JP2020204350A

JP2020204350A - Roller bearing

Info

Publication number: JP2020204350A
Application number: JP2019111488A
Authority: JP
Inventors: 佐野　徹; Toru Sano; 徹佐野
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2019-06-14
Filing date: 2019-06-14
Publication date: 2020-12-24
Anticipated expiration: 2039-06-14
Also published as: JP7275886B2

Abstract

To provide a roller bearing which enables improvement of rotation performance, increase of a load capacity, and enhancement of strength of a retainer while inhibiting increase of manufacturing costs.SOLUTION: A roller bearing 1 includes: an outer ring 2 having an outer ring raceway surface 2a on an inner peripheral surface; an inner ring 3 having an inner ring raceway surface 3a on an outer peripheral surface; and rollers 4 disposed in a rollable manner between the outer ring raceway surface 2a and the inner ring raceway surface 3a. A pair of shaft parts 4d is formed at axis positions of both axial end surfaces 4w of each of the rollers 4. The roller bearing 1 includes a pair of annular plates 5 which are disposed at both axial sides of the rollers 4, respectively have through holes 5a, which are fitted with the pair of shaft parts 4d of the rollers 4, and rotatably support the rollers 4.SELECTED DRAWING: Figure 2

Description

本発明は、ころ軸受に関し、例えば、円筒ころ軸受、円すいころ軸受、又は自動調心ころ軸受等のころ軸受に関する。 The present invention relates to roller bearings, for example, roller bearings such as cylindrical roller bearings, tapered roller bearings, and self-aligning roller bearings.

従来から、圧延機等の製鉄機械、建設機械、鉱山機械、風力発電設備等の重荷重、衝撃荷重、振動、急加減速が発生するような機械、設備等において、高負荷能力を有する円筒ころ軸受、円すいころ軸受、又は自動調心ころ軸受が使用されている。 Conventionally, tapered rollers with high load capacity in iron-making machines such as rolling mills, construction machines, mining machines, wind power generation equipment, and other machines and equipment that generate heavy loads, impact loads, vibrations, and rapid acceleration and deceleration. Bearings, tapered roller bearings, or self-aligning roller bearings are used.

そして、従来の高負荷能力を有するころ軸受としては、例えば、保持器を備えていない総ころ軸受と称される円筒ころ軸受が知られている（例えば、特許文献１参照）。 As a conventional roller bearing having a high load capacity, for example, a cylindrical roller bearing called a full roller bearing without a cage is known (see, for example, Patent Document 1).

また、内輪と、外輪と、これら内外輪の間に転動自在に設けた複数のころと、これらころの両側に設けた環状板と、を備えるころ軸受において、各ころは、両端面の中心部に凹部を有し、各環状板は、独立であって、上記各凹部に、これら凹部と回転可能に挿入する複数の係止ピンを備えるものが知られている（例えば、特許文献２参照）。 Further, in a roller bearing provided with an inner ring, an outer ring, a plurality of rollable rollers provided between the inner and outer rings, and annular plates provided on both sides of these rollers, each roller is the center of both end faces. It is known that each annular plate has a recess in the portion, and each annular plate is provided with a plurality of locking pins that are rotatably inserted into each of the recesses (see, for example, Patent Document 2). ).

特開平０９−０８８９７０号公報Japanese Unexamined Patent Publication No. 09-08870 特開平１０−２１３１４０号公報Japanese Unexamined Patent Publication No. 10-213140

ところで、上記した特許文献１は、保持器を省略した円筒ころ軸受、即ち、総ころ軸受であるため、負荷容量が大きく重荷重条件下での使用に適しているが、総ころ軸受は、隣り合うころの転動面同士が逆方向にすべり接触しながら回転するため回転性能が低く、さらに、ころ表面において損傷が起こりやすいことから、適用は低速回転の機械や設備等に限られていた。 By the way, Patent Document 1 described above is a cylindrical roller bearing without a cage, that is, a total roller bearing, and therefore has a large load capacity and is suitable for use under heavy load conditions. Since the rolling surfaces of the rollers that meet each other rotate while sliding in opposite directions, the rotation performance is low, and the roller surface is liable to be damaged, so the application has been limited to machines and equipment that rotate at low speeds.

また、上記した特許文献２では、保持器の柱部（円周方向に隣り合うころところの間に設けられた、保持器の一部分）を取り除き、多くのころを配置して、負荷容量を大きくすることができると共に、他部と比べて強度の低い柱部を有しないことによって保持器の強度を充分に高くすることができるものの、係止ピンの溶接が必要であるため、製造コストが増加してしまっていた。また、溶接不具合により溶接部の割れ、脱落や係止ピンの脱落等が起きる可能性があり、これらが発生した場合、機械や設備等の運転を停止してメンテナンスを行う必要がある。 Further, in Patent Document 2 described above, the pillar portion of the cage (a part of the cage provided between the rollers adjacent to each other in the circumferential direction) is removed, and many rollers are arranged to increase the load capacity. Although it is possible to sufficiently increase the strength of the cage by not having a pillar portion whose strength is lower than that of other portions, the manufacturing cost increases because the locking pin needs to be welded. I had done it. In addition, there is a possibility that the welded portion may crack, fall off, or the locking pin may fall off due to a welding defect. If these occur, it is necessary to stop the operation of the machine or equipment for maintenance.

本発明は、上述した課題を鑑みてなされたものであり、その目的は、製造コストの増加を抑制しつつ、回転性能を高くし、負荷容量を大きくすることができると共に、保持器の強度を高くすることができるころ軸受を提供することにある。 The present invention has been made in view of the above-mentioned problems, and an object of the present invention is to increase the rotational performance, increase the load capacity, and increase the strength of the cage while suppressing an increase in manufacturing cost. The purpose is to provide roller bearings that can be raised.

本発明の上記目的は、下記の構成により達成される。
（１）内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、前記外輪軌道面と前記内輪軌道面との間に転動自在に配置される複数のころと、を備えるころ軸受であって、前記複数のころの軸方向両端面の軸心位置には、一対の軸部が形成され、前記複数のころの軸方向両側に配置され、前記複数のころの一対の軸部と嵌合する穴部をそれぞれ有し、前記複数のころを回転可能に支持する一対の環状板を備える、ころ軸受。
（２）前記一対の環状板は、別体である、（１）に記載のころ軸受。
（３）前記外輪又は前記内輪に設けられ、前記複数のころの軸方向位置を規制するつばとつば輪を備え、前記つばと前記つば輪には、前記環状板の軸方向外側面と対向して、前記環状板の軸方向位置を規制する突部が設けられる、（２）に記載のころ軸受。
（４）前記つば輪は、前記外輪又は前記内輪に対してインロー構造により組み付けられると共に、固定手段により固定される、（３）に記載のころ軸受。
（５）前記環状板の前記穴部は、貫通穴であり、前記軸部の軸方向外端部には、前記環状板の軸方向外側面と対向するフランジが取り付けられる、（１）〜（４）のいずれかに記載のころ軸受。 The above object of the present invention is achieved by the following configuration.
(1) An outer ring having an outer ring raceway surface on the inner peripheral surface, an inner ring having an inner ring raceway surface on the outer peripheral surface, and a plurality of rollers rotatably arranged between the outer ring raceway surface and the inner ring raceway surface. A roller bearing comprising ,, wherein a pair of shaft portions are formed at the axial center positions of both end faces in the axial direction of the plurality of rollers, and are arranged on both sides in the axial direction of the plurality of rollers. A roller bearing having holes for fitting a pair of shafts and a pair of annular plates for rotatably supporting the plurality of rollers.
(2) The roller bearing according to (1), wherein the pair of annular plates are separate bodies.
(3) A brim and a brim ring provided on the outer ring or the inner ring and regulating the axial positions of the plurality of rollers are provided, and the brim and the brim ring face the axial outer surface of the annular plate. The roller bearing according to (2), wherein a protrusion for regulating the axial position of the annular plate is provided.
(4) The roller bearing according to (3), wherein the brim ring is assembled to the outer ring or the inner ring by an in-row structure and fixed by a fixing means.
(5) The hole portion of the annular plate is a through hole, and a flange facing the axial outer surface of the annular plate is attached to the axial outer end portion of the shaft portion (1) to (1). The roller bearing according to any one of 4).

本発明によれば、複数のころの軸方向両端面の軸心位置には、一対の軸部が形成され、複数のころの軸方向両側に配置され、複数のころの一対の軸部と嵌合する穴部をそれぞれ有し、複数のころを回転可能に支持する一対の環状板を備えるため、製造コストの増加を抑制しつつ、回転性能を高くし、負荷容量を大きくすることができると共に、環状板の強度を高くすることができる。このため、重荷重、衝撃荷重、振動、急加減速を伴う使用条件下でも軸受を長期間使用することができる。 According to the present invention, a pair of shaft portions are formed at the axial positions of both end faces in the axial direction of the plurality of rollers, are arranged on both sides in the axial direction of the plurality of rollers, and fit with the pair of shaft portions of the plurality of rollers. Since it has a pair of annular plates that have matching holes and rotatably support a plurality of rollers, it is possible to improve the rotation performance and the load capacity while suppressing an increase in manufacturing cost. , The strength of the annular plate can be increased. Therefore, the bearing can be used for a long period of time even under usage conditions involving heavy load, impact load, vibration, and rapid acceleration / deceleration.

本発明に係るころ軸受の第１実施形態の側面図である。It is a side view of the 1st Embodiment of the roller bearing which concerns on this invention. 図１のＡ−Ａ線断面図である。FIG. 1 is a cross-sectional view taken along the line AA of FIG. 第１実施形態において、ころ案内の場合の図２の要部拡大図である。In the first embodiment, it is an enlarged view of a main part of FIG. 2 in the case of roller guidance. 第１実施形態において、内輪案内の場合の図３に対応する要部拡大図である。In the first embodiment, it is an enlarged view of a main part corresponding to FIG. 3 in the case of inner ring guidance. 第１実施形態のころ軸受の第１変形例を示す断面図である。It is sectional drawing which shows the 1st modification of the roller bearing of 1st Embodiment. 第１実施形態のころ軸受の第２変形例を示す断面図である。It is sectional drawing which shows the 2nd modification of the roller bearing of 1st Embodiment. 第２実施形態のころ軸受を示す断面図である。It is sectional drawing which shows the roller bearing of 2nd Embodiment. 第２実施形態において、ころ案内の場合の図３に対応する要部拡大図である。In the second embodiment, it is an enlarged view of a main part corresponding to FIG. 3 in the case of roller guidance. 第２実施形態において、外輪案内の場合の図３に対応する要部拡大図である。In the second embodiment, it is an enlarged view of a main part corresponding to FIG. 3 in the case of outer ring guidance. 第２実施形態のころ軸受の第１変形例を示す断面図である。It is sectional drawing which shows the 1st modification of the roller bearing of 2nd Embodiment. 第２実施形態のころ軸受の第２変形例を示す断面図である。It is sectional drawing which shows the 2nd modification of the roller bearing of 2nd Embodiment. 本発明に係るころ軸受の第３実施形態の断面図である。It is sectional drawing of the 3rd Embodiment of the roller bearing which concerns on this invention. 第３実施形態のころ軸受の第１変形例を示す断面図である。It is sectional drawing which shows the 1st modification of the roller bearing of 3rd Embodiment. 第３実施形態のころ軸受の第２変形例を示す断面図である。It is sectional drawing which shows the 2nd modification of the roller bearing of 3rd Embodiment. 第３実施形態のころ軸受の第３変形例を示す断面図である。It is sectional drawing which shows the 3rd modification of the roller bearing of 3rd Embodiment. 本発明に係るころ軸受の第４実施形態の断面図である。It is sectional drawing of the 4th Embodiment of the roller bearing which concerns on this invention. 第４実施形態のころ軸受の第１変形例を示す断面図である。It is sectional drawing which shows the 1st modification of the roller bearing of 4th Embodiment. 第４実施形態のころ軸受の第２変形例を示す断面図である。It is sectional drawing which shows the 2nd modification of the roller bearing of 4th Embodiment. 第４実施形態のころ軸受の第３変形例を示す断面図である。It is sectional drawing which shows the 3rd modification of the roller bearing of 4th Embodiment. 第４実施形態のころ軸受の第４変形例を示す断面図である。It is sectional drawing which shows the 4th modification of the roller bearing of 4th Embodiment. 第４実施形態のころ軸受の第５変形例を示す断面図である。It is sectional drawing which shows the 5th modification of the roller bearing of 4th Embodiment. 本発明に係るころ軸受の第５実施形態の断面図である。It is sectional drawing of the 5th Embodiment of the roller bearing which concerns on this invention. ころ案内の場合の図１８の要部拡大図である。It is an enlarged view of the main part of FIG. 18 in the case of roller guidance. 内輪案内の場合の図１８の要部拡大図である。It is an enlarged view of the main part of FIG. 18 in the case of inner ring guidance. 第５実施形態のころ軸受の第１変形例を示す断面図である。It is sectional drawing which shows the 1st modification of the roller bearing of 5th Embodiment. 第５実施形態のころ軸受の第２変形例を示す断面図である。It is sectional drawing which shows the 2nd modification of the roller bearing of 5th Embodiment. 第５実施形態のころ軸受の第３変形例を示す断面図である。It is sectional drawing which shows the 3rd modification of the roller bearing of 5th Embodiment. 本発明に係るころ軸受の第６実施形態の断面図である。It is sectional drawing of the 6th Embodiment of the roller bearing which concerns on this invention. 本発明に係るころ軸受の第７実施形態の断面図である。It is sectional drawing of 7th Embodiment of the roller bearing which concerns on this invention. つば輪の位置決め構造を示す断面図である。It is sectional drawing which shows the positioning structure of a brim ring. 本発明に係るころ軸受の第８実施形態の側面図である。It is a side view of the 8th Embodiment of the roller bearing which concerns on this invention. 図２５のＢ−Ｂ線断面図である。FIG. 25 is a cross-sectional view taken along the line BB of FIG. 本発明に係るころ軸受の第９実施形態の断面図である。It is sectional drawing of the 9th Embodiment of the roller bearing which concerns on this invention. 本発明に係るころ軸受の第１０実施形態の断面図である。It is sectional drawing of the tenth embodiment of the roller bearing which concerns on this invention. 第１０実施形態のころ軸受の変形例を示す断面図である。It is sectional drawing which shows the modification of the roller bearing of 10th Embodiment. 本発明を単列の円すいころ軸受に適用した場合の断面図である。It is sectional drawing when the present invention is applied to a single row tapered roller bearing. 本発明を複列の円すいころ軸受に適用した場合の断面図である。It is sectional drawing when the present invention is applied to a double row tapered roller bearing. 本発明を自動調心ころ軸受に適用した場合の断面図である。It is sectional drawing when this invention is applied to self-aligning roller bearing. 特許文献２を説明する断面図である。It is sectional drawing explaining Patent Document 2.

以下、本発明に係るころ軸受の各実施形態について、図面に基づいて詳細に説明する。なお、以下の説明における左右とは、ころ軸受又はころの回転軸心方向における左右のことである。 Hereinafter, each embodiment of the roller bearing according to the present invention will be described in detail with reference to the drawings. The left and right in the following description are the left and right in the direction of the roller bearing or the rotation axis of the roller.

（第１実施形態）
まず、図１〜図４Ｂを参照して、本発明に係るころ軸受の第１実施形態について説明する。 (First Embodiment)
First, a first embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 1 to 4B.

本実施形態のころ軸受１は、図１及び図２に示すように、単列の円筒ころ軸受であって、内周面に外輪軌道面２ａを有する外輪２と、外周面に内輪軌道面３ａを有する内輪３と、この外輪軌道面２ａと内輪軌道面３ａとの間に転動自在に配置される複数のころ４と、複数のころ４を周方向に略等間隔に保持する左右一対の環状板（保持器）５と、を備える。 As shown in FIGS. 1 and 2, the roller bearing 1 of the present embodiment is a single row cylindrical roller bearing, and has an outer ring 2 having an outer ring raceway surface 2a on the inner peripheral surface and an inner ring raceway surface 3a on the outer peripheral surface. A pair of left and right rollers 4 that are rotatably arranged between the outer ring raceway surface 2a and the inner ring raceway surface 3a, and a pair of left and right rollers that hold the plurality of rollers 4 at substantially equal intervals in the circumferential direction. An annular plate (retainer) 5 is provided.

ころ４の軸方向両端面４ｗの軸心ＣＬ位置には、転動面を構成する円筒部分より小径の一対の軸部４ｄが軸方向に突出して形成されている。ころ４は、軸部４ｄを削り出すことで、該円筒部分と一体に形成される。 A pair of shaft portions 4d having a diameter smaller than that of the cylindrical portion constituting the rolling surface are formed at the axial center CL positions of the axially both end surfaces 4w of the rollers 4 so as to project in the axial direction. The roller 4 is formed integrally with the cylindrical portion by carving out the shaft portion 4d.

ころ４を保持する一対の環状板５は、断面矩形状の円環状部材であり、複数のころ４の軸方向両側に配置される。一対の環状板５には、一対の軸部４ｄとそれぞれ嵌合し、ころ４の軸部４ｄを回転可能に支持する複数の貫通穴（穴部）５ａが周方向に略等間隔で形成されている。一対の環状板５は、複数のころ４を周方向に略等間隔に保持する保持器を構成する。また、本実施形態では、一対の環状板５は、別体であり、互いを軸方向に連結する柱部を備えていない。 The pair of annular plates 5 that hold the rollers 4 are annular members having a rectangular cross section, and are arranged on both sides of the plurality of rollers 4 in the axial direction. A plurality of through holes (holes) 5a, which are fitted to the pair of shaft portions 4d and rotatably support the shaft portions 4d of the rollers 4, are formed in the pair of annular plates 5 at substantially equal intervals in the circumferential direction. ing. The pair of annular plates 5 form a cage that holds the plurality of rollers 4 at substantially equal intervals in the circumferential direction. Further, in the present embodiment, the pair of annular plates 5 are separate bodies and do not have a pillar portion that connects them in the axial direction.

内輪３は、図２に示すように、その一端側（図２中左側）に円環状のつば６が径方向外側に突出して形成され、他端側（図２中右側）につば輪７が取り付けられている。そして、つば６及びつば輪７は、ころ４の軸方向両端面４ｗに対向してころ４の軸方向位置を規制している。 As shown in FIG. 2, the inner ring 3 is formed with an annular brim 6 protruding outward in the radial direction on one end side (left side in FIG. 2) and a brim ring 7 on the other end side (right side in FIG. 2). It is attached. The brim 6 and the brim ring 7 regulate the axial position of the roller 4 so as to face the axially both end surfaces 4w of the roller 4.

つば輪７は、内輪３とは別体に形成された円環状部材であり、内輪３に取り付けられる構造である。つば輪７は、その内周面に段部７ｇが形成されており、内輪３の外周面の他端部（内輪軌道面３ａの延長線上の部分）に外嵌するように組み付けられている。つまり、つば輪７は、内輪３に対してインロー構造により組み付けられている。そして、つば輪７は、その周方向に略等間隔に配置される複数の固定手段（六角穴付ボルト等）１１により内輪３に固定されている。 The brim ring 7 is an annular member formed separately from the inner ring 3, and has a structure attached to the inner ring 3. The brim ring 7 has a stepped portion 7g formed on the inner peripheral surface thereof, and is assembled so as to be fitted on the other end of the outer peripheral surface of the inner ring 3 (a portion on an extension line of the inner ring raceway surface 3a). That is, the brim ring 7 is assembled to the inner ring 3 by an inro structure. The brim ring 7 is fixed to the inner ring 3 by a plurality of fixing means (hexagon socket head bolts or the like) 11 arranged at substantially equal intervals in the circumferential direction thereof.

つば６の外周面の軸方向外端部には、径方向外側に突出する環状の突部６ｄが形成されている。突部６ｄは、一方側（図２中左側）の環状板５の軸方向外側面に対向するように形成され、環状板５の軸方向位置を規制して、稼働時の環状板５の脱落を防止する。 An annular protrusion 6d that projects radially outward is formed at the axially outer end of the outer peripheral surface of the brim 6. The protrusion 6d is formed so as to face the axially outer surface of the annular plate 5 on one side (left side in FIG. 2), regulates the axial position of the annular plate 5, and causes the annular plate 5 to fall off during operation. To prevent.

つば輪７の外周面の軸方向外端部には、径方向外側に突出する環状の突部７ｄが形成されている。突部７ｄは、他方側（図２中右側）の環状板５の軸方向外側面に対向するように形成され、環状板５の軸方向位置を規制して、稼働時の環状板５の脱落を防止する。 An annular protrusion 7d that projects radially outward is formed at the axially outer end of the outer peripheral surface of the brim ring 7. The protrusion 7d is formed so as to face the axially outer surface of the annular plate 5 on the other side (right side in FIG. 2), regulates the axial position of the annular plate 5, and causes the annular plate 5 to fall off during operation. To prevent.

なお、環状板５の案内方式は、ころ案内であってもよいし、内輪案内であってもよい。例えば、環状板５をころ案内で使用する場合、図３Ａに示すように、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間Δ１は、つば６の外周面と環状板５の内周面との間の隙間Δ２（つば輪７の外周面と環状板５の内周面との間の隙間）より小さく設定されている。 The guidance method of the annular plate 5 may be roller guidance or inner ring guidance. For example, when the annular plate 5 is used for roller guidance, as shown in FIG. 3A, the gap Δ1 between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5 is a brim. It is set to be smaller than the gap Δ2 (the gap between the outer peripheral surface of the brim ring 7 and the inner peripheral surface of the annular plate 5) between the outer peripheral surface of 6 and the inner peripheral surface of the annular plate 5.

また、環状板５を内輪案内で使用する場合、図３Ｂに示すように、つば６の外周面と環状板５の内周面との間の隙間Δ２（つば輪７の外周面と環状板５の内周面との間の隙間）は、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間Δ１より小さく設定されている。 Further, when the annular plate 5 is used for the inner ring guide, as shown in FIG. 3B, the gap Δ2 between the outer peripheral surface of the brim 6 and the inner peripheral surface of the annular plate 5 (the outer peripheral surface of the brim ring 7 and the annular plate 5). The gap between the inner peripheral surface and the inner peripheral surface of the roller 4) is set to be smaller than the gap Δ1 between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5.

なお、ころ案内、内輪案内は、機械や設備等の使用条件等によって決められる。ただし、環状板５の挙動を安定化するために、軌道輪案内（内輪案内、後述する外輪案内）を採用した方がより好ましい。また、つば６の突部６ｄ、つば輪７の突部７ｄ等により環状板５の軸方向の動きが制限され、環状板５の挙動が安定化する場合は、転動体案内（ころ案内）を採用してもよい。 The roller guidance and inner ring guidance are determined by the usage conditions of machines and equipment. However, in order to stabilize the behavior of the annular plate 5, it is more preferable to adopt the raceway ring guide (inner ring guide, outer ring guide described later). Further, when the axial movement of the annular plate 5 is restricted by the protrusion 6d of the brim 6 and the protrusion 7d of the brim ring 7 and the behavior of the annular plate 5 is stabilized, the rolling element guidance (roller guidance) is performed. It may be adopted.

このように構成された本実施形態のころ軸受１によれば、複数のころ４の軸方向両端面４ｗの軸心ＣＬ位置には、一対の軸部４ｄが形成され、また、複数のころ４の軸方向両側に配置され、複数のころ４の一対の軸部４ｄと嵌合する穴部をそれぞれ有し、複数のころ４を回転可能に支持する一対の環状板５を備える。このため、ころ軸受１の稼働時に、各ころ４間に隙間が設けられた状態でころ４が一対の環状板５に回転可能に支持されるので、回転性能を高くすることができる。また、ころ軸受１は、従来保持器のような係止ピンを環状板に溶接する溶接工程が不要であるため、製造コストの増加を抑制することができる。さらに、ころ軸受１は、一対の環状板５同士を連結する柱部（例えば、実用新案登録第２５９５８７６号のステー１０４や特許第６２５３８７７号の柱部３３）がなく、ころ数を多くすることができ、負荷容量を大きくすることができる。また、環状板５は、他部と比べて強度の低い柱部を有していない構造の保持器であり、保持器としての強度を高くすることができる。このため、重荷重、衝撃荷重、振動、急加減速を伴う使用条件下でも軸受を長期間使用することができる。 According to the roller bearing 1 of the present embodiment configured in this way, a pair of shaft portions 4d are formed at the axial CL positions of the axially both end surfaces 4w of the plurality of rollers 4, and the plurality of rollers 4 A pair of annular plates 5 which are arranged on both sides in the axial direction of the above, have holes for fitting with a pair of shaft portions 4d of the plurality of rollers 4, and rotatably support the plurality of rollers 4. Therefore, when the roller bearing 1 is in operation, the rollers 4 are rotatably supported by the pair of annular plates 5 with a gap provided between the rollers 4, so that the rotational performance can be improved. Further, since the roller bearing 1 does not require a welding step of welding the locking pin to the annular plate as in the conventional cage, an increase in manufacturing cost can be suppressed. Further, the roller bearing 1 does not have a pillar portion for connecting the pair of annular plates 5 to each other (for example, the stay 104 of the utility model registration No. 2595876 and the pillar portion 33 of the patent No. 6253877), and the number of rollers may be increased. The load capacity can be increased. Further, the annular plate 5 is a cage having a structure that does not have a pillar portion having a lower strength than the other portions, and the strength as a cage can be increased. Therefore, the bearing can be used for a long period of time even under usage conditions involving heavy load, impact load, vibration, and rapid acceleration / deceleration.

また、本実施形態のころ軸受１によれば、内輪３に、複数のころ４の軸方向位置を規制するつば６とつば輪７が設けられ、つば６とつば輪７に設けられる突部６ｄ，７ｄにより、簡素な構造で稼働時の環状板５の脱落を防止することができる。 Further, according to the roller bearing 1 of the present embodiment, the inner ring 3 is provided with a brim 6 and a brim ring 7 for regulating the axial positions of the plurality of rollers 4, and a protrusion 6d provided on the brim 6 and the brim ring 7. , 7d makes it possible to prevent the annular plate 5 from falling off during operation with a simple structure.

また、本実施形態のころ軸受１によれば、つば輪７は、内輪３に対してインロー構造により組み付けられるため、内輪３とつば輪７の中心合わせを容易且つ確実に行うことができる。また、中心合わせを行った後につば輪７を固定手段（六角穴付ボルト等）１１により固定するため、固定作業を容易にすることができる。 Further, according to the roller bearing 1 of the present embodiment, since the brim ring 7 is assembled to the inner ring 3 by an in-row structure, the inner ring 3 and the brim ring 7 can be easily and surely centered. Further, since the brim ring 7 is fixed by the fixing means (hexagon socket head cap screw or the like) 11 after the centering is performed, the fixing work can be facilitated.

なお、本実施形態では、固定手段（六角穴付ボルト等）１１は、各ころ４の位置毎に２本ずつ配置されているが、１本ずつ配置されていてもよいし、各ころ４の位置毎に配置されていなくてもよい。つまり、固定手段１１の数や配置に制限はない。また、固定手段１１はボルトに限定されない。 In the present embodiment, two fixing means (hexagon socket head bolts, etc.) 11 are arranged at each position of each roller 4, but one may be arranged one by one, or each roller 4 may be arranged. It does not have to be arranged for each position. That is, there is no limit to the number or arrangement of the fixing means 11. Further, the fixing means 11 is not limited to bolts.

本発明の効果を確認するため、本発明例（第１実施形態相当品）と比較例１〜３のころ本数を比較した。また、比較例１は、ころ間に間座を備える軸受（特開２００５−３４４８５４号公報参照）で、ころ本数は２１本であり、比較例２は、ピン形保持器を備える軸受（特開昭５３−０００３５８号公報参照）で、ころ本数は２１本であり、比較例３は、もみ抜き保持器を備えるころ軸受で、ころ本数は１９本である。なお、議論を簡単にするため、ころ本数以外の値（寸法等）はすべて同じとした。また、比較例１〜３のころ本数は、特開２００５−３４４８５４号公報の表１を参照した。 In order to confirm the effect of the present invention, the numbers of the examples of the present invention (corresponding to the first embodiment) and Comparative Examples 1 to 3 were compared. Further, Comparative Example 1 is a bearing having a spacer between rollers (see JP-A-2005-344854), the number of rollers is 21, and Comparative Example 2 is a bearing having a pin-shaped cage (Japanese Patent Laid-Open No. 2005). (Refer to Japanese Patent Application Laid-Open No. 53-000358), the number of rollers is 21, and Comparative Example 3 is a roller bearing provided with a punching cage, and the number of rollers is 19. For the sake of simplicity, all values (dimensions, etc.) other than the number of rollers are the same. For the number of the rollers of Comparative Examples 1 to 3, refer to Table 1 of JP-A-2005-344854.

本発明例のころ本数は２２本であり、比較例１〜３のころ本数（１９〜２１本）よりも多くなるため、本発明例の軸受寿命は、比較例１〜３よりも長くなる。 Since the number of rollers in the example of the present invention is 22, which is larger than the number of rollers in Comparative Examples 1 to 3 (19 to 21), the bearing life of the examples of the present invention is longer than that of Comparative Examples 1 to 3.

なお、本実施形態の第１変形例として、図４Ａに示すように、内輪３の左右両側につば輪７が取り付けられる構造としてもよい。これにより、ころ軸受１が左右対称形状となり、内輪３を容易に製造加工することができる。 As a first modification of the present embodiment, as shown in FIG. 4A, the brim rings 7 may be attached to the left and right sides of the inner ring 3. As a result, the roller bearing 1 has a symmetrical shape, and the inner ring 3 can be easily manufactured and processed.

また、本実施形態の第２変形例として、図４Ｂに示すように、内輪側につば６及びつば輪７が設けられるとともに、外輪２は、内輪３に設けられたつば輪７と径方向に対向する部分につば８を形成してもよい。もちろん、外輪２は、内輪３に設けられた、つば６と径方向に対向する部分につば８を形成してもよい。 Further, as a second modification of the present embodiment, as shown in FIG. 4B, a brim 6 and a brim ring 7 are provided on the inner ring side, and the outer ring 2 is radial to the brim ring 7 provided on the inner ring 3. A brim 8 may be formed on the opposing portions. Of course, the outer ring 2 may form a brim 8 at a portion provided on the inner ring 3 that faces the brim 6 in the radial direction.

（第２実施形態）
次に、図５〜図７Ｂを参照して、本発明に係るころ軸受の第２実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (Second Embodiment)
Next, a second embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 5 to 7B. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

この実施形態では、図５に示すように、つば８及びつば輪９が外輪２の左右両側に設けられている。つば輪９は、外輪２に対してインロー構造により組み付けられるため、外輪２とつば輪９の中心合わせを容易且つ確実に行うことができる。また、中心合わせを行った後につば輪９を固定手段（六角穴付ボルト等）１１により固定するため、固定作業を容易にすることができる。
また、本実施形態の場合も、つば８とつば輪９に設けられる突部８ｄ，９ｄにより、簡素な構造で稼働時の環状板５の脱落を防止することができる。 In this embodiment, as shown in FIG. 5, a brim 8 and a brim ring 9 are provided on both the left and right sides of the outer ring 2. Since the brim ring 9 is assembled to the outer ring 2 by an in-row structure, the centering of the outer ring 2 and the brim ring 9 can be easily and surely performed. Further, since the brim ring 9 is fixed by the fixing means (hexagon socket head cap screw or the like) 11 after the centering is performed, the fixing work can be facilitated.
Further, also in the case of the present embodiment, the protrusions 8d and 9d provided on the brim 8 and the brim ring 9 can prevent the annular plate 5 from falling off during operation with a simple structure.

なお、環状板５の案内方式は、ころ案内であってもよいし、外輪案内であってもよい。例えば、環状板５をころ案内で使用する場合、図６Ａに示すように、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間は、つば８の内周面と環状板５の外周面との間の隙間（つば輪９の内周面と環状板５の外周面との間の隙間）より小さく設定されている。 The guidance method of the annular plate 5 may be roller guidance or outer ring guidance. For example, when the annular plate 5 is used for roller guidance, as shown in FIG. 6A, the gap between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5 is a brim 8. It is set to be smaller than the gap between the inner peripheral surface of the ring 9 and the outer peripheral surface of the annular plate 5 (the gap between the inner peripheral surface of the brim ring 9 and the outer peripheral surface of the annular plate 5).

また、環状板５を外輪案内で使用する場合、図６Ｂに示すように、つば８の内周面と環状板５の外周面との間の隙間（つば輪９の内周面と環状板５の外周面との間の隙間）は、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間より小さく設定されている。 Further, when the annular plate 5 is used for the outer ring guide, as shown in FIG. 6B, a gap between the inner peripheral surface of the brim 8 and the outer peripheral surface of the annular plate 5 (the inner peripheral surface of the brim 9 and the annular plate 5). The gap between the outer peripheral surface and the outer peripheral surface of the roller 4) is set to be smaller than the gap between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5.

ここで、本実施形態のころ軸受１の回転性能について、図３３に示す特許文献２に記載のころ軸受と比較しながら説明する。特許文献２では、保持器（環状板１１８と係止ピン１１９）の重心Ｇがころ１０７上になく、保持器の重心から外れた位置に荷重がかかるため、保持器は軸方向外側に倒れようとし（矢印Ｚ参照）、不安定な挙動（倒れる、戻るの繰り返しによる暴れ）を示す。そして、つば輪１１７の内周面の突部１１７ａで不安定な挙動に起因する大きな荷重を受けるのであるが、このとき突部１１７ａの軸方向内側面と環状板１１８の軸方向外側面とが片当たりとなるため、面圧Ｐが大きくなる。 Here, the rotational performance of the roller bearing 1 of the present embodiment will be described in comparison with the roller bearing described in Patent Document 2 shown in FIG. 33. In Patent Document 2, the center of gravity G of the cage (annular plate 118 and locking pin 119) is not on the roller 107, and the load is applied at a position deviated from the center of gravity of the cage, so that the cage may fall outward in the axial direction. (See arrow Z), and shows unstable behavior (falling down, rampage due to repeated returning). Then, a large load is applied to the protrusion 117a on the inner peripheral surface of the brim ring 117 due to unstable behavior. At this time, the axial inner surface of the protrusion 117a and the axial outer surface of the annular plate 118 are subjected to each other. Since it is a one-sided contact, the surface pressure P becomes large.

これに対して、本実施形態では、図６Ａ及び図６Ｂに示すように、保持器（環状板５）の重心Ｇがころ４の軸部４ｄ上にあり、保持器の重心に荷重がかかるため、保持器が軸方向外側に倒れにくく、不安定な挙動を示しにくい。そして、図６Ａの場合、ころ４の軸部４ｄの外周面で保持器の重量を受ける（不安定な挙動に起因する大きな荷重は受けない）のであるが、このときころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面とは片当たりとなりにくいため、面圧Ｐが上記特許文献２よりも小さい。また、図６Ｂの場合、つば８（つば輪９）の内周面で保持器の重量を受ける（不安定な挙動に起因する大きな荷重は受けない）のであるが、つば８（つば輪９）の内周面と環状板５の外周面とは片当たりとなりにくいため、面圧Ｐが上記特許文献２よりも小さい。つまり、本実施形態の方が上記特許文献２よりも面圧Ｐが小さい。 On the other hand, in the present embodiment, as shown in FIGS. 6A and 6B, the center of gravity G of the cage (annular plate 5) is on the shaft portion 4d of the roller 4, and a load is applied to the center of gravity of the cage. , The cage does not easily fall outward in the axial direction, and it does not easily show unstable behavior. Then, in the case of FIG. 6A, the weight of the cage is received on the outer peripheral surface of the shaft portion 4d of the roller 4 (a large load due to unstable behavior is not received), but at this time, the shaft portion 4d of the roller 4 receives the weight. Since the outer peripheral surface and the inner peripheral surface of the through hole 5a of the annular plate 5 are unlikely to come into contact with each other, the surface pressure P is smaller than that of Patent Document 2. Further, in the case of FIG. 6B, the weight of the cage is received on the inner peripheral surface of the brim 8 (brimming wheel 9) (a large load due to unstable behavior is not received), but the brim 8 (brimming wheel 9) The surface pressure P is smaller than that of Patent Document 2 because the inner peripheral surface of the ring and the outer peripheral surface of the annular plate 5 are unlikely to come into contact with each other. That is, the surface pressure P of this embodiment is smaller than that of Patent Document 2.

従って、上記特許文献２では、面圧Ｐが大きいため、すべり速度Ｖを大きくすること（例えば、軸受回転数を大きくすること等）が困難である。これに対して、本発明では、面圧Ｐが上記特許文献２よりも小さいため、すべり速度Ｖを上記特許文献２よりも大きくすることができる。つまり、本実施形態は、すべり接触におけるＰＶ値（面圧Ｐとすべり速度Ｖの積であり、所定値を超えると摩耗が早く進んだり、発熱したり、発熱による焼付きが起こったりする）を所定値以下にすることが容易である。 Therefore, in Patent Document 2, since the surface pressure P is large, it is difficult to increase the slip speed V (for example, increase the bearing rotation speed, etc.). On the other hand, in the present invention, since the surface pressure P is smaller than that of Patent Document 2, the slip speed V can be made larger than that of Patent Document 2. That is, in the present embodiment, the PV value at the sliding contact (the product of the surface pressure P and the sliding speed V, and if it exceeds a predetermined value, wear progresses quickly, heat is generated, and seizure occurs due to heat generation). It is easy to make it less than a predetermined value.

なお、本実施形態の第１変形例として、図７Ａに示すように、外輪２の左右両側につば輪９が設けられてもよい。 As a first modification of the present embodiment, as shown in FIG. 7A, brim rings 9 may be provided on both the left and right sides of the outer ring 2.

また、本実施形態の第２変形例として、図７Ｂに示すように、外輪側につば８及びつば輪９が設けられるとともに、内輪３は、外輪２に設けられたつば輪９と径方向に対向する部分につば６を形成してもよい。もちろん、内輪３は、外輪２に設けられた、つば８と径方向に対向する部分につば６を形成してもよい。 Further, as a second modification of the present embodiment, as shown in FIG. 7B, a brim 8 and a brim ring 9 are provided on the outer ring side, and the inner ring 3 is radial to the brim ring 9 provided on the outer ring 2. A brim 6 may be formed on the opposing portions. Of course, the inner ring 3 may form a brim 6 at a portion provided on the outer ring 2 that faces the brim 8 in the radial direction.

さらに、本発明によれば、外輪２につば８とつば輪９を設ける形態のころ軸受１を圧延機に使用し、外輪２がハウジングに固定され、内輪３で圧延ロールを支持する場合、メンテナンス等で軸受を分解する際、外輪２側に複数のころ４及び一対の環状板５を残した状態で、内輪３を圧延ロールと共に引き抜いたり、ころ軸受１を残した状態で圧延ロールを引き抜いたりすることができるので、ころ軸受１と圧延ロールのメンテナンスを容易に行うことができる。 Further, according to the present invention, when a roller bearing 1 having a brim 8 and a brim 9 provided on the outer ring 2 is used in the rolling mill, the outer ring 2 is fixed to the housing, and the rolling roll is supported by the inner ring 3, maintenance is performed. When disassembling the bearing by means of, etc., the inner ring 3 may be pulled out together with the rolling roll with the plurality of rollers 4 and the pair of annular plates 5 left on the outer ring 2 side, or the rolling roll may be pulled out with the roller bearing 1 left. Therefore, maintenance of the roller bearing 1 and the rolling roll can be easily performed.

（第３実施形態）
次に、図８〜図１１を参照して、本発明に係るころ軸受の第３実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (Third Embodiment)
Next, a third embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 8 to 11. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態では、図８に示すように、第１実施形態と同様に、つば６及びつば輪７を内輪３側に設けた複列ころ軸受の構造となっている。具体的に、左右のころ４間に位置する内輪３の外周面には、環状の突部６ｄを有するつば６が形成され、左右のころ４の軸方向外側に位置する内輪３の外周面には、つば輪７がそれぞれ取り付けられている。また、突部６ｄは、左右のころ４の軸方向内側の環状板５，５の両方を軸方向に規制する。 In this embodiment, as shown in FIG. 8, the structure is a double row roller bearing in which the brim 6 and the brim ring 7 are provided on the inner ring 3 side, as in the first embodiment. Specifically, a brim 6 having an annular protrusion 6d is formed on the outer peripheral surface of the inner ring 3 located between the left and right rollers 4, and is formed on the outer peripheral surface of the inner ring 3 located on the outer side in the axial direction of the left and right rollers 4. The brim ring 7 is attached to each. Further, the protrusion 6d restricts both the annular plates 5 and 5 inside the left and right rollers 4 in the axial direction in the axial direction.

なお、本実施形態の第１変形例として、図９に示すように、複列ころ軸受は、一方の列（図９中右側）のころ４の長さを、他方の列（図９中左側）のころ４の長さよりも大きくしてもよい。このような左右非対称の複列ころ軸受は、左右の列に異なる荷重が作用する場合に使用され、大きい荷重が作用する側に長さの大きいころを配置し、小さい荷重が作用する側に長さの小さいころを配置する。 As a first modification of the present embodiment, as shown in FIG. 9, in the double row roller bearing, the length of the roller 4 in one row (right side in FIG. 9) is changed to the length of the roller 4 in the other row (left side in FIG. 9). ) May be longer than the length of 4. Such asymmetric double row roller bearings are used when different loads are applied to the left and right rows, and the long rollers are arranged on the side where the large load is applied and the length is long on the side where the small load is applied. Place the small rollers.

次に、本実施形態の第２変形例として、図１０に示すように、複列ころ軸受は、つば８及びつば輪９を外輪２側に設けてもよい。具体的に、左右のころ４間に位置する外輪２の内周面には、環状の突部８ｄを有するつば８が形成され、左右のころ４の軸方向外側に位置する外輪２の内周面には、つば輪９がそれぞれ取り付けられている。 Next, as a second modification of the present embodiment, as shown in FIG. 10, the double row roller bearing may have a brim 8 and a brim ring 9 provided on the outer ring 2 side. Specifically, a brim 8 having an annular protrusion 8d is formed on the inner peripheral surface of the outer ring 2 located between the left and right rollers 4, and the inner circumference of the outer ring 2 located outside the left and right rollers 4 in the axial direction. A brim ring 9 is attached to each of the surfaces.

また、本実施形態の第３変形例として、図１１に示すように、図１０に示す第２変形例の複列ころ軸受に対して、内輪３の外周面の一端部（図１１中左端部）に小つば１０が形成されてもよい。小つば１０の外径は、環状板５の内径より小さく、ころ４の軸方向外側の端面４ｗから離間している。この構造は、例えば、圧延機の圧延ロール支持用のころ軸受のように、ころ軸受の取り外しを考慮し、ころ軸受からころが外れにくい構造である。なお、小つば１０は、ころ軸受の用途に応じて位置を適切に選択して設けることができる。例えば、小つば１０は、図９において、外輪２の内周面の一端部に設けてもよいし、図２において、外輪２の内周面の一端部に設けてもよいし、図５において、内輪３の外周面の一端部に設けてもよい。
その他の構成及び作用効果については、上記第１又は第２実施形態と同様である。 Further, as a third modification of the present embodiment, as shown in FIG. 11, one end of the outer peripheral surface of the inner ring 3 (the left end in FIG. 11) with respect to the double row roller bearing of the second modification shown in FIG. ) May have a small brim 10. The outer diameter of the small brim 10 is smaller than the inner diameter of the annular plate 5 and is separated from the axially outer end surface 4w of the roller 4. This structure is a structure in which the rollers are not easily removed from the roller bearings in consideration of the removal of the roller bearings, such as a roller bearing for supporting a rolling roll of a rolling mill. The small brim 10 can be provided by appropriately selecting the position according to the use of the roller bearing. For example, the small brim 10 may be provided at one end of the inner peripheral surface of the outer ring 2 in FIG. 9, or may be provided at one end of the inner peripheral surface of the outer ring 2 in FIG. , May be provided at one end of the outer peripheral surface of the inner ring 3.
Other configurations and effects are the same as those in the first or second embodiment.

（第４実施形態）
次に、図１２〜図１７を参照して、本発明に係るころ軸受の第４実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (Fourth Embodiment)
Next, a fourth embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 12 to 17. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態では、図１２に示すように、ころ４の一対の軸部４ｄの端面にねじ穴４ｈが形成され、ねじ穴４ｈにボルト１３が取り付けられる。そして、ボルト１３の頭部となるフランジ１３ａにより環状板５の軸部４ｄからの脱落が防止される。また、ねじ穴４ｈは、ころ４の軸心ＣＬの位置に形成されている。 In the present embodiment, as shown in FIG. 12, screw holes 4h are formed on the end faces of the pair of shaft portions 4d of the rollers 4, and bolts 13 are attached to the screw holes 4h. Then, the flange 13a, which is the head of the bolt 13, prevents the annular plate 5 from falling off from the shaft portion 4d. Further, the screw hole 4h is formed at the position of the axial center CL of the roller 4.

本実施形態によれば、ボルト１３に設けられたフランジ１３ａにより、ころ軸受１の分解時及び組立時などにおいて、一対の環状板５と複数のころ４とを同時に引き抜いたり、吊り上げたりすることができ、分解性及び組立性、即ち、メンテナンス性を向上することができる。なお、ころ軸受１の稼動時における環状板５の脱落を防止する役割は、つば６の突部６ｄ及びつば輪７の突部７ｄが果たしている。 According to the present embodiment, the flange 13a provided on the bolt 13 allows the pair of annular plates 5 and the plurality of rollers 4 to be pulled out or lifted at the same time when the roller bearing 1 is disassembled or assembled. It is possible to improve disintegration and assembling property, that is, maintainability. The protrusion 6d of the brim 6 and the protrusion 7d of the brim ring 7 play a role of preventing the annular plate 5 from falling off during the operation of the roller bearing 1.

次に、本実施形態の第１変形例として、図１３に示すように、ボルト１３が取り付けられたころ４は、内輪３の左右両側につば輪７を取り付けた構造にも適用できる。 Next, as a first modification of the present embodiment, as shown in FIG. 13, the roller 4 to which the bolt 13 is attached can also be applied to a structure in which the brim rings 7 are attached to the left and right sides of the inner ring 3.

また、本実施形態の第２変形例として、図１４に示すように、つば６及びつば輪７が突部６ｄ，７ｄを有しない構造としてもよい。本変形例における、フランジ１３ａを有するボルト１３は、ころ軸受１の稼動時において環状板５の脱落を防止する役割を果たすと同時に、ころ軸受１の分解時及び組立時などにおいて環状板５ところ４とを同時に引き抜いたり、吊り上げたりするための役割も果たしている。 Further, as a second modification of the present embodiment, as shown in FIG. 14, the brim 6 and the brim ring 7 may have a structure having no protrusions 6d and 7d. In this modification, the bolt 13 having the flange 13a plays a role of preventing the annular plate 5 from falling off when the roller bearing 1 is in operation, and at the same time, the annular plate 5 and 4 are used when the roller bearing 1 is disassembled and assembled. It also plays a role of pulling out and lifting at the same time.

また、本実施形態の第３変形例として、図１５に示すように、内輪３の左右両側につば６を有し、つば６が突部６ｄを有しない構造としてもよい。本変形例においても、フランジ１３ａを有するボルト１３は、ころ軸受１の稼動時において環状板５の脱落を防止する役割を果たす。また、本変形例は、つば輪７が設けられていないため、ころ軸受１の分解時及び組立時などにおいて環状板５ところ４とを同時に引き抜いたり、吊り上げたりする必要のないときに使用してもよい構造である。 Further, as a third modification of the present embodiment, as shown in FIG. 15, a structure may be configured in which the inner ring 3 has brims 6 on both the left and right sides, and the brims 6 do not have the protrusions 6d. Also in this modification, the bolt 13 having the flange 13a plays a role of preventing the annular plate 5 from falling off during the operation of the roller bearing 1. Further, in this modification, since the brim ring 7 is not provided, it is used when it is not necessary to simultaneously pull out or lift the annular plate 5 and 4 at the time of disassembling and assembling the roller bearing 1. It is also a good structure.

また、本実施形態の第４変形例として、図１６に示すように、ころ４の両端面４ｗと軸部４ｄとの間に新たな段部４ｅを設けてもよい。したがって、環状板５は、段部４ｅとフランジ１３ａによって軸方向位置を規制されている。また、本変形例においても、つば６及びつば輪７に突部６ｄ，７ｄを有しない構造である。本変形例によれば、ころ４に新たな段部４ｅ（（環状板５の外径−環状板５の内径）／２＞段部４ｅの直径）を設けるため、ころ４と環状板５とのすべり速度を小さくすることができ、これにより、摩擦による発熱や環状板５の摩耗（ころ４よりも環状板５の方が軟らかい場合）を低減させることができる場合がある。 Further, as a fourth modification of the present embodiment, as shown in FIG. 16, a new step portion 4e may be provided between both end surfaces 4w of the roller 4 and the shaft portion 4d. Therefore, the axial position of the annular plate 5 is regulated by the step portion 4e and the flange 13a. Further, also in this modification, the structure is such that the brim 6 and the brim ring 7 do not have protrusions 6d and 7d. According to this modification, the rollers 4 and the annular plate 5 are provided with a new step portion 4e ((outer diameter of the annular plate 5-inner diameter of the annular plate 5) / 2> diameter of the step portion 4e). The sliding speed can be reduced, which may reduce heat generation due to friction and wear of the annular plate 5 (when the annular plate 5 is softer than the rollers 4).

また、本実施形態の第５変形例として、図１７に示すように、つば６及びつば輪７の突部６ｄ，７ｄを環状板５の軸方向内側面ところ４の両端面４ｗとの間に形成してもよい。この場合、環状板５は、突部６ｄ、７ｄとフランジ１３ａによって軸方向位置を規制されている。本変形例は、例えば、ころ４の両端面４ｗと環状板５とを接触させたくない場合や、第４変形例のように、ころ４に新たな段部４ｅを設けられない場合の対応策の１つである。 Further, as a fifth modification of the present embodiment, as shown in FIG. 17, the protrusions 6d and 7d of the brim 6 and the brim ring 7 are placed between the both end faces 4w of the axial inner side surface portion 4 of the annular plate 5. It may be formed. In this case, the position of the annular plate 5 in the axial direction is regulated by the protrusions 6d and 7d and the flange 13a. In this modification, for example, when it is not desired to bring both end surfaces 4w of the roller 4 into contact with the annular plate 5, or when a new step portion 4e cannot be provided on the roller 4 as in the fourth modification, a countermeasure is taken. It is one of.

なお、該変形例は、内輪３の左右両側につば６を有する構造であってもよい。また、本変形例は、突部６ｄ，７ｄを環状板５の軸方向内側面ところ４の両端面４ｗとの間に形成しているため、ころ軸受１の分解時及び組立時などにおいて環状板５ところ４とを同時に引き抜いたり、吊り上げたりする必要のないときに使用してもよい構造である。
その他の構成及び作用効果については、上記第１実施形態と同様である。 The modified example may have a structure having brims 6 on both the left and right sides of the inner ring 3. Further, in this modification, since the protrusions 6d and 7d are formed between the axial inner side surfaces of the annular plate 5 and both end surfaces 4w of the annular plate 5, the annular plate is formed when the roller bearing 1 is disassembled or assembled. It is a structure that may be used when it is not necessary to pull out or lift the 5 and 4 at the same time.
Other configurations and effects are the same as those in the first embodiment.

（第５実施形態）
次に、図１８〜２２を参照して、本発明に係るころ軸受の第５実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (Fifth Embodiment)
Next, a fifth embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 18 to 22. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態では、図１８に示すように、一対の環状板５の内周面の軸方向内端部に突部５ｅをそれぞれ形成すると共に、つば６及びつば輪７の外周面の軸方向内端部に、突部５ｅを回転可能に嵌合させる段部６ｅ，７ｅをそれぞれ形成する。そして、本実施形態では、一対の環状板５の突部５ｅとつば６及びつば輪７の段部６ｅ，７ｅとの接触により、環状板５の脱落が防止されている。 In the present embodiment, as shown in FIG. 18, the protrusions 5e are formed at the axial inner ends of the inner peripheral surfaces of the pair of annular plates 5, and the inner peripheral surfaces of the brim 6 and the brim ring 7 are formed in the axial direction. Step portions 6e and 7e for rotatably fitting the protrusions 5e are formed at the end portions, respectively. Then, in the present embodiment, the annular plate 5 is prevented from falling off by the contact between the protrusion 5e of the pair of annular plates 5 and the step portions 6e and 7e of the brim 6 and the brim ring 7.

また、環状板５をころ案内で使用する場合、図１９Ａに示すように、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間Δ１は、つば６の外周面と環状板５の内周面との間の隙間Δ２（つば輪７の外周面と環状板５の内周面との間の隙間）より小さく設定されている。また、環状板５の突部５ｅの軸方向外端面５ｅ１とつば６（つば輪７）の段部６ｅ（段部７ｅ）の径方向に沿う垂直面６１は接触可能であり、環状板５の突部５ｅの内周面とつば６（つば輪７）の段部６ｅ（段部７ｅ）の外周面は非接触である。 Further, when the annular plate 5 is used for roller guidance, as shown in FIG. 19A, the gap Δ1 between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5 is a brim. It is set to be smaller than the gap Δ2 (the gap between the outer peripheral surface of the brim ring 7 and the inner peripheral surface of the annular plate 5) between the outer peripheral surface of 6 and the inner peripheral surface of the annular plate 5. Further, the axial outer end surface 5e1 of the protrusion 5e of the annular plate 5 and the vertical surface 61 along the radial direction of the step portion 6e (step portion 7e) of the brim 6 (brimmed ring 7) are in contact with each other, and the annular plate 5 has contact. The inner peripheral surface of the protrusion 5e and the outer peripheral surface of the step portion 6e (step portion 7e) of the brim 6 (brimmed ring 7) are not in contact with each other.

また、環状板５を内輪案内で使用する場合、図１９Ｂに示すように、つば６の外周面と環状板５の内周面との間の隙間Δ２（つば輪７の外周面と環状板５の内周面との間の隙間）は、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間Δ１より小さく設定されている。また、環状板５の突部５ｅの軸方向外端面５ｅ１とつば６（つば輪７）の段部６ｅ（段部７ｅ）の径方向に沿う垂直面６１は接触可能であり、環状板５の突部５ｅの内周面とつば６（つば輪７）の段部６ｅ（段部７ｅ）の外周面は非接触である。なお、ころ案内、内輪案内は、機械や設備等の使用条件等によって決められる。 Further, when the annular plate 5 is used for the inner ring guide, as shown in FIG. 19B, the gap Δ2 between the outer peripheral surface of the brim 6 and the inner peripheral surface of the annular plate 5 (the outer peripheral surface of the brim ring 7 and the annular plate 5). The gap between the inner peripheral surface and the inner peripheral surface of the roller 4) is set to be smaller than the gap Δ1 between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5. Further, the axial outer end surface 5e1 of the protrusion 5e of the annular plate 5 and the vertical surface 61 along the radial direction of the step portion 6e (step portion 7e) of the brim 6 (brimmed ring 7) are in contact with each other, and the annular plate 5 has contact. The inner peripheral surface of the protrusion 5e and the outer peripheral surface of the step portion 6e (step portion 7e) of the brim 6 (brimmed ring 7) are not in contact with each other. The roller guidance and inner ring guidance are determined by the usage conditions of machines and equipment.

また、本実施形態の第１変形例として、図２０に示すように、外輪２は、図１８に示す内輪３の外周面のつば輪７と径方向に対向する部分につば８を形成してもよい。もちろん、外輪２は、図１８に示す内輪３の外周面のつば６と径方向に対向する部分につば８を形成してもよい。 Further, as a first modification of the present embodiment, as shown in FIG. 20, the outer ring 2 has a brim 8 formed on a portion of the outer peripheral surface of the inner ring 3 shown in FIG. 18 that faces the brim ring 7 in the radial direction. May be good. Of course, the outer ring 2 may have a brim 8 formed on a portion of the outer peripheral surface of the inner ring 3 shown in FIG. 18 that faces the brim 6 in the radial direction.

また、本実施形態の第２変形例として、図２１に示すように、一対の環状板５の突部５ｅにより、環状板５の脱落を防止する構造は、第２実施形態に適用されてもよい。即ち、一対の環状板５の外周面の軸方向内端部に突部５ｅをそれぞれ形成すると共に、つば８（つば輪９）の内周面の軸方向内端部に、突部５ｅを回転可能に嵌合させる段部８ｅ，９ｅ（図２２参照）をそれぞれ形成する。 Further, as a second modification of the present embodiment, as shown in FIG. 21, a structure for preventing the annular plate 5 from falling off by the protrusions 5e of the pair of annular plates 5 may be applied to the second embodiment. Good. That is, the protrusions 5e are formed at the axial inner ends of the outer peripheral surfaces of the pair of annular plates 5, and the protrusions 5e are rotated at the axial inner ends of the inner peripheral surfaces of the brim 8 (brimmed ring 9). Step portions 8e and 9e (see FIG. 22) to be fitted to each other are formed.

この場合も、環状板５を外輪案内で使用する場合、図２１に示すように、つば８の内周面と環状板５の外周面との間の隙間Δ３（つば輪９の内周面と環状板５の外周面との間の隙間）は、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間Δ１より小さく設定されている。また、環状板５の突部５ｅの軸方向外端面５ｅ１とつば８（つば輪９）の段部８ｅ（段部９ｅ）の径方向に沿う垂直面８１は接触可能であり、環状板５の突部５ｅの外周面とつば８（つば輪９）の段部８ｅ（段部９ｅ）の内周面は非接触である。なお、環状板５をころ案内で使用する場合、ころ４の軸部４ｄの外周面と環状板５の貫通穴５ａの内周面との間の隙間Δ１は、つば８の内周面と環状板５の外周面との間の隙間Δ３より小さく設定されている。 Also in this case, when the annular plate 5 is used for the outer ring guide, as shown in FIG. 21, the gap Δ3 between the inner peripheral surface of the brim 8 and the outer peripheral surface of the annular plate 5 (with the inner peripheral surface of the brim ring 9). The gap between the outer peripheral surface of the annular plate 5) is set to be smaller than the gap Δ1 between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5. Further, the axial outer end surface 5e1 of the protrusion 5e of the annular plate 5 and the vertical surface 81 along the radial direction of the step portion 8e (step portion 9e) of the brim 8 (brimmed ring 9) are in contact with each other, and the annular plate 5 has contact with each other. The outer peripheral surface of the protrusion 5e and the inner peripheral surface of the stepped portion 8e (stepped portion 9e) of the brim 8 (brimmed ring 9) are not in contact with each other. When the annular plate 5 is used for roller guidance, the gap Δ1 between the outer peripheral surface of the shaft portion 4d of the roller 4 and the inner peripheral surface of the through hole 5a of the annular plate 5 is annular with the inner peripheral surface of the brim 8. The gap between the plate 5 and the outer peripheral surface is set to be smaller than Δ3.

また、本実施形態の第３変形例として、図２２に示すように、つば８及びつば輪９を外輪２側に設けると共に、突部５ｅを環状板５の外周面の軸方向内端部に形成し、さらに、内輪３は、図２２に示す外輪２のつば輪９と径方向に対向する部分につば６を形成してもよい。もちろん、内輪３は、図２２に示す外輪２のつば８と径方向に対向する部分につば６を形成してもよい。
その他の構成及び作用効果については、上記第１実施形態と同様である。 Further, as a third modification of the present embodiment, as shown in FIG. 22, the brim 8 and the brim ring 9 are provided on the outer ring 2 side, and the protrusion 5e is provided on the inner end portion in the axial direction of the outer peripheral surface of the annular plate 5. Further, the inner ring 3 may form a brim 6 at a portion of the outer ring 2 shown in FIG. 22 that is radially opposed to the brim ring 9. Of course, the inner ring 3 may form a brim 6 at a portion radially opposed to the brim 8 of the outer ring 2 shown in FIG.
Other configurations and effects are the same as those in the first embodiment.

（第６実施形態）
次に、図２３を参照して、本発明に係るころ軸受の第６実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (Sixth Embodiment)
Next, a sixth embodiment of the roller bearing according to the present invention will be described with reference to FIG. 23. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態では、図２３に示すように、つば輪７が内輪３の外周面に外嵌する構造（図２参照）ではなく、つば輪７が内輪３の内周面に内嵌するインロー構造になっている。具体的には、内輪３の内周面の軸方向外端部に凹状の段部３ｆを形成すると共に、つば輪７の軸方向内側面の内径側端部に段部３ｆに内嵌する突部７ｆを形成する。
その他の構成及び作用効果については、上記第１実施形態と同様である。 In the present embodiment, as shown in FIG. 23, the brim ring 7 is not fitted on the outer peripheral surface of the inner ring 3 (see FIG. 2), but is an inlay structure in which the brim ring 7 is fitted on the inner peripheral surface of the inner ring 3. It has become. Specifically, a concave step portion 3f is formed at the axial outer end portion of the inner peripheral surface of the inner ring 3, and a protrusion fitted into the step portion 3f at the inner diameter side end portion of the axial inner side surface of the brim ring 7. Part 7f is formed.
Other configurations and effects are the same as those in the first embodiment.

（第７実施形態）
次に、図２４Ａ及び図２４Ｂを参照して、本発明に係るころ軸受の第７実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (7th Embodiment)
Next, a seventh embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 24A and 24B. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態では、図２４Ａに示すように、図２３における内輪３とつば輪７のインロー構造を取り去って、固定手段（六角穴付ボルト等）１１によりつば輪７を内輪３に取り付けている。この場合、図２４Ｂに示すように、内輪３及びつば輪７に互いに連通するピン挿入穴３ｈ，７ｈを形成し、そのピン挿入穴３ｈ，７ｈに位置決めピンＰを挿入して、内輪３とつば輪７の中心合わせを容易且つ確実に行っている。なお、位置決めピンＰは、２ヶ所設けられていればよいが、３ヶ所以上設けられていてもよい。
その他の構成及び作用効果については、上記第１実施形態と同様である。 In the present embodiment, as shown in FIG. 24A, the in-row structure of the inner ring 3 and the brim ring 7 in FIG. 23 is removed, and the brim ring 7 is attached to the inner ring 3 by a fixing means (hexagon socket head cap screw or the like) 11. In this case, as shown in FIG. 24B, pin insertion holes 3h and 7h communicating with each other are formed in the inner ring 3 and the brim ring 7, and the positioning pin P is inserted into the pin insertion holes 3h and 7h to form the inner ring 3 and the brim. The centering of the ring 7 is easily and surely performed. The positioning pins P may be provided at two locations, but may be provided at three or more locations.
Other configurations and effects are the same as those in the first embodiment.

（第８実施形態）
次に、図２５及び図２６を参照して、本発明に係るころ軸受の第８実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (8th Embodiment)
Next, an eighth embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 25 and 26. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態は、図２５及び図２６に示すように、ころ４を１本以上（本実施形態では１本）抜き取り、空いたスペースに一対の環状板５を軸方向に連結する柱部１４を配置した構造である。柱部１４は、ころ４と接触することなくころ４と平行に配置され、その両端が環状板５に固定手段（ねじ、溶接等）により固定されている。また、柱部１４は、周方向に９０度の間隔で配置されている。なお、本実施形態は、上記したボルト１３を使用できない場合、且つ環状板５ところ４とを同時に引き抜いたり、吊り上げたりしたい場合に有効である。 In this embodiment, as shown in FIGS. 25 and 26, one or more rollers 4 (one in this embodiment) are extracted, and a pillar portion 14 for axially connecting a pair of annular plates 5 to an empty space is provided. It is an arranged structure. The pillar portion 14 is arranged in parallel with the roller 4 without contacting the roller 4, and both ends thereof are fixed to the annular plate 5 by fixing means (screws, welding, etc.). Further, the pillar portions 14 are arranged at intervals of 90 degrees in the circumferential direction. It should be noted that this embodiment is effective when the above-mentioned bolt 13 cannot be used and when it is desired to simultaneously pull out or lift the annular plate 5 and 4.

本実施形態の場合、柱部１４の固定手段の使用により、製造コストが増加することとなるが、稼動時に生じる側板間の周方向のねじれを考慮した上で、環状板５ところ４とを同時に引き抜いたり、吊り上げたりするのに充分な強度を有していればよく、ピン形保持器（特開昭５３−０００３５８号）のように柱部（ピン）へのころの衝突を考慮しなくてよいので、柱部１４の数（固定手段の数）が少なくて済み、製造コストの増加を抑えることができる。なお、稼動時に生じる側板間の周方向のねじれを考慮した上で、引き抜いたり、吊り上げたりするのに充分な強度を有していれば、柱部１４の数は２以上の任意の数から選ぶことができるが、負荷容量の観点から柱部１４の数は少ない方が好ましい。
その他の構成及び作用効果については、上記第１実施形態と同様である。 In the case of the present embodiment, the manufacturing cost increases due to the use of the fixing means of the pillar portion 14, but the annular plates 5 and 4 are simultaneously used in consideration of the circumferential twist between the side plates that occurs during operation. It suffices to have sufficient strength to pull out or lift, and it is not necessary to consider the collision of the rollers with the pillars (pins) as in the pin-shaped cage (Japanese Patent Laid-Open No. 53-000358). Therefore, the number of pillars 14 (the number of fixing means) can be reduced, and an increase in manufacturing cost can be suppressed. The number of pillars 14 should be selected from any number of 2 or more as long as it has sufficient strength to be pulled out or lifted in consideration of the twist in the circumferential direction between the side plates that occurs during operation. However, it is preferable that the number of column portions 14 is small from the viewpoint of load capacity.
Other configurations and effects are the same as those in the first embodiment.

（第９実施形態）
次に、図２７を参照して、本発明に係るころ軸受の第９実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (9th Embodiment)
Next, a ninth embodiment of the roller bearing according to the present invention will be described with reference to FIG. 27. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態では、図２７に示すように、ころ４の一対の軸部４ｄを、軸方向外側に向かうに従って縮径するテーパー形状にしている。本実施形態によれば、軸部４ｄの形状を軸方向外側に向かうに従って縮径するテーパー形状にしているため、ころ４の両端面４ｗと環状板５が接触せず、摩擦による発熱や環状板５の摩耗を低減することができる。しかしながら、テーパーの角度が大きくなればなるほど（軸部４ｄの形状が軸方向外側に向かうに従って細くなればなるほど）突部６ｄ、７ｄの軸方向内側面と環状板５の軸方向外側面との摩擦による発熱が大きくなるので、テーパーの角度は小さいほうがよい。なお、軸部４ｄの形状や段部４ｅ（図１６参照）は、使用条件などによって選択してよい。
その他の構成及び作用効果については、上記第１実施形態と同様である。 In the present embodiment, as shown in FIG. 27, the pair of shaft portions 4d of the rollers 4 have a tapered shape in which the diameter is reduced toward the outside in the axial direction. According to the present embodiment, since the shape of the shaft portion 4d is tapered so as to reduce the diameter toward the outside in the axial direction, both end surfaces 4w of the roller 4 and the annular plate 5 do not come into contact with each other, and heat is generated due to friction or the annular plate. The wear of 5 can be reduced. However, the larger the taper angle (the smaller the shape of the shaft portion 4d toward the outer side in the axial direction), the more the friction between the inner side surfaces in the axial direction of the protrusions 6d and 7d and the outer surface in the axial direction of the annular plate 5. The taper angle should be small because the heat generated by the taper will be large. The shape of the shaft portion 4d and the step portion 4e (see FIG. 16) may be selected depending on usage conditions and the like.
Other configurations and effects are the same as those in the first embodiment.

（第１０実施形態）
次に、図２８及び図２９を参照して、本発明に係るころ軸受の第１０実施形態について説明する。なお、上記第１実施形態と同一又は同等部分については、図面に同一符号を付してその説明を省略或いは簡略化する。 (10th Embodiment)
Next, a tenth embodiment of the roller bearing according to the present invention will be described with reference to FIGS. 28 and 29. The same or equivalent parts as those in the first embodiment are designated by the same reference numerals in the drawings, and the description thereof will be omitted or simplified.

本実施形態は、図２８に示すように、ころ４の軸部４ｄを別部品とし、この軸部４ｄをねじ等の固定手段によりころ４の両端面４ｗに取り付けた構造である。 As shown in FIG. 28, the present embodiment has a structure in which the shaft portion 4d of the roller 4 is a separate part, and the shaft portion 4d is attached to both end faces 4w of the roller 4 by a fixing means such as a screw.

次に、本実施形態の変形例として、図２９に示すように、別部品にした軸部４ｄの軸方向外端部にフランジ４ｆを形成してもよい。 Next, as a modification of the present embodiment, as shown in FIG. 29, a flange 4f may be formed at the outer end portion in the axial direction of the shaft portion 4d which is a separate component.

本変形例によれば、軸部４ｄの軸方向外端部に設けられたフランジ４ｆにより、ころ軸受１の分解時及び組立時などにおいて、一対の環状板５と複数のころ４とを同時に引き抜いたり、吊り上げたりすることができ、分解性及び組立性、メンテナンス性を向上することができる。なお、ころ軸受１の稼動時における環状板５の脱落を防止する役割は、つば６の突部６ｄ及びつば輪７の突部７ｄが果たしている。 According to this modification, the pair of annular plates 5 and the plurality of rollers 4 are simultaneously pulled out by the flange 4f provided at the axially outer end of the shaft portion 4d when the roller bearing 1 is disassembled or assembled. It can be lifted or lifted, and disassembly, assembling, and maintainability can be improved. The protrusion 6d of the brim 6 and the protrusion 7d of the brim ring 7 play a role of preventing the annular plate 5 from falling off during the operation of the roller bearing 1.

また、つば６及びつば輪７が突部６ｄ，７ｄを有しない構造とした場合、軸部４ｄのフランジ４ｆは、ころ軸受１の稼動時において環状板５の脱落を防止する役割を果たすと同時に、ころ軸受１の分解時及び組立時などにおいて環状板５ところ４とを同時に引き抜いたり、吊り上げたりするための役割も果たしている。
その他の構成及び作用効果については、上記第１実施形態と同様である。 Further, when the flange 6 and the brim ring 7 have a structure having no protrusions 6d and 7d, the flange 4f of the shaft portion 4d plays a role of preventing the annular plate 5 from falling off during the operation of the roller bearing 1. It also plays a role of simultaneously pulling out or lifting the annular plate 5 and 4 at the time of disassembling and assembling the roller bearing 1.
Other configurations and effects are the same as those in the first embodiment.

なお、本発明は、上記各実施形態に例示したものに限定されるものではなく、本発明の要旨を逸脱しない範囲において適宜変更可能である。
例えば、本実施形態では、本発明を単列又は複列の円筒ころ軸受に適用した場合を例示したが、これに限定されず、図３０に示す単列の円すいころ軸受、図３１に示す複列の円すいころ軸受、図３２に示す自動調心ころ軸受、四列の円筒ころ軸受、及び四列の円すいころ軸受に本発明を適用してもよい。
さらに、例えば、図１５に示すつばを外輪に設けてもよい（このとき内輪は、つばを有しない）。
また、本発明のころの軸部と回転可能に嵌合する穴部は、上記実施形態の貫通穴に限定されず、有底穴であってもよい。
また、つば輪が周辺の部品等によって内輪（内輪につば輪を設けている時）や外輪（外輪につば輪を設けている時）に対して正しく固定されているような場合は、固定手段（六角穴付ボルト等）１１や位置決めピンＰを設けなくてもよい。 The present invention is not limited to those exemplified in each of the above embodiments, and can be appropriately modified without departing from the gist of the present invention.
For example, in the present embodiment, the case where the present invention is applied to a single row or double row cylindrical roller bearing is illustrated, but the present invention is not limited to this, and the single row tapered roller bearing shown in FIG. 30 and the double row shown in FIG. 31 are shown. The present invention may be applied to a row of tapered roller bearings, a self-aligning roller bearing shown in FIG. 32, a four-row cylindrical roller bearing, and a four-row tapered roller bearing.
Further, for example, the brim shown in FIG. 15 may be provided on the outer ring (at this time, the inner ring does not have a brim).
Further, the hole portion that rotatably fits with the shaft portion of the roller of the present invention is not limited to the through hole of the above embodiment, and may be a bottomed hole.
If the brim ring is correctly fixed to the inner ring (when the brim ring is provided on the inner ring) or the outer ring (when the brim ring is provided on the outer ring) by peripheral parts, etc., the fixing means (Hexagonal hole bolt, etc.) 11 and the positioning pin P may not be provided.

１ころ軸受
２外輪
２ａ外輪軌道面
３内輪
３ａ内輪軌道面
６、８つば
６ｄ、８ｄ突部
７、９つば輪
７ｄ、９ｄ突部
７ｇ段部
４ころ
４ｗ両端面（端面）
４ｄ軸部
５環状板（保持器）
５ａ貫通穴（穴部）
１１固定手段（六角穴付ボルト等）
ＣＬ軸心 1 Roller bearing 2 Outer ring 2a Outer ring raceway surface 3 Inner ring 3a Inner ring raceway surface 6,8 Brim 6d, 8d Projection 7,9 Brim ring 7d, 9d Projection 7g Step 4 Roll 4w Both end faces (end faces)
4d shaft part 5 annular plate (retainer)
5a Through hole (hole)
11 Fixing means (hexagon socket head cap screw, etc.)
CL axis

Claims

It includes an outer ring having an outer ring raceway surface on the inner peripheral surface, an inner ring having an inner ring raceway surface on the outer peripheral surface, and a plurality of rollers rotatably arranged between the outer ring raceway surface and the inner ring raceway surface. Roller bearing
A pair of shaft portions are formed at the axial center positions of both end faces in the axial direction of the plurality of rollers.
Rollers arranged on both sides in the axial direction of the plurality of rollers, each having a hole portion for fitting with the pair of shaft portions of the plurality of rollers, and provided with a pair of annular plates for rotatably supporting the plurality of rollers. bearing.

The roller bearing according to claim 1, wherein the pair of annular plates are separate bodies.

A brim and a brim ring provided on the outer ring or the inner ring and regulating the axial positions of the plurality of rollers are provided.
The roller bearing according to claim 2, wherein the brim and the brim ring are provided with protrusions that face the axially outer surface of the annular plate and regulate the axial position of the annular plate.

The roller bearing according to claim 3, wherein the brim ring is assembled to the outer ring or the inner ring by an in-row structure and fixed by a fixing means.

The hole portion of the annular plate is a through hole.
The roller bearing according to any one of claims 1 to 4, wherein a flange facing the axial outer surface of the annular plate is attached to the axial outer end portion of the shaft portion.