JP2007024139A - Roller bearing - Google Patents

Roller bearing Download PDF

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JP2007024139A
JP2007024139A JP2005205720A JP2005205720A JP2007024139A JP 2007024139 A JP2007024139 A JP 2007024139A JP 2005205720 A JP2005205720 A JP 2005205720A JP 2005205720 A JP2005205720 A JP 2005205720A JP 2007024139 A JP2007024139 A JP 2007024139A
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Prior art keywords
rolling surface
spacer
ring rolling
bearing
inner ring
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JP2005205720A
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JP4470826B2 (en
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Kenji Sunahara
賢治 砂原
Mitsuaki Ikeda
満昭 池田
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Yaskawa Electric Corp
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Yaskawa Electric Corp
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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/361—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers
    • F16C19/362—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers the rollers being crossed within the single row
    • 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
    • F16C19/40—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 with loose spacing bodies between the 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
    • F16C33/3713—Loose spacing bodies with other rolling elements serving as spacing bodies, e.g. the spacing bodies are in rolling contact with the load carrying 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 provide a roller bearing having a longer life without causing the skewing of rollers. <P>SOLUTION: The roller bearing comprises an inner ring 1 having an inner ring rolling surface 3, an outer ring 2 having an outer ring rolling surface 4, a plurality of columnar rollers 6 held between the inner ring rolling surface 3 and the outer ring rolling surface 4, and a plurality of spherical spacers 5a, 5b, 5c mounted between the adjacent rollers 6B. The diameter of the spacer is determined depending on a distance from the rotational center of the bearing to the spacer. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、スキューが発生せず長寿命のころ軸受に関する。   The present invention relates to a long-life roller bearing that does not generate skew.

従来のころ軸受について図３を用いて説明する。図３は円環状をした従来のころ軸受の略断面図であり、回転中心軸を含む平面で内輪と外輪を切断したときの上側部分の図である。図に示すころ軸受は内輪１と外輪２、スペーサ５、円柱状のころ６から構成されている。内輪１は、外周にＶ字状の溝が形成されており、溝の２つの内輪転走面３が９０度の角度をなして形成されている。左右の２つの部材を合せて構成された外輪２は、内周にＶ字状の溝が形成されており、溝の２つの外輪転走面４が９０度の角度をなして形成されている。そして内輪転走面３と外輪転走面４が向かい合うように内輪１の外側に外輪２が配置されている。図３に図示している円柱状のころ６の外周面は内輪転走面３の左側の面と外輪転走面４の右側の面に接触しており、円柱状のころ６の両端面は内輪転走面３の右側の面および外輪転走面４の左側の面と空隙を介して対向している。図３に示しているころ６に隣接するころ、すなわち紙面の手前側と向こう側にある図示しないころ６は、その外周面が内輪転走面３の右側の面と外輪転走面４の左側の面に接触しており、両端面が内輪転走面３の左側の面および外輪転走面４の右側の面と空隙を介して対向している。図３のころ６は垂直方向から右に４５度傾斜しているが、その手前側と向こう側にある図示しないころ６は左に４５度傾斜している。このように、隣同士のころ６の傾斜する方向が９０度異なって配置されており、一般にはクロスローラ軸受と呼ばれている。隣接するころ６の間にはそれぞれスペーサ５が４個ずつ介装されており、２つの内輪転走面３と２つの外輪転走面４によって形成される角、すなわち図３の4箇所の位置に配置されている。内輪と外輪が周方向に相対回転すると、ころ６は接触している転走面を転がり、内輪１と外輪２がガタを生じることなく滑らかに回転する。そのとき、スペーサ５はころ６と内輪転走面３および外輪転走面４と接してころがり、隣り合うころ６同士が接触して摺動することを防いでおり、異常摩耗が生じないようになっている（例えば特許文献１参照）。
特開２００３−３０１８５１ A conventional roller bearing will be described with reference to FIG. FIG. 3 is a schematic cross-sectional view of a conventional roller bearing having an annular shape, and is a view of an upper portion when the inner ring and the outer ring are cut along a plane including the rotation center axis. The roller bearing shown in the figure includes an inner ring 1, an outer ring 2, a spacer 5, and a cylindrical roller 6. The inner ring 1 has a V-shaped groove formed on the outer periphery, and two inner ring rolling surfaces 3 of the groove are formed at an angle of 90 degrees. The outer ring 2 configured by combining the left and right members is formed with a V-shaped groove on the inner periphery, and the two outer ring rolling surfaces 4 of the groove are formed at an angle of 90 degrees. . And the outer ring | wheel 2 is arrange | positioned on the outer side of the inner ring | wheel 1 so that the inner ring | wheel rolling surface 3 and the outer ring rolling surface 4 may face each other. The outer peripheral surface of the cylindrical roller 6 shown in FIG. 3 is in contact with the left side surface of the inner ring rolling surface 3 and the right side surface of the outer ring rolling surface 4, and both end surfaces of the cylindrical roller 6 are It faces the right side surface of the inner ring rolling surface 3 and the left side surface of the outer ring rolling surface 4 through a gap. A roller adjacent to the roller 6 shown in FIG. 3, that is, the roller 6 (not shown) on the front side and the other side of the paper surface, has an outer peripheral surface on the right side of the inner ring rolling surface 3 and a left side of the outer ring rolling surface 4. Both end surfaces are opposed to the left side surface of the inner ring rolling surface 3 and the right side surface of the outer ring rolling surface 4 via a gap. The roller 6 in FIG. 3 is inclined 45 degrees to the right from the vertical direction, but the roller 6 (not shown) on the near side and the other side is inclined 45 degrees to the left. In this way, the directions in which the adjacent rollers 6 incline differ by 90 degrees, and are generally called cross roller bearings. Four spacers 5 are interposed between the adjacent rollers 6, and the corners formed by the two inner ring rolling surfaces 3 and the two outer ring rolling surfaces 4, that is, four positions in FIG. 3. Is arranged. When the inner ring and the outer ring rotate relative to each other in the circumferential direction, the roller 6 rolls on the contact rolling surface, and the inner ring 1 and the outer ring 2 rotate smoothly without causing play. At that time, the spacer 5 rolls in contact with the roller 6, the inner ring rolling surface 3 and the outer ring rolling surface 4, and prevents the adjacent rollers 6 from coming into contact with each other to prevent abnormal wear. (For example, refer to Patent Document 1).
JP2003-301851

ところが従来技術によると、隣り合うころ同士の周方向の距離は、外周側が内周側より長くなっているにもかかわらず、スペーサ５の直径が４個とも同じであるため、外周側ではころとスペーサの間にクリアランスが存在しており、内輪と外輪が相対回転したときにころにスキュー（揺れ）が生じることがあった。このため、ころが転走面に対してやや傾いて転がることになり、それによって軸受寿命を短くしているという問題があった。
そこで本発明は、そのようなころのスキューが発生せず、長寿命のころ軸受を提供することを目的とする。 However, according to the prior art, the circumferential distance between adjacent rollers is the same for all four spacers 5 even though the outer peripheral side is longer than the inner peripheral side. There is a clearance between the spacers, and when the inner ring and the outer ring rotate relative to each other, the roller may be skewed. For this reason, there is a problem that the roller rolls with a slight inclination with respect to the rolling surface, thereby shortening the bearing life.
Therefore, an object of the present invention is to provide a roller bearing that does not cause such roller skew and has a long life.

上記問題を解決するため、第１の発明は、Ｖ字型の内輪転走面が形成された内輪と、Ｖ字型の外輪転走面が形成された外輪と、前記内輪転走面と前記外輪転走面で挟まれて向きが交互に９０度異なる円柱状の複数のころと、隣り合う前記ころの間に各々４個介装された球状の複数のスペーサからなるころ軸受において、軸受の回転中心に近いスペーサの直径より軸受の回転中心より遠いスペーサの直径が大きいことを特徴としている。
また第２の発明は、軸受の回転中心に近いスペーサは内輪転走面の２つの面と２つのころに接しており、軸受の回転中心から遠いスペーサは外輪転走面の２つの面と２つのころに接しており、残りのスペーサは内輪転走面の１つの面と外輪転走面の１つの面と２つのころに接していることを特徴としている。 In order to solve the above problem, the first invention includes an inner ring formed with a V-shaped inner ring rolling surface, an outer ring formed with a V-shaped outer ring rolling surface, the inner ring rolling surface, In a roller bearing comprising a plurality of cylindrical rollers sandwiched between outer ring rolling surfaces and different in orientation by 90 degrees alternately, and a plurality of spherical spacers interposed between four adjacent rollers, The diameter of the spacer farther from the rotation center of the bearing is larger than the diameter of the spacer near the rotation center.
In the second invention, the spacer near the rotation center of the bearing is in contact with the two surfaces of the inner ring rolling surface and the two rollers, and the spacer far from the rotation center of the bearing is the two surfaces of the outer ring rolling surface and 2 The remaining spacers are in contact with one roller, and the remaining spacers are in contact with one surface of the inner ring rolling surface, one surface of the outer ring rolling surface, and two rollers.

第１の発明によると、軸受の回転中心に近いスペーサの直径より軸受の回転中心より遠いスペーサの直径を大きくしているので、スペーサを配置する空間の大きさが軸受の回転中心からスペーサまでの距離によって変っても、ころとスペーサ間のクリアランスがなくなり、スキューの発生を防止して軸受の寿命を長くすることができるという効果がある。
第２の発明によると、特にスペーサの全てが内輪転走面と外輪転走面の何れかまたは両方ところの間でクリアランスがなくなるので、スキューの発生を防止して軸受の寿命を長くすることができるという特段の効果がある。 According to the first invention, since the diameter of the spacer farther from the rotation center of the bearing is larger than the diameter of the spacer near the rotation center of the bearing, the size of the space in which the spacer is arranged is from the rotation center of the bearing to the spacer. Even if the distance varies, there is no clearance between the roller and the spacer, and there is an effect that the occurrence of skew can be prevented and the life of the bearing can be extended.
According to the second aspect of the invention, in particular, since all the spacers have no clearance between one or both of the inner ring rolling surface and the outer ring rolling surface, it is possible to prevent the occurrence of skew and prolong the life of the bearing. There is a special effect that can be done.

以下、本発明の実施の形態について図に基づいて説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１、図２は本発明のころ軸受を説明する図であり、図１は図２のＢ−Ｂ’線に沿って内輪と外輪を切り欠いたときに切り欠いた方からみた断面図であり、図２は図１のＡ−Ａ’線に沿って内輪と外輪の一部を切り欠いたときに切り欠いた方からみた側面図である。図１が図３と異なるのは、これらの図面上の４つのスペーサのうち上と下にある２つのスペーサの大きさが異なっている点である。２つのスペーサ５ｂは図３のスペーサ５と同じ大きさであるが、下側のスペーサ５ａ、すなわち内輪転走面３によって形成されたＶ字形の底に当たっているスペーサはスペーサ５ｂよりも小さくなっており、上側のスペーサ５ｃ、すなわち外輪転走面４によって形成されたＶ字形の底に当たっているスペーサはスペーサ５ｂよりも大きくなっている。そのスペーサ５ａの直径はころ６の直径の約３０％，スペーサ５ｂの直径はころ６の直径の約４０％、スペーサ５ｃの直径はころ６の直径の約５０％になっている。このようにスペーサの直径が外周に行くほど大きくなっており、ころ６とスペーサ５の間のクリアランスは、内周側と外周側のいずれにおいても無くなっている。すなわち、軸受が組み立てられた状態では、スペーサ５ａは隣り合う２つのころ６と内輪転走面３の２つの面とで挟まれて隙間なく接しており、スペーサ５ｂは隣り合う２つのころ６と内輪転走面３および外輪転走面４とで挟まれて隙間なく接しており、スペーサ５ｃは隣り合う２つのころ６と外輪転走面４の２つの面とで挟まれて隙間なく接している。
なお、ころ６の材料はＳＵＳ４４０Ｃであり、図３の従来のものと同じになっている。
以上の実施例では隣り合うころ同士が直交して配置されたいわゆるクロスローラ軸受を用いたが、本発明の趣旨によると、隣り合うころ同士の外周側と内周側の周方向の距離の違いを補うようにスペーサの直径を変えていることがポイントであるので、隣り合うころ同士の外周側と内周側の周方向の距離の違いがあるものであればどのような軸受であっても適用することができ、ラジアルころ軸受やスラストころ軸受、円すいころ軸受などに適用しても同様の効果を得ることができる。また本発明は、真空中や高温、低温、放射線下などの過酷な環境下で使われる固体潤滑ころ軸受に適用することができ、さらに真空用モータやロボットの固体潤滑ころ軸受に適用することができる。
ここで本発明により軸受の寿命が延びる効果があることを具体例で比較したので以下に示す。その比較の結果、下記のように寿命の大幅な延長効果が認められ、本発明の効果が大きいことが確かめられた。
（軸受仕様）
軸受の内径=30mm、軸受の外径55mm、軸受の幅10mm
ころの直径=4.00mm、ころの長さ=3.85mm
スペーサ5aの直径=1.20mm、スペーサ5bの直径=1.59mm
スペーサ5cの直径=2.00mm、スペーサ５の直径=1.59mm
スペーサ5a、5b、5c、５の材料（軸受ボール）：SUS440C
（寿命試験の内容）
軸受２個に215Nのアキシャル荷重をかける。
320r/minで回転させる。
モータのトルクをモニタする。
（軸受寿命の判定方法）
モータのトルクが定常時の２倍を越えた時点を軸受寿命とする。
（試験の結果（寿命の比））
従来の軸受の寿命：本発明の軸受の寿命＝１：1.69 1 and 2 are views for explaining a roller bearing according to the present invention. FIG. 1 is a cross-sectional view seen from a notch when an inner ring and an outer ring are notched along the line BB ′ of FIG. FIG. 2 is a side view of the inner ring and the outer ring taken along a line AA ′ in FIG. FIG. 1 differs from FIG. 3 in that the size of the two spacers above and below the four spacers on these drawings is different. The two spacers 5b are the same size as the spacer 5 in FIG. 3, but the lower spacer 5a, that is, the spacer that hits the V-shaped bottom formed by the inner ring rolling surface 3, is smaller than the spacer 5b. The upper spacer 5c, that is, the spacer that hits the V-shaped bottom formed by the outer ring rolling surface 4, is larger than the spacer 5b. The diameter of the spacer 5a is about 30% of the diameter of the roller 6, the diameter of the spacer 5b is about 40% of the diameter of the roller 6, and the diameter of the spacer 5c is about 50% of the diameter of the roller 6. As described above, the diameter of the spacer increases toward the outer periphery, and the clearance between the roller 6 and the spacer 5 is eliminated on both the inner peripheral side and the outer peripheral side. That is, in a state where the bearing is assembled, the spacer 5a is sandwiched between the two adjacent rollers 6 and the two surfaces of the inner ring rolling surface 3 so as to be in contact with each other without any gap, and the spacer 5b is connected to the two adjacent rollers 6 with each other. The spacer 5c is sandwiched between the inner ring rolling surface 3 and the outer ring rolling surface 4 and is in contact with no gap, and the spacer 5c is sandwiched between the two adjacent rollers 6 and the two surfaces of the outer ring rolling surface 4 to be in contact with no gap. Yes.
The material of the roller 6 is SUS440C, which is the same as the conventional one in FIG.
In the above embodiment, a so-called cross roller bearing in which adjacent rollers are arranged orthogonal to each other is used. However, according to the gist of the present invention, the difference in the circumferential distance between the outer peripheral side and the inner peripheral side of adjacent rollers. It is important to change the diameter of the spacer so as to compensate for any bearings, so long as there is a difference in the circumferential distance between the outer peripheral side and the inner peripheral side of adjacent rollers. The same effect can be obtained even when applied to radial roller bearings, thrust roller bearings, tapered roller bearings, and the like. Further, the present invention can be applied to solid lubricated roller bearings used in harsh environments such as in vacuum, high temperature, low temperature, and radiation, and can also be applied to solid lubricated roller bearings for vacuum motors and robots. it can.
Here, the effect of extending the life of the bearing according to the present invention is compared by a specific example, and will be described below. As a result of the comparison, it was confirmed that the effect of the present invention was great as shown in the following, and the effect of extending the lifetime was recognized.
(Bearing specification)
Bearing inner diameter = 30mm, bearing outer diameter 55mm, bearing width 10mm
Roller diameter = 4.00mm, Roller length = 3.85mm
Spacer 5a diameter = 1.20mm, spacer 5b diameter = 1.59mm
Spacer 5c diameter = 2.00mm, spacer 5 diameter = 1.59mm
Spacer 5a, 5b, 5c, 5 material (bearing ball): SUS440C
(Contents of life test)
Apply an axial load of 215N to the two bearings.
Rotate at 320r / min.
Monitor motor torque.
(Bearing life judgment method)
The point in time when the motor torque exceeds twice the steady state is defined as the bearing life.
(Test results (life ratio))
Life of conventional bearing: Life of bearing of the present invention = 1: 1.69

本発明のころ軸受の一部断面図（図２のＢ−Ｂ’断面図）Partial sectional view of the roller bearing of the present invention (B-B 'sectional view of FIG. 2) 本発明のころ軸受の一部破断斜視図（図１のＡ−Ａ’断面図）The partially broken perspective view of the roller bearing of the present invention (A-A 'sectional view of Drawing 1) 従来のころ軸受の一部断面図Partial sectional view of a conventional roller bearing

符号の説明Explanation of symbols

１ 内輪、 ２ 外輪、 ３ 内輪転走面、 ４ 外輪転走面
５ スペーサ、 ６、６Ｂ ころ



1 inner ring, 2 outer ring, 3 inner ring rolling surface, 4 outer ring rolling surface 5 spacer, 6, 6B roller



Claims (2)

Ｖ字型の内輪転走面が形成された内輪と、Ｖ字型の外輪転走面が形成された外輪と、前記内輪転走面と前記外輪転走面で挟まれて向きが交互に９０度異なる円柱状の複数のころと、隣り合う前記ころの間に各々４個介装された球状の複数のスペーサからなるころ軸受において、
軸受の回転中心に近いスペーサの直径より軸受の回転中心より遠いスペーサの直径が大きいことを特徴とするころ軸受。 The inner ring on which the V-shaped inner ring rolling surface is formed, the outer ring on which the V-shaped outer ring rolling surface is formed, and the direction is alternately sandwiched between the inner ring rolling surface and the outer ring rolling surface. In a roller bearing comprising a plurality of cylindrical rollers having different degrees and a plurality of spherical spacers interposed between four adjacent rollers,
A roller bearing characterized in that the diameter of the spacer farther from the center of rotation of the bearing is larger than the diameter of the spacer near the center of rotation of the bearing. 軸受の回転中心に近いスペーサは内輪転走面の２つの面と２つのころに接しており、
軸受の回転中心から遠いスペーサは外輪転走面の２つの面と２つのころに接しており、
残りのスペーサは内輪転走面の１つの面と外輪転走面の１つの面と２つのころに接していることを特徴とする請求項１に記載のころ軸受。 The spacer near the center of rotation of the bearing is in contact with the two surfaces of the inner ring rolling surface and the two rollers.
The spacer far from the center of rotation of the bearing is in contact with the two surfaces of the outer ring rolling surface and the two rollers,
2. The roller bearing according to claim 1, wherein the remaining spacer is in contact with one surface of the inner ring rolling surface, one surface of the outer ring rolling surface, and two rollers.
JP2005205720A 2005-07-14 2005-07-14 Roller bearing Active JP4470826B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011006326A1 (en) * 2011-03-29 2012-10-18 Zf Friedrichshafen Ag Rolling bearing cylindrical rolling bearing has intermediate rolling elements with diameter smaller than rolling diameter of rolling elements, which are arranged in circumferential direction between adjacent rolling elements

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011006326A1 (en) * 2011-03-29 2012-10-18 Zf Friedrichshafen Ag Rolling bearing cylindrical rolling bearing has intermediate rolling elements with diameter smaller than rolling diameter of rolling elements, which are arranged in circumferential direction between adjacent rolling elements

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