JP2006275285A - Thrust cylindrical roller bearing - Google Patents

Thrust cylindrical roller bearing Download PDF

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JP2006275285A
JP2006275285A JP2006052724A JP2006052724A JP2006275285A JP 2006275285 A JP2006275285 A JP 2006275285A JP 2006052724 A JP2006052724 A JP 2006052724A JP 2006052724 A JP2006052724 A JP 2006052724A JP 2006275285 A JP2006275285 A JP 2006275285A
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diameter side
cylindrical roller
outer diameter
flat plate
cage
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JP2006275285A5 (en
JP4483803B2 (en
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Susumu Ryu
劉　　軍
Ryosuke Yamada
亮輔 山田
Koji Kobayashi
孝司 小林
Azusa Otani
梓 大谷
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NSK Ltd
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NSK Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To realize structure facilitated in design to secure loading capacity and capable of restricting abrasion of an outer diameter side peripheral edge 22 of a pocket 7 provided in a holder 2. <P>SOLUTION: Dimension of a cylindrical roller 8, which is held in each of the pockets 7 of the holder 2 positioned in the axial direction with a guide by a roller, in the radial direction of a chamfer 11 formed in an axial directional end surface at a part close to the outer diameter is set so that a central flat surface 9 existing inside the chamfer 11 is not exposed in an outer surface of an outer diameter side flat plate 14. The cylindrical roller 8 makes a difference between the minimum value Δ<SB>B</SB>of projection of the outer diameter side flat plate 14, which is projected from the outer surface, and a dimension W<SB>11</SB>of the chamfer 11 in the radial direction smaller than plate thickness T<SB>2</SB>of the holder 2. With this structure, rubbing speed between the outer diameter side peripheral edge 22 and the central flat surface 9 can be restricted. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、自動車用変速機、カーエアコン用コンプレッサ、工作機械等、各種機械装置の回転支持部に組み込むスラスト円筒ころ軸受の改良に関する。具体的には、１枚の金属板に打ち抜き加工及び曲げ加工を施す事により低コストで造れる保持器を備えたスラスト円筒ころ軸受の改良に関し、この保持器の摩耗を低減して優れた耐久性を有する構造を実現するものである。尚、本発明の対象となるスラスト円筒ころ軸受には、転動体として、外径寸法に比べて軸方向寸法が大きなニードル（針状ころ）を使用した、スラストニードル軸受も含む。従って、本明細書及び特許請求の範囲に記載した円筒ころには、上記ニードルも含む。   The present invention relates to an improvement of a thrust cylindrical roller bearing incorporated in a rotation support portion of various mechanical devices such as an automobile transmission, a car air conditioner compressor, and a machine tool. Specifically, regarding the improvement of a thrust cylindrical roller bearing with a cage that can be manufactured at low cost by punching and bending a single metal plate, the wear of this cage is reduced and excellent durability is achieved. The structure which has is realized. The thrust cylindrical roller bearing that is the subject of the present invention includes a thrust needle bearing that uses a needle (needle roller) having a larger axial dimension than the outer diameter as a rolling element. Therefore, the cylindrical roller described in the present specification and claims includes the needle.

１枚の金属板に打ち抜き加工及び曲げ加工を施す事により低コストで造れる保持器を備えたスラスト円筒ころとして、特許文献１〜５に記載された技術が知られている。図１３〜１７は、これら各特許文献に記載される等により知られている、従来構造の第１例のスラスト円筒ころ軸受１を示している。このスラスト円筒ころ軸受１は、１個の保持器２と、複数個の円筒ころ８、８とを備える。この保持器２は、鋼板等の金属板を曲げ形成する事により一体に造られたもので、円筒状の内径側リム部４と、円筒状の外径側リム部５と、中間板部６と、複数のポケット７、７とを備える。   As a thrust cylindrical roller provided with a cage that can be manufactured at a low cost by punching and bending a single metal plate, techniques described in Patent Documents 1 to 5 are known. 13 to 17 show a thrust cylindrical roller bearing 1 of a first example having a conventional structure, which is known as described in each of these patent documents. The thrust cylindrical roller bearing 1 includes one cage 2 and a plurality of cylindrical rollers 8 and 8. The cage 2 is integrally formed by bending a metal plate such as a steel plate, and has a cylindrical inner diameter side rim portion 4, a cylindrical outer diameter side rim portion 5, and an intermediate plate portion 6. And a plurality of pockets 7,7.

このうちの内径側リム部４は、上記保持器２の内周縁部に存在するもので、全周に亙って連続する円環状である。又、上記外径側リム部５は、上記保持器２の外周縁部に存在するもので、上記内径側リム部４と同心で全周に亙って連続する円環状である。又、上記中間板部６は、この内径側リム部４と上記外径側リム部５との間に存在するもので、断面形状が径方向に関して屈曲している。更に、上記各ポケット７、７は、上記中間板部６に円周方向に関して間欠的に、それぞれ放射方向に形成されたもので、それぞれの内側に円筒ころ８、８を、転動自在に保持する。   Among these, the inner diameter side rim portion 4 is present at the inner peripheral edge portion of the cage 2 and has an annular shape continuous over the entire circumference. Further, the outer diameter side rim portion 5 is present on the outer peripheral edge portion of the cage 2 and has an annular shape that is concentric with the inner diameter side rim portion 4 and is continuous over the entire circumference. Further, the intermediate plate portion 6 exists between the inner diameter side rim portion 4 and the outer diameter side rim portion 5, and the cross-sectional shape is bent with respect to the radial direction. Further, each of the pockets 7 and 7 is formed in the intermediate plate portion 6 intermittently in the radial direction with respect to the circumferential direction, and holds the cylindrical rollers 8 and 8 in a freely rollable manner inside each. To do.

これら各円筒ころ８、８の軸方向両端面には、図１４に示す様に、これら各円筒ころ８、８の回転中心軸に対し直角方向に拡がる中央平坦面９と、この中央平坦面９の外周縁と転動面１０とを全周に亙って連続させる、部分円すい凸面状若しくは断面形状が部分凸円弧状である凸曲面状の面取り部１１とを形成している。従来構造の場合、この面取り部１１の寸法のうち、上記各円筒ころ８の軸方向の寸法Ｌ8 と径方向の寸法Ｗ8 とをほぼ等しく（Ｌ8 ≒Ｗ8 ）している。又、上記中間板部６のうちで、円周方向に隣り合うポケット７、７同士の間部分は、柱部１２、１２となっている。尚、上記中央平坦面９を含め、本明細書及び特許請求の範囲に記載した中央平坦面は、完全な平坦面とは限らない。平坦面にする事を意図して加工された面であれば良く、例えば、軸方向に１０μｍ程度凹んでいる面も、中央平坦面である。要するに、上記中央平坦面９には、完全な平坦面とする為に厳密な加工を施す必要はない。 As shown in FIG. 14, a central flat surface 9 extending in a direction perpendicular to the rotation center axis of each cylindrical roller 8, 8, and the central flat surface 9 A chamfered portion 11 having a partially conical convex surface shape or a convex curved surface shape having a partially convex arc shape is formed, which continues the outer peripheral edge and the rolling surface 10 over the entire circumference. In the case of the conventional structure, among the dimensions of the chamfered portion 11, the axial dimension L 8 and the radial dimension W 8 of each cylindrical roller 8 are substantially equal (L 8 ≈W 8 ). Further, in the intermediate plate portion 6, the portions between the pockets 7, 7 adjacent in the circumferential direction are column portions 12, 12. In addition, the central flat surface described in this specification and the claims including the central flat surface 9 is not necessarily a perfect flat surface. Any surface may be used as long as it is processed so as to be a flat surface. For example, a surface recessed by about 10 μm in the axial direction is also a central flat surface. In short, the central flat surface 9 does not need to be subjected to strict processing in order to obtain a completely flat surface.

又、上記中間板部６は、中央平板部１３と、外径側平板部１４と、内径側平板部１５と、内径側連続部１６と、外径側連続部１７とから成る。このうちの中央平板部１３は、径方向（図１３、１５の左右方向、図１６の上下方向、図１７の表裏方向）中間部で軸方向一端（図１３、１５の下端）寄り部分に形成されている。又、上記外径側平板部１４は、上記外径側リム部５の径方向内側（図１５の左側）に隣接する、軸方向他端（図１３、１５の上端）寄り部分に形成されている。又、上記内径側平板部１５は、上記内径側リム部４の径方向外側（図１５の右側）に隣接する、軸方向他端寄り部分に形成されている。上記外径側、内径側両平板部１４、１５は、同一平面上に位置する。又、上記内径側連続部１６は、上記内径側平板部１５の外周縁と、上記中央平板部１３の内周縁とを連続させ、上記外径側連続部１７は、この中央平板部１３の外周縁と上記外径側平板部１４の内周縁とを連続させる。これら内径側、外径側両連続部１６、１７同士の間隔は、上記中央平板部１３から離れる程大きくなる。この中央平板部１３の外側面と上記内径側、外径側両リム部４、５の先端縁とは、同一平面上に位置するか、或いは、上記中央平板部１３の外側面の方がこの先端縁よりも軸方向に突出している。   The intermediate plate portion 6 includes a central flat plate portion 13, an outer diameter side flat plate portion 14, an inner diameter side flat plate portion 15, an inner diameter side continuous portion 16, and an outer diameter side continuous portion 17. Of these, the central flat plate portion 13 is formed at a portion closer to one end in the axial direction (the lower end of FIGS. 13 and 15) in the middle portion in the radial direction (the left-right direction in FIGS. 13 and 15, the up and down direction in FIG. Has been. Further, the outer diameter side flat plate portion 14 is formed at a portion near the other end in the axial direction (upper end in FIGS. 13 and 15) adjacent to the radially inner side (left side in FIG. 15) of the outer diameter side rim portion 5. Yes. Further, the inner diameter side flat plate portion 15 is formed at a portion near the other end in the axial direction adjacent to the radially outer side (right side in FIG. 15) of the inner diameter side rim portion 4. The outer diameter side and inner diameter side flat plate portions 14 and 15 are located on the same plane. Further, the inner diameter side continuous portion 16 continues the outer peripheral edge of the inner diameter side flat plate portion 15 and the inner peripheral edge of the central flat plate portion 13, and the outer diameter side continuous portion 17 is an outer periphery of the central flat plate portion 13. The peripheral edge and the inner peripheral edge of the outer diameter side flat plate portion 14 are made continuous. The distance between the inner diameter side and outer diameter side continuous portions 16 and 17 increases as the distance from the central flat plate portion 13 increases. The outer side surface of the central flat plate portion 13 and the leading edges of the inner diameter side and outer diameter side rim portions 4 and 5 are located on the same plane, or the outer side surface of the central flat plate portion 13 is this side. It protrudes in the axial direction from the tip edge.

上述の様に構成する保持器２は、上記各ポケット７、７内に円筒ころ８、８を転動自在に保持した状態で、スラストころ軸受を構成する１対のレース面である、軸方向に対向する互いに平行な１対の平面同士の間に挟持する。上記中間板部６を構成する、上記中央、外径側、内径側各平板部１３〜１５のうち、前記各柱部１２、１２の円周方向両側縁部分は、上記内径側、外径側両連続部１６、１７の両側縁部分に比べて、上記各ポケット７、７内に向け少し突出している。   The cage 2 configured as described above is a pair of race surfaces constituting a thrust roller bearing in a state in which the cylindrical rollers 8 and 8 are rotatably held in the pockets 7 and 7, and are axial directions. Is sandwiched between a pair of parallel planes facing each other. Among the flat plate portions 13 to 15 constituting the intermediate plate portion 6, the circumferential edge portions of the column portions 12 and 12 are the inner diameter side and the outer diameter side. Compared to the side edge portions of both continuous portions 16 and 17, they protrude slightly into the pockets 7 and 7.

即ち、径方向外側位置の上記外径側平板部１４、及び、径方向内側位置の上記内径側平板部１５で、上記各柱部１２、１２の円周方向端縁部を、それぞれ外径側係止部１８、１８及び内径側係止部１９、１９としている。そして、図１５、１７の（Ａ）に示す様に、これら外径側、内径側各係止部１８、１９と、上記各円筒ころ８の転動面１０との係合により、これら各円筒ころ８の一部が上記中央平板部１３及び上記内径側、外径側両リム部４、５の先端縁よりも軸方向に突出したままの状態となる様に、上記保持器２の軸方向一端側（図１５、１７の下側）への軸方向変位を規制している。   That is, in the outer diameter side flat plate portion 14 at the radially outer position and the inner diameter side flat plate portion 15 at the radially inner position, the circumferential end edges of the column portions 12 and 12 are respectively set on the outer diameter side. The locking portions 18 and 18 and the inner diameter side locking portions 19 and 19 are provided. Then, as shown in FIGS. 15 and 17 (A), the engagement between the outer diameter side and inner diameter side locking portions 18 and 19 and the rolling surfaces 10 of the cylindrical rollers 8 makes these cylinders. The axial direction of the cage 2 is such that a part of the roller 8 remains in the axial direction protruding from the central flat plate portion 13 and the leading edge of the inner diameter side and outer diameter side rim portions 4, 5. Axial displacement to one end side (lower side in FIGS. 15 and 17) is restricted.

又、径方向中間位置の上記中央平板部１３で上記各柱部１２、１２の円周方向端縁部を、それぞれ中央係止部２０、２０としている。そして、図１５、１７の（Ｂ）に示す様に、これら中央係止部２０、２０と上記各円筒ころ８の転動面１０との係合により、これら各円筒ころ８の一部が上記外径側、内径側両平板部１４、１５よりも軸方向に突出したままの状態となる様に、上記保持器２の軸方向他端側（図１５、１７の上側）への軸方向変位を規制している。
要するに、上記各ポケット７、７内に上記各円筒ころ８、８を保持した状態で、上記各係止部１８〜２０とこれら各円筒ころ８、８の転動面１０とを係合させて、これら各円筒ころ８、８に対する、上記保持器２の軸方向の変位を抑えている。即ち、この保持器２の軸方向に関する位置決めを、所謂ころ案内により図っている。 Further, in the central flat plate portion 13 at the intermediate position in the radial direction, the circumferential edge portions of the column portions 12 and 12 are set as central locking portions 20 and 20, respectively. Then, as shown in FIGS. 15 and 17B, due to the engagement between the central locking portions 20 and 20 and the rolling surface 10 of each cylindrical roller 8, a part of each cylindrical roller 8 is Axial displacement of the cage 2 toward the other axial end (upper side of FIGS. 15 and 17) so that the outer and inner flat plates 14 and 15 remain protruding in the axial direction. Is regulated.
In short, in a state where the cylindrical rollers 8 and 8 are held in the pockets 7 and 7, the locking portions 18 to 20 and the rolling surfaces 10 of the cylindrical rollers 8 and 8 are engaged with each other. The axial displacement of the cage 2 with respect to the cylindrical rollers 8 and 8 is suppressed. That is, the positioning of the cage 2 in the axial direction is achieved by so-called roller guidance.

上述の様なスラスト円筒ころ軸受１を構成する上記各円筒ころ８、８としては、前述の図１４に示す様に、軸方向両端面中央部（外周縁寄りの面取り部の内側部分）を平坦面としたものが、負荷容量を確保する面から、近年多く使用される様になっている。即ち、円筒ころには、軸方向両端面を部分球面状或いは円すい面状の凸面としたものがあるが、この様な円筒ころの場合には、荷重を支承自在な転動面の軸方向長さ（有効長さ）が短くなり、その分、支承可能な負荷が小さくなる。これに対して、上記軸方向両端面中央部を平坦面とした円筒ころ８、８は、有効長さＬ（図１４参照）を確保して、この円筒ころ８、８を組み込んだスラスト円筒ころ軸受１の負荷容量を確保し易くなる。   As the above-mentioned cylindrical rollers 8 and 8 constituting the thrust cylindrical roller bearing 1 as described above, as shown in FIG. 14 described above, the center part of the axial end faces (the inner part of the chamfered part near the outer peripheral edge) is flat. In recent years, the surface has been frequently used from the viewpoint of securing the load capacity. In other words, some cylindrical rollers have a partially spherical or conical convex surface at both axial end surfaces. In the case of such cylindrical rollers, the axial length of the rolling surface on which a load can be supported is provided. (Effective length) is shortened, and the load that can be supported is reduced accordingly. On the other hand, the cylindrical rollers 8 and 8 having flat central surfaces at both axial end faces secure an effective length L (see FIG. 14), and are thrust cylindrical rollers incorporating the cylindrical rollers 8 and 8. It becomes easy to ensure the load capacity of the bearing 1.

ところで、上述の様なスラスト円筒ころ軸受１の使用時に上記各円筒ころ８、８には、遠心力に基づいて上記保持器２の径方向外方に向いた力が加わる。そして、この力により上記各円筒ころ８、８の軸方向両端面のうち、上記保持器２の径方向外側となる外径側端面２１が、上記各ポケット７、７の周縁部のうち、この保持器２の径方向外側となる外径側周縁部２２に押し付けられる。この結果、この外径側周縁部２２と上記外径側端面２１とが、図１７の（Ａ）の斜格子で示した部分で擦れ合う。但し、この外径側端面２１は上記外径側周縁部２２に対し、均等に押し付けられる訳ではない。実際の場合にこの外径側端面２１は、上記各ポケット７、７内での上記各円筒ころ８、８のスキューに起因して、その外径寄り部分が上記外径側周縁部２２に押し付けられた状態で、互いに摺接する。   By the way, when the thrust cylindrical roller bearing 1 as described above is used, a force directed radially outward of the cage 2 is applied to the cylindrical rollers 8 and 8 based on the centrifugal force. And by this force, the outer diameter side end surface 21 which becomes the radial direction outer side of the cage 2 among the axial direction both end surfaces of the cylindrical rollers 8 and 8 is the outer peripheral side portion of the pockets 7 and 7. The retainer 2 is pressed against the outer peripheral side peripheral edge 22 which is the radially outer side. As a result, the outer diameter side peripheral edge portion 22 and the outer diameter side end face 21 rub against each other at the portion indicated by the oblique lattice in FIG. However, the outer diameter side end face 21 is not uniformly pressed against the outer diameter side peripheral edge 22. In an actual case, the outer diameter side end surface 21 is pressed against the outer diameter side peripheral edge portion 22 due to the skew of the cylindrical rollers 8, 8 in the pockets 7, 7. In contact with each other.

即ち、スラスト円筒ころ軸受１の運転時には、図１８の（Ａ）に示す様に、上記各円筒ころ８、８の自転軸の方向と上記保持器２の径方向とが互いに一致している事が理想であるが、実際の場合には、図１８の（Ｂ）に鎖線で示す様に、これら両方向が互いに不一致になる、スキューが発生する事が避けられない。この様なスキューは、上記各円筒ころ８、８の転動面１０とレース面との転がり接触部の摩擦係数が、転がり接触部の長さ方向に関して不均一である等により発生する。又、上記外径側端面２１と上記外径側周縁部２２とが片当たりする程度は、上記両方向のずれ角度（スキュー角度）が大きくなる程著しくなる。   That is, when the thrust cylindrical roller bearing 1 is operated, as shown in FIG. 18A, the direction of the rotation shaft of each of the cylindrical rollers 8 and 8 and the radial direction of the cage 2 must coincide with each other. In an actual case, it is inevitable that a skew occurs in which these two directions do not coincide with each other, as indicated by a chain line in FIG. Such a skew is caused by the friction coefficient of the rolling contact portion between the rolling surface 10 of each of the cylindrical rollers 8 and 8 and the race surface being non-uniform in the length direction of the rolling contact portion. Further, the degree of contact between the outer diameter side end face 21 and the outer diameter side peripheral edge 22 becomes more significant as the deviation angle (skew angle) in both directions increases.

上記各円筒ころ８、８がスキューしつつ、上記外径側端面２１のうちで、前記中央平坦面９のうちの外周縁部と前記面取り部１１との境界部分と上記外径側周縁部２２とが擦れ合うと、この擦れ合い部に局部的な応力集中が発生し、しかも大きな擦れ合い速度で擦れ合う。更には、この擦れ合い部に潤滑の為の油膜が形成されにくくなって、この擦れ合い部に金属接触が発生し易くなる。この結果、上記各円筒ころ８、８を構成する軸受鋼に比較して軟質の金属により造られた保持器２の一部で上記外径側周縁部２２部分に、図１９に示す様な、保持器２の円周方向両側程摩耗程度が著しい、凹入部２３が形成される。   While the cylindrical rollers 8 and 8 are skewed, a boundary portion between the outer peripheral edge portion of the central flat surface 9 and the chamfered portion 11 and the outer diameter side peripheral edge portion 22 in the outer diameter side end surface 21. When the two rub against each other, local stress concentration occurs in the rubbing portion, and rubbing occurs at a high rubbing speed. Furthermore, it becomes difficult to form an oil film for lubrication in the rubbing portion, and metal contact is likely to occur in the rubbing portion. As a result, a part of the cage 2 made of a soft metal compared to the bearing steel constituting each of the cylindrical rollers 8 and 8 is formed on the outer peripheral side peripheral edge 22 portion as shown in FIG. A recessed portion 23 is formed in which the degree of wear is remarkable on both sides in the circumferential direction of the cage 2.

この様な凹入部２３が或る程度大きくなると、上記各円筒ころ８、８の一部で上記保持器２の径方向外端部外周縁に設けた面取り部１１が、上記凹入部２３内に入り込みつつ、本来のポケット７、７の位置よりも上記保持器２の径方向外方に変位する、所謂潜り込みが発生する。この様な潜り込みが発生すると、保持器に対するころ端面の摺動抵抗が増大し、前記スラスト円筒ころ軸受１を組み込んだ回転支持部の回転抵抗が大きくなり、この回転支持部を有する各種機械装置の性能が低下するだけでなく、著しい場合にはフレーキングや焼き付き等の故障の原因となる。この様な不都合を生じる摩耗は、近年に於ける自動車の性能向上により、トランスミッションやカーエアコンコンプレッサ等の各種機械装置の回転部分の回転速度が速くなる事に伴い、従来に比べて発生し易くなっている。   When such a recessed portion 23 becomes large to some extent, a chamfered portion 11 provided on the outer peripheral edge of the retainer 2 in the radial direction at a part of each of the cylindrical rollers 8, 8 is formed in the recessed portion 23. While entering, a so-called submergence occurs that is displaced radially outward of the cage 2 from the original position of the pockets 7 and 7. When such subsidence occurs, the sliding resistance of the roller end surface with respect to the cage increases, and the rotational resistance of the rotational support portion incorporating the thrust cylindrical roller bearing 1 increases. Not only is the performance deteriorated, but it may cause a failure such as flaking or seizure if it is remarkable. Wear that causes such inconvenience is more likely to occur than in the past, as the speed of rotation of various mechanical devices such as transmissions and car air conditioner compressors has increased due to recent improvements in automobile performance. ing.

一方、図２０に示す様な、軸方向両端面を部分球状の凸面とした円筒ころ８ａを、図２１に示す様に、上述した従来構造の場合と同様の保持器２に組み込んだ場合には、スキューの有無に拘らず、この保持器２のポケット７の外径側周縁部２２のうちの内側面端縁と上記円筒ころ８ａの部分球状の凸面である外径側端面２１ａとが擦れ合う（エッジ当たりする）事により、この外径側周縁部２２の中央部に、図２２に示す様な部分円弧状の凹入部２３ａが形成される。そして、この凹入部２３ａが大きくなると、やはり上述した様な問題を生じる。   On the other hand, when a cylindrical roller 8a having a partially spherical convex surface at both axial end faces as shown in FIG. 20 is incorporated in the cage 2 similar to the conventional structure described above, as shown in FIG. Regardless of the presence or absence of skew, the inner surface edge of the outer diameter side peripheral portion 22 of the pocket 7 of the cage 2 and the outer diameter side end surface 21a which is a partial spherical convex surface of the cylindrical roller 8a are rubbed together ( By hitting the edge, a concave portion 23a having a partial arc shape as shown in FIG. 22 is formed at the center of the outer peripheral side peripheral edge portion 22. And when this recessed part 23a becomes large, the problem as mentioned above will also arise.

この様な不都合を低減させる構造として従来から、特許文献５に記載された構造が知られている。図２３は、この特許文献５に記載された発明に準じた従来構造を示している。この従来構造の場合には、保持器２のポケット７ａを、外径側リム部５ａの基部に達する部分にまで形成している。そして、このポケット７ａ内に、軸方向両端面を部分球状の凸面とした円筒ころ８ａを保持し、この円筒ころ８ａの外径側端面２１ａを、上記外径側リム部５ａの内周面に対向させている。この様な従来構造の場合、これら両面同士が擦れ合った場合でも、擦れ合い部の直径を僅少にして擦れ合い速度Ｖを極く小さく抑えられるので、上記擦れ合い部の摩耗を抑えられる。但し、この様な引用文献５に記載された従来構造の場合には、軸方向端面を凸面とした円筒ころ８ａを使用する事が必要となるので、この円筒ころ８ａのうち、荷重を支承自在な転動面の軸方向長さＬ8aが短くなり、その分、支承可能な負荷が小さくなる。 Conventionally, a structure described in Patent Document 5 has been known as a structure for reducing such inconvenience. FIG. 23 shows a conventional structure according to the invention described in Patent Document 5. In the case of this conventional structure, the pocket 7a of the cage 2 is formed up to the portion reaching the base of the outer diameter side rim portion 5a. And in this pocket 7a, the cylindrical roller 8a which made the axial direction both end surface the partial spherical convex surface is hold | maintained, and the outer diameter side end surface 21a of this cylindrical roller 8a is made into the inner peripheral surface of the said outer diameter side rim | limb part 5a. They are facing each other. In the case of such a conventional structure, even when these two surfaces are rubbed against each other, the rubbed portion diameter is made small and the rubbed speed V can be kept extremely low, so that wear of the rubbed portion can be suppressed. However, in the case of the conventional structure described in the cited document 5, it is necessary to use a cylindrical roller 8a having a convex end surface in the axial direction. The length L 8a in the axial direction of the rolling surface is shortened, and the load that can be supported is correspondingly reduced.

特開平６−９４０３８号公報JP-A-6-94038 特開２０００−２１３５４６号公報JP 2000-213546 A 特開２００２−２０６５２５号公報JP 2002-206525 A 特開平１１−３５１２４５号公報JP-A-11-351245 特開２００３−８３３３３号公報JP 2003-83333 A

本発明は、上述の様な事情に鑑みて、負荷容量を確保する為の設計が容易で、保持器のポケット内に円筒ころを組み込む事を容易に行なえ、しかも保持器に設けたポケットの外径側周縁部の摩耗を抑えられる円筒ころ軸受を実現すべく発明したものである。   In view of the circumstances as described above, the present invention is easy to design for securing the load capacity, can easily incorporate cylindrical rollers into the pocket of the cage, and is outside the pocket provided in the cage. The invention was invented to realize a cylindrical roller bearing capable of suppressing the wear of the radial side periphery.

本発明のスラスト円筒ころ軸受は、何れも、前述した従来から知られているスラスト円筒ころ軸受と同様に、保持器と、複数個の円筒ころとを備える。
このうちの保持器は、全体を円輪状に造られて、円周方向複数個所に、それぞれが放射方向に配置された複数のポケットを備える。
又、上記保持器は、金属板を曲げ形成する事により一体に造られて、内径側リム部と、外径側リム部と、中間板部と、上記各ポケットと、複数の柱部とを備える。
このうちの内径側リム部は内周縁部に存在し、全周に亙って連続する円環状であり、上記外径側リム部は、外周縁部に存在し、上記内径側リム部と同心で全周に亙って連続する円環状である。
又、上記中間板部は、上記外径側リム部と上記内径側リム部との間に存在して、断面形状が径方向に関し屈曲しており、中央平板部と、外径側平板部と、内径側平板部と、内径側連続部と、外径側連続部とから成る。
このうちの中央平板部は、径方向中間部で軸方向一端寄り部分に形成されている。
又、上記外径側平板部は、上記外径側リム部の径方向内側に隣接する、軸方向他端寄り部分に形成されている。
又、上記内径側平板部は、上記内径側リム部の径方向外側に隣接する、軸方向他端寄り部分に形成されている。
又、上記内径側連続部は、上記内径側平板部の外周縁と上記中央平板部の内周縁とを連続させ、上記外径側連続部は、この中央平板部の外周縁と上記外径側平板部の内周縁とを連続させる。
又、上記各ポケットは、上記中間板部の径方向に長い矩形孔であって、この中間板部に円周方向に関して間欠的に、それぞれ放射方向に形成されている。
又、上記各円筒ころは、上記保持器の各ポケット内に、転動自在に保持されている。 Each of the thrust cylindrical roller bearings of the present invention includes a cage and a plurality of cylindrical rollers, like the conventionally known thrust cylindrical roller bearing.
Of these, the cage is formed in an annular shape as a whole, and includes a plurality of pockets arranged in a radial direction at a plurality of locations in the circumferential direction.
The cage is integrally formed by bending a metal plate, and includes an inner diameter side rim portion, an outer diameter side rim portion, an intermediate plate portion, the respective pockets, and a plurality of column portions. Prepare.
Of these, the inner diameter side rim portion is present at the inner peripheral edge and has an annular shape continuous over the entire circumference, and the outer diameter side rim portion is present at the outer peripheral edge portion and is concentric with the inner diameter side rim portion. It is an annular shape that continues around the entire circumference.
Further, the intermediate plate portion exists between the outer diameter side rim portion and the inner diameter side rim portion, and the cross-sectional shape is bent in the radial direction, and the central flat plate portion, the outer diameter side flat plate portion, The inner diameter side flat plate portion, the inner diameter side continuous portion, and the outer diameter side continuous portion.
Among these, the central flat plate portion is formed at a portion near one end in the axial direction at the radial intermediate portion.
Further, the outer diameter side flat plate portion is formed in a portion near the other end in the axial direction adjacent to the radially inner side of the outer diameter side rim portion.
Further, the inner diameter side flat plate portion is formed in a portion near the other end in the axial direction adjacent to the radially outer side of the inner diameter side rim portion.
The inner diameter side continuous portion continuously connects the outer peripheral edge of the inner diameter side flat plate portion and the inner peripheral edge of the central flat plate portion, and the outer diameter side continuous portion includes the outer peripheral edge of the central flat plate portion and the outer diameter side. The inner peripheral edge of the flat plate portion is made continuous.
The pockets are rectangular holes that are long in the radial direction of the intermediate plate portion, and are formed in the intermediate plate portion in the radial direction intermittently in the circumferential direction.
Further, each of the cylindrical rollers is rotatably held in each pocket of the cage.

又、本発明の円筒ころ軸受は、前述した従来から知られているスラスト円筒ころ軸受と同様に、上記軸方向一端側への上記保持器の軸方向変位を、上記外径側平板部及び内径側平板部の一部で上記各柱部の円周方向端縁に設けられた各外径側係止部及び各内径側係止部と上記各円筒ころの転動面との係合により、これら各円筒ころの一部が上記内径側、外径側両リム部の先端縁及び上記中央平板部よりも軸方向に突出したままの状態となる様に規制している。
又、上記軸方向他端側への上記保持器の軸方向変位を、上記中央平板部の一部で上記各柱部の円周方向端縁に設けられた各中央係止部と上記各円筒ころの転動面との係合により、これら各円筒ころの一部が上記外径側平板部及び上記内径側平板部よりも軸方向に突出したままの状態となる様に規制している。 Further, the cylindrical roller bearing of the present invention is similar to the previously known thrust cylindrical roller bearing, and the axial displacement of the cage toward the one end in the axial direction is changed to the outer diameter side flat plate portion and the inner diameter. By engaging each outer diameter side locking portion and each inner diameter side locking portion provided on the circumferential edge of each column portion with a part of the side flat plate portion and the rolling surface of each cylindrical roller, A part of each of these cylindrical rollers is regulated so as to remain protruding in the axial direction from the leading edge of both the inner diameter side and outer diameter side rim portions and the central flat plate portion.
In addition, the axial displacement of the cage toward the other end in the axial direction is caused by each central locking portion provided at the circumferential edge of each column portion and each cylinder at a part of the central flat plate portion. Engagement with the rolling surface of the roller restricts a part of each of the cylindrical rollers to protrude in the axial direction from the outer diameter side flat plate portion and the inner diameter side flat plate portion.

特に、本発明のスラスト円筒ころ軸受に於いては、何れも、上記各円筒ころは、それぞれの軸方向両端面のうちの少なくとも上記保持器の外径側端面に、これら各円筒ころの回転中心軸に対し直角方向に拡がる中央平坦面と、この中央平坦面の外周縁と転動面とを全周に亙って連続させる面取り部とを備えたものである。   In particular, in the thrust cylindrical roller bearing of the present invention, each of the cylindrical rollers has a rotational center of the cylindrical rollers at least on the outer diameter side end surface of the cage among the both axial end surfaces. A central flat surface that extends in a direction perpendicular to the axis, and a chamfered portion that continuously connects the outer peripheral edge and the rolling surface of the central flat surface over the entire circumference.

そして、請求項１に記載したスラスト円筒ころ軸受の場合には、上記保持器を軸方向一端側に変位させて上記各外径側係止部及び各内径側係止部と上記各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記保持器を構成する外径側、内径側両平板部の外面から突出する量を、これら各円筒ころの径方向に関する上記面取り部の寸法未満にしている。これと共に、上記保持器を軸方向他端側に変位させて上記各中央係止部と上記各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記保持器を構成する外径側平板部の外面から突出する量とこれら各円筒ころの径方向に関する上記面取り部の寸法との差を、上記金属板の板厚よりも小さくしている。   In the case of the thrust cylindrical roller bearing according to claim 1, the retainer is displaced to one end side in the axial direction so that each of the outer diameter side locking portions, each inner diameter side locking portion, and each of the cylindrical rollers is displaced. With the rolling surface engaged, the amount of a part of each cylindrical roller protruding from the outer surface of both the outer diameter side and inner diameter side flat plate portions constituting the cage is determined in the radial direction of each cylindrical roller. The dimension of the chamfered portion is less than that of the above. At the same time, the retainer is displaced to the other end side in the axial direction so that the central locking portions and the rolling surfaces of the cylindrical rollers are engaged with each other. The difference between the amount protruding from the outer surface of the outer diameter side flat plate portion constituting the vessel and the dimension of the chamfered portion in the radial direction of each cylindrical roller is made smaller than the thickness of the metal plate.

上述の様に構成する本発明によれば、負荷容量を確保する為の設計が容易で、しかも保持器に設けた各ポケットの外径側周縁部の摩耗を抑え、この摩耗に基づく、各円筒ころの外径側端部が保持器の外径寄り部分の片面側に潜り込む事を防止できるスラスト円筒ころ軸受を実現できる。
即ち、上記各ポケットの外径側周縁部と、これら各ポケット内に保持された各円筒ころの外径側端面との擦れ合い部を、従来に比べて狭い範囲内に収め、この擦れ合い部をより各ポケットの円周方向の中央寄り部分に位置させる事ができる。この為、スキューによる片当たりを起因として、この擦れ合い部に局部的な応力集中が発生しにくくなり、更にこの擦れ合い部の滑り速度Ｖを小さく抑えられる。この結果、上記外径側周縁部部分に、前述の図１９に示した様な、摩耗による凹入部２３が形成される事を防止できる。
又、上記各円筒ころとして、軸方向両端面のうちの少なくとも上記保持器の外径側端面に、これら各円筒ころの回転中心軸に対し直角方向に拡がる中央平坦面を備えたものを使用する為、スラスト円筒ころ軸受の負荷容量の確保を図るべく、これら各円筒ころの有効長さを大きくする設計が容易になる。
更に、上記保持器の軸方向位置を、上記各ポケットに形成した上記各係止部と上記各円筒ころの転動面との係合により図っているので、上記保持器の軸方向両側面と相手レース面とが擦れ合う事がない。この為、この保持器がこのレース面に付着した潤滑油を掻き取る事を防止して、このレース面と上記各円筒ころの転動面との転がり接触部を良好に潤滑できる。 According to the present invention configured as described above, the design for securing the load capacity is easy, and further, the wear of the outer peripheral side peripheral portion of each pocket provided in the cage is suppressed, and each cylinder based on this wear. A thrust cylindrical roller bearing that can prevent the outer diameter side end of the roller from entering one side of the outer diameter portion of the cage can be realized.
That is, the rubbing portion between the outer diameter side peripheral portion of each pocket and the outer diameter side end surface of each cylindrical roller held in each pocket is accommodated within a narrow range compared to the conventional case, and this rubbing portion. Can be positioned more in the circumferentially central portion of each pocket. For this reason, local stress concentration is less likely to occur in the rubbing portion due to the piece contact due to the skew, and the sliding speed V of the rubbing portion can be further reduced. As a result, it is possible to prevent the recessed portion 23 from being formed by wear as shown in FIG.
Further, as each of the cylindrical rollers, one provided with a central flat surface that extends in a direction perpendicular to the rotation center axis of each cylindrical roller at least on the outer diameter side end surface of the cage among both axial end surfaces. Therefore, in order to secure the load capacity of the thrust cylindrical roller bearing, it is easy to design to increase the effective length of each cylindrical roller.
Furthermore, since the axial position of the cage is achieved by the engagement between the locking portions formed in the pockets and the rolling surfaces of the cylindrical rollers, both axial sides of the cage There is no rubbing against the opponent race surface. For this reason, it is possible to prevent the retainer from scraping off the lubricating oil adhering to the race surface and to satisfactorily lubricate the rolling contact portion between the race surface and the rolling surface of each cylindrical roller.

本発明を実施する場合に好ましくは、請求項２に記載した様に、保持器を軸方向一端側に変位させて各外径側係止部及び各内径側係止部と各円筒ころの転動面とを係合させた状態で、これら各円筒ころの中央平坦面と各ポケットの外径側周縁部との擦れ合い面の長さを、これら各円筒ころの直径の８０％以内に抑える。
この様に構成すれば、擦れ合い部に於ける局部的な応力集中をより一層発生しにくくでき、この擦れ合い部の滑り速度Ｖを更に小さくできる。この結果、上記外径側周縁部部分に、前述の図１９に示した様な、摩耗による凹入部２３が形成される事をより有効に防止できる。 In carrying out the present invention, preferably, as described in claim 2, the cage is displaced toward one end in the axial direction so that each outer diameter side locking portion, each inner diameter side locking portion and each cylindrical roller are rotated. With the moving surface engaged, the length of the rubbing surface between the central flat surface of each cylindrical roller and the outer peripheral side peripheral portion of each pocket is kept within 80% of the diameter of each cylindrical roller. .
With this configuration, local stress concentration in the rubbing portion can be made less likely to occur, and the sliding speed V of the rubbing portion can be further reduced. As a result, it is possible to more effectively prevent the concave portion 23 due to wear as shown in FIG.

又、本発明を実施する場合に好ましくは、請求項３に記載した様に、各円筒ころの面取り部の寸法のうち、これら各円筒ころの軸方向の寸法よりも同じく径方向の寸法を大きくする。
この様な構成を採用すれば、スラスト円筒ころ軸受の負荷容量の確保を図るべく、これら各円筒ころの有効長さを更に大きくする設計が可能になる。 Preferably, when carrying out the present invention, as described in claim 3, among the dimensions of the chamfered portion of each cylindrical roller, the radial dimension is set to be larger than the axial dimension of each cylindrical roller. To do.
By adopting such a configuration, it is possible to design the effective length of each cylindrical roller to be further increased in order to secure the load capacity of the thrust cylindrical roller bearing.

又、本発明を実施する場合に好ましくは、請求項４に記載した様に、保持器を軸方向一端側に変位させて各外径側係止部及び各内径側係止部と各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記保持器を構成する外径側、内径側両平板部の外面から突出する量と、この保持器を軸方向他端側に変位させて各中央係止部と上記各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記両平板部の外面から突出する量との差、即ち、これら各円筒ころに対する上記保持器の軸方向に関するガタ量を、５０μｍ以上とする。
前述した、この保持器の軸方向に関する位置決めをころ案内で図る為の条件を満たしつつ、上記ガタ量を５０μｍ以上確保すれば、上記各円筒ころの転動面と上記保持器を構成する各柱部の円周方向両側縁との隙間を十分に確保できる。この為、上記各円筒ころの転動面に付着した潤滑油がこれら各柱部の円周方向両側縁により掻き取られる事を防止して、これら各円筒ころの転動面と相手レース面との転がり接触部に十分な潤滑油を供給できる。そして、これら各転がり接触部に十分な油膜を形成して、上記各円筒ころの転動面及び相手レース面の転がり疲れ寿命の確保を図れる。 Further, when the present invention is implemented, preferably, as described in claim 4, the retainer is displaced to one end side in the axial direction so that each outer diameter side locking portion, each inner diameter side locking portion and each cylindrical roller are displaced. The amount of protrusion of each cylindrical roller from the outer surface of both the outer diameter side and inner diameter side flat plate portions constituting the cage, and the cage in the axial direction. In a state where each central locking portion and the rolling surface of each cylindrical roller are engaged with each other by being displaced to the other end side, a part of each of these cylindrical rollers protrudes from the outer surface of the both flat plate portions. The difference, that is, the backlash in the axial direction of the cage with respect to each cylindrical roller is set to 50 μm or more.
While satisfying the above-mentioned conditions for positioning the cage in the axial direction with the roller guide, and securing the backlash amount of 50 μm or more, the rolling surfaces of the cylindrical rollers and the columns constituting the cage A sufficient gap can be secured between both side edges of the portion in the circumferential direction. For this reason, it is possible to prevent the lubricating oil adhering to the rolling surface of each cylindrical roller from being scraped off by the circumferential side edges of each column portion, and the rolling surface of each cylindrical roller and the mating race surface. Sufficient lubricating oil can be supplied to the rolling contact portion. And sufficient oil film can be formed in each of these rolling contact portions, and the rolling fatigue life of the rolling surface and the mating race surface of each cylindrical roller can be ensured.

更に、本発明を実施する場合に好ましくは、請求項５に記載した様に、上記各円筒ころの転動面とそれぞれ転がり接触するレース面を有する１対の部材を、何れも使用時に回転するものとし、保持器の中央平板部を、使用回転速度が速い部材に対向させる。
この様な構成を採用すれば、より多くの潤滑油を上記各円筒ころの外径側端面と上記保持器の外径側周縁部との擦れ合い部に送り込め、この擦れ合い部での金属接触を発生しにくくできる。 Further, when the present invention is carried out, preferably, as described in claim 5, each of the pair of members having race surfaces which are in rolling contact with the rolling surfaces of the respective cylindrical rollers is rotated during use. Assume that the central flat plate portion of the cage is opposed to a member having a high rotational speed.
If such a configuration is adopted, a larger amount of lubricating oil is fed into the rubbed portion between the outer diameter side end surface of each cylindrical roller and the outer rim side peripheral portion of the cage, and the metal at the rubbed portion is fed. It is difficult to generate contact.

更に、本発明を実施する場合に好ましくは、請求項６に記載した様に、各ポケットを、金属板に打ち抜き加工を施す事により形成する。又、この打ち抜き加工は、パンチを、外径側、内径側両平板部の内面側から外面側に突き通す事により行なう。従って、上記各ポケットの内周縁のうちで上記外径側、内径側両平板部に対応する部分に、これら両平板部の内面側に上記打ち抜き加工に伴う剪断面が、同じく外側面側に破断面が、それぞれ存在する。そして、各円筒ころの軸方向両端面のうちの少なくとも上記保持器の外径側端面に設けた中央平坦面を、上記各ポケット内での上記各円筒ころの変位に拘らず、上記破断面と接触しない様にする。この為に、これら各円筒ころの一部が上記保持器を構成する外径側平板部の外面から突出する量とこれら各円筒ころの径方向に関する面取り部の寸法との差を、上記破断面の幅との関係で規制する。   Furthermore, when implementing this invention, Preferably, as described in Claim 6, each pocket is formed by stamping a metal plate. This punching process is performed by penetrating the punch from the inner surface side to the outer surface side of both the outer diameter side and inner diameter side flat plate portions. Therefore, in the inner peripheral edge of each pocket, the shear surface associated with the punching process on the inner surface side of both the flat plate portions is also broken on the outer surface side in the portions corresponding to both the outer diameter side and inner diameter side flat plate portions. Each cross section exists. And, the central flat surface provided on at least the outer diameter side end surface of the cage among the axial end surfaces of each cylindrical roller is the fracture surface regardless of the displacement of each cylindrical roller in each pocket. Avoid contact. Therefore, the difference between the amount of a part of each cylindrical roller protruding from the outer surface of the outer diameter side flat plate portion constituting the cage and the dimension of the chamfered portion in the radial direction of each cylindrical roller is determined by the above-described fracture surface. Regulate in relation to the width of

この様な構成を採用すれば、低コストで造れる構成で、上記各円筒ころの軸方向端面に存在する中央平坦面と、上記破断面とが擦れ合う事を防止できる。そして、この中央平坦面と、上記各ポケットの内周縁のうちで上記外径側平板部に対応する部分との擦れ合い部の摩擦を低減できる。即ち、上記各ポケットの形成作業を低コストで行なう為には、プレス加工機を使用した、パンチでの打ち抜き加工による事が好ましい。但し、打ち抜き加工により上記各ポケットを形成すると、形成後の各ポケットの内周縁に、剪断面と破断面とが形成される。このうちの剪断面が上記パンチの挿入方向入口側に、破断面が同じく出口側に、それぞれ形成される。素材となる上記金属板の厚さ方向に関する、これら剪断面と破断面との割合は、上記パンチと受型との間のクリアランスや、パンチの先端縁の形状等、打ち抜き加工の条件により変わる。具体的には、クリアランスを小さくし、先端縁を尖らせる程、剪断面の割合が多くなる。但し、スラスト円筒ころ軸受用保持器の製造作業を、低コストで能率良く行なう事を考慮した場合、剪断面と破断面との割合は、ほぼ同じ程度になる。   By adopting such a configuration, it is possible to prevent the central flat surface existing on the axial end surface of each cylindrical roller from rubbing against the fracture surface with a configuration that can be manufactured at low cost. And the friction of the friction part of this center flat surface and the part corresponding to the said outer diameter side flat plate part among the inner peripheral edges of each said pocket can be reduced. That is, in order to perform the operation of forming the pockets at a low cost, it is preferable to perform punching with a punch using a press machine. However, when each of the pockets is formed by punching, a shear surface and a fracture surface are formed on the inner peripheral edge of each pocket after the formation. Of these, a shear surface is formed on the inlet side of the punch in the insertion direction, and a fracture surface is formed on the outlet side. The ratio between the shear surface and the fracture surface in the thickness direction of the metal plate as the material varies depending on the punching conditions such as the clearance between the punch and the receiving die and the shape of the tip edge of the punch. Specifically, as the clearance is reduced and the tip edge is sharpened, the ratio of the shear surface increases. However, when considering the production of the thrust cylindrical roller bearing retainer efficiently at a low cost, the ratio between the sheared surface and the fractured surface is approximately the same.

上記剪断面の表面粗さと上記破断面の表面粗さとを比較した場合、剪断面の表面粗さの値が小さい（平滑面に近い、比較的良好な摩擦面である）。従って、請求項６に記載した発明の構造によれば、上記各円筒ころの軸方向端面に存在する中央平坦面と、比較的良好な摩擦面である上記剪断面とのみを摺接させて（この中央平坦面と上記破断面とが擦れ合う事を防止して）、この中央平坦面と相手面との擦れ合い部の摩擦を低減できる。従って、上記各ポケットの内周縁に、製造コストの上昇に結び付く様な仕上加工を行なわなくても、スラスト円筒ころ軸受の耐久性向上を図れる。   When the surface roughness of the shear surface is compared with the surface roughness of the fracture surface, the value of the surface roughness of the shear surface is small (a relatively good friction surface close to a smooth surface). Therefore, according to the structure of the invention described in claim 6, only the central flat surface existing on the axial end surface of each cylindrical roller and the shear surface, which is a relatively good friction surface, are brought into sliding contact ( This prevents the center flat surface and the fracture surface from rubbing), thereby reducing the friction of the rubbing portion between the center flat surface and the mating surface. Therefore, it is possible to improve the durability of the thrust cylindrical roller bearing without performing a finishing process on the inner peripheral edge of each of the pockets so as to increase the manufacturing cost.

図１〜２は、請求項１に対応する、本発明の実施例１を示している。尚、本実施例の特徴は、各円筒ころ８の軸方向両端面外径寄り部分に形成した面取り部１１の径方向寸法（中央部に形成した中央平坦面９の直径）との関係で、保持器２を構成する中間板部６に放射方向に設けた複数のポケット７内での各円筒ころ８の動きを規制する事により、これら各円筒ころ８として、軸方向端面の中央部に中央平坦面９を設けたものを使用しても、上記各ポケット７の外径側周縁部２２に、前述の図１９に示す凹入部２３に結び付く様な摩耗が生じる事を防止する点にある。その他の部分の構成及び作用は、前述の図１３〜１６に示した従来構造と同様であるから、重複する図示並びに説明は、省略若しくは簡略にし、以下、本実施例の特徴部分を中心に説明する。   1 and 2 show a first embodiment of the present invention corresponding to claim 1. The feature of this embodiment is the relationship with the radial dimension of the chamfered portion 11 formed in the portion near the outer diameter of each axial end surface of each cylindrical roller 8 (the diameter of the central flat surface 9 formed in the central portion). By restricting the movement of each cylindrical roller 8 in a plurality of pockets 7 provided in the radial direction on the intermediate plate portion 6 constituting the cage 2, these cylindrical rollers 8 are centered on the central portion of the axial end surface. Even when a flat surface 9 is used, it is possible to prevent the outer diameter side peripheral edge portion 22 of each pocket 7 from being worn like the concave portion 23 shown in FIG. Since the configuration and operation of the other parts are the same as those of the conventional structure shown in FIGS. 13 to 16 described above, overlapping illustrations and explanations are omitted or simplified, and the following description will focus on the features of this embodiment. To do.

本実施例の場合、図１の（Ａ）に示す様に、上記各円筒ころ８に対し上記保持器２を軸方向一端側（図１の下側）に変位させて、各外径側係止部１８、１８及び各内径側係止部１９、１９と上記各円筒ころ８の転動面１０とを係合させた状態で、これら各円筒ころ８の一部が上記保持器２を構成する外径側、内径側両平板部１４、１５の外面から突出する量△A を、上記各円筒ころ８の径方向に関する面取り部１１の寸法Ｗ11未満（△A ＜Ｗ11）にしている。従って、上記外径側、内径側各係止部１８、１９と上記各円筒ころ８の転動面１０とを係合させた状態では、図１の（Ａ）−（ｂ）に斜格子で示す様に、上記各円筒ころ８の中央平坦面９と上記各ポケット７の外径側周縁部２２との擦れ合い面が、上記保持器２を構成する金属板の板厚の範囲内に収まる。言い換えれば、上記各ポケット７の外径側周縁部２２のうちで、上記各円筒ころ８の自転軸から離れた外径側平板部１４の表面寄り部分には、上記面取り部１１が対向し、これら表面寄り部分と面取り部１１との間に隙間が存在する（擦れ合わない）様にしている。 In the case of this embodiment, as shown in FIG. 1A, the cage 2 is displaced toward one end side in the axial direction (the lower side in FIG. 1) with respect to each cylindrical roller 8, and each outer diameter side member is engaged. A part of each cylindrical roller 8 constitutes the cage 2 in a state in which the stoppers 18 and 18 and the inner diameter side locking portions 19 and 19 are engaged with the rolling surfaces 10 of the cylindrical rollers 8. outer diameter side to the amount △ a protruding from the outer surface of the inner diameter side flat plates part 14, 15 are less than the dimensions W 11 of the chamfer 11 in the radial direction of each cylindrical roller 8 (△ a <W 11) . Accordingly, in a state where the outer diameter side and inner diameter side locking portions 18 and 19 are engaged with the rolling surfaces 10 of the cylindrical rollers 8, a diagonal lattice is shown in FIGS. As shown, the rubbing surface between the central flat surface 9 of each cylindrical roller 8 and the outer peripheral side peripheral edge portion 22 of each pocket 7 falls within the thickness range of the metal plate constituting the cage 2. . In other words, the chamfered portion 11 is opposed to a portion near the surface of the outer diameter side flat plate portion 14 away from the rotation axis of each cylindrical roller 8 in the outer diameter side peripheral edge portion 22 of each pocket 7. A gap exists between these portions close to the surface and the chamfered portion 11 (no rubbing).

更に、本実施例の場合には、図１の（Ｂ）に示す様に、上記各円筒ころ８に対し上記保持器２を軸方向他端側（図１の上側）に変位させて、各中央係止部２０、２０と上記各円筒ころ８の転動面１０とを係合させた状態で、これら各円筒ころ８の一部が上記保持器２を構成する外径側平板部１４の外面から突出する量△B とこれら各円筒ころ８の径方向に関する上記面取り部の寸法Ｗ11との差（Ｗ11−△B ）を、上記保持器２を構成する金属板の板厚Ｔ2 よりも小さく｛（Ｗ11−△B ）＜Ｔ2 ｝している。従って、上記各中央係止部２０、２０と上記各円筒ころ８の転動面１０とを係合させた状態でも、図１の（Ｂ）−（ｂ）に斜格子で示す様に、上記各円筒ころ８の中央平坦面９と上記各ポケット７の外径側周縁部２２とが擦れ合う。言い換えれば、この外径側周縁部２２の内面側端縁と前記面取り部１１とが擦れ合う（エッジ当りする）事はない。 Further, in this embodiment, as shown in FIG. 1B, the cage 2 is displaced to the other end side in the axial direction (upper side in FIG. In a state where the central locking portions 20, 20 are engaged with the rolling surfaces 10 of the cylindrical rollers 8, a part of the cylindrical rollers 8 is part of the outer diameter side flat plate portion 14 constituting the cage 2. the difference between the dimension W 11 of the chamfered portion on the quantity △ B and radial directions of the cylindrical rollers 8 projecting from the outer surface (W 11 - △ B) the plate thickness of the metal plate constituting the cage 2 T 2 Smaller than {(W 11 −Δ B ) <T 2 }. Accordingly, even when the respective central locking portions 20 and 20 and the rolling surfaces 10 of the respective cylindrical rollers 8 are engaged, as shown by the oblique lattices in FIGS. The central flat surface 9 of each cylindrical roller 8 and the outer diameter side peripheral edge portion 22 of each pocket 7 rub against each other. In other words, the inner surface side edge of the outer diameter side peripheral edge portion 22 and the chamfered portion 11 do not rub against each other (contact with the edge).

上記各突出量（最大突出量）△A 、△B を上述の範囲に規制する為に、本実施例の場合には、図２に示す様に、上記各ポケット７毎に互いに対向する、１対の外径側係止部１８、１８同士の間隔Ｄ18（＝１対の内径側係止部１９、１９同士の間隔Ｄ19）と、１対の中央係止部２０、２０同士の間隔Ｄ20を、上記各円筒ころ８の直径Ｄ8 （図１参照）との関係で規制している。 In the case of the present embodiment, in order to restrict each of the protrusion amounts (maximum protrusion amounts) Δ A and Δ B to the above-described range, as shown in FIG. The distance D 18 between the pair of outer diameter side locking portions 18, 18 (= the distance D 19 between the pair of inner diameter side locking portions 19, 19 ) and the distance between the pair of central locking portions 20, 20. D 20 is regulated in relation to the diameter D 8 (see FIG. 1) of each cylindrical roller 8.

本実施例の場合、上述の様な構成により、上記外径側周縁部２２のうちの、各円筒ころ８の自転中心軸から離れた外径側平板部１４の表面（図１の上面）寄り部分と、これら各円筒ころ８の外径側端面２１とが擦れ合わない様にしている。言い換えれば、上記各ポケット７の外径側周縁部２２と、これら各ポケット７内に保持された上記各円筒ころ８の外径側端面２１との擦れ合い部を、図１の（Ａ）−（ｂ）、（Ｂ）−（ｂ）に斜格子で示す様に、上記各ポケット７の円周方向の中央寄り部分に位置させている。この為、スキューによる片当たりを起因として、上記擦れ合い部に局部的な応力集中が発生しにくくなり、更に、この擦れ合い部の滑り速度Ｖを小さく抑えられる。この結果、上記外径側周縁部２２部分に、前述の図１９に示した様な、摩耗による凹入部２３が形成される事を防止できる。又、上記外径側周縁部２２の内面側端縁と上記面取り部１１とがエッジ当りする事がなく、当該部分に著しい摩耗が生じる事がない。   In the case of the present embodiment, due to the configuration as described above, the outer diameter side peripheral edge portion 22 is closer to the surface (upper surface in FIG. 1) of the outer diameter side flat plate portion 14 away from the rotation center axis of each cylindrical roller 8. The portion and the outer diameter side end face 21 of each cylindrical roller 8 are prevented from rubbing. In other words, the rubbing portion between the outer diameter side peripheral edge portion 22 of each pocket 7 and the outer diameter side end surface 21 of each cylindrical roller 8 held in each pocket 7 is shown in FIG. As shown by the oblique lattice in (b), (B)-(b), the pockets 7 are positioned at the central portion in the circumferential direction. For this reason, local stress concentration is less likely to occur in the rubbing portion due to a piece contact due to skew, and the sliding speed V of the rubbing portion can be kept small. As a result, it is possible to prevent the recessed portion 23 due to wear as shown in FIG. 19 from being formed in the outer peripheral side peripheral edge portion 22 portion. Further, the inner edge of the outer peripheral edge 22 and the chamfered portion 11 do not come into contact with each other, and no significant wear occurs in the portion.

更に、本実施例の場合には、上記保持器２の軸方向位置を、上記各ポケット７に形成した前記各係止部１８〜２０と、上記各円筒ころ８の転動面１０との係合により図っているので、上記保持器２の軸方向両側面と相手レース面とが擦れ合う事がない。この為、この保持器２がこのレース面に付着した潤滑油を掻き取る事を防止して、このレース面と上記各円筒ころ８の転動面１０との転がり接触部を良好に潤滑できる。この為、厳しい使用条件の下でも、この転動面１０及び上記各相手レース面の損傷防止を図れる。   Furthermore, in the case of the present embodiment, the axial position of the cage 2 is related to the locking portions 18 to 20 formed in the pockets 7 and the rolling surfaces 10 of the cylindrical rollers 8. Therefore, the both side surfaces in the axial direction of the cage 2 do not rub against each other. For this reason, it is possible to prevent the retainer 2 from scraping off the lubricating oil adhering to the race surface, and to satisfactorily lubricate the rolling contact portion between the race surface and the rolling surface 10 of each cylindrical roller 8. For this reason, it is possible to prevent damage to the rolling surface 10 and the respective race surfaces even under severe use conditions.

次の表１は、本実施例の効果を確認する為に行なった第一の実験の結果を示している。この第一の実験は、スラスト円筒ころ軸受に、動定格荷重の１５％のスラスト荷重を付加した状態で、このスラスト円筒ころ軸受を、許容回転速度の２倍の回転速度で１００時間運転した後、各部の摩耗を観察する事で行なった。使用した潤滑油はＡＴフルードとし、温度は室温とした。

Figure 2006275285
Table 1 below shows the results of a first experiment conducted to confirm the effect of this example. This first experiment was conducted after operating this thrust cylindrical roller bearing for 100 hours at a rotational speed twice the allowable rotational speed with a thrust load of 15% of the dynamic load rating applied to the thrust cylindrical roller bearing. This was done by observing the wear of each part. The lubricating oil used was AT fluid and the temperature was room temperature.
Figure 2006275285

この表１に記載された第一の実験の結果から明らかな通り、本実施例の構造によれば、保持器２に設けた各ポケット７の外径側周縁部２２の摩耗を抑え、この摩耗による、各円筒ころ８の外径側端部が保持器２の外径寄り部分の片面側に潜り込む事を防止し、しかも転がり接触部の潤滑を良好にできる。   As is apparent from the results of the first experiment described in Table 1, according to the structure of the present embodiment, the wear of the outer peripheral side peripheral portion 22 of each pocket 7 provided in the cage 2 is suppressed, and this wear is reduced. Therefore, it is possible to prevent the end portion on the outer diameter side of each cylindrical roller 8 from entering one side of the portion near the outer diameter of the cage 2, and to improve the lubrication of the rolling contact portion.

又、本実施例の様に、上記各ポケット７の外径側周縁部２２と、上記各円筒ころ８の外径側端面２１とを、中央平坦面９部分でのみ摺接させる（この外径側周縁部２２と面取り部１１とを摺接させない）事の効果に就いて解析した結果を、図３により説明する。この図３のうちの（Ａ）は、本実施例の様に、外径側周縁部２２と上記中央平坦面９部分とを摺接させる場合を、同じく（Ｂ）は、この外径側周縁部２２と上記面取り部１１の一部とを摺接させる場合を、それぞれ示している。又、図３の（ａ）は、図１の（ｂ）と同様の図であり、図３の（ｂ）は、上記各円筒ころ８の中心からの距離（横軸）と、各位置でのｑｖ値（荷重ｑと滑り速度ｖとの積）との関係を示すグラフである。尚、スラスト円筒ころ軸受を構成する円筒ころの数は５０とし、４６０Ｎのアキシアル荷重を支承しつつ、１７３００min-1 で回転するとして解析した。 Further, as in this embodiment, the outer peripheral side peripheral portion 22 of each of the pockets 7 and the outer peripheral side end surface 21 of each of the cylindrical rollers 8 are brought into sliding contact only at the central flat surface 9 portion (this outer diameter). The results of analysis on the effect of preventing the side peripheral edge portion 22 and the chamfered portion 11 from sliding contact will be described with reference to FIG. 3A shows a case where the outer diameter side peripheral edge portion 22 and the central flat surface 9 portion are slidably contacted as in the present embodiment. Similarly, FIG. 3B shows the outer diameter side peripheral edge portion. The case where the part 22 and a part of the chamfered part 11 are brought into sliding contact with each other is shown. 3A is a view similar to FIG. 1B, and FIG. 3B shows the distance from the center of each cylindrical roller 8 (horizontal axis) and each position. It is a graph which shows the relationship with qv value (product of the load q and the sliding speed v). The number of cylindrical rollers constituting the thrust cylindrical roller bearing was 50, and it was analyzed that it rotated at 17300 min −1 while supporting an axial load of 460 N.

図３の（Ａ）−（ａ）に示した本実施例の構造の場合には、上記各円筒ころ８の外径側端面２１と上記外径側周縁部２２とは、中央平坦面９の周縁部でのみ比較的強く擦れ合うが、この周縁部でもｑｖは、図３の（Ａ）−（ｂ）に示した様に、限られた値に止まる。この結果、上記外径側周縁部２２に、実用上問題となる様な偏摩耗が生じる事はない。これに対して、図３の（Ｂ）−（ａ）に示した比較例の構造の様に、上記各円筒ころ８の外径側端面２１と上記外径側周縁部２２とが、前記面取り部１１の一部で擦れ合う場合には、これら外径側端面２１と外径側周縁部２２との擦れ合い面積が狭くなって、狭い面積に荷重ｑが集中して加わる状態となる。この結果、図３の（Ｂ）−（ｂ）に示す様に、擦れ合い部のｑｖ値が局部的に高くなり、この擦れ合い部の摩耗が著しくなる（偏摩耗を生じる）。この様な解析結果を示した図３からも、本実施例の構造により、前記保持器２に設けた上記各ポケット７の外径側周縁部２２の摩耗を抑えられる事が分かる。   In the case of the structure of the present embodiment shown in FIGS. 3A to 3A, the outer diameter side end face 21 and the outer diameter side peripheral edge 22 of each cylindrical roller 8 are formed on the central flat surface 9. Although it rubs relatively strongly only at the peripheral portion, qv remains at a limited value at this peripheral portion as shown in FIGS. As a result, uneven wear that causes a problem in practice does not occur in the outer peripheral edge portion 22. On the other hand, like the structure of the comparative example shown in FIGS. 3B to 3A, the outer diameter side end surface 21 and the outer diameter side peripheral edge portion 22 of each cylindrical roller 8 are formed by the chamfering. When rubbing at a part of the portion 11, the rubbing area between the outer diameter side end face 21 and the outer diameter side peripheral edge portion 22 becomes narrow, and the load q is concentrated and applied to the narrow area. As a result, as shown in (B)-(b) of FIG. 3, the qv value of the rubbing portion is locally increased, and wear of the rubbing portion becomes remarkable (deviation wear occurs). FIG. 3 showing such an analysis result also shows that the wear of the outer peripheral side peripheral edge portion 22 of each pocket 7 provided in the cage 2 can be suppressed by the structure of the present embodiment.

図４は、請求項１〜２に対応する、本発明の実施例２を示している。尚、本実施例の特徴も、各円筒ころ８の軸方向両端面外径寄り部分に形成した面取り部１１の径方向寸法（中央部に形成した中央平坦面９の直径）との関係で、保持器２を構成する中間板部６に放射方向に設けた複数のポケット７内での各円筒ころ８の動きを規制する事により、これら各円筒ころ８として、軸方向端面の中央部に中央平坦面９を設けたものを使用しても、上記各ポケット７の外径側周縁部２２に、前述の図１９に示す凹入部２３に結び付く様な摩耗が生じる事を防止する点にある。その他の部分の構成及び作用は、前述の図１３〜１６に示した従来構造と同様であるから、重複する図示並びに説明は、省略若しくは簡略にし、以下、本実施例の特徴部分を中心に説明する。   FIG. 4 shows a second embodiment of the present invention corresponding to claims 1 and 2. The feature of the present embodiment is also related to the radial dimension of the chamfered portion 11 formed on the portion near the outer diameter of each axial end surface of each cylindrical roller 8 (diameter of the central flat surface 9 formed in the central portion). By restricting the movement of each cylindrical roller 8 in a plurality of pockets 7 provided in the radial direction on the intermediate plate portion 6 constituting the cage 2, these cylindrical rollers 8 are centered on the central portion of the axial end surface. Even when a flat surface 9 is used, it is possible to prevent the outer diameter side peripheral edge portion 22 of each pocket 7 from being worn like the concave portion 23 shown in FIG. Since the configuration and operation of the other parts are the same as those of the conventional structure shown in FIGS. 13 to 16 described above, overlapping illustrations and explanations are omitted or simplified, and the following description will focus on the features of this embodiment. To do.

本実施例の場合には、図４の（Ａ）に示す様に、上記円筒ころ８に対し上記保持器２を軸方向一端側｛図４の（Ａ）の下側｝に変位させて、各外径側係止部１８、１８及び各内径側係止部１９、１９と上記各円筒ころ８の転動面１０とを係合させた状態で、これら各円筒ころ８の軸方向端面に設けた中央平坦面９と上記各ポケット７の外径側周縁部２２とが、図４の（Ａ）に斜格子で示した擦れ合い面２４で摺接する。本実施例の場合には、この擦れ合い面２４の上記保持器２の円周方向に関する長さＬ24を、上記各円筒ころ８の直径Ｄ8 の８０％以内（Ｌ24≦０．８Ｄ8 ）に、好ましくは４０〜７０％の範囲内｛Ｌ24＝（０．４〜０．７）Ｄ8 ｝に規制している。上記擦れ合い面２４の長さＬ24をこの範囲に規制する為の具体的構造は、前述の実施例１の場合と同様である。そして、本実施例の場合も、この実施例１の場合と同様に、上記外径側周縁部２２に、上記円筒ころ８の潜り込みに繋がる様な摩耗が発生する事を防止できる。 In the case of the present embodiment, as shown in FIG. 4A, the cage 2 is displaced to one end side in the axial direction {lower side of FIG. 4A) relative to the cylindrical roller 8; In a state where the outer diameter side locking portions 18 and 18 and the inner diameter side locking portions 19 and 19 are engaged with the rolling surfaces 10 of the cylindrical rollers 8, the axial end surfaces of the cylindrical rollers 8 are engaged. The provided central flat surface 9 and the outer peripheral side peripheral edge portion 22 of each of the pockets 7 are in sliding contact with a rubbing surface 24 shown by an oblique lattice in FIG. In the case of this embodiment, the length L 24 of the rubbing surface 24 in the circumferential direction of the cage 2 is within 80% of the diameter D 8 of each cylindrical roller 8 (L 24 ≦ 0.8D 8 ), Preferably within the range of 40 to 70% {L 24 = (0.4 to 0.7) D 8 }. Specific structure for regulating the length L 24 of the rubbing surface 24 in this range is the same as in Example 1 above. Also in the case of the present embodiment, similarly to the case of the first embodiment, it is possible to prevent the outer diameter side peripheral edge portion 22 from being worn to cause the cylindrical roller 8 to sink.

図５〜７は、請求項１〜３に対応する、本発明の実施例３を示している。尚、本実施例の特徴は、保持器２を構成する中間板部６に放射方向に設けた複数のポケット７内での各円筒ころ８ｂの動きとの関係で、これら各円筒ころ８ｂの軸方向両端面の外径寄り部分に形成した面取り部１１ａ、１１ａの形状及び寸法を規制する事により、これら各円筒ころ８ｂとして、軸方向端面の中央部に中央平坦面９ａを設けたものを使用しても、上記各ポケット７の外径側周縁部２２に、前述の図１９に示す凹入部２３に結び付く様な摩耗が生じる事を防止する点にある。その他の部分の構成及び作用は、前述の図１３〜１６に示した従来構造と同様であるから、重複する図示並びに説明は、省略若しくは簡略にし、以下、本実施例の特徴部分を中心に説明する。   FIGS. 5-7 has shown Example 3 of this invention corresponding to Claims 1-3. The feature of this embodiment is the relationship between the movement of each cylindrical roller 8b in a plurality of pockets 7 provided in the radial direction on the intermediate plate portion 6 constituting the cage 2, and the axis of each cylindrical roller 8b. By restricting the shape and dimensions of the chamfered portions 11a, 11a formed on the outer diameter portions of the both end surfaces in the direction, the cylindrical roller 8b having a central flat surface 9a at the center of the axial end surface is used. Even so, it is to prevent the outer peripheral side peripheral portion 22 of each pocket 7 from being worn like the concave portion 23 shown in FIG. Since the configuration and operation of the other parts are the same as those of the conventional structure shown in FIGS. 13 to 16 described above, overlapping illustrations and explanations are omitted or simplified, and the following description will focus on the features of this embodiment. To do.

本実施例の場合、上記各円筒ころ８ｂは、それぞれの軸方向両端面の外径寄り部分に形成した面取り部１１ａ、１１ａの寸法のうち、上記各円筒ころ８ｂの軸方向の寸法Ｌ11a よりも径方向の寸法Ｗ11a を大きく（Ｌ11a ＜Ｗ11a ）している。従って、本実施例に組み込む上記各円筒ころ８ｂの軸方向両端面中央部に形成した中央平坦面９ａの直径Ｄ9aは、前述した従来構造に組み込む各円筒ころ８の軸方向両端面中央部に形成した中央平坦面９の直径Ｄ9 （図１４参照）よりも小さい（Ｄ9a＜Ｄ9 ）。言い換えれば、本実施例の場合、上記中央平坦面９ａと上記両面取り部１１ａ、１１ａとの境界部が、従来構造の場合の境界部よりも、上記各円筒ころ８ｂの（自転）中心軸寄り部分に存在する。尚、上記径方向の寸法Ｗ11a を上記軸方向の寸法Ｌ11a よりも大きくする程度は、１．１〜２倍程度｛Ｗ11a ＝（１．１〜２）Ｌ11a ｝が好ましい。 In the case of the present embodiment, each cylindrical roller 8b has a dimension L 11a in the axial direction of each cylindrical roller 8b among the dimensions of the chamfered portions 11a and 11a formed in the portions near the outer diameter of both axial end faces. Also, the radial dimension W 11a is increased (L 11a <W 11a ). Therefore, the diameter D 9a of the center flat surface 9a formed at the center of both end surfaces in the axial direction of each cylindrical roller 8b incorporated in the present embodiment is the center of each end surface in the axial direction of each cylindrical roller 8 incorporated in the conventional structure described above. It is smaller than the diameter D 9 (see FIG. 14) of the formed central flat surface 9 (D 9a <D 9 ). In other words, in the case of the present embodiment, the boundary between the central flat surface 9a and the double-sided chamfers 11a and 11a is closer to the (rotation) center axis of each cylindrical roller 8b than the boundary in the case of the conventional structure. Exists in the part. It should be noted that the degree of making the radial dimension W 11a larger than the axial dimension L 11a is preferably about 1.1 to 2 times {W 11a = (1.1 to 2) L 11a }.

本実施例の場合、上記両面取り部１１ａ、１１ａの寸法を上述の様に規制する事により、上記各円筒ころ８ｂの転動面１０の軸方向長さＬ10（＝各円筒ころ８ｂの有効長さ）を確保しつつ、これら各円筒ころ８ｂの外径側端面２１ｂと上記各ポケット７の外径側周縁部２２との擦れ合い部の摩耗を抑え、前述した実施例１の場合と同様に、上記外径側周縁部２２に、上記円筒ころ８ｂの潜り込みに繋がる様な摩耗が発生する事を防止できる。 In this embodiment, by regulating the double-sided chamfer 11a, the dimensions of 11a as described above, the effective axial length L 10 (= the cylindrical roller 8b of the rolling surface 10 of each cylindrical roller 8b The length of the cylindrical roller 8b and the outer diameter side end face 21b of each cylindrical roller 8b and the outer diameter side peripheral edge portion 22 of each of the pockets 7 are prevented from being worn and the same as in the case of the first embodiment described above. In addition, it is possible to prevent the outer diameter side peripheral edge portion 22 from being worn such that the cylindrical roller 8b is submerged.

又、本実施例の場合には、上記各円筒ころ８ｂとして、軸方向両端面に、これら各円筒ころ８ｂの回転中心軸に対し直角方向に拡がる中央平坦面９ａを備え、この中央平坦面９ａと転動面１０とを、前述した様な寸法Ｌ11a 、Ｗ11a を有する面取り部１１ａにより連続させたものを使用する。この為、上記転動面１０の軸方向長さＬ10（＝各円筒ころ８ｂの有効長さ）を大きくして、これら各円筒ころ８ｂを組み込んだスラスト円筒ころ軸受の負荷容量の確保を図る設計が容易になる。 In the case of this embodiment, each cylindrical roller 8b is provided with a central flat surface 9a extending in a direction perpendicular to the rotation center axis of each cylindrical roller 8b on each axial end surface, and this central flat surface 9a. The rolling surface 10 is made continuous by the chamfered portion 11a having the dimensions L 11a and W 11a as described above. For this reason, the axial length L 10 of the rolling surface 10 (= the effective length of each cylindrical roller 8b) is increased to ensure the load capacity of the thrust cylindrical roller bearing in which each cylindrical roller 8b is incorporated. Design becomes easy.

請求項４に記載した発明に就いて、図８を参照しつつ説明する。先に説明した請求項１〜３に記載した発明を実施する場合に好ましくは、各ポケット７内での各円筒ころ８の、保持器２の軸方向に関する変位量を、或る程度確保する。この変位量を規制する為に、図８に記載した２通りの状態を考える。このうち、図８の左側に示した状態は、上記保持器２を軸方向一端側に変位させて、各外径側係止部１８及び各内径側係止部１９と各円筒ころ８の転動面１０とを係合させた状態である。この状態での、これら各円筒ころ８の一部が上記保持器２を構成する外径側、内径側両平板部１４、１５の外面から突出する量を、△max とする。これに対して、図８の右側に示した状態は、上記保持器２を軸方向他端側に変位させて、各中央係止部２０と上記各円筒ころ８の転動面１０とを係合させた状態である。この状態での、これら各円筒ころ８の一部が上記外径側、内径側両平板部１４、１５の外面から突出する量を、△min とする。そして、これら両突出量△max 、△min 同士の差（△max −△min ）、即ち、上記各円筒ころ８に対する上記保持器２の軸方向に関するガタ量を、５０μｍ以上とする。 The invention described in claim 4 will be described with reference to FIG. Preferably, when carrying out the invention described in claims 1 to 3 described above, a certain amount of displacement of each cylindrical roller 8 in each pocket 7 in the axial direction of the cage 2 is secured. In order to regulate the amount of displacement, consider the two states shown in FIG. Among these, the state shown on the left side of FIG. 8 is that the cage 2 is displaced toward one end in the axial direction, and the outer diameter side locking portions 18 and the inner diameter side locking portions 19 and the cylindrical rollers 8 are rotated. In this state, the moving surface 10 is engaged. In this state, an amount in which a part of each of the cylindrical rollers 8 protrudes from the outer surfaces of both the outer diameter side and inner diameter side flat plate portions 14 and 15 constituting the cage 2 is defined as Δmax . On the other hand, in the state shown on the right side of FIG. 8, the cage 2 is displaced to the other end side in the axial direction, and the central locking portions 20 and the rolling surfaces 10 of the cylindrical rollers 8 are engaged. It is a combined state. In this state, the amount of part of each of these cylindrical roller 8 projects from the outer surface of the outer diameter side, the inner diameter side flat plates 14, 15, and △ min. The difference between the two protrusion amounts Δ max and Δ min (Δ max −Δ min ), that is, the backlash amount in the axial direction of the cage 2 with respect to the cylindrical rollers 8 is set to 50 μm or more.

先に述べた実施例１〜３の様に、上記保持器２の軸方向に関する位置決めをころ案内で図る為の条件を満たしつつ、上記ガタ量を５０μｍ以上確保すれば、上記各円筒ころ８の転動面１０と上記保持器２を構成する各柱部１２の円周方向両側縁との隙間を十分に確保できる。この為、上記各円筒ころ８の転動面１０に付着した潤滑油がこれら各柱部１２の円周方向両側縁により掻き取られる事を防止して、上記各円筒ころ８の転動面１０と相手レース面との転がり接触部に十分な潤滑油を供給できる。そして、これら各転がり接触部に十分な油膜を形成して、上記各円筒ころ８の転動面１０及び相手レース面の転がり疲れ寿命の確保を図れる。   As in the first to third embodiments described above, if the backlash amount is secured to 50 μm or more while satisfying the conditions for positioning the cage 2 in the axial direction with roller guides, A sufficient gap can be ensured between the rolling surface 10 and both side edges in the circumferential direction of each column portion 12 constituting the cage 2. For this reason, it is prevented that the lubricating oil adhering to the rolling surface 10 of each said cylindrical roller 8 is scraped off by the circumferential both-sides edge of each said column part 12, and the rolling surface 10 of each said cylindrical roller 8 is prevented. And sufficient lubricating oil can be supplied to the rolling contact portion between the race surface and the opponent. And sufficient oil film can be formed in each of these rolling contact parts, and the rolling fatigue life of the rolling surface 10 of each said cylindrical roller 8 and the other race surface can be ensured.

請求項６に記載した発明に就いて、図９〜１２を参照しつつ説明する。本実施例は、前述の実施例１で規制した、図１の（Ａ）−（ｂ）に示した突出量（最大突出量）△A を、各ポケット７の外径側周縁部２２に存在する剪断面２５と破断面２６との寸法との関係で、上記実施例１の場合よりも更に厳密に規制する事により、各部の摩耗をより一層低減できる様にするものである。 The invention described in claim 6 will be described with reference to FIGS. This example was regulated in Example 1 above, in Fig. 1 (A) - the presence of (b) projection amount shown in (maximum protrusion amount) △ A, the outer diameter side peripheral edge 22 of each pocket 7 By further strictly regulating the relationship between the size of the shearing surface 25 and the fracture surface 26 as compared with the case of the first embodiment, the wear of each part can be further reduced.

本発明のスラスト円筒ころ軸受に組み込む保持器２は、金属板にプレス加工を施して造る事が、この保持器２の製造コストを抑える面からは好ましい。この場合に上記各ポケット７は、上記金属板に、プレスによる打ち抜き加工を施す事により形成する。この打ち抜き加工は、プレス加工の技術分野で広く知られている如く、図１１に示す様に、上記各ポケット７に見合う形状及び大きさの端面形状を有するパンチ２７により金属板２８の一部を、受型２９に設けた受孔３０内に押し込む事により行なう。この様な打ち抜き加工に伴って、上記金属板２８の一部で上記パンチ２７の外周縁と上記受孔３０の内周縁とに挟まれる部分に剪断力が加わり、このパンチ２７の先端面が突き当てられた部分が打ち抜かれる。   The cage 2 incorporated in the thrust cylindrical roller bearing of the present invention is preferably manufactured by pressing a metal plate from the viewpoint of reducing the manufacturing cost of the cage 2. In this case, the pockets 7 are formed by punching the metal plate with a press. As is widely known in the technical field of press working, as shown in FIG. 11, this punching process is performed by cutting a portion of the metal plate 28 with a punch 27 having an end face shape corresponding to each of the pockets 7. This is done by pushing into a receiving hole 30 provided in the receiving die 29. With such a punching process, a shearing force is applied to a portion of the metal plate 28 sandwiched between the outer peripheral edge of the punch 27 and the inner peripheral edge of the receiving hole 30, and the front end surface of the punch 27 protrudes. The applied part is punched out.

この様な打ち抜き加工の初期段階では、上記金属板２８の一部で上記各ポケット７の内周縁に対応する部分に剪断面２５が生じ、上記パンチ２７が或る程度進行すると、このパンチ２７の先端面外周縁に対応する部分が一気に破断する。この状態で、上記各ポケット７の内周縁に対応する部分に破断面２６が生じる。尚、上記打ち抜き加工の極く初期段階では、上記金属板２８の一部にダレが生じる。従って、打ち抜き加工後に於ける上記各ポケット７の内周縁には、図１２に示す様に、上記パンチ２７の入口側から順番に、ダレ３１と、剪断面２５と、破断面２６とが生じる。何れにしても、上記保持器２の製造コストを抑える為には、この様に加工された上記各ポケット７の内周縁に、表面粗さを向上させる（平滑にする）為の仕上加工を施す事は好ましくない。   In such an initial stage of punching, a shearing surface 25 is formed in a part of the metal plate 28 corresponding to the inner peripheral edge of each pocket 7, and when the punch 27 advances to some extent, A portion corresponding to the outer peripheral edge of the tip surface is broken at a stroke. In this state, a fracture surface 26 is generated at a portion corresponding to the inner peripheral edge of each pocket 7. In the very initial stage of the punching process, sagging occurs in a part of the metal plate 28. Accordingly, as shown in FIG. 12, a sag 31, a shearing surface 25, and a fracture surface 26 are formed on the inner peripheral edge of each pocket 7 after punching in order from the inlet side of the punch 27. In any case, in order to reduce the manufacturing cost of the cage 2, finishing processing for improving (smoothing) the surface roughness is performed on the inner peripheral edge of each pocket 7 processed in this way. Things are not good.

一方、剪断面の表面粗さの値と破断面の表面粗さの値とを比較した場合、剪断面の表面粗さの値の方が小さい（平滑面に近く、擦れ合い面として良好である）。従って、上記各ポケット７の外径側周縁部２２と各円筒ころ８の外径側端面２１との擦れ合い部の摩耗を抑える為には、これら各円筒ころ８の外径側端面２１を、上記各ポケット７の外径側周縁部２２のうちで剪断面２５部分に当接させる事が好ましい。そこで本実施例の場合には、上記打ち抜き加工時に於ける上記パンチ２７の打ち抜き方向を規制すると共に、上記各円筒ころ８の一部が上記保持器２を構成する外径側平板部１４の外面から突出する量と、これら各円筒ころ８の径方向に関する前記面取り部１１の寸法との差を、上記破断面２６の幅との関係で規制している。   On the other hand, when comparing the surface roughness value of the sheared surface and the surface roughness value of the fractured surface, the surface roughness value of the sheared surface is smaller (close to a smooth surface and better as a rubbing surface. ). Therefore, in order to suppress wear of the rubbing portion between the outer peripheral side peripheral portion 22 of each pocket 7 and the outer diameter side end surface 21 of each cylindrical roller 8, the outer diameter side end surface 21 of each cylindrical roller 8 is It is preferable that the outer peripheral side edge 22 of each pocket 7 is brought into contact with the shearing surface 25 portion. Therefore, in the case of this embodiment, the punching direction of the punch 27 at the time of the punching process is restricted, and a part of each cylindrical roller 8 is an outer surface of the outer diameter side flat plate portion 14 constituting the cage 2. The difference between the amount of protrusion and the dimension of the chamfered portion 11 in the radial direction of each cylindrical roller 8 is restricted in relation to the width of the fracture surface 26.

具体的には、上記打ち抜き加工を、パンチ２７を外径側、内径側両平板部１４、１５の内面側から外面側に、図１０の下から上に突き通す事により行なう。そして、上記外径側周縁部２２を含む、上記各ポケット７の内周縁のうちの、上記外径側、内径側両平板部１４、１５の内面側（図９、１０の下面側）に上記打ち抜き加工に伴う剪断面２５を、同じく外側面側（図９、１０の上面側）に破断面２６を、それぞれ存在させる。   Specifically, the punching process is performed by penetrating the punch 27 from the inner surface side to the outer surface side of both the outer diameter side and inner diameter side flat plate portions 14 and 15 from the bottom to the top of FIG. And the inner diameter side (the lower surface side in FIGS. 9 and 10) of the outer diameter side and inner diameter side flat plate portions 14, 15 of the inner peripheral edge of each pocket 7 including the outer diameter side peripheral edge portion 22. Similarly, the fracture surface 26 is present on the outer surface side (upper surface side in FIGS. 9 and 10) of the shearing surface 25 associated with the punching process.

更に、上記各ポケット７内での上記各円筒ころ８の変位量、特に、上記外径側、内径側両平板部１４、１５の外面からの突出量の最大値｛図９の（Ｂ）−（ｂ）に示した様に、上記各円筒ころ８がこれら両平板部１４、１５側に変位し切った状態での突出量｝△max を、前述の実施例１の場合よりも小さく規制している。又、上記各円筒ころ８の上記外径側、内径側両平板部１４、１５の外面からの突出量の最小値｛図９の（Ａ）−（ｂ）に示した様に、上記各円筒ころ８が中央平板部１３側に変位し切った状態での突出量｝△min を、上記実施例１の場合と同様に規制している。 Furthermore, the maximum amount of displacement of each cylindrical roller 8 in each pocket 7, in particular, the amount of protrusion from the outer surfaces of both the outer diameter side and inner diameter side flat plate portions 14, 15 {(B) − of FIG. As shown in (b), the amount of projection} Δmax in a state where the cylindrical rollers 8 are fully displaced toward the flat plate portions 14 and 15 is restricted to be smaller than that in the case of the first embodiment. ing. Further, the minimum value of the protruding amount from the outer surface of the outer diameter side and inner diameter side flat plate portions 14 and 15 of each cylindrical roller 8 {as shown in FIGS. 9A to 9B, the amount of protrusion} △ min in a state in which the rollers 8 is fully displaced in the central flat portion 13 side, and regulates the same manner as in example 1.

先ず、上記最大値△max の規制に就いて、図９の（Ｂ）により説明する。この最大値△max は、上記保持器２を構成する金属板２８の厚さ方向に関する上記破断面２６の幅Ｗ26と、上記外径側端面２１に存在する面取り部１１の、上記各円筒ころ８の径方向に関する幅Ｗ11との関係で規制する。即ち、上記破断面２６の幅Ｗ26と上記最大値△max との和（Ｗ26＋△max ）を、上記面取り部１１の幅Ｗ11未満｛（Ｗ26＋△max ）＜Ｗ11、（Ｗ26＋△max ）／Ｗ11＜１｝としている。この様な規制により、上記各ポケット７内での上記各円筒ころ８の変位に拘らず、これら各円筒ころ８の外径側端面２１に設けた中央平坦面９が、上記破断面２６と接触しない様にしている。 First, the restriction on the maximum value Δmax will be described with reference to FIG. The maximum value △ max has a width W 26 of the cage 2 above broken surface 26 about the thickness direction of the metal plate 28 constituting a chamfered portion 11 that exists in the outside diameter side end face 21, each cylindrical roller 8 is regulated in relation to the width W 11 in the radial direction. That is, the sum of the width W 26 and the maximum value △ max of the fracture surface 26 (W 26 + △ max), the width W 11 less than {(W 26 + △ max) <W 11 of the chamfer 11, ( W 26 + Δmax ) / W 11 <1}. Due to such regulation, the central flat surface 9 provided on the outer diameter side end surface 21 of each cylindrical roller 8 is in contact with the fracture surface 26 regardless of the displacement of the cylindrical roller 8 in the pocket 7. I try not to.

次に、上記最小値△min の規制に就いて、図９の（Ａ）により説明する。この最小値△min の規制に就いては、前述の実施例１の場合｛図１の（Ｂ）−（ｂ）の△B の場合｝と同様である。即ち、上記面取り部１１の径方向に関する幅寸法Ｗ11と上記最小値△min との差（Ｗ11−△min ）を、上記保持器２を構成する金属板の板厚Ｔ2 よりも小さく｛（Ｗ11−△min ）＜Ｔ2 、（Ｗ11−△min ）／Ｔ2 ＜１｝している。従って、上記各円筒ころ８が上記中央平板部１３側に変位し切った状態でも、図９の（Ａ）−（ｂ）に斜格子で示す様に、上記各円筒ころ８の中央平坦面９と上記各ポケット７の外径側周縁部２２（のうちの上記剪断面２５）とが擦れ合う。言い換えれば、この外径側周縁部２２の内面側端縁と上記面取り部１１とが擦れ合う（エッジ当りする）事はない。 Next, concerning the regulation of the minimum value △ min, illustrated by (A) in FIG. For the regulation of the minimum value △ min, in Example 1 described above - is the same as {shown in FIG. 1 (B) For △ B of (b)}. That is, the difference between the width dimension in the radial direction W 11 and the minimum value △ min of the chamfered portion 11 - a (W 11 △ min), less than the thickness T 2 of the metal plate constituting the cage 2 { (W 11 −Δmin ) <T 2 , (W 11 −Δmin ) / T 2 <1}. Accordingly, even when the cylindrical rollers 8 are completely displaced toward the central flat plate portion 13 side, the central flat surface 9 of the cylindrical rollers 8 is shown in FIG. 9 (A)-(b) as a diagonal lattice. And the outer peripheral side peripheral edge portion 22 (the shear surface 25 of them) rub against each other. In other words, the inner surface side edge of the outer diameter side peripheral edge portion 22 and the chamfered portion 11 do not rub against each other (contact with the edge).

本実施例の場合には、上述の様な構成を採用する事により、低コストで造れる構成で、前述の実施例１により得られる効果に加えて、上記各円筒ころ８の軸方向端面に存在する中央平坦面９と、上記破断面２６とが擦れ合う事を防止して、より一層の耐久性向上を図れる。即ち、前記突出量の最大値△max を、上記破断面２６の幅Ｗ26と上記面取り部１１の幅Ｗ11との関係で前述の様に規制している為、上記中央平坦面９と、表面粗さの値が大きい（粗い）上記破断面２６とが擦れ合う事を防止できる。言い換えれば、上記中央平坦面９を、表面粗さの値が小さい（比較的滑らかな）前記剪断面２５と摺接させて、擦れ合い部の摩擦を低減できる。従って、前述した様に、上記各ポケット７の内周縁に、製造コストの上昇に結び付く様な仕上加工を行なわなくても、スラスト円筒ころ軸受の耐久性向上を図れる。 In the case of the present embodiment, by adopting the above-described configuration, it can be manufactured at a low cost, and in addition to the effect obtained by the above-described first embodiment, it exists on the end surface in the axial direction of each cylindrical roller 8. This prevents the center flat surface 9 and the fracture surface 26 from rubbing against each other, thereby further improving the durability. That is, the maximum value △ max of the protrusion amount, because of the restriction as described above with respect to the width W 11 of width W 26 and the chamfered portion 11 of the fracture surface 26, and the central flat surface 9, It is possible to prevent the fracture surface 26 having a large (rough) surface roughness value from being rubbed. In other words, the center flat surface 9 can be brought into sliding contact with the shearing surface 25 having a small surface roughness value (relatively smooth) to reduce friction of the rubbing portion. Therefore, as described above, it is possible to improve the durability of the thrust cylindrical roller bearing without performing a finishing process on the inner peripheral edge of each pocket 7 so as to increase the manufacturing cost.

次の表２は、本実施例の効果を確認する為に行なった、第二の実験の結果を示している。この第二の実験には、内径が５０mm、外径が７０mm、厚さが０．５mmの保持器を組み込んだスラスト円筒ころ軸受を、スラスト荷重を付加しない状態で、許容回転速度の２倍の回転速度（１２０００min-1 ）で５０時間運転した。その後、上記スラスト円筒ころ軸受を分解し、上記各ポケット７の外径側周縁部２２のうちで、最も摩耗が進んだ部分の摩耗深さを測定した。使用した潤滑油はＡＴフルードとし、温度は室温とした。又、各円筒ころ８の外径側端面２１の表面粗さは０．３５〜０．４μｍＲａとした。又、外径側周縁部２２を含め、各ポケット７の周縁部の表面粗さは、剪断面２５部分に関しては０．１５〜０．５μｍＲａとし、破断面２６部分に関しては１．０〜２．５μｍＲａとした。粗さに幅があるのは、試料毎に面に差が生じる為であり、意識的に差をつけたものではない。又、剪断面２５の表面粗さの値は、素材となる金属板（アンコイラから引き出したコイル材）の表面粗さの値とほぼ同じ値である。 Table 2 below shows the results of a second experiment conducted to confirm the effect of this example. In this second experiment, a thrust cylindrical roller bearing incorporating a cage with an inner diameter of 50 mm, an outer diameter of 70 mm, and a thickness of 0.5 mm was doubled the allowable rotational speed without applying a thrust load. It was operated for 50 hours at a rotation speed (12000 min −1 ). Thereafter, the thrust cylindrical roller bearing was disassembled, and the wear depth of the most worn portion of the outer diameter side peripheral edge portion 22 of each pocket 7 was measured. The lubricating oil used was AT fluid and the temperature was room temperature. Moreover, the surface roughness of the outer diameter side end face 21 of each cylindrical roller 8 was 0.35 to 0.4 μmRa. Moreover, the surface roughness of the peripheral part of each pocket 7 including the outer peripheral side peripheral part 22 shall be 0.15-0.5 micrometer Ra regarding the shearing surface 25 part, and 1.0-2. The thickness was 5 μm Ra. The reason why the roughness is wide is that there is a difference in the surface for each sample, and it is not a conscious difference. Further, the value of the surface roughness of the shearing surface 25 is substantially the same as the value of the surface roughness of the metal plate (coil material drawn out from the uncoiler) as the material.

Figure 2006275285
この表２にその結果を示した実験から明らかな通り｛特に、（Ｗ26＋△max ）／Ｗ11＞１である左半分と、（Ｗ26＋△max ）／Ｗ11＜１である右半分との間で比較すれば分かる様に｝、本実施例の構造によれば、各円筒ころ８の外径側端面２１と、各ポケット７の外径側周縁部２２との擦れ合い部の摩擦環境を改善して、この擦れ合い部の摩耗を低減できる。尚、この擦れ合い部を構成する各面の表面粗さは、上記外径側端面２１に関しては０．３μｍＲａ以下とし、上記剪断面２５部分に関しては０．５μｍＲａ以下とし、破断面２６部分に関しても２．５μｍＲａとする事が、コスト上昇を抑えつつ各擦れ合い部の摩耗を抑える面からは好ましい。尚、本例の構造を実施する限り、上記破断面２６は上記各円筒ころ８の外径側端面２１とは擦れ合わない。但し、（接触荷重は小さいが）転動面１０と擦れ合う事がある為、表面粗さをできる限り良好な値に抑える事が好ましい。
Figure 2006275285
 As is apparent from the experiment showing the result in Table 2, {particularly, the left half where (W 26 + Δ max ) / W 11 > 1 and the right half where (W 26 + Δ max ) / W 11 <1 As can be seen from a comparison between the halves}, according to the structure of the present embodiment, the frictional portion between the outer diameter side end face 21 of each cylindrical roller 8 and the outer diameter side peripheral edge portion 22 of each pocket 7 is obtained. The friction environment can be improved and the wear of the rubbing portion can be reduced. The surface roughness of each surface constituting the rubbing portion is 0.3 μmRa or less for the outer diameter side end surface 21, 0.5 μmRa or less for the shearing surface 25 portion, and the fracture surface 26 portion also. A thickness of 2.5 μmRa is preferable from the viewpoint of suppressing wear of each rubbing portion while suppressing an increase in cost. As long as the structure of this example is implemented, the fracture surface 26 does not rub against the outer diameter side end face 21 of each cylindrical roller 8. However, since it may rub against the rolling surface 10 (although the contact load is small), it is preferable to keep the surface roughness as good as possible.

本発明の実施例１を説明する為、円筒ころに対し保持器を（Ａ）に示した軸方向一端側と（Ｂ）に示した軸方向他端側とに変位させた状態を示す図で、それぞれの（ａ）は、スラスト円筒ころ軸受を保持器の中心軸を含む仮想平面で切断した状態で示す部分断面図、それぞれの（ｂ）は（ａ）のイ−イ断面図。In order to demonstrate Example 1 of the present invention, it is a figure showing the state where the cage was displaced to the one axial end side shown in (A) and the other axial end side shown in (B) with respect to the cylindrical roller. Each (a) is a partial cross-sectional view showing a thrust cylindrical roller bearing cut in a virtual plane including the central axis of the cage, and each (b) is a cross-sectional view taken along the line (a). 保持器のポケットの形状を示す為に、このポケットを保持器の軸方向から見た状態で示す図。The figure which shows this pocket in the state seen from the axial direction of the holder | retainer in order to show the shape of the pocket of a holder | retainer. 実施例１の効果を確認する為に行なった解析の結果を示す、模式図及びグラフ。The schematic diagram and graph which show the result of the analysis performed in order to confirm the effect of Example 1. FIG. 本発明の実施例２を説明する為の、円筒ころの外径側端面とポケットの外径側周縁部との摩擦状態とポケットの外径側周縁部の摩耗状態とを示す、図７と同様の図。7 illustrates the friction state between the outer diameter side end surface of the cylindrical roller and the outer diameter side peripheral edge portion of the pocket and the wear state of the outer diameter side peripheral edge portion of the pocket for explaining the second embodiment of the present invention. Illustration. 本発明の実施例３に組み込む円筒ころの側面図。The side view of the cylindrical roller integrated in Example 3 of this invention. この円筒ころを保持器に組み込んで成るスラスト円筒ころ軸受の実施例３を、保持器の中心軸を含む仮想平面で切断した状態で示す部分断面図。The fragmentary sectional view which shows Example 3 of the thrust cylindrical roller bearing which incorporates this cylindrical roller in a holder | retainer in the state cut | disconnected by the virtual plane containing the central axis of a holder | retainer. 実施例３での円筒ころの外径側端面とポケットの外径側周縁部との摩擦状態とポケットの外径側周縁部の摩耗状態とを示しており、（Ａ）は図６のロ−ロ断面図、（Ｂ）はポケットを（Ａ）の下方から見た図。The frictional state between the outer diameter side end face of the cylindrical roller and the outer diameter side peripheral edge portion of the pocket and the worn state of the outer diameter side peripheral edge portion of the pocket in Example 3 are shown. FIG. (B) is a view of the pocket as viewed from below (A). 円筒ころに対する保持器の好ましい軸方向変位量に就いて説明する為に、この保持器を軸方向両端部に移動させると共に、スラスト円筒ころ軸受を保持器の中心軸を含む仮想平面で切断した状態で示す部分断面図。In order to explain the preferable axial displacement of the cage with respect to the cylindrical roller, the cage is moved to both axial ends, and the thrust cylindrical roller bearing is cut along a virtual plane including the central axis of the cage. FIG. 実施例５を説明する為、保持器に対し円筒ころを（Ａ）に示した外径側、内径側両平板部側に変位させた状態と、（Ｂ）に示した中央平板部側に変位させた状態とを示す図で、それぞれの（ａ）は、スラスト円筒ころ軸受を保持器の中心軸を含む仮想平面で切断した状態で示す部分断面図、それぞれの（ｂ）は（ａ）のハ−ハ断面図。In order to explain the fifth embodiment, the cylindrical roller is displaced with respect to the cage to the outer diameter side and inner diameter side both flat plate side shown in (A), and to the central flat plate side shown in (B). FIG. 4A is a partial cross-sectional view showing a state in which each thrust cylindrical roller bearing is cut along a virtual plane including the central axis of the cage, and each FIG. FIG. ポケットの内周縁に存在する剪断面と破断面とを説明する為の図で、（Ａ）は保持器の中心軸を含む仮想平面に関する断面図、（Ｂ）は外径側周縁部を示す、（Ａ）のニ矢視図。It is a figure for demonstrating the shearing surface and fracture surface which exist in the inner periphery of a pocket, (A) is sectional drawing regarding the virtual plane containing the central axis of a holder, (B) shows an outer diameter side peripheral part, FIG. ポケットを打ち抜く状態を示す、部分拡大断面図。The partial expanded sectional view which shows the state which punches a pocket. 打ち抜かれた部分を示す図で、（Ａ）は図１１の拡大ホ矢視図、（Ｂ）は（Ａ）のヘ−ヘ断面図。It is a figure which shows the punched-out part, (A) is an enlarged arrow view of FIG. 11, (B) is a cross-sectional view of (A). 従来構造の１例を示す、保持器の断面図。Sectional drawing of a holder | retainer which shows an example of a conventional structure. 円筒ころを取り出して示す側面図。The side view which takes out and shows a cylindrical roller. 円筒ころに対し保持器を、（Ａ）に示した軸方向一端側と（Ｂ）に示した軸方向他端側とに変位させ、スラスト円筒ころ軸受を保持器の中心軸を含む仮想平面で切断した状態で示す部分断面図。The cage is displaced to one end side in the axial direction shown in (A) and the other end side in the axial direction shown in (B) with respect to the cylindrical roller, and the thrust cylindrical roller bearing is moved in a virtual plane including the central axis of the cage. The fragmentary sectional view shown in the cut | disconnected state. 保持器のポケットの形状を示す為に、このポケットを保持器の中心軸方向から見た状態で示す図。The figure which shows this pocket in the state seen from the central-axis direction of the holder | retainer in order to show the shape of the pocket of a holder | retainer. 円筒ころの軸方向端面の面取り部の寸法が不適正である場合に生じる不都合を説明する為の、図１の（ｂ）と同様の断面図。Sectional drawing similar to FIG.1, (b) for demonstrating the inconvenience which arises when the dimension of the chamfering part of the axial direction end surface of a cylindrical roller is improper. 円筒ころのスキューに就いて説明する為、円筒ころを図２と同方向から見た状態で示す図。The figure which shows the state which looked at the cylindrical roller from the same direction as FIG. 2 in order to demonstrate about the skew of a cylindrical roller. 保持器のポケットの外径側周縁部が摩耗した状態を示す、図４の（Ｂ）と同様の図。The figure similar to (B) of Drawing 4 showing the state where the outside diameter side peripheral part of the pocket of a cage was worn. 軸方向端面を球状凸面とした円筒ころの側面図。The side view of the cylindrical roller which made the axial direction end surface the spherical convex surface. この円筒ころを組み込んだスラスト円筒ころ軸受の第１例を、保持器の中心軸を含む仮想平面で切断した状態で示す部分断面図。The fragmentary sectional view which shows the 1st example of the thrust cylindrical roller bearing incorporating this cylindrical roller in the state cut | disconnected by the virtual plane containing the central axis of a holder | retainer. 軸方向端面を凸面とした円筒ころを組み込んだスラスト円筒ころ軸受で生じる、ポケットの外径側周縁部の摩耗状態を示す、図４の（Ｂ）と同様の図。The figure similar to (B) of FIG. 4 which shows the abrasion state of the outer peripheral side peripheral part of a pocket produced with the thrust cylindrical roller bearing incorporating the cylindrical roller which made the axial direction end surface convex. 軸方向端面を凸面とした円筒ころを組み込んだスラスト円筒ころ軸受の第２例を、保持器の中心軸を含む仮想平面で切断した状態で示す部分断面図。The fragmentary sectional view which shows the 2nd example of the thrust cylindrical roller bearing incorporating the cylindrical roller which made the axial direction end surface convex surface cut | disconnected in the virtual plane containing the central axis of a holder | retainer.

符号の説明Explanation of symbols

１ スラスト円筒ころ軸受
２、２ａ 保持器
４ 内径側リム部
５、５ａ 外径側リム部
６ 中間板部
７、７ａ ポケット
８、８ａ、８ｂ 円筒ころ
９、９ａ 中央平坦面
１０ 転動面
１１、１１ａ 面取り部
１２ 柱部
１３ 中央平板部
１４ 外径側平板部
１５ 内径側平板部
１６ 内径側連続部
１７ 外径側連続部
１８ 外径側係止部
１９ 内径側係止部
２０ 中央係止部
２１、２１ａ、２１ｂ 外径側端面
２２ 外径側周縁部
２３、２３ａ 凹入部
２４ 擦れ合い面
２５ 剪断面
２６ 破断面
２７ パンチ
２８ 金属板
２９ 受型
３０ 受孔
３１ ダレ DESCRIPTION OF SYMBOLS 1 Thrust cylindrical roller bearing 2, 2a Cage 4 Inner diameter side rim part 5, 5a Outer diameter side rim part 6 Intermediate | middle board part 7, 7a Pocket 8, 8a, 8b Cylindrical roller 9, 9a Central flat surface 10 Rolling surface 11, 11a Chamfered portion 12 Column portion 13 Central flat plate portion 14 Outer diameter side flat plate portion 15 Inner diameter side flat plate portion 16 Inner diameter side continuous portion 17 Outer diameter side continuous portion 18 Outer diameter side locking portion 19 Inner diameter side locking portion 20 Central locking portion 21, 21a, 21b Outer diameter side end surface 22 Outer diameter side peripheral edge 23, 23a Recessed portion 24 Friction surface 25 Shear surface 26 Fracture surface 27 Punch 28 Metal plate 29 Receiving die 30 Receiving hole 31 Sag

Claims (6)

全体を円輪状に造られて円周方向複数個所に、それぞれが放射方向に配置された複数のポケットを備えた保持器と、これら各ポケット内に転動自在に保持された複数個の円筒ころとを備え、この保持器は、金属板を曲げ形成する事により一体に造られて、内周縁部に存在する、全周に亙って連続する円環状の内径側リム部と、外周縁部に存在する、この内径側リム部と同心で全周に亙って連続する円環状の外径側リム部と、この外径側リム部と上記内径側リム部との間に存在する、断面形状が径方向に関して屈曲した中間板部と、この中間板部に円周方向に関して間欠的に、それぞれ放射方向に形成された上記各ポケットと、円周方向に隣り合うポケット同士の間に設けられた複数の柱部とを備え、上記中間板部は、径方向中間部で軸方向一端寄り部分に形成された中央平板部と、上記外径側リム部の径方向内側に隣接する軸方向他端寄り部分に形成された外径側平板部と、上記内径側リム部の径方向外側に隣接する軸方向他端寄り部分に形成された内径側平板部と、この内径側平板部の外周縁と上記中央平板部の内周縁とを連続させる内径側連続部と、この中央平板部の外周縁と上記外径側平板部の内周縁とを連続させる外径側連続部とから成り、上記軸方向一端側への上記保持器の軸方向変位を、上記外径側平板部及び内径側平板部の一部で上記各柱部の円周方向端縁に設けられた各外径側係止部及び各内径側係止部と上記各円筒ころの転動面との係合により、これら各円筒ころの一部が上記内径側、外径側両リム部の先端縁及び上記中央平板部よりも軸方向に突出したままの状態となる様に規制しており、上記軸方向他端側への上記保持器の軸方向変位を、上記中央平板部の一部で上記各柱部の円周方向端縁に設けられた各中央係止部と上記各円筒ころの転動面との係合により、これら各円筒ころの一部が上記外径側平板部及び上記内径側平板部よりも軸方向に突出したままの状態となる様に規制しているスラスト円筒ころ軸受に於いて、上記各円筒ころは、それぞれの軸方向両端面のうちの少なくとも上記保持器の外径側端面に、それぞれの回転中心軸に対し直角方向に拡がる中央平坦面と、この中央平坦面の外周縁と転動面とを全周に亙って連続させる面取り部とを備えたものであり、上記保持器を軸方向一端側に変位させて上記各外径側係止部及び各内径側係止部と上記各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記保持器を構成する外径側、内径側両平板部の外面から突出する量を、これら各円筒ころの径方向に関する上記面取り部の寸法未満にすると共に、上記保持器を軸方向他端側に変位させて上記各中央係止部と上記各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記保持器を構成する外径側平板部の外面から突出する量とこれら各円筒ころの径方向に関する上記面取り部の寸法との差を、上記金属板の板厚よりも小さくした事を特徴とするスラスト円筒ころ軸受。   A cage that is formed in an annular shape and is provided with a plurality of pockets that are radially arranged at a plurality of locations in the circumferential direction, and a plurality of cylindrical rollers that are rotatably held in the pockets. The retainer is integrally formed by bending a metal plate, and is present on the inner peripheral edge, and is formed on an inner diameter side rim that is continuous over the entire circumference, and an outer peripheral edge. A circular outer diameter side rim portion that is concentric with the inner diameter side rim portion and continuous over the entire circumference, and a cross section that exists between the outer diameter side rim portion and the inner diameter side rim portion. An intermediate plate portion whose shape is bent with respect to the radial direction, and intermittently with respect to the circumferential direction in the intermediate plate portion, each pocket formed in the radial direction is provided between the pockets adjacent to each other in the circumferential direction. A plurality of pillar portions, and the intermediate plate portion is the same in the axial direction at the radially intermediate portion. A central flat plate portion formed in the near portion, an outer diameter side flat plate portion formed in a portion near the other axial end adjacent to the radially inner side of the outer diameter side rim portion, and a radially outer side of the inner diameter side rim portion An inner diameter side flat plate portion formed near the other end in the axial direction adjacent to the inner diameter side flat plate portion, an inner diameter side continuous portion that connects the outer peripheral edge of the inner diameter side flat plate portion and the inner peripheral edge of the central flat plate portion, An outer diameter side continuous portion that continues the outer peripheral edge and the inner peripheral edge of the outer diameter side flat plate portion, and the axial displacement of the cage toward the one end side in the axial direction is changed to the outer diameter side flat plate portion and the inner diameter side. By engaging each outer diameter side locking portion and each inner diameter side locking portion provided on the circumferential edge of each column portion with a part of the flat plate portion and the rolling surface of each cylindrical roller, these A part of each cylindrical roller is projected in the axial direction from the leading edge of both the inner diameter side and outer diameter side rim parts and the central flat plate part. And the axial displacement of the cage toward the other end in the axial direction is a part of the central flat plate portion and is provided at the circumferential edge of each column portion. Due to the engagement between the central locking portion and the rolling surface of each cylindrical roller, a part of each cylindrical roller remains protruding in the axial direction from the outer diameter side flat plate portion and the inner diameter side flat plate portion. In the thrust cylindrical roller bearing which is regulated in such a manner, each cylindrical roller has a direction perpendicular to each rotation center axis at least on the outer diameter side end face of the cage among the both axial end faces. And a chamfered portion for continuously connecting the outer peripheral edge of the central flat surface and the rolling surface over the entire circumference, and the cage is displaced toward one end in the axial direction. Each outer diameter side locking portion and each inner diameter side locking portion are engaged with the rolling surface of each cylindrical roller. Thus, the amount by which a part of each cylindrical roller protrudes from the outer surface of both the outer diameter side and inner diameter side flat plate portions constituting the cage is less than the dimension of the chamfered portion in the radial direction of each cylindrical roller. In a state where the cage is displaced to the other end side in the axial direction and the central locking portions are engaged with the rolling surfaces of the cylindrical rollers, a part of each of the cylindrical rollers holds the cage. A thrust cylindrical roller characterized in that the difference between the protruding amount of the flat plate portion on the outer diameter side and the dimension of the chamfered portion in the radial direction of each cylindrical roller is smaller than the thickness of the metal plate. bearing. 保持器を軸方向一端側に変位させて各外径側係止部及び各内径側係止部と各円筒ころの転動面とを係合させた状態で、これら各円筒ころの中央平坦面と各ポケットの外径側周縁部との擦れ合い面の長さを、これら各円筒ころの直径の８０％以内とした、請求項１に記載したスラスト円筒ころ軸受。   The central flat surface of each cylindrical roller in a state in which the cage is displaced to one end side in the axial direction and each outer diameter side locking portion and each inner diameter side locking portion is engaged with the rolling surface of each cylindrical roller. The thrust cylindrical roller bearing according to claim 1, wherein a length of a frictional surface between each pocket and an outer peripheral side peripheral portion of each pocket is within 80% of a diameter of each cylindrical roller. 各円筒ころの面取り部の寸法のうち、これら各円筒ころの軸方向の寸法よりも同じく径方向の寸法を大きくしている、請求項１〜２のうちの何れか１項に記載したスラスト円筒ころ軸受。   The thrust cylinder according to any one of claims 1 to 2, wherein among the dimensions of the chamfered portion of each cylindrical roller, the radial dimension is made larger than the axial dimension of each cylindrical roller. Roller bearing. 保持器を軸方向一端側に変位させて各外径側係止部及び各内径側係止部と各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記保持器を構成する外径側、内径側両平板部の外面から突出する量と、この保持器を軸方向他端側に変位させて各中央係止部と上記各円筒ころの転動面とを係合させた状態で、これら各円筒ころの一部が上記両平板部の外面から突出する量との差を５０μｍ以上とした、請求項１〜３のうちの何れか１項に記載したスラスト円筒ころ軸受。   In a state where the cage is displaced to one end side in the axial direction and the outer diameter side locking portions and the inner diameter side locking portions are engaged with the rolling surfaces of the cylindrical rollers, a part of each cylindrical roller is The amount of protrusion from the outer surface of both the outer diameter side and inner diameter side flat plate portions constituting the cage, and the center locking portion and the rolling surface of each cylindrical roller by displacing the cage to the other axial end side The difference between the amount of a part of each of these cylindrical rollers protruding from the outer surfaces of the two flat plate portions is 50 μm or more. Thrust cylindrical roller bearing. 各円筒ころの転動面とそれぞれ転がり接触するレース面を有する１対の部材が、何れも使用時に回転するものであり、保持器の中央平板部が、使用回転速度が速い部材に対向している、請求項１〜４のうちの何れか１項に記載したスラスト円筒ころ軸受。   A pair of members each having a race surface that is in rolling contact with the rolling surface of each cylindrical roller rotate in use, and the central flat plate portion of the cage faces a member that has a high rotational speed. The thrust cylindrical roller bearing according to any one of claims 1 to 4. 各ポケットが金属板に打ち抜き加工を施す事により形成されたもので、この打ち抜き加工は、パンチを外径側、内径側両平板部の内面側から外面側に突き通す事により行なわれたものであって、上記各ポケットの内周縁のうちで上記外径側、内径側両平板部に対応する部分に、これら両平板部の内面側に上記打ち抜き加工に伴う剪断面が、同じく外側面側に破断面が、それぞれ存在しており、各円筒ころの軸方向両端面のうちの少なくとも上記保持器の外径側端面に設けた中央平坦面が、上記各ポケット内での上記各円筒ころの変位に拘らず、上記破断面と接触しない様に、これら各円筒ころの一部が上記保持器を構成する外径側平板部の外面から突出する量とこれら各円筒ころの径方向に関する面取り部の寸法との差を、上記破断面の幅との関係で規制した、請求項１〜５のうちの何れか１項に記載したスラスト円筒ころ軸受。
Each pocket was formed by punching a metal plate, and this punching was performed by penetrating the punch from the inner surface side to the outer surface side of both the outer diameter side and inner diameter side flat plate portions. In addition, the shearing surface associated with the punching process on the inner surface side of both the flat plate portions on the inner peripheral edge of each pocket corresponding to the outer diameter side and inner diameter side flat plate portions is also broken on the outer surface side. Cross sections exist, and a central flat surface provided on at least the outer diameter side end surface of the cage among both axial end surfaces of each cylindrical roller is used for displacement of each cylindrical roller in each pocket. Regardless of the amount of protrusion of each cylindrical roller from the outer surface of the outer diameter side flat plate portion constituting the cage and the dimension of the chamfered portion in the radial direction of each cylindrical roller so as not to contact the fracture surface. And the width of the fracture surface Was regulated by the relationship, axial cylindrical roller bearing according to any one of claims 1 to 5.
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008261476A (en) * 2007-03-19 2008-10-30 Nsk Ltd Thrust needle roller bearing
JP2010174970A (en) * 2009-01-29 2010-08-12 Jtekt Corp Thrust roller bearing
JP2015528553A (en) * 2012-09-05 2015-09-28 シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ Thrust cage for cylindrical rolling elements
JP2016128711A (en) * 2015-01-09 2016-07-14 Ntn株式会社 Retainer for thrust roller bearing, and method of manufacturing the same

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008261476A (en) * 2007-03-19 2008-10-30 Nsk Ltd Thrust needle roller bearing
JP2010174970A (en) * 2009-01-29 2010-08-12 Jtekt Corp Thrust roller bearing
JP2015528553A (en) * 2012-09-05 2015-09-28 シェフラー テクノロジーズ アー・ゲー ウント コー． カー・ゲーＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ Thrust cage for cylindrical rolling elements
JP2016128711A (en) * 2015-01-09 2016-07-14 Ntn株式会社 Retainer for thrust roller bearing, and method of manufacturing the same

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