JP2006077875A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP2006077875A
JP2006077875A JP2004262031A JP2004262031A JP2006077875A JP 2006077875 A JP2006077875 A JP 2006077875A JP 2004262031 A JP2004262031 A JP 2004262031A JP 2004262031 A JP2004262031 A JP 2004262031A JP 2006077875 A JP2006077875 A JP 2006077875A
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rolling
raceway surface
rolling elements
rolling element
auxiliary
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JP4113979B2 (en
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Yasuo Ueno
上野康男
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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
    • F16C33/38—Ball cages
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • 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
    • F16C33/38—Ball cages
    • F16C33/3893—Ball cages with rolling elements with smaller diameter than the load carrying balls, e.g. cages with counter-rotating spacers
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4688—Cages for rollers or needles with rolling elements with smaller diameter than the load carrying rollers, e.g. cages with counter-rotating spacers
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers

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

Abstract

<P>PROBLEM TO BE SOLVED: To solve problems on a conventional rolling bearing being widely used wherein rolling elements and the wall face of a retainer or adjacent rolling elements contact each other to similarly generate intermittent friction force which lowers starting performance to cause a trouble in smooth rotation. <P>SOLUTION: The rolling bearing comprises a first bearing ring having a first raceway surface, a second bearing ring having a second raceway surface, and the plurality of rolling elements to be rotated in contact with the first raceway surface and the second raceway surface. Auxiliary rolling elements are provided between adjacent rolling elements, and the centers of the auxiliary rolling elements are located on a line connecting the centers of the adjacent rolling elements to each other. This construction prevents the generation of intermittent friction force. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、広く一般に使用されるころがり軸受であるが、特に摩擦抵抗の少ないころがり軸受に関するものである。   The present invention relates to a rolling bearing that is widely used in general, and particularly relates to a rolling bearing having a low frictional resistance.

従来、ころがり軸受の転動体は保持器によって等間隔に保持されるか、又は総ボールと称する全周に転動体を配置して保持器を排除したものが有る。 しかし、前者では回転時に転動体とリテーナーの壁面とが接触すると摩擦力が発生する。 又、後者では隣り合う転動体同士が接触することによって同様に摩擦力が発生する。 この摩擦力は断続的に発生するために起動性能を低下し、滑らかな回転を妨げる原因となり得る。   2. Description of the Related Art Conventionally, rolling elements of rolling bearings are either held at regular intervals by a cage, or some rolling elements are arranged around the entire circumference called a total ball and the cage is eliminated. However, in the former, a frictional force is generated when the rolling elements come into contact with the wall surface of the retainer during rotation. In the latter case, frictional force is similarly generated when adjacent rolling elements come into contact with each other. Since this frictional force is generated intermittently, the starting performance is deteriorated, and smooth rotation can be hindered.

この対策として、転動体同士の接触を防止する技術として本出願人が出願した下記特許が認可され効果を上げているが、新たな軌道面の追加により比較的高い製作精度が要求されるために、あまり広く利用されていない。
特許３４５３７０１号 ころがり軸受 As a countermeasure against this, the following patent filed by the present applicant as a technology for preventing contact between rolling elements has been approved and has been effective, but a relatively high manufacturing accuracy is required due to the addition of a new raceway surface. It is not widely used.
Patent No. 3453701 Rolling bearing

本発明は上記特許と同等の効果を持ちながら新たな軌道面を必要とせず、製作が容易なころがり軸受を実現するものである。   The present invention realizes a rolling bearing that has the same effect as the above-mentioned patent, does not require a new raceway surface, and is easy to manufacture.

上記課題を解決するための本発明の手段は、第１の軌道面を有する第１の軌道輪と、第２の軌道面を有する第２の軌道輪と、該第１の軌道面と第２の軌道面に接して回転する複数の転動体を配置してなるころがり軸受において、各々の隣り合う転動体の間に補助転動体を設け、該補助転動体の中心位置を隣り合う転動体の中心を結ぶ直線上に配置したことを特徴とするころがり軸受を提供するものである。   The means of the present invention for solving the above-described problems includes a first raceway having a first raceway surface, a second raceway having a second raceway surface, the first raceway surface and a second raceway surface. In the rolling bearing formed by arranging a plurality of rolling elements rotating in contact with the raceway surface, an auxiliary rolling element is provided between each adjacent rolling element, and the center position of the auxiliary rolling element is set to the center of the adjacent rolling element. The present invention provides a rolling bearing characterized by being arranged on a straight line connecting the two.

上記手段における実施形態のひとつとして、第１の軌道面と第２の軌道面の断面を円弧状として、転動体を球状としたころがり軸受を提供するものである。   As one embodiment of the above means, there is provided a rolling bearing in which the cross section of the first raceway surface and the second raceway surface is an arc shape and the rolling elements are spherical.

又、上記手段における他の実施形態として、第１の軌道面と第２の軌道面の断面を直線状として、転動体を円筒状としたころがり軸受を提供するものである。   As another embodiment of the above means, there is provided a rolling bearing in which the cross section of the first raceway surface and the second raceway surface is linear and the rolling element is cylindrical.

又、上記手段における補助転動体の実施形態のひとつとしては、補助転動体の形状を球状としたころがり軸受を提供するものである。   Moreover, as one embodiment of the auxiliary rolling element in the above means, a rolling bearing having a spherical shape of the auxiliary rolling element is provided.

又、上記手段における補助転動体の他の実施形態としては、補助転動体の形状を円筒状としたころがり軸受を提供するものである。   Further, as another embodiment of the auxiliary rolling element in the above means, a rolling bearing in which the shape of the auxiliary rolling element is cylindrical is provided.

本発明のころがり軸受は、上記の手段に示すように第１の軌道面を有する第１の軌道輪と、第２の軌道面を有する第２の軌道輪と、該第１の軌道面と第２の軌道面に接して回転する複数の転動体を配置してなるころがり軸受において、各々の隣り合う転動体の間に補助転動体を設け、該補助転動体の中心位置を隣り合う転動体の中心を結ぶ直線上に配置している。   The rolling bearing according to the present invention includes a first race ring having a first raceway surface, a second race ring having a second raceway surface, the first raceway surface and the first raceway surface as shown in the above means. In the rolling bearing formed by arranging a plurality of rolling elements rotating in contact with the raceway surface, an auxiliary rolling element is provided between each adjacent rolling element, and the center position of the auxiliary rolling element is set between the adjacent rolling elements. It is arranged on a straight line connecting the centers.

このように構成することによって、隣り合う転動体の距離が接近した場合、補助転動体に接触すると、補助転動体は転動体と逆方向に回転することでころがり接触状態を保つ。
この場合、隣り合う転動体の中心を結ぶ直線上に補助転動体の中心があるので補助転動体を側方に押し出す力は働かない。 補助転動体の中心がこの直線上からずれたとき保持器によってある程度以上のずれが生じないように支持すれば良い。 この支持力はずれ量が少ないほど小さい。 その支持力の大きさは、ずれ量と隣り合った転動体の中心間距離のとの比に比例する。 仮にこの比が１％ならば、支持力は転動体と補助転動体の接触圧の２％である。 補助転動体は両側から等しい力で押されているので、合計の支持力は２％の２倍で４％となる。このように直に保持器と転動体がすべり接触する従来のタイプに比べて摩擦力を大幅に減少させることが出来る。 By comprising in this way, when the distance of an adjacent rolling element approaches, when it contacts an auxiliary rolling element, an auxiliary rolling element will maintain a rolling contact state by rotating to a reverse direction with a rolling element.
In this case, since the center of the auxiliary rolling element is on the straight line connecting the centers of the adjacent rolling elements, the force for pushing the auxiliary rolling element to the side does not work. What is necessary is just to support so that a shift | offset | difference more than a certain amount may not be produced with a holder | retainer, when the center of an auxiliary | assistant rolling element shift | deviates from this straight line. The supporting force is smaller as the shift amount is smaller. The magnitude of the supporting force is proportional to the ratio between the shift amount and the distance between the centers of the adjacent rolling elements. If this ratio is 1%, the supporting force is 2% of the contact pressure between the rolling element and the auxiliary rolling element. Since the auxiliary rolling element is pushed with equal force from both sides, the total supporting force is doubled to 2% to 4%. Thus, the frictional force can be greatly reduced as compared with the conventional type in which the cage and the rolling element are in sliding contact directly.

上記手段における実施形態のひとつとして、第１の軌道面と第２の軌道面の断面を円弧状として、転動体を球状とした場合は、一般にアンギュラーコンタクト軸受と呼ばれる軸受に実施される場合が多い。 この場合の補助転動体の形状は球体状でも円筒状でも良い。 前者の場合は製造が容易で安価となり、後者は補助転動体の直径を小さくすることで転動体の数を増加し、大きな荷重に耐える軸受とすることが出来る。   As one embodiment of the above means, when the cross section of the first raceway surface and the second raceway surface is arcuate and the rolling element is spherical, it may be implemented in a bearing generally called an angular contact bearing. Many. In this case, the shape of the auxiliary rolling element may be spherical or cylindrical. In the former case, manufacture is easy and inexpensive, and in the latter case, the number of rolling elements can be increased by reducing the diameter of the auxiliary rolling elements, and the bearing can withstand a large load.

又、上記手段における他の実施形態として、第１の軌道面と第２の軌道面の断面を直線状として、転動体を円筒状としたいわゆる円筒コロ軸受の場合は、軸方向の荷重には対応出来ないが、半径方向の大きな荷重に耐えることが出来る。 この場合の補助転動体は、円筒状のものか、又は球状のものを２列に配置することとなる。   As another embodiment of the above means, in the case of a so-called cylindrical roller bearing in which the cross section of the first raceway surface and the second raceway surface is linear and the rolling element is cylindrical, Cannot handle, but can withstand large radial loads. In this case, the auxiliary rolling elements are cylindrical or spherical and are arranged in two rows.

尚、転動体が球状の場合は第１と第２の軌道輪が軸方向に対向したいわゆるスラスト軸受としても応用することが出来る。この場合も効果は前記アンギュラーコンタクト軸受の場合と同じである。   When the rolling element is spherical, it can also be applied as a so-called thrust bearing in which the first and second race rings are opposed in the axial direction. In this case as well, the effect is the same as in the case of the angular contact bearing.

尚、本発明を実施する上で新たな軌道面の追加はなく、補助転動体の追加と、保持器の変更のみで良いので製造は容易であり、安価に製作する事が出来る。   It should be noted that in carrying out the present invention, there is no addition of a new raceway surface, and it is only necessary to add an auxiliary rolling element and change the cage, so that the manufacture is easy and can be manufactured at low cost.

本発明のころがり軸受は、上記の手段により明らかなように、新たな軌道面を追加することなしに、アンギュラーコンタクト軸受、円筒コロ軸受、スラスト軸受などに広い範囲に容易に実施することが可能であり、従来のものに比べて摩擦力の大幅な低減を可能にするものである。   As apparent from the above means, the rolling bearing of the present invention can be easily implemented in a wide range of angular contact bearings, cylindrical roller bearings, thrust bearings and the like without adding a new raceway surface. Therefore, the frictional force can be greatly reduced as compared with the conventional one.

本発明の構造は、その好ましい実施形態のひとつとして、断面が円弧状の第１の軌道面を有する第１の軌道輪（外輪）と、断面が円弧状の第２の軌道面を有する第２の軌道輪（内輪）と、該第１の軌道面と第２の軌道面に接して回転する複数の球状の転動体を配置してなるころがり軸受において、各々の隣り合う転動体の間に球状の補助転動体を設け、該補助転動体の中心位置を隣り合う転動体の中心を結ぶ直線上に配置している。 この位置関係を保つために、転動体が緩く収まる半径方向の複数の穴と、補助転動体が緩く収まる円周方向の複数の穴を有する保持器が設けられている。   As one preferred embodiment of the structure of the present invention, a first race ring (outer ring) having a first raceway surface having an arcuate cross section and a second raceway surface having a second raceway surface having an arcuate cross section. And a plurality of spherical rolling elements rotating in contact with the first raceway surface and the second raceway surface, a rolling bearing having a spherical shape between each adjacent rolling element. The auxiliary rolling elements are provided, and the center positions of the auxiliary rolling elements are arranged on a straight line connecting the centers of the adjacent rolling elements. In order to maintain this positional relationship, a cage having a plurality of holes in the radial direction in which the rolling elements fit loosely and a plurality of holes in the circumferential direction in which the auxiliary rolling elements fit loosely is provided.

このように構成したころがり軸受は、第１の軌道輪と第２の軌道輪が相対回転運動をすると、転動体は第１の軌道面と第２の軌道面に接触した状態でころがり運動をする。 しかし、荷重の方向が軸受の回転中心軸に対して傾いた場合などに該ころがり運動の回転軸が傾き、 隣り合った転動体の間隔が変動することがある。 この場合、接近した転動体は補助転動体に接触し、補助転動体が転動体の外周の回転速度と同じ速度で逆回転して、ころがり運動をする。 補助転動体の中心が隣り合った転動体の中心を結ぶ線上にあれば、補助転動体を側方に押し出す力は働かない。 この線上からずれると、保持器が側方から補助転動体を支持してそのずれ量を制限する。 その支持力の大きさは、ずれ量と隣り合った転動体の中心間距離のとの比に比例する。 仮にこの比が１％ならば、支持力は転動体と補助転動体の接触圧の２％である。 補助転動体は両側から等しい力で押されているので、合計の支持力は２％の２倍で４％となる。 このように、補助転動体を使用しない従来の軸受に比べてこの部分の摩擦を大幅に減少させることが出来る。   In the rolling bearing configured as described above, when the first race ring and the second race ring make a relative rotational movement, the rolling element rolls in a state in which the rolling element is in contact with the first race face and the second race face. . However, when the direction of the load is inclined with respect to the rotation center axis of the bearing, the rotation axis of the rolling motion may be inclined, and the interval between the adjacent rolling elements may fluctuate. In this case, the approaching rolling element comes into contact with the auxiliary rolling element, and the auxiliary rolling element rotates reversely at the same speed as the rotation speed of the outer periphery of the rolling element to perform a rolling motion. If the center of the auxiliary rolling element is on a line connecting the centers of the adjacent rolling elements, the force that pushes the auxiliary rolling element to the side does not work. If it deviates from on this line, a cage will support an auxiliary rolling element from the side, and will limit the amount of deviation. The magnitude of the supporting force is proportional to the ratio between the shift amount and the distance between the centers of the adjacent rolling elements. If this ratio is 1%, the supporting force is 2% of the contact pressure between the rolling element and the auxiliary rolling element. Since the auxiliary rolling element is pushed with equal force from both sides, the total supporting force is doubled to 2% to 4%. Thus, the friction of this part can be significantly reduced compared with the conventional bearing which does not use an auxiliary rolling element.

尚、本発明において、上記説明の構造は、単なる一例であり、転動体の形状、補助転動体の形状、又軌道輪も半径方向に対向するものではなく、軸方向に対向するもの等、多くの応用が可能である。   In the present invention, the structure described above is merely an example, and the shape of the rolling element, the shape of the auxiliary rolling element, and the races are not opposed to each other in the radial direction, but many such as those facing the axial direction. Can be applied.

以下図について本発明の実施形態について説明する。
図１は本発明の一実施形態の構造を示す側断面図であり、図２はその正面図である。
図１及び図２において、断面が円弧状の第１の軌道面１を有する第１の軌道輪（外輪）２と、断面が円弧状の第２の軌道面３を有する第２の軌道輪（内輪）４と、該第１の軌道面１と第２の軌道面３に接して回転する複数の球状の転動体５を配置してなるころがり軸受において、各々の隣り合う転動体５の間に球状の補助転動体６を設け、該補助転動体６の中心位置を隣り合う転動体５の中心を結ぶ直線７上に配置している。 この位置関係を保つために、転動体５が緩く収まる半径方向の複数の穴８と、補助転動体６が緩く収まる円周方向の複数の穴９を有する保持器１０が設けられている。 Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a side sectional view showing the structure of an embodiment of the present invention, and FIG. 2 is a front view thereof.
1 and 2, a first raceway (outer ring) 2 having a first raceway surface 1 having an arcuate cross section and a second raceway having a second raceway surface 3 having an arcuate cross section ( In a rolling bearing in which a plurality of spherical rolling elements 5 that rotate in contact with the first raceway surface 1 and the second raceway surface 3 are arranged between the adjacent rolling elements 5. A spherical auxiliary rolling element 6 is provided, and the center position of the auxiliary rolling element 6 is arranged on a straight line 7 connecting the centers of the adjacent rolling elements 5. In order to maintain this positional relationship, a cage 10 having a plurality of radial holes 8 in which the rolling elements 5 fit loosely and a plurality of circumferential holes 9 in which the auxiliary rolling elements 6 fit loosely is provided.

このように構成したころがり軸受は、第１の軌道輪２と第２の軌道輪４が相対回転運動をすると、転動体５は第１の軌道面１と第２の軌道面３に接触した状態でころがり運動をする。 しかし、荷重の方向が軸受の回転中心軸１１に対して傾いた場合などに該転動体５のころがり運動の回転軸が傾き、 隣り合った転動体５の間隔が変動することがある。 この場合、接近した転動体５は補助転動体６に接触し、補助転動体６が転動体５の外周の回転速度と同じ速度で逆回転して、ころがり運動をする。 補助転動体６の中心が隣り合った転動体５の中心を結ぶ線７上にあれば、補助転動体６を側方に押し出す力は働かない。 この線上からずれると、保持器１０の円周方向の穴９が側方から補助転動体６を支持してそのずれ量を制限する。 その支持力の大きさは、隣り合った転動体５の中心間距離とずれ量との比に比例する。 仮にこの比が１％ならば、支持力は転動体５と補助転動体６の接触圧の２％である。 補助転動体６は両側から等しい力で転動体５に押されているので、合計の支持力は２％の２倍で４％となる。 このように、補助転動体６を使用しない従来の軸受に比べてこの部分の摩擦を大幅に減少させることが出来る。   In the rolling bearing configured as described above, when the first raceway ring 2 and the second raceway ring 4 undergo relative rotational motion, the rolling elements 5 are in contact with the first raceway surface 1 and the second raceway surface 3. Do rolling exercise. However, when the direction of the load is inclined with respect to the rotation center axis 11 of the bearing, the rotation axis of the rolling motion of the rolling element 5 may be inclined, and the interval between the adjacent rolling elements 5 may fluctuate. In this case, the approaching rolling element 5 comes into contact with the auxiliary rolling element 6, and the auxiliary rolling element 6 rotates in the reverse direction at the same speed as the rotation speed of the outer periphery of the rolling element 5 to perform a rolling motion. If the center of the auxiliary rolling element 6 is on the line 7 connecting the centers of the adjacent rolling elements 5, the force for pushing the auxiliary rolling element 6 to the side does not work. If it deviates from this line, the hole 9 in the circumferential direction of the cage 10 supports the auxiliary rolling element 6 from the side to limit the deviation amount. The magnitude of the supporting force is proportional to the ratio between the distance between the centers of the adjacent rolling elements 5 and the amount of deviation. If this ratio is 1%, the supporting force is 2% of the contact pressure between the rolling element 5 and the auxiliary rolling element 6. Since the auxiliary rolling elements 6 are pushed by the rolling elements 5 with equal force from both sides, the total supporting force is doubled to 2% to 4%. Thus, the friction of this part can be significantly reduced compared with the conventional bearing which does not use the auxiliary rolling element 6.

また、図３及び図４について本発明の他の実施形態について説明する。
図３は本発明の一実施形態の構造を示す側断面図であり、図４はその正面図である。
図３、図４において、断面が直線状の第１の軌道面２１を有する第１の軌道輪（外輪）２２と、断面が円弧状の第２の軌道面２３を有する第２の軌道輪（内輪）２４と、該第１の軌道面２１と第２の軌道面２３に接して回転する複数の円筒状の転動体２５を配置してなるころがり軸受において、各々の隣り合う転動体２５の間に円筒状の補助転動体２６を設け、該補助転動体２６の中心位置を隣り合う転動体２５の中心を結ぶ直線２７上に配置している。 この位置関係を保つために、転動体２５が緩く収まる半径方向の複数の穴２８と、補助転動体２６が緩く収まる円周方向の複数の穴２９を有する保持器３０が設けられている。 Further, another embodiment of the present invention will be described with reference to FIGS.
FIG. 3 is a side sectional view showing the structure of one embodiment of the present invention, and FIG. 4 is a front view thereof.
3 and 4, a first raceway (outer ring) 22 having a first raceway surface 21 having a linear cross section and a second raceway having a second raceway surface 23 having a circular cross section ( In a rolling bearing formed by arranging a plurality of cylindrical rolling elements 25 that rotate in contact with the first raceway surface 21 and the second raceway surface 23, the inner ring) 24, and between the adjacent rolling elements 25 A cylindrical auxiliary rolling element 26 is provided at the center, and the center position of the auxiliary rolling element 26 is arranged on a straight line 27 connecting the centers of the adjacent rolling elements 25. In order to maintain this positional relationship, a cage 30 having a plurality of holes 28 in the radial direction in which the rolling elements 25 fit loosely and a plurality of holes 29 in the circumferential direction in which the auxiliary rolling elements 26 fit loosely is provided.

このように構成したころがり軸受の作用は図１及び図３に示した構造のものとほぼ同様であるが、軸方向の荷重を受けることは出来ない代わりに、半径方向の大きな荷重を支えることが出来る。   The operation of the rolling bearing constructed in this way is almost the same as that of the structure shown in FIGS. 1 and 3, but it cannot support an axial load but can support a large radial load. I can do it.

図５は、本発明の他の実施例の構造を示す側断面図である。
図５において、補助転動体４６は球状をなし、転動体２５の長手方向に対して２列に配置されている。 保持器５０の円周方向の穴４９もこの補助転動体４６を緩く収めるべく２列に設けられている。 図５に示す構造のころがり軸受の作用は、図３及び図４に示す構造のものとほぼ同じであるが、比較的転動体２５の数が少ない軸受について、保持器が製造上容易な形状となる利点がある。 FIG. 5 is a side sectional view showing the structure of another embodiment of the present invention.
In FIG. 5, the auxiliary rolling elements 46 have a spherical shape and are arranged in two rows with respect to the longitudinal direction of the rolling elements 25. The holes 49 in the circumferential direction of the cage 50 are also provided in two rows in order to accommodate the auxiliary rolling elements 46 loosely. The operation of the rolling bearing having the structure shown in FIG. 5 is substantially the same as that of the structure shown in FIGS. 3 and 4, but the bearing has a shape that allows the cage to be easily manufactured for a bearing having a relatively small number of rolling elements 25. There are advantages.

図６は、本発明の他の実施例の構造を示す側断面図であり。 図７は、その正面図である。
図６及び図７において、断面が円弧状の第１の軌道面６１を有する第１の軌道輪６２と、断面が円弧状の第２の軌道面６３を有する第２の軌道輪６４とは相互の軌道面６１と６３が軸方向に対向している。 該第１の軌道面６１と第２の軌道面６３に接して回転する複数の球状の転動体６５を配置してなるころがり軸受において、各々の隣り合う転動体６５の間に球状の補助転動体６６を設け、該補助転動体６６の中心位置を隣り合う転動体６５の中心を結ぶ直線６７上に配置している。 この位置関係を保つために、転動体６５が緩く収まるころがり軸受の回転中心軸７１方向の複数の穴６８と、補助転動体６６が緩く収まる円周方向の複数の穴６９を有する保持器７０が設けられている。該保持器７０は製造、組み立て上の理由で軸受の回転中心軸７１に直角な平面で２分割され、転動体６５及び補助転動体６６を組み込み後にリベット７２で結合されている。 FIG. 6 is a side sectional view showing the structure of another embodiment of the present invention. FIG. 7 is a front view thereof.
6 and 7, the first raceway ring 62 having the first raceway surface 61 having an arcuate cross section and the second raceway ring 64 having the second raceway surface 63 having an arcuate cross section are mutually connected. The track surfaces 61 and 63 are opposed to each other in the axial direction. In a rolling bearing in which a plurality of spherical rolling elements 65 rotating in contact with the first raceway surface 61 and the second raceway surface 63 are arranged, a spherical auxiliary rolling element is provided between the adjacent rolling elements 65. 66, and the center position of the auxiliary rolling element 66 is arranged on a straight line 67 that connects the centers of the adjacent rolling elements 65. In order to maintain this positional relationship, a cage 70 having a plurality of holes 68 in the direction of the rotation center axis 71 of the rolling bearing in which the rolling elements 65 are loosely fitted and a plurality of holes 69 in the circumferential direction in which the auxiliary rolling elements 66 are loosely accommodated is provided. Is provided. The retainer 70 is divided into two by a plane perpendicular to the rotation center shaft 71 of the bearing for manufacturing and assembly reasons, and the rolling element 65 and the auxiliary rolling element 66 are assembled and connected by a rivet 72.

このように構成したころがり軸受は、第１の軌道輪６２と第２の軌道輪６４が相対回転運動をすると、転動体６５は第１の軌道面６１と第２の軌道面６３に接触した状態でころがり運動をする。 しかし、荷重の方向が軸受の回転中心軸７１に対して傾いた場合などに該転動体６５のころがり運動の回転軸が傾き、隣り合った転動体６５の間隔が変動することがある。 この場合、接近した転動体６５は補助転動体６６に接触し、補助転動体６６が転動体６５の外周の回転速度と同じ速度で逆回転して、ころがり運動をする。
この場合の作用は図１及び図２に示す構造の場合とほぼ同様である。 但し、保持器７０の複数の穴６８には転動体６５の公転に伴う遠心力がより強く働くので、保持器の材質はこの遠心力に耐える金属で製作されることが望ましい。 補助転動体６６は径が小さく
質量が小さいので、遠心力の影響を受けることはかなりの高速回転時以外問題になることは少ない。 その場合も、補助転動体６６の材質を比重の軽いセラミックなどで製作することによって解決する事が出来る。 In the rolling bearing configured as described above, when the first raceway ring 62 and the second raceway ring 64 perform relative rotational motion, the rolling element 65 is in contact with the first raceway surface 61 and the second raceway surface 63. Do rolling exercise. However, when the direction of the load is inclined with respect to the rotation center axis 71 of the bearing, the rotation axis of the rolling motion of the rolling element 65 may be inclined, and the interval between the adjacent rolling elements 65 may vary. In this case, the approaching rolling element 65 comes into contact with the auxiliary rolling element 66, and the auxiliary rolling element 66 rotates in the reverse direction at the same speed as the rotation speed of the outer periphery of the rolling element 65, thereby rolling.
The operation in this case is almost the same as that of the structure shown in FIGS. However, since the centrifugal force accompanying the revolution of the rolling element 65 works more strongly in the plurality of holes 68 of the cage 70, it is desirable that the material of the cage is made of a metal that can withstand this centrifugal force. Since the auxiliary rolling element 66 has a small diameter and a small mass, it is unlikely that the influence of the centrifugal force becomes a problem except during a considerably high speed rotation. In this case as well, the problem can be solved by manufacturing the auxiliary rolling element 66 with a ceramic having a light specific gravity.

以上の説明だ明らかのごとく、本発明のころがり軸受は、転動体同士又は保持器の壁面と転動体の接触による断続的な摩擦力の発生を大幅に低減することが出来る上、新たな軌道面の追加が不要であり、保持器の変更と補助転動体の追加のみで実施が可能であるので、従来の軸受との置き換えも容易であるため、安価に実施することが出来、摩擦力の減少効果を従来の軸受と比較しやすい。 又、アンギュラーコンタクト軸受、円筒コロ軸受、スラスト軸受など広く応用することが出来るため、その産業上の効果は極めて著しい。   As is clear from the above description, the rolling bearing of the present invention can greatly reduce the generation of intermittent frictional force due to contact between rolling elements or the wall surface of the cage and the rolling element, and a new raceway surface. Is not necessary, and can be implemented only by changing the cage and adding auxiliary rolling elements, so it can be easily replaced with conventional bearings, and can be implemented at low cost, reducing frictional force. The effect is easy to compare with conventional bearings. Further, since it can be widely applied to angular contact bearings, cylindrical roller bearings, thrust bearings, etc., its industrial effect is extremely remarkable.

本発明の一実施形態の構造を示す側断面図である。It is a sectional side view which shows the structure of one Embodiment of this invention. その正面図である。It is the front view. 本発明の他の実施形態の構造を示す分解斜視図である。It is a disassembled perspective view which shows the structure of other embodiment of this invention. その正面図である。It is the front view. 本発明の他の実施形態の構造を示す分解斜視図である。It is a disassembled perspective view which shows the structure of other embodiment of this invention. 本発明の他の実施形態の構造を示す側断面図である。It is a sectional side view which shows the structure of other embodiment of this invention. その正面図である。It is the front view.

符号の説明Explanation of symbols

１、２１、６１：第１の軌道面
２、２２、６２：第１の軌道輪
３、２３、６３：第２の軌道面
４、２４、６４：第２の軌道輪
５、２５、６５：転動体
６、２６、４６、６６：補助転動体
７、２７、６７：直線
８、２８、６８：半径方向の複数の穴
９、２９、４９、６９：円周方向の複数の穴
１０、３０、５０、７０：保持器
１１、７１：ころがり軸受の回転中心軸
７２：リベット
1, 21, 61: First raceway 2, 22, 62: First raceway 3, 23, 63: Second raceway 4, 24, 64: Second raceway 5, 25, 65: Rolling elements 6, 26, 46, 66: Auxiliary rolling elements 7, 27, 67: Straight lines 8, 28, 68: Multiple holes in radial direction 9, 29, 49, 69: Multiple holes 10, 30 in circumferential direction , 50, 70: Cage 11, 71: Rolling bearing shaft 72: Rivet

Claims (5)

第１の軌道面を有する第１の軌道輪と、第２の軌道面を有する第２の軌道輪と、該第１の軌道面と第２の軌道面に接して回転する複数の転動体を配置してなるころがり軸受において、各々の隣り合う転動体の間に補助転動体を設け、該補助転動体の中心位置を隣り合う転動体の中心を結ぶ直線上に配置したことを特徴とするころがり軸受。   A first raceway having a first raceway surface; a second raceway having a second raceway surface; and a plurality of rolling elements rotating in contact with the first raceway surface and the second raceway surface. In the rolling bearing formed by arranging, an auxiliary rolling element is provided between each adjacent rolling element, and the center position of the auxiliary rolling element is arranged on a straight line connecting the centers of the adjacent rolling elements. bearing. 第１の軌道面と第２の軌道面の断面を円弧状として、転動体を球状としたことを特徴とする請求項１記載のころがり軸受。   The rolling bearing according to claim 1, wherein the first raceway surface and the second raceway surface have a circular cross section, and the rolling elements are spherical. 第１の軌道面と第２の軌道面の断面を直線状として、転動体を円筒状としたことを特徴とする請求項１記載のころがり軸受。   The rolling bearing according to claim 1, wherein the first raceway surface and the second raceway surface have a straight section, and the rolling element has a cylindrical shape. 補助転動体の形状を球状としたことを特徴とする請求項１記載のころがり軸受。   2. The rolling bearing according to claim 1, wherein the auxiliary rolling element has a spherical shape. 補助転動体の形状を円筒状としたことを特徴とする請求項１記載のころがり軸受。
The rolling bearing according to claim 1, wherein the auxiliary rolling element has a cylindrical shape.
JP2004262031A 2004-09-09 2004-09-09 Rolling bearing Expired - Fee Related JP4113979B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6865905B1 (en) * 2020-04-20 2021-04-28 三菱電機株式会社 bearing

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6865905B1 (en) * 2020-04-20 2021-04-28 三菱電機株式会社 bearing

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