JP2005344854A - Cylindrical roller bearing - Google Patents

Cylindrical roller bearing Download PDF

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Publication number
JP2005344854A
JP2005344854A JP2004165925A JP2004165925A JP2005344854A JP 2005344854 A JP2005344854 A JP 2005344854A JP 2004165925 A JP2004165925 A JP 2004165925A JP 2004165925 A JP2004165925 A JP 2004165925A JP 2005344854 A JP2005344854 A JP 2005344854A
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Japan
Prior art keywords
cylindrical roller
roller bearing
spacer
cylindrical
track
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JP2004165925A
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Japanese (ja)
Inventor
Takuya Ozu
琢也 小津
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2004165925A priority Critical patent/JP2005344854A/en
Publication of JP2005344854A publication Critical patent/JP2005344854A/en
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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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/37—Loose spacing bodies
    • F16C33/3706—Loose spacing bodies with concave surfaces conforming to the shape of the rolling elements, e.g. the spacing bodies are in sliding contact with the rolling elements

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

Abstract

<P>PROBLEM TO BE SOLVED: To solve the problems of galling of mutual rollers of the whole roller bearings, roller collapsing of a pin type retainer and a cost increase, while securing high load capacity. <P>SOLUTION: This cylindrical roller bearing is composed of an inner race 2 having a track on the outer periphery, an outer race 4 having a track on the inner periphery, a plurality of cylindrical rollers 6 rollingly interposed between the track of the inner race 2 and the track of the outer race 4, a spacer 8 positioned between the adjacent cylindrical rollers 6 and exceeding the length of the cylindrical rollers 6, and a pair of annular side plates 10 positioned on both end sides in the shaft direction of the spacer 8. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は円筒ころ軸受に関する。   The present invention relates to a cylindrical roller bearing.

円筒ころ軸受は、転動体として円筒ころを用いたラジアル軸受である。ラジアル負荷能力が大きく、高速回転にも適している。円筒ころ軸受には保持器を用いて複数の円筒ころを円周方向で所定間隔に保つようにしたタイプと、保持器を用いない総ころタイプ（特許文献１参照）とがある。保持器にはもみ抜き保持器（特許文献２参照）、ピンタイプ保持器（特許文献３参照）、スタッドタイプ保持器（特許文献４参照）、ディスク保持器（特許文献５参照）などがある。
特開平１０−１８４６９３号公報（段落番号０００２、図３） 特開平１１−２９４４６０号公報（段落番号０００３、図１） 特開昭５３−０００３５８号公報（第１頁右下欄第３〜８行、第１図） 実開平０７−０２０４２３号公報（図１〜５） 特開２００２−９８１５４号公報（図１、２） The cylindrical roller bearing is a radial bearing using cylindrical rollers as rolling elements. Large radial load capacity, suitable for high-speed rotation. Cylindrical roller bearings include a type that uses a cage to keep a plurality of cylindrical rollers at a predetermined interval in the circumferential direction, and a full roller type that does not use a cage (see Patent Document 1). Examples of the cage include a machined cage (see Patent Literature 2), a pin type cage (see Patent Literature 3), a stud type cage (see Patent Literature 4), a disk cage (see Patent Literature 5), and the like.
JP-A-10-184893 (paragraph number 0002, FIG. 3) JP 11-294460 A (paragraph number 0003, FIG. 1) Japanese Patent Laid-Open No. 53-000358 (first page, lower right column, lines 3 to 8, line 1) Japanese Utility Model Publication No. 07-020423 (FIGS. 1 to 5) JP 2002-98154 A (FIGS. 1 and 2)

総ころ軸受は、保持器を用いないでより多くのころを組み込めるようにしたものであるため負荷容量が大きく安価である反面、ころ同士が逆回転ですべり接触するためかじりやすく、極低速回転（ｄｎ値２０万以下）でしか使えない。   Full roller bearings are designed so that more rollers can be assembled without using a cage, so the load capacity is large and inexpensive. It can only be used at a dn value of 200,000 or less.

もみ抜き保持器は安価である反面、強度・剛性確保のために保持器は太い柱を必要とし、結果として負荷容量が小さい。軸受内空間容積のうち３０％程度が保持器容積となる。
ピンタイプ保持器は負荷容量が大きい反面、中空ころを使用するのでころ強度が低下し、また、組立に溶接を用いるため高価である。 While the machined cage is inexpensive, the cage requires a thick column to ensure strength and rigidity, resulting in a small load capacity. About 30% of the bearing internal volume is the cage volume.
The pin type cage has a large load capacity, but uses hollow rollers, so that the roller strength is lowered, and it is expensive because welding is used for assembly.

スタッドタイプ保持器は中実ころでありながらピンタイプ保持器同等の負荷容量を有する反面、複数の溶接箇所を有し、構造も複雑であるため高価である。   The stud type cage has a load capacity equivalent to that of the pin type cage while being a solid roller, but has a plurality of welded portions and is complicated and expensive.

ディスク保持器は、中実ころを使用し保持器構造も単純である反面、内輪または外輪を２部材から構成する必要があり、加工コスト、組立工数共に大である。また、内輪または外輪の一部に全周にわたって溝を有するため負荷容量がやや劣る。   The disk cage uses solid rollers and the cage structure is simple, but the inner ring or the outer ring needs to be composed of two members, and both the processing cost and the assembly man-hour are large. In addition, the load capacity is slightly inferior because the inner ring or a part of the outer ring has grooves all around.

この発明の円筒ころ軸受は、外周に軌道を有する内輪２と、内周に軌道を有する外輪４と、内輪２の軌道と外輪４の軌道との間に転動自在に介在する複数の円筒ころ６と、隣り合った円筒ころ６間に位置する間座８と、間座８の軸方向両端を支持する一対の環状の側板１０とを具備している。すなわち、より多くの円筒ころ６を軸受に組み込むために、従来の保持器に代えて間座８を採用し、円筒ころ６間に間座８を挿入して、一対の側板１０により間座８の両端を支持して案内するようにしたもので、これにより、中実の円筒ころ６を使用した高負荷容量型円筒ころ軸受を提供するものである。総ころ軸受と異なり円筒ころ６同士が接触しないため、かじりのおそれはない。しかも、従来の保持器の柱に相当する間座８と従来の保持器のリング部に相当する側板１０とが分離しているため、間座８の破断の可能性が極めて低い。間座８は円筒ころ６だけで挟むこともできるが、内輪２または外輪４または側板１０によって案内させることで、より挙動が安定する。さらに、間座８は溶接を必要とせず、形状が単純であるため、組立が容易で安価である。なお、側板１０は内輪２または外輪４のいずれかに固定する。固定方法はボルト止めまたは圧入とすることができる。   The cylindrical roller bearing according to the present invention includes an inner ring 2 having a raceway on the outer periphery, an outer ring 4 having a raceway on the inner periphery, and a plurality of cylindrical rollers interposed between the race of the inner ring 2 and the race of the outer ring 4 in a freely rolling manner. 6, a spacer 8 positioned between adjacent cylindrical rollers 6, and a pair of annular side plates 10 that support both axial ends of the spacer 8. That is, in order to incorporate more cylindrical rollers 6 into the bearing, a spacer 8 is adopted instead of the conventional cage, the spacer 8 is inserted between the cylindrical rollers 6, and the spacer 8 is inserted by the pair of side plates 10. In this way, a high load capacity type cylindrical roller bearing using solid cylindrical rollers 6 is provided. Unlike the full roller bearing, the cylindrical rollers 6 do not contact each other, so there is no risk of galling. In addition, since the spacer 8 corresponding to the pillar of the conventional cage is separated from the side plate 10 corresponding to the ring portion of the conventional cage, the possibility of the spacer 8 being broken is extremely low. The spacer 8 can be sandwiched only by the cylindrical rollers 6, but the behavior is further stabilized by being guided by the inner ring 2, the outer ring 4, or the side plate 10. Furthermore, since the spacer 8 does not require welding and has a simple shape, it is easy to assemble and inexpensive. The side plate 10 is fixed to either the inner ring 2 or the outer ring 4. The fixing method can be bolted or press-fitted.

この発明によれば、高負荷容量を確保しつつ、総ころ軸受におけるころ同士のかじり、ピンタイプ保持器品におけるころ圧砕、コスト大といった問題点が解消した円筒ころ軸受を提供することができる。   According to the present invention, it is possible to provide a cylindrical roller bearing in which high load capacity is ensured, and problems such as galling of rollers in a full roller bearing, roller crushing in a pin type cage product, and high cost are solved.

以下、図面に従って本発明の実施の形態を説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１（Ａ）に示すように、円筒ころ軸受は、内輪２と外輪４と円筒ころ６と間座８と側板１０とを主要な構成要素として成り立っている。内輪２は外周に軌道を有し、外輪４は内周に軌道を有する。内輪２の軌道と外輪４の軌道との間に複数の円筒ころ６が転動自在に介在させてある。間座８は、円筒ころ６の長さを越えて軸方向に延在している。側板１０は環状で、ここでは外輪４の両側にボルト１２で固定してある。側板１０の内側面には環状の凹部１４が設けてある。そして、間座８の軸方向両端部を側板１０の凹部１４にて受け入れることにより、間座８を側板１０で支持・案内する。側板１０を介して間座８を外輪４によって案内させることにより、間座８の挙動が安定する。かじり防止のため、間座８と側板１０の材質は異材とするのが望ましい。たとえば、間座８の材質を黄銅または樹脂とし、側板１０の材質を鉄または黄銅とする。   As shown in FIG. 1A, the cylindrical roller bearing includes an inner ring 2, an outer ring 4, a cylindrical roller 6, a spacer 8, and a side plate 10 as main components. The inner ring 2 has a track on the outer periphery, and the outer ring 4 has a track on the inner periphery. A plurality of cylindrical rollers 6 are movably interposed between the race of the inner ring 2 and the race of the outer ring 4. The spacer 8 extends in the axial direction beyond the length of the cylindrical roller 6. The side plate 10 is annular, and is fixed here with bolts 12 on both sides of the outer ring 4. An annular recess 14 is provided on the inner surface of the side plate 10. Then, the spacer 8 is supported and guided by the side plate 10 by receiving both axial end portions of the spacer 8 by the concave portions 14 of the side plate 10. By causing the spacer 8 to be guided by the outer ring 4 through the side plate 10, the behavior of the spacer 8 is stabilized. In order to prevent galling, the spacer 8 and the side plate 10 are preferably made of different materials. For example, the spacer 8 is made of brass or resin, and the side plate 10 is made of iron or brass.

ここでは側板１０を外輪４に固定してあるが、内輪２に固定してもよい。また、固定方法もボルト止めに代えて圧入を採用してもよい。さらに、場合によってはハウジング側の幅押さえに頼ることもできる。また、図示するように別体の側板１０を採用するほか、軌道輪（２または４）のつば輪の形状を工夫して側板１０の機能を兼備させることにより別体の側板１０を廃止してもよい。   Although the side plate 10 is fixed to the outer ring 4 here, it may be fixed to the inner ring 2. In addition, the fixing method may be press-fitting instead of bolting. Furthermore, depending on the case, it is possible to rely on the width control on the housing side. In addition to adopting a separate side plate 10 as shown in the figure, the separate side plate 10 is eliminated by devising the shape of the collar ring of the raceway ring (2 or 4) and combining the functions of the side plate 10 with each other. Also good.

図１（Ｂ）に示すように、間座８は隣り合った円筒ころ６の間に介在し、同図に一点鎖線で示したピッチ円を挟んで保持器の半径方向に、言い換えればピッチ円の内径側から外径側まで、延在している。したがって、ピッチ円上における円筒ころ６間すきまによって間座８の最小肉厚が決まる。たとえば、ピッチ円上の円筒ころ６間すきまは、ころ径をＤWとしたとき、０．０５×ＤW〜０．１０×ＤWの範囲内である。図１（Ｂ）に示す実施の形態では、間座８の側面の断面形状が円筒ころ６の転動面の曲率半径よりも僅かに大きい曲率半径の円弧である。間座８は円筒ころ６のピッチ円を挟んで軸受の半径方向に延在している。この場合、間座８が円筒ころ６のピッチ円を越えて円筒ころ６を抱くため、内輪２または外輪４を抜いても円筒ころ６は分離しない。したがって、分解・組立や保管等の取り扱いが容易である。 As shown in FIG. 1B, the spacer 8 is interposed between the cylindrical rollers 6 adjacent to each other, and in the radial direction of the cage with the pitch circle shown by the one-dot chain line in FIG. It extends from the inner diameter side to the outer diameter side. Therefore, the minimum thickness of the spacer 8 is determined by the clearance between the cylindrical rollers 6 on the pitch circle. For example, the clearance between the cylindrical rollers 6 on the pitch circle is in the range of 0.05 × D W to 0.10 × D W when the roller diameter is D W. In the embodiment shown in FIG. 1B, the cross-sectional shape of the side surface of the spacer 8 is an arc having a slightly larger curvature radius than the curvature radius of the rolling surface of the cylindrical roller 6. The spacer 8 extends in the radial direction of the bearing across the pitch circle of the cylindrical roller 6. In this case, since the spacer 8 holds the cylindrical roller 6 beyond the pitch circle of the cylindrical roller 6, the cylindrical roller 6 is not separated even if the inner ring 2 or the outer ring 4 is pulled out. Therefore, handling such as disassembly / assembly and storage is easy.

図２は、側板１０を外輪４に圧入により固定した実施の形態を示す。また、この実施の形態では、側板１０が軸方向に貫通した油穴１６を有し、間座８の側面にも軸受の半径方向に延びる油溝１８が設けてある。いずれも、円筒ころ６の周囲にある潤滑油が外部に流出しやすくして潤滑油による攪拌抵抗を軽減させる役割を果たす。   FIG. 2 shows an embodiment in which the side plate 10 is fixed to the outer ring 4 by press fitting. Further, in this embodiment, the side plate 10 has an oil hole 16 penetrating in the axial direction, and an oil groove 18 extending in the radial direction of the bearing is also provided on the side surface of the spacer 8. In any case, the lubricating oil around the cylindrical roller 6 easily flows out to the outside and plays a role of reducing stirring resistance by the lubricating oil.

次に、ＮＪ３０４４（φ２２０×φ３４０×９０）に本発明を適用した実施例と比較例とについて、ころ本数および軸受寿命比を比較した結果を表１に示す。   Next, Table 1 shows the result of comparing the number of rollers and the bearing life ratio in the example and the comparative example in which the present invention is applied to NJ3044 (φ220 × φ340 × 90).

上記型番の場合、ＰＣＤ上のころ間すきま＝０．１０×ころ径となり、表１から分かるように、実施例の円筒ころ軸受はピンタイプ保持器を用いた円筒ころ軸受と同一本数の円筒ころを組み込むことが可能で、寿命比は総ころタイプよりは劣るものの、ピンタイプ保持器の場合と同じで、もみ抜き保持器の場合より２５％向上した。   In the case of the above model numbers, the clearance between rollers on the PCD is 0.10 × roller diameter. As can be seen from Table 1, the cylindrical roller bearings of the examples are the same number of cylindrical roller bearings as the cylindrical roller bearings using pin type cages. Although the life ratio is inferior to that of the full roller type, the life ratio is the same as that of the pin type cage, which is 25% higher than that of the machined cage.

なお、本発明は、上述の実施の形態に限定されるものではなく、本発明の要旨を逸脱しない範囲内において種々変更を加え得ることは勿論である。   In addition, this invention is not limited to the above-mentioned embodiment, Of course, a various change can be added in the range which does not deviate from the summary of this invention.

(Ａ)は本発明の実施の形態を示す円筒ころ軸受の断面図、（Ｂ）は図１（Ａ）における右側の側板を取り除いた状態の側面図である。(A) is sectional drawing of the cylindrical roller bearing which shows embodiment of this invention, (B) is a side view of the state which removed the right side board in FIG. 1 (A). （Ａ）は別の実施の形態を示す円筒ころ軸受の断面図、（Ｂ）は一部を破断した側面図である。(A) is sectional drawing of the cylindrical roller bearing which shows another embodiment, (B) is the side view which fractured | ruptured one part.

符号の説明Explanation of symbols

２ 内輪
４ 外輪
６ 円筒ころ
８ 保持器
１０ 側板
１２ ボルト
１４ 凹部
１６ 油穴
１８ 油溝 2 Inner ring 4 Outer ring 6 Cylindrical roller 8 Cage 10 Side plate 12 Bolt 14 Recess 16 Oil hole 18 Oil groove

Claims (8)

外周に軌道を有する内輪と、内周に軌道を有する外輪と、内輪の軌道と外輪の軌道との間に転動自在に介在する複数の円筒ころと、隣り合った円筒ころ間に位置する間座と、間座の軸方向両端を支持する一対の環状の側板とを具備したことを特徴とする円筒ころ軸受。   Between an inner ring having a track on the outer periphery, an outer ring having a track on the inner periphery, a plurality of cylindrical rollers movably interposed between the track of the inner ring and the track of the outer ring, and between adjacent cylindrical rollers A cylindrical roller bearing comprising a seat and a pair of annular side plates that support both axial ends of the spacer. 前記間座が円筒ころのピッチ円の内径側から外径側まで延在している請求項１の円筒ころ軸受。   The cylindrical roller bearing according to claim 1, wherein the spacer extends from an inner diameter side to an outer diameter side of a pitch circle of the cylindrical roller. 前記間座の側面の断面形状が円筒ころの転動面の曲率半径よりも僅かに大きい曲率半径の円弧である請求項１または２の円筒ころ軸受。   The cylindrical roller bearing according to claim 1 or 2, wherein a cross-sectional shape of a side surface of the spacer is an arc having a radius of curvature slightly larger than a radius of curvature of a rolling surface of the cylindrical roller. 前記側板を外輪に固定した請求項１ないし３のいずれかの円筒ころ軸受。   The cylindrical roller bearing according to claim 1, wherein the side plate is fixed to the outer ring. 前記側板を内輪に固定した請求項１ないし３のいずれかの円筒ころ軸受。   The cylindrical roller bearing according to claim 1, wherein the side plate is fixed to an inner ring. 前記側板が軸方向に貫通した油穴を有する請求項１ないし５のいずれかの円筒ころ軸受。   The cylindrical roller bearing according to claim 1, wherein the side plate has an oil hole penetrating in the axial direction. 前記間座の側面に保持器の半径方向に延びる油溝を設けた請求項１ないし６のいずれかの円筒ころ軸受。   The cylindrical roller bearing according to claim 1, wherein an oil groove extending in a radial direction of the cage is provided on a side surface of the spacer. ピッチ円径上の円筒ころ間すきまが、ころ径をＤWとしたとき、０．０５×ＤW〜０．１０×ＤWの範囲内である請求項１ないし７のいずれかの円筒ころ軸受。 The cylindrical roller bearing according to any one of claims 1 to 7, wherein a clearance between the cylindrical rollers on the pitch circle diameter is in a range of 0.05 x D W to 0.10 x D W when the roller diameter is D W. .
JP2004165925A 2004-06-03 2004-06-03 Cylindrical roller bearing Withdrawn JP2005344854A (en)

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JP2004165925A Withdrawn JP2005344854A (en) 2004-06-03 2004-06-03 Cylindrical roller bearing

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007069392A1 (en) * 2005-12-16 2007-06-21 Ntn Corporation Roller bearing
JP2007170571A (en) * 2005-12-22 2007-07-05 Ntn Corp Radial roller bearing
JP2014214809A (en) * 2013-04-25 2014-11-17 Ntn株式会社 Roller bearing
CN112460140A (en) * 2020-11-27 2021-03-09 朱华风 Transmission bearing convenient to connect

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007069392A1 (en) * 2005-12-16 2007-06-21 Ntn Corporation Roller bearing
US7963702B2 (en) 2005-12-16 2011-06-21 Ntn Corporation Roller bearing
JP2007170571A (en) * 2005-12-22 2007-07-05 Ntn Corp Radial roller bearing
JP2014214809A (en) * 2013-04-25 2014-11-17 Ntn株式会社 Roller bearing
CN112460140A (en) * 2020-11-27 2021-03-09 朱华风 Transmission bearing convenient to connect
CN112460140B (en) * 2020-11-27 2022-08-09 聊城鲁寰轴承有限公司 Transmission bearing convenient to connect

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Effective date: 20070807