JP2000291665A - Rolling bearing - Google Patents
Rolling bearingInfo
- Publication number
- JP2000291665A JP2000291665A JP11099145A JP9914599A JP2000291665A JP 2000291665 A JP2000291665 A JP 2000291665A JP 11099145 A JP11099145 A JP 11099145A JP 9914599 A JP9914599 A JP 9914599A JP 2000291665 A JP2000291665 A JP 2000291665A
- Authority
- JP
- Japan
- Prior art keywords
- curvature
- radius
- raceway surface
- rolling bearing
- arc
- 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
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/70—Diameters; Radii
- F16C2240/76—Osculation, i.e. relation between radii of balls and raceway groove
-
- 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
- F16C2360/00—Engines or pumps
- F16C2360/46—Fans, e.g. ventilators
-
- 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
- F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は転がり軸受に係り、
例えば流体継ぎ手（冷却装置のフアンカップリング装
置）等に用いられる転がり軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling bearing,
For example, the present invention relates to a rolling bearing used for a fluid joint (fan coupling device of a cooling device) and the like.
【０００２】[0002]
【従来の技術】図４に示すように、一般的な冷却装置を
構成するファンカップリング装置40は、モータ41の回転
軸42に直結された軟鋼製軸43と、アルミ製のハウジング
45とが転がり軸受50を介して連結され、軟鋼製軸43の先
端に固定されたアルミ製のロータ44と、ハウジング45と
の相互対向面にそれぞれ同心円状に設けられた多数の溝
を組み合わせることによりラビリンス46が形成されてい
る。そして、ファンカップリング装置40は、モータ41の
軌道に伴ってロータ44が回転すると、ラビリンス46に封
入されたシリコーンオイル47の粘性抵抗によりハウジン
グ45が連れ回り、これによりハウジング45に装着された
冷却ファン48を回転させる。2. Description of the Related Art As shown in FIG. 4, a fan coupling device 40 constituting a general cooling device comprises a mild steel shaft 43 directly connected to a rotating shaft 42 of a motor 41, and an aluminum housing.
45 is connected via a rolling bearing 50, and an aluminum rotor 44 fixed to the tip of a mild steel shaft 43 is combined with a number of grooves provided concentrically on the mutually facing surfaces of the housing 45. The labyrinth 46 is formed by this. When the rotor 44 rotates along with the trajectory of the motor 41, the fan coupling device 40 rotates the housing 45 due to the viscous resistance of the silicone oil 47 sealed in the labyrinth 46. Rotate the fan 48.
【０００３】図５に示すように、転がり軸受50は、外輪
51の外輪軌道面51Ａと、内輪52の内輪軌道面52Ａとの間
に配置された球状の転動体53を有し、内輪軌道面52Ａの
断面形状および外輪軌道面51Ａの断面形状が一定曲率半
径を有する円弧面とされている。このような転がり軸受
50は、外輪軌道面51Ａの断面曲率半径が内輪軌道面52Ａ
の断面曲率半径よりも大きく設定されていることが多
い。As shown in FIG. 5, a rolling bearing 50 includes an outer ring.
51, a spherical rolling element 53 disposed between the outer raceway surface 51A of the inner race 52 and the inner raceway surface 52A of the inner race 52. The cross-sectional shape of the inner raceway surface 52A and the cross-sectional shape of the outer raceway surface 51A have a constant radius of curvature. Are formed. Such a rolling bearing
50 is a cross-sectional radius of curvature of the outer ring raceway surface 51A, the inner ring raceway surface 52A.
Are often set to be larger than the section radius of curvature.
【０００４】また、フアンカップリング装置40に用いら
れる転がり軸受50の耐用期間は、当該転がり軸受50に作
用する荷重が小さいため、外輪51，内輪52，転動体53等
に生じる金属疲労の影響よりも、当該転がり軸受30に封
入されるグリースの劣化に大きく左右される。このた
め、フアンカップリング装置40に用いられる転がり軸受
50は、高温時においても良好な潤滑が得られるように、
あらかじめシリコーン系あるいはフッ素系等の流動性が
低い耐熱グリースが封入されている。[0004] The life of the rolling bearing 50 used in the fan coupling device 40 depends on the effect of metal fatigue on the outer ring 51, the inner ring 52, the rolling elements 53, etc. because the load acting on the rolling bearing 50 is small. This is also greatly affected by the deterioration of the grease sealed in the rolling bearing 30. For this reason, the rolling bearing used in the fan coupling device 40
50, so that good lubrication can be obtained even at high temperatures,
Heat-resistant grease having low fluidity such as silicone or fluorine is sealed in advance.
【０００５】ところで、フアンカップリング装置40を高
温下で運転すると、ハウジング45を介して転がり軸受50
が加熱されるため、転がり軸受50の外輪51が膨張し、外
輪軌道面51Ａと転動体53との間のラジアルすきまが大き
くなる。前述したように、転がり軸受50は、外輪軌道面
51Ａの断面曲率半径が内輪軌道面52Ａの断面曲率半径よ
りも大きいため、ラジアルすきまが大きくなると、内輪
52の軸線に対して外輪51の軸線が傾斜可能な状態とな
る。When the fan coupling device 40 is operated at a high temperature, the rolling bearing 50
Is heated, the outer ring 51 of the rolling bearing 50 expands, and the radial clearance between the outer ring raceway surface 51A and the rolling element 53 increases. As described above, the rolling bearing 50 is provided on the outer raceway surface.
Since the cross-sectional radius of curvature of 51A is larger than the cross-sectional radius of curvature of inner ring raceway surface 52A, when the radial clearance increases, the inner ring
The axis of the outer race 51 can be inclined with respect to the axis of 52.
【０００６】この場合、フアンカップリング装置40は、
ロータ44およびハウジング45の相対位置や相対角度が変
化して、ラビリンス46のラビリンス隙間が増減したり、
あるいはロータ44およびハウジング45が互いに接触する
というラビリンス干渉が生じる虞れがある。このため、
フアンカップリング装置40に用いられる転がり軸受50
は、高温下においてラビリンス干渉が生じないように、
外輪51が膨張することを考慮して、あらかじめラジアル
すきまをマイナスすきま（負すきま）としている。In this case, the fan coupling device 40 is
The relative position and the relative angle of the rotor 44 and the housing 45 change, the labyrinth gap of the labyrinth 46 increases or decreases,
Alternatively, there is a possibility that labyrinth interference occurs in which the rotor 44 and the housing 45 come into contact with each other. For this reason,
Rolling bearing 50 used for fan coupling device 40
Is to avoid labyrinth interference at high temperature,
In consideration of the expansion of the outer ring 51, the radial clearance is previously set to a minus clearance (a minus clearance).
【０００７】[0007]
【発明が解決しようとする課題】一方、フアンカップリ
ング装置40を低温下において運転した場合、冷却された
外輪51が縮径するため、転がり軸受50のラジアルすきま
が小さくなる。この場合、転がり軸受50は、転動体53と
外輪軌道面51Ａ，内輪軌道面52Ａとの間にグリースを引
き込み難くなるため潤滑不良が生じやすく、これにより
異音や焼付が生ずる虞れがある。特に、低温下において
は、耐熱グリースの流動性が一層低くなるため、転がり
軸受50に潤滑不良が一層生じ易くなるという問題があっ
た。On the other hand, when the fan coupling device 40 is operated at a low temperature, the diameter of the cooled outer ring 51 is reduced, so that the radial clearance of the rolling bearing 50 is reduced. In this case, in the rolling bearing 50, it is difficult to draw grease between the rolling element 53 and the outer raceway surface 51A and the inner raceway surface 52A, so that poor lubrication is likely to occur, which may cause abnormal noise and seizure. In particular, at low temperatures, since the fluidity of the heat-resistant grease is further reduced, there is a problem that the lubrication failure of the rolling bearing 50 is more likely to occur.
【０００８】この問題に対して、あらかじめ外輪軌道面
51Ａ，内輪軌道面52Ａの断面曲率半径を転動体53におけ
る転動面の曲率半径よりも大きく設定しておくことが考
えられる。しかしながら、この場合、常温下においても
内輪52の軸線に対して外輪51の軸線が傾斜可能な状態と
なることを回避するために、外輪軌道面51Ａ，内輪軌道
面52Ａの断面曲率半径に上限があり、有効な解決策とは
ならない。[0008] To solve this problem, the outer raceway surface
It is conceivable that the radius of curvature of the cross section of the inner raceway surface 51A and the inner raceway surface 52A is set to be larger than the radius of curvature of the rolling surface of the rolling element 53. However, in this case, in order to avoid the state where the axis of the outer ring 51 can be inclined with respect to the axis of the inner ring 52 even at normal temperature, the upper limit is set to the cross-sectional radius of curvature of the outer ring raceway surface 51A and the inner ring raceway surface 52A. Yes, not a valid solution.
【０００９】本発明は、前述した問題点に鑑みてなされ
たものであり、その目的は高温下における軸線傾斜を抑
制できるとともに、低温下における潤滑不足が生じ難い
転がり軸受を提供することにある。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and an object of the present invention is to provide a rolling bearing that can suppress the inclination of an axis at a high temperature and that does not easily cause insufficient lubrication at a low temperature.
【００１０】[0010]
【課題を解決するための手段】前述した目的を達成する
ために、本発明は、外輪軌道面および内輪軌道面間に転
動体が配置された転がり軸受であって、前記外輪軌道面
および内輪軌道面のうちの一方の断面形状が第１円弧
と、前記第１円弧を挟むとともに凹凸が生じないように
連続する一対の第２円弧とを有し、前記第１円弧の曲率
半径が前記転動体における転動面の曲率半径よりも大き
く設定されているとともに、前記第２円弧の曲率半径が
前記第１円弧の曲率半径よりも小さく設定されているこ
とを特徴としている。In order to achieve the above-mentioned object, the present invention relates to a rolling bearing having a rolling element disposed between an outer raceway surface and an inner raceway surface, wherein the outer raceway surface and the inner raceway are provided. One of the surfaces has a first circular arc, and a pair of second circular arcs sandwiching the first circular arc so as not to cause unevenness, and the radius of curvature of the first circular arc is the rolling element. And the curvature radius of the second circular arc is set smaller than the radius of curvature of the first circular arc.
【００１１】ここで、本発明は、球状の転動体を採用し
た転がり軸受に限定せず、円筒形状，円錐形状，樽形状
等の転動体を採用した転がり軸受にも適用可能であり、
冷却装置のフアンカップリング装置以外の各種装置にも
適用可能である。また、第２円弧は、第１円弧より小さ
ければよく、転動面の曲率半径よりも大きくても小さく
てもよい。そして、第１円弧および第２円弧の境界部分
が峰あるいは谷とならないように、第１円弧の円弧端部
と円弧中心とを結ぶ線状に、第２円弧の円弧中心を設定
すればよい。このような断面形状を有する軌道面は、外
輪および内輪のうちの一方のみ、あるいは双方に適用し
てもよい。Here, the present invention is not limited to a rolling bearing employing a spherical rolling element, but is also applicable to a rolling bearing employing a cylindrical, conical or barrel-shaped rolling element.
The present invention is also applicable to various devices other than the fan coupling device of the cooling device. The second arc may be smaller than the first arc, and may be larger or smaller than the radius of curvature of the rolling surface. Then, the arc center of the second arc may be set in a line connecting the arc end of the first arc and the arc center so that the boundary between the first arc and the second arc does not become a peak or a valley. The raceway surface having such a cross-sectional shape may be applied to only one or both of the outer ring and the inner ring.
【００１２】このような転がり軸受においては、外輪軌
道面あるいは内輪軌道面を構成する第１円弧の曲率半径
が転動体における転動面の曲率半径よりも大きく設定さ
れているため、低温下においても転動体および軌道面間
にグリースを確実に引き込み可能となり、これにより潤
滑不良が生じないことになる。また、この転がり軸受に
おいては、第２円弧の曲率半径が第１円弧の曲率半径よ
りも小さく設定されているため、軌道面の断面形状が一
定曲率半径を有する円弧面である場合に比較して、軌道
面の断面開口が若干閉じ気味の略Ｕ字状となる。すなわ
ち、この転がり軸受においては、高温下においてラジア
ル隙間が増大しても、各第２円弧の断面端部が転動体の
転動面に接触することにより、内輪に対する外輪の傾斜
角度を一定以下に規制できることになる。従って、この
ような転がり軸受においては、従来に比較して、高温下
における軸線傾斜を抑制できるとともに、低温下におけ
る潤滑不足を解消でき、これにより前述した目的を達成
できる。In such a rolling bearing, since the radius of curvature of the first arc constituting the outer raceway surface or the inner raceway surface is set to be larger than the radius of curvature of the rolling surface of the rolling element, even at a low temperature. Grease can be reliably drawn in between the rolling elements and the raceway surface, thereby preventing poor lubrication. Further, in this rolling bearing, the radius of curvature of the second arc is set smaller than the radius of curvature of the first arc, so that the cross-sectional shape of the raceway surface is an arc surface having a constant radius of curvature. In this case, the cross-section opening of the raceway surface is slightly closed, and becomes substantially U-shaped. That is, in this rolling bearing, even if the radial gap increases at high temperatures, the cross-sectional end of each second arc contacts the rolling surface of the rolling element, so that the inclination angle of the outer ring with respect to the inner ring is kept to a certain value or less. It will be able to regulate. Therefore, in such a rolling bearing, the inclination of the axis at a high temperature can be suppressed and insufficient lubrication at a low temperature can be eliminated, thereby achieving the object described above.
【００１３】なお、本発明は、各第２円弧面に対して凹
凸が生じないように連続する第３円弧を有していてもよ
い。このような転がり軸受においては、第３円弧の曲率
半径が転動体における転動面の曲率半径に等しければ、
高温下においてラジアル隙間が増大して外輪の軸線およ
び内輪の軸線が傾斜した状態でも潤滑不足が生じないこ
とになる。The present invention may have a third circular arc which is continuous so that no irregularities are formed on each of the second circular arc surfaces. In such a rolling bearing, if the radius of curvature of the third arc is equal to the radius of curvature of the rolling surface of the rolling element,
Under a high temperature, the radial gap increases and the lubrication deficiency does not occur even when the axis of the outer ring and the axis of the inner ring are inclined.
【００１４】[0014]
【発明の実施の形態】以下、本発明に係る実施形態を、
図面に基づいて詳細に説明する。なお、以下に説明する
各実施形態において、既に図４および図５において説明
した部材等については、図中相当符号を付すことによ
り、説明を簡単化あるいは省略する。BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, an embodiment according to the present invention will be described.
This will be described in detail with reference to the drawings. In addition, in each embodiment described below, the members and the like already described in FIGS. 4 and 5 are denoted by the same reference numerals in the drawings to simplify or omit the description.
【００１５】図１（Ａ）に示すように、本発明に係る第
１実施形態の転がり軸受10は、外輪11の外輪軌道面11Ａ
と、内輪12の内輪軌道面12Ａとの間に球状の転動体13が
配置されている。そして、図１（Ｂ）に示すように、内
輪軌道面12Ａの断面形状は、中心部の第１円弧14と、第
１円弧14を挟んで凹凸が生じないように滑らかに連続す
る一対の第２円弧15，15と、各第２円弧15，15に対して
凹凸が生じないように滑らかに連続する一対の第３円弧
15，15とを有している。As shown in FIG. 1A, a rolling bearing 10 according to a first embodiment of the present invention comprises an outer raceway surface 11A of an outer race 11.
And a spherical rolling element 13 is disposed between the inner race 12 and the inner raceway surface 12A of the inner race 12. As shown in FIG. 1 (B), the cross-sectional shape of the inner raceway surface 12A has a first circular arc 14 at the center and a pair of first circular arcs 14 which smoothly intersect the first circular arc 14 so as not to cause irregularities. Two circular arcs 15, 15 and a pair of third circular arcs that are smoothly continuous so as not to cause irregularities in each of the second circular arcs 15, 15.
15 and 15.
【００１６】第１円弧14の曲率半径Ｒ１は、転動体13に
おける曲率半径Ｄ／２以上に大きく設定されている。ま
た、各第２円弧15の曲率半径Ｒ２は、曲率半径Ｒ１より
も小さく設定されている。そして、各第３円弧15の曲率
半径Ｒ３は、曲率半径Ｒ１に等しく設定されている。The radius of curvature R1 of the first circular arc 14 is set to be larger than the radius of curvature D / 2 of the rolling element 13. The radius of curvature R2 of each second arc 15 is set smaller than the radius of curvature R1. The radius of curvature R3 of each third arc 15 is set equal to the radius of curvature R1.
【００１７】すなわち、内輪軌道面12Ａの断面形状は、 Ｒ１＝Ｒ３＞Ｒ２≧Ｄ／２ とされている。従って、内輪軌道面12Ａの断面形状は、
一定の曲率半径を有する円弧である場合に比較して、断
面端部が転動体13に接近するように断面開口が若干閉じ
た断面略Ｕ字状とされている。That is, the cross-sectional shape of the inner raceway surface 12A is such that R1 = R3> R2 ≧ D / 2. Therefore, the cross-sectional shape of the inner raceway surface 12A is
Compared to the case of an arc having a constant radius of curvature, the cross-section opening is slightly U-shaped so that the cross-section opening is slightly closed so that the cross-section end approaches the rolling element 13.
【００１８】このような第１実施形態によれば、内輪軌
道面12Ａを構成する第１円弧14の曲率半径Ｒ１が転動体
13における転動面の曲率半径Ｄ／２よりも大きく設定さ
れているため、低温下においても内輪軌道面12Ａおよび
転動体13にグリースを確実に引き込み可能となり、これ
により潤滑不良が生じない。また、この第１実施形態に
よれば、各第２円弧15により内輪軌道面12Ａの断面開口
が若干閉じ気味の略Ｕ字状であるため、高温下において
ラジアル隙間が増大しても、内輪12に対する内輪11の傾
斜角度を一定以下に規制できる。すなわち、第１実施形
態の転がり軸受10によれば、内輪軌道面12Ａの断面形状
が一定の曲率半径を有する円弧である場合に比較して、
高温下における軸線傾斜を抑制できるとともに、低温下
における潤滑不足を解消できる。According to the first embodiment, the radius of curvature R1 of the first circular arc 14 constituting the inner raceway surface 12A is determined by the rolling element.
Since the radius of curvature of the rolling surface in D13 is set to be larger than D / 2, grease can be reliably drawn into the inner raceway surface 12A and the rolling element 13 even at a low temperature, thereby preventing poor lubrication. Also, according to the first embodiment, since the cross-sectional opening of the inner raceway surface 12A is slightly closed by each second arc 15, the inner raceway surface 12A tends to be slightly U-shaped. Can be restricted to a certain angle or less. That is, according to the rolling bearing 10 of the first embodiment, compared to the case where the cross-sectional shape of the inner raceway surface 12A is an arc having a constant radius of curvature,
It is possible to suppress the inclination of the axis at a high temperature and to eliminate the insufficient lubrication at a low temperature.
【００１９】また、第１実施形態の転がり軸受10は、内
輪軌道面12Ａが第３円弧16を有し、これらの第３円弧16
の曲率半径Ｒ３が第１円弧14の曲率半径Ｒ１に等しく、
換言すれば各第３円弧16の曲率半径Ｒ３が転動面の曲率
半径Ｄ／２よりも大きく設定されているため、内輪12に
対して外輪11が傾斜した状態でも内輪軌道面12Ａと転動
体13との間にグリースを確実に引き込み可能となる。す
なわち、第１実施形態の転がり軸受10によれば、内輪12
に対して外輪11が傾斜した状態でも潤滑不良が生じず、
常に安定した性能を発揮できる。Further, in the rolling bearing 10 of the first embodiment, the inner raceway surface 12A has the third circular arcs 16, and these third circular arcs 16 are formed.
Is equal to the radius of curvature R1 of the first arc 14,
In other words, since the radius of curvature R3 of each third arc 16 is set to be larger than the radius of curvature D / 2 of the rolling surface, even when the outer ring 11 is inclined with respect to the inner ring 12, the inner ring raceway surface 12A and the rolling element Grease can be reliably drawn in between the grease 13 and the grease. That is, according to the rolling bearing 10 of the first embodiment, the inner race 12
In contrast, even when the outer ring 11 is inclined, poor lubrication does not occur,
It can always exhibit stable performance.
【００２０】次に、図２（Ａ）に示す第２実施形態の転
がり軸受20は、前述した第１実施形態と同様に、内輪軌
道面22Ａの断面形状が中心部の第１円弧24と、第１円弧
24を挟んで凹凸が生じないように滑らかに連続する一対
の第２円弧25，25と、各第２円弧25に滑らかに連続する
第３円弧26，26とを有している。Next, the rolling bearing 20 of the second embodiment shown in FIG. 2 (A) has a first circular arc 24 having a center portion whose inner ring raceway surface 22A has a cross-sectional shape similar to the first embodiment described above. 1st arc
It has a pair of second arcs 25, 25 that are smoothly continuous so that no irregularities are formed across the 24, and third arcs 26, 26 that are smoothly continuous with each second arc 25.
【００２１】この転がり軸受20において、転動体23の曲
率半径Ｄ／２に対する第１円弧24の曲率半径Ｒ１，各第
２円弧25の曲率半径Ｒ２および各第３円弧26の曲率半径
Ｒ３は、 Ｒ１＞Ｒ３＞Ｒ２≧Ｄ／２ とされている。すなわち、この転がり軸受20において、
内輪軌道面22Ａの断面形状は、前述した第１実施形態に
比較して、さらに断面形状が閉じた断面略Ｕ字状となっ
ている。In this rolling bearing 20, the radius of curvature R1 of the first circular arc 24, the radius of curvature R2 of each second circular arc 25, and the radius of curvature R3 of each third circular arc 26 with respect to the radius of curvature D / 2 of the rolling element 23 are R1. >R3> R2 ≧ D / 2. That is, in this rolling bearing 20,
The cross-sectional shape of the inner raceway surface 22A is substantially U-shaped in cross section as compared with the first embodiment described above.
【００２２】このような第２実施形態によれば、基本的
に前述した第１実施形態と同様に構成されているため、
高温下における軸線傾斜を抑制できるとともに、低温下
における潤滑不足を解消できる。そして、この第２実施
形態によれば、内輪軌道面22Ａの断面形状が、前述した
第１実施形態に比較して、さらに閉じた断面略Ｕ字状と
なっているため、内輪22に対する外輪21の許容傾斜角度
を小さくできる。According to the second embodiment, since the configuration is basically the same as that of the first embodiment,
It is possible to suppress the inclination of the axis at a high temperature and to eliminate the insufficient lubrication at a low temperature. According to the second embodiment, since the cross-sectional shape of the inner ring raceway surface 22A is a substantially closed U-shaped cross section as compared with the above-described first embodiment, the outer race 21 with respect to the inner race 22 is formed. Can be reduced.
【００２３】なお、本発明において第３円弧は必須では
なく、図３に示す転がり軸受30も本発明に含まれるもの
である。すなわち、図３に示す転がり軸受30は、内輪軌
道面32Ａの断面形状が中心部の第１円弧34と、第１円弧
34を挟む一対の第２円弧35，35とにより構成されてい
る。このような転がり軸受30においても、内輪軌道面の
断面形状が一定の曲率半径を有する円弧である場合（図
３中一点鎖線参照）に比較して、内輪軌道面32Ａの断面
端部が転動体33に接近するように断面開口が若干閉じた
断面略Ｕ字状とされているため、高温下における軸線傾
斜を抑制できるとともに、低温下における潤滑不足を解
消できる。In the present invention, the third arc is not essential, and the rolling bearing 30 shown in FIG. 3 is also included in the present invention. In other words, the rolling bearing 30 shown in FIG. 3 has a first circular arc 34 having a cross-sectional shape of the inner raceway surface 32A at the center and a first circular arc 34.
It comprises a pair of second arcs 35, 35 sandwiching the. Also in such a rolling bearing 30, the cross-sectional end of the inner ring raceway surface 32A has a rolling element as compared with the case where the cross-sectional shape of the inner raceway surface is an arc having a constant radius of curvature (see the dashed line in FIG. 3). Since the cross-section opening has a substantially U-shaped cross-section that is slightly closed so as to approach 33, the inclination of the axis at high temperatures can be suppressed, and insufficient lubrication at low temperatures can be eliminated.
【００２４】その他、本発明は、前述した各実施形態に
限定されるものではなく、例えば各実施形態において例
示した外輪軌道面，内輪軌道面，転動体等の材質，形
状，形態，数，配置等は、本発明を達成できるものであ
れば任意であり、限定されない。また、本発明の転がり
軸受は、例えば自動車等の冷却装置のフアンカップリン
グ装置用に限定されず、その他の流体継ぎ手等で使用す
る転がり軸受にも適用可能である。In addition, the present invention is not limited to the above-described embodiments. For example, the material, shape, form, number, and arrangement of the outer raceway surface, the inner raceway surface, the rolling elements, and the like exemplified in each embodiment. Etc. are arbitrary and not limited as long as the present invention can be achieved. Further, the rolling bearing of the present invention is not limited to a fan coupling device for a cooling device of an automobile or the like, but can be applied to a rolling bearing used in other fluid joints or the like.
【００２５】[0025]
【発明の効果】以上、説明したように、本発明によれ
ば、軌道面を構成する第１円弧の曲率半径が転動体にお
ける転動面の曲率半径よりも大きく設定されているた
め、低温下においても転動体および軌道面間にグリース
を確実に引き込み可能となり、これにより潤滑不良が生
じず、軌道面を構成する第２円弧の曲率半径が第１円弧
の曲率半径よりも小さく設定されているため、軌道面の
断面開口が若干閉じ気味の略Ｕ字状となり、内輪に対す
る外輪の傾斜角度を一定以下に規制できる。As described above, according to the present invention, the radius of curvature of the first arc constituting the raceway surface is set to be larger than the radius of curvature of the rolling surface of the rolling element, so In this case, the grease can be reliably drawn into between the rolling elements and the raceway surface, whereby poor lubrication does not occur, and the radius of curvature of the second arc constituting the raceway surface is set to be smaller than the radius of curvature of the first arc. For this reason, the cross-sectional opening of the raceway surface is slightly U-shaped, and the inclination angle of the outer ring with respect to the inner ring can be restricted to a certain value or less.
【図１】本発明に係る第１実施形態を示す要部断面図お
よび模式図である。FIG. 1 is a sectional view and a schematic view of a main part showing a first embodiment according to the present invention.
【図２】本発明に係る第２実施形態を示す要部断面図お
よび模式図である。FIG. 2 is a cross-sectional view and a schematic view of a main part showing a second embodiment according to the present invention.
【図３】本発明の変形例を示す要部断面図である。FIG. 3 is a sectional view of a main part showing a modification of the present invention.
【図４】フアンカップリング装置の断面図である。FIG. 4 is a cross-sectional view of the fan coupling device.
【図５】従来の転がり軸受の断面図である。FIG. 5 is a sectional view of a conventional rolling bearing.
10，20，30 転がり軸受 11, 21，31 外輪 12，22，32 内輪 13，23，33 転動体 14，24，34 第１円弧 15，25，35 第２円弧 10, 20, 30 Rolling bearings 11, 21, 31 Outer ring 12, 22, 32 Inner ring 13, 23, 33 Rolling element 14, 24, 34 First arc 15, 25, 35 Second arc
Claims (1)
が配置された転がり軸受であって、 前記外輪軌道面および内輪軌道面のうちの一方の断面形
状が第１円弧と、前記第１円弧を挟むとともに凹凸が生
じないように連続する一対の第２円弧とを有し、 前記第１円弧の曲率半径が前記転動体における転動面の
曲率半径よりも大きく設定されているとともに、前記第
２円弧の曲率半径が前記第１円弧の曲率半径よりも小さ
く設定されていることを特徴とする転がり軸受。1. A rolling bearing in which rolling elements are arranged between an outer raceway surface and an inner raceway surface, wherein one of the outer raceway surface and the inner raceway surface has a first circular arc and a cross section of the first raceway. A pair of second circular arcs sandwiching the circular arc and having no irregularities, wherein a radius of curvature of the first circular arc is set to be larger than a radius of curvature of a rolling surface of the rolling element; A rolling bearing, wherein the radius of curvature of the second arc is set smaller than the radius of curvature of the first arc.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11099145A JP2000291665A (en) | 1999-04-06 | 1999-04-06 | Rolling bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11099145A JP2000291665A (en) | 1999-04-06 | 1999-04-06 | Rolling bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000291665A true JP2000291665A (en) | 2000-10-20 |
Family
ID=14239542
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11099145A Pending JP2000291665A (en) | 1999-04-06 | 1999-04-06 | Rolling bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000291665A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004051101A1 (en) * | 2002-12-05 | 2004-06-17 | Koyo Seiko Co., Ltd. | Worm support device and power assist unit having the same |
| JP2012202524A (en) * | 2011-03-28 | 2012-10-22 | Nsk Ltd | Rolling bearing |
| JP2014059030A (en) * | 2012-09-19 | 2014-04-03 | Jtekt Corp | Rolling bearing |
| WO2015175603A1 (en) * | 2014-05-15 | 2015-11-19 | The Timken Company | Bearing and method of forming a bearing |
| CN106640947A (en) * | 2016-12-27 | 2017-05-10 | 洛阳轴研科技股份有限公司 | Angular contact ball bearing and design method thereof |
| EP3165781A4 (en) * | 2014-07-03 | 2017-08-02 | NSK Ltd. | Linear motion guide device |
| CN108397477A (en) * | 2018-04-24 | 2018-08-14 | 瓦房店爱国轴承研究院有限公司 | Three cambered surface raceway deep groove ball bearings |
-
1999
- 1999-04-06 JP JP11099145A patent/JP2000291665A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004051101A1 (en) * | 2002-12-05 | 2004-06-17 | Koyo Seiko Co., Ltd. | Worm support device and power assist unit having the same |
| US7568550B2 (en) | 2002-12-05 | 2009-08-04 | Jtekt Corporation | Worm support device and power assist unit having the same |
| JP2012202524A (en) * | 2011-03-28 | 2012-10-22 | Nsk Ltd | Rolling bearing |
| JP2014059030A (en) * | 2012-09-19 | 2014-04-03 | Jtekt Corp | Rolling bearing |
| WO2015175603A1 (en) * | 2014-05-15 | 2015-11-19 | The Timken Company | Bearing and method of forming a bearing |
| JP2017519958A (en) * | 2014-05-15 | 2017-07-20 | ザ・ティムケン・カンパニーＴｈｅ Ｔｉｍｋｅｎ Ｃｏｍｐａｎｙ | Bearing and method of forming a bearing |
| US10060479B2 (en) | 2014-05-15 | 2018-08-28 | The Timken Company | Bearing and method of forming a bearing |
| EP3165781A4 (en) * | 2014-07-03 | 2017-08-02 | NSK Ltd. | Linear motion guide device |
| CN106640947A (en) * | 2016-12-27 | 2017-05-10 | 洛阳轴研科技股份有限公司 | Angular contact ball bearing and design method thereof |
| CN108397477A (en) * | 2018-04-24 | 2018-08-14 | 瓦房店爱国轴承研究院有限公司 | Three cambered surface raceway deep groove ball bearings |
| CN108397477B (en) * | 2018-04-24 | 2023-11-14 | 瓦房店爱国轴承研究院有限公司 | Three cambered surface raceway deep groove ball bearing |
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