WO2017110907A1 - Roller bearing - Google Patents
Roller bearing Download PDFInfo
- Publication number
- WO2017110907A1 WO2017110907A1 PCT/JP2016/088176 JP2016088176W WO2017110907A1 WO 2017110907 A1 WO2017110907 A1 WO 2017110907A1 JP 2016088176 W JP2016088176 W JP 2016088176W WO 2017110907 A1 WO2017110907 A1 WO 2017110907A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- coupling member
- ring
- race
- holes
- axial direction
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/28—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with two or more rows of rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C43/00—Assembling bearings
- F16C43/04—Assembling rolling-contact bearings
Definitions
- the same coupling member can be used even if the bearing size is different as long as it is another bearing provided with a radially thick bearing ring capable of forming a storage portion corresponding to the coupling member. Therefore, it is not necessary to prepare a coupling member for each bearing size.
- the holes are formed by a general drilling process that opens in the axial direction from the side surface of each track ring, and the space opens in the radial direction from the inner periphery or outer periphery of each track ring. It can be formed by a general drilling process. That is, since it becomes unnecessary to form the storage portion in the raceway by machining using a special tool, machining of the raceway is facilitated.
- the storage portions 21 and 22 do not exist on the extension of the contact direction between the raceway surface 9 and the rolling element 3, and are formed only within a range continuous with the collar 10 in the radial direction. This is to avoid a decrease in rigidity of the raceway surface 9 when a bearing load is applied.
Abstract
The present invention both yields a linking means that allows races to be easily processed and assembled, and prevents the coupling member from coming loose, it being unnecessary for linking members used to fasten two races to be prepared for each bearing size. The coupling means comprises a first storage part (21) opening axially in a side surface (11) of a first race (7), a second storage part (22) opening in a side surface (11) of a second race (8) so as to axially face the first storage part (21), and a coupling member (23) having a first head part (28) that can be axially press-fitted into the first storage part (21) and a second head part (29) that can be axially press-fitted into the second storage part (22). The storage parts (21, 22) are formed, in respective manner, using axially opening holes (24, 25), and spaces (26, 27) opening diametrically so as to intersect the holes (24, 25).
Description
この発明は、複列（二列以上）の転がり軸受に関する。
This invention relates to a double row (two or more rows) rolling bearing.
従来、複列の転がり軸受においては、一列以上の軌道面をもった軌道輪同士を締結することによって、複列の軌道面をもった内輪又は外輪に組み立てるものがある。この種の転がり軸受は、軸受の装置への取付け、取り外し時に、当該内輪又は外輪を分離せずに一体的に取り扱えるので、取扱い性に優れる。
Conventionally, some double-row rolling bearings are assembled into inner rings or outer rings having double-row raceways by fastening raceways having one or more raceways. Since this type of rolling bearing can be handled integrally without separating the inner ring or the outer ring when the bearing is attached to or removed from the apparatus, it is excellent in handling.
例えば、クレーンシーブ用軸受において、薄い金属製の締結環を内径面に沿ってローリングプレス加工で加締めすることにより、二個の軌道輪を締結するものがある。この結合手段には特殊な冶具が必要となると共に、サイズに合わせた締結環が必要となり、工程の複雑化やコストアップにつながる。
For example, in a crane sheave bearing, there are some that fasten two race rings by caulking a thin metal fastening ring along the inner diameter surface by rolling press processing. A special jig is required for this coupling means, and a fastening ring suitable for the size is required, which leads to a complicated process and an increased cost.
このような問題に対して、クリップ状の結合部材を用いた結合手段が提案されている（下記特許文献１）。
For such a problem, a coupling means using a clip-shaped coupling member has been proposed (Patent Document 1 below).
また、環状の本体部の軸方向両側において係止片とスリットとを周方向に交互に形成した締結環を用いた結合手段も提案されている（下記特許文献２）。
Also, a coupling means using a fastening ring in which locking pieces and slits are alternately formed in the circumferential direction on both axial sides of the annular main body has been proposed (Patent Document 2 below).
また、軌道輪の端面に内部に向かって広がった溝を形成し、溝に弾性体を挿入する結合手段も提案されている（下記特許文献３）。
Also, a coupling means has been proposed in which a groove extending toward the inside is formed on the end face of the race, and an elastic body is inserted into the groove (Patent Document 3 below).
しかしながら、特許文献１のような結合手段は、クリップ状の結合部材の締め付けを厳密に管理しなければ、結合部材の脱落に至る懸念がある。
However, there is a concern that the coupling means as in Patent Document 1 may cause the coupling member to drop off unless the tightening of the clip-shaped coupling member is strictly managed.
特許文献２のような結合手段は、軸受サイズに応じて軌道輪の周長が異なるので、サイズごとに締結環を用意しなければならない問題がある。
The coupling means such as Patent Document 2 has a problem that the fastening ring must be prepared for each size since the circumference of the raceway ring varies depending on the bearing size.
特許文献３のような結合手段は、軌道輪の端面に形成する溝が特殊な断面形状をもつため、専用の工具を要する問題がある。
The coupling means as in Patent Document 3 has a problem that a special tool is required because the groove formed on the end face of the raceway has a special cross-sectional shape.
そこで、この発明が解決しようとする課題は、二個の軌道輪の締結に用いる結合部材を軸受サイズごとに用意することが不要であって軌道輪の加工・組立作業が容易な結合手段にすると共に、結合部材の脱落を防止することである。
Therefore, the problem to be solved by the present invention is to provide a coupling means that makes it easy to process and assemble the bearing ring without the need to prepare a coupling member for fastening the two bearing rings for each bearing size. At the same time, it is to prevent the coupling member from falling off.
上記の課題を達成するため、この発明は、第一の軌道輪と、第二の軌道輪と、前記第一の軌道輪と前記第二の軌道輪とを締結する結合手段とを備える転がり軸受において、前記結合手段が、前記第一の軌道輪の側面で軸方向に開口している第一の格納部と、前記第一の格納部と軸方向に向き合うように前記第二の軌道輪の側面に開口している第二の格納部と、前記第一の格納部に軸方向に圧入可能な第一の頭部及び前記第二の格納部に軸方向に圧入可能な第二の頭部をもった結合部材とからなり、前記第一の格納部及び前記第二の格納部が、それぞれ軸方向に開口している穴と、当該穴と交差するように径方向に開口している空間とによって形成されている、という構成を採用したものである。
To achieve the above object, the present invention provides a rolling bearing comprising a first race ring, a second race ring, and a coupling means for fastening the first race ring and the second race ring. In the first embodiment, the coupling means includes a first storage portion that is open in an axial direction on a side surface of the first track ring, and a second storage ring that faces the first storage portion in the axial direction. A second storage portion that is open on a side surface, a first head that can be press-fit in the axial direction into the first storage portion, and a second head that can be press-fit in the axial direction into the second storage portion And a space in which the first storage portion and the second storage portion are open in the axial direction and open in the radial direction so as to intersect the holes, respectively. It is a structure that is formed by.
上記構成によれば、結合部材の第一及び第二の頭部をそれぞれ対応の第一の格納部又は第二の格納部の穴から軸方向に圧入することによって、結合部材で第一の軌道輪と第二の軌道輪を締結することが可能である。
また、二個の軌道輪が結合部材で締結されると、穴から圧入された両頭部が第一の格納部及び第二の格納部に収まるので、これら軌道輪から結合部材が脱落できない状態となる。
また、結合部材が軌道輪の側面に開口している穴から格納部に軸方向に圧入するものなので、軌道輪の周長が結合部材の配置に及ぼす影響は小さい。このため、結合部材に対応の格納部を形成可能な径方向肉厚の軌道輪を備える他軸受であれば、軸受サイズが異なっていても同じ結合部材を用いることが可能である。したがって、結合部材を軸受サイズごとに用意することが不要になる。
また、各格納部の形成に際し、穴は、各軌道輪の側面から軸方向に開口する一般的な穴開け加工で形成し、空間は、各軌道輪の内周又は外周から径方向に開口する一般的な穴開け加工で形成することが可能である。すなわち、特殊な工具を用いた加工で軌道輪に格納部を形成することが不要になるので、軌道輪の加工が容易になる。 According to the above configuration, the first track and the second head of the coupling member are respectively press-fitted in the axial direction from the corresponding first storage portion or the hole of the second storage portion. It is possible to fasten the wheel and the second race.
In addition, when the two race rings are fastened by the coupling member, both heads press-fitted from the holes are accommodated in the first storage portion and the second storage portion, so that the coupling member cannot be removed from these race rings. Become.
Further, since the coupling member is press-fitted in the axial direction from the hole opened on the side surface of the race ring in the axial direction, the influence of the circumference of the race ring on the arrangement of the coupling member is small. For this reason, the same coupling member can be used even if the bearing size is different as long as it is another bearing provided with a radially thick bearing ring capable of forming a storage portion corresponding to the coupling member. Therefore, it is not necessary to prepare a coupling member for each bearing size.
Further, when forming each storage portion, the holes are formed by a general drilling process that opens in the axial direction from the side surface of each track ring, and the space opens in the radial direction from the inner periphery or outer periphery of each track ring. It can be formed by a general drilling process. That is, since it becomes unnecessary to form the storage portion in the raceway by machining using a special tool, machining of the raceway is facilitated.
また、二個の軌道輪が結合部材で締結されると、穴から圧入された両頭部が第一の格納部及び第二の格納部に収まるので、これら軌道輪から結合部材が脱落できない状態となる。
また、結合部材が軌道輪の側面に開口している穴から格納部に軸方向に圧入するものなので、軌道輪の周長が結合部材の配置に及ぼす影響は小さい。このため、結合部材に対応の格納部を形成可能な径方向肉厚の軌道輪を備える他軸受であれば、軸受サイズが異なっていても同じ結合部材を用いることが可能である。したがって、結合部材を軸受サイズごとに用意することが不要になる。
また、各格納部の形成に際し、穴は、各軌道輪の側面から軸方向に開口する一般的な穴開け加工で形成し、空間は、各軌道輪の内周又は外周から径方向に開口する一般的な穴開け加工で形成することが可能である。すなわち、特殊な工具を用いた加工で軌道輪に格納部を形成することが不要になるので、軌道輪の加工が容易になる。 According to the above configuration, the first track and the second head of the coupling member are respectively press-fitted in the axial direction from the corresponding first storage portion or the hole of the second storage portion. It is possible to fasten the wheel and the second race.
In addition, when the two race rings are fastened by the coupling member, both heads press-fitted from the holes are accommodated in the first storage portion and the second storage portion, so that the coupling member cannot be removed from these race rings. Become.
Further, since the coupling member is press-fitted in the axial direction from the hole opened on the side surface of the race ring in the axial direction, the influence of the circumference of the race ring on the arrangement of the coupling member is small. For this reason, the same coupling member can be used even if the bearing size is different as long as it is another bearing provided with a radially thick bearing ring capable of forming a storage portion corresponding to the coupling member. Therefore, it is not necessary to prepare a coupling member for each bearing size.
Further, when forming each storage portion, the holes are formed by a general drilling process that opens in the axial direction from the side surface of each track ring, and the space opens in the radial direction from the inner periphery or outer periphery of each track ring. It can be formed by a general drilling process. That is, since it becomes unnecessary to form the storage portion in the raceway by machining using a special tool, machining of the raceway is facilitated.
このように、この発明は、上記構成の採用により、二個の軌道輪の締結に用いる結合部材を軸受サイズごとに用意することが不要であって軌道輪の加工・組立作業が容易な結合手段にすると共に、結合部材の脱落を防止することができる。
As described above, according to the present invention, by adopting the above configuration, it is not necessary to prepare a coupling member for fastening two bearing rings for each bearing size, and coupling means that facilitates the processing and assembly of the bearing rings. In addition, the coupling member can be prevented from falling off.
以下、この発明の第一実施形態に係る転がり軸受を添付図面の図１～図３に基づいて説明する。図１に示すように、この転がり軸受は、内輪１と、外輪２と、内輪１及び外輪２間で複列に介在する転動体３とを備える。この転がり軸受は、主として径方向の荷重を支持するラジアル軸受になっており、特に、クレーンシーブの支持用途に好適な総ころ形の複列円筒ころ軸受を例示している。
Hereinafter, a rolling bearing according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 3 of the accompanying drawings. As shown in FIG. 1, the rolling bearing includes an inner ring 1, an outer ring 2, and rolling elements 3 interposed between the inner ring 1 and the outer ring 2 in a double row. This rolling bearing is a radial bearing that mainly supports a load in the radial direction. In particular, a full-roller type double-row cylindrical roller bearing suitable for a crane sheave support application is illustrated.
ここで、「径方向」とは、同心に配置された内輪１及び外輪２の中心軸に直角な方向のことをいい、「総ころ形」とは、転動体間のすきまの和が転動体の直径を超えていない（すなわち、各列の転動体数を最大化している。）軸受のことをいう。以下、前述の中心軸に沿った方向のことを単に「軸方向」といい、その中心軸周りの円周方向のことを単に「周方向」という。
Here, the “radial direction” means a direction perpendicular to the central axis of the inner ring 1 and the outer ring 2 arranged concentrically, and the “full roller shape” means that the sum of the clearances between the rolling elements is a rolling element. The diameter of the bearing is not exceeded (that is, the number of rolling elements in each row is maximized). Hereinafter, the direction along the central axis is simply referred to as “axial direction”, and the circumferential direction around the central axis is simply referred to as “circumferential direction”.
外輪２は、一体に形成された環状部品からなる。外輪２は、径方向に面した軌道面４を内周に複列で有するラジアル軸受用のものとなっている。また、外輪２は、中つば５と、軸方向の外輪幅を規定する側面６とを有する。軌道面４は、円筒面状になっている。側面６は、径方向に沿った平坦面になっている。一列の転動体３を軸方向に外輪２の内方へ挿入可能とするため、外輪２の内周のうち、側面６から最寄りの軌道面４に至るまでの部分は、軌道面４以上の内径寸法に設定されている。
The outer ring 2 is composed of an annular part formed integrally. The outer ring 2 is for a radial bearing having a raceway surface 4 facing in the radial direction in a double row on the inner periphery. The outer ring 2 has a middle collar 5 and side surfaces 6 that define the outer ring width in the axial direction. The raceway surface 4 has a cylindrical surface shape. The side surface 6 is a flat surface along the radial direction. In order to allow one row of rolling elements 3 to be inserted inward of the outer ring 2 in the axial direction, the portion from the side surface 6 to the nearest raceway surface 4 in the inner circumference of the outer ring 2 has an inner diameter larger than the raceway surface 4. Set to dimensions.
内輪１は、第一の軌道輪７と，第二の軌道輪８とを締結することによって構成されている。これら軌道輪７，８は、それぞれ一体に形成された環状部品からなる。第一の軌道輪７と第二の軌道輪８は、同形になっている。これら軌道輪７，８は、それぞれ径方向に面した単列の軌道面９を外周に有するラジアル軸受用のものとなっている。また、これら軌道輪７，８は、外周の両端部に形成されたつば１０と、それぞれ軸方向の軌道輪幅を規定する側面１１を有する。軌道面９は、円筒面状になっている。側面１１は、径方向に沿った平坦面になっている。
The inner ring 1 is configured by fastening a first race ring 7 and a second race ring 8. Each of the race rings 7 and 8 is composed of an annular part formed integrally. The first race ring 7 and the second race ring 8 have the same shape. These race rings 7 and 8 are for radial bearings having a single row raceway surface 9 facing the radial direction on the outer periphery. Each of the race rings 7 and 8 has a collar 10 formed at both ends of the outer periphery, and a side surface 11 that defines the race ring width in the axial direction. The raceway surface 9 has a cylindrical surface shape. The side surface 11 is a flat surface along the radial direction.
転動体３は、円筒ころからなる。転動体３は、つば１０や中つば５によって案内される。
The rolling element 3 consists of cylindrical rollers. The rolling element 3 is guided by the collar 10 and the middle collar 5.
これら軌道輪７，８を締結する結合手段は、図２、図３に示すように、第一の軌道輪７の図中右側の側面１１で軸方向に開口している第一の格納部２１と、第一の格納部２１と軸方向に向き合うように第二の軌道輪８の図中左側の側面１１に開口している第二の格納部２２と、第一の格納部２１及び第二の格納部２２に軸方向に圧入可能な結合部材２３とからなる。
As shown in FIGS. 2 and 3, the coupling means for fastening the bearing rings 7, 8 is a first storage portion 21 opened in the axial direction on the right side surface 11 of the first bearing ring 7 in the drawing. The second storage part 22 opened in the left side surface 11 of the second race ring 8 so as to face the first storage part 21 in the axial direction, the first storage part 21 and the second storage part 21 And a coupling member 23 that can be press-fitted into the storage portion 22 in the axial direction.
第一の格納部２１及び第二の格納部２２は、それぞれ軸方向に開口している穴２４，２５と、穴２４，２５と交差するように径方向に開口している空間２６，２７とによって形成されている。これら格納部２１，２２は、軸方向（図中左右方向）に向き合うことが可能な対称形になっている。
The first storage portion 21 and the second storage portion 22 include holes 24 and 25 that are open in the axial direction, and spaces 26 and 27 that are open in the radial direction so as to intersect the holes 24 and 25, respectively. Is formed by. These storage parts 21 and 22 are symmetrical so that they can face each other in the axial direction (left-right direction in the figure).
穴２４，２５の内周は、それぞれ対応の側面１１から連続する円筒状になっている。このような穴２４，２５は、それぞれ対応の側面１１から軸方向に穴開け加工を行うことよって、簡単に形成することが可能である。
The inner peripheries of the holes 24 and 25 are each formed in a continuous cylindrical shape from the corresponding side surface 11. Such holes 24 and 25 can be easily formed by drilling in the axial direction from the corresponding side surfaces 11 respectively.
一方、空間２６，２７は、それぞれ対応の軌道輪７の外周端部（図示例において図中右側のつば１０の外径面）又は軌道輪８の外周端部（図示例において図中左側のつば１０の外径面）から連続する径方向の穴状に形成されている。空間２６，２７の内周は、それぞれ対応の穴２４，２５の穴軸線と同じ周方向位置に径方向の穴軸線をもった円筒状になっている。このような空間２６，２７は、それぞれ対応の外周端部（つば１０の外径面）から径方向に穴開け加工を行うことによって、簡単に形成することが可能である。
On the other hand, the spaces 26 and 27 respectively correspond to the outer peripheral end of the corresponding bearing ring 7 (the outer diameter surface of the collar 10 on the right side in the figure) or the outer peripheral end of the bearing ring 8 (the left collar in the figure on the example). 10 outer diameter surfaces). The inner peripheries of the spaces 26 and 27 have a cylindrical shape with a radial hole axis at the same circumferential position as the hole axes of the corresponding holes 24 and 25, respectively. Such spaces 26 and 27 can be easily formed by drilling in the radial direction from the corresponding outer peripheral end (outer diameter surface of the collar 10).
格納部２１，２２は、軌道面９と転動体３の接触方向の延長上に存在せず、つば１０と径方向に連続する範囲内に限って形成されている。これは、軸受荷重の負荷時における軌道面９の剛性低下を避けるためである。
The storage portions 21 and 22 do not exist on the extension of the contact direction between the raceway surface 9 and the rolling element 3, and are formed only within a range continuous with the collar 10 in the radial direction. This is to avoid a decrease in rigidity of the raceway surface 9 when a bearing load is applied.
図１、図２、図４に示すように、結合部材２３は、格納部２１，２２への圧入に耐えると共に二個の軌道輪７，８の締結に要する強度をもった一体の部材になっている。結合部材２３の図中左端部は、第一の格納部２１に軸方向に圧入可能な第一の頭部２８になっている。結合部材２３の図中右端部は、第二の格納部２２に軸方向に圧入可能な第二の頭部２９になっている。これら頭部２８，２９は、概ね球状になっている。結合部材２３は、これら頭部２８，２９間に連なる柱部３０をもっている。柱部３０は、軸方向に沿った円柱状になっている。
As shown in FIGS. 1, 2, and 4, the coupling member 23 is an integral member that can withstand the press-fitting into the storage portions 21 and 22 and has the strength required to fasten the two race rings 7 and 8. ing. The left end portion of the coupling member 23 in the figure is a first head portion 28 that can be press-fitted into the first storage portion 21 in the axial direction. The right end portion of the coupling member 23 in the figure is a second head portion 29 that can be press-fitted in the second storage portion 22 in the axial direction. These heads 28 and 29 are substantially spherical. The coupling member 23 has a column portion 30 that is continuous between the head portions 28 and 29. The column part 30 has a cylindrical shape along the axial direction.
ここで、穴２４，２５の径をＤ１とする。また、空間２６，２７の径をＤ２とする。また、頭部２８，２９のうちの径方向で最大となる位置で測った径方向の寸法を、最大径：Ｄ３とする。また、柱部３０の径をＤ４とする。また、頭部２８の最大径Ｄ３の位置と、頭部２９の最大径Ｄ３の位置間の距離をＬとする。また、空間２６，２７から対応の側面１１までの距離をＴとする。空間２６，２７の断面高さをＨとする。なお、断面高さＨは、内輪１の中心軸を含む仮想平面での断面（図１、図２に示す断面も該当する。）上において、穴２４，２５の軸方向延長上から内径側及び外径側へ均等に頭部２８，２９の収容空間を取れる範囲の径方向長さである。
Here, the diameter of the holes 24 and 25 is D1. The diameter of the spaces 26 and 27 is D2. The dimension in the radial direction measured at the maximum position in the radial direction of the heads 28 and 29 is defined as the maximum diameter: D3. The diameter of the column part 30 is set to D4. Further, L is the distance between the position of the maximum diameter D3 of the head 28 and the position of the maximum diameter D3 of the head 29. Further, T is the distance from the spaces 26 and 27 to the corresponding side surface 11. Let H be the sectional height of the spaces 26 and 27. In addition, the cross-sectional height H is the inner diameter side from the axial extension of the holes 24 and 25 on the cross section in the virtual plane including the central axis of the inner ring 1 (the cross section shown in FIGS. 1 and 2 also applies). It is the length in the radial direction of the range in which the accommodation spaces of the heads 28 and 29 can be taken evenly toward the outer diameter side.
空間２６，２７は、頭部２８，２９の最大径Ｄ３よりも大きな断面高さＨに設定されており、空間２６，２７の径Ｄ２は、頭部２８，２９の球径よりも大きく設定されている。すなわち、空間２６，２７により、対応の頭部２８又は頭部２９の収容空間が形成されている。
The spaces 26 and 27 are set to have a sectional height H larger than the maximum diameter D3 of the heads 28 and 29, and the diameter D2 of the spaces 26 and 27 is set larger than the spherical diameter of the heads 28 and 29. ing. That is, a space for accommodating the corresponding head 28 or head 29 is formed by the spaces 26 and 27.
頭部２８，２９の最大径Ｄ３、柱部３０の径Ｄ４及び穴２４，２５の径Ｄ１については、径Ｄ３＞径Ｄ１＞径Ｄ４に設定されており、距離Ｌと距離Ｔについては、距離Ｌ＞２×距離Ｔに設定されている。これら設定により、頭部２８，２９を穴２４，２５から軸方向に空間２６，２７へ圧入して第一の格納部２１及び第二の格納部２２に収容すること、及び、空間２６，２７に収容された頭部２８，２９と、軌道輪７，８の距離Ｔを規定する肉厚部との軸方向の接触によって第一の軌道輪７と第二の軌道輪８の軸方向への分離を阻止することが可能となっている。
The maximum diameter D3 of the heads 28 and 29, the diameter D4 of the column part 30, and the diameter D1 of the holes 24 and 25 are set such that diameter D3> diameter D1> diameter D4. L> 2 × distance T is set. With these settings, the heads 28 and 29 are pressed into the spaces 26 and 27 in the axial direction from the holes 24 and 25 to be accommodated in the first storage unit 21 and the second storage unit 22, and the spaces 26 and 27 are stored. In the axial direction of the first race ring 7 and the second race ring 8 by the axial contact between the heads 28 and 29 housed in the shaft and the thick portion defining the distance T between the race rings 7 and 8. It is possible to prevent separation.
特に、穴２４，２５の径Ｄ１＞柱部３０の径Ｄ４の設定により、第一の格納部２１と第二の格納部２２との間に周方向の位置ずれが生じている状態で結合部材２３の圧入工程が実施された場合であっても、結合部材２３が穴２４，２５に対して傾斜して挿入されることを許しつつ、第一の軌道輪７に対する第二の軌道輪８の偏心を防止することが可能となっている。
In particular, when the diameter D1 of the holes 24 and 25> the diameter D4 of the column part 30 is set, the coupling member is in a state in which a circumferential displacement occurs between the first storage part 21 and the second storage part 22. Even when the press-fitting process of 23 is performed, the coupling member 23 is inserted into the holes 24 and 25 while being inclined, and the second race ring 8 with respect to the first race ring 7 is inserted. It is possible to prevent eccentricity.
結合部材２３の材料は特に限定されないが、結合部材２３を第一の格納部２１及び第二の格納部２２に圧入すること、多数の軸受型番に対して一種類の結合部材２３を使用可能にすること等の理由から、弾性変形性、大量生産性、機械的強度に優れた材料を採用することが好ましい。
The material of the coupling member 23 is not particularly limited, but it is possible to use one type of coupling member 23 for a large number of bearing model numbers by press-fitting the coupling member 23 into the first storage unit 21 and the second storage unit 22. Therefore, it is preferable to employ a material excellent in elastic deformability, mass productivity, and mechanical strength.
結合部材２３は、樹脂材料によって形成されている。樹脂材料を採用すると、良好な弾性変形性を得ることが可能であると共に、結合部材２３を射出成型等により安価で大量生産することが可能である。前述の樹脂材料としては、例えば、ポリアミド（ＰＡ）のようなエンジニアリングプラスチックや、繊維強化樹脂が挙げられる。
The coupling member 23 is made of a resin material. When a resin material is employed, it is possible to obtain good elastic deformability, and it is possible to mass-produce the coupling member 23 at low cost by injection molding or the like. Examples of the resin material include engineering plastics such as polyamide (PA) and fiber reinforced resins.
また、結合部材２３は、金属によって形成されているものでもよい。金属を採用すると、結合部材２３の機械的強度を確保することが容易である。前述の金属としては、例えば、鋼、アルミニウム合金，銅合金，鋳鉄が挙げられる。
Further, the coupling member 23 may be made of metal. If metal is employed, it is easy to ensure the mechanical strength of the coupling member 23. Examples of the metal include steel, aluminum alloy, copper alloy, and cast iron.
第一実施形態に係る転がり軸受は、上述のようなものであり、結合部材２３を二個の軌道輪７，８によって軸方向両側から挟み込むように両頭部２８，２９を対応の穴２４，２５から空間２６，２７へ圧入することにより、両頭部２８、２９が第一の格納部２１及び第二の格納部２２に収容される。この収容状態では、これら軌道輪７，８から結合部材２３が脱落できない。このため、結合部材２３及び両格納部２１，２２からなる結合手段によって、これら軌道輪７，８同士が実質的に分離できないように軸方向に締結されている内輪１の形態に維持される。
The rolling bearing according to the first embodiment is as described above, and the two heads 28 and 29 are provided in the corresponding holes 24 and 25 so that the coupling member 23 is sandwiched between the two race rings 7 and 8 from both sides in the axial direction. The heads 28 and 29 are accommodated in the first storage unit 21 and the second storage unit 22 by being press-fitted into the spaces 26 and 27 from the first storage unit 21. In this accommodated state, the coupling member 23 cannot be removed from the races 7 and 8. For this reason, the coupling means comprising the coupling member 23 and the storage portions 21 and 22 is maintained in the form of the inner ring 1 that is fastened in the axial direction so that the raceways 7 and 8 cannot be substantially separated from each other.
また、結合部材２３が軌道輪７，８の側面１１に開口している穴２４，２５から格納部２１，２２に軸方向に圧入するものなので、軌道輪７，８の周長が結合部材２３の配置に及ぼす影響は小さい。このため、第一実施形態に係る転がり軸受は、結合部材２３に対応の格納部２１，２２を形成可能な径方向肉厚の軌道輪を備える他軸受であれば、軸受サイズが異なっていても同じ結合部材２３を用いることが可能である。図示例においては、結合部材２３の各部の寸法は穴２４，２５の径Ｄ１、頭部２８，２９の最大径Ｄ３及び空間２６，２７の断面高さＨ、距離Ｔによって決まるが、全ての寸法は内輪１の内径によらず設計可能なため、軸受サイズに関係なく結合部材２３を兼用することができる。したがって、第一実施形態に係る転がり軸受は、結合部材２３を軸受サイズごとに用意することが不要になる。
Further, since the coupling member 23 is press-fitted axially into the storage portions 21 and 22 from the holes 24 and 25 opened in the side surface 11 of the race rings 7 and 8, the circumferential length of the race rings 7 and 8 is the coupling member 23. The effect on the placement of the is small. For this reason, if the rolling bearing according to the first embodiment is another bearing having a radially thick bearing ring capable of forming the storage portions 21 and 22 corresponding to the coupling member 23, the bearing size may be different. The same coupling member 23 can be used. In the illustrated example, the dimensions of each part of the coupling member 23 are determined by the diameter D1 of the holes 24, 25, the maximum diameter D3 of the heads 28, 29, the cross-sectional height H of the spaces 26, 27, and the distance T. Can be designed regardless of the inner diameter of the inner ring 1, so that the coupling member 23 can also be used regardless of the bearing size. Therefore, in the rolling bearing according to the first embodiment, it is not necessary to prepare the coupling member 23 for each bearing size.
また、格納部２１，２２の形成に際し、穴２４，２５は、各軌道輪７，８の側面１１から軸方向に開口する一般的な穴開け加工で形成し、空間２６，２７は、各軌道輪７，８の内周又は外周から径方向に開口する一般的な穴開け加工で形成することが可能である。すなわち、特殊な断面形状を持たない穴２４，２５や空間２６，２７は、一般的に使用されるドリルやバイトによって軌道輪７，８に加工可能である。したがって、第一実施形態に係る転がり軸受は、特殊な工具を用いた加工で軌道輪７，８に格納部２１，２２を形成することが不要になるので、軌道輪７，８の加工が容易になる。
Further, when the storage portions 21 and 22 are formed, the holes 24 and 25 are formed by a general drilling process that opens in the axial direction from the side surface 11 of each raceway ring 7 and 8, and the spaces 26 and 27 are formed in each raceway. It can be formed by a general drilling process that opens in the radial direction from the inner periphery or outer periphery of the rings 7 and 8. That is, the holes 24 and 25 and the spaces 26 and 27 having no special cross-sectional shape can be processed into the races 7 and 8 by a commonly used drill or bite. Therefore, in the rolling bearing according to the first embodiment, it is not necessary to form the storage portions 21 and 22 in the race rings 7 and 8 by machining using a special tool, so that the race rings 7 and 8 can be easily machined. become.
このように、第一実施形態に係る転がり軸受は、二個の軌道輪７，８の締結に用いる結合部材２３を軸受サイズごとに用意することが不要であって軌道輪７，８の加工・組立作業が容易な結合手段にすると共に、結合部材２３の脱落を防止することができる。
Thus, in the rolling bearing according to the first embodiment, it is not necessary to prepare the coupling member 23 used for fastening the two race rings 7 and 8 for each bearing size. The coupling means can be easily assembled and the coupling member 23 can be prevented from falling off.
また、第一実施形態に係る転がり軸受において、結合部材２３が樹脂材料によって形成されているものは、結合部材２３の頭部２８，２９を格納部２１，２２に圧入する際の弾性変形性、結合部材２３の大量生産性に優れる。
Further, in the rolling bearing according to the first embodiment, the coupling member 23 formed of a resin material is elastically deformable when the heads 28 and 29 of the coupling member 23 are press-fitted into the storage units 21 and 22. The coupling member 23 is excellent in mass productivity.
また、第一実施形態に係る転がり軸受において、結合部材２３が金属によって形成されているものは、結合部材２３の機械的強度に優れる。
Further, in the rolling bearing according to the first embodiment, the one in which the coupling member 23 is formed of metal is excellent in the mechanical strength of the coupling member 23.
なお、第一実施形態においては球状の頭部２８，２９を例示したが、前述の各部の寸法（径Ｄ１，最大径Ｄ３等）の関係を満足するならば、球状に限られず、対応の穴２４，２６に向かって先細な錐状にしてもよい。球状の頭部２８，２９や錐状の頭部は、穴２４，２６の穴縁に押し当てる圧入初期において穴２４，２６と同心な位置へ案内可能な利点がある。
In the first embodiment, the spherical heads 28 and 29 are illustrated. However, as long as the relationship of the dimensions (diameter D1, maximum diameter D3, etc.) of the respective parts described above is satisfied, the shape is not limited to the spherical shape, and the corresponding holes. You may make it into a tapered cone shape toward 24,26. The spherical heads 28 and 29 and the cone-shaped head have the advantage that they can be guided to positions concentric with the holes 24 and 26 at the initial press-fitting time against the hole edges of the holes 24 and 26.
また、第一実施形態においては軌道輪７，８の側面１１に穴２４，２６が周方向の一箇所だけに形成されている例を示したが、穴２４，２６を周方向の複数個所に形成し、複数の結合部材２３で二個の軌道輪７，８を締結するようにしてもよい。この場合、例えば、穴２４，２６を周方向等配に配置することにより、二個の軌道輪７，８を周方向にバランスよく締結することができる。
In the first embodiment, the holes 24 and 26 are formed at only one place in the circumferential direction on the side surface 11 of the raceway rings 7 and 8. However, the holes 24 and 26 are provided at a plurality of places in the circumferential direction. Alternatively, the two race rings 7 and 8 may be fastened by a plurality of coupling members 23. In this case, for example, the two race rings 7 and 8 can be fastened in a balanced manner in the circumferential direction by arranging the holes 24 and 26 in the circumferentially equal distribution.
また、第一実施形態においては軌道輪７，８の外周から径方向に穴開けする止め穴状の空間２６，２７を例示したが、空間２６，２７は軌道輪７，８の内周から穴開けしてもよく、また、軌道輪７，８の内外周間を径方向に貫通する穴にしてもよい。
Further, in the first embodiment, the stop holes-like spaces 26 and 27 that are pierced in the radial direction from the outer circumferences of the race rings 7 and 8 are illustrated, but the spaces 26 and 27 are formed from the inner circumferences of the race rings 7 and 8. You may open, and you may make it the hole penetrated between the inner and outer periphery of the race rings 7 and 8 to radial direction.
また、第一実施形態においては丸穴状の穴２４，２５や空間２６，２７を例示したが、ドリルや旋盤等のバイトのように、工具又はワーク（軌道輪）間の単純な相対回転によって加工可能な形状の穴２４，２５や空間２６，２７にすればよい。その一例としての第二実施形態を図５に基づいて説明する。以下、第一実施形態との相違点を述べるに留める。
In the first embodiment, the round holes 24 and 25 and the spaces 26 and 27 are exemplified. However, by a simple relative rotation between tools or workpieces (track rings), such as a drill or a lathe. What is necessary is just to make it the holes 24 and 25 of the shape which can be processed, and the spaces 26 and 27. A second embodiment as an example thereof will be described with reference to FIG. Hereinafter, only differences from the first embodiment will be described.
第二実施形態に係る軌道輪４０，４１の格納部４２，４３は、それぞれ軸方向に貫通している穴４４と、周方向の溝状になっている空間４５とによって形成されている。空間４５は、軌道輪４０，４１の全周に亘っている。このような空間４５は、例えば、一般的な旋盤で簡単に加工することが可能である。第二実施形態のように周方向の溝状の空間４５は、周方向の複数個所に穴４４を形成する場合に、これら複数の穴４４に交差する空間４５を共通化して一工程で形成することができる。また、必要に応じて軌道輪４０，４１に穴４４を当初の数から増やし、二個の軌道輪４０，４１の結合箇所を増やすことも可能となる。なお、穴４４は、格納部４２，４３に圧入された結合部材（図示省略）の周方向位置及び径方向位置を保持するため、周方向の溝状にすることはできない。
The storage portions 42 and 43 of the races 40 and 41 according to the second embodiment are each formed by a hole 44 penetrating in the axial direction and a space 45 having a groove shape in the circumferential direction. The space 45 extends over the entire circumference of the races 40 and 41. Such a space 45 can be easily machined with, for example, a general lathe. As in the second embodiment, the circumferential groove-like space 45 is formed in one step by sharing the spaces 45 intersecting the plurality of holes 44 when the holes 44 are formed at a plurality of locations in the circumferential direction. be able to. Moreover, it is also possible to increase the number of holes 44 in the raceways 40 and 41 from the initial number as necessary, and to increase the number of places where the two raceways 40 and 41 are joined. In addition, since the hole 44 holds the circumferential direction position and radial position of the coupling member (not shown) press-fitted into the storage portions 42 and 43, it cannot be formed in a circumferential groove shape.
第二実施形態の場合、空間４５の形成に伴い、つば４６の軸方向の肉厚は全周に亘って反対側のつば１０よりも薄くなるが、図１の外輪１の中つば５によっても図５のつば４６と同側のころ端面を案内可能なため（図１参照）、つば４６が全周に亘って薄肉化されても問題ない。
In the case of the second embodiment, along with the formation of the space 45, the thickness of the collar 46 in the axial direction becomes thinner than the collar 10 on the opposite side over the entire circumference, but also by the middle collar 5 of the outer ring 1 in FIG. Since the roller end surface on the same side as the collar 46 in FIG. 5 can be guided (see FIG. 1), there is no problem even if the collar 46 is thinned over the entire circumference.
前述の第一実施形態や第二実施形態ではラジアル軸受を例示したが、スラスト軸受に形成する場合でも、同様に結合手段を構成することが可能である。
Although the radial bearing is exemplified in the first embodiment and the second embodiment described above, the coupling means can be configured in the same manner even when formed in a thrust bearing.
また、前述の第一実施形態や第二実施形態では内輪を二個の軌道輪で構成する例を示したが、外輪を二個の軌道輪で構成する場合でも同様に結合手段を構成することが可能である。
In the first embodiment and the second embodiment described above, the inner ring is composed of two race rings. However, even when the outer ring is composed of two race rings, the coupling means is similarly constructed. Is possible.
また、前述の第一実施形態や第二実施形態では円筒ころ軸受を例示したが、円すいころ軸受、玉軸受等、他形式の軸受にも同様に結合手段を構成することが可能である。
In the first embodiment and the second embodiment described above, the cylindrical roller bearing is exemplified. However, the coupling means can be configured similarly to other types of bearings such as a tapered roller bearing and a ball bearing.
今回開示された実施形態はすべての点で例示であって制限的なものではないと考えられるべきである。したがって、本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。
The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. Accordingly, the scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.
１ 内輪
２ 外輪
３ 転動体
４，９ 軌道面
７，４０ 第一の軌道輪
８，４１ 第二の軌道輪
１１ 側面
２１，４２ 第一の格納部
２２，４３ 第二の格納部
２３ 結合部材
２４，２５，４４ 穴
２６，２７，４５ 空間
２８ 第一の頭部
２９ 第二の頭部 DESCRIPTION OFSYMBOLS 1 Inner ring 2 Outer ring 3 Rolling elements 4, 9 Track surface 7, 40 First track ring 8, 41 Second track ring 11 Side surface 21, 42 First storage part 22, 43 Second storage part 23 Coupling member 24 , 25, 44 Holes 26, 27, 45 Space 28 First head 29 Second head
２ 外輪
３ 転動体
４，９ 軌道面
７，４０ 第一の軌道輪
８，４１ 第二の軌道輪
１１ 側面
２１，４２ 第一の格納部
２２，４３ 第二の格納部
２３ 結合部材
２４，２５，４４ 穴
２６，２７，４５ 空間
２８ 第一の頭部
２９ 第二の頭部 DESCRIPTION OF
Claims (6)
- 第一の軌道輪と、第二の軌道輪と、前記第一の軌道輪と前記第二の軌道輪とを締結する結合手段とを備える転がり軸受において、
前記結合手段が、前記第一の軌道輪の側面で軸方向に開口している第一の格納部と、前記第一の格納部と軸方向に向き合うように前記第二の軌道輪の側面に開口している第二の格納部と、前記第一の格納部に軸方向に圧入可能な第一の頭部及び前記第二の格納部に軸方向に圧入可能な第二の頭部をもった結合部材とからなり、
前記第一の格納部及び前記第二の格納部が、それぞれ軸方向に開口している穴と、当該穴と交差するように径方向に開口している空間とによって形成されていることを特徴とする転がり軸受。 In a rolling bearing comprising a first race ring, a second race ring, and a coupling means for fastening the first race ring and the second race ring,
The coupling means is provided on the side surface of the second raceway ring so as to face the first storage portion that is axially open on the side surface of the first raceway ring and the first storage portion in the axial direction. A second storage part that is open, a first head that can be press-fitted in the axial direction into the first storage part, and a second head that can be press-fitted in the axial direction into the second storage part. A connecting member,
The first storage portion and the second storage portion are each formed by a hole opening in the axial direction and a space opening in the radial direction so as to intersect the hole. Rolling bearing. - 前記空間が径方向の穴状になっている請求項１に記載の転がり軸受。 The rolling bearing according to claim 1, wherein the space has a hole shape in a radial direction.
- 前記空間が周方向の溝状になっている請求項１に記載の転がり軸受。 The rolling bearing according to claim 1, wherein the space has a circumferential groove shape.
- 前記結合部材が樹脂材料によって形成されている請求項１から３のいずれか１項に記載の転がり軸受。 The rolling bearing according to any one of claims 1 to 3, wherein the coupling member is formed of a resin material.
- 前記結合部材が金属によって形成されている請求項１から３のいずれか１項に記載の転がり軸受。 The rolling bearing according to any one of claims 1 to 3, wherein the coupling member is made of metal.
- 前記第一の軌道輪及び前記第二の軌道輪が、それぞれラジアル軸受用のものである請求項１から５のいずれか１項に記載の転がり軸受。 The rolling bearing according to any one of claims 1 to 5, wherein each of the first raceway ring and the second raceway ring is for a radial bearing.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015251827A JP2017115979A (en) | 2015-12-24 | 2015-12-24 | Rolling bearing |
| JP2015-251827 | 2015-12-24 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2017110907A1 true WO2017110907A1 (en) | 2017-06-29 |
Family
ID=59089416
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/JP2016/088176 WO2017110907A1 (en) | 2015-12-24 | 2016-12-21 | Roller bearing |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2017115979A (en) |
| WO (1) | WO2017110907A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111520413A (en) * | 2020-05-06 | 2020-08-11 | 湖北文理学院 | Spacer ring feeding device and needle bearing automatic assembly device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5840618U (en) * | 1981-09-10 | 1983-03-17 | エヌ・テ−・エヌ東洋ベアリング株式会社 | cylindrical roller bearing |
| JPH0144806Y2 (en) * | 1984-06-12 | 1989-12-25 | ||
| JP2007303516A (en) * | 2006-05-10 | 2007-11-22 | Nsk Ltd | Cross roller bearing |
-
2015
- 2015-12-24 JP JP2015251827A patent/JP2017115979A/en active Pending
-
2016
- 2016-12-21 WO PCT/JP2016/088176 patent/WO2017110907A1/en active Application Filing
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5840618U (en) * | 1981-09-10 | 1983-03-17 | エヌ・テ−・エヌ東洋ベアリング株式会社 | cylindrical roller bearing |
| JPH0144806Y2 (en) * | 1984-06-12 | 1989-12-25 | ||
| JP2007303516A (en) * | 2006-05-10 | 2007-11-22 | Nsk Ltd | Cross roller bearing |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111520413A (en) * | 2020-05-06 | 2020-08-11 | 湖北文理学院 | Spacer ring feeding device and needle bearing automatic assembly device |
| CN111520413B (en) * | 2020-05-06 | 2021-08-31 | 湖北文理学院 | Spacer ring feeding device and needle bearing automatic assembly device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017115979A (en) | 2017-06-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8790019B2 (en) | Rolling bearing | |
| WO2014065234A1 (en) | Cylindrical roller bearing | |
| KR101439584B1 (en) | A bearing assembly with overmoulded annular bodies of plastic material | |
| US9903417B2 (en) | Assembly procedure of a bearing unit—HUB flange | |
| JP2011137530A (en) | Split type retainer of tapered roller bearing | |
| US9841058B2 (en) | Assembly procedure of a bearing unit—hub flange | |
| US9273728B2 (en) | Rolling bearing having rings with stepped surfaces opposite to the raceways | |
| US20210348653A1 (en) | Bearing unit with eccentric clamping collar | |
| US7637664B2 (en) | Composite roll bearing | |
| JP2013015200A (en) | Conical roller bearing | |
| US10683891B1 (en) | Stacked thrust bearing arrangement | |
| WO2017110907A1 (en) | Roller bearing | |
| US10570960B2 (en) | Segmented cage for rolling bearing | |
| TWI726224B (en) | Rolling bearings and retainers | |
| US9388851B1 (en) | Split cylindrical roller bearing | |
| JP5876117B2 (en) | Tapered roller bearing split cage | |
| JPH01116316A (en) | Double-row roller bearing | |
| JP2013096505A (en) | Cage for thrust bearing, thrust bearing and three-row composite cylindrical roller bearing using the same | |
| JP2012031904A (en) | Cage for roller bearing | |
| JP2014156876A (en) | Cage for rolling bearing, rolling bearing, and method of manufacturing rolling bearing | |
| JP2006144829A (en) | Non-separation type rolling bearing | |
| JP2005221001A (en) | Tapered roller bearing | |
| JP2009002480A5 (en) | ||
| US20230160421A1 (en) | Rolling bearing, notably large-diameter rolling bearing | |
| JP2013133881A (en) | Cylindrical-roller bearing |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 16878794 Country of ref document: EP Kind code of ref document: A1 |
|
| NENP | Non-entry into the national phase |
Ref country code: DE |
|
| 122 | Ep: pct application non-entry in european phase |
Ref document number: 16878794 Country of ref document: EP Kind code of ref document: A1 |