JPH0712133A - Cylindrical roller bearing - Google Patents
Cylindrical roller bearingInfo
- Publication number
- JPH0712133A JPH0712133A JP17851793A JP17851793A JPH0712133A JP H0712133 A JPH0712133 A JP H0712133A JP 17851793 A JP17851793 A JP 17851793A JP 17851793 A JP17851793 A JP 17851793A JP H0712133 A JPH0712133 A JP H0712133A
- Authority
- JP
- Japan
- Prior art keywords
- cylindrical roller
- roller bearing
- ring raceway
- outer ring
- curvature
- 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
- 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
- F16C19/225—Details of the ribs supporting the end of 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
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明に係る円筒ころ軸受は、
ガスタービン、ジェットエンジン等、高速で回転する円
筒ころ軸受の改良に関する。BACKGROUND OF THE INVENTION The cylindrical roller bearing according to the present invention is
The present invention relates to improvement of cylindrical roller bearings that rotate at high speed, such as gas turbines and jet engines.
【０００２】[0002]
【従来の技術】ガスタービンの回転軸等、各種回転部分
を支持する為に、図１〜２に示す様な円筒ころ軸受が広
く使用されている。この円筒ころ軸受は何れも、外周面
に内輪軌道１を有する内輪２と、内周面に外輪軌道３を
有する外輪４と、上記内輪軌道１と外輪軌道３との間に
転動自在に設けられた複数個の円筒ころ５と、この複数
個の円筒ころ５を保持した状態で、上記内輪軌道１と外
輪軌道３との間に回転自在に設けられた保持器６とを備
えている。2. Description of the Related Art Cylindrical roller bearings as shown in FIGS. 1 and 2 are widely used to support various rotating parts such as a rotating shaft of a gas turbine. In each of the cylindrical roller bearings, an inner ring 2 having an inner ring raceway 1 on the outer peripheral surface, an outer ring 4 having an outer ring raceway 3 on the inner peripheral surface, and a rollable installation between the inner ring raceway 1 and the outer ring raceway 3 are provided. A plurality of cylindrical rollers 5 are provided, and a retainer 6 rotatably provided between the inner ring raceway 1 and the outer ring raceway 3 while holding the plurality of cylindrical rollers 5.
【０００３】内輪軌道１の両端部（図２の場合）又は外
輪軌道３の両端部（図１の場合）には１対の鍔７、７を
形成している。この鍔７、７同士の間隔は、上記円筒こ
ろ５の軸方向（図１〜２の左右方向）に亙る長さ寸法よ
りも僅かに大きい。従って上記各円筒ころ５は、これら
１対の鍔７、７により軸方向両側から挟まれ、軸方向へ
の変位を防止される。A pair of flanges 7, 7 are formed at both ends of the inner ring raceway 1 (in the case of FIG. 2) or both ends of the outer ring raceway 3 (in the case of FIG. 1). The interval between the collars 7, 7 is slightly larger than the length dimension of the cylindrical roller 5 in the axial direction (left-right direction in FIGS. 1 and 2). Therefore, the cylindrical rollers 5 are sandwiched by the pair of collars 7, 7 from both sides in the axial direction, and are prevented from being displaced in the axial direction.
【０００４】上記各円筒ころ５は図３〜４に詳示する様
に、転動面８と軸方向両端面９、９との間に面取り部１
０、１０を設けている。そして、各面取り部１０、１０
の内周端と、上記両端面９、９とを、それぞれ曲面１１
で連続させている。各曲面１１はバレル加工により形成
する。従来の円筒ころ軸受に於いてこれら各曲面１１
は、単にエッヂを取り除く程度の加工しか施されておら
ず、曲率半径Ｒは０．２mm以下の小さいものであった。As described in detail in FIGS. 3 and 4, each of the cylindrical rollers 5 has a chamfered portion 1 between the rolling surface 8 and both axial end surfaces 9, 9.
0 and 10 are provided. And each chamfer 10,10
The inner peripheral edge of the and the both end surfaces 9 and 9 are respectively curved surfaces 11
It is made continuous with. Each curved surface 11 is formed by barrel processing. Each of these curved surfaces 11 in the conventional cylindrical roller bearing
Was only processed to remove edges, and the radius of curvature R was as small as 0.2 mm or less.
【０００５】上述の様に構成される円筒ころ軸受の使用
時には、例えば上記内輪２を回転軸の中間部に外嵌固定
し、上記外輪４をハウジングに内嵌固定する。回転軸の
回転時には、上記複数個の円筒ころ５が転動する事で、
上記外輪４の内側で内輪２が回転する事を許容する。When the cylindrical roller bearing constructed as described above is used, for example, the inner ring 2 is externally fitted and fixed to the intermediate portion of the rotary shaft, and the outer ring 4 is internally fitted and fixed to the housing. When the rotary shaft rotates, the plurality of cylindrical rollers 5 roll,
The inner ring 2 is allowed to rotate inside the outer ring 4.
【０００６】[0006]
【発明が解決しようとする課題】ところが、上述の様に
構成され作用する従来の円筒ころ軸受に於いては、円筒
ころ５の形状に起因して、鍔７、７の内側面に摩耗が生
じる事がある。即ち、円筒ころ軸受の運転時にしばし
ば、各円筒ころ５の中心軸が内輪２及び外輪４の中心軸
と非平行になる、所謂スキューが発生する。この様なス
キューが発生すると、図５〜７に示す様に、上記各円筒
ころ５の両端部外周縁部が鍔７、７の内側面に、Ａ、Ｂ
の２点で当接し、各円筒ころ５の転動に伴って各当接部
Ａ、Ｂが擦れ合う。図７の鎖線ａは、擦れ合い部分の軌
跡を示している。However, in the conventional cylindrical roller bearing configured and operating as described above, the inner surfaces of the collars 7, 7 are worn due to the shape of the cylindrical roller 5. There is a thing. That is, when the cylindrical roller bearing is in operation, a so-called skew occurs in which the central axis of each cylindrical roller 5 is not parallel to the central axis of the inner ring 2 and the outer ring 4. When such a skew occurs, as shown in FIGS. 5 to 7, the outer peripheral edge portions of both ends of each of the cylindrical rollers 5 are A, B on the inner side surfaces of the collars 7, 7.
The two contact points A, B contact each other as the cylindrical rollers 5 roll. A chain line a in FIG. 7 indicates the locus of the rubbing portion.
【０００７】この様に各円筒ころ５の両端部外周縁部が
鍔７、７の内側面に当接する場合に於いて、上記各円筒
ころ５側の接触部位は、図７に示す様に、面取り部１
０、１０と端面９、９との間の曲面１１部分（図４参
照）になる。そして、従来使用されていた円筒ころ５の
場合、この曲面１１の曲率半径が小さい為、上記当接部
に作用するエッヂロードが大きくなる。この様にエッヂ
ロードが大きくなると、上記各円筒ころ５の転動に伴う
摩擦により上記鍔７、７の内側面が、上記鎖線ａで示し
た擦れ合い部分に沿って摩耗するだけでなく、潤滑不良
等の悪条件が重なると、円筒ころ軸受が焼き付く恐れが
ある。When the outer peripheral edge portions of both ends of each cylindrical roller 5 come into contact with the inner side surfaces of the collars 7, 7, the contact portion on the side of each cylindrical roller 5 is, as shown in FIG. Chamfer 1
It becomes a curved surface 11 portion (see FIG. 4) between 0 and 10 and the end surfaces 9 and 9. In the case of the conventionally used cylindrical roller 5, since the curved surface 11 has a small radius of curvature, the edge load acting on the contact portion becomes large. When the edge load increases in this way, the inner side surfaces of the collars 7, 7 are not only worn along the rubbing portions indicated by the chain line a, but also lubricated due to the friction associated with the rolling of the cylindrical rollers 5. If bad conditions such as defects overlap, the cylindrical roller bearing may be seized.
【０００８】この様な問題は、内輪２、外輪４、円筒こ
ろ５を軸受鋼により造った通常の円筒ころ軸受でも生じ
るが、円筒ころ５のみを窒化珪素セラミックにより造っ
たハイブリッド円筒ころ軸受、更には円筒ころだけでな
く内輪２及び外輪４も窒化珪素セラミックにより造った
セラミック円筒ころ軸受の場合に著しい。これは、窒化
珪素セラミックが軸受鋼に比べて塑性変形しにくく、し
かもヤング率が高い為、上記当接部に作用するエッヂロ
ードが著しく高くなる為である。Although such a problem occurs also in a normal cylindrical roller bearing in which the inner ring 2, the outer ring 4, and the cylindrical roller 5 are made of bearing steel, a hybrid cylindrical roller bearing in which only the cylindrical roller 5 is made of silicon nitride ceramic, Is remarkable in the case of a ceramic cylindrical roller bearing in which not only the cylindrical roller but also the inner ring 2 and the outer ring 4 are made of silicon nitride ceramic. This is because the silicon nitride ceramic is less likely to be plastically deformed than the bearing steel and has a high Young's modulus, so that the edge load acting on the contact portion is significantly increased.
【０００９】本発明の円筒ころ軸受は、この様な鍔７、
７の摩耗や円筒ころ軸受の焼き付きを防止すべく発明し
たものである。The cylindrical roller bearing of the present invention has the above-mentioned collar 7,
This invention was invented in order to prevent abrasion of No. 7 and seizure of the cylindrical roller bearing.
【００１０】[0010]
【課題を解決するための手段】本発明の円筒ころ軸受
は、上述した従来の円筒ころ軸受と同様に、外周面に内
輪軌道を有する内輪と、内周面に外輪軌道を有する外輪
と、上記内輪軌道と外輪軌道との間に転動自在に設けら
れた複数個の円筒ころと、上記内輪軌道と外輪軌道との
一方の軌道の両側に、各円筒ころの長さ寸法よりも僅か
に大きな間隔をあけて設けられた１対の鍔とを備え、上
記各円筒ころは転動面と両端面との間に面取り部を設け
たものである。A cylindrical roller bearing according to the present invention includes an inner ring having an inner ring raceway on an outer peripheral surface, an outer ring having an outer ring raceway on an inner peripheral surface, as in the conventional cylindrical roller bearing described above. A plurality of cylindrical rollers rotatably provided between the inner ring raceway and the outer ring raceway, and slightly larger than the length dimension of each cylindrical roller on both sides of one of the inner ring raceway and the outer ring raceway. A pair of collars provided at intervals is provided, and each of the cylindrical rollers has a chamfered portion between the rolling surface and both end surfaces.
【００１１】特に、本発明の円筒ころ軸受に於いては、
上記各面取り部と上記両端面とを、曲率半径が０．３mm
以上の曲面で連続させた事を特徴としている。Particularly, in the cylindrical roller bearing of the present invention,
The radius of curvature of each of the chamfered portions and the both end surfaces is 0.3 mm.
It is characterized by being continuous with the above curved surface.
【００１２】[0012]
【作用】上述の様に構成される本発明の円筒ころ軸受に
よれば、円筒ころがスキューし、各面取り部と両端面と
の連続部が鍔の内側面部分と摺接しても、この摺接部に
働くエッヂロードが小さくて済む。又、摺接部への油膜
形成が効率良く行なわれ、上記摺接部分に著しい摩耗に
結び付く様な金属接触が起こりにくくなる。この結果、
上記内側面部分の摩耗防止が図られる。次に、これらの
理由を詳細に説明する。According to the cylindrical roller bearing of the present invention configured as described above, even if the cylindrical roller is skewed and the continuous portion of each chamfered portion and both end surfaces is in sliding contact with the inner side surface portion of the collar, this sliding contact The edge load working on the contact area is small. Further, the oil film is efficiently formed on the sliding contact portion, and it is difficult for the sliding contact portion to be brought into contact with the metal, which would lead to remarkable wear. As a result,
It is possible to prevent wear of the inner surface portion. Next, these reasons will be described in detail.
【００１３】先ず、エッヂロードが小さくて済む理由に
就いて、前記図５〜７に図８を加えて説明する。図８
は、円筒ころ５の端部外周縁部と鍔７の内側面との当接
状態を示す説明図で、図８に−で表した２本の曲線
は、図７の−線で切断した状態での円筒ころ５と鍔
７との表面形状を表している。そして、Ｒ1 は、図４の
曲率半径Ｒに相当する（Ｒ1 ＝Ｒ）もので、図７の−
線に沿った円筒ころ５表面の曲率半径を、Ｒ1 ´は、
図７の−線に沿った鍔７表面の曲率半径を、それぞ
れ表している。First, the reason why the edge load is small will be described with reference to FIGS. Figure 8
8 is an explanatory view showing a contact state between the outer peripheral edge of the end portion of the cylindrical roller 5 and the inner side surface of the collar 7, and the two curves represented by − in FIG. 8 are cut along the − line in FIG. 7. The surface shape of the cylindrical roller 5 and the collar 7 in FIG. Then, R 1 corresponds to the radius of curvature R in FIG. 4 (R 1 = R), and
R 1 ′ is the radius of curvature of the cylindrical roller 5 surface along the line,
The respective radii of curvature of the surface of the collar 7 along the-line in FIG. 7 are represented.
【００１４】又、図８に−で表した２本の曲線は、
図７の−線で切断した状態での円筒ころ５と鍔７と
の表面形状を表している。そして、Ｒ2 は、図７の−
線に沿った円筒ころ５表面の曲率半径を、Ｒ2 ´は、
図７の−線に沿った鍔７表面の曲率半径を、それぞ
れ表している。Further, the two curves represented by-in FIG.
The surface shape of the cylindrical roller 5 and the collar 7 in the state cut by the negative line in FIG. 7 is shown. Then, R 2 is − in FIG.
The radius of curvature of the cylindrical roller 5 surface along the line is R 2 ′ is
The respective radii of curvature of the surface of the collar 7 along the-line in FIG. 7 are represented.
【００１５】前記摺接部に対応する各部の形状が上述の
様である場合に、摺接部に働く接触面圧σは、次式で表
されるWhen the shape of each portion corresponding to the sliding contact portion is as described above, the contact surface pressure σ acting on the sliding contact portion is expressed by the following equation.
【数１】 この（１）式中の曲率半径Ｒ1 、Ｒ1 ´、Ｒ2 、Ｒ2 ´
の内、Ｒ1 が最も小さく、Ｒ1 ´はＲ1 よりも十分に大
きく、Ｒ2 、Ｒ2 ´はＲ1 よりも遥かに大きい。従っ
て、上記（１）式中の１／Ｒ1 、１／Ｒ1 ´、１／Ｒ
2 、１／Ｒ2 ´の内１／Ｒ1 が最も接触面圧σに影響
し、他の１／Ｒ1 ´、１／Ｒ2 、１／Ｒ2 ´による影響
は１／Ｒ1 よりも遥かに小さい。この事を考慮しつつ
（１）式を見れば明らかな通り、各面取り部１０、１０
と両端面９、９とを連続させる曲面１１の曲率半径Ｒ
（＝Ｒ1 ）を大きくすれば、上記接触面圧σを小さくし
て、この接触面圧σに比例するエッヂロードを小さくで
きる。[Equation 1] The radii of curvature R 1 , R 1 ′, R 2 , R 2 ′ in the equation (1)
Among them, R 1 is the smallest, R 1 ′ is sufficiently larger than R 1 , and R 2 and R 2 ′ are much larger than R 1 . Therefore, 1 / R 1 , 1 / R 1 ′, 1 / R in the above equation (1)
Of the 2 and 1 / R 2 ′, 1 / R 1 most affects the contact surface pressure σ, and the other 1 / R 1 ′, 1 / R 2 and 1 / R 2 ′ influences more than 1 / R 1 Much smaller. As can be seen from the equation (1) while taking this into consideration, each chamfered portion 10, 10
Radius R of the curved surface 11 that connects the end surfaces 9 and 9 with each other
By increasing (= R 1 ), the contact surface pressure σ can be reduced, and the edge load proportional to the contact surface pressure σ can be reduced.
【００１６】次に、摺接部への油膜形成が効率良く行な
われる理由に就いて、図９〜１０により説明する。図９
は潤滑油の流れ状態を示している。円筒ころ５の転動面
８と外輪軌道３との接触点をＰ、円筒ころ５の端部と鍔
７の内側面との接触点をＡとし、内輪２が矢印イで示す
様に時計方向に回転した場合に潤滑油は、図９に矢印Ｖ
で示す速度で流れる。この矢印Ｖの方向は、線分ＡＰに
対し直角で円筒ころ５の内向方向である。Next, the reason why the oil film is efficiently formed on the sliding contact portion will be described with reference to FIGS. Figure 9
Indicates the flow state of the lubricating oil. The contact point between the rolling surface 8 of the cylindrical roller 5 and the outer ring raceway 3 is P, the contact point between the end of the cylindrical roller 5 and the inner surface of the collar 7 is A, and the inner ring 2 is clockwise as indicated by the arrow a. If the lubricating oil is rotated in the direction of arrow V
Flows at the speed indicated by. The direction of the arrow V is perpendicular to the line segment AP and is the inward direction of the cylindrical roller 5.
【００１７】図１０は、図９の−線で切断した状態
での円筒ころ５と鍔７との表面形状を表している。ｒ1
は、上記接触点Ａの近傍部分での円筒ころ５表面の曲率
半径を、ｒ2 は同じく鍔７表面の曲率半径を、それぞれ
表している。円筒ころ５の転動に伴って潤滑油は、図１
０に矢印Ｖ´で示す様に上記接触点Ａに向けて送り込ま
れ、この接触点Ａ部分に油膜を形成する。この油膜形成
が円滑に行なわれる為には、上記両曲率半径ｒ1 、ｒ2
を大きくし、潤滑油取り込み時に於けるくさび効果を大
きくする事が有利である。上記円筒ころ５表面の曲率半
径ｒ1 は、前記曲面１１の曲率半径Ｒが大きくなるほど
大きくなる。従って、曲面１１の曲率半径Ｒを大きくす
る事は、油膜形成の点からも有利である事が解る。FIG. 10 shows the surface shapes of the cylindrical roller 5 and the collar 7 in the state of being cut along the negative line in FIG. r 1
Indicates the radius of curvature of the surface of the cylindrical roller 5 in the vicinity of the contact point A, and r 2 similarly indicates the radius of curvature of the surface of the collar 7. As the cylindrical roller 5 rolls, the lubricating oil is
0 is fed toward the contact point A as indicated by an arrow V ′, and an oil film is formed at this contact point A portion. In order to form this oil film smoothly, both the above-mentioned radii of curvature r 1 , r 2
To increase the wedge effect at the time of incorporating the lubricating oil. The radius of curvature r 1 of the surface of the cylindrical roller 5 increases as the radius of curvature R of the curved surface 11 increases. Therefore, it can be understood that increasing the radius of curvature R of the curved surface 11 is advantageous from the viewpoint of forming an oil film.
【００１８】[0018]
【実施例】次に、本発明の効果を確認する為、本発明者
が行なった実験に就いて説明する。実験は図１１に示す
様な円筒ころ軸受を内輪回転で運転する事により行なっ
た。ころ軸受の内径は２５mm、外径は４７mm、幅は１４
mm、円筒ころ５、５の外径及び長さは何れも６．３５mm
である。又、内輪２及び外輪４は軸受鋼製で各円筒ころ
５、５は窒化珪素セラミック製である、ハイブリッド円
筒ころ軸受を使用した。EXAMPLES Next, in order to confirm the effects of the present invention, an experiment conducted by the present inventor will be described. The experiment was carried out by operating a cylindrical roller bearing as shown in FIG. 11 with inner ring rotation. The roller bearing has an inner diameter of 25 mm, an outer diameter of 47 mm, and a width of 14
mm, the outer diameter and the length of the cylindrical rollers 5 and 5 are 6.35 mm.
Is. A hybrid cylindrical roller bearing was used in which the inner ring 2 and the outer ring 4 were made of bearing steel and the cylindrical rollers 5, 5 were made of silicon nitride ceramic.
【００１９】この円筒ころ軸受を、８５kgf のラジアル
荷重を加えた状態で、オイルジェットによる強制潤滑で
潤滑しつつ、７６０００r.p.m.で１５０時間回転させた
後、鍔部７の内側面の表面形状を測定した。測定部位を
図１２に、測定結果を図１３〜１４に、それぞれ示す。
測定部位は図１２に斜格子で示した様に、鍔７の内側面
である。又、図１３〜１４に記載した測定結果の値は、
外輪４の軸方向（図１２〜１４の上下方向）には１００
０倍に、直径方向（同じく左右方向）には２０倍に、そ
れぞれ拡大して表している。This cylindrical roller bearing was rotated for 150 hours at 76000 rpm while being lubricated by forced lubrication with an oil jet under a radial load of 85 kgf, and then the surface shape of the inner surface of the collar portion 7 was changed. It was measured. The measurement site is shown in FIG. 12, and the measurement results are shown in FIGS.
The measurement site is the inner surface of the collar 7, as shown by the diagonal grid in FIG. The values of the measurement results shown in FIGS.
100 in the axial direction of the outer ring 4 (vertical direction in FIGS. 12 to 14).
It is shown in an enlarged scale of 0 times and 20 times in the diameter direction (also in the left-right direction).
【００２０】図１３〜１４の内、各図（イ）は試験前に
於ける鍔７の内側面形状を、各図（ロ）は試験後に於け
る鍔７の内側面形状を、それぞれ表している。又、図１
３は、各面取り部１０、１０と両端面９、９とを連続さ
せる曲面１１（図４）の曲率半径Ｒが０．３mmである転
がり軸受（本発明品）を試験した場合の測定結果を、図
１４は、この曲率半径Ｒが０．２mmである転がり軸受
（従来品）を試験した場合の測定結果を、それぞれ表し
ている。13 to 14, each figure (a) shows the inner side shape of the collar 7 before the test, and each figure (b) shows the inner side shape of the collar 7 after the test. There is. Moreover, FIG.
3 is a measurement result when a rolling bearing (product of the present invention) in which the radius of curvature R of the curved surface 11 (FIG. 4) that connects the chamfered portions 10 and 10 and both end surfaces 9 and 9 is 0.3 mm is tested. FIG. 14 shows the measurement results when a rolling bearing (conventional product) having a radius of curvature R of 0.2 mm was tested.
【００２１】この図１３〜１４から明らかな通り、本発
明の円筒ころ軸受によれば、鍔７、７の内側面の摩耗を
抑える事ができる。尚、上記曲面１１の曲率半径Ｒを大
きくするには、前記面取り部１０、１０形成後に行なう
バレル加工の処理時間を長くする。又、本発明は、外輪
４の側に鍔７、７を形成した円筒ころ軸受だけでなく、
図２に示した様な、内輪２の側に鍔７、７を形成した円
筒ころ軸受にも適用できる事は明らかである。As is apparent from FIGS. 13 to 14, according to the cylindrical roller bearing of the present invention, it is possible to suppress the wear of the inner side surfaces of the collars 7, 7. In addition, in order to increase the radius of curvature R of the curved surface 11, the processing time of barrel processing performed after forming the chamfered portions 10 and 10 is lengthened. Further, the present invention is not limited to the cylindrical roller bearing in which the collars 7, 7 are formed on the outer ring 4 side,
It is obvious that the present invention can also be applied to a cylindrical roller bearing in which the collars 7, 7 are formed on the inner ring 2 side as shown in FIG.
【００２２】[0022]
【発明の効果】本発明の円筒ころ軸受は、以上に述べた
通り構成され作用する為、鍔内側面の摩耗防止並びに焼
き付き防止を図って、円筒ころ軸受を組み込んだ各種機
械装置の耐久性、信頼性を向上させる事ができる。Since the cylindrical roller bearing of the present invention is constructed and operates as described above, it is possible to prevent wear and seizure of the inner surface of the collar, and to improve durability of various mechanical devices incorporating the cylindrical roller bearing. The reliability can be improved.
【図１】本発明の対象となる円筒ころ軸受の第１例を示
す部分断面図。FIG. 1 is a partial sectional view showing a first example of a cylindrical roller bearing to which the present invention is applied.
【図２】同第２例を示す部分断面図。FIG. 2 is a partial cross-sectional view showing the second example.
【図３】円筒ころのみを取り出して示す正面図。FIG. 3 is a front view showing only cylindrical rollers.
【図４】図３のＸ部拡大断面図。FIG. 4 is an enlarged cross-sectional view of the X part of FIG.
【図５】円筒ころがスキューした状態を示す正面図。FIG. 5 is a front view showing a state where the cylindrical rollers are skewed.
【図６】図５の下方から見た図。FIG. 6 is a view seen from below in FIG. 5;
【図７】円筒ころと鍔との接触状態を説明する為、図５
の側方から見た透視図。FIG. 7 is a view for explaining a contact state between a cylindrical roller and a collar.
Perspective view seen from the side.
【図８】円筒ころと鍔との接触状態を説明する為の合成
断面図。FIG. 8 is a composite sectional view for explaining a contact state between a cylindrical roller and a collar.
【図９】潤滑油の送り込み状態を説明する為の、図７と
同様の図。9 is a view similar to FIG. 7 for explaining the feeding state of lubricating oil.
【図１０】潤滑油の送り込み状態を説明する、図７の
−線に沿った拡大断面図。FIG. 10 is an enlarged cross-sectional view taken along the line − in FIG. 7 for explaining the feeding state of lubricating oil.
【図１１】本発明の効果を確認する為の試験に使用した
転がり軸受の断面図。FIG. 11 is a sectional view of a rolling bearing used in a test for confirming the effect of the present invention.
【図１２】表面形状を測定した部分と表面形状の拡大割
合とを説明する図。FIG. 12 is a diagram illustrating a portion where a surface shape is measured and a magnification rate of the surface shape.
【図１３】本発明の円筒ころ軸受の鍔部の、試験前後に
於ける表面形状を示す断面図。FIG. 13 is a cross-sectional view showing the surface shape of the flange portion of the cylindrical roller bearing of the present invention before and after the test.
【図１４】従来の円筒ころ軸受の鍔部の、試験前後に於
ける表面形状を示す断面図。FIG. 14 is a cross-sectional view showing a surface shape of a flange portion of a conventional cylindrical roller bearing before and after a test.
１ 内輪軌道 ２ 内輪 ３ 外輪軌道 ４ 外輪 ５ 円筒ころ ６ 保持器 ７ 鍔 ８ 転動面 ９ 端面 １０ 面取り部 １１ 曲面 1 Inner ring raceway 2 Inner ring 3 Outer ring raceway 4 Outer ring 5 Cylindrical roller 6 Cage 7 Collar 8 Rolling surface 9 End face 10 Chamfer 11 Curved surface
Claims (1)
面に外輪軌道を有する外輪と、上記内輪軌道と外輪軌道
との間に転動自在に設けられた複数個の円筒ころと、上
記内輪軌道と外輪軌道との一方の軌道の両側に、各円筒
ころの長さ寸法よりも僅かに大きな間隔をあけて設けら
れた１対の鍔とを備え、上記各円筒ころは転動面と両端
面との間に面取り部を設けたものである円筒ころ軸受に
於いて、各面取り部と上記両端面とを、曲率半径が０．
３mm以上の曲面で連続させた事を特徴とする円筒ころ軸
受。1. An inner ring having an inner ring raceway on an outer peripheral surface, an outer ring having an outer ring raceway on an inner peripheral surface, and a plurality of cylindrical rollers rotatably provided between the inner ring raceway and the outer ring raceway. On both sides of one of the inner ring raceway and the outer ring raceway, there are provided a pair of flanges provided at intervals slightly larger than the length dimension of each cylindrical roller, and each cylindrical roller has a rolling surface. In a cylindrical roller bearing in which a chamfered portion is provided between the chamfered portion and both end faces, each chamfered portion and the both end faces have a radius of curvature of 0.
Cylindrical roller bearing characterized by being continuous with a curved surface of 3 mm or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17851793A JPH0712133A (en) | 1993-06-28 | 1993-06-28 | Cylindrical roller bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17851793A JPH0712133A (en) | 1993-06-28 | 1993-06-28 | Cylindrical roller bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0712133A true JPH0712133A (en) | 1995-01-17 |
Family
ID=16049863
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17851793A Pending JPH0712133A (en) | 1993-06-28 | 1993-06-28 | Cylindrical roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0712133A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11236920A (en) * | 1998-02-24 | 1999-08-31 | Nippon Seiko Kk | Rolling bearing |
| US6464398B2 (en) | 2000-05-22 | 2002-10-15 | Nsk Ltd. | Roller bearing |
| US6767134B2 (en) | 2001-07-05 | 2004-07-27 | Nsk Ltd. | Roller bearing |
| US6997617B2 (en) | 2003-05-28 | 2006-02-14 | Nsk Ltd. | Roller bearing |
-
1993
- 1993-06-28 JP JP17851793A patent/JPH0712133A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11236920A (en) * | 1998-02-24 | 1999-08-31 | Nippon Seiko Kk | Rolling bearing |
| US6464398B2 (en) | 2000-05-22 | 2002-10-15 | Nsk Ltd. | Roller bearing |
| US6767134B2 (en) | 2001-07-05 | 2004-07-27 | Nsk Ltd. | Roller bearing |
| CN100436851C (en) * | 2001-07-05 | 2008-11-26 | 日本精工株式会社 | Roller bearing |
| USRE48586E1 (en) | 2001-07-05 | 2021-06-08 | Nsk Ltd. | Roller bearing |
| US6997617B2 (en) | 2003-05-28 | 2006-02-14 | Nsk Ltd. | Roller bearing |
| EP1482191A3 (en) * | 2003-05-28 | 2007-04-04 | NSK Ltd., | Roller bearing |
| CN100360820C (en) * | 2003-05-28 | 2008-01-09 | 日本精工株式会社 | Roller bearing |
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