JPH0483916A - Roller bearing - Google Patents
Roller bearingInfo
- Publication number
- JPH0483916A JPH0483916A JP2195523A JP19552390A JPH0483916A JP H0483916 A JPH0483916 A JP H0483916A JP 2195523 A JP2195523 A JP 2195523A JP 19552390 A JP19552390 A JP 19552390A JP H0483916 A JPH0483916 A JP H0483916A
- Authority
- JP
- Japan
- Prior art keywords
- circumferential surface
- distance
- contact area
- roller
- lubricating oil
- 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
- 230000007423 decrease Effects 0.000 claims abstract description 11
- 238000013459 approach Methods 0.000 claims description 11
- 239000010687 lubricating oil Substances 0.000 abstract description 36
- 238000005461 lubrication Methods 0.000 abstract description 6
- 239000007921 spray Substances 0.000 abstract description 2
- 239000012141 concentrate Substances 0.000 abstract 1
- 230000002093 peripheral effect Effects 0.000 description 8
- 238000005096 rolling process Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 230000000717 retained effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000014759 maintenance of location Effects 0.000 description 2
- 241000894006 Bacteria Species 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
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
- F16C19/364—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone
-
- 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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/088—Ball or roller bearings self-adjusting by means of crowning
-
- 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
- F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
-
- 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
- F16C2240/50—Crowning, e.g. crowning height or crowning radius
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
本発明は、ころ軸受、例えば、車両の回転部分に用いる
ころ軸受に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a roller bearing, for example, a roller bearing used in a rotating part of a vehicle.
(従来の技術)
従来のころ軸受としては、例えば、第5.6図に示すよ
うなものがある。第5図において、1はころ軸受である
円錐ころ軸受であり、円錐ころ軸受1は軸線2を共有す
る内輪3および外輪4を有し、内輪3と外輪4との間に
は外輪3および内輪4に接触しながら回転する円錐形状
の複数のコロ5を有している。円錐ころ軸受1は車両の
回転部分に軸受として使用する場合、例えば、内輪3お
よび外輪4はコロ5と接触しながら回転し、コロ5は内
輪3および外輪4のそれぞれの転勤面3aおよび4aに
接触しながら自転するとともに内輪3の周囲を公転する
。また、内輪3および外輪4の転動面3a、4aおよび
コロ5との接触部5aに発生する摩擦熱を除去するとと
もに、接触部5aの摩耗を抑制するために、これらの転
勤面3a、4aおよび接触部5aに潤滑油7を飛沫状お
よび噴霧状で吹き付けたり、または直接に接触するよう
に、循環させたりしている。(Prior Art) An example of a conventional roller bearing is the one shown in FIG. 5.6. In FIG. 5, 1 is a tapered roller bearing, which is a roller bearing, and the tapered roller bearing 1 has an inner ring 3 and an outer ring 4 that share an axis 2. Between the inner ring 3 and the outer ring 4, an outer ring 3 and an inner ring It has a plurality of conical rollers 5 that rotate while contacting the rollers 4. When the tapered roller bearing 1 is used as a bearing in a rotating part of a vehicle, for example, the inner ring 3 and the outer ring 4 rotate while contacting the rollers 5, and the rollers 5 contact the rolling surfaces 3a and 4a of the inner ring 3 and the outer ring 4, respectively. It rotates while contacting the inner ring 3 and revolves around the inner ring 3. In addition, in order to remove frictional heat generated at the rolling surfaces 3a, 4a of the inner ring 3 and outer ring 4 and the contact portion 5a with the rollers 5, and to suppress wear of the contact portion 5a, these rolling surfaces 3a, 4a are The lubricating oil 7 is sprayed onto the contact portion 5a in the form of droplets or sprays, or is circulated so that the contact portion 5a comes into direct contact with the lubricating oil 7.
(発明が解決しようとする課題)
しかしながら、このような従来のころ軸受にあっては、
第6図に示すように、外輪4の転動面4aがテーパで、
コロ5の外周面5bが直線となっており、かつ、軸線2
に対して傾斜して回転している。このため、コロ5と外
輪4との接触部5aの回転半径Raより大きい回転半径
Rbを有する部分5cに付着した潤滑油7は、コロ5の
回転に伴って遠心力により円錐ころ軸受lの放射外方に
飛び出して飛散し、潤滑油7が接触部5aに集まりにく
り、接触部5aの近傍の潤滑が十分でないという問題点
がある。また、潤滑油7の円錐ころ軸受1内への保持性
も悪いという問題点もある。(Problem to be solved by the invention) However, in such conventional roller bearings,
As shown in FIG. 6, the rolling surface 4a of the outer ring 4 is tapered,
The outer peripheral surface 5b of the roller 5 is a straight line, and the axis 2
It rotates at an angle to the Therefore, as the rollers 5 rotate, the lubricating oil 7 adhering to the portion 5c having a radius of rotation Rb larger than the radius of rotation Ra of the contact portion 5a of the outer ring 4 radiates from the tapered roller bearing l due to centrifugal force as the rollers 5 rotate. There is a problem in that the lubricating oil 7 flies outward and scatters, and the lubricating oil 7 tends to collect at the contact portion 5a, resulting in insufficient lubrication in the vicinity of the contact portion 5a. Another problem is that the lubricating oil 7 is poorly retained in the tapered roller bearing 1.
そこで、本発明は、このような、従来の問題点に着目し
てなされたものであり、請求項1では、ころの外周面は
、軸方向中央付近の外輪との外接部から両端部に近づく
に従って、外周長を漸減するよう湾曲させ、かつ、両端
部と内輪の軸線との距離を外接部と軸線との距離よりも
小さくすることにより、潤滑油が外接部に集まるように
し、接触部の潤滑を向上できるころ軸受とし、また、請
求項2では、ころの外周面を前記のように湾曲させると
ともに、外輪の内周面を軸方向中央付近の内接部から両
端部に近づくに従って内周長を漸減するよう湾曲させ、
かつ、内周面の両端部と内輪の軸線との距離を外輪の内
接部と軸線との距離よりも小さくすることにより、接触
部の潤滑を向上できるとともに、さらに、潤滑油の保持
性を向上させたころ軸受を提供することを課題とする。Therefore, the present invention has been made by focusing on such conventional problems, and in claim 1, the outer peripheral surface of the roller approaches both ends from the circumferential part with the outer ring near the center in the axial direction. Accordingly, by curving the outer circumference so as to gradually reduce the length, and by making the distance between both ends and the axis of the inner ring smaller than the distance between the circumscribed part and the axis, lubricating oil collects at the circumscribed part, and the contact part The roller bearing can improve lubrication, and in the second aspect, the outer circumferential surface of the roller is curved as described above, and the inner circumferential surface of the outer ring is curved from the inscribed part near the axial center to the inner circumference as it approaches both ends. Curved so that the length gradually decreases,
In addition, by making the distance between both ends of the inner circumferential surface and the axis of the inner ring smaller than the distance between the inscribed part of the outer ring and the axis, it is possible to improve the lubrication of the contact area and further improve the retention of lubricating oil. The objective is to provide an improved roller bearing.
(課題を解決するための手段)
本発明の請求項1に係るころ軸受では、軸線を共有する
内輪および外輪の間に該外輪および内輪に接触しながら
回転可能に保持された複数のころを有するころ軸受にお
いて、前記ころの外周面はころの軸方向中央付近で前記
外輪に接触する外接部を有し、該外接部から前記ころの
軸方向両端部に近づくに従って外周長を漸減するよう湾
曲し、かつ、該両端部と前記内輪の軸線との距離を前記
外接部と該軸線との距離よりも小さくすることを特徴と
している。(Means for Solving the Problems) A roller bearing according to claim 1 of the present invention includes a plurality of rollers rotatably held between an inner ring and an outer ring that share an axis while contacting the outer ring and the inner ring. In the roller bearing, the outer peripheral surface of the roller has a circumscribed part that contacts the outer ring near the axial center of the roller, and is curved so that the outer circumferential length gradually decreases as it approaches both axial ends of the roller from the circumscribed part. , and the distance between the both end portions and the axis of the inner ring is smaller than the distance between the circumscribed portion and the axis.
また、請求項2に係るころ軸受では、請求項1記載に加
え、前記外輪の内周面は前記ころが接触する外輪の軸方
向中央付近の内接部から外輪の軸方向両端部に近づくに
従って内周長を漸減するよう湾曲し、かつ、前記両端部
と前記内輪の軸線との距離を、前記内接部と該軸線との
距離よりも小さくすることを特徴としている。In the roller bearing according to a second aspect of the present invention, in addition to the first aspect, the inner circumferential surface of the outer ring increases as the inner peripheral surface of the outer ring approaches both ends of the outer ring in the axial direction from an inscribed portion near the axial center of the outer ring with which the rollers come into contact. It is characterized in that it is curved so that the inner peripheral length gradually decreases, and the distance between the both ends and the axis of the inner ring is smaller than the distance between the inscribed part and the axis.
(作用)
本発明では、ころの外周面が外輪に接触する軸方向中央
付近の外接部から両端部に近づくに従って、外周長を漸
減するように湾曲させ、かつ、両端部と内輪の軸線との
距離を外接部と軸線との距離よりも小さくしているので
、ころ軸受が潤滑油の飛沫を受けながら回転し、ころが
外輪および内輪に接触し自転しながら公転すると、ころ
の外周面上の両端部に付着した潤滑油には、外周面に垂
直方向の耐着力F、と、ころの自転および公転による遠
心力により放射外方への遠心力F2が作用し、この合力
F、が外周面のほぼ接線方向に作用する。このため、外
周面の両端部に付着した潤滑油;よ外周面に付着しなが
ら、外周面の湾曲に沿って外接部側に移動し、外輪と接
触した外接部の近傍および外接部を潤滑し、さらには、
内輪と接触する外接部の近傍を潤滑する。(Function) In the present invention, the outer circumferential surface of the roller is curved so that the outer circumferential length gradually decreases as it approaches both ends from the circumscribed part near the axial center where it contacts the outer ring, and Since the distance is made smaller than the distance between the circumscribed part and the axis, when the roller bearing rotates while receiving splashes of lubricating oil, and the rollers contact the outer ring and inner ring and revolve while rotating, the outer peripheral surface of the roller The lubricating oil attached to both ends is subjected to an anti-adhesion force F in the direction perpendicular to the outer circumferential surface and a radially outward centrifugal force F2 due to the centrifugal force caused by the rotation and revolution of the rollers, and this resultant force F acts on the outer circumferential surface. It acts almost tangentially to . Therefore, the lubricating oil that adheres to both ends of the outer circumferential surface moves along the curvature of the outer circumferential surface toward the circumscribed part, and lubricates the vicinity of the circumscribed part that has contacted the outer ring and the circumscribed part. ,Furthermore,
Lubricate the vicinity of the outer part that contacts the inner ring.
また、請求項2においては、請求項1に記載したように
、ころの外周面が湾曲にするとともに、外輪の内周面が
軸方向中央付近の内接部から両端部に近づくに従って、
内周長を漸減するように湾曲させ、かつ、両端部と内輪
の軸線との距離を内接部と軸線との距離よりも小さくし
ているので、ころ軸受が潤滑油の飛沫を受けながら回転
し、ころが外輪および内輪に接触し自転しながら公転す
ると、潤滑油は放射外方への遠心力により外輪の内周面
およびころの外周面に飛沫し付着する。外輪の内周面の
両端部に付着した潤滑油は、両端部より放射外方側にあ
る内接部側に内周面の湾曲に沿って移動し、ころの外周
面の両端部に付着した潤滑油は、前述と同様、外接部側
に移動する。このため、潤滑油は外接部および内接部の
近傍を潤滑にするとともにころ軸受内に保持される。Further, in claim 2, as described in claim 1, the outer circumferential surface of the roller is curved, and as the inner circumferential surface of the outer ring approaches both ends from the inscribed portion near the center in the axial direction,
The inner circumference is curved so that it gradually decreases, and the distance between both ends and the axis of the inner ring is smaller than the distance between the inscribed part and the axis, so the roller bearing rotates while receiving splashes of lubricating oil. However, when the rollers contact the outer ring and the inner ring and revolve while rotating, the lubricating oil is splashed and adhered to the inner circumferential surface of the outer ring and the outer circumferential surface of the rollers due to radially outward centrifugal force. The lubricating oil adhering to both ends of the inner circumferential surface of the outer ring moves along the curvature of the inner circumferential surface toward the inscribed part that is radially outward from both ends, and the lubricating oil adheres to both ends of the outer circumferential surface of the roller. The lubricating oil moves to the circumscribed portion side as described above. Therefore, the lubricating oil lubricates the vicinity of the external and internal parts and is retained within the roller bearing.
(実施例) 以下、本発明の実施例を図面に基づき説明する。(Example) Embodiments of the present invention will be described below based on the drawings.
第1.2図は本発明の請求項1記載の一実施例を示す図
である。FIG. 1.2 is a diagram showing an embodiment according to claim 1 of the present invention.
まず、構成について説明する。First, the configuration will be explained.
第1図において、11はころ軸受であり、ころ軸受11
は軸線12を共有する内輪13および外輪14を有し、
内輪13と外輪14との間には複数のテーパコロ16(
以下、単にコロという)が円周上にほぼ等間隔に配置さ
れている。コロ16は内輪13および外輪14に接触し
ながら軸線12に対して傾斜した傾斜軸線17の回りに
回転可能に保持されている。In FIG. 1, 11 is a roller bearing, and the roller bearing 11
has an inner ring 13 and an outer ring 14 that share an axis 12,
A plurality of tapered rollers 16 (
The rollers (hereinafter simply referred to as rollers) are arranged at approximately equal intervals on the circumference. The rollers 16 are rotatably held around an inclined axis 17 inclined with respect to the axis 12 while contacting the inner ring 13 and the outer ring 14 .
内輪13は第1図に示す断面において、軸線L2rこほ
ぼ平行な内周面13aと、内周面13aの放射外方にコ
ロ16の傾斜軸線17に対応して軸線12に対しで傾斜
したほぼ直線状の外転動面13bとを有している。内周
面13aは通常回転軸18に嵌合し、図示していない回
転軸18の段付部等により固定され、回転軸18と一体
的に回転可能である。In the cross section shown in FIG. 1, the inner ring 13 has an inner circumferential surface 13a substantially parallel to the axis L2r, and an inner circumferential surface 13a radially outward of the inner circumferential surface 13a that is substantially inclined with respect to the axis 12 corresponding to the inclined axis 17 of the rollers 16. It has a linear outer rolling surface 13b. The inner circumferential surface 13a normally fits into the rotating shaft 18, is fixed by a stepped portion of the rotating shaft 18 (not shown), etc., and is rotatable integrally with the rotating shaft 18.
外輪14は軸線12にほぼ平行な外周面14aと、コロ
16の傾斜軸線17に対応して傾斜した断面でほぼ直線
状の内側の内転動面14bとを有している。外周面14
aは通常ハウジング19等に固定されている。The outer ring 14 has an outer circumferential surface 14a that is substantially parallel to the axis 12, and an inner inner rolling surface 14b that is substantially straight in cross section and is inclined corresponding to the inclined axis 17 of the rollers 16. Outer surface 14
a is usually fixed to the housing 19 or the like.
コロ16の外周面21は、コロ16の軸である傾斜軸線
17の軸方向中央付近で外輪14の内転動面14bに線
接触、または若干面接触する外接部21aを有している
。外周面21は外接部21aから軸方向両端部21bに
近づくに従って、外周面21の傾斜軸線17に直交する
断面上外周長L2+が漸減するように、いわゆるクラウ
ン状または太鼓形状に湾曲し、かつ、両端部21bと内
輪13の軸線12との端部路MDbを外接部21aと軸
線12との外接距離Daよりも小さくするようになされ
ている。図の右側の端部21bと軸線12との端部距離
Dcは図の左側の端部21bと軸線12との端部距離D
bよりも傾斜軸線17の傾斜に対応して小さ(なってい
る。The outer circumferential surface 21 of the roller 16 has a circumscribed portion 21a that makes line contact or slight surface contact with the inner rolling surface 14b of the outer ring 14 near the axial center of the inclined axis 17, which is the axis of the roller 16. The outer circumferential surface 21 is curved in a so-called crown shape or drum shape so that the outer circumferential length L2+ of the outer circumferential surface 21 on a cross section perpendicular to the inclined axis 17 gradually decreases as it approaches both axial ends 21b from the circumscribed portion 21a, and The end path MDb between both ends 21b and the axis 12 of the inner ring 13 is made smaller than the circumscribed distance Da between the circumscribed portion 21a and the axis 12. The end distance Dc between the right end 21b in the figure and the axis 12 is the end distance Dc between the left end 21b in the figure and the axis 12.
b is smaller than that corresponding to the inclination of the inclination axis 17.
次に、作用につき説明する。Next, the effect will be explained.
本発明に係るころ軸受は、コロ16の外周面21が外接
部21aから両端部21bにクラウン状に湾曲し、かつ
、端部距離Dbを外接距離Daよりも小さ(するように
しているので、外周面21が潤滑油23の飛沫23a(
以下、単に潤滑油23ともいう)をあびながら回転する
と、潤滑油23がコロ16の外周面21に付着する。コ
ロ16は、内輪13および外輪14に接触し、自転しな
がら内輪13の回りを公転しており、コロ16の外周面
21の両端部21bに付着した潤滑油23には第2図に
示すように、外周面21に垂直方向の耐着力F1と、放
射外方へ向う遠心力F2とが作用し、その合力F3が外
周面21のほぼ接線方向に作用している。このため、潤
滑油23には外周面21の両端部21bより放射外方側
にある中央付近の外接部21a側に向う(図には矢印P
にて示す)移動力F3が働き、飛沫23aはコロ16の
外接部21a側に、すなわち、クラウン状外周面21の
頂点側に向って移動する。外周面21が頂点は外周面2
1の外輪14と接触する外接部21aでもあるので、潤
滑油23は外接部21aに集まり、外接部21aおよび
外接部21aの近傍の潤滑性を向上する。第2菌におい
ては、第1図の左側の端部21 b について示したが
、右側の端部21bにおいても同様に飛沫23aが両端
部21bから外接部21a側に移動するのは勿論である
。In the roller bearing according to the present invention, the outer peripheral surface 21 of the roller 16 is curved in a crown shape from the circumscribed portion 21a to both ends 21b, and the end distance Db is smaller than the circumscribed distance Da. The outer peripheral surface 21 is covered with droplets 23a of the lubricating oil 23 (
When the roller 16 is rotated while being coated with lubricating oil 23 (hereinafter also simply referred to as lubricating oil 23), the lubricating oil 23 adheres to the outer circumferential surface 21 of the roller 16. The rollers 16 are in contact with the inner ring 13 and the outer ring 14, and revolve around the inner ring 13 while rotating on their own axis. A vertical adhesion force F1 and a radially outward centrifugal force F2 act on the outer circumferential surface 21, and a resultant force F3 acts on the outer circumferential surface 21 in a substantially tangential direction. For this reason, the lubricating oil 23 flows toward the circumscribed part 21a near the center, which is radially outward from both ends 21b of the outer circumferential surface 21 (in the figure, arrow P
The moving force F3 (shown in ) acts, and the droplets 23a move toward the circumscribed portion 21a of the roller 16, that is, toward the apex of the crown-shaped outer circumferential surface 21. The apex of the outer circumferential surface 21 is the outer circumferential surface 2
Since the lubricating oil 23 is also the circumscribed portion 21a that contacts the outer ring 14 of No. 1, the lubricating oil 23 gathers at the circumscribed portion 21a, improving the lubricity of the circumscribed portion 21a and the vicinity of the circumscribed portion 21a. Regarding the second bacterium, the left end 21 b in FIG. 1 is shown, but it goes without saying that the droplets 23 a similarly move from both ends 21 b to the circumscribed part 21 a side at the right end 21 b.
次に、本発明の請求項2の実施例について説明する。Next, an embodiment of claim 2 of the present invention will be described.
第3.4図は請求項2に係るころ軸受の実施例を示す図
であり、第1.2図と同し構成には同し符号をつける。Fig. 3.4 is a diagram showing an embodiment of the roller bearing according to claim 2, and the same components as in Fig. 1.2 are given the same reference numerals.
請求項2に係るころ軸受31では、外輪34の内周面3
6はコロ16が接触する外輪34の軸方向中央付近の内
接部36aから外輪34の軸方向両端部36bに近づく
に従って、外輪34の軸vA12に直交する断面上の内
周長L36が漸減するように、いわゆる逆クラウン状に
湾曲し、かつ、両端部36bと内輪13の軸線12との
端部距離Ebを内接部36aと軸線12との内接距離E
aよりも小さくするようになされている。内接距離Ea
は請求項1における外接距離と等しい。In the roller bearing 31 according to the second aspect, the inner circumferential surface 3 of the outer ring 34
6, the inner circumferential length L36 on the cross section perpendicular to the axis vA12 of the outer ring 34 gradually decreases as it approaches both axial ends 36b of the outer ring 34 from the inscribed part 36a near the axial center of the outer ring 34 where the rollers 16 contact. As shown in FIG.
It is designed to be smaller than a. Inscribed distance Ea
is equal to the circumscribed distance in claim 1.
前述以外は第1.2図に示す請求項1の実施例と同じで
あり、同じ符号をつける。Everything other than the above is the same as the embodiment of claim 1 shown in FIG. 1.2, and is given the same reference numeral.
本発明の請求項2においては、ころ16の外周面21が
第1図に示すように、外接部21aから両端部21bに
クラウン状に湾曲し、かつ、端部距離Dbが外接部MD
aよりも小さ(するようにするとともに、外輪34の内
周面36が、内接部36aから両端部36bに逆クラウ
ン状に湾曲し、かつ、端部距離Ebを内接距離Eaより
も小さくするようになされているので、内周面36が潤
滑油23の飛沫23aをあびながら回転すると、潤滑油
23が外輪34の内周面36に付着する。コロ16は外
輪34および内輪13に接触し、自転しながら、内輪1
3の回りを公転しており、内周面36には内輪13の回
転およびコロ16の自転および公転により飛散された潤
滑油23が遠心力により内周面36に衝突し、さらに、
内周面36の両端部36bの潤滑油23は両端部36b
より放射外方側にある内接部36a側に、湾曲した内周
面36に沿って移動し、内接部36aの近傍に集まる。In claim 2 of the present invention, as shown in FIG. 1, the outer circumferential surface 21 of the roller 16 is curved in a crown shape from the circumscribed part 21a to both ends 21b, and the end distance Db is the circumscribed part MD.
In addition, the inner circumferential surface 36 of the outer ring 34 is curved in an inverted crown shape from the inscribed portion 36a to both ends 36b, and the end distance Eb is smaller than the inscribed distance Ea. Therefore, when the inner circumferential surface 36 rotates while being sprayed with droplets 23a of the lubricating oil 23, the lubricating oil 23 adheres to the inner circumferential surface 36 of the outer ring 34. The rollers 16 contact the outer ring 34 and the inner ring 13. Then, while rotating, the inner ring 1
3, and the lubricating oil 23 scattered on the inner circumferential surface 36 by the rotation of the inner ring 13 and the rotation and revolution of the rollers 16 collides with the inner circumferential surface 36 due to centrifugal force.
The lubricating oil 23 on both ends 36b of the inner circumferential surface 36 is
The particles move along the curved inner circumferential surface 36 toward the inscribed portion 36a, which is more radially outward, and gather near the inscribed portion 36a.
したがって、内接部36aの近傍の潤滑性を向上すると
ともに潤滑油23を内周面36内に保持する。すなわち
、本発明のころ軸受31ではコロ16の外周面21をク
ラウン形状にするとともに外輪34の内周面36を逆ク
ラウン形状にすることにより、コロ16と外輪34との
接触部(すなわち、コロ16と外輪34との間を線接触
または面接触する内接部36aおよび外接部21a)の
潤滑性が向上し、ころ軸受の耐焼付性が大幅に向上でき
る。さらにまた、外輪34の内周面36を逆クラウン形
状にすることにより、外輪34とコロ16との接触面積
が増加し、面圧を低減でき、ころ軸受31の耐久性を向
上できる。Therefore, the lubricity near the internal part 36a is improved and the lubricating oil 23 is retained within the inner circumferential surface 36. That is, in the roller bearing 31 of the present invention, the outer circumferential surface 21 of the rollers 16 is formed into a crown shape, and the inner circumferential surface 36 of the outer ring 34 is formed into an inverted crown shape. The lubricity of the inner contact portion 36a and the outer contact portion 21a) which are in line contact or surface contact between the roller bearing 16 and the outer ring 34 is improved, and the seizure resistance of the roller bearing can be greatly improved. Furthermore, by forming the inner circumferential surface 36 of the outer ring 34 into an inverted crown shape, the contact area between the outer ring 34 and the rollers 16 increases, surface pressure can be reduced, and the durability of the roller bearing 31 can be improved.
(効果)
以上説明したように、本発明の請求項1によれば、ころ
の外周面は、軸方向中央付近の外輪との外接部から両端
部に近づくに従って、外周長を漸減するよう湾曲させ、
かつ、両端部と内輪の軸線との距離を外接部と軸線との
距離よりも小さ(することにより、潤滑油が外接部に集
まるようにし、接触部の潤滑を向上できるころ軸受とし
、また、請求項2では、ころの外周面を前記のように湾
曲させるとともに、外輪の内周面を逆クラウン状に湾曲
させ、かつ、内周面の両端部と内輪の軸線との距離を外
輪の内接部と軸線との距離よりも小さくすることにより
、接触部の潤滑を向上できるとともに、さらに、潤滑油
の保持性を向上でき、ころ軸受の耐焼付性が大幅に向上
できる。(Effects) As explained above, according to claim 1 of the present invention, the outer circumferential surface of the roller is curved so that the outer circumferential length gradually decreases as it approaches both ends from the circumscribed part with the outer ring near the axial center. ,
In addition, the distance between both ends and the axis of the inner ring is smaller than the distance between the circumscribed part and the axis (thereby, lubricating oil collects in the circumscribed part, and the roller bearing can improve lubrication of the contact part, and In claim 2, the outer circumferential surface of the roller is curved as described above, the inner circumferential surface of the outer ring is curved in an inverted crown shape, and the distance between both ends of the inner circumferential surface and the axis of the inner ring is set to By making the distance smaller than the distance between the contact part and the axis, it is possible to improve the lubrication of the contact part, and furthermore, it is possible to improve the retention of lubricating oil, and the seizure resistance of the roller bearing can be greatly improved.
さらにまた、外輪の内周面を逆クラウン状にすることに
より、ころの外周面をクラウン状にし、かつ、外輪とコ
ロとの面圧を低減でき、ころ軸受の耐久性を大幅に向上
できる。Furthermore, by forming the inner circumferential surface of the outer ring into an inverted crown shape, the outer circumferential surface of the rollers can be made into a crown shape, and the contact pressure between the outer ring and the rollers can be reduced, and the durability of the roller bearing can be greatly improved.
第1〜2図は本発明の請求項1に係るころ軸受の一実施
例を示す図であり、第1図はその一部断面図、第2図は
その要部断面図である。第3.4図は本発明の請求項2
に係るころ軸受の一実施例を示す図であり、第3図はそ
の一部断面図、第4図はその要部断面図である。第5.
6図は従来のころ軸受を示す図であり、第5図はその一
部断面図、第6図はその拡大断面図である。
11.31・・・・・・ころ軸受、
12・・・・・・軸線、
13・・・・・・内輪、
14.34・・・・・・外輪、
16・・・・・・コロ、
21・・・・・・外周面、
21a・・・・・・外接部、
21b・・・・・・両端部、
36・−・・・・内周面、
36a・・・・・・内接部、
36b・−・・・・両端部、
L2□・・・・・・外周長、
Li2−・・・・・内周長、
Da・・・・・・外接距離、
Db、Eb・・・・・・端部距離、
Ea・・・・・・内接距離。
特 許 出 願 人 日産自動車株式会社第
図
第
図1 and 2 are diagrams showing one embodiment of a roller bearing according to claim 1 of the present invention, with FIG. 1 being a partial sectional view thereof, and FIG. 2 being a sectional view of an essential part thereof. Figure 3.4 shows claim 2 of the present invention.
FIG. 3 is a partial cross-sectional view of the roller bearing, and FIG. 4 is a cross-sectional view of the main part thereof. Fifth.
6 is a diagram showing a conventional roller bearing, FIG. 5 is a partial sectional view thereof, and FIG. 6 is an enlarged sectional view thereof. 11.31... Roller bearing, 12... Axis line, 13... Inner ring, 14.34... Outer ring, 16... Roller, 21...Outer circumferential surface, 21a...Externally connected portion, 21b...Both ends, 36...Inner circumferential surface, 36a...Inscribed Part, 36b...Both ends, L2□...Outer circumference length, Li2-...Inner circumference length, Da... Circumscribed distance, Db, Eb... ... End distance, Ea ... Inscribed distance. Patent applicant: Nissan Motor Co., Ltd.
Claims (2)
び内輪に接触しながら回転可能に保持された複数のころ
を有するころ軸受において、前記ころの外周面はころの
軸方向中央付近で前記外輪に接触する外接部を有し、該
外接部から前記ころの軸方向両端部に近づくに従って外
周長を漸減するよう湾曲し、かつ、該両端部と前記内輪
の軸線との距離を前記外接部と該軸線との距離よりも小
さくすることを特徴とするころ軸受。(1) In a roller bearing having a plurality of rollers rotatably held between an inner ring and an outer ring that share an axis while contacting the outer ring and the inner ring, the outer circumferential surface of the roller is located near the axial center of the roller. It has a circumscribed part that contacts the outer ring, and is curved so that the outer circumference gradually decreases as it approaches both axial ends of the roller from the circumscribed part, and the distance between the both ends and the axis of the inner ring is set by the circumscribed part. A roller bearing characterized in that the distance between the axis and the axis is smaller than the distance between the axis and the axis.
方向中央付近の内接部から外輪の軸方向両端部に近づく
に従って内周長を漸減するよう湾曲し、かつ、前記両端
部と前記内輪の軸線との距離を前記内接部と該軸線との
距離よりも小さくすることを特徴とする請求項1記載の
ころ軸受。(2) The inner circumferential surface of the outer ring is curved so that the inner circumferential length gradually decreases as it approaches both axial ends of the outer ring from the inscribed part near the axial center of the outer ring where the rollers contact, and The roller bearing according to claim 1, wherein a distance between the inner ring and the axis of the inner ring is smaller than a distance between the inscribed portion and the axis.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2195523A JPH0483916A (en) | 1990-07-24 | 1990-07-24 | Roller bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2195523A JPH0483916A (en) | 1990-07-24 | 1990-07-24 | Roller bearing |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0483916A true JPH0483916A (en) | 1992-03-17 |
Family
ID=16342510
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2195523A Pending JPH0483916A (en) | 1990-07-24 | 1990-07-24 | Roller bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0483916A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005058149A1 (en) * | 2005-12-06 | 2007-07-05 | Schaeffler Kg | Tapered roller bearings with curved raceways |
CN104565022A (en) * | 2014-12-31 | 2015-04-29 | 浙江大学 | Variable-contact angle tapered roller bearing |
-
1990
- 1990-07-24 JP JP2195523A patent/JPH0483916A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005058149A1 (en) * | 2005-12-06 | 2007-07-05 | Schaeffler Kg | Tapered roller bearings with curved raceways |
CN104565022A (en) * | 2014-12-31 | 2015-04-29 | 浙江大学 | Variable-contact angle tapered roller bearing |
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