JP2002339977A - Spherical roller - Google Patents
Spherical rollerInfo
- Publication number
- JP2002339977A JP2002339977A JP2001180873A JP2001180873A JP2002339977A JP 2002339977 A JP2002339977 A JP 2002339977A JP 2001180873 A JP2001180873 A JP 2001180873A JP 2001180873 A JP2001180873 A JP 2001180873A JP 2002339977 A JP2002339977 A JP 2002339977A
- Authority
- JP
- Japan
- Prior art keywords
- spherical
- ball
- roller
- rolling
- contact
- 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
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、玉のように使い
易い性能を持ち、且つころのように高負荷容量を合わせ
持つ「球ころ」（日研産業（株）商標出願中）に関する
ものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a "ball roller" which has an easy-to-use performance like a ball and a high load capacity like a roller (Nikken Sangyo Co., Ltd. trademark pending). is there.
【０００２】[0002]
【従来の技術】従来の転がり軸受等に使用する転動体と
しては、「玉」と「ころ」があった。玉は、点接触であ
り、負荷容量が小さいが、わずかの自動調心性があり、
それによる使い易さがある。また、玉は、ラジアル荷重
の１／１０位のスラスト荷重を受けられる。一方、ころ
は、ころ軸受で線接触であり、負荷容量は玉軸受の６倍
と高荷重，高剛性に耐えられるが、図４（Ｃ）に示すよ
うに、軌道面１１０に沿ってころ１００の端面１０３を
支持するつば部１１１が必要で、ころ１００は転動面１
０２と端面１０３の二面拘束となる（ラジアル方向とス
ラスト方向の２方向に接触）。この場合、ラジアル方向
の転動面１０２およびスラスト方向の端面１０３の両方
とも、正確かつきれいな面にする必要があり、仕上がり
面の超仕上げが要求されることはもちろん、ころ１００
が接触する軌道面１１０とつば部１１１との完全な直角
度、さらにはころ１００の端面１０３と正確な面接触を
させるためにつば部１１１の高精度加工が必要となる。
また、正確に面接触させるための軌道面１１０およびつ
ば部１１１が正確にできても、内外輪が取り付けられる
ハウジングや軸の取付面が狂っていると摩擦抵抗が増大
するので、ハウジングや軸についても高精度が必要とな
る。また、高精度に加工したとしても、使用時に実際に
加わる力や熱膨張などによって軌道面が変形した場合、
ころ１００には自動調心性が無いので、ころ１００の端
部が軌道面１１０およびつば部１１１に片当たりすると
いう欠点がある。さらに、スラスト荷重を受けるころ１
００の端面１０３はすべり接触であり摩擦抵抗が大き
い。また、平面接触しているころ１００の端面１０３と
つば部１１１の接触面Ａ間には潤滑剤が入りにくく、潤
滑不良となり摩耗しやすい。また、発熱が大きくなっ
て、甚だしい場合は焼き付いてしまう。2. Description of the Related Art Rolling elements used in conventional rolling bearings and the like include "balls" and "rollers". The ball is a point contact, has a small load capacity, but has a slight self-centering,
It is easy to use. Further, the ball can receive a thrust load of about 1/10 of the radial load. On the other hand, the rollers are in linear contact with the roller bearings and have a load capacity six times that of the ball bearings and can withstand high loads and high rigidity. However, as shown in FIG. A flange 111 for supporting the end face 103 of the roller is required, and the roller 100
02 and the end face 103 are restricted (contact in two directions, the radial direction and the thrust direction). In this case, both the radial rolling surface 102 and the thrust end surface 103 need to be accurate and clean, and the finished surface must be super-finished.
In order to make a perfect right angle between the raceway surface 110 and the flange portion 111 that makes contact with each other, and to make an accurate surface contact with the end surface 103 of the roller 100, high-precision processing of the collar portion 111 is required.
In addition, even if the raceway surface 110 and the brim portion 111 for accurate surface contact can be accurately formed, if the mounting surface of the housing or shaft on which the inner and outer rings are mounted is incorrect, the frictional resistance increases. Also requires high precision. In addition, even if processed with high precision, if the raceway surface is deformed due to the actual applied force or thermal expansion during use,
Since the roller 100 has no self-aligning property, there is a disadvantage that the end portion of the roller 100 hits against the raceway surface 110 and the collar portion 111. In addition, when the thrust load is
The end face 103 of 00 is in sliding contact and has high frictional resistance. Further, it is difficult for the lubricant to enter between the end surface 103 of the roller 100 and the contact surface A of the flange portion 111 which are in planar contact, and poor lubrication is likely to occur and wear is likely. In addition, heat generation becomes large, and in severe cases, it burns.
【０００３】[0003]
【発明が解決しようとする課題】本発明の目的は、ころ
程ではないが玉より３〜４倍の負荷容量を持つ玉ところ
の中間的な特徴を持ち、また、ころのような転動面と端
面の二面拘束の制約が無く、大きいスラスト荷重につい
ても低摩擦で対応でき、しかもコストが安い新規形状の
球ころを提供することにある。SUMMARY OF THE INVENTION It is an object of the present invention to provide an intermediate feature of a ball having a load capacity that is three to four times that of a ball, though not as much as a roller. Another object of the present invention is to provide a spherical roller having a new shape, which is free from restrictions of two-sided restraint of an end face, can cope with a large thrust load with low friction, and is inexpensive.
【０００４】[0004]
【課題を解決するための手段】上記目的を達成するた
め、この発明の球ころは、円弧状に膨らんだ転動球面部
と、該転動球面部両端の球面状に膨らんだ端面球面部
と、を備え、前記転動球面部の曲率半径が端面球面部の
曲率半径よりも大きく、前記転動球面部の回転中心線上
に前記端面球面部の曲率中心を持ち、前記転動球面部の
最大径と端面球面部の頂点間の長さの比率を略８０％±
１７％の範囲とした形状を有している。この転動体の形
状には、転動球面部の一端が大径かつ他端が小径で長手
方向円弧に勾配が付けられたテーパ球面形状も含まれ
る。テーパ球面形状とは、円錐形の直線的な勾配のつい
た斜面に対して円弧状に膨らんだ形状の意味である。In order to achieve the above object, a spherical roller according to the present invention comprises a rolling spherical portion bulging in an arc shape, and a spherical spherical end surface at both ends of the rolling spherical portion. Wherein the radius of curvature of the rolling spherical surface portion is larger than the radius of curvature of the end spherical surface portion, has a center of curvature of the end spherical surface portion on the rotation center line of the rolling spherical surface portion, and has a maximum radius of the rolling spherical surface portion. Approximately 80% ±
It has a shape with a range of 17%. The shape of the rolling element includes a tapered spherical shape in which one end of the rolling spherical portion has a large diameter at one end and a small diameter at the other end, and the longitudinal arc is inclined. The tapered spherical shape means a shape bulging in an arc shape with respect to a conical slope having a linear gradient.
【０００５】[0005]
【発明の実施の形態】次に、この発明の実施の形態につ
いて、図面を参照しつつ詳細に説明する。図１は、この
発明の実施の形態に係る球ころを示している。この球こ
ろ１は、円弧状に膨らんだ転動球面部２と、この転動球
面部２左右両端の球面状に膨らんだ端面球面部３，３
と、を備え、転動球面部２の曲率半径Ｒが左右の端面球
面部３，３の曲率半径ｒ１，ｒ２よりも大きく、前記転
動球面部２の回転中心線Ｎ上に前記端面球面部３，３の
曲率中心Ｏ１，Ｏ２を有している。そして、転動球面部
２の最大径である短径ｄと端面球面部３の頂点ｔ１，ｔ
２間の長さである長径Ｗの比率を略８０％±１７％の範
囲とした形状を有している。Next, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a spherical roller according to an embodiment of the present invention. The spherical roller 1 includes a rolling spherical portion 2 bulging in an arc shape, and spherical bulging end surface spherical portions 3, 3 on both right and left ends of the rolling spherical portion 2.
Wherein the radius of curvature R of the rolling spherical surface portion 2 is larger than the curvature radii r1 and r2 of the left and right end spherical surface portions 3 and 3, and the end spherical surface portion is located on the rotation center line N of the rolling spherical surface portion 2. It has three and three centers of curvature O1 and O2. Then, the minor diameter d, which is the maximum diameter of the rolling spherical surface portion 2, and the vertices t1, t of the end spherical surface portion 3
It has a shape in which the ratio of the major axis W, which is the length between two, is in the range of approximately 80% ± 17%.
【０００６】左右の端面球面部３，３の中心Ｏ１，Ｏ２
は、図１（Ａ）に示すようにずれていてもよいし、図１
（Ｄ）に示すようにほぼ一致させておいてもよい。転動
球面部２の左右両端は同一径で、転動球面部２の最大径
位置は回転中心線Ｎ方向の中央位置に位置する。このよ
うに、球ころ１の外形は、転動球面部２の円弧面と端面
球面部３，３の球面とを組み合わせた形状で、その長手
方向断面が略楕円形と円形の中間の形状となっている。
また、転動球面部２と端面球面部３，３の境界部には丸
みが付けられている。図１（Ａ）〜（Ｃ）は８０％の
例、図１（Ｄ）〜（Ｆ）は９０％の例である。すなわ
ち、短径ｄと長径Ｗの比率が小さい（差が小さい）ほど
球に近くなり、比率が大きい（差が大きい）ほどころに
近づき、高負荷容量が得られ、重荷重に適する。なお、
図２に示すように、転動球面部２をテーパ球面形状とし
てもよい。すなわち、転動球面部２は、その一端が大径
かつ他端が小径で長手方向円弧に勾配が付けられてい
る。図示例は、長径Ｗに対する短径ｄの割合を８０％に
した例である。The centers O1, O2 of the spherical portions 3, 3 on the left and right end surfaces.
May be shifted as shown in FIG.
As shown in (D), they may be substantially matched. The left and right ends of the rolling spherical surface portion 2 have the same diameter, and the maximum diameter position of the rolling spherical surface portion 2 is located at the center position in the direction of the rotation center line N. As described above, the outer shape of the spherical roller 1 is a shape obtained by combining the arc surface of the rolling spherical portion 2 and the spherical surfaces of the end surface spherical portions 3 and 3, and its longitudinal section is a shape intermediate between an approximately elliptical shape and a circular shape. Has become.
Further, the boundary between the rolling spherical surface portion 2 and the end surface spherical portions 3 and 3 is rounded. 1A to 1C show an example of 80%, and FIGS. 1D to 1F show an example of 90%. In other words, the smaller the ratio of the minor axis d to the major axis W (the smaller the difference), the closer to the sphere, and the larger the ratio (the larger the difference), the closer to the roller, the higher the load capacity, and the higher the load. In addition,
As shown in FIG. 2, the rolling spherical portion 2 may have a tapered spherical shape. That is, the rolling spherical surface portion 2 has a large diameter at one end and a small diameter at the other end, and is inclined in a longitudinal arc. The illustrated example is an example in which the ratio of the minor axis d to the major axis W is set to 80%.
【０００７】球ころ１の製造は次のようにして行う。図
１（Ｄ）に示したような短径ｄと長径Ｗの比率が小さい
球ころの場合には、完成した鋼球２０を使用し、図３
（Ａ）に示すように、転動球面部２の希望する半径の凹
面５２を持った砥石５０によって、転動球面部２を研削
し、その研削面を超仕上げすれば、本発明の球ころをき
わめて安く簡単に製造することができる。この場合、端
面球面部２は鋼球２０の球面がそのまま残る。一方、図
１（Ａ）に示したような短径ｄと長径Ｗの比率が大きい
球ころの場合には、図３（Ｂ）に示すように、球面状の
凹部７１を備えた型７０を用いて素材を軸方向に圧縮し
て球状の素材３０を予備成形する。この予備成形される
素材３０は、焼き入れ前の玉の素球（生ボール）の中央
部を、転造等によって、円弧状に押し潰して成形しても
よいし、円筒状の素材を転造などによって円弧状に押し
潰して成形してもよい。この素材３０を、図３（Ｃ）に
示すように、転動球面部２に対応する半径の第１凹面６
２と、この第１凹面６２の両側に端面球面部３，３に対
応する半径の第２凹面６３，６３を有する砥石６０によ
って研削することによって、簡単に転動球面部２の回転
中心線Ｎ上に端面球面部３，３の曲率中心Ｏ１，Ｏ２が
位置する形状の球ころ１をきわめて安く簡単に製造する
ことができる。また、図３（Ｄ）に示すように、端面球
面部３，３は予備成形の面をそのまま利用し、端面球面
部３，３をチャックして、転動球面部２に対応する凹部
８１を備えた砥石８０によって研削するようにしてもよ
い。The manufacture of the ball roller 1 is performed as follows. In the case of a spherical roller having a small ratio between the minor axis d and the major axis W as shown in FIG. 1 (D), the completed steel ball 20 is used and FIG.
As shown in (A), if the rolling spherical surface portion 2 is ground with a grindstone 50 having a concave surface 52 of a desired radius of the rolling spherical surface portion 2 and the ground surface is super-finished, the spherical roller of the present invention can be obtained. Can be manufactured very cheaply and easily. In this case, the spherical surface of the steel ball 20 remains in the end surface spherical portion 2 as it is. On the other hand, in the case of a spherical roller having a large ratio between the minor axis d and the major axis W as shown in FIG. 1A, a mold 70 having a spherical concave portion 71 is used as shown in FIG. The material is axially compressed to form a spherical material 30 in advance. This preformed material 30 may be formed by crushing the central part of a raw ball (raw ball) before quenching into an arc shape by rolling or the like, or by rolling a cylindrical material. It may be formed by crushing into an arc shape by molding or the like. As shown in FIG. 3 (C), this material 30 is formed into a first concave surface 6 having a radius corresponding to the rolling spherical surface portion 2.
2 and grinding by a grindstone 60 having second concave surfaces 63, 63 having a radius corresponding to the end spherical surfaces 3, 3 on both sides of the first concave surface 62, the rotation center line N of the rolling spherical surface portion 2 can be easily obtained. The spherical roller 1 having a shape on which the centers of curvature O1 and O2 of the spherical surface portions 3 and 3 are located can be manufactured very cheaply and easily. Further, as shown in FIG. 3D, the spherical surfaces 3 and 3 of the end faces use the preformed surface as they are, and the spherical faces 3 and 3 of the end faces are chucked to form the concave portion 81 corresponding to the rolling spherical portion 2. The grinding may be performed by the provided grindstone 80.
【０００８】なお、転動球面部２および端面球面部３の
形状は、幾何学的に厳密な意味での球面形状である必要
はなく丸く膨らんだ形状であればよい。また、端面球面
部３，３の頂点にセンタ孔を設けてもよい。The shapes of the rolling spherical surface portion 2 and the end surface spherical surface portion 3 do not need to be spherical shapes in a strictly geometrical sense, but may be any shape as long as they are round and expanded. In addition, a center hole may be provided at the vertex of the end surface spherical portions 3.
【０００９】このような球ころ１は、玉と比較すると、
転動球面部２の接触長が長くなるので、玉に比べて負荷
容量は数倍大きくなる。有効接触長さは、ころの２／３
程度に設定することが好適で、このようにすれば、調心
性に優れ、しかも玉の４倍程度の負荷容量が得られる。
また、図４（Ａ）に示すように、接触長さをＷ１とする
と、中央部と両端部の径の差に起因する差動すべり量π
（ｄ−ｄ０）は、玉の場合のπ（ｄ１−ｄ０）に比べて
小さいので、摩擦抵抗が軽減され、軽快に回転する。[0009] Such a ball roller 1 is, when compared with a ball,
Since the contact length of the rolling spherical portion 2 is long, the load capacity is several times larger than that of the ball. Effective contact length is 2/3 of roller
It is preferable to set the load capacity to such a degree. In this way, excellent alignment and a load capacity about four times as large as that of a ball can be obtained.
Further, as shown in FIG. 4A, assuming that the contact length is W1, the differential slip amount π caused by the difference in diameter between the center and both ends is shown.
Since (d−d0) is smaller than π (d1−d0) in the case of a ball, frictional resistance is reduced and the ball rotates lightly.
【００１０】さらに、本発明の球ころ１の場合には、転
動球面部２が円弧形状の軌道溝１０に接触するので、軽
いスラスト荷重の場合には、軌道溝１０との接触部によ
って支持することができ、図４（Ｃ）に示した円筒ころ
１００のようにつば部１１１は不要である。また、大き
なスラスト荷重を受ける場合には、軌道溝１０を端面球
面部３が一部接触する深溝とすればよい。端面球面部３
と端面接触部１１間は基本的には転がり接触（転がり＋
すべり）となるので、摩擦抵抗が小さく、大きなスラス
ト荷重を受けることができる。Further, in the case of the spherical roller 1 of the present invention, the rolling spherical surface portion 2 comes into contact with the arc-shaped raceway groove 10, so that in the case of a light thrust load, it is supported by the contact portion with the raceway groove 10. The collar portion 111 is unnecessary as in the case of the cylindrical roller 100 shown in FIG. When a large thrust load is received, the raceway groove 10 may be a deep groove with which the end surface spherical portion 3 partially contacts. End spherical surface part 3
And the end surface contact portion 11 is basically in rolling contact (rolling +
As a result, the frictional resistance is small and a large thrust load can be received.
【００１１】また、従来のころの場合には、自動調心性
が無く、図４（Ｃ）に示すように、軌道面１１０が軸方
向に傾くと、ころ１００の転動面部端部が軌道面１１０
に片当たりするが、本発明の球ころ１の場合には、図４
（Ｂ）に示すように、軌道溝１０に対しては転動球面部
２が円弧状なので玉と同様に調心性を有する。また、端
面球面部３が一部接触するように軌道溝１０を深溝とし
た場合、端面接触面１１に対しても端面球面部３が球面
接触となるので、軌道部材の傾きを許容でき、玉と同
様、内外輪等の軌道部材の加工や組立に高い寸法精度が
要求されず、取りいやすい利点がある。軌道溝１０を球
ころ１の転動球面部２の曲率半径より多少大きくしてお
くことにより、油等の潤滑剤が軌道溝１０に入り易く、
接触面も玉と異なり面接触で潤滑剤の油膜切れも生じに
くいので、良好な潤滑が維持され摩擦抵抗も少ない。軌
道溝１０を深溝として端面球面部３が一部接触する場合
でも、軌道溝１０の端面接触面１１と端面球面部３間の
隙間に潤滑剤が入りやすく摩擦抵抗が少ない。この端面
接触面１１の曲率半径は端面球面部３に対して多少大き
くなっている。In the case of the conventional roller, there is no self-aligning property, and as shown in FIG. 4C, when the raceway surface 110 is inclined in the axial direction, the end of the rolling surface portion of the roller 100 is 110
In the case of the ball roller 1 of the present invention, FIG.
As shown in (B), since the rolling spherical surface portion 2 has an arc shape with respect to the raceway groove 10, it has an aligning property like a ball. Further, when the raceway groove 10 is a deep groove so that the end surface spherical portion 3 is partially in contact, the end surface spherical portion 3 comes into spherical contact with the end surface contact surface 11, so that the inclination of the race member can be allowed, and Similarly to the above, there is an advantage that high dimensional accuracy is not required for processing and assembling of the track members such as the inner and outer rings, and it is easy to take. By making the raceway groove 10 slightly larger than the radius of curvature of the rolling spherical portion 2 of the ball roller 1, lubricant such as oil easily enters the raceway groove 10,
Since the contact surface is also unlike the ball, the oil film of the lubricant does not easily break due to the surface contact, so that good lubrication is maintained and the frictional resistance is small. Even when the end surface spherical portion 3 is partially in contact with the raceway groove 10 as a deep groove, the lubricant easily enters the gap between the end surface contact surface 11 of the raceway groove 10 and the end surface spherical portion 3 and the frictional resistance is small. The radius of curvature of the end surface contact surface 11 is slightly larger than that of the end surface spherical portion 3.
【００１２】図５乃至図８には、球ころを用いたベアリ
ングの球ころ装着例を、玉１２０の場合と比較して示し
ている。図５及び図６は本発明の球ころと従来の高荷重
型の深溝タイプの玉軸受との比較例、図７及び図８は本
発明の深溝タイプとした球ころと従来の深溝タイプの玉
軸受との比較例である。球ころ１の組み込みは、図５
（Ｃ），図７（Ｃ）に示すように、内輪１３を偏心させ
て外輪１４の内周に内接させ、外輪１４内周と内輪１３
外周間の円弧状の空間にできるだけ多くの球ころ１を装
着し、その後、内輪１３を外輪１４と同心位置に移動さ
せて、図６（Ａ），図８（Ａ）に示すように球ころ１を
一列に整列させる。FIGS. 5 to 8 show examples of mounting of a bearing using a ball roller in comparison with the case of the ball 120. FIG. 5 and 6 are comparative examples of the ball roller of the present invention and a conventional high-load type deep groove type ball bearing. FIGS. 7 and 8 are ball rollers of the present invention and the conventional deep groove type ball bearing. It is a comparative example with a bearing. Fig. 5
(C), as shown in FIG. 7 (C), the inner ring 13 is eccentric and inscribed in the inner circumference of the outer ring 14, and the inner circumference of the outer ring 14
As many ball rollers 1 as possible are mounted in the arc-shaped space between the outer peripheries, and then the inner ring 13 is moved to a position concentric with the outer ring 14 to obtain a ball roller as shown in FIGS. 6 (A) and 8 (A). Align 1 in a row.
【００１３】球ころ１の長径（端面球面部３，３の頂点
間の距離）と同一径の玉の場合（図５（Ｂ），図５
（Ｄ），図６（Ｂ）；図７（Ｂ），図７（Ｄ），図８
（Ｂ）参照）と比較すると、球ころ１の短径ｄ（転動球
面部４の径）が玉１２０の径ｄ０よりも小径なので、球
ころ１の装着数を多くすることができる。特に、図５
（Ａ）の浅溝タイプの球ころ軸受の内外輪間隔Ｓ（外輪
１４の内径と内輪１３の外径との差）は深溝タイプの玉
軸受の内外輪間隔Ｓ１よりも広く、装着数をより多くで
きる。図７（Ａ）の深溝タイプの球ころ軸受の内外輪間
隔は深溝タイプの玉軸受の内外輪間隔Ｓ１と同じであ
る。図示例の場合には、浅溝タイプの球ころ軸受では、
玉軸受が１３個に対して球ころ１が２３個、深溝タイプ
の球ころ軸受では、一般の玉軸受が１３個に対して球こ
ろ１が１９個と、いずれも約５割以上の多く入る構成と
なっている。球ころ１は玉に対して４倍程度の負荷容量
を有しているので、定格荷重は、浅溝タイプの球ころ軸
受で、単純に計算して、４×２３／１３＝７倍程度、深
溝タイプの球ころ軸受で、４×１９／１３＝５．８倍程
度の増加させることができる。また、スラスト荷重につ
いても、玉軸受と同等以上に受けることができる。な
お、この球ころは、従来の球やころが使用される直線運
動案内装置、転がり軸受、等速ジョイント等の種々の転
がり接触装置全般に広く使用することができる。In the case of a ball having the same diameter as the long diameter of the ball roller 1 (the distance between the vertices of the end face spherical portions 3 and 3) (FIGS. 5B and 5B).
(D), FIG. 6 (B); FIG. 7 (B), FIG. 7 (D), FIG.
Compared with (B), the short diameter d (diameter of the rolling spherical portion 4) of the ball roller 1 is smaller than the diameter d0 of the ball 120, so that the number of mounted ball rollers 1 can be increased. In particular, FIG.
The inner-outer ring interval S (difference between the inner diameter of the outer ring 14 and the outer diameter of the inner ring 13) of the shallow groove type ball roller bearing (A) is wider than the inner and outer ring interval S1 of the deep groove type ball bearing, and the number of mountings is larger. You can do much. The interval between the inner and outer rings of the deep groove type ball bearing of FIG. 7A is the same as the inner and outer ring interval S1 of the deep groove type ball bearing. In the case of the illustrated example, in the case of a shallow groove type ball roller bearing,
In the case of 13 ball bearings, 23 ball rollers 1 are provided, and in the case of deep groove type ball roller bearings, 13 ball bearings are provided, and 19 ball rollers 1 are provided in 13 ball bearings. It has a configuration. Since the ball roller 1 has a load capacity about four times as large as the ball, the rated load is a simple calculation using a shallow groove type ball roller bearing, and 4 × 23/13 = about seven times, With a deep groove type spherical roller bearing, it is possible to increase about 4 × 19/13 = 5.8 times. Also, the thrust load can be received at least equal to that of the ball bearing. The ball roller can be widely used in various rolling contact devices such as a linear motion guide device, a rolling bearing, and a constant velocity joint in which a conventional ball or roller is used.
【００１４】[0014]
【発明の効果】以上説明したように、本発明にあって
は、転動球面部の接触長が長くなるので玉に比べて負荷
容量は数倍大きく、ころには及ばないが、高荷重，高剛
性化を図ることができる。また、転動球面部の中央部と
両端部の径の差が玉に比べて小さいので、差動すべりは
小さく摩擦抵抗が軽減される。従って、玉に比べて軽快
に移動すると共に発熱量も小さい。As described above, in the present invention, since the contact length of the rolling spherical portion is longer, the load capacity is several times larger than that of the ball, and although it is not as good as the rollers, the load is higher. High rigidity can be achieved. Further, since the difference in diameter between the central portion and both ends of the rolling spherical portion is smaller than that of the ball, differential slip is small and frictional resistance is reduced. Therefore, it moves lightly and generates less heat than a ball.
【００１５】また、本発明の球ころは、従来のころと異
なり、転動球面部が円弧形状で軸方向にずれないので軸
方向への移動を規制するつば部は不要である。また、軽
いスラスト荷重の場合には転動球面部のみで左右両方向
のスラスト荷重を受けることが可能である。多少大きい
スラスト荷重を必要とする場合には、内外の軌道輪に設
けられる軌道溝に端面球面部の一部が接触できるように
深溝タイプにすればよい。端面球面部は平坦なローラ端
面のようにすべり接触ではなく転がりすべり接触なので
摩擦抵抗が少なく、発熱も少ない。球ころの長径（端面
球面部の頂点間の距離）と同一径の玉と比較すると、ベ
アリングに組み込む場合には、球ころの短径（転動球面
部の径）が玉よりも小径なので、球ころの装着数が多く
なり、定格荷重が大きくなる。また、軌道輪の軌道溝を
球ころの転動球面部の曲率半径より多少大きくしておく
ことにより、潤滑剤が軌道溝に入り易く、接触面も面接
触で油切れも生じにくいので、良好な潤滑が維持され摩
耗が防止される。また、発熱も少なく焼き付くおそれも
ない。軌道溝を深溝として端面球面部が一部接触する場
合でも、軌道溝と端面球面部が面接触で接触面間に潤滑
剤が入りやすく、摩耗，焼き付きを防止することができ
る。Further, unlike the conventional roller, the spherical roller of the present invention does not require a flange portion for restricting the axial movement since the rolling spherical portion has a circular arc shape and does not shift in the axial direction. In the case of a light thrust load, the thrust load in both the left and right directions can be received only by the rolling spherical surface portion. If a somewhat large thrust load is required, a deep groove type may be used so that a part of the spherical surface of the end face can contact the raceway grooves provided on the inner and outer races. Unlike the flat roller end surface, the end surface spherical portion is not in sliding contact but is in rolling sliding contact, so that the frictional resistance is small and the heat generation is small. Compared to a ball with the same diameter as the long diameter of the ball roller (the distance between the vertices of the spherical surface of the end face), when incorporated in a bearing, the short diameter of the ball roller (the diameter of the rolling spherical part) is smaller than the ball. The number of mounted ball rollers increases, and the rated load increases. Also, by making the raceway groove of the raceway ring slightly larger than the radius of curvature of the rolling spherical portion of the spherical roller, the lubricant is easy to enter the raceway groove, and the contact surface and the surface contact hardly run out of oil. Lubrication is maintained and wear is prevented. Also, there is little heat generation and there is no risk of seizure. Even when the raceway groove is a deep groove and the end face spherical surface partly contacts, the raceway groove and the end face spherical surface part are in surface contact, so that lubricant can easily enter between the contact surfaces, and wear and seizure can be prevented.
【００１６】また、本発明の球ころは、軌道溝に対して
は、転動球面部が円弧状なので玉と同様に調心性を有す
る。また、軌道溝を深溝として端面球面部が一部接触す
る場合でも、端面球面部は球面状の接触なので調心性を
有し、軌道溝の傾きを許容でき、玉と同様、軌道輪やハ
ウジング，軸等の相手部品の加工や組立に高い寸法精度
が要求されない。このように、本発明の「球ころ」は、
「玉」と「ころ」の中間的な耐負荷能力と自動調心性を
有し、しかもコストが安く、軸受、直線運動案内装置、
等速ジョイント等の広範な製品群に革新をもたらすもの
である。Further, the spherical roller of the present invention has the same centering property as the ball since the rolling spherical portion is arc-shaped with respect to the raceway groove. In addition, even when the raceway groove is a deep groove and the end surface spherical portion partially contacts, the end surface spherical portion has spherical contact, so that the end surface spherical portion has a centering property, and the inclination of the raceway groove can be tolerated. High dimensional accuracy is not required for machining and assembling of mating parts such as shafts. Thus, the "ball roller" of the present invention is:
It has an intermediate load-bearing capacity and self-alignment between "ball" and "roller", and is low in cost.
It brings innovation to a wide range of products such as constant velocity joints.
【図面の簡単な説明】[Brief description of the drawings]
【図１】図１は本発明の実施の形態に係る球ころを示す
もので、同図（Ａ），（Ｂ），（Ｃ）は長径に対する短
径の割合が８０％、同図（Ｄ），（Ｅ），（Ｆ）は９０
％の球ころのそれぞれ正面図，平面図および側面図であ
る。FIG. 1 shows a spherical roller according to an embodiment of the present invention. FIGS. 1 (A), 1 (B) and 1 (C) show a ratio of a minor axis to a major axis of 80%, and FIG. ), (E) and (F) are 90
3 is a front view, a plan view, and a side view, respectively, of the% roller. FIG.
【図２】図２は本発明の転動球面部をテーパ形状とした
球ころを示すもので、同図（Ａ）は正面図、同図（Ｂ）
は側面図である。FIG. 2 shows a spherical roller in which the rolling spherical surface portion of the present invention has a tapered shape. FIG. 2 (A) is a front view and FIG. 2 (B).
Is a side view.
【図３】図３（Ａ）〜（Ｃ）は本発明の球ころの製造手
順を示す図である。FIGS. 3 (A) to 3 (C) are diagrams showing a manufacturing procedure of the spherical roller of the present invention.
【図４】図４（Ａ）は本発明の球ころの軌道溝との接触
状態を示す説明図、図４（Ｂ）は本発明の球ころの軌道
溝を深溝タイプとした状態の説明図、図４（Ｃ）は従来
のころの軌道面との接触状態を示す図である。4 (A) is an explanatory view showing a contact state of a ball roller of the present invention with a raceway groove, and FIG. 4 (B) is an explanatory view of a state where the raceway groove of the present invention is a deep groove type. FIG. 4C is a view showing a state of contact with a raceway surface of a conventional roller.
【図５】図５は深溝タイプのベアリングの球ころと玉の
装着例を比較して示すもので、同図（Ａ）は球ころを用
いたベアリングの断面図、同図（Ｃ）は球ころの組込説
明図、同図（Ｂ）は玉を用いたベアリングの断面図、同
図（Ｄ）は玉の組込説明図である。5A and 5B show a comparison between an example of mounting a ball and a ball of a deep groove type bearing. FIG. 5A is a sectional view of a bearing using the ball roller, and FIG. FIG. 4B is a sectional view of a bearing using balls, and FIG. 4D is a sectional view of incorporating the balls.
【図６】図６（Ａ）は図５（Ａ）の球ころを用いたベア
リングの平面図、同図（Ｂ）は図５（Ｂ）の玉を用いた
ベアリングの平面図である。6 (A) is a plan view of a bearing using the ball roller of FIG. 5 (A), and FIG. 6 (B) is a plan view of a bearing using the ball of FIG. 5 (B).
【図７】図７は深溝タイプのベアリングの球ころと玉の
装着例を比較して示すもので、同図（Ａ）は球ころを用
いたベアリングの断面図、同図（Ｃ）は球ころの組込説
明図、同図（Ｂ）は玉を用いたベアリングの断面図、同
図（Ｄ）は玉の組込説明図である。FIGS. 7A and 7B show a comparison between an example of mounting a ball and a ball of a deep groove type bearing. FIG. 7A is a cross-sectional view of a bearing using the ball roller, and FIG. FIG. 4B is a sectional view of a bearing using balls, and FIG. 4D is a sectional view of incorporating the balls.
【図８】図８（Ａ）は図７（Ａ）の球ころを用いたベア
リングの平面図、同図（Ｂ）は図７（Ｂ）の玉を用いた
ベアリングの平面図である。8 (A) is a plan view of a bearing using the ball roller of FIG. 7 (A), and FIG. 8 (B) is a plan view of a bearing using the ball of FIG. 7 (B).
１ 球ころ ２ 転動球面部 ３ 端面球面部 ４ 球面 １０ 軌道面 １１ 端面保持面 ２０ 鋼球 ３０ 素材 Ｎ 回転中心線 Ｒ 曲率半径（転動球面部） ｒ１，ｒ２ 曲率半径（端面球面部） Ｏ１，Ｏ２ 曲率中心（端面球面部） Ｗ 長径（端面球面部の頂点間長さ） ｄ 短径（転動球面部の最大） DESCRIPTION OF SYMBOLS 1 Ball roller 2 Rolling spherical surface part 3 End spherical surface part 4 Spherical surface 10 Orbital surface 11 End surface holding surface 20 Steel ball 30 Material N Rotation center line R Curvature radius (Rolling spherical surface portion) r1, r2 Curvature radius (End surface spherical surface portion) O1 , O2 Center of curvature (spherical surface at end face) W Long diameter (length between vertices of spherical surface at end face) d Minor diameter (maximum at rolling spherical part)
Claims (1)
球面部両端の球面状に膨らんだ端面球面部と、を備え、 前記転動球面部の曲率半径が端面球面部の曲率半径より
も大きく、前記転動球面部の回転中心線上に前記端面球
面部の曲率中心を持ち、前記転動球面部の最大径と端面
球面部の頂点間の長さの比率を略８０％±１７％の範囲
とした形状の球ころ。1. A rolling spherical portion bulging in an arc shape, and a spherical end surface sphere bulging at both ends of the rolling spherical portion, wherein a radius of curvature of the rolling spherical portion is a curvature of the spherical end surface portion. A center of curvature of the end surface spherical portion on the rotation center line of the rolling spherical portion, and a ratio of a maximum diameter of the rolling spherical portion to a length between vertexes of the end surface spherical portion is approximately 80% ± 17% spherical roller.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001180873A JP2002339977A (en) | 2001-05-11 | 2001-05-11 | Spherical roller |
| US10/120,636 US6896414B2 (en) | 2000-01-25 | 2002-04-11 | Ball roller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001180873A JP2002339977A (en) | 2001-05-11 | 2001-05-11 | Spherical roller |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002339977A true JP2002339977A (en) | 2002-11-27 |
Family
ID=19021223
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001180873A Pending JP2002339977A (en) | 2000-01-25 | 2001-05-11 | Spherical roller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002339977A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004092603A1 (en) * | 2003-04-16 | 2004-10-28 | Nsk Ltd. | Roller bearing for belt-type stepless speed changer |
| JP2010014154A (en) * | 2008-07-01 | 2010-01-21 | Ntn Corp | Bearing roller, bearing and bearing roller processing method |
| CN108757737A (en) * | 2018-08-10 | 2018-11-06 | 江苏天驰轴承有限公司 | A kind of bearing and its fusiform rolling element |
-
2001
- 2001-05-11 JP JP2001180873A patent/JP2002339977A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004092603A1 (en) * | 2003-04-16 | 2004-10-28 | Nsk Ltd. | Roller bearing for belt-type stepless speed changer |
| US7488113B2 (en) | 2003-04-16 | 2009-02-10 | Nsk Ltd. | Roller bearing for belt-type stepless speed changer |
| JP2010014154A (en) * | 2008-07-01 | 2010-01-21 | Ntn Corp | Bearing roller, bearing and bearing roller processing method |
| CN108757737A (en) * | 2018-08-10 | 2018-11-06 | 江苏天驰轴承有限公司 | A kind of bearing and its fusiform rolling element |
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