WO2023042603A1 - Shell roller bearing and fixing structure for shell roller bearing - Google Patents

Shell roller bearing and fixing structure for shell roller bearing Download PDF

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Publication number
WO2023042603A1
WO2023042603A1 PCT/JP2022/031365 JP2022031365W WO2023042603A1 WO 2023042603 A1 WO2023042603 A1 WO 2023042603A1 JP 2022031365 W JP2022031365 W JP 2022031365W WO 2023042603 A1 WO2023042603 A1 WO 2023042603A1
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Prior art keywords
outer ring
roller bearing
shell
main body
tapered surface
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PCT/JP2022/031365
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French (fr)
Japanese (ja)
Inventor
彰汰 一柳
大旺 佐藤
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Ntn株式会社
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Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to CN202280061402.5A priority Critical patent/CN117940685A/en
Publication of WO2023042603A1 publication Critical patent/WO2023042603A1/en

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    • 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
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing

Definitions

  • the present invention relates to a shell outer ring of a cup roller bearing that bears a radial load.
  • Conventional drawn cup needle roller bearings incorporated in compressors for car air conditioners include a shell outer ring and a retainer incorporated on the inner diameter side of the shell outer ring, as described in, for example, Japanese Patent Application Laid-Open No. 2008-038986 (Patent Document 1). and needle rollers as rolling elements held by a retainer.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2008-038986
  • needle rollers as rolling elements held by a retainer.
  • both axial end portions located on the axial outer side are folded back by 180 degrees toward the inner diameter side.
  • the outer peripheral surfaces of both ends in the axial direction are tapered. These taper angles are between 5 and 25 degrees. The reason for this is that when the taper angle is 5 degrees to 25 degrees, the introduction into the opening is guided by the tapered surface.
  • Patent Document 1 recommends that the outer periphery of the end portion in the axial direction of the shell outer ring is tapered by 5 degrees or more and 25 degrees or less. In other words, the axial dimension of the drawn cup needle roller bearing is inevitably small, which means that the axial ends of the drawn cup outer ring are separated from the casing. I am concerned about getting out of.
  • Patent Document 1 there is a method of increasing the interference by providing a negative clearance in order to avoid coming off, but this increases the risk of galling. Therefore, it is necessary to make further improvements from Patent Document 1.
  • the drawn cup roller bearing according to the present invention is premised to have a shell outer ring, a cage incorporated in the shell outer ring, and rollers held by the cage and rolling on the inner diameter surface of the shell outer ring.
  • the shell outer ring includes a cylindrical outer ring body that is press-fitted into the opening of the axle box, and a flange that protrudes radially inward from both ends of the outer ring body in the axial direction. is provided with a tapered surface whose outer diameter gradually decreases from the inner side to the outer side in the axial direction, and the taper angle of the tapered surface falls within the range of 0.5 degrees or more and less than 5 degrees.
  • the tapered surface of the shell outer ring comes into surface contact with the inner diameter surface of the opening when the shell outer ring is press-fitted into the opening of the axle box. This secures a contact area between the shell outer ring and the axle box, and the shell outer ring is firmly press-fitted into the axle box.
  • the tapered surface allows the outer ring of the shell to be introduced into the opening without tilting, thereby preventing galling.
  • a tapered surface whose outer diameter gradually decreases from the inner side to the outer side in the axial direction refers to a tapered shape in which the outer diameter decreases toward the ends in the axial direction when viewed from the center in the axial direction.
  • the tapered surface is provided at least on the press-fitted side of both ends of the shell outer ring in the axial direction. That is, the tapered surfaces may be provided at both ends of the shell outer ring in the axial direction, respectively, or may be provided at only one end.
  • the plate thickness of the flange is not particularly limited, but when forming the flange by bending the edge of the cylindrical body, the flange is preferably thin for ease of bending. However, it is preferable that the brim portion is thick in order to secure the rigidity for being introduced into the opening by press fitting.
  • the plate thickness of the flange portion provided at one axial end portion of the outer ring main body is included in the range of 40% or more and 75% or less of the plate thickness of the outer ring main body. According to this aspect, it is possible to satisfy both the easiness of bending and the securing of rigidity for press-fitting.
  • the axially outer end surface of the flange and the tapered surface are connected via a chamfer formed at one axial end of the outer ring main body, and the shell outer ring has an axial dimension of 6 mm or more.
  • the sum of the axial dimension of the tapered surface and the axial dimension of the chamfer falls within the range of 1.5 [mm] or more and 3.5 [mm] or less. According to this aspect, it is possible to facilitate press-fitting and secure a contact area.
  • the radial dimension of the tapered surface is not particularly limited, in a more preferred aspect of the present invention, the radial dimension of the tapered surface is 1.1 times or more the interference obtained by subtracting the inner diameter radius of the opening from the outer diameter radius of the shell outer ring. Included in the range of 1.5 times or less. According to this aspect, it is possible to secure a contact area while preventing galling.
  • a fixed structure for a drawn cup roller bearing according to the present invention comprises the above-described shell outer ring, a cage incorporated in the shell outer ring, rollers held by the cage and rolling on the inner diameter surface of the outer ring main body, and the shell outer ring.
  • An axle box has an opening with an inner diameter smaller than the outer diameter, and the inner diameter surface of the opening is in close contact with the outer diameter surface of the outer ring body with a negative clearance.
  • the axle box is made of a light alloy.
  • a light alloy is, for example, a light metal such as aluminum, or an alloy containing a light metal such as aluminum as a main component.
  • FIG. 1 is a longitudinal sectional view showing a drawn cup roller bearing according to an embodiment of the present invention
  • FIG. It is a longitudinal cross-sectional view which shows the same embodiment press-fitted and fixed to the axle box.
  • FIG. 2 is an enlarged cross-sectional view showing an upper left portion of the outer race of the shell in FIG. 1
  • FIG. 2 is an enlarged cross-sectional view showing an upper right portion of the outer ring of the shell in FIG. 1
  • FIG. 2 is an enlarged cross-sectional view showing an upper right portion of the outer ring of the shell in FIG. 1 ;
  • FIG. 1 is a longitudinal sectional view showing a drawn cup roller bearing according to one embodiment of the present invention.
  • FIG. 2 is a vertical cross-sectional view showing the same embodiment press-fitted and fixed to the opening of the axle box.
  • the drawn cup roller bearing 10 includes a drawn outer ring 11, a retainer 21, and rollers 31, and is press-fitted into an opening 41 of an axle box 40 as shown in FIG.
  • the cross-sectional patterns are omitted.
  • the shell outer ring 11 is an integral body and includes an outer ring main body 12 and flanges 13 and 14 .
  • the flange portion 13 rises from one axial end of the cylindrical outer ring main body 12 toward the inner diameter side at approximately 90 degrees.
  • the plate thickness of the outer ring main body 12 and the plate thickness of the flange portion 13 are substantially the same, or the plate thickness of the flange portion 13 is greater.
  • the flange portion 14 rises from the other end in the axial direction of the cylindrical outer ring main body 12 toward the inner diameter side at approximately 90 degrees.
  • the plate thickness of the flange portion 14 is smaller than the plate thickness of the outer ring main body 12 .
  • Approximately 90 degrees means that the angle of the collar portion 14 may vary by 90 ⁇ 10 degrees with respect to the outer ring main body 12 .
  • the flange portion 14 is also called an edge curved portion because it is formed by gradually bending the other edge in the axial direction of the cylindrical shaped material toward the inner diameter side.
  • the plate thickness of the flange portion 14 is a predetermined value within a range of 40% or more and 75% or less of the plate thickness of the central region of the outer ring main body 12 in the axial direction.
  • a retainer 21 and rollers 31 are arranged between the pair of flanges 13 and 14 .
  • the outer diameter dimension of cage 21 is larger than the inner diameter dimension of flange portion 13 and/or flange portion 14 .
  • a cylindrical retainer 21 is mounted on the inner diameter side of the shell outer ring 11 and is restrained from moving in the axial direction by flanges 13 and 14 .
  • a plurality of pockets 22 are formed in the retainer 21 at intervals in the circumferential direction.
  • a roller 31 is arranged in each pocket 22, and the roller 31 is held by a roller stop portion (not shown) formed in the retainer 21 so as not to fall off.
  • the rollers 31 are needle rollers, for example, and roll on the inner diameter surface 12 c of the outer ring body 12 . Therefore, the inner diameter surface 12c of the outer ring main body 12 corresponds to the outer raceway surface.
  • FIG. 3 is an enlarged cross-sectional view showing the collar portion 13 of the shell outer ring and one axial end of the outer ring main body 12 .
  • One axial end of the outer ring body 12 is formed into a gently tapered surface 15 .
  • a taper angle ⁇ of the tapered surface 15 is a predetermined angle within a range of 0.5 degrees or more and less than 5 degrees.
  • an R (R) portion 16 having an arcuate cross section is formed on the outer end surface 13 b of the flange portion 13 and the tapered surface 15 .
  • the R portion 16 is chamfered to have a convex curved surface and is smoothly connected to the outer end surface 13 b and the tapered surface 15 .
  • the axial position of the R portion 16 is included in the axial position of the collar portion 13 .
  • the axial position of the tapered surface 15 overlaps the axial positions of the flange portion 13 and the outer ring main body 12 .
  • an annular groove-shaped relief portion 18 is formed on the inner peripheral surface of the outer ring main body 12 at the other end in the axial direction.
  • the recessed portion 18 retreats radially outward from the inner diameter surface 12c.
  • the surface of the recessed portion 18 connects with the inner diameter surface 12c on the inner side in the axial direction, and connects with the inner end surface of the collar portion 14 on the outer side in the axial direction.
  • the relief portion 18 facilitates formation of the collar portion 14 by bending.
  • the shell outer ring 11 is press-fitted and fixed in the opening 41 having a circular cross section.
  • the large dimensional difference of this negative clearance is called an interference region S, which is indicated by hatching on the outer diameter portion of the outer ring main body in FIGS. 1 and 3 to 5.
  • the interference region S occupies the entire circumference from one axial end to the other axial end of the outer ring main body 12 and overlaps the tapered surface 15 .
  • the taper angle ⁇ of the tapered surface 15 is set to a predetermined value of 0.5 degrees or more and less than 5 degrees, the taper angle becomes gentler than the conventional one, and the interference is reduced as shown in FIG. A region S is sufficiently secured from one axial end to the other axial end of the shell outer ring 11 .
  • the contact area between the shell outer ring 11 and the axle box 40 is increased, and the shell outer ring 11 is fixed to the axle box 40 . Therefore, the possibility that the shell outer ring 11 will slip out of the axle box 40 is eliminated.
  • this embodiment has the tapered surface 15, even if the axle box 40 is made of a light alloy, galling of the axle box 40 is prevented when the drawn cup roller bearing 10 is press-fitted into the opening 41. .
  • the axial dimension Ls of the shell outer ring 11 of this embodiment is 8 [mm] or more.
  • the total Lq of the axial dimension of the tapered surface 15 on one side and the axial dimension of the R portion 16 is recommended to be 2.0 ⁇ Lq ⁇ 3.5 [mm] in order to secure the contact area. .
  • the reason for this is that when Lq ⁇ 2.0 [mm], galling may occur during press-fitting. Also, when Lq>3.5 [mm], the contact area becomes insufficient, and the shell outer ring 11 falls off from the axle box 40 .
  • the interference region S reaches the R portion 16 in the embodiment shown in FIG. That is, the relationship between the radial dimension Rs of the interference S and the radial dimension Rt of the tapered surface 15 is [Formula 1] Rt/Rs ⁇ 1.0 satisfy.
  • the radial dimension Rs of the interference S is half the difference between the inner diameter dimension of the axle box 40 and the outer diameter dimension of the outer ring main body 12 .
  • the radial dimension Rt of the tapered surface 15 is the value of the radial distance between points P and Q where the tapered generatrix intersects the outer diameter surface 17 of the outer ring main body 12 and the R portion 16, respectively.
  • FIG. 5 a modified example shown in FIG. 5 may be used.
  • the drawn cup roller bearing 10 can be smoothly press-fitted into the opening 41 .
  • the drawn cup roller bearing 10 can be press-fitted into the opening 41 without any problem. There is a concern that it will not be possible to secure
  • the thickness of the flange portion 14 is a predetermined value within the range of 40% or more and 75% or less of the thickness of the central region of the outer ring main body 12 in the axial direction.
  • the rigidity of the other end in the axial direction of the shell outer ring 11 including the collar portion 14 is reduced, and galling of the axle box 40 can be prevented when the collar portion 14 is press-fitted into the opening 41 .
  • the plate thickness of the flange portion 14 is less than 40% of the plate thickness of the outer ring main body 12, the rigidity of the other axial end portion of the shell outer ring 11 is too low, and there is a risk of buckling during press fitting.
  • the plate thickness of the flange portion 14 is less than 40% of the plate thickness of the outer ring main body 12, the rigidity of the other axial end portion of the shell outer ring 11 is too high, and galling may occur in the axle box 40 when it is press-fitted. be.
  • the shell outer ring 11 is entirely carburized and hardened, and the other axial end of the shell outer ring 11 including the flange 14 is induction hardened and annealed. Thereby, the rigidity of the other end in the axial direction of the shell outer ring 11 is increased.
  • the present invention can be advantageously used in rolling bearings for car air-conditioning compressors and rolling bearings incorporated in light alloy axle boxes even in cases other than car air-conditioning compressors.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

A shell outer ring (11) is provided with a cylindrical outer ring body (12) that is press-fitted to an opening of a shaft box and a flange portion (14) that protrudes radially inward from an end portion of the outer ring body in the axial direction. A tapered surface (15) is provided on the outer peripheral surface of one end portion of the outer ring body in the axial direction and the taper angle θ of the tapered surface (15) is in a range of 0.5 to less than 5 degrees.

Description

シェル形ころ軸受およびシェル形ころ軸受の固定構造Drawn cup roller bearings and fixing structures for drawn cup roller bearings
　本発明は、ラジアル荷重を受け持つシェル形ころ軸受のシェル外輪に関する。 The present invention relates to a shell outer ring of a cup roller bearing that bears a radial load.
　カーエアコン用コンプレッサに組み込まれるシェル形針状ころ軸受として従来、例えば特開２００８―０３８９８６号公報（特許文献１）に記載されるように、シェル外輪と、シェル外輪の内径側に組み込まれる保持器と、保持器に保持される転動体としての針状ころとを備えるものが知られている。特許文献１のシェル外輪では、軸方向外側に位置する軸方向両端部が内径側に１８０°折り返されて形成される。また、軸方向両端部の外周面がテーパ形状に形成される。これらのテーパ角は５度～２５度である。この理由として、テーパ角が５度～２５度であると、テーパ面によって開口への導入が案内されるため、ハウジングの開口にシェル外輪を圧入する際にシェル外輪の倒れやかじりを抑制でき、汎用の工具を用いてもスムーズな組付けを行うことができる、というものである。テーパ角が５度未満であると、シェル外輪がハウジングの開口に圧入する際の嵌合幅を十分確保できず、ハウジングに対するシェル外輪の座りが不十分になる、というものである。 Conventional drawn cup needle roller bearings incorporated in compressors for car air conditioners include a shell outer ring and a retainer incorporated on the inner diameter side of the shell outer ring, as described in, for example, Japanese Patent Application Laid-Open No. 2008-038986 (Patent Document 1). and needle rollers as rolling elements held by a retainer. In the shell outer ring of Patent Literature 1, both axial end portions located on the axial outer side are folded back by 180 degrees toward the inner diameter side. Further, the outer peripheral surfaces of both ends in the axial direction are tapered. These taper angles are between 5 and 25 degrees. The reason for this is that when the taper angle is 5 degrees to 25 degrees, the introduction into the opening is guided by the tapered surface. Smooth assembly can be performed even with a general-purpose tool. If the taper angle is less than 5 degrees, a sufficient fitting width cannot be ensured when the shell outer ring is press-fitted into the opening of the housing, and the seating of the shell outer ring with respect to the housing becomes insufficient.
特開２００８―０３８９８６号公報Japanese Unexamined Patent Application Publication No. 2008-038986
　近年の軽量化の要請に従い、シェル形針状ころ軸受が圧入される軸箱はアルミニウム等を主成分とする軽合金系軸箱が使用されることが多くなってきている。軽合金系軸箱では、鉄系軸箱に比べてシェル外輪のかじりが発生するリスクが上がる。かじり対策として特許文献１では、シェル外輪の軸線方向端部外周に５度以上２５度以下のテーパを付けることを推奨としているが、５度以上のテーパを付けると、今度はシェル外輪と軸箱が接触する軸線方向寸法が必然的に小さくなり、つまりシェル外輪の軸線方向端部が軸箱から離れてしまい、十分な固定力が得られず温度条件によってはシェル形針状ころ軸受が軸箱から抜ける懸念がある。 Due to the recent demand for weight reduction, the use of light alloy axle boxes with aluminum as the main component is becoming more common for the axle boxes into which drawn cup needle roller bearings are press-fitted. A light alloy axle box has a higher risk of galling of the shell outer ring than an iron axle box. As a countermeasure against galling, Patent Document 1 recommends that the outer periphery of the end portion in the axial direction of the shell outer ring is tapered by 5 degrees or more and 25 degrees or less. In other words, the axial dimension of the drawn cup needle roller bearing is inevitably small, which means that the axial ends of the drawn cup outer ring are separated from the casing. I am worried about getting out of.
　そこで、抜け回避のため、負すきまを設けて締め代を大きくする方法があるが、そうするとかじりのリスクが増大する。そのため、特許文献１より更なる改良を行う必要がある。 Therefore, there is a method of increasing the interference by providing a negative clearance in order to avoid coming off, but this increases the risk of galling. Therefore, it is necessary to make further improvements from Patent Document 1.
　本発明は、上述の実情に鑑み、軸箱にシェル外輪を圧入固定する際、当該圧入時のかじりを防止しつつ、シェル外輪を確り軸箱に固定させることができる構造を提供することを目的とする。 SUMMARY OF THE INVENTION In view of the above circumstances, it is an object of the present invention to provide a structure capable of firmly fixing the shell outer ring to the axle box while preventing the shell outer ring from galling at the time of press fitting and fixing the shell outer ring to the axle box. and
　この目的のため本発明によるシェル形ころ軸受は、シェル外輪と、シェル外輪の中に組み込まれる保持器と、保持器に保持されてシェル外輪の内径面を転動するころとを備えることを前提とする。シェル外輪は、軸箱の開口に圧入固定される円筒形状の外輪本体と、外輪本体の軸線方向両端部から内径側に突出する鍔部とを含み、外輪本体の軸線方向一端部の外周面には軸線方向内側から軸線方向外側に向かって外径が徐々に小さくなるテーパ面が設けられ、テーパ面のテーパ角が０．５度以上５度未満の範囲に含まれる。 For this purpose, the drawn cup roller bearing according to the present invention is premised to have a shell outer ring, a cage incorporated in the shell outer ring, and rollers held by the cage and rolling on the inner diameter surface of the shell outer ring. and The shell outer ring includes a cylindrical outer ring body that is press-fitted into the opening of the axle box, and a flange that protrudes radially inward from both ends of the outer ring body in the axial direction. is provided with a tapered surface whose outer diameter gradually decreases from the inner side to the outer side in the axial direction, and the taper angle of the tapered surface falls within the range of 0.5 degrees or more and less than 5 degrees.
　かかる本発明によれば、従来よりも緩やかなテーパ面が形成されることから、シェル外輪が軸箱の開口に圧入されることによってシェル外輪のテーパ面が開口の内径面に面接触する。これによりシェル外輪と軸箱の接触面積が確保され、シェル外輪は軸箱に確りと圧入固定される。またテーパ面によってシェル外輪は傾くことなく開口に導入され、かじりを防止することができる。軸線方向内側から軸線方向外側に向かって外径が徐々に小さくなるテーパ面とは、軸線方向中央からみて軸線方向端へ向かうほど外径が小さくなる縮径形状をいう。なおテーパ面はシェル外輪の軸線方向両端部のうち、少なくとも圧入される側に設けられる。つまりテーパ面は、シェル外輪の軸線方向両端部にそれぞれ設けられてもよいし、あるいはいずれか一方端のみに設けられてもよい。 According to the present invention, since the tapered surface is formed more gradually than the conventional one, the tapered surface of the shell outer ring comes into surface contact with the inner diameter surface of the opening when the shell outer ring is press-fitted into the opening of the axle box. This secures a contact area between the shell outer ring and the axle box, and the shell outer ring is firmly press-fitted into the axle box. Moreover, the tapered surface allows the outer ring of the shell to be introduced into the opening without tilting, thereby preventing galling. A tapered surface whose outer diameter gradually decreases from the inner side to the outer side in the axial direction refers to a tapered shape in which the outer diameter decreases toward the ends in the axial direction when viewed from the center in the axial direction. The tapered surface is provided at least on the press-fitted side of both ends of the shell outer ring in the axial direction. That is, the tapered surfaces may be provided at both ends of the shell outer ring in the axial direction, respectively, or may be provided at only one end.
　鍔部の板厚は特に限定されないが、円筒体の縁部を折り曲げて鍔部を形成する場合、曲げ加工の容易性のために鍔部は薄いほうが好ましい。しかしながら圧入によって開口に導入されるための剛性を確保するために鍔部は厚いほうが好ましい。本発明の一局面として、外輪本体の軸線方向一端部に設けられる鍔部の板厚が、外輪本体の板厚の４０％以上７５％以下の範囲に含まれる。かかる局面によれば、曲げ加工の容易性と、圧入のための剛性の確保と、双方を満足させることができる。 The plate thickness of the flange is not particularly limited, but when forming the flange by bending the edge of the cylindrical body, the flange is preferably thin for ease of bending. However, it is preferable that the brim portion is thick in order to secure the rigidity for being introduced into the opening by press fitting. As one aspect of the present invention, the plate thickness of the flange portion provided at one axial end portion of the outer ring main body is included in the range of 40% or more and 75% or less of the plate thickness of the outer ring main body. According to this aspect, it is possible to satisfy both the easiness of bending and the securing of rigidity for press-fitting.
　本発明の好ましい局面として、鍔部の軸線方向外側端面と、テーパ面は、外輪本体の軸線方向一端に形成される面取りを介して接続され、シェル外輪の軸線方向寸法が６［ｍｍ］以上であり、テーパ面の軸線方向寸法および面取りの軸線方向寸法の合計が、１．５［ｍｍ］以上３．５［ｍｍ］以下の範囲に含まれる。かかる局面によれば、圧入の容易性と、接触面積の確保を図ることができる。 As a preferred aspect of the present invention, the axially outer end surface of the flange and the tapered surface are connected via a chamfer formed at one axial end of the outer ring main body, and the shell outer ring has an axial dimension of 6 mm or more. Yes, and the sum of the axial dimension of the tapered surface and the axial dimension of the chamfer falls within the range of 1.5 [mm] or more and 3.5 [mm] or less. According to this aspect, it is possible to facilitate press-fitting and secure a contact area.
　テーパ面の径方向寸法は特に限定されないが、本発明のさらに好ましい局面として、テーパ面の径方向寸法は、シェル外輪の外径半径から開口の内径半径を差し引いた締め代の１．１倍以上１．５倍以下の範囲に含まれる。かかる局面によれば、かじりを防止しつつ、接触面積を確保することができる。 Although the radial dimension of the tapered surface is not particularly limited, in a more preferred aspect of the present invention, the radial dimension of the tapered surface is 1.1 times or more the interference obtained by subtracting the inner diameter radius of the opening from the outer diameter radius of the shell outer ring. Included in the range of 1.5 times or less. According to this aspect, it is possible to secure a contact area while preventing galling.
　本発明のシェル形ころ軸受の固定構造は、上述したシェル外輪と、シェル外輪の中に組み込まれる保持器と、保持器に保持されて外輪本体の内径面を転動するころと、シェル外輪の外径寸法よりも小さな内径寸法の開口を有し、開口の内径面が外輪本体の外径面と負すきまで密着する軸箱とを具備する。本発明の一局面として、軸箱は軽合金で形成される。軽合金は例えばアルミニウム等の軽金属であったり、あるいは、アルミニウム等の軽金属を主成分とする合金であったりする。 A fixed structure for a drawn cup roller bearing according to the present invention comprises the above-described shell outer ring, a cage incorporated in the shell outer ring, rollers held by the cage and rolling on the inner diameter surface of the outer ring main body, and the shell outer ring. An axle box has an opening with an inner diameter smaller than the outer diameter, and the inner diameter surface of the opening is in close contact with the outer diameter surface of the outer ring body with a negative clearance. In one aspect of the invention, the axle box is made of a light alloy. A light alloy is, for example, a light metal such as aluminum, or an alloy containing a light metal such as aluminum as a main component.
　このように本発明によれば、軸箱のかじりを防止しつつ、シェル形ころ軸受を軸箱に確りと固定することができる。 Thus, according to the present invention, it is possible to firmly fix the drawn cup roller bearing to the axle box while preventing galling of the axle box.
本発明の一実施形態になるシェル形ころ軸受を示す縦断面図である。1 is a longitudinal sectional view showing a drawn cup roller bearing according to an embodiment of the present invention; FIG. 軸箱に圧入固定された同実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows the same embodiment press-fitted and fixed to the axle box. 図１中、シェル外輪の紙面上部左側部分を示す拡大断面図である。FIG. 2 is an enlarged cross-sectional view showing an upper left portion of the outer race of the shell in FIG. 1 ; 図１中、シェル外輪の紙面上部右側部分を示す拡大断面図である。FIG. 2 is an enlarged cross-sectional view showing an upper right portion of the outer ring of the shell in FIG. 1 ; 図１中、シェル外輪の紙面上部右側部分を示す拡大断面図である。FIG. 2 is an enlarged cross-sectional view showing an upper right portion of the outer ring of the shell in FIG. 1 ;
　以下、本発明の実施の形態を、図面に基づき詳細に説明する。図１は、本発明の一実施形態になるシェル形ころ軸受を示す縦断面図である。図２は、軸箱の開口に圧入固定された同実施形態を示す縦断面図である。シェル形ころ軸受１０は、シェル外輪１１と、保持器２１と、ころ３１とを具備し、図２に示すように軸箱４０の開口４１に圧入固定される。なお図面が煩雑になることを避けるため、図１～図５の断面図では、断面を表す模様が図略される。 Hereinafter, embodiments of the present invention will be described in detail based on the drawings. FIG. 1 is a longitudinal sectional view showing a drawn cup roller bearing according to one embodiment of the present invention. FIG. 2 is a vertical cross-sectional view showing the same embodiment press-fitted and fixed to the opening of the axle box. The drawn cup roller bearing 10 includes a drawn outer ring 11, a retainer 21, and rollers 31, and is press-fitted into an opening 41 of an axle box 40 as shown in FIG. In order to avoid complicating the drawings, in the cross-sectional views of FIGS. 1 to 5, the cross-sectional patterns are omitted.
　シェル外輪１１は、一体物であって外輪本体１２および鍔部１３，１４を備える。鍔部１３は、円筒形状の外輪本体１２の軸線方向一端から、内径側へ略９０度に立ち上がる。外輪本体１２の板厚と鍔部１３の板厚は、略等しいか、あるいは鍔部１３の板厚の方が大きい。鍔部１４は、円筒形状の外輪本体１２の軸線方向他端から、内径側へ略９０度に立ち上がる。鍔部１４の板厚は、外輪本体１２の板厚よりも小さい。略９０度というのは、鍔部１４の角度が外輪本体１２に対して９０±１０度の差を伴ってよいという意味である。 The shell outer ring 11 is an integral body and includes an outer ring main body 12 and flanges 13 and 14 . The flange portion 13 rises from one axial end of the cylindrical outer ring main body 12 toward the inner diameter side at approximately 90 degrees. The plate thickness of the outer ring main body 12 and the plate thickness of the flange portion 13 are substantially the same, or the plate thickness of the flange portion 13 is greater. The flange portion 14 rises from the other end in the axial direction of the cylindrical outer ring main body 12 toward the inner diameter side at approximately 90 degrees. The plate thickness of the flange portion 14 is smaller than the plate thickness of the outer ring main body 12 . Approximately 90 degrees means that the angle of the collar portion 14 may vary by 90±10 degrees with respect to the outer ring main body 12 .
　鍔部１４は、円筒形状の素形材の軸線方向他方縁を、内径側へ徐々に折り曲げて形成されることから、縁曲部ともいう。曲げ加工の容易性確保のため、鍔部１４の板厚は、外輪本体１２の軸線方向中央領域における板厚の４０％以上７５％以下の範囲に含まれる所定値である。 The flange portion 14 is also called an edge curved portion because it is formed by gradually bending the other edge in the axial direction of the cylindrical shaped material toward the inner diameter side. To ensure ease of bending, the plate thickness of the flange portion 14 is a predetermined value within a range of 40% or more and 75% or less of the plate thickness of the central region of the outer ring main body 12 in the axial direction.
　１対の鍔部１３，１４間には、保持器２１およびころ３１が配置される。保持器２１の外径寸法は鍔部１３および／または鍔部１４の内径寸法よりも大きい。円筒形状の保持器２１は、シェル外輪１１の内径側に組み込まれ、鍔部１３，１４によって軸線方向移動を規制される。保持器２１には、周方向に間隔を空けてポケット２２が複数形成される。各ポケット２２にはころ３１が配置され、ころ３１は保持器２１に形成されるころ止め部（図略）によって脱落しないよう保持される。ころ３１は、例えば針状ころであり、外輪本体１２の内径面１２ｃを転動する。このため外輪本体１２の内径面１２ｃは外側軌道面に相当する。 A retainer 21 and rollers 31 are arranged between the pair of flanges 13 and 14 . The outer diameter dimension of cage 21 is larger than the inner diameter dimension of flange portion 13 and/or flange portion 14 . A cylindrical retainer 21 is mounted on the inner diameter side of the shell outer ring 11 and is restrained from moving in the axial direction by flanges 13 and 14 . A plurality of pockets 22 are formed in the retainer 21 at intervals in the circumferential direction. A roller 31 is arranged in each pocket 22, and the roller 31 is held by a roller stop portion (not shown) formed in the retainer 21 so as not to fall off. The rollers 31 are needle rollers, for example, and roll on the inner diameter surface 12 c of the outer ring body 12 . Therefore, the inner diameter surface 12c of the outer ring main body 12 corresponds to the outer raceway surface.
　図３は、シェル外輪の鍔部１３と、外輪本体１２の軸線方向一方端部を示す拡大断面図である。外輪本体１２の軸線方向一方端部は緩やかなテーパ面１５に形成される。テーパ面１５のテーパ角度θは、０．５度以上５度未満の範囲に含まれる所定角度である。内向きフランジ形状の鍔部１３に関し、鍔部１３の外側端面１３ｂとテーパ面１５は断面円弧状のＲ（アール）部１６が形成される。Ｒ部１６は凸曲面の面取りであり、外側端面１３ｂおよびテーパ面１５と滑らかに接続する。図３に示すように、Ｒ部１６の軸線方向位置は、鍔部１３の軸線方向位置に含まれる。これに対しテーパ面１５の軸線方向位置は、鍔部１３および外輪本体１２の軸線方向位置と重なる。軸線方向他方の鍔部１４、テーパ面１５、およびＲ部１６についても同様である。 FIG. 3 is an enlarged cross-sectional view showing the collar portion 13 of the shell outer ring and one axial end of the outer ring main body 12 . One axial end of the outer ring body 12 is formed into a gently tapered surface 15 . A taper angle θ of the tapered surface 15 is a predetermined angle within a range of 0.5 degrees or more and less than 5 degrees. Regarding the inward flange-shaped flange portion 13 , an R (R) portion 16 having an arcuate cross section is formed on the outer end surface 13 b of the flange portion 13 and the tapered surface 15 . The R portion 16 is chamfered to have a convex curved surface and is smoothly connected to the outer end surface 13 b and the tapered surface 15 . As shown in FIG. 3 , the axial position of the R portion 16 is included in the axial position of the collar portion 13 . On the other hand, the axial position of the tapered surface 15 overlaps the axial positions of the flange portion 13 and the outer ring main body 12 . The same applies to the flange portion 14, the tapered surface 15, and the R portion 16 on the other side in the axial direction.
　図４を参照して、外輪本体１２の軸線方向他方端部の内周面には円環溝状の盗み部１８が形成される。盗み部１８は内径面１２ｃよりも外径側へ後退する。盗み部１８の表面は、軸線方向内側で内径面１２ｃと接続し、軸線方向外側で鍔部１４の内側端面と接続する。盗み部１８により、曲げ加工による鍔部１４の形成が容易にされる。 With reference to FIG. 4, an annular groove-shaped relief portion 18 is formed on the inner peripheral surface of the outer ring main body 12 at the other end in the axial direction. The recessed portion 18 retreats radially outward from the inner diameter surface 12c. The surface of the recessed portion 18 connects with the inner diameter surface 12c on the inner side in the axial direction, and connects with the inner end surface of the collar portion 14 on the outer side in the axial direction. The relief portion 18 facilitates formation of the collar portion 14 by bending.
　シェル外輪１１は図２に示すように断面円形の開口４１に圧入固定されることから、圧入固定前のシェル外輪１１の原形状態の外径寸法が、開口４１の原形状態の内径寸法よりもわずかに大きい、この負すきまの寸法差を締め代領域Ｓといい、図１、図３～図５の外輪本体外径部分にハッチング模様を付して表示される。締め代領域Ｓは、全周に亘って外輪本体１２の軸線方向一方端部から他方端部までを占めており、テーパ面１５と重なる。 As shown in FIG. 2, the shell outer ring 11 is press-fitted and fixed in the opening 41 having a circular cross section. The large dimensional difference of this negative clearance is called an interference region S, which is indicated by hatching on the outer diameter portion of the outer ring main body in FIGS. 1 and 3 to 5. The interference region S occupies the entire circumference from one axial end to the other axial end of the outer ring main body 12 and overlaps the tapered surface 15 .
　ところで本実施形態によれば、テーパ面１５のテーパ角θを０．５度以上５度未満の所定値としたことから、テーパ角が従来よりも緩やかになり、図２に示すように締め代領域Ｓがシェル外輪１１の軸線方向一方端部から他方端部まで十分に確保される。本実施形態によれば、シェル外輪１１と軸箱４０の接触面積が広くなり、シェル外輪１１は軸箱４０に固定される。したがってシェル外輪１１が軸箱４０から抜け出す虞が解消される。 By the way, according to the present embodiment, since the taper angle θ of the tapered surface 15 is set to a predetermined value of 0.5 degrees or more and less than 5 degrees, the taper angle becomes gentler than the conventional one, and the interference is reduced as shown in FIG. A region S is sufficiently secured from one axial end to the other axial end of the shell outer ring 11 . According to this embodiment, the contact area between the shell outer ring 11 and the axle box 40 is increased, and the shell outer ring 11 is fixed to the axle box 40 . Therefore, the possibility that the shell outer ring 11 will slip out of the axle box 40 is eliminated.
　また本実施形態はテーパ面１５を有することから、軸箱４０が軽合金製である場合であっても、シェル形ころ軸受１０を開口４１に圧入する際、軸箱４０のかじりが防止される。 Further, since this embodiment has the tapered surface 15, even if the axle box 40 is made of a light alloy, galling of the axle box 40 is prevented when the drawn cup roller bearing 10 is press-fitted into the opening 41. .
　ここで附言すると、図１に示すように本実施形態のシェル外輪１１の軸線方向寸法Ｌｓは８［ｍｍ］以上である。図４を参照して、片側のテーパ面１５の軸線方向寸法およびＲ部１６の軸線方向寸法の合計Ｌｑは、接触面積確保のため２．０≦Ｌｑ≦３．５［ｍｍ］に推奨される。この理由として、Ｌｑ＜２．０［ｍｍ］の場合、圧入する際のかじりが懸念されるためである。またＬｑ＞３．５［ｍｍ］の場合、接触面積が不十分となり、シェル外輪１１が軸箱４０から脱落するためである。 To add here, as shown in FIG. 1, the axial dimension Ls of the shell outer ring 11 of this embodiment is 8 [mm] or more. Referring to FIG. 4, the total Lq of the axial dimension of the tapered surface 15 on one side and the axial dimension of the R portion 16 is recommended to be 2.0≦Lq≦3.5 [mm] in order to secure the contact area. . The reason for this is that when Lq<2.0 [mm], galling may occur during press-fitting. Also, when Lq>3.5 [mm], the contact area becomes insufficient, and the shell outer ring 11 falls off from the axle box 40 .
　同様の理由により、Ｌｓ＜８［ｍｍ］の場合、Ｌｑ＜２．０［ｍｍ］に推奨される。 For the same reason, when Ls < 8 [mm], it is recommended that Lq < 2.0 [mm].
　かかる本実施形態に基づくと、Ｌｓ≧６［ｍｍ］の場合、１．５≦Ｌｑ≦３．５［ｍｍ］に推奨される。 Based on this embodiment, when Ls≧6 [mm], it is recommended that 1.5≦Lq≦3.5 [mm].
　図４に示す実施形態では、締め代領域ＳがＲ部１６に達することが理解される。つまり締め代Ｓの半径寸法Ｒｓと、テーパ面１５の半径寸法Ｒｔの関係は、
［式１］Ｒｔ／Ｒｓ＜１．０
を満足する。ここで、締め代Ｓの半径寸法Ｒｓとは、軸箱４０の内径寸法と外輪本体１２外径寸法の差の半分の値である。また、テーパ面１５の半径寸法Ｒｔとは、テーパ母線が外輪本体１２の外径面１７と、R部１６とそれぞれ交差した点Ｐ,Ｑの半径方向の距離の値である。 It is understood that the interference region S reaches the R portion 16 in the embodiment shown in FIG. That is, the relationship between the radial dimension Rs of the interference S and the radial dimension Rt of the tapered surface 15 is
[Formula 1] Rt/Rs<1.0
satisfy. Here, the radial dimension Rs of the interference S is half the difference between the inner diameter dimension of the axle box 40 and the outer diameter dimension of the outer ring main body 12 . The radial dimension Rt of the tapered surface 15 is the value of the radial distance between points P and Q where the tapered generatrix intersects the outer diameter surface 17 of the outer ring main body 12 and the R portion 16, respectively.
　式１によれば、シェル形ころ軸受１０を開口４１に圧入すると、テーパ面１５が開口４１の内径面に接触して、シェル外輪１１の接触面積が確保される。この結果、シェル外輪１１は軸箱４０に確りと固定される。 According to Formula 1, when the drawn cup roller bearing 10 is press-fitted into the opening 41, the tapered surface 15 comes into contact with the inner diameter surface of the opening 41, and the contact area of the shell outer ring 11 is ensured. As a result, the shell outer ring 11 is firmly fixed to the axle box 40 .
　あるいは図４に代えて、図５に示す変形例であってもよい。この変形例では、
［式２］１．１≦Ｒｔ／Ｒｓ≦１．５
を満足する。式２によれば、シェル形ころ軸受１０を開口４１に円滑に圧入することができる。 Alternatively, instead of FIG. 4, a modified example shown in FIG. 5 may be used. In this variant,
[Formula 2] 1.1 ≤ Rt/Rs ≤ 1.5
satisfy. According to Formula 2, the drawn cup roller bearing 10 can be smoothly press-fitted into the opening 41 .
　なおＲｔ／Ｒsが１．５を超える場合、シェル形ころ軸受１０を開口４１に問題なく圧入できるが、製造過程においてテーパ面１５の径方向長さが長すぎると圧入後にシェル外輪１１の接触面積を確保できない懸念がある。 If Rt/Rs exceeds 1.5, the drawn cup roller bearing 10 can be press-fitted into the opening 41 without any problem. There is a concern that it will not be possible to secure
　本実施形態によれば、鍔部１４の板厚は、外輪本体１２の軸線方向中央領域における板厚の４０％以上７５％以下の範囲に含まれる所定値である。これにより、鍔部１４を含むシェル外輪１１の軸線方向他方端部の剛性が低くなり、鍔部１４から開口４１に圧入する際、軸箱４０のかじりを防止することができる。なお鍔部１４の板厚が外輪本体１２の板厚の４０％未満の場合、シェル外輪１１の軸線方向他方端部の剛性が低すぎて、圧入する際に座屈する虞がある。また鍔部１４の板厚が外輪本体１２の板厚の４０％未満の場合、シェル外輪１１の軸線方向他方端部の剛性が高すぎて、圧入する際に軸箱４０にかじりが生じる虞がある。 According to the present embodiment, the thickness of the flange portion 14 is a predetermined value within the range of 40% or more and 75% or less of the thickness of the central region of the outer ring main body 12 in the axial direction. As a result, the rigidity of the other end in the axial direction of the shell outer ring 11 including the collar portion 14 is reduced, and galling of the axle box 40 can be prevented when the collar portion 14 is press-fitted into the opening 41 . If the plate thickness of the flange portion 14 is less than 40% of the plate thickness of the outer ring main body 12, the rigidity of the other axial end portion of the shell outer ring 11 is too low, and there is a risk of buckling during press fitting. If the plate thickness of the flange portion 14 is less than 40% of the plate thickness of the outer ring main body 12, the rigidity of the other axial end portion of the shell outer ring 11 is too high, and galling may occur in the axle box 40 when it is press-fitted. be.
　なお座屈防止のため、本実施形態では、シェル外輪１１の全体に浸炭焼入れが施され、さらにシェル外輪１１のうち鍔部１４を含む軸線方向他方端部に高周波焼入れ焼きなましが施されている。これにより、シェル外輪１１の軸線方向他方端部の剛性が高められている。 In order to prevent buckling, in the present embodiment, the shell outer ring 11 is entirely carburized and hardened, and the other axial end of the shell outer ring 11 including the flange 14 is induction hardened and annealed. Thereby, the rigidity of the other end in the axial direction of the shell outer ring 11 is increased.
　本発明は、カーエアコン用コンプレッサの転がり軸受、およびカーエアコン用コンプレッサ以外であっても軽合金系軸箱に組み込まれる転がり軸受において有利に利用される。 The present invention can be advantageously used in rolling bearings for car air-conditioning compressors and rolling bearings incorporated in light alloy axle boxes even in cases other than car air-conditioning compressors.
　１０　シェル形ころ軸受、　　　１１　シェル外輪、　　　１２　外輪本体、　　　１２ｃ　内径面、　　　１３，１４　鍔部、　　　１５　テーパ面、　　　１６　Ｒ部、　　　１８　盗み部、　　　２１　保持器、　　　４０　軸箱、　　　４１　開口。 10 Drawn cup roller bearing, 11 Shell outer ring, 12 Outer ring main body, 12c inner diameter surface, 13, 14 flange portion, 15 tapered surface, 16 R portion, 18 recessed portion, 21 retainer, 40 axle box, 41 opening.

Claims (6)

  1. 　シェル外輪と、
    　前記シェル外輪の中に組み込まれる保持器と、
    　前記保持器に保持されて前記シェル外輪の内径面を転動するころとを備え、
    　　前記シェル外輪は、軸箱の開口に圧入固定される円筒形状の外輪本体と、前記外輪本体の軸線方向両端部から内径側に突出する鍔部とを含み、
    　前記外輪本体の軸線方向一端部の外周面には軸線方向内側から軸線方向外側に向かって外径が徐々に小さくなるテーパ面が設けられ、
    　前記テーパ面のテーパ角が０．５度以上５度未満の範囲に含まれる、シェル形ころ軸受。     a shell outer ring;
    a retainer incorporated in the shell outer ring;
    rollers held by the retainer and rolling on the inner diameter surface of the shell outer ring;
    The shell outer ring includes a cylindrical outer ring main body that is press-fitted into an opening of the axle box and fixed, and flanges that protrude radially inward from both ends of the outer ring main body in the axial direction,
    The outer peripheral surface of one axial end of the outer ring main body is provided with a tapered surface whose outer diameter gradually decreases from the axially inner side to the axially outer side,
    A drawn cup roller bearing, wherein the tapered surface has a taper angle of 0.5 degrees or more and less than 5 degrees.
  2. 　前記外輪本体の軸線方向一端部に設けられる前記鍔部の板厚が、前記外輪本体の板厚の４０％以上７５％以下の範囲に含まれる、請求項１に記載のシェル形ころ軸受。 The drawn cup roller bearing according to claim 1, wherein the plate thickness of the flange provided at one axial end of the outer ring body is within a range of 40% or more and 75% or less of the plate thickness of the outer ring body.
  3. 　前記鍔部の軸線方向外側端面と、前記テーパ面は、前記外輪本体の軸線方向一端に形成される面取りを介して接続され、
    　前記シェル外輪の軸線方向寸法が６［ｍｍ］以上であり、
    　前記テーパ面の軸線方向寸法および前記面取りの軸線方向寸法の合計が、１．５［ｍｍ］以上３．５［ｍｍ］以下の範囲に含まれる、請求項１に記載のシェル形ころ軸受。     The axially outer end surface of the flange portion and the tapered surface are connected via a chamfer formed at one axial end of the outer ring main body,
    The shell outer ring has an axial dimension of 6 [mm] or more,
    2. The drawn cup roller bearing according to claim 1, wherein the sum of the axial dimension of said tapered surface and the axial dimension of said chamfer is within the range of 1.5 [mm] or more and 3.5 [mm] or less.
  4. 　前記テーパ面の径方向寸法は、前記シェル外輪の外径半径から前記開口の内径半径を差し引いた締め代の１．１倍以上１．５倍以下の範囲に含まれる、請求項１に記載のシェル形ころ軸受。 2. The radial dimension of the tapered surface according to claim 1, wherein the radial dimension is within a range of 1.1 to 1.5 times the interference obtained by subtracting the inner diameter radius of the opening from the outer diameter radius of the shell outer ring. Drawn cup roller bearing.
  5. 　請求項１～４のいずれかに記載のシェル形ころ軸受と、
    　前記シェル外輪の外径寸法よりも小さな内径寸法の開口を有し、前記開口の内径面が前記外輪本体の外径面と負すきまで密着する軸箱とを具備する、シェル形ころ軸受の固定構造。     a drawn cup roller bearing according to any one of claims 1 to 4;
    Fixing of a drawn cup roller bearing, comprising an axle box having an opening with an inner diameter smaller than the outer diameter of the shell outer ring, the inner diameter surface of the opening closely contacting the outer diameter surface of the outer ring main body with a negative clearance. structure.
  6. 　前記軸箱は軽合金で形成される、請求項５に記載のシェル形ころ軸受の固定構造。 The fixed structure for a drawn cup roller bearing according to claim 5, wherein the axle box is made of a light alloy.
PCT/JP2022/031365 2021-09-16 2022-08-19 Shell roller bearing and fixing structure for shell roller bearing WO2023042603A1 (en)

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JP2021-150919 2021-09-16

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4970042A (en) * 1972-11-13 1974-07-06
JPH0312016U (en) * 1989-06-15 1991-02-07
JPH11303863A (en) * 1998-04-15 1999-11-02 Nippon Seiko Kk Shell type roller bearing
JPH11351145A (en) * 1998-06-05 1999-12-21 Ntn Corp Needle roller bearing for swash plate compressor
JP2008038986A (en) * 2006-08-03 2008-02-21 Nsk Ltd Shell type needle bearing

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4970042A (en) * 1972-11-13 1974-07-06
JPH0312016U (en) * 1989-06-15 1991-02-07
JPH11303863A (en) * 1998-04-15 1999-11-02 Nippon Seiko Kk Shell type roller bearing
JPH11351145A (en) * 1998-06-05 1999-12-21 Ntn Corp Needle roller bearing for swash plate compressor
JP2008038986A (en) * 2006-08-03 2008-02-21 Nsk Ltd Shell type needle bearing

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CN117940685A (en) 2024-04-26

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