion of the inner ring.

本発明の第１の実施形態の円すいころ軸受の断面図である。It is sectional drawing of the tapered roller bearing of the 1st Embodiment of this invention. 図１の円すいころ軸受の構成を説明する説明図である。It is explanatory drawing explaining the structure of the tapered roller bearing of FIG. 本発明の第１の実施形態の円すいころ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 tapered roller bearing of the 1st Embodiment of this invention. 本発明の第１の実施形態の円すいころ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 tapered roller bearing of the 1st Embodiment of this invention. 本発明の第１の実施形態の円すいころ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 tapered roller bearing of the 1st Embodiment of this invention. 本発明の第２の実施形態の円すいころ軸受の断面図であるIt is sectional drawing of the tapered roller bearing of the 2nd Embodiment of this invention. 図６の円すいころ軸受の内輪の構成を説明する説明図である。It is explanatory drawing explaining the structure of the inner ring | wheel of the tapered roller bearing of FIG. 第１の従来例の円すいころ軸受の断面図である。It is sectional drawing of the tapered roller bearing of a 1st prior art example. 第２の従来例の円すいころ軸受の断面図である。It is sectional drawing of the tapered roller bearing of the 2nd prior art example.

この発明の第1の実施の形態を、以下図面を参照して説明する。   A first embodiment of the present invention will be described below with reference to the drawings.

図１は、本発明の第１の実施形態の円すいころ軸受１の断面図である。
円すいころ軸受１は外輪２と、内輪３と、複数の円すいころ４と、複数の円すいころ４を保持する保持器５を備え、内輪３は内輪本体部３１と鍔部３２とで構成される。 FIG. 1 is a sectional view of a tapered roller bearing 1 according to a first embodiment of the present invention.
The tapered roller bearing 1 includes an outer ring 2, an inner ring 3, a plurality of tapered rollers 4, and a cage 5 that holds the plurality of tapered rollers 4, and the inner ring 3 includes an inner ring main body portion 31 and a flange portion 32. .

図２は図１の円すいころ軸受１の構成を説明する説明図である。
外輪２は、内周側に円すい軌道面２ａを有する。一方内輪本体部３１は内周側に内径面３１ｄと外周側に円すい軌道面３１ａおよび、円すい軌道面３１ａの最大径位置で円すい軌道面３１ａに連なり、内径面３１ｄと同心の円筒形状に形成された外径面３１ｂを有し、外径面３１ｂから半径方向内方に延在して内径面３１ｄに垂直な軸受背面３１ｃを有する。 FIG. 2 is an explanatory view illustrating the configuration of the tapered roller bearing 1 of FIG.
The outer ring 2 has a conical track surface 2a on the inner peripheral side. On the other hand, the inner ring main body 31 is formed in a cylindrical shape concentric with the inner diameter surface 31d, which is connected to the inner diameter surface 31d on the inner peripheral side, the conical raceway surface 31a on the outer peripheral side, and the conical raceway surface 31a at the maximum diameter position of the conical raceway surface 31a. And a bearing back surface 31c extending radially inward from the outer diameter surface 31b and perpendicular to the inner diameter surface 31d.

ここで、内輪本体部３１の外径面３１ｂの直径は、円すいころ４が円すいころ軸受１に組み込まれた状態で円すいころ４の転動面が内輪本体部の軌道面に接する最大径すなわち最大内接円径ｄｒに略等しく形成されており、円すいころ軸受１の定格荷重算出の要素である円すいころ４の転動面４ａと内輪本体部３１の軌道面３１ａとの有効接触長さが確保されている。すなわち、内輪本体部３１の外径面３１ｂの直径は、軸受定格荷重を確保できる範囲での最小値となっている。   Here, the diameter of the outer diameter surface 31b of the inner ring main body 31 is the maximum diameter in which the rolling surface of the tapered roller 4 is in contact with the raceway surface of the inner ring main body in a state where the tapered roller 4 is incorporated in the tapered roller bearing 1. It is formed substantially equal to the inscribed circle diameter dr and ensures an effective contact length between the rolling surface 4a of the tapered roller 4 and the raceway surface 31a of the inner ring main body 31 which is an element for calculating the rated load of the tapered roller bearing 1. Has been. That is, the diameter of the outer diameter surface 31b of the inner ring main body 31 is a minimum value within a range in which the bearing load rating can be secured.

鍔部３２は内周側に内輪本体部３１の外径面３１ｂと同心の円筒形状に形成された内径面３２ｂを、軸方向内方の端面に中心軸が軸受の回転中心ＣＬに等しく半径方向内方に凹状の円すい形状の鍔面３２ａをそれぞれ有している。ここで鍔面３２ａの断面形状は直線または、直線に近い軸方向外方に凹状の円弧に形成されている。もう一方の端面は内径面３２ｂに垂直な外方端面３２ｃである。内径面３２ｂの直径は内輪本体部３１の外径面３１ｂの直径と略等しく、上述のごとく、軸受定格荷重を確保できる範囲での最小値に形成されている。これにより、前記外方側面３２ｃの面積は、軸受定格荷重を確保できる範囲で最大となる。   The flange portion 32 has an inner diameter surface 32b formed in a cylindrical shape concentric with the outer diameter surface 31b of the inner ring main body portion 31 on the inner peripheral side. Each has a concave conical flange surface 32a. Here, the cross-sectional shape of the flange surface 32a is a straight arc or an arc that is concave outward in the axial direction close to the straight line. The other end face is an outer end face 32c perpendicular to the inner diameter face 32b. The diameter of the inner diameter surface 32b is substantially equal to the diameter of the outer diameter surface 31b of the inner ring main body 31 and is formed to a minimum value within a range in which a bearing load rating can be secured as described above. Thereby, the area of the said outer side surface 32c becomes the maximum in the range which can ensure a bearing rated load.

また、複数の円すいころ４は円すい形状の転動面４ａおよび、大端面４ｂを有する。また、転動面４ａと大端面４ｂの交差部に面取り４ｃを有する。ここで大端面４ｂは転動面４ａを延長した円すいの頂点Ｏから大端面４ｂまでの距離に略等しい曲率半径Ｒｒを持つ球面に形成されている。   Further, the plurality of tapered rollers 4 have a tapered rolling surface 4a and a large end surface 4b. Further, a chamfer 4c is provided at the intersection of the rolling surface 4a and the large end surface 4b. Here, the large end face 4b is formed into a spherical surface having a radius of curvature Rr substantially equal to the distance from the apex O of the cone extending from the rolling face 4a to the large end face 4b.

図１および、図２に示すように、複数の円すいころ４は対向する外輪２の円すい軌道面２ａと、内輪本体部３１の円すい軌道面３１ａに転動面４ａを接し、鍔面３２ａに大端面４ｂを接して、保持器５に所定の間隔に保持されている。また、内輪本体部３１と鍔部３２とは、内輪本体部３１の外径面３１ｂと鍔部３２の内径面３２ｂとが軸受１に通常の予圧が与えられた時は軸方向に相対移動可能であるが、軸受１の自重のみでは相対移動できない程度のしめしろの嵌合いで係合されている。すなわち、運搬時や組付け時の鍔部３２と内輪本体部３１の分離による不具合を防止できる。   As shown in FIG. 1 and FIG. 2, the plurality of tapered rollers 4 are in contact with the conical raceway surface 2a of the opposed outer ring 2 and the conical raceway surface 31a of the inner ring main body 31, and the rolling surface 4a is in contact with the flange 32a. The end surface 4b is contacted and held by the cage 5 at a predetermined interval. Further, the inner ring body 31 and the flange 32 are relatively movable in the axial direction when the outer diameter surface 31b of the inner ring body 31 and the inner surface 32b of the flange 32 are given a normal preload to the bearing 1. However, the bearings 1 are engaged with an interference fit that cannot be relatively moved only by the weight of the bearing 1 alone. That is, it is possible to prevent problems due to separation of the collar portion 32 and the inner ring main body portion 31 during transportation or assembly.

図３は本実施形態の円すいころ軸受の作用を説明する説明図である。
車両の終減速器等の軸受装置に組込まれた本実施形態の円すいころ軸受１は、内輪本体３１は前記軸受装置の軸５０に圧入され、内輪本体部３１の背面３１ｃおよび、鍔部３２の外方端面３２ｃは軸５０の肩部端面５０ａに接して組込まれている。 FIG. 3 is an explanatory view for explaining the operation of the tapered roller bearing of the present embodiment.
In the tapered roller bearing 1 of this embodiment incorporated in a bearing device such as a final reduction gear of a vehicle, the inner ring body 31 is press-fitted into the shaft 50 of the bearing device, and the back surface 31c of the inner ring body portion 31 and the flange portion 32 The outer end surface 32 c is assembled in contact with the shoulder end surface 50 a of the shaft 50.

ここで、円すいころ軸受１がスラスト荷重Ｆａおよびラジアル荷重Ｆｒを受けると、各円すいころ４の転動面４ａと外輪軌道２ａの間の負荷Ｐｏ、転動面４ａと内輪軌道３１ａの間の負荷Ｐｉおよび円すいころ４の端面４ｂと前記鍔面３２ａとの間の負荷Ｐｒが作用する。このとき、本実施形態の円すいころ軸受１においては、鍔部３２はあらかじめ内輪本体部３１とは分離しているため、鍔部３２には主に軸方向の圧縮応力が発生するだけで、従来の円すいころ軸受に見られるような鍔面と内輪軌道面の交差部の応力集中は生じない。その結果、鍔部の強度が低下することがない。また、軸５０の肩部端面５０ａと接触する鍔部３２の外方側面３２ｃの面積は上述のごとく、軸受定格荷重を確保できる範囲で最大に形成されているため、鍔部３２の軸方向の圧縮応力は軸受定格荷重を確保できる範囲で最小となる。   Here, when the tapered roller bearing 1 receives the thrust load Fa and the radial load Fr, the load Po between the rolling surface 4a of each tapered roller 4 and the outer ring raceway 2a, and the load between the rolling surface 4a and the inner ring raceway 31a. Pi and the load Pr between the end surface 4b of the tapered roller 4 and the flange surface 32a act. At this time, in the tapered roller bearing 1 of the present embodiment, since the flange portion 32 is separated from the inner ring main body portion 31 in advance, only the axial compressive stress is generated in the flange portion 32. No stress concentration occurs at the intersection between the flange surface and the inner ring raceway surface, as seen in tapered roller bearings. As a result, the strength of the buttocks does not decrease. Moreover, since the area of the outer side surface 32c of the collar part 32 which contacts the shoulder part end surface 50a of the axis | shaft 50 is formed in the maximum in the range which can ensure a bearing rated load as mentioned above, it is the axial direction of the collar part 32. The compressive stress is minimized within the range where the bearing load rating can be secured.

図４および図５に軸５０の肩部端面５０ａの平坦度が悪く、肩部端面５０ａと鍔部３２の外方端面３２ｃとの間に隙間δが形成され場合を示す。この状態で円すいころ軸受１が荷重ＦｒおよびＦａを受け、鍔面３２ａに負荷Ｐｒが作用すると、従来の円すいころ軸受においては鍔面と内輪軌道面の交差部に極端に大きな応力の集中がみられ、鍔の寿命は著しく短くなるが、本実施形態の円すいころ軸受１においては、図５に示すように、鍔部３２は前記隙間δに略等しい距離だけ軸方向外方に移動し、軸５０の肩部端面５０ａに接触し安定状態を保つため、鍔部には異常な応力の集中は発生しない。   4 and 5 show a case where the flatness of the shoulder end face 50a of the shaft 50 is poor and a gap δ is formed between the shoulder end face 50a and the outer end face 32c of the flange 32. FIG. In this state, when the tapered roller bearing 1 receives the loads Fr and Fa and the load Pr acts on the flange surface 32a, in the conventional tapered roller bearing, an extremely large stress concentration is observed at the intersection of the flange surface and the inner ring raceway surface. However, in the tapered roller bearing 1 of the present embodiment, as shown in FIG. 5, the collar portion 32 moves outward in the axial direction by a distance substantially equal to the gap δ. In order to maintain a stable state by contacting the shoulder end face 50a of 50, abnormal stress concentration does not occur in the buttocks.

すなわち本実施形態の円すいころ軸受１によれば、通常の組付け状態においても、軸５０の肩部端面５０ａの平坦度が悪い組付け状態においても従来の円すいころ軸受にくらべ鍔部強度が優れ、軸受の長寿命化を図ることができる。
さらに鍔部の幅を縮小することも可能になり、通常の軸受に比べ転動面の長さが長い円すいころを採用することにより、軸受の負荷容量を増大させることもできる。 That is, according to the tapered roller bearing 1 of the present embodiment, the strength of the flange portion is superior to that of the conventional tapered roller bearing even in a normal assembled state and in an assembled state in which the flatness of the shoulder end surface 50a of the shaft 50 is poor. The life of the bearing can be extended.
Further, it is possible to reduce the width of the flange portion, and it is possible to increase the load capacity of the bearing by employing a tapered roller having a longer rolling surface than a normal bearing.

次に、図６および図７に基づいて本発明の第２の実施の形態を説明するが、第２の実施形態の円すいころ軸受１１では、第１の実施形態の円すいころ軸受１と共通の構成、作用効果については説明を省略することにし、第１の実施形態の円すいころ軸受１と異なる構成、作用効果についてのみ説明を行う。   Next, a second embodiment of the present invention will be described with reference to FIGS. 6 and 7. The tapered roller bearing 11 of the second embodiment is common to the tapered roller bearing 1 of the first embodiment. The description of the configuration and the operational effects will be omitted, and only the configuration and the operational effects different from the tapered roller bearing 1 of the first embodiment will be described.

図６は本発明の第２の実施形態の円すいころ軸受１１の断面図である。
図７は図６の円すいころ軸受１１の構成を説明する説明図である。
第２の実施形態は内輪本体部１３１と鍔部１３２の係合部が第１の実施形態と異なる。
図６および図７において、内輪本体部１３１の外径部１３１ｂの軸方向外方には矩形の溝１３１ｅを有し、鍔部１３２の内径部１３２ｂ軸方向外方には矩形の溝１３２ｅを有している。また、鍔部１３２の内径部１３２ｂと内輪本体部１３２の外径部１３１ｂはすきま嵌めで嵌合されている。さらに、溝１３１ｅおよび、１３２ｅには例えばＯリング等の弾性材料で形成された保持リング１３３が挿入され、鍔部１３２と内輪本体１３１が係止されている。 FIG. 6 is a sectional view of the tapered roller bearing 11 according to the second embodiment of the present invention.
FIG. 7 is an explanatory view illustrating the configuration of the tapered roller bearing 11 of FIG.
The second embodiment is different from the first embodiment in the engagement portion between the inner ring main body 131 and the flange 132.
6 and 7, a rectangular groove 131e is provided on the outer side in the axial direction of the outer diameter portion 131b of the inner ring main body 131, and a rectangular groove 132e is provided on the outer side in the axial direction of the inner diameter portion 132b of the flange portion 132. is doing. Further, the inner diameter portion 132b of the flange portion 132 and the outer diameter portion 131b of the inner ring main body portion 132 are fitted with a clearance fit. Further, a holding ring 133 made of an elastic material such as an O-ring is inserted into the grooves 131e and 132e, and the flange 132 and the inner ring main body 131 are locked.

本実施形態の円すいころ軸受１１によれば、軸受を容易に組立てることができ、また、運搬時や組付け時の鍔部１３２と内輪本体部１３１の分離を防止でき、かつ軸方向の負荷による鍔部の移動は容易に行え、常に安定状態を保つため、鍔部に異常な応力の集中は発生せず、鍔部強度が優れ、軸受の長寿命化を図ることができる。   According to the tapered roller bearing 11 of the present embodiment, the bearing can be easily assembled, the separation of the flange 132 and the inner ring main body 131 during transportation and assembly can be prevented, and due to an axial load. Since the collar portion can be easily moved and always kept stable, abnormal stress concentration does not occur in the collar portion, the collar strength is excellent, and the life of the bearing can be extended.

なお、第２の実施形態における円すいころ軸受１１はＯリング等の弾性材料で形成された保持リング１３３で構成されているが、この発明では金属材料で形成された保持リングで構成される円すいころ軸受であってもよい。   The tapered roller bearing 11 in the second embodiment is configured by a holding ring 133 formed of an elastic material such as an O-ring. In the present invention, the tapered roller configured by a holding ring formed of a metal material is used. It may be a bearing.

また、第２の実施形態における円すいころ軸受１１は内輪本体部１３１および、鍔部１３２の両方に保持リング１３３を挿入する矩形の溝１３１ｅおよび、１３２ｅを有しているが、この発明では内輪本体部１３１または、鍔部１３２のいずれかに保持リングを挿入する矩形の溝を有する円すいころ軸受であってもよい。   The tapered roller bearing 11 in the second embodiment has rectangular grooves 131e and 132e into which the retaining ring 133 is inserted into both the inner ring main body 131 and the flange 132. A tapered roller bearing having a rectangular groove into which the holding ring is inserted into either the portion 131 or the flange portion 132 may be used.

なお、第１の実施形態および、第２の実施形態における円すいころ軸受１および、円すいころ軸受１１は単列の円すいころで構成される単列円すいころ軸受であるが、この発明では多列の円すいころで構成される複列円すいころ軸受や４列円すいころ軸受等の多列円すいころ軸受であってもよい。   The tapered roller bearing 1 and the tapered roller bearing 11 in the first embodiment and the second embodiment are single-row tapered roller bearings configured by a single-row tapered roller. It may be a multi-row tapered roller bearing such as a double-row tapered roller bearing or a 4-row tapered roller bearing composed of tapered rollers.

１、１１、２１、３１ ‥ 円すいころ軸受
２ ‥ 外輪
３、１３、２３、３３ ‥ 内輪
３１、１３１ ‥ 内輪本体部
３１ａ、２３ａ、３３ａ ‥ 軌道面
３１ｂ、１３１ｂ ‥ 外径面
３１ｄ ‥ 内輪本体部の内径面
３２、１３２ ‥ 鍔部
３２ｂ、１３２ｂ ‥ 鍔部の内径面
４ ‥ 円すいころ
４ｂ ‥ 大端面
ｄｒ ‥ 円すいころの最大内接円径
５ ‥ 保持器
５０ ‥ 軸
１３３ ‥ 保持リング 1, 11, 21, 31 ... Tapered roller bearing 2 ... Outer ring 3, 13, 23, 33 ... Inner ring 31, 131 ... Inner ring main body 31a, 23a, 33a ... Track surface 31b, 131b ... Outer diameter surface 31d ... Inner ring main body Inner diameter surfaces 32, 132 ··· flange portions 32b and 132b ··· Inner diameter surface 4 of the flange portion · Tapered roller 4b · Large end surface dr · Maximum inscribed circle diameter 5 of the tapered roller · · · Cage 50 · · · Shaft 133 · · · Holding ring

Claims (5)

外輪と、内輪と、前記外輪と前記内輪の間に配置された複数の円すいころとを備える円すいころ軸受において、
前記内輪は内周に内径面、外周に軌道面および、外径面を有する内輪本体部と、前記円すいころの大端面に接する鍔部とに分離され、前記鍔部は前記内輪本体部に外接して配置され、
前記鍔部の内径面および前記内輪本体部の外径面が前記内輪本体部の内径面と同心の円筒面に形成されることにより、前記鍔部と前記内輪本体部は軸方向に相対移動が可能であることを特徴とする円すいころ軸受。 In a tapered roller bearing comprising an outer ring, an inner ring, and a plurality of tapered rollers disposed between the outer ring and the inner ring,
The inner ring is separated into an inner ring body portion having an inner diameter surface on the inner periphery, a raceway surface on the outer periphery, and an outer diameter surface, and a flange portion that contacts the large end surface of the tapered roller, and the flange portion circumscribes the inner ring body portion. Arranged,
By forming the inner diameter surface of the flange portion and the outer diameter surface of the inner ring main body portion on a cylindrical surface concentric with the inner diameter surface of the inner ring main body portion, the flange portion and the inner ring main body portion are relatively moved in the axial direction. Tapered roller bearings that are possible. 前記鍔部の内径面の直径および前記内輪本体部の外径面の直径は前記複数の円すいころの最大内接円径に略等しく形成されたことを特徴とする請求項１に記載の円すいころ軸受。   2. The tapered roller according to claim 1, wherein a diameter of an inner diameter surface of the flange portion and a diameter of an outer diameter surface of the inner ring main body portion are substantially equal to a maximum inscribed circle diameter of the plurality of tapered rollers. bearing. 前記鍔部の内径面と前記内輪本体部の外径面は締め代を持った嵌めあいで係合されたことを特徴とする請求項１または請求項２に記載の円すいころ軸受。   The tapered roller bearing according to claim 1 or 2, wherein an inner diameter surface of the flange portion and an outer diameter surface of the inner ring main body portion are engaged with each other with a tight fit. 前記鍔部の内径面と前記内輪本体部の外径面の間に保持リングが介在され、前記保持リングによって前記内輪本体部と前記鍔部が係止されたことを特徴とする請求項１から請求項３のいずれかに記載の円すいころ軸受。   2. A holding ring is interposed between an inner diameter surface of the flange portion and an outer diameter surface of the inner ring main body portion, and the inner ring main body portion and the flange portion are locked by the holding ring. The tapered roller bearing according to claim 3. 前記保持リングは弾性材料で形成されたことを特徴とする請求項４に記載の円すいころ軸受。   The tapered roller bearing according to claim 4, wherein the retaining ring is made of an elastic material.
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205745A1 (en) * 2015-03-31 2016-10-06 Aktiebolaget Skf bearing arrangement

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205745A1 (en) * 2015-03-31 2016-10-06 Aktiebolaget Skf bearing arrangement

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