JPS5938453B2 - Gapless rolling bearing - Google Patents

Gapless rolling bearing

Info

Publication number
JPS5938453B2
JPS5938453B2 JP13460381A JP13460381A JPS5938453B2 JP S5938453 B2 JPS5938453 B2 JP S5938453B2 JP 13460381 A JP13460381 A JP 13460381A JP 13460381 A JP13460381 A JP 13460381A JP S5938453 B2 JPS5938453 B2 JP S5938453B2
Authority
JP
Japan
Prior art keywords
rolling
outer ring
bearings
elements
inner ring
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.)
Expired
Application number
JP13460381A
Other languages
Japanese (ja)
Other versions
JPS5834223A (en
Inventor
昭 高見
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP13460381A priority Critical patent/JPS5938453B2/en
Priority to PCT/JP1982/000331 priority patent/WO1983000729A1/en
Priority to DE19823248980 priority patent/DE3248980A1/en
Publication of JPS5834223A publication Critical patent/JPS5834223A/en
Publication of JPS5938453B2 publication Critical patent/JPS5938453B2/en
Expired legal-status Critical Current

Links

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
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Description

【発明の詳細な説明】 この発明は、一般機械要素としてのころがり軸受、特に
その内輪、外輪相互間に、がたつきが生じることなく使
用できる無間隙ころがり軸受に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rolling bearing as a general mechanical element, and more particularly to a gapless rolling bearing that can be used without rattling between the inner and outer rings.

従来周知のころがり軸受には、転動子の形状として、球
、針状または円筒状ころ、およびこれらの変形と考えら
れる円錐状ころ、蹴球状（逆つづみ状）ころなどが用い
られている。In conventional rolling bearings, the shapes of the rolling elements include balls, needles, or cylindrical rollers, as well as variations of these rollers, such as conical rollers and ball-shaped (inverted hexagonal) rollers. .

そして、これらの転動子と内輪、外輪との構成によつて
、ラジアル軸受、スラスト軸受、アンギユラコンタクト
軸受および自動調心軸受など機能上の特徴をもたせた各
形式のころがり軸受が製造され使用に供されている。こ
れらのころがり軸受における内輪、外輪相互間のがたつ
き（以下内外輪間がたつきと略す）について説明する。Various types of rolling bearings with functional characteristics such as radial bearings, thrust bearings, angular contact bearings, and self-aligning bearings are manufactured and used based on the configuration of these rolling elements, inner rings, and outer rings. It is served to. The rattling between the inner ring and the outer ring (hereinafter abbreviated as rattling between the inner and outer rings) in these rolling bearings will be explained.

ここで、内外輪間がたつきを機構的に整理し、ラジアル
方向がたつき、スラスト方向がたつきおよび中心軸の角
振れの３要素（いずれにおいても内外輪間のものである
が説明を省いている。以下も同様）に分解して扱うこと
にする。まず、ラジアル軸受においては、転動子が球、
針状等のころの如何にかかわらず、ラジアル方向がたつ
きがゼロもしくはマイナスであることが理想ではあるが
、製造上の加工寸法誤差や、マイナスがたつき品の組付
困難性の問題などから、通常は微少なラジアル方向がた
つきが許容されている。Here, we will mechanically organize the rattling between the inner and outer rings, and explain the three elements: radial wobbling, thrust wobbling, and angular runout of the center shaft (all of these are between the inner and outer rings, but we will explain them below). (The same applies below). First, in radial bearings, the rolling elements are balls,
Ideally, the radial wobble should be zero or negative, regardless of whether the rollers are needle-shaped, etc. However, there are problems such as manufacturing dimensional errors and the difficulty of assembling products with negative wobbling. Therefore, slight radial wobbling is usually allowed.

まして、ラジアル軸受におけるスラスト方向がたつきは
、上記ラジアル方向がたつきよりはるかに大であること
は機構的に明白である。また、中心軸の角振れについて
は、転動子として複列の球を用いたものおよび針状ころ
を用いたものなどが、単列の球を用いたものよりも比較
的少なく抑えられると云えるが、いずれにおいてもこれ
を完全に無くするようにはなつていない。次にスラスト
軸受においては、それ自体にスラスト方向がたつき規制
機能が備わつているものでなく、通常、ころがり軸受の
外からスラスト方向の力を受けて、しかも一方向のみに
スラスト方向がたつきを無くする構成がとり得るものと
しか云えない。Furthermore, it is mechanically clear that the thrust direction wobbling in a radial bearing is much larger than the above-mentioned radial direction wobbling. In addition, it is said that the angular runout of the center shaft can be suppressed comparatively less with rollers that use double rows of balls or needle rollers than with rollers that use a single row of balls. However, none of them has been able to completely eliminate this problem. Next, thrust bearings do not themselves have a function to regulate thrust direction wobbling, but are usually subjected to thrust direction force from outside the rolling bearing, and thrust direction wobbling occurs only in one direction. It can only be said that a configuration that eliminates the friction is possible.

また、スラスト軸受におけるラジアル方向がたつきは、
ラジアル軸受におけるスラスト方向がたつきの場合と同
様、両立して抑え得る機能は備わつていない。なお、ラ
ジアル方向がたつきとスラスト方向がたつきを共に抑え
るものとしてアンギユラコンタクト軸受があるが、これ
もころがり軸受単独で、内外輪間がたつきの抑制機能を
有しているのではなく、すくなくとも２個のころがり軸
受と、軸受外から受けるスラスト方向の力との組合せで
構成するなどではじめて内外輪間がたつきを無くするこ
とができるものである。In addition, the radial play in the thrust bearing is
As with the case of thrust direction wobbling in radial bearings, there is no function that can simultaneously suppress it. Angular contact bearings are used to suppress both radial and thrust vibrations, but these are not rolling bearings that have the function of suppressing rattles between the inner and outer rings. The rattling between the inner and outer rings can only be eliminated by a combination of at least two rolling bearings and a thrust force applied from outside the bearings.

また、特殊なものに、単列の球を転動子としたラジアル
軸受の内輪もしくは外輪のいずれか一方を、転動子が転
動する面に沿つて２分割し、それぞれに転動面をもたせ
て、残る外輪もしくは内輪の転動面と併せて、３方から
転動子を締めつけるように構成した無間隙ころがり軸受
も公知であるが、このもので無間隙効果を高めようとす
れば、転動部のすべり率が、著しく悪化するなど、ころ
がり軸受の基本機能を犠性にして、必要上やむなく構成
している例であり、やはり原理機構上からみた完全な無
間隙ころがり軸受であるとは云えない。In addition, in a special case, either the inner ring or the outer ring of a radial bearing with a single row of balls as rolling elements is divided into two parts along the surface on which the rolling elements roll, and each part has a rolling surface. Gapless rolling bearings are also known in which the rolling elements are tightened from three sides together with the remaining outer ring or inner ring rolling surface, but if this is used to enhance the gapless effect, This is an example of a rolling bearing being constructed out of necessity, at the cost of sacrificing the basic functions of a rolling bearing, such as the sliding rate of the rolling part being significantly deteriorated.After all, it is a perfect clearanceless rolling bearing from the mechanical principle point of view. I can't say that.

従来のころがり軸受は以上に説明したように、内外輪間
がたつきが全く無いという要件が、ころがり軸受自体に
備わつているものは無く、従つて内外輪間がたつきを無
くするためには、機械装置の構成上で、例えばラジアル
軸受にスラスト軸受の併用、ころがり軸受使用個数の追
加などの手段をとる必要があり、構成が複雑でかつコス
トもかかるという欠点があつた。As explained above, conventional rolling bearings do not have the requirement that there is no play between the inner and outer rings; therefore, in order to eliminate play between the inner and outer rings, However, it is necessary to take measures such as using a thrust bearing in combination with a radial bearing or using an additional number of rolling bearings in the configuration of the mechanical device, which has the disadvantage that the configuration is complicated and expensive.

この発明は上記のような従来のものの欠点をおぎなうた
めになされたもので、ころがり軸受の機素、すなわち内
輪、外輪および転動子をすきま無く構成させて、原理的
にも完全な無間隙ころがり軸受を提供することを目的と
している。This invention was made in order to overcome the above-mentioned drawbacks of the conventional bearings.The elements of a rolling bearing, that is, the inner ring, outer ring, and rolling elements, are configured without any gaps, and in principle, it is possible to achieve perfect clearance-free rolling. The purpose is to provide bearings.

以下、この発明の一実施例を図について説明する。An embodiment of the present invention will be described below with reference to the drawings.

第１図乃至第６図において、１０は円盤状の転動子、１
１はこの転動子１０の外周部に設けた転動面で、第３図
に示す外径ｄ１および半径ｒ１によつて構成される環状
曲面をなしている。２０は両側に鍔部を有し筒状部材か
ら形成される内輪、２１はこの内輪２０に備わつていて
、ころがり軸受を代表する内径部であつて、例えば回転
軸７７に圧入されるなどの方法で利用される部分である
。In FIGS. 1 to 6, 10 is a disk-shaped rolling element;
Reference numeral 1 denotes a rolling surface provided on the outer periphery of the rotor 10, which is an annular curved surface defined by an outer diameter d1 and a radius r1 shown in FIG. 20 is an inner ring formed from a cylindrical member having flanges on both sides, and 21 is an inner diameter portion that is included in this inner ring 20 and is representative of a rolling bearing, and is press-fitted into the rotating shaft 77, for example. This is the part used in this method.

２２，２３は、それぞれ前記内輪２０の外周上に、かつ
軸方向には互いに対向して設けられ、前記転動子１０と
接触して転動する第１、第２の転動面で、第４図に示す
直径Ｄ２および半径Ｒ２によつて構成される環状曲面を
なしている。22 and 23 are first and second rolling surfaces that are provided on the outer periphery of the inner ring 20 and facing each other in the axial direction, and that roll in contact with the rolling element 10; It has an annular curved surface formed by a diameter D2 and a radius R2 shown in FIG.

３０は端部に鍔部を有する外輪、３１はこの外輪３０に
備わつて、ころがり軸受を代表する外径部であつて、例
えば機械装置の本体部８８に圧入されるなどの方法で利
用される部分である。Reference numeral 30 denotes an outer ring having a flange at the end, and 31 is an outer diameter portion of the outer ring 30 representing a rolling bearing, which is used by, for example, being press-fitted into the main body 88 of a mechanical device. This is the part that

３２は前記外輪３０の内周に設けられ、前記転動子１０
と接触して転動する第３の転動面で、第５図に示す直径
Ｄ３および半径Ｒ３によつて構成される環状曲面をなし
ている。32 is provided on the inner periphery of the outer ring 30 and is connected to the rotor 10.
The third rolling surface that rolls in contact with the third rolling surface has an annular curved surface defined by a diameter D3 and a radius R3 shown in FIG.

３３は後記する副外輪を嵌合させる内管面、３４はこの
内管面３３の片方の側端近くに設けられ、後記する止め
輪を嵌着させるようにした環状溝である。Reference numeral 33 denotes an inner tube surface into which a sub-outer ring to be described later is fitted, and 34 is an annular groove provided near one side end of this inner tube surface 33 into which a retaining ring to be described later is fitted.

４０は端部に鍔部を有する副外輪、４１はこの副外輪４
０の外管部で、前記内管面３３に嵌合している。40 is a sub-outer ring having a flange at the end; 41 is this sub-outer ring 4;
The outer tube part 0 fits into the inner tube surface 33.

４２は前記副外輪４０の内周に設けられ、前記転動子１
０と接触して転動する第４の転動面で、第５図に示す直
径Ｄ４および半径Ｒ４によつて構成される環状曲面をな
している。42 is provided on the inner periphery of the auxiliary outer ring 40, and
This is the fourth rolling surface that rolls in contact with 0, and has an annular curved surface configured by a diameter D4 and a radius R4 shown in FIG.

５５は皿ばね、６６は止め輪である。55 is a disc spring, and 66 is a retaining ring.

皿ばね５５は圧縮状態で組付けられており、その拡張弾
力は止め輪６６を介して前記外輪３０と前記副外輪４０
との間で、前記転動子１０を挟みつける方向に作用して
いる。なお、転動子１０は、内輪２０と外輪３０および
副外輪４０とがかたちづくる円環状空間部に配置され、
内輪の一方の転動面２３と外輪の転動面３２とに接触し
て転動させるものと、内輪の他の一方の転動面２２と副
外輪の転動面４２とに接触して転動させるものとの各々
につき、すくなくとも３個以上、計６個以上で構成させ
ることが必要で、またこれらをほぼ半数ずつ、かつほぼ
交互に配列することが望ましい。The disc spring 55 is assembled in a compressed state, and its expansion elasticity is applied to the outer ring 30 and the sub-outer ring 40 via a retaining ring 66.
The roller 10 acts in a direction in which the rolling element 10 is sandwiched between the rollers 10 and 10. Note that the rolling element 10 is arranged in an annular space formed by the inner ring 20, the outer ring 30, and the sub-outer ring 40,
One that contacts the rolling surface 23 of the inner ring and the rolling surface 32 of the outer ring and rolls, and one that contacts the other rolling surface 22 of the inner ring and the rolling surface 42 of the auxiliary outer ring and rolls. It is necessary to configure at least three or more, six or more in total, for each of the movable parts, and it is desirable to arrange approximately half of these each and approximately alternately.

次に、このように構成したころがり軸受の作用を説明す
る。Next, the operation of the rolling bearing constructed in this way will be explained.

第６図はこの発明による無間隙ころがり軸受の単体状態
での構成機素間の作用力を示したものである。Ｆは皿ば
ね５５の働きによるばね力で、これによつて、４組の転
動面、すなわち１１−４２，１１−２２，１１−２３お
よび１１一３２で接触しているすべての転動子１０には
、等しい抗力Ｐが生じている。しかして、これらばね力
と抗力の大きさは、Ｐ−？Ｆなる関Ｎｃ：Ｉｉα 係式で表わすことができる。FIG. 6 shows the acting forces between the constituent elements of the gapless rolling bearing according to the present invention in a single unit state. F is the spring force due to the action of the disk spring 55, which causes all the rolling elements in contact at the four sets of rolling surfaces, namely 11-42, 11-22, 11-23 and 11-32. 10, an equal drag force P is generated. However, the magnitude of these spring force and drag force is P-? It can be expressed by the relationship F: Nc:Iiα.

担し、ｎは転動子１０の総数である。また、α−ＣＯｓ
−１詳？［」？＝ＡＬ）である。and n is the total number of rolling elements 10. Also, α-COs
-1 details? [”? =AL).

ここですべ９Ａ−一Ａｒ−ての転動子１０に抗力が作用
するということは、このころがり軸受が、構成機素間の
どの部分にもすきまを生じておらず、従つて、ラジアル
方向がたつき、スラスト方向がたつきおよび中心軸の角
振れのいずれをも生じさせない構成を原理的に示してい
るのと同様である。Here, the fact that a drag force acts on all the rolling elements 10 means that this rolling bearing does not have any gaps between its constituent elements, and therefore the radial direction is This is similar to the principle that shows a configuration that does not cause wobbling, thrust direction wobbling, or angular wobbling of the central axis.

しかも、転動子１０に作用する外力は、ころがり軸受と
しての正規の転動面に正常方向に生じる抗力Ｐ以外には
一切無く、内輪２０についてもまた同様であり、この軸
受が、ころがり理論を何らさまたげることなく、内外輪
間がたつきを皆無となし得たものであることは明白であ
る。Furthermore, there is no external force acting on the rolling element 10 other than the drag force P that occurs in the normal direction on the normal rolling surface of a rolling bearing, and the same is true for the inner ring 20, which makes it possible for this bearing to comply with the rolling theory. It is clear that it has been possible to eliminate all the fluctuations between the inner and outer rings without any hindrance.

なお、以上の実施例の説明においては、第３図乃至第５
図に代数的に示した転動面の寸法関係はＲ２：Ｒ３：Ｒ
４：ｒ１ラＤ３動Ｄ４として扱つたｏ上記の実施例では
、外輪側で転動面を分離し、外輪３０、副外輪４０で構
成したもので説明したが、内輪側に置き替えても効果は
同様に構成できる。In addition, in the above description of the embodiment, FIGS.
The dimensional relationship of the rolling surface shown algebraically in the figure is R2:R3:R
4: treated as r1 D3 dynamic D4 o In the above embodiment, the rolling surface was separated on the outer ring side and was explained as consisting of an outer ring 30 and a sub-outer ring 40, but the effect can be obtained even if it is replaced on the inner ring side. can be constructed similarly.

また、外輪、副外輪という形ではなく実施例における副
外輪４０様の単純な形状の外輪２個を直接本体部８８に
取付け、加圧作用も本体部に移して構成すれば、より単
純構造となる場合も考えられる。なお、このような無間
隙ころがり軸受を必要とする応用例としては、機関点火
用配電器のブレーカにおける真空進角用ベースの軸受、
力ークーラ一のコンプレツサ一におけるアイドルカツト
用空転プーリの軸受などがある。以上のように、この発
明によれば円盤状の転動子でころがり軸受を構成したの
で、・ころがり軸受の基本機能を犠性にすることなく完
全な無間隙ころがり軸受が安価に得られる効果がある。Furthermore, instead of having an outer ring and a sub-outer ring, two simple outer rings, such as the sub-outer ring 40 in the embodiment, can be attached directly to the main body 88, and the pressure action can also be transferred to the main body, resulting in a simpler structure. There may be cases where this happens. Examples of applications that require such gapless rolling bearings include vacuum advance angle base bearings in engine ignition power distributor breakers;
Examples include bearings for idle pulleys for idle cuts in compressors for power coolers. As described above, according to the present invention, since the rolling bearing is configured with disk-shaped rolling elements, it is possible to obtain a complete clearance-free rolling bearing at low cost without sacrificing the basic functions of the rolling bearing. be.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図はこの発明の一実施例による無間隙ころがり軸受
を示す断面側面図、第２図は第１図における−線による
断面図、第３図は転動子の平面図とその側面図、第４図
は内輪の断面側面図、第５図は外輪および副外輪の断面
側面図、第６図は構成機素間の作用力を示した図である
。FIG. 1 is a cross-sectional side view showing a gapless rolling bearing according to an embodiment of the present invention, FIG. 2 is a cross-sectional view taken along the - line in FIG. 1, and FIG. 3 is a plan view of a rolling element and a side view thereof. FIG. 4 is a cross-sectional side view of the inner ring, FIG. 5 is a cross-sectional side view of the outer ring and the sub-outer ring, and FIG. 6 is a diagram showing the acting forces between the constituent elements.

Claims (1)

【特許請求の範囲】 １ 略々円盤状に形成されかつ円周部分に転動面を有し
てなる複数の転動子、軸方向において略々対向した位置
に形成された上記転動子を転動せしめる第１、第２の転
動面を有する内輪、該内輪の径方向外側に設けられ、か
つ上記軸方向において略々対向した位置に形成された上
記転動子を転動せしめる第３、第４の転動面を有する外
輪を備え、内輪をその両端に上記第１と第２の転動面を
形成するための鍔部を有する筒状部材にて構成し、外輪
を上記第３の転動面を形成するための鍔部を有する筒状
部材と該筒状部材に嵌合し上記第４の転動面を形成する
ための鍔部を有する筒状部材とにより構成し、上記複数
の転動子を夫々上記内輪と外輪の第１と第４、第２と第
３の転動面で接触せしめることにより、円周方向におい
て交互に傾斜させて配設し、かつ上記第４の転動面を形
成するための鍔部を有する筒状部材を、皿ばねにより上
記転動子を挟み込むように付勢することにより、上記各
転動子の転動面上での抗力を略々均等となるように構成
したことを特徴とする無間隙ころがり軸受。 ２ 複数の転動子を６個にて構成し、３個を上記第１と
第４の転動面に、残り３個を第２と第３の転動面に夫々
接触せしめ、これらを円周方向において交互に傾斜させ
て配設したことを特徴とする特許請求の範囲第１項に記
載の無間隙ころがり軸受。[Scope of Claims] 1. A plurality of rolling elements each having a substantially disk shape and having a rolling surface on a circumferential portion, the rolling elements being formed at substantially opposite positions in the axial direction. an inner ring having first and second rolling surfaces for rolling, and a third roller for rolling the rolling elements, which are provided on the radially outer side of the inner ring and are formed at positions substantially opposite to each other in the axial direction; , an outer ring having a fourth rolling surface, an inner ring made of a cylindrical member having flanges at both ends thereof for forming the first and second rolling surfaces, and an outer ring having a fourth rolling surface. a cylindrical member having a flange for forming the fourth rolling surface; and a cylindrical member having a flange for fitting into the cylindrical member and forming the fourth rolling surface; The plurality of rolling elements are arranged so as to be inclined alternately in the circumferential direction by contacting the first and fourth and second and third rolling surfaces of the inner ring and the outer ring, respectively, and By biasing a cylindrical member having a flange for forming a rolling surface with a disc spring so as to sandwich the rolling element, the drag force on the rolling surface of each of the rolling elements can be substantially reduced. A gapless rolling bearing characterized in that it is configured so that the bearings are evenly spaced. 2 Consisting of six rolling elements, three of which are brought into contact with the first and fourth rolling surfaces, and the remaining three are brought into contact with the second and third rolling surfaces, and these are brought into contact with a circular shape. The gapless rolling bearing according to claim 1, characterized in that the bearings are arranged so as to be inclined alternately in the circumferential direction.
JP13460381A 1981-08-24 1981-08-26 Gapless rolling bearing Expired JPS5938453B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP13460381A JPS5938453B2 (en) 1981-08-26 1981-08-26 Gapless rolling bearing
PCT/JP1982/000331 WO1983000729A1 (en) 1981-08-24 1982-08-24 Roller bearing
DE19823248980 DE3248980A1 (en) 1981-08-24 1982-08-24 BALL AND ROLLER BEARINGS

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP13460381A JPS5938453B2 (en) 1981-08-26 1981-08-26 Gapless rolling bearing

Publications (2)

Publication Number Publication Date
JPS5834223A JPS5834223A (en) 1983-02-28
JPS5938453B2 true JPS5938453B2 (en) 1984-09-17

Family

ID=15132254

Family Applications (1)

Application Number Title Priority Date Filing Date
JP13460381A Expired JPS5938453B2 (en) 1981-08-24 1981-08-26 Gapless rolling bearing

Country Status (1)

Country Link
JP (1) JPS5938453B2 (en)

Also Published As

Publication number Publication date
JPS5834223A (en) 1983-02-28

Similar Documents

Publication Publication Date Title
US6527449B1 (en) Pivot bearing
JP2006528326A (en) Bearing race and wheel bearing device
US5443317A (en) Rolling bearing having balls of different diameters
JP2012132495A (en) Rolling bearing unit with mounting plate
JP3419053B2 (en) Double-row rolling bearing device with preload
JP2009243555A (en) Bearing unit and pivot device
JPS5938453B2 (en) Gapless rolling bearing
US3058788A (en) Anti-friction bearing
JPS6196217A (en) Device for fixing inner race of bearing to shaft
JPS5834222A (en) Rolling bearing
JPS5855362B2 (en) Bidirectional load type ball bearing
JPS5834224A (en) Rolling bearing
JP3064441B2 (en) Bearing structure and spindle motor
JP2841648B2 (en) Magnetic disk drive
JPS6030491Y2 (en) Thrust bearing device
JP4113979B2 (en) Rolling bearing
JP2000055044A (en) Ball-and-roller bearing
JP2000039026A (en) Bearing unit for swing arm
JPS5931934Y2 (en) Spacer for combination bearing
JPH04157208A (en) Needle type roller bearing
JPH0953644A (en) Shaft fixed with externally fit inner ring
JPS6318829Y2 (en)
JPH0324894Y2 (en)
JPH0648179Y2 (en) spindle
JP2589053Y2 (en) Combination bearing device