JP6381232B2 - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
JP6381232B2
JP6381232B2 JP2014039213A JP2014039213A JP6381232B2 JP 6381232 B2 JP6381232 B2 JP 6381232B2 JP 2014039213 A JP2014039213 A JP 2014039213A JP 2014039213 A JP2014039213 A JP 2014039213A JP 6381232 B2 JP6381232 B2 JP 6381232B2
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peripheral surface
outer peripheral
lip
inner ring
cored bar
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JP2015161403A (en
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英信 馬上
英信 馬上
今野　勝広
勝広 今野
永嶋　正道
正道 永嶋
四阿　佳昭
佳昭 四阿
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NSK Ltd
Nok Corp
Nippon Steel Corp
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NSK Ltd
Nok Corp
Nippon Steel 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7806—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for spherical roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/084—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface sliding on a complementary spherical surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward

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

Description

本発明は、転がり軸受に関する。 The present invention relates to a rolling bearing rising.

鉄等の金属材料を圧延するための連続鋳造機のロールは、その軸方向両端部に同軸上に設けたロールネックと称される円柱部を、例えば複列円すいころ軸受を介して回転自在に支承した構造を有する。このような連続鋳造機設備に用いられる軸受は、通常、シールなしの非密封タイプであり、グリースが連続給脂機構により常に軸受に供給される。   A roll of a continuous casting machine for rolling a metal material such as iron can be freely rotated through a cylindrical portion called a roll neck provided coaxially at both axial end portions thereof, for example, via a double row tapered roller bearing. Has a supported structure. The bearing used in such a continuous casting machine facility is usually an unsealed type without a seal, and grease is always supplied to the bearing by a continuous greasing mechanism.

また、連続鋳造機設備に用いられる軸受としては、圧延水や冷却水が軸受内部に浸入することを防止するためにシール装置を具備している密封タイプもある。このようなシール装置としては、軸受の軸方向端部開口を遮蔽して、内輪及び外輪間の軸受内部空間をシールするシールリップ部を接触面に摺接させる接触シール構造からなるものが知られている（例えば、特許文献１参照）。特許文献１のシール装置では、シールリップ部の基端部位に金属環が埋設されており、当該金属環によって基端部位が補強されている。   Moreover, as a bearing used for continuous casting machine equipment, there is also a sealed type provided with a sealing device to prevent rolling water or cooling water from entering the inside of the bearing. As such a seal device, there is known a device having a contact seal structure that shields a bearing lip portion that seals the bearing inner space between the inner ring and the outer ring and that contacts the contact surface by shielding the axial end opening of the bearing. (For example, refer to Patent Document 1). In the sealing device of Patent Document 1, a metal ring is embedded in the base end portion of the seal lip portion, and the base end portion is reinforced by the metal ring.

特開２００３−２２７５２２号公報JP 2003-227522 A

ところで、連続鋳造設備は、水蒸気や酸化スケールのある環境内に使用される為、グリースが水やスケールにより汚染されやすく、汚染されたグリースが軸受内部へ供給されると、軸受の摩耗・破損に繋がる。更に、連続給脂用のグリースは、一台の連続鋳造機にあたり年間およそ３０〜７０トンの使用量が必要とれるので、グリース廃棄物の量が膨大であり、環境汚染の虞があり、グリース廃棄物の処理も煩雑でコストがかかる。このように、グリースの使用量を減らし、環境負荷の少ない軸受の開発が課題となっている。   By the way, since the continuous casting equipment is used in an environment with water vapor and oxide scale, grease is likely to be contaminated by water and scale, and if contaminated grease is supplied into the bearing, the bearing may be worn or damaged. Connected. Furthermore, since grease for continuous lubrication requires a usage of approximately 30 to 70 tons per year per continuous casting machine, the amount of grease waste is enormous and there is a risk of environmental pollution. Processing of objects is also complicated and expensive. Thus, the development of bearings that reduce the amount of grease used and have a low environmental load is an issue.

そこで、特許文献１のように、シール装置を有する密封タイプの軸受を用いることも考えられるが、このシール装置では、軸の偏心や傾きが発生した場合、接触面との接触状態が変化し、強く当たる部分と弱く当たる部分とが発生する。そして、接触面と強く当接している部分では、破損が生じ易くなってしまう。一方、接触面と弱く当接している部分では、接触面とのしめしろが弱くなることで、軸受内部の潤滑剤が漏れ易くなると共に、外部から異物が浸入し易くなり、軸受の早期損傷を招く虞がある。   Therefore, it is conceivable to use a sealed bearing having a sealing device as in Patent Document 1, but in this sealing device, when the shaft is eccentric or inclined, the contact state with the contact surface changes, A portion that hits strongly and a portion that hits weakly occur. And in the part which is contact | abutting strongly with a contact surface, it will become easy to produce a damage. On the other hand, at the portion that is weakly in contact with the contact surface, the interference with the contact surface is weakened, so that the lubricant inside the bearing is likely to leak and foreign matter can easily enter from the outside, causing early bearing damage. There is a risk of inviting.

また、ゴム材からなるシールリップ部に疲労（塑性変形やへたり）が生じた場合や、
連続鋳造設備が高温運転（約７００〜１５００℃）されることにより、軸受の内部温度が約７０℃〜８０℃に上昇して軸受内の圧力上昇が発生した場合も、シールリップ部と接触面とが開き、軸受内の潤滑剤の漏れや、外部からの異物浸入が発生する虞がある。 Also, when fatigue (plastic deformation or sag) occurs in the seal lip part made of rubber material,
Even when the internal temperature of the bearing rises to about 70 ° C. to 80 ° C. due to the high temperature operation (about 700 to 1500 ° C.) of the continuous casting equipment, the seal lip portion and the contact surface May open, causing leakage of the lubricant in the bearing and entry of foreign matter from the outside.

本発明は、前述した課題に鑑みてなされたものであり、軸の偏心や傾きが発生した場合であっても軸受の密封性を良好に維持可能であり、且つ、シールリップ部の耐圧性（耐内圧性、耐外圧性）を向上可能であり、疲労の発生を抑制可能な転がり軸受を提供することにある。 The present invention has been made in view of the above-described problems, and can maintain the sealing performance of the bearing well even when the shaft is eccentric or inclined, and the pressure resistance of the seal lip portion ( It is an object of the present invention to provide a rolling bearing capable of improving internal pressure resistance and external pressure resistance and capable of suppressing the occurrence of fatigue.

本発明の上記目的は、下記の構成により達成される。
（１） 内輪の外周面並びに外輪若しくは外輪の径方向外側に配置された球面座の内周面との間に存在する空間の軸方向端部開口を塞ぐように、略円環形状に形成される転がり軸受用密封装置を備える転がり軸受であって、
前記転がり軸受用密封装置は、略円環形状の芯金と、前記芯金に固定される弾性体と、
を備え、
前記芯金は、前記外輪若しくは前記球面座の内周面に固定され、径方向内側に延びる第一芯金と、前記第一芯金の径方向内側端部よりも軸方向内側に配置され、径方向内側に延びる第二芯金と、に分割され、
前記弾性体は、前記第一芯金の径方向内側端部と前記第二芯金の径方向外側端部とを接続する接続部と、前記第二芯金に固定されるシールリップ部と、を有し、
前記シールリップ部は、前記第二芯金に固定されるリップ腰部と、前記リップ腰部から連続し、その径方向内側端部が前記内輪の外周面に摺接するリップ先端部と、を有し、
前記リップ先端部の外周面には、該リップ先端部を前記内輪の外周面に向けて付勢するスプリングが配置され、
前記リップ先端部の、径方向内側端部と前記スプリングの径方向内側端部との間の径方向厚さは、前記内輪の外周面の直径の１％以上であり、
前記第二芯金の内径は、前記リップ腰部の径方向厚さが最小となる箇所の外周面の径より小さく、
前記スプリングと前記第二芯金の間にある前記リップ腰部の径方向厚さは、最小となる箇所において、前記内輪の外周面の直径の１％以上であることを特徴とする転がり軸受。
（２） 前記リップ先端部の径方向内側端部は、前記内輪の外周面に対して、しめしろを持って摺接しており、
前記しめしろの２倍の値は、前記内輪の外周面の直径の１％以上であることを特徴とする（１）に記載の転がり軸受。 The above object of the present invention can be achieved by the following constitution.
(1) It is formed in a substantially annular shape so as to close the axial end opening of the space existing between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring or the spherical seat disposed radially outside the outer ring. A rolling bearing provided with a sealing device for the rolling bearing ,
The rolling bearing sealing device includes a substantially ring-shaped cored bar, an elastic body fixed to the cored bar,
With
The cored bar is fixed to the inner peripheral surface of the outer ring or the spherical seat, and is arranged on the inner side in the axial direction than the first cored bar extending radially inward and the radially inner end of the first cored bar, Divided into a second mandrel extending radially inward,
The elastic body includes a connecting portion that connects a radially inner end portion of the first cored bar and a radially outer end portion of the second cored bar, a seal lip portion fixed to the second cored bar, Have
The seal lip portion includes a lip waist portion fixed to the second core metal, and a lip tip portion that is continuous from the lip waist portion and whose radially inner end portion is in sliding contact with the outer peripheral surface of the inner ring,
On the outer peripheral surface of the lip tip portion, a spring that urges the lip tip portion toward the outer peripheral surface of the inner ring is disposed,
The radial thickness between the radially inner end of the lip tip and the radially inner end of the spring is 1% or more of the diameter of the outer peripheral surface of the inner ring,
Inner diameter of the second core metal is rather smaller than the diameter of the outer peripheral surface of a portion radial thickness of the lip waist is minimized,
The rolling bearing according to claim 1, wherein a radial thickness of the lip waist portion between the spring and the second metal core is 1% or more of a diameter of an outer peripheral surface of the inner ring at a minimum position .
( 2 ) The radially inner end of the lip tip is in sliding contact with the outer peripheral surface of the inner ring with an interference,
2 times the value of White said tightening is rolling bearing according to (1) said at inner ring of more than 1% of the diameter of the outer peripheral surface.

本発明の転がり軸受によれば、芯金は、外輪若しくは球面座の内周面に固定され径方向内側に延びる第一芯金と、第一芯金の径方向内側端部よりも軸方向内側に配置され径方向内側に延びる第二芯金と、を有しており、弾性体は、第一芯金の径方向内側端部と第二芯金の径方向外側端部とを接続する接続部と、第二芯金に固定され、リップ先端部の径方向内側端部が内輪の外周面に摺接するシールリップ部と、を有する。したがって、軸の偏心や傾きが発生した場合であっても、弾性体の接続部が軸の偏心や傾きに追従することによって、シールリップ部と内輪の外周面との接触を維持することが可能である。また、シールリップ部は、第二芯金に固定されるので、内輪の外周面とのしめしろ及び緊迫力を一定に保つことができ、良好なシール性能を発揮することが可能である。
また、リップ先端部の、径方向内側端部とスプリングの径方向内側端部との間の径方向厚さが、内輪の外周面の直径の１％以上となるよう、リップ先端部の肉厚を適切に設定したので、シールリップ部の耐圧性（耐内圧性、耐外圧性）が向上し、軸受の温度上昇によって内部圧力が上昇した場合や、軸受の外部圧力が上昇した場合でも、内輪の外周面に対する緊迫力を維持することが可能であると共に、疲労の発生を抑制することが可能である。 According to the rolling bearing of the present invention, the cored bar is fixed to the inner peripheral surface of the outer ring or the spherical seat and extends radially inward, and axially inward from the radially inner end of the first cored bar. The elastic core is connected to connect the radially inner end of the first core and the radially outer end of the second core. And a seal lip portion that is fixed to the second core metal and in which the radially inner end portion of the lip tip portion is in sliding contact with the outer peripheral surface of the inner ring. Therefore, even when eccentricity or inclination of the shaft occurs, it is possible to maintain the contact between the seal lip portion and the outer peripheral surface of the inner ring by the connecting portion of the elastic body following the eccentricity or inclination of the shaft. It is. Further, since the seal lip portion is fixed to the second cored bar, the interference with the outer peripheral surface of the inner ring and the tightening force can be kept constant, and good sealing performance can be exhibited.
Further, the thickness of the lip tip is such that the radial thickness between the radially inner end of the lip tip and the radially inner end of the spring is 1% or more of the diameter of the outer peripheral surface of the inner ring. Since the pressure resistance (internal pressure resistance and external pressure resistance) of the seal lip is improved, the inner ring increases even if the internal pressure increases due to the temperature rise of the bearing or the external pressure of the bearing increases. It is possible to maintain the tightening force with respect to the outer peripheral surface, and it is possible to suppress the occurrence of fatigue.

また、リップ腰部の径方向厚さを、最小となる箇所において、内輪の外周面の直径の１％以上となるよう、リップ腰部の肉厚を適切に設定した場合、シールリップ部の耐圧性（耐内圧性、耐外圧性）がさらに向上し、軸受の温度上昇によって内部圧力が上昇した場合や、軸受の外部圧力が上昇した場合でも、内輪の外周面に対する緊迫力をさらに維持することが可能であると共に、疲労の発生をさらに抑制することが可能である。   In addition, when the thickness of the lip waist portion is appropriately set so that the radial thickness of the lip waist portion is 1% or more of the diameter of the outer peripheral surface of the inner ring at the minimum position, the pressure resistance of the seal lip portion ( (Internal pressure resistance and external pressure resistance) are further improved, and even when the internal pressure rises due to the temperature rise of the bearing or when the external pressure of the bearing rises, it is possible to further maintain the tightening force against the outer peripheral surface of the inner ring In addition, it is possible to further suppress the occurrence of fatigue.

また、リップ先端部の径方向内側端部を、内輪の外周面に対して、しめしろを持って摺接させ、当該しめしろの２倍の値が、内輪の外周面の直径の１％以上となるように設定した場合、シールリップ部の耐圧性（耐内圧性、耐外圧性）がさらに向上し、軸受の温度上昇によって内部圧力が上昇した場合や、軸受の外部圧力が上昇した場合でも、内輪の外周面に対する緊迫力をさらに維持することが可能であると共に、疲労の発生をさらに抑制することが可能である。   Also, the radially inner end of the lip tip is brought into sliding contact with the outer peripheral surface of the inner ring with an interference, and the double value of the interference is 1% or more of the diameter of the outer peripheral surface of the inner ring. The pressure resistance (internal pressure resistance, external pressure resistance) of the seal lip is further improved, and even if the internal pressure increases due to the temperature rise of the bearing or the external pressure of the bearing increases Further, it is possible to further maintain the tightening force with respect to the outer circumferential surface of the inner ring and to further suppress the occurrence of fatigue.

実施形態に係る自動調心ころ軸受の要部断面図である。It is principal part sectional drawing of the self-aligning roller bearing which concerns on embodiment. オイルシールの要部断面図である。It is principal part sectional drawing of an oil seal. 連続鋳造機のロールの要部断面図である。It is principal part sectional drawing of the roll of a continuous casting machine. 耐圧試験装置の断面図である。It is sectional drawing of a pressure | voltage resistant test apparatus. 球面座付き複列円錐ころ軸受の要部断面図である。It is principal part sectional drawing of a double row tapered roller bearing with a spherical seat. 球面座付き円筒ころ軸受の要部断面図である。It is principal part sectional drawing of a cylindrical roller bearing with a spherical seat. 球面座付き複列円錐ころ軸受の要部断面図である。It is principal part sectional drawing of a double row tapered roller bearing with a spherical seat. 球面座付き円筒ころ軸受の要部断面図である。It is principal part sectional drawing of a cylindrical roller bearing with a spherical seat.

以下、本発明の一実施形態に係る転がり軸受用密封装置について、図面に基づいて詳細に説明する。   Hereinafter, a rolling bearing sealing device according to an embodiment of the present invention will be described in detail with reference to the drawings.

本実施形態に係る自動調心ころ軸受１０は、図１に示すように、内周面に球面状の外輪軌道溝１１ａが形成された外輪１１と、外周面に球面状の内輪軌道溝１２ａが二列形成された内輪１２と、保持器１３によって回動自在に保持され、外輪軌道溝１１ａと内輪軌道溝１２ａとの間に二列に整列して転動自在に配設された複数の転動体である樽形のころ１４と、外輪１１の内周面と内輪１２の外周面との間に存在する空間の軸方向両端部開口を塞ぐようにそれぞれ配設され、軸受内部を密封する一対の転がり軸受用密封装置としてのオイルシール２０と、を備える。   As shown in FIG. 1, the self-aligning roller bearing 10 according to the present embodiment includes an outer ring 11 having a spherical outer ring raceway groove 11a formed on the inner peripheral surface, and a spherical inner ring raceway groove 12a formed on the outer peripheral surface. A plurality of rolling wheels are rotatably supported by the inner ring 12 formed in two rows and the cage 13 and are arranged in two rows between the outer ring raceway groove 11a and the inner ring raceway groove 12a. A pair of barrel-shaped rollers 14 that are moving bodies and a pair of seals that seals the inside of the bearing, respectively, so as to close the openings in both axial ends of the space existing between the inner peripheral surface of the outer ring 11 and the outer peripheral surface of the inner ring 12. And an oil seal 20 as a rolling bearing sealing device.

外輪１１の軸方向中間部には、外周面から内周面に貫通し、軸受空間に潤滑剤を供給可能且つ空気抜きが可能な貫通孔１５が形成されている。なお、貫通孔１５に雌ねじ部（不図示）を設け、当該雌ねじ部に軸受空間を密封するための栓を螺合してもよい。また、軸受空間内に潤滑剤が封入される構成である限り、貫通孔１５を設けなくても構わない。ここで、軸受空間内に封入される潤滑剤は、粘度が４０℃で３００ｍｍ２／ｓ〜５００ｍｍ２／ｓである高粘度の潤滑油、又は動粘度が４０℃で７０ｍｍ２／ｓ〜５００ｍｍ２／ｓである基油とウレア化合物を増ちょう剤とする耐熱性及び耐摩耗性に優れたグリースが用いられる。 A through hole 15 that penetrates from the outer peripheral surface to the inner peripheral surface, can supply the lubricant to the bearing space, and can vent the air is formed in the axially intermediate portion of the outer ring 11. In addition, a female screw part (not shown) may be provided in the through-hole 15 and a plug for sealing the bearing space may be screwed into the female screw part. Further, as long as the lubricant is sealed in the bearing space, the through hole 15 may not be provided. Here, a lubricant sealed in the bearing space, 70mm 2 / s~500mm 2 Viscosity high viscosity lubricating oil which is 300mm 2 / s~500mm 2 / s at 40 ° C., or kinematic viscosity at 40 ° C. Grease having excellent heat resistance and wear resistance using a base oil and urea compound as / s as a thickener.

図２も参照し、オイルシール２０は、全体として略円環形状に形成されており、外輪１１の内周面に固定される芯金３０と、芯金３０の軸方向外側面に固定され、ゴム等の弾性材料から形成された弾性体４０と、を有する。   Referring also to FIG. 2, the oil seal 20 is formed in a substantially annular shape as a whole, and is fixed to the core 30 fixed to the inner peripheral surface of the outer ring 11 and the axially outer surface of the core 30. And an elastic body 40 made of an elastic material such as rubber.

芯金３０は、外輪１１の内周面の軸方向外側端部に形成された溝部１１ｂに圧入されて固定され、径方向内側に延びる断面略Ｌ字形状（以降、断面とは周方向断面を意味する。）の第一芯金３２と、第一芯金３２の径方向内側端部３２ａよりも軸方向内側に配置され、径方向内側に延びる断面略直線形状の第二芯金３４と、に分割されている。   The core metal 30 is press-fitted and fixed in a groove 11b formed at the axially outer end of the inner peripheral surface of the outer ring 11, and has a substantially L-shaped cross section that extends radially inward (hereinafter, the cross section refers to a circumferential cross section). A first cored bar 32), a second cored bar 34 that is arranged on the inner side in the axial direction than the radially inner end 32a of the first cored bar 32 and extends inward in the radial direction, It is divided into

弾性体４０は、第一芯金３２の軸方向外側面に固定される断面略Ｌ字形状の第一延出部４１と、第二芯金３４の軸方向外側面に固定される断面略直線形状の第二延出部４２と、第一延出部４１及び第二延出部４２に連続すると共に、第一芯金３２の径方向内側端部３２ａ及び第二芯金３４の径方向外側端部３４ａを接続する接続部４３と、を有する。ここで、第一芯金３２の径方向内側端部３２ａが、第二芯金３４の径方向外側端部３４ａよりも径方向外側に位置しているので、弾性体４０の接続部４３は、軸方向内側に向かうにしたがって径方向内側に若干傾斜する断面略直線形状とされている。   The elastic body 40 includes a first extending portion 41 having a substantially L-shaped cross section that is fixed to the outer surface in the axial direction of the first metal core 32 and a substantially straight line that is fixed to the outer surface in the axial direction of the second metal core 34. The second extending portion 42 having the shape, the first extending portion 41 and the second extending portion 42 are continuous, and the radially inner end 32a of the first core metal 32 and the radially outer side of the second core metal 34 are connected. And a connection portion 43 for connecting the end portion 34a. Here, since the radially inner end portion 32a of the first core metal 32 is located radially outside the radially outer end portion 34a of the second core metal 34, the connecting portion 43 of the elastic body 40 is The cross section has a substantially linear shape that is slightly inclined radially inward as it goes inward in the axial direction.

また、弾性体４０は、第二延出部４２の径方向内側端部から連続して軸方向外側に延びると共に、第二芯金３４の径方向内側端部３４ｂに軸方向外側で固定されるリップ腰部４４ａと、リップ腰部４４ａから連続し、その径方向内側端部４４ｃが内輪１２の外周面の軸方向外側端部に形成された溝部１２ｂに対してしめしろＧを持って弾性的に摺接するリップ先端部４４ｂと、を有するシールリップ部４４を備える。ここで、しめしろＧとは、シールリップ部４４が摺動する面である内輪１２の外周面（溝部１２ｂ）の直径（外径）と、リップ先端部４４ｂの径方向内側端部４４ｃの直径（内径）と、の差を意味する。なお、シールリップ部４４を内輪１２の溝部１２ｂに摺接させて外輪１１と内輪１２との間を確実にシールする必要があることから、シールリップ部４４の外周面４４ｄにスプリング５０を装着し、そのスプリング５０の弾性力によりシールリップ部４４を内輪１２の溝部１２ｂ側へ付勢するようにしている。   The elastic body 40 continuously extends from the radially inner end portion of the second extending portion 42 to the outer side in the axial direction, and is fixed to the radially inner end portion 34 b of the second core metal 34 on the outer side in the axial direction. The lip waist portion 44a and the lip waist portion 44a are continuous from the lip waist portion 44a, and the radially inner end portion 44c thereof slides elastically with an interference G with respect to the groove portion 12b formed at the outer end surface of the inner ring 12 in the axial direction. A seal lip portion 44 having a lip tip portion 44b in contact therewith. Here, the interference G is the diameter (outer diameter) of the outer peripheral surface (groove portion 12b) of the inner ring 12 on which the seal lip portion 44 slides, and the diameter of the radially inner end portion 44c of the lip tip portion 44b. (Inner diameter) and the difference. Since the seal lip portion 44 needs to be slidably contacted with the groove portion 12b of the inner ring 12 to securely seal between the outer ring 11 and the inner ring 12, a spring 50 is attached to the outer peripheral surface 44d of the seal lip portion 44. The seal lip 44 is urged toward the groove 12b of the inner ring 12 by the elastic force of the spring 50.

さらに、弾性体４０は、第二芯金３４の径方向内側端部３４ｂに固定されると共に、シールリップ部４４よりも軸方向内側に位置するバンパーリップ部４５を有する。バンパーリップ部４５は、その径方向内側端部４５ａがリップ先端部４４ｂの径方向内側端部４４ｃよりも径方向外側に位置するように形成されており、内輪１２の溝部１２ｂとの間で非接触のシールを形成する補助リップ部として働く。   Furthermore, the elastic body 40 has a bumper lip portion 45 that is fixed to the radially inner end portion 34 b of the second core metal 34 and that is located on the axially inner side of the seal lip portion 44. The bumper lip portion 45 is formed such that its radially inner end portion 45a is positioned radially outward from the radially inner end portion 44c of the lip tip portion 44b, and is not between the groove portion 12b of the inner ring 12. Acts as an auxiliary lip that forms a seal of contact.

ここで、本実施形態のオイルシール２０においては、シールリップ部４４の耐圧性（耐内圧性、耐外圧性）を向上させ、且つ、疲労の発生を抑制するために、リップ腰部４４ａ及びリップ先端部４４ｂの径方向厚さが適切な値に設定されている。より詳細には、リップ腰部４４ａの径方向厚さは、最小となる箇所（図２中、Ｆで示している。）において、内輪１２の外周面（溝部１２ｂ）の直径（外径）の１％以上となるように設定される。また、リップ先端部４４ｂの、径方向内側端部４４ｃとスプリング５０の径方向内側端部５０ａとの間の径方向厚さＥは、内輪１２の外周面（溝部１２ｂ）の直径（外径）の１％以上となるように設定される。さらに、リップ先端部４４ｂは、内輪１２の溝部１２ｂに対するしめしろＧの２倍の値が、内輪１２の外周面（溝部１２ｂ）の直径（外径）の１％以上となるように設定される。   Here, in the oil seal 20 of the present embodiment, in order to improve the pressure resistance (internal pressure resistance, external pressure resistance) of the seal lip portion 44 and suppress the occurrence of fatigue, the lip waist portion 44a and the lip tip end. The radial thickness of the portion 44b is set to an appropriate value. More specifically, the diameter (outer diameter) of the outer peripheral surface (groove portion 12b) of the inner ring 12 is 1 at the position where the radial thickness of the lip waist portion 44a is minimized (indicated by F in FIG. 2). % Is set to be at least%. The radial thickness E between the radial inner end 44c of the lip tip 44b and the radial inner end 50a of the spring 50 is the diameter (outer diameter) of the outer peripheral surface (groove 12b) of the inner ring 12. Is set to be 1% or more. Furthermore, the lip tip 44b is set so that the double value of the interference G with respect to the groove 12b of the inner ring 12 is 1% or more of the diameter (outer diameter) of the outer peripheral surface (groove 12b) of the inner ring 12. .

以上のように構成されたオイルシール２０を備える自動調心ころ軸受１０は、例えば、連続鋳造設備等の回転速度が非常に遅い箇所（１分間に数回転）に使用され、良好なシール性能が発揮されて、封入された潤滑剤が長寿命に保たれる。より具体的には、図３に示すように、自動調心ころ軸受１０は、内輪１２がロール７０のロールネック部７０ａに外嵌し、外輪１１がハウジング７１に外嵌するように、連続鋳造機に組み込まれる。   The self-aligning roller bearing 10 including the oil seal 20 configured as described above is used, for example, at a location where the rotational speed is very slow (several revolutions per minute) such as continuous casting equipment, and has good sealing performance. Demonstrated, the encapsulated lubricant is maintained for a long life. More specifically, as shown in FIG. 3, the self-aligning roller bearing 10 is continuously cast so that the inner ring 12 is fitted on the roll neck portion 70 a of the roll 70 and the outer ring 11 is fitted on the housing 71. Built into the machine.

ハウジング７１の軸側端部（図３中、左側端部）とロールネック部７０ａの軸側端部との径方向における間には軸側チョックシール７２が配置され、ハウジング７１のロール側端部（図３中、右側端部）とロールネック部７０ａのロール側端部との径方向における間には一対のロール側チョックシール７３が配置されており、これらのチョックシール７２、７３によってハウジング７１とロールネック部７０ａとの間の空間がシールされる。   A shaft side chock seal 72 is arranged between the shaft side end portion of the housing 71 (left side end portion in FIG. 3) and the shaft side end portion of the roll neck portion 70a in the radial direction. A pair of roll side chock seals 73 is arranged between the radial direction between the right side end portion in FIG. 3 and the roll side end portion of the roll neck portion 70a. And the space between the roll neck portion 70a is sealed.

ハウジング７１の内部には、軸側端面から軸方向に向かってグリース供給孔７４が設けられ、当該グリース供給孔７４は、一対のロール側チョックシール７３の軸方向における間に形成された空間７５に接続されて、断面略Ｌ字形状とされている。また、ハウジング７１には、空間７５からハウジング７１の外周面に貫通するグリース排出孔７６が設けられている。   Inside the housing 71, a grease supply hole 74 is provided in the axial direction from the axial end surface, and the grease supply hole 74 is formed in a space 75 formed between the pair of roll side chock seals 73 in the axial direction. It is connected and has a substantially L-shaped cross section. Further, the housing 71 is provided with a grease discharge hole 76 penetrating from the space 75 to the outer peripheral surface of the housing 71.

ここで、図３中、矢印で示すように、グリースは、グリース供給孔７４を介して、空間７５に供給され、ロール７０のロールネック部７０ａ等の回転部材の潤滑に供され、その後、グリース排出孔７６を通過してハウジング７１の外部に排出される。   Here, as indicated by an arrow in FIG. 3, the grease is supplied to the space 75 through the grease supply hole 74 and is used for lubricating rotating members such as the roll neck portion 70 a of the roll 70. It passes through the discharge hole 76 and is discharged to the outside of the housing 71.

ここで、グリース供給孔７４を介して供給されるグリースは、ロール側チョックシール７３によって空間７５内に密封されることが望ましいが、ロール側チョックシール７３のシールが不完全である場合、自動調心ころ軸受１０側の空隙７７に浸入することがある。このとき、空隙７７内のグリースは、自動調心ころ軸受１０に対して外圧を付与するので、当該外圧が軸受内の内圧に比べて大きくなった場合、オイルシール２０に対して、内輪１２の外周面との間に隙間が生じる方向に力が作用する。   Here, it is desirable that the grease supplied through the grease supply hole 74 is sealed in the space 75 by the roll side chock seal 73. However, if the seal of the roll side chock seal 73 is incomplete, automatic adjustment is performed. It may enter the gap 77 on the side of the center roller bearing 10. At this time, since the grease in the gap 77 applies an external pressure to the self-aligning roller bearing 10, when the external pressure becomes larger than the internal pressure in the bearing, the grease of the inner ring 12 is against the oil seal 20. A force acts in a direction in which a gap is generated between the outer peripheral surface.

しかしながら、本実施形態のオイルシール２０によれば、上記径方向厚さＥ、Ｆ及びしめしろＧが、内輪１２の外周面の直径の１％以上となるよう、肉厚を適切に設定したので、シールリップ部４４の耐圧性（耐外圧性）が向上し、軸受外部の圧力が上昇した場合でも、内輪１２の外周面に対する緊迫力を維持することが可能であると共に、疲労の発生を抑制することが可能である。したがって、軸受外部からのグリース、水、異物等の浸入を防止することが可能である。   However, according to the oil seal 20 of the present embodiment, the thicknesses are appropriately set so that the radial thicknesses E and F and the interference G are 1% or more of the diameter of the outer peripheral surface of the inner ring 12. The pressure resistance (external pressure resistance) of the seal lip 44 is improved, and even when the pressure outside the bearing rises, it is possible to maintain the tightening force against the outer peripheral surface of the inner ring 12 and suppress the occurrence of fatigue. Is possible. Therefore, it is possible to prevent the ingress of grease, water, foreign matter, etc. from the outside of the bearing.

なお、軸受の温度上昇等によって軸受内部の圧力が上昇し、当該内圧が外圧に比べて大きくなった場合も、オイルシール２０に対して、内輪１２の外周面との間に隙間が生じる方向に力が作用する。しかしながら、上述したように、本実施形態のオイルシール２０によれば上記径方向厚さＥ、Ｆ及びしめしろＧが、内輪１２の外周面の直径の１％以上となるよう、肉厚を適切に設定したので、シールリップ部４４の耐圧性（耐内圧性）が向上し、軸受内部の圧力が上昇した場合でも、内輪１２の外周面に対する緊迫力を維持することが可能であると共に、疲労の発生を抑制することが可能である。したがって、軸受内部空間に封入された潤滑剤が軸受外部に漏洩することを防止することが可能であり、潤滑剤を長寿命に保つことが可能となる。   Even when the pressure inside the bearing rises due to the temperature rise of the bearing and the internal pressure becomes larger than the external pressure, a gap is generated between the oil seal 20 and the outer peripheral surface of the inner ring 12. Force acts. However, as described above, according to the oil seal 20 of the present embodiment, the radial thicknesses E and F and the interference G are appropriately set so that the diameter of the outer peripheral surface of the inner ring 12 is 1% or more. Therefore, the pressure resistance (internal pressure resistance) of the seal lip portion 44 is improved, and even when the pressure inside the bearing rises, it is possible to maintain the pressing force against the outer peripheral surface of the inner ring 12 and fatigue. Can be suppressed. Therefore, it is possible to prevent the lubricant enclosed in the bearing internal space from leaking to the outside of the bearing, and it is possible to maintain the lubricant with a long life.

（実施例）
ここで、軸受温度が回転等によって０℃（最低温度Ｔ０）から８０℃（最高温度Ｔ１）に上昇した場合の軸受内圧を計算する。空気の温度がＴ０＝２７３．１５［Ｋ］のときの圧力をｐ０とし、Ｔ１＝２７３．１５＋８０＝３５３．１５［Ｋ］のときの圧力をｐ１とすれば、シャルルボイルの法則よりｐ０／Ｔ０＝ｐ１／Ｔ１、すなわちｐ１／ｐ０＝Ｔ１／Ｔ０＝１．３となる。つまり、Ｔ１＝８０［℃］での圧力ｐ１はＴ０＝０［℃］のときの圧力ｐ０の１．３倍になる。ｐ０を大気圧とすると、圧力差ｐ１−ｐ０が温度Ｔ１のときの相対圧力となり、Ｐａ単位の圧力に換算すれば、ｐ１−ｐ０＝１．０１３２５×１０５×（１．３−１）＝３．０４×１０４［Ｐａ］＝３０．４［ｋＰａ］となる。したがって、軸受温度が０℃から８０℃に上昇した場合の軸受内圧は３０．４ｋＰａとなる。 (Example)
Here, the bearing internal pressure when the bearing temperature rises from 0 ° C. (minimum temperature T0) to 80 ° C. (maximum temperature T1) due to rotation or the like is calculated. Assuming that the pressure when the air temperature is T0 = 273.15 [K] is p0 and the pressure when T1 = 273.15 + 80 = 353.15 [K] is p1, p0 / T0 according to Charles Boyle's law = P1 / T1, that is, p1 / p0 = T1 / T0 = 1.3. That is, the pressure p1 at T1 = 80 [° C.] is 1.3 times the pressure p0 at T0 = 0 [° C.]. When p0 is an atmospheric pressure, the pressure difference p1-p0 is a relative pressure at the temperature T1, and when converted to a pressure in Pa, p1-p0 = 1.01325 × 10 5 × (1.3-1) = 3.04 × 10 4 [Pa] = 30.4 [kPa]. Therefore, the bearing internal pressure when the bearing temperature rises from 0 ° C. to 80 ° C. is 30.4 kPa.

このように、オイルシール２０のシールリップ部４４の耐圧性（耐内圧性）としては、軸受内圧が３０ｋＰａよりも大きい場合であっても、内輪１２の外周面に対する緊迫力が維持されることが望ましい。   As described above, the pressure resistance (internal pressure resistance) of the seal lip portion 44 of the oil seal 20 is such that even when the bearing internal pressure is larger than 30 kPa, the tension force on the outer peripheral surface of the inner ring 12 is maintained. desirable.

そこで、本実施形態のオイルシール２０のシールリップ部４４の耐圧性（耐内圧性）について、耐圧試験装置を用いて試験を行った結果を以下に示す。   Then, the result of having tested using the pressure resistance test apparatus about the pressure resistance (internal pressure resistance) of the seal lip part 44 of the oil seal 20 of this embodiment is shown below.

図４に示すように、耐圧試験装置６０は外輪相当部材１１Ａ及び内輪相当部材１２Ａを備えており、オイルシール２０は、外輪相当部材１１Ａの内周面に固定され、シールリップ部４４のリップ先端部４４ｂの径方向内側端部４４ｃは、内輪相当部材１２Ａの外周面に当接する。   As shown in FIG. 4, the pressure test device 60 includes an outer ring equivalent member 11A and an inner ring equivalent member 12A, and the oil seal 20 is fixed to the inner peripheral surface of the outer ring equivalent member 11A, and the lip tip of the seal lip portion 44 is provided. The radially inner end 44c of the portion 44b contacts the outer peripheral surface of the inner ring equivalent member 12A.

また、耐圧試験装置６０は、オイルシール２０の軸方向内側（図４中、左側）及び軸方向外側（図４中、右側）に、それぞれ内部圧力を変更可能な第一圧力室６２及び第二圧力室６４を備えている。第一圧力室６２は、軸受内部空間に相当し、その圧力が内圧Ｐ１として表される。また、第二圧力室６４は、軸受の外部に相当し、その圧力が外圧Ｐ２として表される。   In addition, the pressure test apparatus 60 includes a first pressure chamber 62 and a second pressure chamber that can change the internal pressure on the axially inner side (left side in FIG. 4) and the axially outer side (right side in FIG. 4) of the oil seal 20, respectively. A pressure chamber 64 is provided. The first pressure chamber 62 corresponds to a bearing internal space, and the pressure is expressed as an internal pressure P1. The second pressure chamber 64 corresponds to the outside of the bearing, and the pressure is expressed as an external pressure P2.

なお、本試験において、オイルシール２０は、リップ径（シールリップ部４４の径方向内側端部４４ｃの直径）がφ１８５（ｍｍ）であり、上述した径方向厚さＥ及びＦ（図２参照）が、内輪１２の外周面（溝部１２ｂ）の直径（外径）の１％以上であるものと、１％未満であるものを使用した。   In this test, the oil seal 20 has a lip diameter (diameter of the radially inner end 44c of the seal lip portion 44) of φ185 (mm), and the radial thicknesses E and F described above (see FIG. 2). However, those having a diameter (outer diameter) of 1% or more of the outer peripheral surface (groove portion 12b) of the inner ring 12 and those having a diameter of less than 1% were used.

そして、第二圧力室６４の外圧Ｐ２を大気圧に維持するとともに、第一圧力室６２の内圧Ｐ１を、シールリップ部４４及び内輪相当部材１２Ａの外周面の間からエアー漏れが発生するまで、各１０ｋＰａ毎（上昇後各３０分維持）に上昇させ、エアー漏れするまでの圧力を試験した。当該試験の結果を表１に示す。   The external pressure P2 of the second pressure chamber 64 is maintained at atmospheric pressure, and the internal pressure P1 of the first pressure chamber 62 is maintained between the seal lip portion 44 and the outer peripheral surface of the inner ring equivalent member 12A until air leakage occurs. The pressure was increased every 10 kPa (maintained for 30 minutes after the increase), and the pressure until air leaked was tested. The results of the test are shown in Table 1.

Figure 0006381232
Figure 0006381232

このように、径方向厚さＥ及びＦが共に１％未満である場合は、シールリップ部４４の耐圧性（耐内圧性）に乏しく、内圧Ｐ１が３０ｋＰａよりも大きい場合、すなわち内圧Ｐ１が４０ｋＰａである場合、エアー漏れが発生してしまう。一方、上述の実施形態のように径方向厚さＥ及びＦが共に１％以上である場合は、内圧Ｐ１が４０ｋＰａである場合でもエアー漏れが発生せず、シールリップ部４４の耐圧性（耐内圧性）が良好であることがわかる。   Thus, when both the radial thicknesses E and F are less than 1%, the pressure resistance (internal pressure resistance) of the seal lip portion 44 is poor, and the internal pressure P1 is larger than 30 kPa, that is, the internal pressure P1 is 40 kPa. If this is the case, air leakage will occur. On the other hand, when the radial thicknesses E and F are both 1% or more as in the above-described embodiment, air leakage does not occur even when the internal pressure P1 is 40 kPa, and the pressure resistance (resistance to It can be seen that the internal pressure property is good.

以上、説明したように本実施形態のオイルシール２０によれば、芯金３０は、外輪１１の内周面に固定され径方向内側に延びる第一芯金３２と、第一芯金３２の径方向内側端部３２ａよりも軸方向内側に配置され径方向内側に延びる第二芯金３４と、を有しており、弾性体４０は、第一芯金３２の径方向内側端部３２ａと第二芯金３４の径方向外側端部３４ａとを接続する接続部４３と、第二芯金３４に固定され、リップ先端部４４ｂの径方向内側端部４４ｃが内輪１２の外周面に摺接するシールリップ部４４と、を有する。したがって、軸の偏心や傾きが発生した場合であっても、弾性体４０の接続部４３が軸の偏心や傾きに追従することによって、シールリップ部４４と内輪１２の外周面との接触を維持することが可能である。また、シールリップ部４４は、第二芯金３４に固定されるので、内輪１２の外周面とのしめしろ及び緊迫力を一定に保つことができ、良好なシール性能を発揮することが可能である。
また、リップ先端部４４ｂの、径方向内側端部４４ｃとスプリング５０の径方向内側端部５０ａとの間の径方向厚さＥが、内輪１２の外周面（溝部１２ｂ）の直径（外径）の１％以上となるよう、リップ先端部４４ｂの肉厚を適切に設定したので、シールリップ部４４の耐圧性（耐内圧性、耐外圧性）が向上し、軸受の温度上昇によって内部圧力が上昇した場合や、軸受の外部圧力が上昇した場合でも、内輪１２の外周面に対する緊迫力を維持することが可能であると共に、疲労の発生を抑制することが可能である。 As described above, according to the oil seal 20 of the present embodiment, the core metal 30 is fixed to the inner peripheral surface of the outer ring 11 and extends radially inward, and the diameter of the first core metal 32. A second cored bar 34 that is disposed on the inner side in the axial direction than the inner end 32a and extends inward in the radial direction, and the elastic body 40 includes a second inner end 32a of the first cored bar 32 and a second cored bar 34a. A connecting portion 43 that connects the radially outer end 34a of the double cored bar 34 and a seal that is fixed to the second cored bar 34 and that the radially inner end 44c of the lip tip 44b slides on the outer peripheral surface of the inner ring 12. And a lip portion 44. Therefore, even if the shaft is eccentric or inclined, the contact portion 43 of the elastic body 40 follows the eccentricity or inclination of the shaft, so that the contact between the seal lip portion 44 and the outer peripheral surface of the inner ring 12 is maintained. Is possible. Further, since the seal lip portion 44 is fixed to the second cored bar 34, the interference with the outer peripheral surface of the inner ring 12 and the tightening force can be kept constant, and good sealing performance can be exhibited. is there.
Further, the radial thickness E between the radially inner end 44c of the lip tip 44b and the radially inner end 50a of the spring 50 is the diameter (outer diameter) of the outer peripheral surface (groove 12b) of the inner ring 12. Since the thickness of the lip tip portion 44b is appropriately set so as to be 1% or more, the pressure resistance (internal pressure resistance, external pressure resistance) of the seal lip portion 44 is improved, and the internal pressure is increased by the temperature rise of the bearing. Even when it rises or when the external pressure of the bearing rises, it is possible to maintain the tightening force against the outer peripheral surface of the inner ring 12 and to suppress the occurrence of fatigue.

また、リップ腰部４４ａの最小となる箇所における径方向厚さＦを、内輪１２の外周面（溝部１２ｂ）の直径（外径）の１％以上となるよう、リップ腰部４４ａの肉厚を適切に設定したので、シールリップ部４４の耐圧性（耐内圧性、耐外圧性）がさらに向上し、軸受の温度上昇によって内部圧力が上昇した場合や、軸受の外部圧力が上昇した場合でも、内輪１２の外周面に対する緊迫力をさらに維持することが可能であると共に、疲労の発生をさらに抑制することが可能である。   In addition, the thickness of the lip waist portion 44a is appropriately adjusted so that the radial thickness F at the smallest portion of the lip waist portion 44a is 1% or more of the diameter (outer diameter) of the outer peripheral surface (groove portion 12b) of the inner ring 12. Since it is set, the pressure resistance (internal pressure resistance, external pressure resistance) of the seal lip portion 44 is further improved, and even when the internal pressure increases due to the temperature rise of the bearing or when the external pressure of the bearing increases, the inner ring 12 It is possible to further maintain the tightening force with respect to the outer peripheral surface and further suppress the occurrence of fatigue.

また、リップ先端部４４ｂの径方向内側端部４４ｃは、内輪１２の外周面（溝部１２ｂ）に対して、しめしろＧを持って摺接しており、当該しめしろＧの２倍の値が、内輪１２の外周面（溝部１２ｂ）の直径（外径）の１％以上であるので、シールリップ部４４の耐圧性（耐内圧性、耐外圧性）がさらに向上し、軸受の温度上昇によって内部圧力が上昇した場合や、軸受の外部圧力が上昇した場合でも、内輪の外周面に対する緊迫力をさらに維持することが可能であると共に、疲労の発生をさらに抑制することが可能である。   In addition, the radially inner end 44c of the lip tip 44b is in sliding contact with the outer peripheral surface (groove 12b) of the inner ring 12 with an interference G, and the value twice the interference G is Since it is 1% or more of the diameter (outer diameter) of the outer peripheral surface (groove portion 12b) of the inner ring 12, the pressure resistance (internal pressure resistance, external pressure resistance) of the seal lip portion 44 is further improved, and the internal temperature increases due to the temperature rise of the bearing. Even when the pressure rises or when the external pressure of the bearing rises, it is possible to further maintain the pressing force against the outer peripheral surface of the inner ring and to further suppress the occurrence of fatigue.

また、第一芯金３２の径方向内側端部３２ａが第二芯金３４の径方向外側端部３４ａよりも径方向外側に位置し、弾性体４０の接続部４３が軸方向内側に向かうにしたがって径方向内側に傾斜する断面略直線形状であるので、軸の偏心や傾きが発生した場合、接続部４３が曲がり易く、軸の偏心や傾きに対する追従性を高めることが可能である。   Further, the radially inner end portion 32a of the first core metal 32 is positioned on the radially outer side of the radially outer end portion 34a of the second core metal 34, and the connecting portion 43 of the elastic body 40 is directed inward in the axial direction. Therefore, since the cross section is a substantially linear shape inclined inward in the radial direction, when the eccentricity or inclination of the shaft occurs, the connecting portion 43 is easily bent, and the followability to the eccentricity or inclination of the shaft can be improved.

また、弾性体４０はバンパーリップ部４５を有するので、軸の傾きや偏心が起こった場合であっても、当該バンパーリップ部４５が内輪１２の外周面と緩衝し、シールリップ部４４の異常摩耗及び変形を防止することが可能である。   Further, since the elastic body 40 has the bumper lip portion 45, even when the shaft is tilted or decentered, the bumper lip portion 45 cushions against the outer peripheral surface of the inner ring 12 and the seal lip portion 44 is abnormally worn. It is possible to prevent deformation.

なお、本発明は、前述した各実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。   In addition, this invention is not limited to each embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

例えば、オイルシール２０が適用される転がり軸受としては、上述した自動調心ころ軸受１０に限定されず、図５に示すような球面座付き複列円錐ころ軸受や、図６に示すような球面座付き円筒ころ軸受、不図示の球面座付き複列円筒ころ軸受であってもよい。図５及び図６には、球面座８０の内周面に外輪１１が配置された状態が示されている。   For example, the rolling bearing to which the oil seal 20 is applied is not limited to the self-aligning roller bearing 10 described above, but includes a double row tapered roller bearing with a spherical seat as shown in FIG. 5 and a spherical seat as shown in FIG. A cylindrical roller bearing or a double-row cylindrical roller bearing with a spherical seat (not shown) may be used. 5 and 6 show a state in which the outer ring 11 is arranged on the inner peripheral surface of the spherical seat 80. FIG.

また、本発明のオイルシール２０は、図７に示すような球面座付き複列円錐ころ軸受や、図８に示すような球面座付き円筒ころ軸受に適用しても構わない。これらの軸受では、内輪１２の外周面と外輪１１の径方向外側に配置された球面座８０の内周面との間に存在する空間の軸方向端部開口を塞ぐように、オイルシール２０が形成されており、オイルシール２０の芯金３０が、球面座８０の内周面の軸方向外側端部に形成された溝部８０ａに圧入されて固定される。   Further, the oil seal 20 of the present invention may be applied to a double row tapered roller bearing with a spherical seat as shown in FIG. 7 or a cylindrical roller bearing with a spherical seat as shown in FIG. In these bearings, the oil seal 20 is provided so as to close the axial end opening of the space existing between the outer peripheral surface of the inner ring 12 and the inner peripheral surface of the spherical seat 80 disposed radially outside the outer ring 11. The cored bar 30 of the oil seal 20 is press-fitted into a groove 80a formed at the axially outer end of the inner peripheral surface of the spherical seat 80 and fixed.

また、上述の実施形態においては、補助リップ部としてバンパーリップ部４５を設けるとしたが、外部からのダスト侵入を防止するダストリップ部としてもよい。また、補助リップ部は、必ずしも内輪１２の外周面に接触する構成に限られず、内輪１２の外周面との間でシールを形成する限り非接触であってもよい。また、補助リップ部を設けない構成としても構わない。   In the above-described embodiment, the bumper lip portion 45 is provided as the auxiliary lip portion. However, a dust lip portion that prevents dust from entering from the outside may be used. Further, the auxiliary lip portion is not necessarily limited to the configuration in contact with the outer peripheral surface of the inner ring 12, and may be non-contact as long as a seal is formed with the outer peripheral surface of the inner ring 12. Further, the auxiliary lip portion may not be provided.

１０ 自動調心ころ軸受（転がり軸受）
１１ 外輪
１１ａ 外輪軌道溝
１１ｂ 溝部
１１Ａ 外輪相当部材
１２ 内輪
１２ａ 内輪軌道溝
１２ｂ 溝部
１２Ａ 内輪相当部材
１３ 保持器
１４ ころ
１５ 貫通孔
２０ オイルシール（転がり軸受用密封装置）
３０ 芯金
３２ 第一芯金
３２ａ 径方向内側端部
３４ 第二芯金
３４ａ 径方向外側端部
３４ｂ 径方向内側端部
４０ 弾性体
４１ 第一延出部
４２ 第二延出部
４３ 接続部
４４ シールリップ部
４４ａ リップ腰部
４４ｂ リップ先端部
４４ｃ 径方向内側端部
４４ｄ 外周面
４５ バンパーリップ部（補助リップ部）
４５ａ 径方向内側端部
５０ スプリング
５０ａ 径方向内側端部
６０ 耐圧試験装置
６２ 第一圧力室
６４ 第二圧力室
７０ ロール
７０ａ ロールネック部
７１ ハウジング
７２ 軸側チョックシール
７３ ロール側チョックシール
７４ グリース供給孔
７５ 空間
７６ グリース排出孔
７７ 空隙
８０ 球面座
８０ａ 溝部
Ｅ、Ｆ 径方向厚さ
Ｇ しめしろ 10 Spherical roller bearings (rolling bearings)
11 outer ring 11a outer ring raceway groove 11b groove 11A outer ring equivalent member 12 inner ring 12a inner ring raceway groove 12b groove 12A inner ring equivalent member 13 cage 14 roller 15 through hole 20 oil seal (sealing device for rolling bearing)
30 cored bar 32 first cored bar 32a radial inner end 34 second cored bar 34a radial outer end 34b radial inner end 40 elastic body 41 first extension part 42 second extension part 43 connection part 44 Seal lip 44a Lip waist 44b Lip tip 44c Radial inner end 44d Outer peripheral surface 45 Bumper lip (auxiliary lip)
45a Radial inner end portion 50 Spring 50a Radial inner end portion 60 Pressure resistance test device 62 First pressure chamber 64 Second pressure chamber 70 Roll 70a Roll neck portion 71 Housing 72 Shaft side chock seal 73 Roll side chock seal 74 Grease supply hole 75 Space 76 Grease discharge hole 77 Air gap 80 Spherical seat 80a Groove E, F Radial thickness G Interference

Claims (2)

内輪の外周面並びに外輪若しくは外輪の径方向外側に配置された球面座の内周面との間に存在する空間の軸方向端部開口を塞ぐように、略円環形状に形成される転がり軸受用密封装置を備える転がり軸受であって、
前記転がり軸受用密封装置は、略円環形状の芯金と、前記芯金に固定される弾性体と、
を備え、
前記芯金は、前記外輪若しくは前記球面座の内周面に固定され、径方向内側に延びる第一芯金と、前記第一芯金の径方向内側端部よりも軸方向内側に配置され、径方向内側に延びる第二芯金と、に分割され、
前記弾性体は、前記第一芯金の径方向内側端部と前記第二芯金の径方向外側端部とを接続する接続部と、前記第二芯金に固定されるシールリップ部と、を有し、
前記シールリップ部は、前記第二芯金に固定されるリップ腰部と、前記リップ腰部から連続し、その径方向内側端部が前記内輪の外周面に摺接するリップ先端部と、を有し、
前記リップ先端部の外周面には、該リップ先端部を前記内輪の外周面に向けて付勢するスプリングが配置され、
前記リップ先端部の、径方向内側端部と前記スプリングの径方向内側端部との間の径方向厚さは、前記内輪の外周面の直径の１％以上であり、
前記第二芯金の内径は、前記リップ腰部の径方向厚さが最小となる箇所の外周面の径より小さく、
前記スプリングと前記第二芯金の間にある前記リップ腰部の径方向厚さは、最小となる箇所において、前記内輪の外周面の直径の１％以上であることを特徴とする転がり軸受。 Rolling bearing formed in a substantially annular shape so as to close the axial end opening of the space existing between the outer peripheral surface of the inner ring and the outer peripheral ring or the inner peripheral surface of the spherical seat disposed radially outside the outer ring. A rolling bearing provided with a sealing device for
The rolling bearing sealing device includes a substantially ring-shaped cored bar, an elastic body fixed to the cored bar,
With
The cored bar is fixed to the inner peripheral surface of the outer ring or the spherical seat, and is arranged on the inner side in the axial direction than the first cored bar extending radially inward and the radially inner end of the first cored bar, Divided into a second mandrel extending radially inward,
The elastic body includes a connecting portion that connects a radially inner end portion of the first cored bar and a radially outer end portion of the second cored bar, a seal lip portion fixed to the second cored bar, Have
The seal lip portion includes a lip waist portion fixed to the second core metal, and a lip tip portion that is continuous from the lip waist portion and whose radially inner end portion is in sliding contact with the outer peripheral surface of the inner ring,
On the outer peripheral surface of the lip tip portion, a spring that urges the lip tip portion toward the outer peripheral surface of the inner ring is disposed,
The radial thickness between the radially inner end of the lip tip and the radially inner end of the spring is 1% or more of the diameter of the outer peripheral surface of the inner ring,
Inner diameter of the second core metal is rather smaller than the diameter of the outer peripheral surface of a portion radial thickness of the lip waist is minimized,
The rolling bearing according to claim 1, wherein a radial thickness of the lip waist portion between the spring and the second metal core is 1% or more of a diameter of an outer peripheral surface of the inner ring at a minimum position . 前記リップ先端部の径方向内側端部は、前記内輪の外周面に対して、しめしろを持って摺接しており、
前記しめしろの２倍の値は、前記内輪の外周面の直径の１％以上であることを特徴とする請求項１に記載の転がり軸受。 The radially inner end of the lip tip is in sliding contact with the outer peripheral surface of the inner ring with an interference.
2 times the value of White said tightening is rolling bearing according to claim 1, characterized in that at least 1% of the diameter of the outer peripheral surface of the inner ring.
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