JP2016038079A - Roller bearing - Google Patents

Roller bearing Download PDF

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JP2016038079A
JP2016038079A JP2014163713A JP2014163713A JP2016038079A JP 2016038079 A JP2016038079 A JP 2016038079A JP 2014163713 A JP2014163713 A JP 2014163713A JP 2014163713 A JP2014163713 A JP 2014163713A JP 2016038079 A JP2016038079 A JP 2016038079A
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inner ring
roller bearing
ring raceway
groove
end surface
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JP6369211B2 (en
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村田　順司
Junji Murata
順司 村田
鎌本　繁夫
Shigeo Kamamoto
繁夫 鎌本
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JTEKT Corp
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JTEKT Corp
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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
    • F16C19/34—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 both radial and axial load
    • F16C19/36—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 both radial and axial load with a single row of rollers
    • F16C19/364—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 both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/225—Details of the ribs supporting the end of the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a roller bearing capable of reducing sliding friction without generating an edge load between an end surface of a roller and a flange end surface of an inner ring.SOLUTION: A conical roller bearing 1 includes: an outer ring 2 having an outer ring raceway surface 2a at an inner periphery thereof; an inner ring 3 having an inner ring raceway surface 3a at an outer periphery thereof and having a radially outwardly protruding flange 7a on one side in an axial direction of the inner ring raceway 3a; and a plurality of rollers 4 rotatably disposed between the outer ring raceway surface 2a and the inner ring raceway surface 3a. An end surface 7a of the flange 7a has a lubrication groove 8 on a further radially outside than a contact portion C with end surfaces 4a of the rollers 4.SELECTED DRAWING: Figure 1

Description

本発明は、ころ軸受に関する。   The present invention relates to a roller bearing.

従来のころ軸受においては、ころの端面と内輪の鍔部端面との接触によるすべり摩擦を低減するために、両端面の接触部分に潤滑油を供給するための溝が、内輪の鍔部端面に形成されている（例えば、特許文献１参照）。   In conventional roller bearings, in order to reduce sliding friction due to contact between the roller end surface and the inner ring flange end surface, a groove for supplying lubricating oil to the contact portion of both end surfaces is provided on the inner ring flange end surface. (For example, refer patent document 1).

特開２０１３−１００８３９号公報JP 2013-1000083 A

しかし、前記特許文献１に記載された溝は、内輪の鍔部端面において、ころの端面との接触部分を含む径方向全体に亘って形成されているため、ころの端面が溝の開口端縁に接触することでエッジロードが発生し、かえってすべり摩擦が増大するおそれがある。
本発明はこのような事情に鑑みてなされたものであり、ころの端面と内輪の鍔部端面との間で、エッジロードを発生させることなく、すべり摩擦を低減することができるころ軸受を提供することを目的とする。 However, since the groove described in Patent Document 1 is formed over the entire radial direction including the contact portion with the end face of the roller at the flange end face of the inner ring, the end face of the roller is the opening edge of the groove. Contact with the surface may cause an edge load, which may increase sliding friction.
The present invention has been made in view of such circumstances, and provides a roller bearing capable of reducing sliding friction without generating an edge load between the end surface of the roller and the flange end surface of the inner ring. The purpose is to do.

上記目的を達成するための本発明は、内周に外輪軌道面を有する外輪と、外周に内輪軌道面を有するとともに、前記内輪軌道面の少なくとも軸方向一方側に径方向外方へ突出する鍔部を有する内輪と、前記外輪軌道面及び前記内輪軌道面との間に転動自在に介在する複数のころと、を備えたころ軸受であって、前記鍔部の端面には、前記ころの端面との接触部分よりも径方向外側に潤滑溝が設けられていることを特徴としている。   To achieve the above object, the present invention provides an outer ring having an outer ring raceway surface on the inner periphery, an inner ring raceway surface on the outer periphery, and protruding radially outward at least on one axial side of the inner ring raceway surface. A roller bearing comprising: an inner ring having a portion; and a plurality of rollers movably interposed between the outer ring raceway surface and the inner ring raceway surface, wherein the end surface of the flange includes A lubrication groove is provided on the outer side in the radial direction from the contact portion with the end face.

上記のように構成されたころ軸受によれば、内輪の鍔部の端面において、ころの端面との接触部分よりも径方向外側に潤滑溝が設けられているため、ころの端面が潤滑溝の開口端縁に接触することがない。したがって、ころの端面と潤滑溝の開口端縁との間でエッジロードが発生するのを防止することができる。また、潤滑溝から、鍔部の端面ところの端面との接触部分に潤滑油が供給されることで、これら両端面同士の接触によるすべり摩擦を低減することができる。   According to the roller bearing configured as described above, the end face of the inner ring is provided with a lubricating groove on the outer side in the radial direction from the contact portion with the end face of the roller. There is no contact with the opening edge. Therefore, it is possible to prevent an edge load from occurring between the end face of the roller and the opening edge of the lubricating groove. Further, the lubricating oil is supplied from the lubrication groove to the contact portion with the end surface of the flange portion, so that the sliding friction due to the contact between the both end surfaces can be reduced.

上記ころ軸受において、前記潤滑溝は、軸方向断面において径方向外端から径方向内端へ向かうに従って溝深さが漸次浅くなるように楔形状とされているのが好ましい。
この場合、楔形状の潤滑溝に溜まった潤滑油は、溝深さが浅く形成された潤滑溝の径方向内端から上記接触部分に向かって流れ易くなるため、上記両端面の接触によるすべり摩擦を効果的に低減することができる。また、潤滑溝に溜まった潤滑油は、溝深さが深く形成された潤滑溝の径方向外端から径方向外方に流出しにくいため、上記接触部分への潤滑油の供給量が低減するのを抑制することができる。 In the roller bearing, it is preferable that the lubrication groove has a wedge shape so that the groove depth gradually decreases in the axial section from the radially outer end toward the radially inner end.
In this case, the lubricating oil accumulated in the wedge-shaped lubricating groove is likely to flow from the radially inner end of the lubricating groove formed with a shallow groove depth toward the contact portion. Can be effectively reduced. Further, since the lubricating oil accumulated in the lubricating groove is unlikely to flow out radially outward from the radially outer end of the lubricating groove formed with a deep groove depth, the amount of lubricating oil supplied to the contact portion is reduced. Can be suppressed.

上記ころ軸受において、前記ころの端面には、軸方向に窪ませた逃げ部が形成されており、軸方向断面において、前記鍔部の端面における径方向外端から前記潤滑溝の径方向外端までの距離が、前記鍔部の端面における径方向外端から前記逃げ部の開口端に対向する位置までの距離よりも短く設定されているのが好ましい。
この場合、鍔部の端面において、潤滑溝の径方向外端は、ころの逃げ部の開口端に対向する位置よりも径方向外側に配置される。つまり、潤滑溝の径方向外端部には、その対向する位置にころの逃げ部が存在するため、潤滑溝がころの端面により塞がれるのを防止することができる。したがって、潤滑溝よりも径方向外方にある潤滑油を、潤滑溝を介して上記接触部分に確実に供給することできる。 In the roller bearing, an end portion recessed in the axial direction is formed on the end surface of the roller, and the radial outer end of the lubrication groove extends from the radial outer end on the end surface of the flange portion in the axial section. Is preferably set shorter than the distance from the radially outer end of the end surface of the flange portion to the position facing the opening end of the escape portion.
In this case, on the end face of the flange portion, the radially outer end of the lubricating groove is disposed on the radially outer side than the position facing the opening end of the roller relief portion. In other words, since the roller relief portion exists at the opposed position at the radially outer end of the lubrication groove, it is possible to prevent the lubrication groove from being blocked by the end surface of the roller. Therefore, the lubricating oil that is radially outward from the lubricating groove can be reliably supplied to the contact portion via the lubricating groove.

本発明のころ軸受によれば、ころの端面と内輪の鍔部端面との間で、エッジロードを発生させることなく、すべり摩擦を低減することができる。   According to the roller bearing of the present invention, sliding friction can be reduced without generating an edge load between the end face of the roller and the flange end face of the inner ring.

本発明の一実施形態に係るころ軸受を示す軸方向断面図である。It is an axial sectional view showing a roller bearing according to an embodiment of the present invention. 上記ころ軸受における内輪の大鍔部端面の形状を説明する軸方向拡大断面図である。It is an axial direction expanded sectional view explaining the shape of the large collar part end surface of the inner ring | wheel in the said roller bearing. 上記大鍔部端面を図１のＡ方向から見た図である。It is the figure which looked at the said big collar part end surface from the A direction of FIG. 上記潤滑溝の変形例を示す軸方向拡大断面図である。It is an axial direction expanded sectional view which shows the modification of the said lubricating groove.

次に、本発明の好ましい実施形態について添付図面を参照しながら説明する。
図１は、本発明の一実施形態に係るころ軸受を示す軸方向断面図である。図１に示すように、本実施形態のころ軸受は円すいころ軸受１からなる。円すいころ軸受１は、外輪２と、外輪２の内周側に同心に配置された内輪３と、外輪２と内輪３との間に配列された複数の円すいころ４と、複数の円すいころ４を円周方向に沿って所定間隔毎に保持している保持器５とを備えている。 Next, preferred embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is an axial sectional view showing a roller bearing according to an embodiment of the present invention. As shown in FIG. 1, the roller bearing of the present embodiment includes a tapered roller bearing 1. The tapered roller bearing 1 includes an outer ring 2, an inner ring 3 concentrically arranged on the inner peripheral side of the outer ring 2, a plurality of tapered rollers 4 arranged between the outer ring 2 and the inner ring 3, and a plurality of tapered rollers 4. Are held at predetermined intervals along the circumferential direction.

外輪２は、軸受鋼や機械構造用鋼等を用いて形成された環状の部材であり、その内周には、円すいころ４が転動するように、円すい面からなる外輪軌道面２ａが形成されている。
内輪３も、外輪２と同様に、軸受鋼や機械構造用鋼等を用いて形成された環状の部材であり、その外周には、外輪軌道面２ａに対向しているとともに、複数の円すいころ４が転動するように、円すい面からなる内輪軌道面３ａが形成されている。
内輪３の外周には、内輪軌道面３ａの軸方向一端側に隣接して小鍔部６が径方向外方へ突出して形成され、内輪軌道面３ａの軸方向他端側に隣接して大鍔部７が径方向外方へ突出して形成されている。大鍔部７の内輪軌道面３ａ側の端面（以下、大鍔部端面ともいう）７ａは凹曲面状に形成されている。 The outer ring 2 is an annular member formed using bearing steel, machine structural steel, or the like, and an outer ring raceway surface 2a composed of a conical surface is formed on the inner periphery thereof so that the tapered roller 4 rolls. Has been.
Similarly to the outer ring 2, the inner ring 3 is an annular member formed using bearing steel, machine structural steel, or the like, and has an outer periphery facing the outer ring raceway surface 2a and a plurality of tapered rollers. An inner ring raceway surface 3a made of a conical surface is formed so that 4 rolls.
On the outer periphery of the inner ring 3, a small flange portion 6 is formed to protrude radially outward adjacent to one axial end side of the inner ring raceway surface 3 a and is large adjacent to the other axial end side of the inner ring raceway surface 3 a. The collar portion 7 is formed so as to protrude outward in the radial direction. An end surface (hereinafter also referred to as a large collar end surface) 7a on the inner ring raceway surface 3a side of the large collar portion 7 is formed in a concave curved surface shape.

円すいころ４は、軸受鋼等を用いて形成された部材であり、外輪軌道面２ａと内輪軌道面３ａとの間に転動自在に介在している。円すいころ４の大径側端面４ａは、凸曲面状に形成されており、内輪３の大鍔部端面７ａに摺接するようになっている。
円すいころ４の大径側端面４ａには、軸方向内側に窪ませた逃げ部４ｂが形成されている。この逃げ部４ｂは、図３に示す正面視において円すいころ４の軸線を中心として円形状に形成されている。 The tapered roller 4 is a member formed using bearing steel or the like, and is interposed between the outer ring raceway surface 2a and the inner ring raceway surface 3a so as to roll freely. The large-diameter side end surface 4a of the tapered roller 4 is formed in a convex curved surface shape, and is in sliding contact with the large collar end surface 7a of the inner ring 3.
On the large-diameter side end surface 4a of the tapered roller 4, a relief portion 4b that is recessed inward in the axial direction is formed. The escape portion 4b is formed in a circular shape with the axis of the tapered roller 4 as the center in the front view shown in FIG.

図２は、内輪３の大鍔部端面７ａの形状を説明する軸方向拡大断面図である。また、図３は、その大鍔部端面７ａを図１のＡ方向から見た図である。
図２及び図３に示すように、大鍔部端面７ａには、円すいころ４の大径側端面４ａとの接触部分Ｃよりも径方向外側に潤滑溝８が形成されている。潤滑溝８には、上記接触部分Ｃに供給される潤滑油が一時的に溜められる。 FIG. 2 is an axially enlarged sectional view for explaining the shape of the large collar end surface 7 a of the inner ring 3. FIG. 3 is a view of the large collar end surface 7a as viewed from the direction A in FIG.
As shown in FIGS. 2 and 3, a lubricating groove 8 is formed on the large flange end surface 7 a on the radially outer side than the contact portion C with the large diameter side end surface 4 a of the tapered roller 4. Lubricating oil supplied to the contact portion C is temporarily stored in the lubricating groove 8.

図３に示すように、潤滑溝８は、大鍔部端面７ａの全周に亘って円環状に形成されている。また、図２に示すように、潤滑溝８は、軸方向断面において、径方向外端（図中の上端）から径方向内端（図中の下端）へ向かうに従って溝深さが漸次浅くなるように楔形状とされている。具体的には、潤滑溝８は、軸方向断面において、大鍔部端面７ａに対してほぼ垂直に形成された周面８ａと、大鍔部端面７ａに対して所定の傾斜角度θで傾斜した底面８ｂとを有している。   As shown in FIG. 3, the lubricating groove 8 is formed in an annular shape over the entire circumference of the large collar end surface 7a. Further, as shown in FIG. 2, the groove depth of the lubricating groove 8 gradually decreases from the radially outer end (upper end in the drawing) to the radial inner end (lower end in the drawing) in the axial section. It is made into a wedge shape. Specifically, the lubricating groove 8 is inclined at a predetermined inclination angle θ with respect to the circumferential surface 8a formed substantially perpendicular to the large collar end surface 7a and the large collar end surface 7a in the axial section. And a bottom surface 8b.

図２に示す軸方向断面において、大鍔部端面７ａにおける径方向外端から潤滑溝８の径方向外端までの距離Ｌａは、大鍔部端面７ａにおける径方向外端から円すいころ４の逃げ部４ｂの開口端に対向する位置までの距離Ｌｂよりも短く設定されている。また、上記距離Ｌｂは、大鍔部端面７ａにおける径方向外端から潤滑溝８の径方向内端までの距離Ｌｃよりも短く設定されている。さらに、潤滑溝８の上記傾斜角度θは、４５°未満に設定されている。   In the axial cross section shown in FIG. 2, the distance La from the radial outer end of the large flange end surface 7a to the radial outer end of the lubricating groove 8 is the clearance of the tapered roller 4 from the radial outer end of the large flange end surface 7a. It is set to be shorter than the distance Lb to the position facing the opening end of the portion 4b. The distance Lb is set to be shorter than the distance Lc from the radially outer end of the large collar end surface 7a to the radially inner end of the lubricating groove 8. Further, the inclination angle θ of the lubricating groove 8 is set to be less than 45 °.

以上の構成により、大鍔部端面７ａにおいて、潤滑溝８の径方向外端は、逃げ部４ｂの開口端に対向する位置よりも径方向外側に配置される。つまり、潤滑溝８の径方向外端部には、その対向する位置に逃げ部４ｂが存在するため、潤滑油は、図２及び図３の実線矢印で示すように、大鍔部端面７ａの径方向外端部から逃げ部４ｂを通過して、潤滑溝８に一時的に溜められる。そして、潤滑溝８に溜められた潤滑油は、潤滑溝８の溝深さが浅い径方向内端から接触部分Ｃに向けて径方向内方に流れる。   With the above configuration, the radial outer end of the lubrication groove 8 is arranged on the outer side in the radial direction with respect to the opening end of the escape portion 4b on the large flange end face 7a. In other words, since the relief portion 4b exists at the opposed position at the radially outer end portion of the lubricating groove 8, the lubricating oil flows on the large flange end surface 7a as shown by the solid line arrows in FIGS. It passes from the radially outer end portion through the escape portion 4 b and is temporarily stored in the lubricating groove 8. The lubricating oil stored in the lubricating groove 8 flows radially inward from the radially inner end toward which the groove depth of the lubricating groove 8 is shallow toward the contact portion C.

以上、本実施形態の円すいころ軸受１によれば、内輪３の大鍔部端面７ａにおいて、円すいころ４の大径側端面４ａとの接触部分Ｃよりも径方向外側に潤滑溝８が設けられているため、円すいころ４の大径側端面４ａが潤滑溝８の開口端縁に接触することがない。したがって、円すいころ４の大径側端面４ａと潤滑溝８の開口端縁との間でエッジロードが発生するのを防止することができる。また、潤滑溝８から、大鍔部端面７ａと円すいころ４の大径側端面４ａと接触部分Ｃに潤滑油が供給されることで、これら両端面７ｂ，４ａ同士の接触によるすべり摩擦を低減することができる。   As described above, according to the tapered roller bearing 1 of the present embodiment, the lubricating groove 8 is provided on the outer side in the radial direction from the contact portion C with the large-diameter side end surface 4a of the tapered roller 4 at the large flange end surface 7a of the inner ring 3. Therefore, the large-diameter side end face 4 a of the tapered roller 4 does not contact the opening edge of the lubricating groove 8. Therefore, it is possible to prevent an edge load from occurring between the large-diameter side end face 4 a of the tapered roller 4 and the opening edge of the lubricating groove 8. Further, the lubricating oil is supplied from the lubricating groove 8 to the large flange end surface 7a, the large diameter side end surface 4a of the tapered roller 4 and the contact portion C, thereby reducing sliding friction due to contact between the both end surfaces 7b, 4a. can do.

また、潤滑溝８は、軸方向断面において径方向外端から径方向内端へ向かうに従って溝深さが漸次浅くなるように楔形状とされているため、以下の作用効果を奏する。すなわち、潤滑溝８に溜まった潤滑油は、溝深さが浅く形成された潤滑溝８の径方向内端から接触部分Ｃに向かって流れ易くなるため、上記両端面７ｂ，４ａ同士の接触によるすべり摩擦を効果的に低減することができる。また、潤滑溝８に溜まった潤滑油は、溝深さが深く形成された潤滑溝８の径方向外端から径方向外方に流出しにくいため、接触部分Ｃへの潤滑油の供給量が低減するのを抑制することができる。   Further, the lubrication groove 8 has a wedge shape so that the groove depth gradually becomes shallower from the radially outer end toward the radially inner end in the axial section, and thus has the following effects. That is, since the lubricating oil accumulated in the lubricating groove 8 is likely to flow from the radially inner end of the lubricating groove 8 formed with a shallow groove depth toward the contact portion C, the contact between the both end faces 7b and 4a results. Sliding friction can be effectively reduced. Further, since the lubricating oil accumulated in the lubricating groove 8 does not easily flow out radially outward from the radially outer end of the lubricating groove 8 formed with a deep groove depth, the amount of lubricating oil supplied to the contact portion C is small. Reduction can be suppressed.

また、潤滑溝８の径方向外端は、逃げ部４ｂの開口端に対向する位置よりも径方向外側に配置されているため、潤滑溝８の径方向外端部には、その対向する位置に逃げ部４ｂが存在している。したがって、潤滑溝８が円すいころ４の大径側端面４ａにより塞がれるのを防止することができるため、潤滑溝８よりも径方向外方にある潤滑油を、潤滑溝８を介して接触部分Ｃに確実に供給することできる。   Further, since the radially outer end of the lubrication groove 8 is disposed radially outside the position facing the opening end of the escape portion 4b, the radially outer end portion of the lubrication groove 8 is positioned opposite to the position. There is an escape portion 4b. Accordingly, since the lubricating groove 8 can be prevented from being blocked by the large-diameter side end face 4 a of the tapered roller 4, the lubricating oil that is radially outward from the lubricating groove 8 is contacted via the lubricating groove 8. Part C can be reliably supplied.

図４は、潤滑溝８の変形例を示す軸方向拡大断面図である。
図４に示すように、本変形例では、大鍔部端面７ａの径方向外端部に、全周に亘って面取り面７ａ１が形成されている。また、内輪３の大鍔部７の外周面には、例えば鉄等の金属製からなる環状板１０が固定されている。環状板１０は、その軸方向内端部（図中の左端部）に大鍔部７の外周面の軸方向内端よりも軸方向内方に突出する突出部１０ａを有している。これにより、本変形例の大鍔部端面７ａには、上記突出部１０ａの内周面１０ａ１を周面８ａとし、かつ上記面取り面７ａ１を底面８ｂとした円環状の潤滑溝８が設けられている。 FIG. 4 is an axially enlarged sectional view showing a modified example of the lubricating groove 8.
As shown in FIG. 4, in this modification, a chamfered surface 7a1 is formed over the entire circumference at the radially outer end of the large collar end surface 7a. An annular plate 10 made of metal such as iron is fixed to the outer peripheral surface of the large collar portion 7 of the inner ring 3. The annular plate 10 has a protruding portion 10a that protrudes inward in the axial direction from the inner end in the axial direction of the outer peripheral surface of the large collar portion 7 at the inner end in the axial direction (left end in the drawing). As a result, an annular lubricating groove 8 is provided on the large collar end surface 7a of the present modification, with the inner peripheral surface 10a1 of the protruding portion 10a as the peripheral surface 8a and the chamfered surface 7a1 as the bottom surface 8b. Yes.

以上のように、本変形例では、大鍔部端面７ａに面取り面７ａ１を形成するだけで良いため、上記実施形態のように大鍔部端面７ａに潤滑溝８の全体を形成する場合に比べて、潤滑溝８を大鍔部端面７ａに簡単に設けることができる。
これに対して、上記実施形態の円すいころ軸受１は、本変形例のように環状板１０を用いる必要がないので、本変形例に比べて部品点数が少なく、コスト安価に製作することができる。 As described above, in this modified example, it is only necessary to form the chamfered surface 7a1 on the large collar end surface 7a, so that compared to the case where the entire lubricating groove 8 is formed on the large collar end surface 7a as in the above embodiment. Thus, the lubricating groove 8 can be easily provided on the large collar end surface 7a.
On the other hand, the tapered roller bearing 1 of the above embodiment does not need to use the annular plate 10 as in the present modification, and therefore can be manufactured at a lower cost and with fewer parts compared to the present modification. .

なお、今回開示した実施形態は例示であって制限的なものではない。本発明の権利範囲は特許請求の範囲によって示され、特許請求の範囲の構成と均等の範囲内での全ての変更が含まれる。例えば、上記実施形態では、潤滑溝８を楔形状としているが、凹形状など他の形状であっても良い。また、ころ軸受は、円すいころ軸受に限らず、円筒ころ軸受であっても良い。   The embodiment disclosed this time is illustrative and not restrictive. The scope of the present invention is defined by the terms of the claims, and includes all modifications that are within the scope of the claims and equivalents. For example, in the above-described embodiment, the lubricating groove 8 has a wedge shape, but may have another shape such as a concave shape. The roller bearing is not limited to a tapered roller bearing, and may be a cylindrical roller bearing.

１：円すいころ軸受（ころ軸受）、２：外輪、２ａ：外輪軌道面、３：内輪、３ａ：内輪軌道面、４：円すいころ（ころ）、４ａ：大径側端面（端面）、７：大鍔部（鍔部）、７ａ：大鍔部端面（端面）、８：潤滑溝、Ｃ：接触部分   1: Tapered roller bearing (roller bearing), 2: outer ring, 2a: outer ring raceway surface, 3: inner ring, 3a: inner ring raceway surface, 4: tapered roller (roller), 4a: large diameter side end face (end face), 7: Large collar part (buttock part), 7a: Large collar part end face (end face), 8: Lubrication groove, C: Contact part

Claims (3)

内周に外輪軌道面を有する外輪と、
外周に内輪軌道面を有するとともに、前記内輪軌道面の少なくとも軸方向一方側に径方向外方へ突出する鍔部を有する内輪と、
前記外輪軌道面及び前記内輪軌道面との間に転動自在に介在する複数のころと、を備えたころ軸受であって、
前記鍔部の端面には、前記ころの端面との接触部分よりも径方向外側に潤滑溝が設けられていることを特徴とするころ軸受。 An outer ring having an outer ring raceway surface on the inner periphery;
An inner ring having an inner ring raceway surface on the outer periphery and having a flange projecting radially outward on at least one axial side of the inner ring raceway surface;
A plurality of rollers movably interposed between the outer ring raceway surface and the inner ring raceway surface, and a roller bearing comprising:
The roller bearing according to claim 1, wherein a lubricating groove is provided on an end surface of the flange portion on a radially outer side than a contact portion with the end surface of the roller. 前記潤滑溝は、軸方向断面において径方向外端から径方向内端へ向かうに従って溝深さが漸次浅くなるように楔形状とされている請求項１に記載のころ軸受。   2. The roller bearing according to claim 1, wherein the lubricating groove has a wedge shape such that the groove depth gradually decreases in the axial section from the radially outer end toward the radially inner end. 前記ころの端面には、軸方向に窪ませた逃げ部が形成されており、
軸方向断面において、前記鍔部の端面における径方向外端から前記潤滑溝の径方向外端までの距離が、前記鍔部の端面における径方向外端から前記逃げ部の開口端に対向する位置までの距離よりも短く設定されている請求項１又は２に記載のころ軸受。 On the end face of the roller, a relief portion recessed in the axial direction is formed,
In the axial cross section, the distance from the radially outer end of the end surface of the flange portion to the radially outer end of the lubricating groove is opposed to the opening end of the escape portion from the radially outer end of the end surface of the flange portion. The roller bearing according to claim 1, wherein the roller bearing is set to be shorter than the distance up to.
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JPH11190333A (en) * 1997-09-22 1999-07-13 Nippon Seiko Kk Conical roller bearing
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Publication number Priority date Publication date Assignee Title
CN106369047A (en) * 2016-12-09 2017-02-01 瓦房店轴承集团有限责任公司 Conical roller bearing of novel structure copper retainer

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