JP2008261481A - Radial ball bearing and radial ball bearing cage - Google Patents

Radial ball bearing and radial ball bearing cage Download PDF

Info

Publication number
JP2008261481A
JP2008261481A JP2007205464A JP2007205464A JP2008261481A JP 2008261481 A JP2008261481 A JP 2008261481A JP 2007205464 A JP2007205464 A JP 2007205464A JP 2007205464 A JP2007205464 A JP 2007205464A JP 2008261481 A JP2008261481 A JP 2008261481A
Authority
JP
Japan
Prior art keywords
concave surface
surface portion
ball
spherical concave
ball bearing
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
Application number
JP2007205464A
Other languages
Japanese (ja)
Inventor
Takamitsu Tomuro
貴光 戸室
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP2007205464A priority Critical patent/JP2008261481A/en
Publication of JP2008261481A publication Critical patent/JP2008261481A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • 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
    • F16C33/41—Ball cages comb-shaped
    • F16C33/418—Details of individual pockets, e.g. shape or ball retaining means
    • 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
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • F16C33/6614—Retaining the grease in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

Landscapes

  • 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 radial ball bearing to be rotatable without causing poor lubrication on the raceway surfaces of the bearing and the noises of a cage while setting the radius ratio of the groove radius of at least one raceway surface to the diameter of a ball to be 52% or less to reduce stress on a groove, and to provide the radial ball bearing cage. <P>SOLUTION: The radial ball bearing uses the cage for holding the plurality of balls 5 between the raceway surface of an inner ring and the raceway surface of an outer ring. The cage 20 annularly formed as a whole has pockets 18 at a plurality of positions in the circumferential direction. The radius ratio r/D of the groove radius r of at least one of the raceway surface of the inner ring and the raceway surface of the outer ring to the diameter D of the ball is 52% or less. A concave portion 29 of each pocket of the cage has a first spherically concave portion 21 spherically formed on the bottom face side opposed to an opening portion T, a second spherically concave portion 23 spherically formed on the opening portion side, and an axial cylindrically concave portion 22 cylindrically formed between the first spherically concave portion and the second spherically concave portion with a rolling center axis v of the ball as a center. Lubricant reservoir portions A, B are provided near boundaries between each of the first and second spherically concave portions and the axial cylindrically concave portion. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、軌道面間に配置される複数の玉を転動自在に保持する保持器を有するラジアル玉軸受及びラジアル玉軸受用保持器に関する。   The present invention relates to a radial ball bearing having a cage that holds a plurality of balls arranged between raceway surfaces in a rollable manner, and a radial ball bearing cage.

ラジアル玉軸受は各種回転機械装置で回転軸等を支持する軸受部に広く使用されているが、このラジアル玉軸受の従来例の概略的構成を図３に示す（下記特許文献１，２，３参照）。図３のラジアル玉軸受１０は、外周面に内輪軌道面１を形成した内輪２と、内周面に外輪軌道面３を形成した外輪４とを同心的に配置し、内輪軌道面１と外輪軌道面３との間に複数個の玉５を転動自在に設けて構成されている。複数個の玉５は保持器６により転動自在に保持されている。図４に図３の保持器６の斜視図を示す。   Radial ball bearings are widely used in bearings that support rotating shafts and the like in various rotating machine devices. A schematic configuration of a conventional example of this radial ball bearing is shown in FIG. 3 (Patent Documents 1, 2, and 3 below). reference). A radial ball bearing 10 in FIG. 3 is formed by concentrically arranging an inner ring 2 having an inner ring raceway surface 1 formed on an outer peripheral surface and an outer ring 4 having an outer ring raceway surface 3 formed on an inner peripheral surface. A plurality of balls 5 are provided between the raceway surface 3 so as to be freely rollable. The plurality of balls 5 are held by a cage 6 so as to be freely rollable. FIG. 4 is a perspective view of the cage 6 of FIG.

図４に示すように、保持器６は、円環状の冠型に構成されており、樹脂から射出成形により製造され、従来の金属からプレス成形で製造された波型保持器の代わりに用いられるようになっている（下記特許文献１，２，３参照）。図４の冠型保持器６は、円環状の主部１７の円周方向の複数個所に玉５（図３）を転動自在に保持するように設けられたポケット１８と、ポケット１８の両側に設けられた弾性変形可能な一対の弾性片１６ａ、１６ｂと、を複数組有する。各ポケット１８は、主部１７に互いに間隔をあけて配置された一対の弾性片１６ａ、１６ｂの片側面と、一対の弾性片１６ａと１６ｂとの間に設けられた凹面部１９と、からほぼ全体が球面状に構成されている。各ポケット１８の図の上部には一対の弾性片１６ａ、１６ｂ間に開口部Ｔが形成される。   As shown in FIG. 4, the cage 6 is formed in an annular crown shape, and is manufactured by injection molding from a resin, and is used in place of a corrugated cage that is manufactured by press molding from a conventional metal. (See Patent Documents 1, 2, and 3 below). 4 includes a pocket 18 provided to hold the balls 5 (FIG. 3) in a plurality of positions in the circumferential direction of an annular main portion 17 so as to be able to roll, and both sides of the pocket 18. A plurality of elastically deformable pairs of elastic pieces 16a and 16b provided on the surface are provided. Each pocket 18 is substantially composed of one side surface of a pair of elastic pieces 16a and 16b arranged at a distance from each other in the main portion 17, and a concave surface portion 19 provided between the pair of elastic pieces 16a and 16b. The whole is formed in a spherical shape. An opening T is formed between the pair of elastic pieces 16a and 16b in the upper portion of each pocket 18 in the figure.

図４の冠型保持器６を用いて図３のようなラジアル玉軸受を組み立てる場合、玉５を、ポケット１８の爪状の一対の弾性片（爪状部）１６ａ、１６ｂの先端縁同士の間隔を弾性的に押し広げて弾性片１６ａ、１６ｂの間の開口部Ｔから押し込むようにして挿入する。このように、冠型保持器６は各ポケット１８内に各玉５を抱き込むことで、玉５を内輪軌道面１と外輪軌道面３との間（図３）で転動自在に保持する。   When the radial ball bearing as shown in FIG. 3 is assembled using the crown type cage 6 shown in FIG. 4, the ball 5 is formed between the tip edges of a pair of claw-like elastic pieces (claw-like portions) 16 a and 16 b of the pocket 18. The gap is elastically expanded and inserted so as to be pushed in from the opening T between the elastic pieces 16a and 16b. Thus, the crown type cage 6 holds the balls 5 in the pockets 18 so that the balls 5 can roll between the inner ring raceway surface 1 and the outer ring raceway surface 3 (FIG. 3). .

上述のように、従来のラジアル玉軸受の保持器は、金属製の波型保持器やポケットが単一の球面で成形された樹脂製の円環状の冠型保持器が使われることが一般的であった。
特許第３７４４６６３号公報 特許第３０３５７６６号公報 特開２００５−１３３８９３号公報 As described above, the conventional radial ball bearing retainer is generally a metal corrugated retainer or a resin annular crown retainer with a pocket formed of a single spherical surface. Met.
Japanese Patent No. 3744663 Japanese Patent No. 3035766 JP 2005-133893 A

図５に、図４の保持器６のV-V線方向に切断してみた要部断面図を示す。軸受の高負荷化達成のために軌道面１，３の溝半径と玉５の直径との半径比（図１参照）を通常適用される５２％より小さくし、玉５が接触する軌道面１，３の溝上の応力を下げる工夫を使用条件に合わせて実施しようとする場合、次のような問題がある。   FIG. 5 shows a cross-sectional view of the main part of the cage 6 in FIG. 4 cut in the VV line direction. In order to achieve a high load on the bearing, the radius ratio between the groove radius of the raceway surfaces 1 and 3 and the diameter of the ball 5 (see FIG. 1) is made smaller than the usual 52%, and the raceway surface 1 with which the ball 5 contacts. When attempting to reduce the stress on the grooves according to the usage conditions, there are the following problems.

すなわち、図４のような従来の樹脂製の保持器６は、そのポケット１８が図５のように玉５の中心Ｏを中心とする半径Ｒ０の球面形状であるため、上述のように、半径比が５２％以下であると、玉５の転動により軌道面１，３の溝からグリース等の潤滑剤が押し出されてしまい、その潤滑剤を保持器６内で保持することができず、軌道面１，３の潤滑が不十分になり保持器音の発生、軌道面や転動面での表面剥離、玉の焼付き等を起こすおそれが生じてしまう。   That is, the conventional resin cage 6 shown in FIG. 4 has a spherical shape with a radius R0 centered on the center O of the ball 5 as shown in FIG. When the ratio is 52% or less, lubricant such as grease is pushed out from the grooves of the raceway surfaces 1 and 3 due to rolling of the balls 5, and the lubricant cannot be held in the cage 6, Lubrication of the raceway surfaces 1 and 3 becomes insufficient, and there is a risk of generating cage noise, surface peeling on the raceway surface and rolling surface, and seizure of balls.

本発明は、上述のような従来技術の問題に鑑み、少なくとも一方の軌道面の溝半径と玉の直径との半径比が５２％以下として溝上の応力を低減するとともに、軸受の軌道面における潤滑不良や保持器音の発生を起こすことなく回転可能なラジアル玉軸受及びラジアル玉軸受用保持器を提供することを目的とする。   In view of the above-mentioned problems of the prior art, the present invention reduces the stress on the groove by setting the radius ratio of the groove radius of at least one raceway surface to the diameter of the ball to be 52% or less, and lubricates the raceway surface of the bearing. It is an object of the present invention to provide a radial ball bearing and a radial ball bearing retainer that can rotate without causing defects or generation of cage noise.

上記目的を達成するために、本発明によるラジアル玉軸受は、外周面に内輪軌道面を有する内輪と内周面に外輪軌道面を有する外輪とを互いに同心に配置し、前記内輪軌道面と前記外輪軌道面との間に、保持器を用いて複数の玉を保持し、前記保持器は、全体を円環状に形成して円周方向の複数箇所にポケットを設け、前記各ポケットは前記玉が押し込まれる開口部と、前記玉が位置する凹面部と、を有するラジアル玉軸受であって、前記内輪軌道面及び前記外輪軌道面の少なくとも一方の溝半径（ｒ’）と前記玉の直径（Ｄ）との半径比（ｒ’／Ｄ）が５２％以下であり、前記保持器の前記凹面部は、前記開口部と対向する底面側に球状に形成された第１球状凹面部と、前記開口部側に球状に形成された第２球状凹面部と、前記第１球状凹面部と前記第２球状凹面部との間に前記玉の転動中心軸を中心として円筒状に形成されたアキシャル円筒状凹面部と、を備え、前記第１球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍、及び、前記第２球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍に、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部を有することを特徴とする。   In order to achieve the above object, a radial ball bearing according to the present invention includes an inner ring having an inner ring raceway surface on an outer peripheral surface and an outer ring having an outer ring raceway surface on an inner peripheral surface, and the inner ring raceway surface and the A cage is used to hold a plurality of balls between the outer ring raceway surface, the cage is formed in an annular shape as a whole, and pockets are provided at a plurality of locations in the circumferential direction. A radial ball bearing having an opening into which the ball is pushed, and a concave surface portion where the ball is positioned, wherein the groove radius (r ′) of at least one of the inner ring raceway surface and the outer ring raceway surface and the diameter of the ball ( D) is a radius ratio (r ′ / D) of 52% or less, and the concave surface portion of the retainer is a first spherical concave surface portion formed in a spherical shape on the bottom surface side facing the opening, A second spherical concave surface formed spherically on the opening side, and the first spherical concave An axial cylindrical concave surface portion formed in a cylindrical shape around the rolling center axis of the ball between the first spherical concave surface portion and the second spherical concave surface portion, and the first spherical concave surface portion and the axial cylindrical concave surface A lubricant reservoir for holding the lubricant filled in the bearing in the vicinity of the boundary between the bearing and in the vicinity of the boundary between the second spherical concave surface and the axial cylindrical concave surface. Features.

このラジアル玉軸受によれば、少なくとも一方の軌道面の溝半径ｒ’と玉の直径Ｄとの半径比ｒ’／Ｄを５２％以下として溝上の応力を低減し、軸受の高負荷化を達成するとともに、アキシャル円筒状凹面部の両端側の潤滑剤溜まり部にグリース等の潤滑剤を保持でき、玉は常に潤滑剤に覆われ、上記半径比が５２％以下であるために玉の転動により軌道面の溝から押し出された潤滑剤も保持器のポケットに溜まり、玉を通じて軌道面へ再び流れ込むことができるので、軸受の潤滑性能が向上し、軸受の軌道面における潤滑不良や保持器音の発生を起こすことなく回転することができる。   According to this radial ball bearing, the stress on the groove is reduced by setting the radius ratio r ′ / D between the groove radius r ′ of at least one raceway surface and the diameter D of the ball to 52% or less, thereby achieving high load on the bearing. In addition, lubricant such as grease can be held in the lubricant reservoirs on both ends of the axial cylindrical concave surface, and the balls are always covered with the lubricant, and the radius ratio is 52% or less. The lubricant pushed out from the groove on the raceway surface also accumulates in the pocket of the cage and can flow again into the raceway surface through balls, improving the lubrication performance of the bearing, causing poor lubrication on the raceway surface of the bearing and cage noise. It can rotate without causing the occurrence of.

上記ラジアル玉軸受において、前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心を略中心とする半径をそれぞれ有するように構成できる。   In the radial ball bearing, the first spherical concave surface portion and the second spherical concave surface portion can each be configured to have a radius that is substantially centered on the center of the ball in the pocket.

また、前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心からずれた位置を中心とする半径をそれぞれ有する有するように構成できる。   The first spherical concave surface portion and the second spherical concave surface portion may each have a radius centered at a position shifted from the center of the ball in the pocket.

また、前記潤滑剤としてグリースを充填し、前記グリースの調度が２００乃至２８０の範囲内にあることが好ましい。   Moreover, it is preferable that grease is filled as the lubricant, and the grease has a degree of adjustment in the range of 200 to 280.

本発明によるラジアル玉軸受用保持器は、ラジアル玉軸受の軌道面間に配置される複数の玉を転動自在に保持するために全体を円環状に形成して円周方向の複数箇所にポケットを設け、前記各ポケットは前記玉が押し込まれる開口部と、前記玉が位置する凹面部と、を有するラジアル玉軸受用保持器であって、少なくとも一方の前記軌道面の溝半径（ｒ’）と玉直径（Ｄ）との半径比（ｒ’／Ｄ）が５２％以下であり、前記凹面部は、前記開口部と対向する底面側に球状に形成された第１球状凹面部と、前記開口部側に球状に形成された第２球状凹面部と、前記第１球状凹面部と前記第２球状凹面部との間に前記玉の転動中心軸を中心として円筒状に形成されたアキシャル円筒状凹面部と、を備え、前記第１球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍、及び、前記第２球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍に、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部を有することを特徴とする。   A radial ball bearing retainer according to the present invention is formed in an annular shape in order to hold a plurality of balls arranged between raceway surfaces of a radial ball bearing so as to roll freely, and pockets are formed at a plurality of locations in the circumferential direction. Each of the pockets has a radial ball bearing retainer having an opening into which the ball is pushed and a concave surface portion on which the ball is located, and a groove radius (r ′) of at least one of the raceway surfaces The radius ratio (r ′ / D) between the ball diameter (D) and the ball diameter (D) is 52% or less, and the concave surface portion includes a first spherical concave surface portion formed in a spherical shape on the bottom surface side facing the opening, A second spherical concave surface formed in a spherical shape on the opening side, and an axial formed in a cylindrical shape around the rolling center axis of the ball between the first spherical concave surface and the second spherical concave surface A cylindrical concave surface portion, and the first spherical concave surface portion and the axial cylinder In the vicinity of the boundary portion with the concave surface portion and in the vicinity of the boundary portion between the second spherical concave surface portion and the axial cylindrical concave surface portion, a lubricant reservoir for holding the lubricant filled in the bearing is provided. It is characterized by.

このラジアル玉軸受用保持器によれば、ラジアル玉軸受において、少なくとも一方の軌道面の溝半径ｒ’と玉の直径Ｄとの半径比ｒ’／Ｄを５２％以下として溝上の応力を低減し、軸受の高負荷化を達成するとともに、アキシャル円筒状凹面部の両端側の潤滑剤溜まり部にグリース等の潤滑剤を保持でき、玉は常に潤滑剤に覆われ、上記半径比が５２％以下であるために玉の転動により軌道面の溝から押し出された潤滑剤も保持器のポケットに溜まり、玉を通じて軌道面へ再び流れ込むことができるので、軸受の潤滑性能が向上し、軸受の軌道面における潤滑不良や保持器音の発生を起こすことなく回転することができる。   According to this radial ball bearing retainer, in the radial ball bearing, the radial ratio r ′ / D between the groove radius r ′ of at least one raceway surface and the diameter D of the ball is set to 52% or less to reduce the stress on the groove. In addition to achieving high bearing loads, lubricant such as grease can be held in the lubricant reservoirs on both ends of the axial cylindrical concave surface, and the balls are always covered with lubricant, and the radius ratio is 52% or less. Therefore, the lubricant pushed out from the groove on the raceway surface due to the rolling of the ball also accumulates in the pocket of the cage and can flow again into the raceway surface through the ball, improving the bearing lubrication performance and improving the bearing raceway. It can rotate without causing poor lubrication or cage noise on the surface.

上記ラジアル玉軸受用保持器において、前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心を略中心とする半径をそれぞれ有するように構成できる。   In the above radial ball bearing retainer, the first spherical concave surface portion and the second spherical concave surface portion can each be configured to have a radius that is substantially centered on the center of the ball in the pocket.

また、前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心からずれた位置を中心とする半径をそれぞれ有するように構成できる。   Further, the first spherical concave surface portion and the second spherical concave surface portion can each be configured to have a radius centered at a position shifted from the center of the ball in the pocket.

本発明のラジアル玉軸受及びラジアル玉軸受用保持器によれば、少なくとも一方の軌道面の溝半径と玉の直径との半径比が５２％以下として溝上の応力を低減し軸受の高負荷化を達成するとともに、軸受の潤滑性能が向上し、軌道面における潤滑不良や保持器音の発生を起こすことなく回転できる。   According to the radial ball bearing and the radial ball bearing cage of the present invention, the radial ratio between the groove radius of the at least one raceway surface and the ball diameter is 52% or less to reduce the stress on the groove and increase the load on the bearing. As well as achieving this, the lubrication performance of the bearing is improved and the bearing surface can be rotated without causing poor lubrication or generation of cage noise.

以下、本発明を実施するための最良の形態について図面を用いて説明する。図１は本実施の形態によるラジアル玉軸受（半径比が５２％以下の場合の各軌道輪と玉を示す）の断面図（ａ）及び従来のラジアル玉軸受（半径比が５２％を超えた場合の各軌道輪と玉を示す）の断面図（ｂ）である。図２は本実施の形態によるラジアル玉軸受の保持器を図４のV-V線方向と同様の方向で切断してみた要部断面図である。なお、図１では、説明の便宜上、保持器の図示を省略している。   The best mode for carrying out the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view (a) of a radial ball bearing according to the present embodiment (showing each ring and ball when the radius ratio is 52% or less) and a conventional radial ball bearing (with a radius ratio exceeding 52%). It is sectional drawing (b) of each track ring and ball in the case. FIG. 2 is a cross-sectional view of an essential part of the radial ball bearing retainer according to the present embodiment cut along the direction V-V in FIG. In addition, in FIG. 1, illustration of a holder | retainer is abbreviate | omitted for convenience of explanation.

図１，図２の本実施の形態によるラジアル玉軸受３０は図３と基本的構造が同一であり、図３と対応する部分には同じ符号を付してその説明を省略する。また、ラジアル玉軸受３０に用いられるラジアル玉軸受用保持器２０は、全体形状が図４の保持器と略同一であり、図３のようなラジアル玉軸受に用いられるので、図４と対応する部分には同じ符号を付してその説明を省略する。   The radial ball bearing 30 according to the present embodiment shown in FIGS. 1 and 2 has the same basic structure as that in FIG. 3, and the same reference numerals are given to portions corresponding to those in FIG. Further, the radial ball bearing retainer 20 used for the radial ball bearing 30 has substantially the same shape as the retainer of FIG. 4 and is used for the radial ball bearing as shown in FIG. Parts are denoted by the same reference numerals, and description thereof is omitted.

図１（ａ）に示すように、本実施の形態によるラジアル玉軸受３０は、内輪２の内輪軌道面３１は、溝半径ｒ３１を有する溝状となっており、溝半径ｒ３１と玉５の直径Ｄとの半径比 （ｒ３１／Ｄ）が５２％以下である。同様に、外輪４の外輪軌道面３３は、溝半径ｒ３３を有する溝状となっており、溝半径ｒ３３と玉５の直径Ｄとの半径比 （ｒ３３／Ｄ）が５２％以下である。   As shown in FIG. 1A, in the radial ball bearing 30 according to the present embodiment, the inner ring raceway surface 31 of the inner ring 2 has a groove shape having a groove radius r31, and the diameters of the groove radius r31 and the ball 5 are as follows. Radial ratio (r31 / D) with D is 52% or less. Similarly, the outer ring raceway surface 33 of the outer ring 4 has a groove shape having a groove radius r33, and the radius ratio (r33 / D) between the groove radius r33 and the diameter D of the ball 5 is 52% or less.

上述のように、本実施の形態によるラジアル玉軸受３０では、内輪２の内輪軌道面３１の溝半径ｒ３１及び外輪４の外輪軌道面３３の溝半径ｒ３３と玉５の直径との各半径比（ｒ３１／Ｄ，ｒ３３／Ｄ）を、図１（ｂ）のような従来の場合に適用される５２％よりも小さくすることで、玉５が接触する軌道面３１，３３の溝上の応力を小さくしている。   As described above, in the radial ball bearing 30 according to the present embodiment, each radius ratio between the groove radius r31 of the inner ring raceway surface 31 of the inner ring 2 and the groove radius r33 of the outer ring raceway surface 33 of the outer ring 4 and the diameter of the ball 5 ( r31 / D, r33 / D) is made smaller than 52% applied in the conventional case as shown in FIG. 1B, thereby reducing the stress on the grooves of the raceway surfaces 31 and 33 with which the ball 5 contacts. is doing.

すなわち、図１（ｂ）の場合は内輪軌道面１の溝半径ｒ１と玉５の直径Ｄとの半径比 （ｒ１／Ｄ）が５２％を超え、同様に外輪軌道面３の溝半径ｒ３と玉５の直径Ｄとの半径比 （ｒ３／Ｄ）が５２％を超える。このため、各軌道面１，３において玉５と接触する面積が小さくなることから、各軌道面１，３の溝上の応力が大きくなってしまうのに対し、本実施の形態の図１（ａ）によれば、各半径比（ｒ３１／Ｄ，ｒ３３／Ｄ）が５２％以下であり、内輪軌道面３１及び外輪軌道面３３において玉５と接触する面積が大きくなることから、軌道面３１，３３の溝上の応力が小さくなる。このため、本実施の形態のラジアル玉軸受３０は、適用される軸受装置において高い負荷が可能となって高負荷化を達成できる。   That is, in the case of FIG. 1B, the radius ratio (r1 / D) between the groove radius r1 of the inner ring raceway surface 1 and the diameter D of the ball 5 exceeds 52%, and similarly the groove radius r3 of the outer ring raceway surface 3 The radius ratio (r3 / D) with the diameter D of the ball 5 exceeds 52%. For this reason, since the area which contacts the ball | bowl 5 in each track surface 1 and 3 becomes small, while the stress on the groove | channel of each track surface 1 and 3 becomes large, FIG. 1 (a) of this Embodiment is shown. ), Each radius ratio (r31 / D, r33 / D) is 52% or less, and the area of the inner ring raceway surface 31 and the outer ring raceway surface 33 in contact with the balls 5 is increased. The stress on the groove 33 is reduced. For this reason, the radial ball bearing 30 of the present embodiment can achieve a high load because a high load is possible in the applied bearing device.

なお、上述の各半径比（ｒ３１／Ｄ，ｒ３３／Ｄ）は、５０％以上であることが好ましい。   The radius ratios (r31 / D, r33 / D) described above are preferably 50% or more.

次に、図２を参照して図１（ａ）のラジアル玉軸受３０に用いられる保持器２０について説明する。   Next, the cage 20 used for the radial ball bearing 30 of FIG. 1A will be described with reference to FIG.

図２，図４に示すように、保持器２０は、円環状の主部１７の円周方向に等間隔に形成された複数のポケット１８を備え、各ポケット１８は軸受組み立て時に玉５が押し込まれる開口部Ｔと、押し込まれた玉５が位置し保持される凹面部２９と、を有する。   As shown in FIGS. 2 and 4, the retainer 20 includes a plurality of pockets 18 formed at equal intervals in the circumferential direction of the annular main portion 17, and the balls 5 are pushed into the respective pockets 18 when the bearing is assembled. And a concave surface portion 29 on which the pushed ball 5 is positioned and held.

図２のように、ポケット１８の凹面部２９は、図の下方の開口部Ｔと対向する底部側に設けられ玉５の中心Ｏを中心とした半径Ｒ１（Ｒ１＞ｒ（ｒ：玉５の半径））を有する第１球状凹面部２１と、図の上方に開口部Ｔの両側の爪状部１６ａ、１６ｂの近傍に設けられ玉５の中心Ｏを中心とした半径Ｒ２（Ｒ２＞ｒ）を有する第２球状凹面部２３，２３と、第１球状凹面部２１と第２球状凹面部２３，２３との各中間部分に設けられ玉５の転動中心軸ｖを中心とする円筒面状に構成されたアキシャル円筒状凹面部２２，２２と、を備える。   As shown in FIG. 2, the concave surface portion 29 of the pocket 18 is provided on the bottom side facing the lower opening T in the figure, and has a radius R1 (R1> r (r: A first spherical concave surface portion 21 having a radius)) and a radius R2 (R2> r) centered on the center O of the ball 5 provided in the vicinity of the claw-like portions 16a, 16b on both sides of the opening T in the upper part of the figure. Cylindrical surface centered on the rolling center axis v of the ball 5 provided at each intermediate portion of the second spherical concave surface portions 23, 23 having the first spherical concave surface portion 21 and the second spherical concave surface portions 23, 23. Axial cylindrical concave surface portions 22, 22 configured as described above.

図２のように、第１球状凹面部２１とアキシャル円筒状凹面部２２との境界部分の近傍には、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部Ａが形成され、また、第２球状凹面部２３とアキシャル円筒状凹面部２２との境界部分の近傍には、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部Ｂが形成される。   As shown in FIG. 2, in the vicinity of the boundary portion between the first spherical concave surface portion 21 and the axial cylindrical concave surface portion 22, there is formed a lubricant reservoir portion A that holds the lubricant filled in the bearing, In the vicinity of the boundary portion between the second spherical concave surface portion 23 and the axial cylindrical concave surface portion 22, a lubricant reservoir B that holds the lubricant filled in the bearing is formed.

以上のように、図２の保持器２０を備えるラジアル玉軸受３０によれば、高負荷化を達成することができるとともに、軸受内部に充填された潤滑剤が図２の保持器２０の潤滑剤溜まり部Ａ，Ｂに保持されることにより、玉５が常に潤滑剤に覆われ、更に、上記半径比（ｒ３１／Ｄ，ｒ３３／Ｄ）が５２％以下であるために玉５の転動により軌道面３１，３３の溝から押し出された潤滑剤も保持器２０のポケット１８に溜まり、玉５を通じて軌道面３１，３３へ再び流れ込むことができるので、軸受の潤滑性能が向上し、軌道面３１，３３における潤滑不良や保持器音の発生を起こすことなく回転できる。また、軌道面３１，３３や玉５の転動面での表面剥離、玉５の焼付き等の発生を防止できる。   As described above, according to the radial ball bearing 30 provided with the cage 20 of FIG. 2, it is possible to achieve a high load, and the lubricant filled in the bearing is the lubricant of the cage 20 of FIG. Since the balls 5 are always covered with the lubricant by being held in the pool portions A and B, and the radius ratio (r31 / D, r33 / D) is 52% or less, the balls 5 are rolled. Since the lubricant pushed out from the grooves of the raceway surfaces 31 and 33 can also collect in the pocket 18 of the cage 20 and flow again into the raceway surfaces 31 and 33 through the balls 5, the lubrication performance of the bearing is improved and the raceway surface 31 is improved. , 33 can be rotated without causing poor lubrication or generation of cage noise. Moreover, generation | occurrence | production of the surface peeling in the raceway surfaces 31 and 33 and the rolling surface of the ball | bowl 5, the seizure of the ball | bowl 5, etc. can be prevented.

なお、図２，図４のような保持器２０は、成形金型を用いて樹脂により射出成形を行うことで製造できる。   2 and 4 can be manufactured by performing injection molding with resin using a molding die.

また、図２において、各ポケット１８とそれに隣り合うポケット１８との間の主部１７には、いわゆる肉盗み部が形成されており、空洞２６となっている。   In FIG. 2, a so-called meat stealing portion is formed in the main portion 17 between each pocket 18 and the pocket 18 adjacent to the pocket 18, thereby forming a cavity 26.

図１（ａ）のラジアル玉軸受３０は、その軸受内部に潤滑剤が充填されて使用されるが、潤滑剤としてグリースを用いることが好ましく、この場合、グリースの調度（グリースの粘度を示す指標）が２００乃至２８０の範囲内にあることが好ましい。このように比較的硬いグリースを潤滑剤として使用する場合、保持器のポケット形状が単一の球面状である場合、軸受使用中にグリースがポケットから一度外に押し出されると、なかなかポケット内に戻り難く、保持器において潤滑不良が発生し易くなってしまうが、本実施の形態のラジアル玉軸受３０によれば、図２のように保持器２０のポケット１８と玉５との間において、潤滑剤溜まり部Ａ，Ｂがそれぞれ形成され、グリースが潤滑剤溜まり部Ａ，Ｂに保持され、ポケット１８から外に押し出され難くなり、また、外に押し出されてもポケット１８内に戻り易くなるから、グリースによる潤滑性能を発揮し維持することができる。なお、保持器２０を後述の図６の構成としてもよく、グリースが潤滑剤溜まり部Ａ’，Ｂ’に保持されるので、同様にしてグリースによる潤滑性能を発揮し維持することができる。   The radial ball bearing 30 in FIG. 1 (a) is used with a lubricant filled in the bearing, but it is preferable to use grease as the lubricant. In this case, grease adjustment (an index indicating the viscosity of the grease) is used. ) Is preferably in the range of 200 to 280. When using relatively hard grease as a lubricant in this way, if the cage pocket shape is a single spherical shape, it will easily return to the pocket once the grease is pushed out of the pocket while the bearing is in use. Although it is difficult to cause poor lubrication in the cage, according to the radial ball bearing 30 of the present embodiment, the lubricant is provided between the pocket 18 and the ball 5 of the cage 20 as shown in FIG. Reservoir portions A and B are formed, respectively, and the grease is held in the lubricant reservoir portions A and B, so that it is difficult to push out from the pocket 18, and even if pushed out, it is easy to return into the pocket 18. Lubricating performance with grease can be demonstrated and maintained. Note that the cage 20 may be configured as shown in FIG. 6 described later, and since the grease is held in the lubricant reservoirs A ′ and B ′, the lubricating performance by the grease can be exhibited and maintained in the same manner.

以上のように本発明を実施するための最良の形態について説明したが、本発明はこれらに限定されるものではなく、本発明の技術的思想の範囲内で各種の変形が可能である。例えば、図６のように、図２の第１球状凹面部２１について半径Ｒ１の中心を玉５の中心ＯからＯ１にずらして半径Ｒ１よりも大きい半径Ｒ３とするとともに、第２球状凹面部２３，２３について半径Ｒ２の中心を玉５の中心ＯからＯ２にずらして半径Ｒ２よりも大きい半径Ｒ４としてもよい。図６において、第１球状凹面部２１とアキシャル円筒状凹面部２２との境界部分の近傍には、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部Ａ’が形成され、また、第２球状凹面部２３とアキシャル円筒状凹面部２２との境界部分の近傍には、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部Ｂ’が形成される。潤滑剤溜まり部Ａ’，Ｂ’は、図２と同様に、軸受内部に充填された潤滑剤を保持することができる。   As described above, the best mode for carrying out the present invention has been described. However, the present invention is not limited to these, and various modifications are possible within the scope of the technical idea of the present invention. For example, as shown in FIG. 6, the center of the radius R1 of the first spherical concave surface portion 21 of FIG. , 23, the center of the radius R2 may be shifted from the center O of the ball 5 to O2, and the radius R4 may be larger than the radius R2. In FIG. 6, in the vicinity of the boundary portion between the first spherical concave surface portion 21 and the axial cylindrical concave surface portion 22, a lubricant reservoir portion A ′ for holding the lubricant filled in the bearing is formed. In the vicinity of the boundary portion between the two spherical concave surface portions 23 and the axial cylindrical concave surface portion 22, a lubricant reservoir B ′ that holds the lubricant filled in the bearing is formed. The lubricant reservoirs A ′ and B ′ can hold the lubricant filled in the bearing as in FIG. 2.

また、図６において、第１球状凹面部２１の中心Ｏ１と半径Ｒ３の少なくとも一方、及び／又は、第２球状凹面部２３の中心Ｏ２と半径Ｒ４の少なくとも一方、及び／又は、アキシャル円筒状凹面部２２の転動中心軸ｖを中心とする半径を適宜変えることで、潤滑剤溜まり部Ａ’，Ｂ’のボリュームを適宜変更することができ、潤滑剤溜まり部Ａ’，Ｂ’における潤滑剤の保持量を調整可能である。   In FIG. 6, at least one of the center O1 and the radius R3 of the first spherical concave surface portion 21 and / or at least one of the center O2 and the radius R4 of the second spherical concave surface portion 23 and / or the axial cylindrical concave surface. The volume of the lubricant reservoirs A ′ and B ′ can be appropriately changed by appropriately changing the radius of the portion 22 around the rolling center axis v, and the lubricant in the lubricant reservoirs A ′ and B ′ can be appropriately changed. Can be adjusted.

本実施の形態によるラジアル玉軸受（半径比が５２％以下の場合の各軌道輪と玉を示す）の断面図（ａ）及び従来のラジアル玉軸受（半径比が５２％を超えた場合の各軌道輪と玉を示す）の断面図（ｂ）である。Sectional view (a) of a radial ball bearing according to this embodiment (showing each ring and ball when the radius ratio is 52% or less) and conventional radial ball bearings (each when the radius ratio exceeds 52%) It is sectional drawing (b) of a bearing ring and a ball | bowl is shown. 本実施の形態によるラジアル玉軸受の保持器を図４のV-V線方向と同様の方向で切断してみた要部断面図である。FIG. 5 is a cross-sectional view of an essential part of the radial ball bearing retainer according to the present embodiment, cut in the same direction as the VV line direction of FIG. 4. 従来のラジアル玉軸受の内部構成を概略的に示すために一部を破断した斜視図である。It is the perspective view which fractured | ruptured partially in order to show the internal structure of the conventional radial ball bearing roughly. 図３のラジアル玉軸受に配置可能な従来の樹脂製の冠型保持器を示す斜視図である。It is a perspective view which shows the conventional resin-made crown type holder | retainer which can be arrange | positioned to the radial ball bearing of FIG. 図４のV-V線方向に切断してみた保持器のポケットの要部断面図である。It is principal part sectional drawing of the pocket of the holder | retainer cut | disconnected in the VV line direction of FIG. 図２の保持器の変形例を示す図であって、図２と同様の図である。It is a figure which shows the modification of the holder | retainer of FIG. 2, Comprising: It is a figure similar to FIG.

符号の説明Explanation of symbols

１ 内輪軌道面
２ 内輪
３ 外輪軌道面
４ 外輪
５ 玉
１８ ポケット
２０ ラジアル玉軸受用保持器、保持器
２１ 第１球状凹面部
２２ アキシャル円筒状凹面部
２３ 第２球状凹面部
２９ ポケット
２９ 凹面部
３０ ラジアル玉軸受
３１ 内輪軌道面、軌道面
３３ 外輪軌道面、軌道面
Ａ，Ｂ 潤滑剤溜まり部
Ａ’，Ｂ’ 潤滑剤溜まり部
Ｄ 玉５の直径
Ｏ 玉５の中心
Ｔ 開口部
ｒ３１ 内輪軌道面３１の溝半径
ｒ３３ 外輪軌道面３３の溝半径
ｖ 転動中心軸 DESCRIPTION OF SYMBOLS 1 Inner ring raceway surface 2 Inner ring 3 Outer ring raceway surface 4 Outer ring 5 Ball 18 Pocket 20 Cage for radial ball bearing, Cage 21 First spherical concave portion 22 Axial cylindrical concave portion 23 Second spherical concave portion 29 Pocket 29 Concave portion 30 Radial ball bearing 31 Inner ring raceway surface, raceway surface 33 Outer ring raceway surface, raceway surface A, B Lubricant reservoir portion A ', B' Lubricant reservoir portion D Diameter of ball 5 O Center of ball 5 T Opening portion r31 Inner ring raceway surface 31 groove radius r33 groove radius of outer raceway surface 33 v rolling center axis

Claims (7)

外周面に内輪軌道面を有する内輪と内周面に外輪軌道面を有する外輪とを互いに同心に配置し、前記内輪軌道面と前記外輪軌道面との間に保持器を用いて複数の玉を保持し、
前記保持器は、全体を円環状に形成して円周方向の複数箇所にポケットを設け、前記各ポケットは前記玉が押し込まれる開口部と、前記玉が位置する凹面部と、を有するラジアル玉軸受であって、
前記内輪軌道面及び前記外輪軌道面の少なくとも一方の溝半径（ｒ’）と前記玉の直径（Ｄ）との半径比（ｒ’／Ｄ）が５２％以下であり、
前記保持器の前記凹面部は、前記開口部と対向する底面側に球状に形成された第１球状凹面部と、前記開口部側に球状に形成された第２球状凹面部と、前記第１球状凹面部と前記第２球状凹面部との間に前記玉の転動中心軸を中心として円筒状に形成されたアキシャル円筒状凹面部と、を備え、
前記第１球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍、及び、前記第２球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍に、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部を有することを特徴とするラジアル玉軸受。 An inner ring having an inner ring raceway surface on an outer peripheral surface and an outer ring having an outer ring raceway surface on an inner peripheral surface are arranged concentrically with each other, and a plurality of balls are placed between the inner ring raceway surface and the outer ring raceway surface using a cage. Hold and
The cage is formed in an annular shape as a whole, and pockets are provided at a plurality of locations in the circumferential direction. Each pocket has a radial ball having an opening into which the ball is pushed and a concave surface where the ball is located. A bearing,
A radius ratio (r ′ / D) between a groove radius (r ′) of at least one of the inner ring raceway surface and the outer ring raceway surface and a diameter (D) of the ball is 52% or less;
The concave surface portion of the cage includes a first spherical concave surface portion formed in a spherical shape on a bottom surface side facing the opening portion, a second spherical concave surface portion formed in a spherical shape on the opening portion side, and the first An axial cylindrical concave surface portion formed in a cylindrical shape around the rolling center axis of the ball between the spherical concave surface portion and the second spherical concave surface portion,
Lubrication filled in the bearing in the vicinity of the boundary between the first spherical concave surface and the axial cylindrical concave surface, and in the vicinity of the boundary between the second spherical concave and the axial cylindrical concave surface. A radial ball bearing having a lubricant reservoir for holding the agent. 前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心を略中心とする半径をそれぞれ有する請求項１に記載のラジアル玉軸受。   2. The radial ball bearing according to claim 1, wherein each of the first spherical concave surface portion and the second spherical concave surface portion has a radius that is substantially centered on a ball center in the pocket. 前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心からずれた位置を中心とする半径をそれぞれ有する請求項１に記載のラジアル玉軸受。   2. The radial ball bearing according to claim 1, wherein the first spherical concave surface portion and the second spherical concave surface portion each have a radius centered at a position shifted from a center of the ball in the pocket. 前記潤滑剤としてグリースを充填し、
前記グリースの調度が２００乃至２８０の範囲内にある請求項１，２または３に記載のラジアル玉軸受。 Filled with grease as the lubricant,
The radial ball bearing according to claim 1, wherein the grease has a degree of adjustment in a range of 200 to 280. ラジアル玉軸受の軌道面間に配置される複数の玉を転動自在に保持するために全体を円環状に形成して円周方向の複数箇所にポケットを設け、前記各ポケットは前記玉が押し込まれる開口部と、前記玉が位置する凹面部と、を有するラジアル玉軸受用保持器であって、
少なくとも一方の前記軌道面の溝半径（ｒ’）と前記玉の直径（Ｄ）との半径比（ｒ’／Ｄ）が５２％以下であり、
前記凹面部は、前記開口部と対向する底面側に球状に形成された第１球状凹面部と、前記開口部側に球状に形成された第２球状凹面部と、前記第１球状凹面部と前記第２球状凹面部との間に前記玉の転動中心軸を中心として円筒状に形成されたアキシャル円筒状凹面部と、を備え、
前記第１球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍、及び、前記第２球状凹面部と前記アキシャル円筒状凹面部との境界部分の近傍に、軸受内部に充填された潤滑剤を保持する潤滑剤溜まり部を有することを特徴とするラジアル玉軸受用保持器。 In order to hold a plurality of balls arranged between raceway surfaces of a radial ball bearing in a freely rolling manner, the whole is formed in an annular shape and provided with pockets in a plurality of circumferential directions, and the balls are pushed into each pocket. A radial ball bearing retainer having an opening and a concave surface where the ball is located,
A radius ratio (r ′ / D) between a groove radius (r ′) of at least one of the raceway surfaces and a diameter (D) of the ball is 52% or less;
The concave surface portion includes a first spherical concave surface portion that is spherically formed on the bottom surface facing the opening, a second spherical concave surface portion that is spherically formed on the opening side, and the first spherical concave surface portion. An axial cylindrical concave surface portion formed in a cylindrical shape around the rolling center axis of the ball between the second spherical concave surface portion,
Lubrication filled in the bearing in the vicinity of the boundary between the first spherical concave surface and the axial cylindrical concave surface, and in the vicinity of the boundary between the second spherical concave and the axial cylindrical concave surface. A radial ball bearing retainer having a lubricant reservoir for retaining the agent. 前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心を略中心とする半径をそれぞれ有する請求項５に記載のラジアル玉軸受用保持器。   The radial ball bearing retainer according to claim 5, wherein each of the first spherical concave surface portion and the second spherical concave surface portion has a radius that is substantially centered on the center of the ball in the pocket. 前記第１球状凹面部及び前記第２球状凹面部は、前記ポケット内の玉の中心からずれた位置を中心とする半径をそれぞれ有する請求項５に記載のラジアル玉軸受用保持器。   The radial ball bearing retainer according to claim 5, wherein the first spherical concave surface portion and the second spherical concave surface portion each have a radius centered at a position shifted from the center of the ball in the pocket.
JP2007205464A 2007-03-16 2007-08-07 Radial ball bearing and radial ball bearing cage Pending JP2008261481A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007205464A JP2008261481A (en) 2007-03-16 2007-08-07 Radial ball bearing and radial ball bearing cage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007068653 2007-03-16
JP2007205464A JP2008261481A (en) 2007-03-16 2007-08-07 Radial ball bearing and radial ball bearing cage

Publications (1)

Publication Number Publication Date
JP2008261481A true JP2008261481A (en) 2008-10-30

Family

ID=39984100

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2007205464A Pending JP2008261481A (en) 2007-03-16 2007-08-07 Radial ball bearing and radial ball bearing cage

Country Status (1)

Country Link
JP (1) JP2008261481A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107989903A (en) * 2017-12-19 2018-05-04 慈兴集团有限公司 A kind of lightweight ball bearing nylon holding frame
KR20220043321A (en) 2020-09-29 2022-04-05 셰플러코리아 유한책임회사 A Semi-tube Cage For Rolling Bearing Having Band

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107989903A (en) * 2017-12-19 2018-05-04 慈兴集团有限公司 A kind of lightweight ball bearing nylon holding frame
KR20220043321A (en) 2020-09-29 2022-04-05 셰플러코리아 유한책임회사 A Semi-tube Cage For Rolling Bearing Having Band

Similar Documents

Publication Publication Date Title
CN108397476A (en) Ball bearing
US9670958B2 (en) Rolling bearing
US11181149B2 (en) Rolling bearing
JP2012041940A (en) Retainer of cylindrical roller bearing and cylindrical roller bearing
JP2016180417A (en) Conical roller bearing
JP5187428B2 (en) Radial ball bearing cage and radial ball bearing
JP2008224026A (en) Rolling bearing and its cage
JP2008261478A (en) Radial ball bearing cage and radial ball bearing
JP2008249127A (en) Radial ball bearing cage and radial ball bearing
JP2008232420A (en) Cage for radial ball bearing, and radial ball bearing
JP2009138863A (en) Retainer for bearings
JP2008261481A (en) Radial ball bearing and radial ball bearing cage
JP2008267400A (en) Ball bearing
JP2008261482A (en) Retainer for radial ball bearing and radial ball bearing
JPH08200376A (en) Cage for roller bearing
JP2008261477A (en) Radial ball bearing cage and radial ball bearing
JP2015121236A (en) Self-aligning roller bearing
JP2008175239A (en) Ball bearing crown cage and ball bearing
JP2008261484A (en) Radial ball bearing cage and radial ball bearing
JP2008169999A (en) Retainer for radial ball bearing and radial ball bearing
JP3892213B2 (en) 4-point contact ball bearing
JP5348271B2 (en) Ball bearing
JP2008256201A (en) Radial ball bearing and retainer for radial ball bearing
JP2003254338A (en) Conical roller bearing
JP2006200672A (en) Thrust roller bearing