JP2002031148A - Rolling bearing device - Google Patents
Rolling bearing deviceInfo
- Publication number
- JP2002031148A JP2002031148A JP2000214752A JP2000214752A JP2002031148A JP 2002031148 A JP2002031148 A JP 2002031148A JP 2000214752 A JP2000214752 A JP 2000214752A JP 2000214752 A JP2000214752 A JP 2000214752A JP 2002031148 A JP2002031148 A JP 2002031148A
- Authority
- JP
- Japan
- Prior art keywords
- rolling bearing
- shaft
- axle box
- rolling
- roll
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- 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
Landscapes
- Sealing Of Bearings (AREA)
- Rolling Contact Bearings (AREA)
- Sealing With Elastic Sealing Lips (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、連続鋳造機におけ
るガイドロールやピンチロール等の回転軸を支承するた
めの軸受が軸箱に装着されてなり、高温で水蒸気にさら
されたり、スケール等の異物が飛散したりする劣悪な環
境条件下で使用されるのに好適な転がり軸受装置に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuous casting machine in which a bearing for supporting a rotating shaft such as a guide roll or a pinch roll is mounted on an axle box. TECHNICAL FIELD The present invention relates to a rolling bearing device suitable for being used under poor environmental conditions in which foreign matter is scattered.
【０００２】[0002]
【従来の技術】従来の連続鋳造機におけるガイドロール
やピンチロールの軸受構造として、開放型転がり軸受を
使用した図５に示すものがある。図５の軸受装置８０
は、ガイドロール８１の自由側軸受構造である。ガイド
ロール８１は、軸箱（ハウジング）８２に装着された転
がり軸受９０に支承されている。一方、特公平２−５７
４６１号公報には、密封型転がり軸受を使用した軸受装
置が開示されている。2. Description of the Related Art As a bearing structure of a guide roll or a pinch roll in a conventional continuous casting machine, there is one shown in FIG. 5 using an open type rolling bearing. Bearing device 80 of FIG.
Is a free side bearing structure of the guide roll 81. The guide roll 81 is supported by a rolling bearing 90 mounted on an axle box (housing) 82. On the other hand, 2-57
No. 461 discloses a bearing device using a sealed rolling bearing.
【０００３】[0003]
【発明が解決しようとする課題】連続鋳造機におけるガ
イドロールやピンチロールを支承する軸受装置は、回転
速度が非常に遅く（数ｒｐｍ）、荷重が非常に大きい
（Ｃｒ／Ｆｒ≒３：基本動定格荷重の１／３程度）とい
う、内・外輪軌道面と転動体転動面との間に潤滑油膜が
形成され難い、軸受にとって過酷な状態で使用される。A bearing device for supporting a guide roll or a pinch roll in a continuous casting machine has a very low rotation speed (several rpm) and a very large load (Cr / Fr ≒ 3: basic dynamics). (Approximately 1/3 of the rated load), which makes it difficult for a lubricating oil film to be formed between the inner and outer raceway surfaces and the rolling element rolling surface, and is used under severe conditions for bearings.
【０００４】また、軸受周辺温度は、鋳片の輻射熱によ
り高く、温度変化も大きい。したがって、ロールの伸び
縮みや軸箱内温度の変化が大きい。図６は従来の軸受装
置８０の模式図である。図６に示すように、ロール８１
が伸長した際には、軸箱８２のバレル側（図中右側）で
はロールの体積Ｖ１の部分が軸箱８２内に侵入し、軸箱
８２の軸端側（図中左側）ではロールの体積Ｖ２（Ｖ２
＜Ｖ１）の部分が軸箱８２外に退出する。また、ロール
８１が収縮した際には、軸箱８２のバレル側ではロール
の体積Ｖ３の部分が軸箱８２外に退出し、軸箱８２の軸
端側ではロールの体積Ｖ４（Ｖ４＜Ｖ３）の部分が軸箱
内に侵入する。すなわち、ロール８１の伸縮に伴って軸
箱８２内に侵入・退出するロールの体積がバレル側と軸
端側とで異なり、ロール８１伸長時には軸箱８２内に正
圧が発生し、ロール８１収縮時には軸箱８２内に負圧が
発生する。このことと、軸箱８２内の温度変化とによ
り、軸箱８２内の圧力変化は大きい。そして、軸箱８２
内の圧力が負圧、即ち軸箱８２の周辺の圧力よりも低く
なった場合、周辺の水蒸気が軸箱８２内へ吸い込まれ
る。吸い込まれた水分は、内・外輪軌道面と転動体転動
面との間の潤滑油膜形成状態を劣化させる。Further, the temperature around the bearing is high due to the radiant heat of the slab, and the temperature change is large. Therefore, the expansion and contraction of the roll and the change in the temperature inside the shaft box are large. FIG. 6 is a schematic view of a conventional bearing device 80. As shown in FIG.
Is extended, a portion of the roll volume V1 enters the shaft box 82 on the barrel side (right side in the figure) of the shaft box 82, and roll volume on the shaft end side (left side in the figure) of the shaft box 82. V2 (V2
The portion <V1) retreats outside the axle box 82. Further, when the roll 81 contracts, a portion of the roll volume V3 on the barrel side of the shaft box 82 retreats outside the shaft box 82, and the roll volume V4 on the shaft end side of the shaft box 82 (V4 <V3). Part enters the axle box. That is, the volume of the roll that enters and exits inside the shaft box 82 as the roll 81 expands and contracts differs between the barrel side and the shaft end side. When the roll 81 extends, a positive pressure is generated inside the shaft box 82 and the roll 81 contracts. At times, a negative pressure is generated in the axle box 82. Due to this and the temperature change in the axle box 82, the pressure change in the axle box 82 is large. And the axle box 82
When the internal pressure becomes lower than the negative pressure, that is, the pressure around the axle box 82, the surrounding water vapor is sucked into the axle box 82. The sucked-in moisture deteriorates a state of forming a lubricating oil film between the inner and outer raceway surfaces and the rolling element rolling surface.
【０００５】軸受が自動調心ころ軸受の場合、このよう
な状態で軸受が回転すると、図７（ａ）〜（ｃ）のよう
な経過をたどり、内輪（図示せず）及び外輪９１の軌道
面や転動体（ころ）９５転動面が大きく摩耗して、軸受
すきまが過大になり、ロールを正規の位置に維持できな
かったり、外輪９１の損傷（割れ）によってロールの回
転が不能になったりする。先ず、図７（ａ）に示す段階
では、外輪９１の軸受端面側Ｅから軸受中央側Ｃにかけ
て局部摩耗１００が生じているものの、純転がり部１０
１が外輪９１に残されている。次第に、図７（ｂ）に示
すように、応力集中によって純転がり部１０１が剥離し
ていく。そして、図７（ｃ）に示すように、剥離の拡大
及び曲げ応力１０２の発生により、縦クラック１０３が
発生して外輪９１が割れる。In the case where the bearing is a self-aligning roller bearing, when the bearing rotates in such a state, the bearing follows the course shown in FIGS. 7 (a) to 7 (c) and tracks the inner ring (not shown) and the outer ring 91. The surface and the rolling elements (rollers) 95 are greatly worn, the bearing clearance becomes excessive, the roll cannot be maintained at a regular position, or the roll cannot be rotated due to damage (crack) of the outer ring 91. Or First, at the stage shown in FIG. 7A, although the local wear 100 occurs from the bearing end surface side E of the outer ring 91 to the bearing center side C, the pure rolling portion 10 is formed.
1 is left on the outer ring 91. Gradually, as shown in FIG. 7B, the pure rolling portion 101 peels off due to stress concentration. Then, as shown in FIG. 7C, the expansion of the peeling and the generation of the bending stress 102 cause a vertical crack 103 to break the outer ring 91.
【０００６】また、潤滑油膜の形成に良好な状態を維持
するためにグリースを間欠的に供給すると、多量のグリ
ースが消費されると共に、軸箱から排出されるグリース
も多量になるため周辺が排出グリースで汚染され、メン
テナンス時の清浄が面倒になる。さらに、グリースを間
欠的に供給するシステム（給脂装置、分配器、給脂配管
等）は、設備コスト及びメンテナンスコストの増大を招
く。本発明の目的は、過酷な条件下でも長期にわたって
良好に作動する安価な転がり軸受装置を提供することに
ある。If grease is intermittently supplied in order to maintain a favorable condition for forming a lubricating oil film, a large amount of grease is consumed and a large amount of grease is discharged from the axle box. Contaminated with grease, which makes cleaning during maintenance troublesome. Further, a system for intermittently supplying grease (greasing device, distributor, greasing pipe, etc.) causes an increase in equipment cost and maintenance cost. An object of the present invention is to provide an inexpensive rolling bearing device that operates well for a long period even under severe conditions.
【０００７】[0007]
【課題を解決するための手段】本発明の前記目的は、転
がり軸受が軸箱内に装着され、前記転がり軸受に支承さ
れる軸と前記軸箱との間を密閉するシール部材が前記軸
箱に設けられた転がり軸受装置において、前記転がり軸
受の内輪、外輪及び転動体により形成される空間内に潤
滑剤含有ポリマーが充填され、前記シール部材の前記軸
に接する先端部が前記空間から離れる外向きにされ、前
記軸箱に設けられた供給路を介して前記空間に圧力３０
ｋＰａ以上の圧縮気体が供給された際に、前記シール部
材と前記軸との間から気体が排出されることを特徴とす
る転がり軸受装置によって達成される。SUMMARY OF THE INVENTION It is an object of the present invention to provide a rolling bearing, wherein a rolling bearing is mounted in an axle box, and a sealing member for sealing between the axle supported by the rolling bearing and the axle box is provided. In the rolling bearing device provided in the above, the space formed by the inner ring, the outer ring and the rolling elements of the rolling bearing is filled with a lubricant-containing polymer, and the tip of the seal member contacting the shaft is separated from the space. And a pressure of 30 psi into the space via a supply passage provided in the axle box.
The rolling bearing device is characterized in that when a compressed gas of kPa or more is supplied, the gas is discharged from between the seal member and the shaft.
【０００８】以上のような転がり軸受装置によれば、軸
箱内に圧縮気体を供給することによって軸箱内の圧力を
軸箱周辺の圧力よりも高く維持できるので、軸の温度変
化等に伴い軸が伸縮したり軸箱内の温度が変化したりし
ても、軸箱内の圧力が負圧になることはなく、周辺の水
蒸気や異物を軸箱内に吸い込むことがない。その結果、
内・外輪軌道面や転動体転動面の潤滑状態を良好に保っ
て摩耗を極めて小さく抑えることができ、摩耗に起因す
るトラブルを解消できる。また、内輪、外輪及び転動体
により形成される空間内に潤滑剤含有ポリマーを充填し
たことによって、多量にグリースが消費されることがな
くなると共に、軸箱から排出されるグリースによる周辺
の汚染がなくなり、メンテナンス時の清浄作業が著しく
簡略化される。さらに、グリースを間欠的に供給するシ
ステムが不要となるため、この転がり軸受装置は安価に
製造できる。また、グリースを間欠的に供給するシステ
ムのメンテナンスが不要となるため、ランニングコスト
を低く抑えることができる。According to the above-described rolling bearing device, the pressure in the axle box can be maintained higher than the pressure around the axle box by supplying the compressed gas into the axle box. Even if the shaft expands or contracts or the temperature inside the shaft box changes, the pressure inside the shaft box does not become negative, and the surrounding water vapor and foreign substances are not sucked into the shaft box. as a result,
The lubrication state of the inner and outer raceway surfaces and the rolling surface of the rolling element can be kept in good condition to minimize wear, and troubles caused by wear can be eliminated. Also, by filling the space formed by the inner ring, the outer ring and the rolling elements with the lubricant-containing polymer, a large amount of grease is not consumed, and peripheral contamination by grease discharged from the axle box is eliminated. In addition, cleaning work during maintenance is significantly simplified. Furthermore, since a system for intermittently supplying grease is not required, this rolling bearing device can be manufactured at low cost. Further, since maintenance of a system for intermittently supplying grease is not required, running costs can be reduced.
【０００９】本発明において、潤滑剤含有ポリマーとし
ては、ポリエチレン等の熱可塑性樹脂とグリース・潤滑
油とからなるものが挙げられる。また、ジアリルフタレ
ート、ポリウレタン、ポリノルボルネン等とグリース・
潤滑油とからなる、熱で硬化或いは架橋するもの等を使
用することもできる。潤滑剤含有ポリマーのポリエチレ
ン等の熱可塑性樹脂とグリース・潤滑油との配合は、重
量％でグリース・潤滑油を３０〜９５％にすることが好
ましい。また本発明において、転がり軸受の外輪の内周
面、内輪の外周面及び転動体の表面の少なくともいずれ
かに、固体潤滑剤の被膜を形成してもよい。こうするこ
とで、より良好な潤滑状態を保つことができる。固体潤
滑剤としては、ポリテトラフロロエチレン（ＰＴＦ
Ｅ）、ＭｏＳ2、グラファイト、Ｎ−ラウロイルＬ−リ
ジン、ｈ−ＢＮ、フッ化黒鉛等を例示できる。In the present invention, examples of the lubricant-containing polymer include those comprising a thermoplastic resin such as polyethylene and a grease / lubricating oil. In addition, diallyl phthalate, polyurethane, polynorbornene, etc.
A lubricating oil that can be cured or cross-linked by heat can also be used. The blending of the lubricant containing polymer such as polyethylene or the like with the grease / lubricating oil is preferably 30 to 95% by weight of the grease / lubricating oil. In the present invention, a solid lubricant film may be formed on at least one of the inner peripheral surface of the outer race of the rolling bearing, the outer peripheral surface of the inner race, and the surface of the rolling element. By doing so, a better lubricating state can be maintained. As a solid lubricant, polytetrafluoroethylene (PTF)
E), MoS 2 , graphite, N-lauroyl L-lysine, h-BN, graphite fluoride and the like.
【００１０】[0010]
【発明の実施の形態】以下、本発明の実施形態を図面に
基づいて詳細に説明する。なお、既に説明した部材等と
同様な構成・作用を有する部材等については、図中に同
一符号又は相当符号を付すことにより、説明を簡略化或
いは省略する。Embodiments of the present invention will be described below in detail with reference to the drawings. In addition, about the member etc. which have the same structure and effect as the member etc. already demonstrated, description is simplified or abbreviate | omitted by attaching | subjecting the same code | symbol or an equivalent code | symbol in a figure.
【００１１】図１に、本発明の実施形態に用いることが
できる自動調心ころ軸受２０を示す。外輪２１と内輪２
２との間には、複数の転動体としてのころ２５が、保持
器２３によって周方向に所定間隔を隔てて回転自在に保
持されている。内輪２２外周面、外輪２１内周面、ころ
２５表面及び保持器２３表面により形成された空間に
は、潤滑剤含有ポリマー部材２６が充填されている。潤
滑剤含有ポリマー部材２６から滲み出す極微量の潤滑油
によって、内輪２２軌道面、外輪２１軌道面、ころ２５
転動面及び保持器２３ポケット面２３ａ等が潤滑され
る。外輪２１の外周面における幅方向中央には、周方向
に連続的に延びる油溝２４が設けられている。油溝２４
内には、周方向に所定間隔を隔てて複数の油孔２４ａが
設けられている。FIG. 1 shows a self-aligning roller bearing 20 that can be used in an embodiment of the present invention. Outer ring 21 and inner ring 2
Rollers 25 as a plurality of rolling elements are rotatably held at predetermined intervals in the circumferential direction by a retainer 23 between them. The space defined by the outer peripheral surface of the inner ring 22, the inner peripheral surface of the outer ring 21, the surface of the rollers 25, and the surface of the cage 23 is filled with a lubricant-containing polymer member 26. A trace amount of lubricating oil oozing out of the lubricant-containing polymer member 26 causes the raceway surface of the inner ring 22, the raceway surface of the outer ring 21, and the rollers 25.
The rolling surface and the pocket surface 23a of the cage 23 are lubricated. An oil groove 24 extending continuously in the circumferential direction is provided at the center in the width direction on the outer peripheral surface of the outer ring 21. Oil groove 24
Inside, a plurality of oil holes 24a are provided at predetermined intervals in the circumferential direction.
【００１２】図２に、図１の自動調心ころ軸受２０を用
いた本発明の第１実施形態である転がり軸受装置１０を
示す。この転がり軸受装置１０は、連続鋳造機のガイド
ロール、ピンチロールの自由側軸受構造に適用されたも
のである。転がり軸受装置１０は、軸箱（ハウジング）
１２内にころ軸受２０を装着してなる。軸箱１２は、こ
ろ軸受２０の外輪２１外周面に隙間嵌めによって嵌め合
わされた外周部１３と、ころ軸受２０を挟む両側で外周
部１３の側方開口に取り付けられた環状の側部１４とを
有する。外周部１３には、ころ軸受２０の油溝２４，油
孔２４ａに連通するエア供給路１３ａが設けられてい
る。側部１４は、その内側面に、外周部１３の側方開口
内に嵌め合わされた筒部１４ａを備えている。筒部１４
ａ先端面と軸受２０端面との間には、ロール（軸）１１
の伸び縮みを吸収するための隙間Ｓが形成されている。
図示しないが、固定側軸受構造においては、ロール１１
の伸縮を吸収する必要がないので、筒部１４ａ先端面と
軸受２０端面との間に隙間Ｓを設けない。FIG. 2 shows a rolling bearing device 10 according to a first embodiment of the present invention using the self-aligning roller bearing 20 of FIG. This rolling bearing device 10 is applied to a free-side bearing structure of a guide roll and a pinch roll of a continuous casting machine. The rolling bearing device 10 includes a shaft box (housing).
12, a roller bearing 20 is mounted. The axle box 12 includes an outer peripheral portion 13 fitted to the outer peripheral surface of the outer ring 21 of the roller bearing 20 by a clearance fit, and an annular side portion 14 attached to a lateral opening of the outer peripheral portion 13 on both sides of the roller bearing 20. Have. The outer peripheral portion 13 is provided with an air supply passage 13 a communicating with the oil groove 24 and the oil hole 24 a of the roller bearing 20. The side part 14 has a cylindrical part 14 a fitted on the inner side surface thereof in a side opening of the outer peripheral part 13. Tube part 14
a Roll (shaft) 11 is provided between the end face and the end face of the bearing 20.
A gap S for absorbing expansion and contraction is formed.
Although not shown, in the fixed-side bearing structure, the roll 11
Since there is no need to absorb the expansion and contraction of the bearing 20, no gap S is provided between the end face of the cylindrical portion 14a and the end face of the bearing 20.
【００１３】側部１４の内周面には、その内周面とロー
ル１１外周面又は間座１７外表面との間を密閉する環状
のシール部材１５が設けられている。シール部材１５
は、側部１４の内周面に固着された断面略Ｌ字状の基部
１５ａと、基部１５ａの先端に接続されて軸箱１２の外
側に向かって延びるリップ部１５ｂとを備えている。す
なわちリップ部１５ｂは、内輪２２外周面、外輪２１内
周面、ころ２５表面及び保持器２３表面により形成され
た空間から離れる方向に延びている。リップ部１５ｂに
は、環状の付勢手段であるガータスプリング１６が外嵌
されている。こうしてリップ部１５ｂは、ガータスプリ
ング１６によって付勢されてロール１１外周面又は間座
１７外表面に密着して、外部からの異物侵入を防いでい
る。An annular seal member 15 is provided on the inner peripheral surface of the side portion 14 to seal between the inner peripheral surface and the outer peripheral surface of the roll 11 or the outer surface of the spacer 17. Seal member 15
Has a base 15a having a substantially L-shaped cross-section and fixed to the inner peripheral surface of the side portion 14, and a lip 15b connected to the tip of the base 15a and extending toward the outside of the axle box 12. That is, the lip portion 15b extends in a direction away from the space formed by the outer peripheral surface of the inner ring 22, the inner peripheral surface of the outer ring 21, the surface of the rollers 25, and the surface of the retainer 23. A garter spring 16 which is an annular urging means is externally fitted to the lip 15b. In this way, the lip portion 15b is urged by the garter spring 16 and adheres tightly to the outer peripheral surface of the roll 11 or the outer surface of the spacer 17 to prevent foreign matter from entering from outside.
【００１４】以下、本実施形態の作用を説明する。軸箱
１２の外周部１３に設けられたエア供給路１３ａに圧縮
空気Ａが供給されると、軸受外輪２１の油溝及び油孔２
４ａを経由してその圧縮空気Ａが、外輪２１軌道と潤滑
剤含有ポリマー部材２６との間の隙間を通過する。こう
して、軸箱１２内の圧力が高められ、軸箱１２内が正圧
となる。圧縮空気Ａの圧力が所定値以上のとき、図２に
拡大図示したように、シール部材１５のリップ部１５ｂ
がロール１１外周面及び間座１７外表面から浮き上が
り、そのリップ部１５ｂとロール１１外周面及び間座１
７外表面との僅かな隙間から圧縮空気Ａが外部に排出さ
れる。こうして、軸箱１２内の圧力がおおむね一定に保
たれる。また、潤滑剤含有ポリマー部材２６から滲み出
した潤滑油がリップ部１５ｂのロール１１外周面又は間
座１７外表面との摺接部に供給されるため、リップ部１
５ｂの摩耗による損傷が防止される。The operation of this embodiment will be described below. When the compressed air A is supplied to the air supply passage 13 a provided in the outer peripheral portion 13 of the axle box 12, the oil groove and the oil hole 2 of the bearing outer ring 21 are provided.
The compressed air A passes through the gap between the outer ring 21 raceway and the lubricant-containing polymer member 26 via 4a. Thus, the pressure inside the axle box 12 is increased, and the inside of the axle box 12 becomes a positive pressure. When the pressure of the compressed air A is equal to or higher than a predetermined value, as shown in an enlarged view in FIG.
Rises from the outer peripheral surface of the roll 11 and the outer surface of the spacer 17, and its lip portion 15b and the outer peripheral surface of the roll 11 and the spacer 1
Compressed air A is discharged to the outside from a slight gap with the outer surface of the outside. Thus, the pressure in the axle box 12 is kept substantially constant. Further, the lubricating oil that has oozed out of the lubricant-containing polymer member 26 is supplied to the outer peripheral surface of the roll 11 of the lip portion 15b or the sliding contact portion of the outer surface of the spacer 17 with the lip portion 15b.
5b is prevented from being damaged by abrasion.
【００１５】圧縮空気Ａの圧力が３０ｋＰａ以上のと
き、より好ましくは３０ｋＰａ以上３００ｋＰａ以下の
とき、シール部材１５のリップ部１５ｂを浮き上がらせ
ることができる。３０ｋＰａ未満の圧力ではシール部材
のリップ部１５ｂがロール１１表面及び間座１７表面か
ら十分に浮き上がらず、圧縮空気Ａを安定して排出する
ことができない。また、３０ｋＰａ未満の圧力で浮き上
がってしまうようにリップ部１５を構成したのでは、十
分なシール性を得られない。一方、３００ｋＰａを超え
るような高圧では、圧縮空気Ａがリップ部１５ｂとロー
ル１１外周面及び間座１７外表面との間から高速で大量
に排出され、騒音発生や粉塵飛散といった問題が生じ
る。また、圧縮空気Ａ消費量が多大となり、圧縮空気発
生装置の容量肥大化等を招き、好ましくない。When the pressure of the compressed air A is 30 kPa or more, more preferably, 30 kPa or more and 300 kPa or less, the lip portion 15 b of the seal member 15 can be raised. If the pressure is less than 30 kPa, the lip 15b of the sealing member does not sufficiently float from the surface of the roll 11 and the surface of the spacer 17, and the compressed air A cannot be discharged stably. Further, if the lip portion 15 is configured to be lifted at a pressure of less than 30 kPa, a sufficient sealing property cannot be obtained. On the other hand, at a high pressure exceeding 300 kPa, a large amount of the compressed air A is discharged at high speed from between the lip portion 15b and the outer peripheral surface of the roll 11 and the outer surface of the spacer 17, causing problems such as noise generation and dust scattering. Further, the consumption of the compressed air A becomes large, which leads to an increase in the capacity of the compressed air generating device, which is not preferable.
【００１６】以上のような構成の転がり軸受装置１０に
よれば、軸箱１２内に圧縮空気Ａを供給することによっ
て軸箱１２内の圧力を軸箱１２周辺の圧力よりも高く維
持できるので、ロール１１が伸縮したり軸箱１２内の温
度が変化したりしても、軸箱１２内の圧力が負圧になる
ことはない。また、圧縮空気Ａのエアパージにより、シ
ール部材１５によるシール性が向上されている。したが
って、軸箱１２周辺の水蒸気やスケール等の異物を軸箱
１２内に吸い込むことがないため、内輪２２軌道面、外
輪２１軌道面及びころ２５転動面の潤滑状態を良好に保
って摩耗を極めて小さく抑えることができ、摩耗に起因
するトラブルを解消できる。また、内輪２２、外輪２１
及びころ２５により形成される空間内に潤滑剤含有ポリ
マー部材２６を充填したことによって、多量にグリース
が消費されることがなくなると共に、軸箱１２から排出
されるグリースによる周辺の汚染がなくなり、メンテナ
ンス時の清浄作業が著しく簡略化される。さらに、グリ
ースを間欠的に供給するシステムが不要となるため、こ
の転がり軸受装置１０は安価に製造できる。また、グリ
ースを間欠的に供給するシステムのメンテナンスが不要
となるため、ランニングコストを低く抑えることができ
る。According to the rolling bearing device 10 configured as described above, the pressure in the axle box 12 can be maintained higher than the pressure around the axle box 12 by supplying the compressed air A into the axle box 12. Even if the roll 11 expands or contracts or the temperature inside the axle box 12 changes, the pressure inside the axle box 12 does not become negative. In addition, the air purge of the compressed air A improves the sealing performance of the seal member 15. Therefore, since foreign matters such as water vapor and scale around the axle box 12 are not sucked into the axle box 12, the lubrication state of the inner ring 22 raceway surface, the outer ring 21 raceway surface and the roller 25 rolling surface is kept good, and wear is reduced. It can be kept extremely small, and troubles caused by wear can be eliminated. Also, the inner ring 22 and the outer ring 21
By filling the space formed by the rollers 25 with the lubricant-containing polymer member 26, a large amount of grease is not consumed, and peripheral contamination by grease discharged from the axle box 12 is eliminated. The cleaning work at the time is greatly simplified. Furthermore, since a system for intermittently supplying grease is not required, the rolling bearing device 10 can be manufactured at low cost. Further, since maintenance of a system for intermittently supplying grease is not required, running costs can be reduced.
【００１７】なお、連続鋳造機のガイドロールやピンチ
ロールの軸箱１２は、連続鋳造材の輻射熱にさらされる
ので、通常水冷ジャケットにて冷却されている。このた
め、軸箱１２内の転がり軸受２０の最高到達温度は、正
常な使用状態では通常７０℃程度である。一方、ポリエ
チレンをベースとした通常の潤滑剤含有ポリマー部材２
６の耐熱温度は８０℃程度であるので、前記軸箱１２の
水冷ジャケットによる冷却が正常に機能していれば、通
常の潤滑剤含有ポリマー部材２６を支障なく使用でき
る。軸箱１２内の転がり軸受２０の最高到達温度が８０
℃を超えることが予想される場合には、特願２０００−
５７３９７「潤滑剤供給体」に開示されているような、
複合ポリエステルエラストマーに複合油を含有させた耐
熱性のある潤滑剤含有ポリマー部材を使用することが望
ましい。The axle box 12 of the guide roll or pinch roll of the continuous casting machine is usually cooled by a water-cooled jacket because it is exposed to the radiant heat of the continuous casting material. For this reason, the maximum attainable temperature of the rolling bearing 20 in the axle box 12 is usually about 70 ° C. in a normal use state. On the other hand, a conventional lubricant-containing polymer member 2 based on polyethylene
Since the heat-resistant temperature of No. 6 is about 80 ° C., if the cooling of the shaft box 12 by the water-cooling jacket is functioning normally, the ordinary lubricant-containing polymer member 26 can be used without any trouble. The maximum temperature of the rolling bearing 20 in the axle box 12 is 80
If the temperature is expected to exceed ℃,
57397 "Lubricant Supplier",
It is desirable to use a heat-resistant lubricant-containing polymer member in which a composite oil is contained in a composite polyester elastomer.
【００１８】図３に、球面座付き円筒ころ軸受４０を用
いた本発明の第２実施形態である転がり軸受装置３０を
示す。また図４に、外輪軌道面やころ転動面の曲率半径
が軸受の回転中心から軌道面までの距離よりも大きい単
列ころ軸受６０を用いた本発明の第３実施形態である転
がり軸受装置５０を示す。これらの実施形態は共に、連
続鋳造機のピンチロールやガイドロールの自由側に適用
されたものである。これらの実施形態では、エア供給路
３３ａ，５３ａが、軸箱３２，５２の側部３４，５４に
それぞれ設けられている。エア供給路３３ａ，５３ａを
軸箱３２，５２の側部３４，５４に設けることで、以下
のような作用効果を奏する。すなわち、分割ロールの場
合、長ロールと短ロールとを組み合せて使用されるが、
長ロール及び短ロールの中央側軸箱は、片側が完全にブ
ラインドになる。そのため、シール部材は軸箱の片側に
だけ取り付けられる。そして、シール部材が取り付けら
れる側の側部にエア供給路を設けることによって、シー
ル性が向上される。FIG. 3 shows a rolling bearing device 30 according to a second embodiment of the present invention using a cylindrical roller bearing 40 with a spherical seat. FIG. 4 shows a rolling bearing device according to a third embodiment of the present invention using a single row roller bearing 60 in which the radius of curvature of the outer ring raceway surface and the roller rolling surface is larger than the distance from the rotation center of the bearing to the raceway surface. 50 is shown. Both of these embodiments are applied to the free side of a pinch roll or guide roll of a continuous casting machine. In these embodiments, the air supply paths 33a and 53a are provided on the side portions 34 and 54 of the axle boxes 32 and 52, respectively. By providing the air supply passages 33a and 53a on the side portions 34 and 54 of the axle boxes 32 and 52, the following operation and effect can be obtained. That is, in the case of a split roll, a long roll and a short roll are used in combination,
The long and short roll central axle boxes are completely blind on one side. Therefore, the seal member is attached to only one side of the axle box. By providing the air supply path on the side where the seal member is attached, the sealing performance is improved.
【００１９】なお、本発明は、前述した実施形態に限定
されるものではなく、適宜な変形、改良等が可能であ
る。例えば、前述した実施形態においては、転がり軸受
を挟む軸箱の両側に、外向きの先端部を有するシール部
材を設けていたが、片側のみにこのようなシール部材を
設けてもよい。例えば、圧力センサ等の検知手段を用い
て軸箱内の圧力を検知して、圧縮空気の圧力を調節する
ようにしてもよい。It should be noted that the present invention is not limited to the above-described embodiment, and appropriate modifications and improvements can be made. For example, in the above-described embodiment, a seal member having an outwardly directed tip portion is provided on both sides of the shaft box sandwiching the rolling bearing, but such a seal member may be provided only on one side. For example, the pressure of the compressed air may be adjusted by detecting the pressure in the axle box using a detection unit such as a pressure sensor.
【００２０】[0020]
【発明の効果】以上説明したように、本発明によれば、
軸箱内の圧力を軸箱周辺の圧力よりも高く維持できるの
で、軸が伸縮したり軸箱内の温度が変化したりしても、
軸箱内の圧力が負圧になることはなく、周辺の水蒸気や
異物を軸箱内に吸い込むことがない。その結果、内・外
輪軌道面や転動体転動面の潤滑状態を良好に保って摩耗
を極めて小さく抑えることができ、過酷な条件下でも長
期にわたって良好に作動する。また、内輪、外輪及び転
動体により形成される空間内に潤滑剤含有ポリマーを充
填したことによって、軸箱から排出されるグリースによ
る周辺の汚染がなくなり、メンテナンス時の清浄作業が
著しく簡略化される。さらに、グリースを間欠的に供給
するシステムが不要となるため、メンテナンスコスト及
びランニングコストを低く抑えることができる。As described above, according to the present invention,
Since the pressure inside the axle box can be maintained higher than the pressure around the axle box, even if the shaft expands or contracts or the temperature inside the axle box changes,
The pressure in the axle box does not become a negative pressure, and the surrounding water vapor and foreign substances are not sucked into the axle box. As a result, the lubrication state of the inner and outer raceway surfaces and the rolling surface of the rolling element can be maintained in a good condition, and the wear can be suppressed to a very small level. In addition, since the space formed by the inner ring, the outer ring and the rolling elements is filled with the lubricant-containing polymer, peripheral contamination by grease discharged from the axle box is eliminated, and cleaning work during maintenance is greatly simplified. . Furthermore, since a system for intermittently supplying grease is not required, maintenance costs and running costs can be reduced.
【図１】本発明の第１実施形態に用いられる転がり軸受
を示す斜視図である。FIG. 1 is a perspective view showing a rolling bearing used in a first embodiment of the present invention.
【図２】本発明の第１実施形態を示す縦断面図である。FIG. 2 is a longitudinal sectional view showing the first embodiment of the present invention.
【図３】本発明の第２実施形態を示す縦断面図である。FIG. 3 is a longitudinal sectional view showing a second embodiment of the present invention.
【図４】本発明の第３実施形態を示す縦断面図である。FIG. 4 is a longitudinal sectional view showing a third embodiment of the present invention.
【図５】従来の転がり軸受装置の一例を示す図である。FIG. 5 is a view showing an example of a conventional rolling bearing device.
【図６】従来の転がり軸受装置の要部模式図である。FIG. 6 is a schematic view of a main part of a conventional rolling bearing device.
【図７】従来の転がり軸受装置における外輪が摩耗する
様子を説明する図である。FIG. 7 is a view for explaining how an outer ring in a conventional rolling bearing device is worn.
１０，３０，５０ 転がり軸受装置 １１ ロール（軸） １２，３２，５２ 軸箱 １５，３５，５５ シール部材 １５ｂ リップ部（先端部） １４，５４，６４ 外輪 ２０，４０，６０ 転がり軸受 ２６，４６，６６ 潤滑剤含有ポリマー部材（潤
滑剤含有ポリマー） １３ａ，３３ａ，５３ａ エア供給路（供給路） Ａ 圧縮空気（圧縮気体）10, 30, 50 Rolling bearing device 11 Roll (shaft) 12, 32, 52 Axle box 15, 35, 55 Seal member 15b Rip (tip) 14, 54, 64 Outer ring 20, 40, 60 Rolling bearing 26, 46 , 66 Lubricant-containing polymer member (lubricant-containing polymer) 13a, 33a, 53a Air supply path (supply path) A Compressed air (compressed gas)
Claims (1)
がり軸受に支承される軸と前記軸箱との間を密閉するシ
ール部材が前記軸箱に設けられた転がり軸受装置におい
て、 前記転がり軸受の内輪、外輪及び転動体により形成され
る空間内に潤滑剤含有ポリマーが充填され、前記シール
部材の前記軸に接する先端部が前記空間から離れる外向
きにされ、前記軸箱に設けられた供給路を介して前記空
間に圧力３０ｋＰａ以上の圧縮気体が供給された際に、
前記シール部材と前記軸との間から気体が排出されるこ
とを特徴とする転がり軸受装置。1. A rolling bearing device in which a rolling bearing is mounted in an axle box, and a seal member is provided on the axle box for sealing between a shaft supported by the rolling bearing and the axle box. The space formed by the inner ring, the outer ring and the rolling elements of the bearing is filled with a lubricant-containing polymer, and the tip of the seal member in contact with the shaft is directed outward away from the space, and provided in the shaft box. When a compressed gas having a pressure of 30 kPa or more is supplied to the space via the supply path,
A rolling bearing device wherein gas is discharged from between the seal member and the shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000214752A JP2002031148A (en) | 2000-07-14 | 2000-07-14 | Rolling bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000214752A JP2002031148A (en) | 2000-07-14 | 2000-07-14 | Rolling bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002031148A true JP2002031148A (en) | 2002-01-31 |
| JP2002031148A5 JP2002031148A5 (en) | 2005-01-06 |
Family
ID=18710273
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000214752A Pending JP2002031148A (en) | 2000-07-14 | 2000-07-14 | Rolling bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002031148A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006080127A1 (en) * | 2005-01-25 | 2006-08-03 | Ntn Corporation | Helical gear support structure, speed increaser for wind power generation plant, and vertical shaft support structure |
| JP2009250279A (en) * | 2008-04-02 | 2009-10-29 | Sumitomo Heavy Ind Ltd | Reduction device |
| US7918649B2 (en) | 2003-11-18 | 2011-04-05 | Ntn Corporation | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
| JP2014023002A (en) * | 2012-07-19 | 2014-02-03 | Shun Hosaka | Sensor device and manufacturing method therefor |
| KR101565290B1 (en) * | 2010-03-26 | 2015-11-04 | 지멘스 브이에이아이 메탈스 테크놀로지스 게엠베하 | Bearing arrangement and rotary inlet for a cooled roller |
| WO2021218922A1 (en) * | 2020-04-26 | 2021-11-04 | 福建南方路面机械股份有限公司 | Rotary sealing structure and spiral sand-water separator |
-
2000
- 2000-07-14 JP JP2000214752A patent/JP2002031148A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7918649B2 (en) | 2003-11-18 | 2011-04-05 | Ntn Corporation | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
| EP1705392B2 (en) † | 2003-11-18 | 2016-08-31 | NTN Corporation | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
| WO2006080127A1 (en) * | 2005-01-25 | 2006-08-03 | Ntn Corporation | Helical gear support structure, speed increaser for wind power generation plant, and vertical shaft support structure |
| JP2009250279A (en) * | 2008-04-02 | 2009-10-29 | Sumitomo Heavy Ind Ltd | Reduction device |
| KR101565290B1 (en) * | 2010-03-26 | 2015-11-04 | 지멘스 브이에이아이 메탈스 테크놀로지스 게엠베하 | Bearing arrangement and rotary inlet for a cooled roller |
| JP2014023002A (en) * | 2012-07-19 | 2014-02-03 | Shun Hosaka | Sensor device and manufacturing method therefor |
| WO2021218922A1 (en) * | 2020-04-26 | 2021-11-04 | 福建南方路面机械股份有限公司 | Rotary sealing structure and spiral sand-water separator |
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