JP4497117B2 - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP4497117B2
JP4497117B2 JP2006079072A JP2006079072A JP4497117B2 JP 4497117 B2 JP4497117 B2 JP 4497117B2 JP 2006079072 A JP2006079072 A JP 2006079072A JP 2006079072 A JP2006079072 A JP 2006079072A JP 4497117 B2 JP4497117 B2 JP 4497117B2
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annular groove
inner ring
ring
rolling element
ball
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JP2007255520A (en
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丈晴 浦西
義明 田浦
制 高橋
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JTEKT Corp
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Description

本発明は、転がり軸受に関し、特に、連続鋳造機の駆動ロールや従動ロールを支持する軸受として使用されれば好適な転がり軸受に関する。   The present invention relates to a rolling bearing, and more particularly to a rolling bearing that is suitable for use as a bearing that supports a drive roll and a driven roll of a continuous casting machine.

従来、ラジアル荷重の負荷容量が大きくて、かつ、アキシアル荷重を負荷できる転がり軸受としては、実開平3−119613号公報(特許文献1)に記載されている円筒ころ軸受がある。この円筒ころ軸受の外輪および内輪の夫々の円筒軌道面の両側には、鍔部が形成されており、円筒ころが、外輪および内輪の両方に対して軸方向に移動出来ないようになっている。すなわち、この円筒ころ軸受は、外輪が内輪に対して軸方向に移動不可能になっている。   Conventionally, as a rolling bearing that has a large radial load capacity and that can be loaded with an axial load, there is a cylindrical roller bearing described in Japanese Utility Model Laid-Open No. 3-119613 (Patent Document 1). On both sides of the cylindrical raceway surfaces of the outer ring and the inner ring of this cylindrical roller bearing, flanges are formed so that the cylindrical roller cannot move in the axial direction with respect to both the outer ring and the inner ring. . That is, in this cylindrical roller bearing, the outer ring cannot move in the axial direction with respect to the inner ring.

この円筒ころ軸受は、例えば、外輪が固定されているハウジングに対して内輪が固定されている軸が軸方向に移動するような環境下で、ハウジングと軸との間に配置されるようになっており、上記軸の軸方向の移動に起因して発生するアキシアル荷重を負荷するようになっている。   The cylindrical roller bearing is, for example, arranged between the housing and the shaft in an environment where the shaft on which the inner ring is fixed moves in the axial direction with respect to the housing on which the outer ring is fixed. An axial load generated due to the movement of the shaft in the axial direction is applied.

しかしながら、上記従来の円筒ころ軸受では、外輪および内輪の両方が、夫々の円筒軌道面の両側に鍔部を有しているので、円筒ころ軸受が都合4つもの鍔部を有することになって、円筒ころと鍔部のかじりに起因して鍔部の摩耗が生じ易く軸方向のガタが大きくなり易いという課題がある。
実開平3−119613号公報(第6図)
However, in the conventional cylindrical roller bearing described above, both the outer ring and the inner ring have flanges on both sides of the respective cylindrical raceway surfaces, so that the cylindrical roller bearing conveniently has as many as four flanges. Further, there is a problem in that wear of the flange portion is likely to occur due to the galling between the cylindrical roller and the flange portion, and the axial play tends to be large.
Japanese Utility Model Publication No. 3-119613 (FIG. 6)

そこで、本発明の課題は、ラジアル荷重の負荷容量が大きいと共に、アキシアル荷重を負荷することができる寿命が長い転がり軸受を提供することにある。   SUMMARY OF THE INVENTION An object of the present invention is to provide a rolling bearing having a long life and a large load capacity for radial load and capable of being loaded with an axial load.

上記課題を解決するため、この発明の転がり軸受は、
内周面が複数の円筒面とその複数の円筒面との間の環状溝とからなる外輪と、
外周面が複数の円筒面とその複数の円筒面との間の環状溝とからなる内輪と、
外周面が複数の円筒面とその複数の円筒面との間の環状溝とからなると共に、上記内周面と上記内輪の上記外周面との間に配置された転動体と、
上記外輪の上記環状溝と、上記転動体の上記環状溝との間に配置された複数の第1の玉と、
上記転動体の上記環状溝と、上記内輪の上記環状溝との間に配置された複数の第2の玉と
を備えることを特徴としている。
In order to solve the above problems, the rolling bearing of the present invention is
An outer ring having an inner circumferential surface composed of a plurality of cylindrical surfaces and an annular groove between the plurality of cylindrical surfaces;
An inner ring whose outer peripheral surface is composed of a plurality of cylindrical surfaces and an annular groove between the plurality of cylindrical surfaces;
The outer peripheral surface is composed of a plurality of cylindrical surfaces and an annular groove between the plurality of cylindrical surfaces, and a rolling element disposed between the inner peripheral surface and the outer peripheral surface of the inner ring,
A plurality of first balls disposed between the annular groove of the outer ring and the annular groove of the rolling element;
It is characterized by comprising a plurality of second balls arranged between the annular groove of the rolling element and the annular groove of the inner ring.

上記内周面は、外輪の内周面のうちの面取りされていない部分であり、上記内輪の上記外周面は、内輪の外周面のうちの面取りされていない部分であるものとする。また、上記転動体の上記外周面は、転動体の外周面のうちの面取りされていない部分であるものとする。   The inner peripheral surface is a portion of the inner peripheral surface of the outer ring that is not chamfered, and the outer peripheral surface of the inner ring is a portion of the outer peripheral surface of the inner ring that is not chamfered. Moreover, the said outer peripheral surface of the said rolling element shall be a part which is not chamfered among the outer peripheral surfaces of a rolling element.

本発明によれば、例えば、内輪が軸方向の力を受けた場合、上記内輪が外輪に対して一定距離以上軸方向に移動しようとしても、上記外輪の上記環状溝と、上記転動体の上記環状溝との間に配置された第1の玉が、上記外輪および上記転動体と接触角(第1の玉が荷重を受ける方向と、転がり軸受の中心軸に垂直な平面とのなす角)が鋭角であるような接触をすると共に、上記転動体の上記環状溝と、上記内輪の上記環状溝との間に配置された第2の玉が、上記転動体および上記内輪と接触角(第2の玉が荷重を受ける方向と、転がり軸受の中心軸に垂直な平面とのなす角)が鋭角であるような接触をするから、内輪が外輪に対して一定距離以上移動することがない。したがって、アキシアル荷重を確実に負荷することができる。   According to the present invention, for example, when the inner ring receives axial force, even if the inner ring tries to move in the axial direction over a certain distance with respect to the outer ring, the annular groove of the outer ring and the rolling element The first ball disposed between the annular groove and the contact angle with the outer ring and the rolling element (the angle between the direction in which the first ball receives a load and a plane perpendicular to the central axis of the rolling bearing) The second ball disposed between the annular groove of the rolling element and the annular groove of the inner ring is in contact with the rolling element and the inner ring (first angle). Since the contact between the ball 2 receiving the load and the angle formed by the plane perpendicular to the central axis of the rolling bearing is an acute angle, the inner ring does not move more than a certain distance with respect to the outer ring. Therefore, the axial load can be reliably applied.

また、本発明によれば、上記内外輪が鍔を有していないから、転動体の軸方向の寸法を従来の円筒ころ軸受と比して大きく設定でき、かつ、転動体が、大きなラジアル荷重を負荷できる円筒面に近い形状の外周面を有しているので、従来の円筒ころ軸受と比して負荷できるラジアル荷重が小さくなることがない。   Further, according to the present invention, since the inner and outer rings do not have flanges, the axial dimension of the rolling element can be set larger than that of a conventional cylindrical roller bearing, and the rolling element has a large radial load. Therefore, the radial load that can be loaded is not reduced as compared with the conventional cylindrical roller bearing.

また、本発明によれば、内外輪が鍔を有していないので、アキシアル荷重支持用の転がり軸受の故障の主要な原因である転動体による鍔の摩耗が生じにくく、転がり軸受の寿命を長くすることができる。   In addition, according to the present invention, since the inner and outer rings do not have the flange, the wear of the flange due to the rolling elements, which is a major cause of the failure of the rolling bearing for supporting the axial load, hardly occurs, and the life of the rolling bearing is prolonged. can do.

また、一実施形態の転がり軸受は、上記外輪および上記内輪のうちの少なくとも一方は、上記外輪の軸方向に当接する二つの部材からなり、上記二つの部材の互いに当接する面の延長面は、上記二つの部材で形成された上記環状溝を通る。   Further, the rolling bearing of one embodiment, at least one of the outer ring and the inner ring is composed of two members that are in contact with each other in the axial direction of the outer ring. It passes through the annular groove formed by the two members.

上記実施形態によれば、上記二つの部材の互いに当接する面の延長面が、上記二つの部材で形成された上記環状溝を通るから、上記二つの部材の一方を組み付けて、玉(第1および第2の玉のうちの少なくとも一方)を環状溝に収容した後、上記二つの部材の他方を組み付けることができる。したがって、上記玉(第1および第2の玉のうちの少なくとも一方)を、容易に組み込むことができる。   According to the above embodiment, since the extended surfaces of the surfaces of the two members that contact each other pass through the annular groove formed by the two members, one of the two members is assembled and a ball (first And at least one of the second balls) in the annular groove, the other of the two members can be assembled. Therefore, the above balls (at least one of the first and second balls) can be easily incorporated.

本発明の転がり軸受によれば、内輪が外輪に対して一定距離以上軸方向に移動しようとしても、外輪の環状溝と、転動体の環状溝との間に配置された第1の玉が、外輪および転動体と接触角が鋭角であるような接触をすると共に、転動体の環状溝と、内輪の環状溝との間に配置された第2の玉が、転動体および内輪と接触角が鋭角であるような接触をするから、内輪が外輪に対して一定距離以上軸方向に移動することがなくて、アキシアル荷重を確実に負荷することができる。   According to the rolling bearing of the present invention, the first ball arranged between the annular groove of the outer ring and the annular groove of the rolling element, even if the inner ring tries to move in the axial direction over a certain distance with respect to the outer ring, The outer ring and the rolling element make contact with an acute contact angle, and the second ball arranged between the annular groove of the rolling element and the annular groove of the inner ring has a contact angle with the rolling element and the inner ring. Since contact is made at an acute angle, the inner ring does not move in the axial direction over a certain distance with respect to the outer ring, and an axial load can be reliably applied.

また、本発明の転がり軸受によれば、内外輪が鍔を有していないから、転動体の軸方向の寸法を従来の円筒ころ軸受と比して大きく設定でき、かつ、転動体が、大きなラジアル荷重を負荷できる円筒面に近い形状の外周面を有しているので、従来の円筒ころ軸受と比して負荷できるラジアル荷重が小さくなることがない。   Further, according to the rolling bearing of the present invention, since the inner and outer rings have no flanges, the axial dimension of the rolling element can be set larger than that of the conventional cylindrical roller bearing, and the rolling element is large. Since the outer peripheral surface has a shape close to a cylindrical surface on which a radial load can be applied, the radial load that can be applied is not reduced as compared with a conventional cylindrical roller bearing.

また、本発明の転がり軸受によれば、内外輪が鍔を有していないので、アキシアル荷重支持用の転がり軸受の故障の主要な原因である転動体による鍔の摩耗が生じにくく、転がり軸受の寿命を長くすることができる。   Further, according to the rolling bearing of the present invention, since the inner and outer rings do not have the flange, the abrasion of the rolling element, which is a major cause of the failure of the rolling bearing for supporting the axial load, hardly occurs. The lifetime can be extended.

以下、本発明を図示の形態により詳細に説明する。   Hereinafter, the present invention will be described in detail with reference to the drawings.

図1は、アキシアル荷重を受けていない状態の本発明の一実施形態の転がり軸受を示す軸方向の模式断面図である。   FIG. 1 is a schematic cross-sectional view in the axial direction showing a rolling bearing according to an embodiment of the present invention in a state where no axial load is received.

この転がり軸受は、図示しない連続鋳造機用従動ロール(以下、従動ロールという)の固定側の端部の外周面に配置され、スラブのラジアル荷重と、従動ロールの熱膨張による伸長に起因するアキシアル荷重とを負荷するようになっている。図1に示すように、この転がり軸受は、外輪1と、内輪2と、調心輪4と、転動体5と、第1の玉7と、第2の玉8とを備える。上記外輪1は、略球面形状の外周面を有する一方、等しい内径を有する二つの円筒面11,12と、この二つの円筒面11,12の間に位置する環状溝14とからなる内周面を有する。上記円筒面11の軸方向の長さと、円筒面12の軸方向の長さとは、略同じになっている。また、上記環状溝14は、略外輪1の周方向に延在している。   This rolling bearing is arranged on the outer peripheral surface of the fixed-side end of a continuous casting machine driven roll (hereinafter referred to as a driven roll) (not shown), and is axial due to the radial load of the slab and the expansion due to the thermal expansion of the driven roll. It is designed to load a load. As shown in FIG. 1, the rolling bearing includes an outer ring 1, an inner ring 2, a centering ring 4, a rolling element 5, a first ball 7, and a second ball 8. The outer ring 1 has a substantially spherical outer peripheral surface, and an inner peripheral surface including two cylindrical surfaces 11 and 12 having an equal inner diameter, and an annular groove 14 positioned between the two cylindrical surfaces 11 and 12. Have The axial length of the cylindrical surface 11 and the axial length of the cylindrical surface 12 are substantially the same. The annular groove 14 extends substantially in the circumferential direction of the outer ring 1.

上記内輪2は、等しい外径を有する二つの円筒面16,17と、この二つの円筒面16,17の間に位置する環状溝18とからなる外周面を有する一方、円筒状の内周面を有している。上記円筒面16の軸方向の長さと、円筒面17の軸方向の長さとは、略同じになっている。上記内輪2は、従動ロールの上記端部の外周面に外嵌されて固定されている。上記内輪2は、軸方向に互いに当接している第1の内輪21と第2の内輪22とからなっている。上記環状溝18は、環状溝18の底が第1の内輪21と第2の内輪22の当接面上に略位置するように、第1の内輪21と第2の内輪22とにまたがるように形成されている。正確には、上記第1の内輪21と第2の内輪22の互いに当接する面の延長面は、第1の内輪21と第2の内輪22とで形成された環状溝18を通るようになっている。   The inner ring 2 has an outer peripheral surface composed of two cylindrical surfaces 16 and 17 having the same outer diameter and an annular groove 18 positioned between the two cylindrical surfaces 16 and 17, while a cylindrical inner peripheral surface. have. The axial length of the cylindrical surface 16 and the axial length of the cylindrical surface 17 are substantially the same. The inner ring 2 is fitted and fixed to the outer peripheral surface of the end of the driven roll. The inner ring 2 includes a first inner ring 21 and a second inner ring 22 that are in contact with each other in the axial direction. The annular groove 18 spans the first inner ring 21 and the second inner ring 22 such that the bottom of the annular groove 18 is substantially positioned on the contact surface between the first inner ring 21 and the second inner ring 22. Is formed. Precisely, the extended surfaces of the surfaces of the first inner ring 21 and the second inner ring 22 that come into contact with each other pass through the annular groove 18 formed by the first inner ring 21 and the second inner ring 22. ing.

上記調心輪4は、略球面形状の内周面を有する一方、円筒状の外周面を有している。上記調心輪4の内周面は外輪1の外周面に当接している。また、上記調心輪4の外周面は、連続鋳造機の軸受箱(図示しない)の内周面に内嵌されて固定されている。   The aligning ring 4 has a substantially spherical inner peripheral surface, and has a cylindrical outer peripheral surface. The inner peripheral surface of the aligning ring 4 is in contact with the outer peripheral surface of the outer ring 1. The outer peripheral surface of the aligning ring 4 is fitted and fixed to the inner peripheral surface of a bearing box (not shown) of the continuous casting machine.

上記転動体5は、略杵形状を有しており、円筒ころの外周面の軸方向の中心を、環状溝が周方向に走っているような形状を有している。詳しくは、上記転動体5は、外径および軸方向の長さが等しい二つの円筒面24,25と、この二つの円筒面24,25の間に位置する環状溝26とからなる外周面を有している。上記転動体5は、その環状溝26が、外輪1の環状溝14と内輪2の環状溝18に径方向に対向するように、外輪1の内周面と内輪2の外周面との間に配置されている。   The rolling element 5 has a substantially bowl shape, and has a shape in which an annular groove runs in the circumferential direction at the axial center of the outer peripheral surface of the cylindrical roller. Specifically, the rolling element 5 has an outer peripheral surface composed of two cylindrical surfaces 24 and 25 having the same outer diameter and axial length, and an annular groove 26 positioned between the two cylindrical surfaces 24 and 25. Have. The rolling element 5 has an annular groove 26 between the inner peripheral surface of the outer ring 1 and the outer peripheral surface of the inner ring 2 such that the annular groove 26 radially faces the annular groove 14 of the outer ring 1 and the annular groove 18 of the inner ring 2. Has been placed.

上記第1の玉7は、外輪1の環状溝14と転動体5の環状溝26との間に、略周方向の全域に亘って配置されており、第2の玉8は、転動体5の環状溝26と内輪2の環状溝18との間に、略周方向の全域に亘って配置されている。なお、図1では、作用を解り易くするために外輪1の環状溝14と第1の玉7との間のすきま、および、転動体5の環状溝26と第2の玉8との間のすきまを大きく記載している。   The first ball 7 is disposed over the entire area in the circumferential direction between the annular groove 14 of the outer ring 1 and the annular groove 26 of the rolling element 5, and the second ball 8 is composed of the rolling element 5. The annular groove 26 and the annular groove 18 of the inner ring 2 are disposed over the entire area in the circumferential direction. In FIG. 1, the clearance between the annular groove 14 of the outer ring 1 and the first ball 7 and the gap between the annular groove 26 of the rolling element 5 and the second ball 8 are shown in order to facilitate understanding of the action. The clearance is indicated largely.

この転がり軸受は、従動ロールに撓みが生じた場合には、外輪1が調心輪4に対して調心移動して傾斜することにより、従動ロールの撓みを吸収するようになっている。また、後に詳述するように、この転がり軸受は、従動ロールの熱膨張による従動ロールの伸長に起因するアキシアル荷重を負荷するようになっている。   This rolling bearing absorbs the bending of the driven roll by tilting the outer ring 1 with respect to the aligning ring 4 when the driven roll is bent. Further, as will be described in detail later, the rolling bearing is adapted to load an axial load resulting from extension of the driven roll due to thermal expansion of the driven roll.

図2は、上記転動体5と第1の玉7と第2の玉8との位置関係を示す図であり、転がり軸受の一部における転動体5と第1の玉7と第2の玉8とを軸方向から見た図である。また、図3は、転がり軸受の一部における転動体5と第1の玉7との位置関係を示す斜視図である。   FIG. 2 is a diagram showing a positional relationship among the rolling element 5, the first ball 7, and the second ball 8, and the rolling element 5, the first ball 7, and the second ball in a part of the rolling bearing. FIG. 8 is a view of FIG. FIG. 3 is a perspective view showing the positional relationship between the rolling elements 5 and the first balls 7 in a part of the rolling bearing.

図2および図3に示すように、外輪1と転動体5の間に配置された第1の玉7および転動体5と内輪2との間に配置された第2の玉8の夫々は、その両側に位置する第1の玉7または第2の玉8の両方と略接触した状態になっている。また、上記第1の玉7の直径は、外輪1の環状溝14の深さよりも大きくなっており、第2の玉8の直径は、内輪1の環状溝18の深さよりも大きくなっている。このことから、上記外輪1と転動体5との間に配置された第1の玉7の一部が、転動体5の径方向の外方に位置すると共に、転動体5と内輪2との間に配置された第2の玉8の一部が、内輪2の径方向の外方に位置している。   As shown in FIGS. 2 and 3, the first ball 7 disposed between the outer ring 1 and the rolling element 5 and the second ball 8 disposed between the rolling element 5 and the inner ring 2 are respectively It is in a state of being substantially in contact with both the first ball 7 or the second ball 8 located on both sides thereof. Further, the diameter of the first ball 7 is larger than the depth of the annular groove 14 of the outer ring 1, and the diameter of the second ball 8 is larger than the depth of the annular groove 18 of the inner ring 1. . From this, a part of the first ball 7 disposed between the outer ring 1 and the rolling element 5 is located outward in the radial direction of the rolling element 5, and the rolling element 5 and the inner ring 2 A part of the second ball 8 disposed therebetween is located outward in the radial direction of the inner ring 2.

図4は、アキシアル荷重を受けている状態の上記実施形態の転がり軸受を示す軸方向の模式断面図である。   FIG. 4 is a schematic cross-sectional view in the axial direction showing the rolling bearing of the above-described embodiment in a state of receiving an axial load.

図4は、内輪2が従動ロールから矢印Aで示す軸方向の力を受けている場合を示している。内輪2が上記力を受けて矢印A方向に移動すると、内輪2の環状溝18と転動体5の環状溝26とで重なっている部分の軸方向の距離が小さくなって、環状溝26と環状溝18との間に配置された第2の玉8が、環状溝26および環状溝18と接触角(第2の玉8が荷重を受ける方向と、転がり軸受の中心軸に垂直な平面とのなす角)が鋭角の接触を行う。そして、環状溝26と環状溝18との間に配置された第2の玉8を介して、転動体5が内輪2の移動方向、すなわち、矢印A方向に移動する。すると、軸方向に移動できないようになっている外輪1の環状溝14と、転動体5の環状溝26とで重なっている部分の軸方向の距離が小さくなって、環状溝14と環状溝26との間に配置された第1の玉7が、環状溝14および環状溝26と接触角(第1の玉7が荷重を受ける方向と、転がり軸受の中心軸に垂直な平面とのなす角)が鋭角の接触を行い、転動体5が矢印A方向に移動できなくなる。このようにして、環状溝14と環状溝26に間に配置された第1の玉7と、環状溝26と環状溝18の間に配置された第2の玉8とを介して、外輪1に対する内輪2のA方向への移動が一定距離内に制限される。この転がり軸受は、このような機構でアキシアル荷重を負荷するようになっている。   FIG. 4 shows a case where the inner ring 2 receives an axial force indicated by an arrow A from the driven roll. When the inner ring 2 receives the above force and moves in the direction of arrow A, the axial distance between the overlapping portions of the annular groove 18 of the inner ring 2 and the annular groove 26 of the rolling element 5 decreases, and the annular groove 26 and the annular ring 26 The second ball 8 disposed between the groove 18 and the annular groove 26 and the annular groove 18 has a contact angle (a direction in which the second ball 8 receives a load and a plane perpendicular to the center axis of the rolling bearing). The contact angle is an acute angle. And the rolling element 5 moves to the moving direction of the inner ring | wheel 2, ie, the arrow A direction, via the 2nd ball | bowl 8 arrange | positioned between the annular groove 26 and the annular groove 18. FIG. As a result, the axial distance between the overlapping portions of the annular groove 14 of the outer ring 1 that cannot be moved in the axial direction and the annular groove 26 of the rolling element 5 is reduced, and the annular groove 14 and the annular groove 26 are reduced. Between the annular groove 14 and the annular groove 26 and the contact angle (the angle formed between the direction in which the first ball 7 receives a load and a plane perpendicular to the central axis of the rolling bearing). ) Makes an acute contact, and the rolling element 5 cannot move in the direction of arrow A. In this way, the outer ring 1 is interposed via the first ball 7 disposed between the annular groove 14 and the annular groove 26 and the second ball 8 disposed between the annular groove 26 and the annular groove 18. The movement of the inner ring 2 in the direction A with respect to is restricted within a certain distance. This rolling bearing is designed to apply an axial load by such a mechanism.

上記実施形態の転がり軸受によれば、例えば、内輪2が軸方向の力を受けた場合、内輪2が外輪1に対して一定距離以上軸方向に移動しようとしても、外輪1の環状溝14と、転動体5の環状溝26との間に配置された第1の玉7が、外輪1および転動体5と接触角が鋭角であるような接触をすると共に、転動体5の環状溝26と、内輪2の環状溝18との間に配置された第2の玉8が、転動体5および内輪2と接触角が鋭角であるような接触をするから、内輪2が外輪1に対して一定距離以上軸方向に移動することがない。したがって、アキシアル荷重を確実に負荷することができる。   According to the rolling bearing of the above embodiment, for example, when the inner ring 2 receives an axial force, even if the inner ring 2 tries to move in the axial direction over a certain distance with respect to the outer ring 1, The first ball 7 arranged between the rolling element 5 and the annular groove 26 makes contact with the outer ring 1 and the rolling element 5 such that the contact angle is an acute angle, and the annular groove 26 of the rolling element 5. Since the second ball 8 disposed between the annular ring 18 of the inner ring 2 makes contact with the rolling element 5 and the inner ring 2 such that the contact angle is an acute angle, the inner ring 2 is constant with respect to the outer ring 1. It does not move in the axial direction beyond the distance. Therefore, the axial load can be reliably applied.

また、上記実施形態の転がり軸受によれば、内外輪1,2が鍔を有していないから、転動体5の軸方向の寸法を従来の円筒ころ軸受と比して大きく設定でき、かつ、転動体5が、大きなラジアル荷重を負荷できる円筒面に近い形状の外周面を有しているので、従来の円筒ころ軸受と比して負荷できるラジアル荷重が小さくなることがない。   Further, according to the rolling bearing of the above embodiment, since the inner and outer rings 1 and 2 do not have flanges, the axial dimension of the rolling element 5 can be set larger than that of a conventional cylindrical roller bearing, and Since the rolling element 5 has an outer peripheral surface having a shape close to a cylindrical surface on which a large radial load can be applied, the radial load that can be applied is not reduced as compared with a conventional cylindrical roller bearing.

また、上記実施形態の転がり軸受によれば、内外輪1,2が鍔を有していないので、アキシアル荷重支持用の転がり軸受の故障の主要な原因である転動体5による鍔の摩耗が生じにくく、転がり軸受の寿命を長くすることができる。   Further, according to the rolling bearing of the above embodiment, since the inner and outer rings 1 and 2 do not have the flange, wear of the flange due to the rolling element 5 which is a major cause of the failure of the rolling bearing for supporting the axial load occurs. It is difficult to extend the life of the rolling bearing.

また、上記実施形態の転がり軸受によれば、内輪2が、第1の内輪21と第2の内輪22とからなり、かつ、第1の内輪21と第2の内輪22の当接面の延長面が、内輪2の環状溝18を通過しているので、第1の内輪21と第2の内輪22とのうちの一方を組み付けて、第2の玉8を環状溝18に収容した後、第1の内輪21と第2の内輪22とのうちの他方を組み付けることができる。したがって、上記第2の玉8を、容易に組み込むことができる。   Further, according to the rolling bearing of the above embodiment, the inner ring 2 is composed of the first inner ring 21 and the second inner ring 22, and the contact surface between the first inner ring 21 and the second inner ring 22 is extended. Since the surface passes through the annular groove 18 of the inner ring 2, after assembling one of the first inner ring 21 and the second inner ring 22 and accommodating the second ball 8 in the annular groove 18, The other of the first inner ring 21 and the second inner ring 22 can be assembled. Therefore, the second ball 8 can be easily incorporated.

尚、上記実施形態の転がり軸受では、外輪1の外周面が球面形状で、外輪1の径方向の外方に調心輪4を有していたが、この発明では、外輪の外周面が円筒形状で、調心輪を有していなくても良い。また、この場合、外輪を、軸方向に互いに当接する二つの部材で構成すると共に、二つの部材の当接面の延長面上に環状溝を形成しても良く、このようにして、第1の玉を所定位置に組み込み易くしても良い。   In the rolling bearing of the above embodiment, the outer peripheral surface of the outer ring 1 has a spherical shape and has the aligning ring 4 on the outer side in the radial direction of the outer ring 1, but in this invention, the outer peripheral surface of the outer ring is cylindrical. The shape does not have to have a centering ring. In this case, the outer ring may be formed of two members that are in contact with each other in the axial direction, and an annular groove may be formed on the extended surface of the contact surface of the two members. The ball may be easily incorporated into a predetermined position.

また、上記実施形態の転がり軸受では、全ての第1の玉7が、その両側の二つの第1の玉7と略接触し、かつ、全ての第2の玉8が、その両側の二つの第2の玉8と略接触するようになっていたが、この発明では、全ての玉が、その両側の二つの玉と接触する必要はない。すなわち、第1の玉は、外輪の溝と転動体の溝との間に、仕様に応じた数(複数個)だけ配置されると共に、第2の玉は、転動体の溝と内輪の溝との間に、仕様に応じた数(複数個)だけ配置されれば良い。   Moreover, in the rolling bearing of the said embodiment, all the 1st balls 7 substantially contact with the two 1st balls 7 of the both sides, and all the 2nd balls 8 are the two of the both sides. Although it has come to come into substantial contact with the second ball 8, in the present invention, it is not necessary for all balls to be in contact with the two balls on both sides thereof. That is, the first ball is arranged between the groove of the outer ring and the groove of the rolling element in the number (plural) according to the specification, and the second ball is the groove of the rolling element and the groove of the inner ring. The number (plural) according to the specification may be arranged between the two.

また、上記実施形態の転がり軸受では、内外輪および転動体1,2,5の夫々は、二つの円筒面11,12,16,17,24,25と、一つの環状溝14,18,26とを有していたが、この発明では、内外輪および転動体は、三つ以上の円筒面と、その三つ以上の円筒面の間に位置する二つ以上の環状溝とを有していても良い。   In the rolling bearing of the above embodiment, each of the inner and outer rings and the rolling elements 1, 2, 5 has two cylindrical surfaces 11, 12, 16, 17, 24, 25 and one annular groove 14, 18, 26. However, in this invention, the inner and outer rings and the rolling element have three or more cylindrical surfaces and two or more annular grooves positioned between the three or more cylindrical surfaces. May be.

また、上記実施形態の転がり軸受では、図1に示すように、内外輪および転動体1,2,5の溝14,18,26の断面形状が、半円形状であったが、内外輪および転動体の断面形状は、半楕円形状や、皿形状等、半円形状以外の形状であっても良い。   In the rolling bearing of the above embodiment, as shown in FIG. 1, the cross-sectional shapes of the inner and outer rings and the grooves 14, 18 and 26 of the rolling elements 1, 2 and 5 are semicircular, The cross-sectional shape of the rolling element may be a shape other than a semicircular shape such as a semi-elliptical shape or a dish shape.

アキシアル荷重を受けていない状態の本発明の一実施形態の転がり軸受を示す軸方向の模式断面図である。It is a schematic cross section of the axial direction which shows the rolling bearing of one Embodiment of this invention of the state which has not received the axial load. 転動体と第1の玉と第2の玉とを軸方向から見た図である。It is the figure which looked at the rolling element, the 1st ball, and the 2nd ball from the axial direction. 転動体と第1の玉との位置関係を示す斜視図である。It is a perspective view which shows the positional relationship of a rolling element and a 1st ball. アキシアル荷重を受けている状態の上記実施形態の転がり軸受を示す軸方向の模式断面図である。It is a schematic cross section of the axial direction which shows the rolling bearing of the said embodiment of the state which has received the axial load.

符号の説明Explanation of symbols

1 外輪
2 内輪
4 調心輪
5 転動体
7 第1の玉
8 第2の玉
11,12,16,17,24,25 円筒面
14,18,26 環状溝
21 第1の内輪
22 第2の内輪
DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 4 Centering ring 5 Rolling element 7 First ball 8 Second ball 11, 12, 16, 17, 24, 25 Cylindrical surface 14, 18, 26 Annular groove 21 First inner ring 22 Second Inner ring

Claims (2)

内周面が複数の円筒面とその複数の円筒面との間の環状溝とからなる外輪と、
外周面が複数の円筒面とその複数の円筒面との間の環状溝とからなる内輪と、
外周面が複数の円筒面とその複数の円筒面との間の環状溝とからなると共に、上記内周面と上記内輪の上記外周面との間に配置された転動体と、
上記外輪の上記環状溝と、上記転動体の上記環状溝との間に配置された複数の第1の玉と、
上記転動体の上記環状溝と、上記内輪の上記環状溝との間に配置された複数の第2の玉と
を備えることを特徴とする転がり軸受。
An outer ring having an inner circumferential surface composed of a plurality of cylindrical surfaces and an annular groove between the plurality of cylindrical surfaces;
An inner ring whose outer peripheral surface is composed of a plurality of cylindrical surfaces and an annular groove between the plurality of cylindrical surfaces;
The outer peripheral surface is composed of a plurality of cylindrical surfaces and an annular groove between the plurality of cylindrical surfaces, and a rolling element disposed between the inner peripheral surface and the outer peripheral surface of the inner ring,
A plurality of first balls disposed between the annular groove of the outer ring and the annular groove of the rolling element;
A rolling bearing, comprising: a plurality of second balls arranged between the annular groove of the rolling element and the annular groove of the inner ring.
請求項1に記載の転がり軸受において、
上記外輪および上記内輪のうちの少なくとも一方は、上記外輪の軸方向に当接する二つの部材からなり、
上記二つの部材の互いに当接する面の延長面は、上記二つの部材で形成された上記環状溝を通ることを特徴とする転がり軸受。
The rolling bearing according to claim 1,
At least one of the outer ring and the inner ring is composed of two members that abut in the axial direction of the outer ring,
The rolling bearing according to claim 1, wherein an extended surface of the surfaces of the two members contacting each other passes through the annular groove formed by the two members.
JP2006079072A 2006-03-22 2006-03-22 Rolling bearing Expired - Fee Related JP4497117B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106481667A (en) * 2016-12-23 2017-03-08 贵州虹轴轴承有限公司 A kind of Biserial cylindrical roller bearing

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103883617A (en) * 2014-03-10 2014-06-25 苏州捷德瑞精密机械有限公司 Rolling needle and rolling ball combined rolling body for bearing
CN104454982A (en) * 2014-11-22 2015-03-25 江阴方艾机器人有限公司 External aligning bearing convenient to mount

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS443364Y1 (en) * 1964-08-12 1969-02-07
JPS50155442U (en) * 1975-04-03 1975-12-23
JPS5624219A (en) * 1979-08-01 1981-03-07 Accurate Bushing Co Bearing loaded radial and axial force
JPS6376909A (en) * 1986-09-17 1988-04-07 Shigeru Yoshida Stepped bearing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS443364Y1 (en) * 1964-08-12 1969-02-07
JPS50155442U (en) * 1975-04-03 1975-12-23
JPS5624219A (en) * 1979-08-01 1981-03-07 Accurate Bushing Co Bearing loaded radial and axial force
JPS6376909A (en) * 1986-09-17 1988-04-07 Shigeru Yoshida Stepped bearing

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106481667A (en) * 2016-12-23 2017-03-08 贵州虹轴轴承有限公司 A kind of Biserial cylindrical roller bearing

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