JP6185306B2 - Cylindrical roller bearing with aligning ring - Google Patents

Cylindrical roller bearing with aligning ring Download PDF

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JP6185306B2
JP6185306B2 JP2013138992A JP2013138992A JP6185306B2 JP 6185306 B2 JP6185306 B2 JP 6185306B2 JP 2013138992 A JP2013138992 A JP 2013138992A JP 2013138992 A JP2013138992 A JP 2013138992A JP 6185306 B2 JP6185306 B2 JP 6185306B2
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ring
aligning
bearing
cylindrical roller
axial
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JP2015010704A (en
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省吾 望月
省吾 望月
塩川　太助
太助 塩川
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NSK Ltd
Nippon Steel Nisshin Co Ltd
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Nippon Steel Nisshin Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—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
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row of rollers

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

Description

本発明は、調心輪付き円筒ころ軸受に関し、より詳細には、連続鋳造機，ブロワー，テーブルローラーに適用可能な調心輪付き円筒ころ軸受に関する。   The present invention relates to a cylindrical roller bearing with a centering ring, and more particularly to a cylindrical roller bearing with a centering ring applicable to a continuous casting machine, a blower, and a table roller.

製鉄所において、精練を終了した鋼は鋳造プロセスに送られる。溶鋼から直接鋼片をつくる連続鋳造機においてスラブ、ブルーム、ビレットなどが鋳造されることが多い。連続鋳造設備の概略は次のようなものである。まず、取鍋からタンディッシュに溶鋼が注がれ、最上部から鋳型に注がれる。そして鋳片表面には冷却水がスプレーされており、表層部が次第に凝固しながら鋳型の下方に向かって連続的に配置した複数のガイドロールによって後方に順次送り出されてゆく。その後、切断装置で所定の長さに切断され所定の製品サイズとなり次工程に搬送される。   At the steelworks, the finished steel is sent to the casting process. Slabs, blooms, billets, etc. are often cast in a continuous casting machine that directly produces billets from molten steel. The outline of the continuous casting equipment is as follows. First, molten steel is poured from the ladle into the tundish, and then poured into the mold from the top. Cooling water is sprayed on the surface of the slab, and the surface layer portion is sequentially fed backward by a plurality of guide rolls arranged continuously toward the lower side of the mold while solidifying gradually. After that, it is cut into a predetermined length by a cutting device to be a predetermined product size and conveyed to the next process.

上記のような連続鋳造設備において用いられるロールは、鋳片から過大なラジアル荷重を受けて撓むので、かかるロールの端部を支持する軸受装置としては、調心性を有する転がり軸受が求められる。   Since the roll used in the continuous casting equipment as described above receives an excessive radial load from the slab and bends, a rolling bearing having alignment is required as a bearing device for supporting the end of the roll.

また、熱い鋳片からロールが加熱されることに起因して生じるロールの熱膨張への対応ならびにロールの軸方向の位置決めのため、ロールの一端を保持する軸受装置は固定状態（固定側）として用いるようにし、ロールの他端を支持する軸受装置は、ロールと外輪との軸線方向の相対変位を許容すべく、いわゆる自由状態（自由側）として用いる構造が一般的である。この自由側の軸受装置には、調心輪付き円筒ころ軸受が用いられることが知られている（例えば、特許文献１参照。）   Also, the bearing device that holds one end of the roll is in a fixed state (fixed side) to cope with the thermal expansion of the roll caused by heating the roll from the hot slab and to position the roll in the axial direction. The bearing device that supports the other end of the roll is generally used in a so-called free state (free side) so as to allow relative displacement in the axial direction between the roll and the outer ring. It is known that a cylindrical roller bearing with a centering ring is used for this free-side bearing device (see, for example, Patent Document 1).

図６は、調心輪付き円筒ころ軸受１００が組み込まれた軸受装置１５０を示している。この軸受装置１５０に使用される調心輪付き円筒ころ軸受１００は、外周面に内輪軌道面１１１を有する内輪１１０と、内周面に外輪軌道面１２１を有し、外周面１２２が球面形状を有する外輪１２０と、内輪軌道面１１１と外輪軌道面１２１との間に転動自在に配置される複数の円筒ころ１３０と、外輪１２０の外周面１２２に揺動可能に嵌合する球面形状の内周面１４１を有する調心輪１４０と、を備える。   FIG. 6 shows a bearing device 150 in which a cylindrical roller bearing 100 with a centering ring is incorporated. A cylindrical roller bearing 100 with an aligning ring used in this bearing device 150 has an inner ring 110 having an inner ring raceway surface 111 on an outer peripheral surface, an outer ring raceway surface 121 on an inner peripheral surface, and the outer peripheral surface 122 has a spherical shape. An outer ring 120 having an inner ring, a plurality of cylindrical rollers 130 which are rotatably arranged between the inner ring raceway surface 111 and the outer ring raceway surface 121, and a spherical inner shape fitted to the outer peripheral surface 122 of the outer ring 120 so as to be swingable. And a centering ring 140 having a peripheral surface 141.

内輪１１０は、回転軸１５１に嵌合し、軸方向両側に位置する内輪間座１５２、１５３を介して図示しないナットや内側押え蓋によって軸方向に位置決めされている。また、調心輪１４０は、軸箱（ハウジング）１６１に嵌合し、軸箱１６１に外側押え蓋１６２をボルト締結することで軸方向に位置決めされている。また、内輪間座１５２と外側押え蓋１６２との間、及び内輪間座１５３と軸箱１６１との間は、それぞれ封止部材１７１、１７２によって密封されている。   The inner ring 110 is fitted to the rotary shaft 151 and is positioned in the axial direction by nuts and inner presser lids (not shown) via inner ring spacers 152 and 153 located on both sides in the axial direction. The aligning ring 140 is positioned in the axial direction by fitting into the axle box (housing) 161 and fastening the outer pressing lid 162 to the axle box 161 with a bolt. Further, the space between the inner ring spacer 152 and the outer presser lid 162 and the space between the inner ring spacer 153 and the axle box 161 are sealed by sealing members 171 and 172, respectively.

特開２００９−００１９２１号公報JP 2009-001921 A

ところで、図６に示すような軸受装置１５０に使用される調心輪付き円筒ころ軸受１００において、基本動定格荷重及び基本静定格荷重を向上するためには、軸受周囲部品を変更して、軸受サイズを大きくするための空間をより広く確保するか、円筒ころの長さを伸ばすことが考えられる。しかしながら、軸受周囲部品を変更することは、軸受装置全体のコストアップにつながり、また、円筒ころの長さを伸ばしていくと外輪のつば部の肉厚が薄くなり、つば部の強度の問題が発生する。   By the way, in the cylindrical roller bearing 100 with the aligning ring used in the bearing device 150 as shown in FIG. 6, in order to improve the basic dynamic load rating and the basic static load rating, the bearing peripheral parts are changed and the bearing is changed. It is conceivable to secure a wider space for increasing the size or to increase the length of the cylindrical roller. However, changing the bearing peripheral parts leads to an increase in the cost of the entire bearing device, and when the length of the cylindrical roller is increased, the thickness of the collar portion of the outer ring is reduced, which causes a problem of the strength of the collar portion. Occur.

本発明は、上述した課題に鑑みてなされたものであり、その目的は、外輪の強度を確保しつつ、基本動定格荷重及び基本静定格荷重の向上が図れ、且つ、軸受が組み込まれる装置のコストアップを抑制することができる調心輪付き円筒ころ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 an object of the present invention is to improve the basic dynamic load rating and the basic static load rating while securing the strength of the outer ring, and to provide a device in which a bearing is incorporated. An object of the present invention is to provide a cylindrical roller bearing with a centering ring capable of suppressing an increase in cost.

本発明の上記目的は、以下の構成によって達成される。
（１） 外周面に内輪軌道面を有する内輪と、
内周面に外輪軌道面を有し、外周面が球面形状を有する外輪と、
前記内輪軌道面と前記外輪軌道面との間に転動自在に配置される複数の円筒ころと、
前記外輪の外周面に揺動可能に嵌合する球面形状の内周面を有する調心輪と
を備えた調心輪付き転がり軸受において、
前記外輪は、軸方向において対称形状を有し、その軸方向中心が前記内輪及び前記調心輪の軸方向中心に対してオフセットして配置され、
前記調心輪は、軸方向において非対称形状に形成されており、
前記外輪の軸方向幅は、前記調心輪と前記内輪の少なくとも一方の軸方向幅より長い
ことを特徴とする調心輪付き円筒ころ軸受。 The above object of the present invention is achieved by the following configurations.
(1) an inner ring having an inner ring raceway surface on the outer peripheral surface;
An outer ring having an outer ring raceway surface on the inner circumferential surface and an outer circumferential surface having a spherical shape;
A plurality of cylindrical rollers arranged to roll between the inner ring raceway surface and the outer ring raceway surface;
In a rolling bearing with a centering ring provided with a centering ring having a spherical inner peripheral surface fitted so as to be swingable to the outer peripheral surface of the outer ring,
The outer ring has a symmetrical shape in the axial direction, and its axial center is offset with respect to the axial center of the inner ring and the aligning ring,
The aligning ring is formed in an asymmetric shape in the axial direction,
An axial width of the outer ring is longer than an axial width of at least one of the aligning ring and the inner ring.

本発明の調心輪付き円筒ころ軸受によれば、外輪は、軸方向において対称形状を有し、その軸方向中心が内輪及び調心輪の軸方向中心に対してオフセットして配置され、調心輪は、軸方向において非対称形状に形成されており、外輪の軸方向幅は、調心輪と内輪の少なくとも一方の軸方向幅より長く設定されている。これにより、外輪のつば部の強度を確保しつつ、円筒ころの長さを長くすることができ、基本動定格荷重及び基本静定格荷重を増加させることができる。また、調心輪及び内輪の幅を変更しないことで、軸受周囲部品を改良する必要がなく、該軸受が組み込まれる装置のコストアップを抑制することができる。 According to the cylindrical roller bearing with the aligning ring of the present invention, the outer ring has a symmetrical shape in the axial direction, and its axial center is arranged offset with respect to the axial center of the inner ring and aligning ring. The core ring is formed in an asymmetric shape in the axial direction, and the axial width of the outer ring is set longer than the axial width of at least one of the aligning ring and the inner ring. Accordingly, the length of the cylindrical roller can be increased while securing the strength of the collar portion of the outer ring, and the basic dynamic load rating and the basic static load rating can be increased. Further, by not changing the widths of the aligning ring and the inner ring, there is no need to improve the bearing peripheral parts, and the cost increase of the device in which the bearing is incorporated can be suppressed.

（ａ）は、本発明の第１実施形態に係る調心輪付き円筒ころ軸受が組み込まれた軸受装置を示す断面図であり、（ｂ）は、（ａ）の調心輪付き円筒ころ軸受の断面図である。(A) is sectional drawing which shows the bearing apparatus with which the cylindrical roller bearing with the aligning ring which concerns on 1st Embodiment of this invention was integrated, (b) is the cylindrical roller bearing with the aligning ring of (a). FIG. （ａ）は、本発明の第２実施形態に係る調心輪付き円筒ころ軸受が組み込まれた軸受装置を示す断面図であり、（ｂ）は、（ａ）の調心輪付き円筒ころ軸受の断面図である。(A) is sectional drawing which shows the bearing apparatus with which the cylindrical roller bearing with the aligning ring which concerns on 2nd Embodiment of this invention was integrated, (b) is the cylindrical roller bearing with the aligning ring of (a). FIG. （ａ）は、本発明の第３実施形態に係る調心輪付き円筒ころ軸受が組み込まれた軸受装置を示す断面図であり、（ｂ）は、（ａ）の調心輪付き円筒ころ軸受の断面図である。(A) is sectional drawing which shows the bearing apparatus with which the cylindrical roller bearing with the aligning ring which concerns on 3rd Embodiment of this invention was integrated, (b) is the cylindrical roller bearing with the aligning ring of (a). FIG. （ａ）は、本発明の第４実施形態に係る調心輪付き円筒ころ軸受が組み込まれた軸受装置を示す断面図であり、（ｂ）は、（ａ）の調心輪付き円筒ころ軸受の断面図である。(A) is sectional drawing which shows the bearing apparatus with which the cylindrical roller bearing with the aligning ring which concerns on 4th Embodiment of this invention was integrated, (b) is the cylindrical roller bearing with the aligning ring of (a). FIG. （ａ）は、本発明の第１変形例に係る調心輪付き円筒ころ軸受が組み込まれた軸受装置を示す断面図であり、（ｂ）は、本発明の第２変形例に係る調心輪付き円筒ころ軸受が組み込まれた軸受装置を示す断面図である。(A) is sectional drawing which shows the bearing apparatus incorporating the cylindrical roller bearing with the aligning ring which concerns on the 1st modification of this invention, (b) is the alignment which concerns on the 2nd modification of this invention. It is sectional drawing which shows the bearing apparatus with which the cylindrical roller bearing with a ring was integrated. （ａ）は、従来の調心輪付き円筒ころ軸受が組み込まれた軸受装置を示す断面図であり、（ｂ）は、（ａ）の調心輪付き円筒ころ軸受の断面図である。(A) is sectional drawing which shows the bearing apparatus in which the conventional cylindrical roller bearing with a centering ring was integrated, (b) is sectional drawing of the cylindrical roller bearing with a centering ring of (a).

以下、本発明の各実施形態に係る調心輪付き円筒ころ軸受について、該軸受が組み込まれる軸受装置とともに、図面を参照しながら説明する。   Hereinafter, a cylindrical roller bearing with a centering ring according to each embodiment of the present invention will be described with reference to the drawings together with a bearing device in which the bearing is incorporated.

（第１実施形態）
図１に示すように、第１実施形態の調心輪付き円筒ころ軸受１は、外周面に内輪軌道面１１を有する内輪１０と、内周面に外輪軌道面２１及びその軸方向両側のつば部２３を有し、外周面２２が球面形状を有する外輪２０と、内輪軌道面１１と外輪軌道面２１との間に転動自在に総ころ形式で配置される複数の円筒ころ３０と、外輪２０の外周面２２に揺動可能に嵌合する球面形状の内周面４１を有する調心輪４０と、を備える。 (First embodiment)
As shown in FIG. 1, a cylindrical roller bearing 1 with a centering ring according to the first embodiment includes an inner ring 10 having an inner ring raceway surface 11 on an outer peripheral surface, an outer ring raceway surface 21 on an inner peripheral surface, and flanges on both axial sides thereof. An outer ring 20 having a portion 23 and an outer peripheral surface 22 having a spherical shape, a plurality of cylindrical rollers 30 that are arranged between the inner ring raceway surface 11 and the outer ring raceway surface 21 so as to roll freely, and an outer ring And an aligning ring 40 having a spherical inner peripheral surface 41 which is fitted to the outer peripheral surface 22 of 20 in a swingable manner.

内輪１０は、回転軸５１に嵌合し、軸方向両側に位置する内輪間座５２、５３を介して図示しないナットや内側押え蓋によって軸方向に位置決めされている。また、調心輪４０は、軸箱（ハウジング）６１に嵌合し、軸箱６１に外側押え蓋６２をボルト締結することで軸方向に位置決めされている。また、内輪間座５２と外側押え蓋６２との間、及び内輪間座５３と軸箱６１との間は、それぞれ封止部材７１、７２によって密封されている。   The inner ring 10 is fitted to the rotary shaft 51 and is positioned in the axial direction by nuts and inner pressing lids (not shown) via inner ring spacers 52 and 53 located on both sides in the axial direction. The aligning ring 40 is positioned in the axial direction by fitting into a shaft box (housing) 61 and fastening the outer pressing cover 62 to the shaft box 61 with bolts. Further, between the inner ring spacer 52 and the outer presser lid 62 and between the inner ring spacer 53 and the axle box 61 are sealed by sealing members 71 and 72, respectively.

このように構成された調心輪付き円筒ころ軸受１は、外輪２０の球面形状の外周面１０２ｂと、調心輪１０４の球面形状の内周面１０４ａ同士を滑らせることで、調心機能を備えた構成となり、過大荷重を受けながら軸のたわみに対応することができる。   The cylindrical roller bearing 1 with the aligning ring configured as described above has the aligning function by sliding the spherical outer peripheral surface 102 b of the outer ring 20 and the spherical inner peripheral surface 104 a of the aligning ring 104. It becomes the composition which is provided, and can cope with the deflection of the shaft while receiving an excessive load.

また、本実施形態では、外輪２０の軸方向幅は、内輪１０及び調心輪４０の軸方向幅より長く設定されており、外輪２０の両端部は、内輪１０及び調心輪４０の軸方向両端面よりも軸方向外側に突出している。また、これに応じて、図６に示す従来の軸受１００よりも、円筒ころ３０の軸方向長さが長く設定されており、外輪２０のつば部２３の強度を確保しつつ、基本動定格荷重及び基本静定格荷重を増加させることができる。また、内輪１０及び調心輪４０の軸方向幅を変更しないことで、軸受周囲部品を改良する必要がなく、該軸受１が組み込まれる軸受装置５０のコストアップを抑制することができる。   In the present embodiment, the axial width of the outer ring 20 is set longer than the axial width of the inner ring 10 and the aligning ring 40, and both end portions of the outer ring 20 are in the axial direction of the inner ring 10 and the aligning ring 40. It protrudes outward in the axial direction from both end faces. Accordingly, the axial length of the cylindrical roller 30 is set longer than that of the conventional bearing 100 shown in FIG. 6, and the basic dynamic load rating is ensured while ensuring the strength of the flange portion 23 of the outer ring 20. And the basic static load rating can be increased. Further, since the axial widths of the inner ring 10 and the aligning ring 40 are not changed, there is no need to improve bearing peripheral parts, and the cost increase of the bearing device 50 in which the bearing 1 is incorporated can be suppressed.

（第２実施形態）
図２は、本発明の第２実施形態に係る調心輪付き円筒ころ軸受１ａ、及び該軸受１ａが組み込まれた軸受装置５０ａを示す。この実施形態では、内輪１０は、内輪軌道面１１の軸方向一端部につば部１２を有し、また、内輪１０の軸方向他端部には、つば部１６をなすつば輪１５が当接して配置されている。したがって、本実施形態では、外輪２０のつば部２３と、内輪１０及びつば輪１５のつば部１２、１６により、軸方向荷重を受けることができる。
なお、その他の構成及び作用については、第１実施形態のものと同様である。 (Second Embodiment)
FIG. 2 shows a cylindrical roller bearing 1a with a centering ring according to a second embodiment of the present invention, and a bearing device 50a incorporating the bearing 1a. In this embodiment, the inner ring 10 has a flange portion 12 at one axial end portion of the inner ring raceway surface 11, and a flange ring 15 that forms a flange portion 16 abuts on the other axial end portion of the inner ring 10. Are arranged. Therefore, in the present embodiment, the flange portion 23 of the outer ring 20 and the flange portions 12 and 16 of the inner ring 10 and the collar ring 15 can receive an axial load.
Other configurations and operations are the same as those in the first embodiment.

（第３実施形態）
図３は、本発明の第３実施形態に係る調心輪付き円筒ころ軸受１ｂ、及び該軸受１ｂが組み込まれた軸受装置５０ｂを示す。この実施形態の軸受装置５０ｂでは、軸方向一端側の封止部材７２が２つ配置されているため、外輪２０は、軸方向一端側において、内輪１０及び調心輪４０の軸方向端面から延出するスペースを確保することができない。このため、外輪２０は、軸方向一端側において、内輪１０及び調心輪４０の軸方向端面と略面一に形成される一方、軸方向他端側において、内輪１０及び調心輪４０の軸方向端面から突出することで、外輪２０の軸方向幅は、内輪１０及び調心輪４０の軸方向幅より長く設定されている。
このため、円筒ころ３０及び外輪２０の軸方向中心Ｘ１は、内輪１０及び調心輪４０の軸方向中心Ｘ２に対して軸方向他端側にオフセットしている。また、本実施形態では、軸方向に対称形状を有する外輪２０がオフセットするため、調心輪４０は、第１及び第２実施形態では、軸方向において対称形状に形成されているが、本実施形態では、外輪２０の外周面２２に合わせて、軸方向において非対称形状に形成されている。 (Third embodiment)
FIG. 3 shows a cylindrical roller bearing 1b with an aligning ring according to a third embodiment of the present invention, and a bearing device 50b incorporating the bearing 1b. In the bearing device 50b of this embodiment, since the two sealing members 72 on one end side in the axial direction are arranged, the outer ring 20 extends from the end faces in the axial direction of the inner ring 10 and the aligning ring 40 on one end side in the axial direction. It is not possible to secure the space to be put out. For this reason, the outer ring 20 is formed substantially flush with the axial end surfaces of the inner ring 10 and the aligning ring 40 on one end side in the axial direction, and the shafts of the inner ring 10 and the aligning ring 40 on the other end side in the axial direction. By projecting from the direction end face, the axial width of the outer ring 20 is set to be longer than the axial widths of the inner ring 10 and the aligning ring 40.
For this reason, the axial center X1 of the cylindrical roller 30 and the outer ring 20 is offset to the other axial end side with respect to the axial center X2 of the inner ring 10 and the aligning ring 40. In this embodiment, since the outer ring 20 having a symmetrical shape in the axial direction is offset, the aligning ring 40 is formed in a symmetrical shape in the axial direction in the first and second embodiments. In the form, it is formed in an asymmetric shape in the axial direction in accordance with the outer peripheral surface 22 of the outer ring 20.

したがって、このような構成であっても、図６に示す従来の軸受１００よりも、円筒ころ３０の軸方向長さが長く設定され、外輪２０のつば部２３の強度を確保しつつ、基本動定格荷重及び基本静定格荷重を増加させることができる。また、内輪１０及び調心輪４０の軸方向幅を変更しないことで、軸受周囲部品を改良する必要がなく、該軸受が組み込まれる軸受装置５０ｂのコストアップを抑制することができる。
なお、その他の構成及び作用については、第１実施形態のものと同様である。 Therefore, even in such a configuration, the axial length of the cylindrical roller 30 is set to be longer than that of the conventional bearing 100 shown in FIG. 6, and the basic motion is ensured while ensuring the strength of the flange portion 23 of the outer ring 20. The rated load and basic static load rating can be increased. Further, by not changing the axial widths of the inner ring 10 and the aligning ring 40, it is not necessary to improve the bearing peripheral parts, and the cost increase of the bearing device 50b in which the bearing is incorporated can be suppressed.
Other configurations and operations are the same as those in the first embodiment.

（第４実施形態）
図４は、本発明の第４実施形態に係る調心輪付き円筒ころ軸受１ｃ、及び該軸受１ｃが組み込まれた軸受装置５０ｃを示す。この実施形態では、第２実施形態と同様に、内輪１０は、内輪軌道面１１の軸方向一端部につば部１２を有し、また、内輪１０の軸方向他端部には、つば部１６をなすつば輪１５が当接して配置されている。また、第３実施形態と同様に、外輪２０は、軸方向他端側のみにおいて、内輪１０及び調心輪４０の軸方向端面から突出することで、外輪２０の軸方向幅は、内輪１０及び調心輪４０の軸方向幅より長く設定されている。これにより、本実施形態では、第２及び第３実施形態と同様の効果を奏することができる。
なお、その他の構成及び作用についても、第１実施形態のものと同様である。 (Fourth embodiment)
FIG. 4 shows a cylindrical roller bearing 1c with a centering ring according to a fourth embodiment of the present invention, and a bearing device 50c incorporating the bearing 1c. In this embodiment, similarly to the second embodiment, the inner ring 10 has a collar portion 12 at one axial end portion of the inner ring raceway surface 11, and a collar portion 16 at the other axial end portion of the inner ring 10. A collar ring 15 is arranged in contact with each other. Similarly to the third embodiment, the outer ring 20 protrudes from the axial end surfaces of the inner ring 10 and the aligning ring 40 only on the other axial end side, so that the axial width of the outer ring 20 is the inner ring 10 and the outer ring 20. It is set longer than the axial width of the aligning ring 40. Thereby, in this embodiment, there can exist an effect similar to 2nd and 3rd embodiment.
Other configurations and operations are the same as those in the first embodiment.

なお、本発明は、上述した実施形態には限定されるものでなく、本発明の要旨を逸脱しない範囲において、適宜、変形、改良等は可能である。
例えば、本発明の外輪及び調心輪は、油溝や油穴を有する形状であってもよいし、油溝や油穴を有しない形状であってもよい。
また、本実施形態では、該軸受は総ころ形式としたが、保持器を有する形式としてもよい。
さらに、本実施形態では、外輪の軸方向幅は、調心輪と内輪の両方の軸方向幅より長くなるように設定されているが、本発明では、外輪の軸方向幅は、調心輪と内輪の少なくとも一方の軸方向幅より長くなるように設定されてもよい。例えば、図５（ａ）及び（ｂ）に示す第１及び第２変形例の調心輪付き円筒ころ軸受１ｄ，１ｅのように、軸箱６１と外側押え蓋６２の位置に決められる軸受取り付け幅を変更せず、調心輪４０の両端部は軸箱６１と外側押え蓋６２に当接させるとともに、調心輪４０の両端部若しくは一端部だけを外輪２０と同幅以下にするように部分的に軸方向に延長する実施形態にしてもよい。なお、第１及び第２変形例は、第１実施形態の調心輪付き円筒ころ軸受１を変更したものであるが、第２〜第４実施形態の調心輪付き円筒ころ軸受１ａ〜１ｃにも転用することが可能である。 The present invention is not limited to the above-described embodiments, and modifications, improvements, etc. can be made as appropriate without departing from the spirit of the present invention.
For example, the outer ring and the aligning ring of the present invention may have a shape having an oil groove or an oil hole, or may have a shape not having an oil groove or an oil hole.
In this embodiment, the bearing is a full roller type, but may be a type having a cage.
Furthermore, in this embodiment, the axial width of the outer ring is set to be longer than the axial width of both the aligning ring and the inner ring. However, in the present invention, the axial width of the outer ring is the aligning ring. And at least one axial width of the inner ring may be set longer. For example, as shown in FIGS. 5 (a) and 5 (b), first and second modified cylindrical roller bearings 1d and 1e with aligning rings, bearing mountings determined at the positions of the shaft box 61 and the outer presser lid 62 are provided. Without changing the width, both ends of the aligning ring 40 are brought into contact with the axle box 61 and the outer presser lid 62, and only both ends or one end of the aligning ring 40 are made equal to or smaller than the outer ring 20. The embodiment may be partially extended in the axial direction. In addition, although the 1st and 2nd modification changes the cylindrical roller bearing 1 with a centering ring of 1st Embodiment, it is the cylindrical roller bearing 1a-1c with a centering ring of 2nd-4th Embodiment. Can also be diverted.

１ 調心輪付き円筒ころ軸受
１０ 内輪
１１ 内輪軌道面
１２ つば部
２０ 外輪
２１ 外輪軌道面
２２ 外周面
２３ つば部
３０ 円筒ころ
４０ 調心輪
４１ 内周面 DESCRIPTION OF SYMBOLS 1 Cylindrical roller bearing with a centering ring 10 Inner ring 11 Inner ring raceway surface 12 Collar part 20 Outer ring 21 Outer ring raceway surface 22 Outer ring surface 23 Collar part 30 Cylindrical roller 40 Alignment ring 41 Inner circumference surface

Claims (1)

外周面に内輪軌道面を有する内輪と、
内周面に外輪軌道面を有し、外周面が球面形状を有する外輪と、
前記内輪軌道面と前記外輪軌道面との間に転動自在に配置される複数の円筒ころと、
前記外輪の外周面に揺動可能に嵌合する球面形状の内周面を有する調心輪と
を備えた調心輪付き転がり軸受において、
前記外輪は、軸方向において対称形状を有し、その軸方向中心が前記内輪及び前記調心輪の軸方向中心に対してオフセットして配置され、
前記調心輪は、軸方向において非対称形状に形成されており、
前記外輪の軸方向幅は、前記調心輪と前記内輪の少なくとも一方の軸方向幅より長いことを特徴とする調心輪付き円筒ころ軸受。 An inner ring having an inner ring raceway surface on the outer peripheral surface;
An outer ring having an outer ring raceway surface on the inner circumferential surface and an outer circumferential surface having a spherical shape;
A plurality of cylindrical rollers arranged to roll between the inner ring raceway surface and the outer ring raceway surface;
In a rolling bearing with a centering ring provided with a centering ring having a spherical inner peripheral surface fitted so as to be swingable to the outer peripheral surface of the outer ring,
The outer ring has a symmetrical shape in the axial direction, and its axial center is offset with respect to the axial center of the inner ring and the aligning ring,
The aligning ring is formed in an asymmetric shape in the axial direction,
An axial width of the outer ring is longer than an axial width of at least one of the aligning ring and the inner ring.
JP2013138992A 2013-07-02 2013-07-02 Cylindrical roller bearing with aligning ring Expired - Fee Related JP6185306B2 (en)

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