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JP2014114904A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP2014114904A
JP2014114904A JP2012270293A JP2012270293A JP2014114904A JP 2014114904 A JP2014114904 A JP 2014114904A JP 2012270293 A JP2012270293 A JP 2012270293A JP 2012270293 A JP2012270293 A JP 2012270293A JP 2014114904 A JP2014114904 A JP 2014114904A
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Prior art keywords
peripheral surface
outer ring
cage
ring
rolling bearing
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JP2012270293A
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Japanese (ja)
Inventor
Taiji Bisata
泰治 美佐田
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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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • 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
    • F16C33/38—Ball cages
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3843—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/3856—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact

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

Abstract

【課題】保持器の摺動摩擦による発熱量を抑制することができる転がり軸受を提供する。
【解決手段】回転輪としての内輪１１と、この内輪１１の外周面に環状空間を隔てて同一中心線上に配設された固定輪としての外輪２０と、内輪１１と外輪２０との間に転動可能に配設された複数の転動体２８と、これら複数の転動体２８を保持する保持器３０とを備える。外輪２０の端部内周面には、環状空間の開口部を塞ぐようにして外輪側固定体６０が配設される。外輪側固定体６０には、保持器３０の内周面と僅かな隙間を隔てて対向する円筒突出部６２が形成される。円筒突出部６２の外周面は、保持器３０の径方向の動きを抑制しながら保持器３０を回転案内する保持器案内面６３としている。
【選択図】図２A rolling bearing capable of suppressing the amount of heat generated by sliding friction of a cage is provided.
An inner ring 11 as a rotating wheel, an outer ring 20 as a fixed ring disposed on the same center line with an annular space on the outer peripheral surface of the inner ring 11, and between the inner ring 11 and the outer ring 20. A plurality of rolling elements 28 movably disposed and a holder 30 that holds the plurality of rolling elements 28 are provided. An outer ring side fixed body 60 is disposed on the inner circumferential surface of the end portion of the outer ring 20 so as to close the opening of the annular space. The outer ring side fixed body 60 is formed with a cylindrical protrusion 62 that faces the inner peripheral surface of the cage 30 with a slight gap therebetween. The outer peripheral surface of the cylindrical protrusion 62 is a cage guide surface 63 that rotates and guides the cage 30 while suppressing the radial movement of the cage 30.
[Selection] Figure 2

Description

この発明は転がり軸受に関する。   The present invention relates to a rolling bearing.

従来、転がり軸受においては、回転輪としての内輪と、この内輪の外周面に環状空間を隔てて同一中心線上に配設された固定輪としての外輪と、内・外輪との間に転動可能に配設された複数の転動体と、これら複数の転動体を保持する保持器とを備えたものがある。
また、このような転がり軸受において、例えば、特許文献１に開示されているように、外輪の軌道肩部の内周面を保持器案内面として保持器の外周面を回転案内する構造のものがある。 Conventionally, in rolling bearings, rolling is possible between an inner ring as a rotating ring, an outer ring as a fixed ring disposed on the same center line with an annular space on the outer peripheral surface of the inner ring, and an inner / outer ring. There are some which are provided with a plurality of rolling elements arranged in and a cage for holding the plurality of rolling elements.
Further, in such a rolling bearing, for example, as disclosed in Patent Document 1, a structure in which the outer peripheral surface of the cage is rotationally guided with the inner peripheral surface of the raceway shoulder portion of the outer ring as the cage guide surface. is there.

特開２０１１−１６９３７０号公報JP 2011-169370 A

例えば、工作機のスピンドルような高速回転する回転軸に組み付けられた転がり軸受において、回転軸の回転数が毎分２万回転の高速回転である場合、転がり軸受の保持器の回転数は毎分９０００回転程度に高速回転する。
この際、転がり軸受において、外輪の保持器案内面に対する保持器の外周面の摺動摩擦による摩擦熱が最も多く発生する。
そして、保持器の外周面の摺動摩擦による摩擦熱によって保持器が熱変形され、ときには、外輪の保持器案内面に対し保持器の外周面が焼き付く恐れもある。 For example, in a rolling bearing assembled on a rotating shaft that rotates at high speed such as a spindle of a machine tool, when the rotating shaft rotates at a high speed of 20,000 rpm, the rotating bearing retainer rotates at a speed of It rotates at a high speed of about 9000 rpm.
At this time, in the rolling bearing, the most frictional heat is generated by the sliding friction of the outer peripheral surface of the cage with respect to the cage guide surface of the outer ring.
The cage is thermally deformed by frictional heat due to sliding friction on the outer circumferential surface of the cage, and sometimes the outer circumferential surface of the cage is seized against the cage guide surface of the outer ring.

この発明の目的は、前記問題点に鑑み、保持器の摺動摩擦による発熱量を抑制することができる転がり軸受を提供することである。   In view of the above problems, an object of the present invention is to provide a rolling bearing capable of suppressing the amount of heat generated by sliding friction of a cage.

前記課題を解決するために、この発明の請求項１に係る転がり軸受は、回転輪としての内輪と、この内輪の外周面に環状空間を隔てて同一中心線上に配設された固定輪としての外輪と、前記内輪と前記外輪との間に転動可能に配設された複数の転動体と、これら複数の転動体を保持する保持器とを備えた転がり軸受であって、
前記外輪の端部内周面には、前記環状空間の開口部を塞ぐようにして外輪側固定体が配設され、
前記外輪側固定体には、前記保持器の内周面に対向する円筒突出部が形成され、
前記円筒突出部の外周面は、前記保持器を回転案内する保持器案内面としていることを特徴とする。 In order to solve the above-mentioned problems, a rolling bearing according to a first aspect of the present invention includes an inner ring as a rotating ring, and a fixed ring disposed on the same center line with an annular space on the outer peripheral surface of the inner ring. A rolling bearing comprising an outer ring, a plurality of rolling elements arranged to roll between the inner ring and the outer ring, and a cage for holding the plurality of rolling elements,
An outer ring side fixed body is disposed on the inner peripheral surface of the end portion of the outer ring so as to close the opening of the annular space,
The outer ring side fixed body is formed with a cylindrical protrusion that faces the inner peripheral surface of the cage.
The outer peripheral surface of the cylindrical protrusion is a cage guide surface for rotating and guiding the cage.

前記構成によると、外輪の端部内周面に配設される外輪側固定体の円筒突出部の外周面を保持器案内面とすることで、この保持器案内面に対する保持器の内周面の摺動摩擦による発熱量を抑制することができる。
すなわち、軸受回転時において、保持器の回転による周速は、保持器の外周面よりも内周面の方が回転半径が小さい分（保持器の径方向の肉厚に相当する分）だけ遅くなる。
このため、従来の外輪の軌道肩部の内周面を保持器案内面として保持器の外周面を回転案内する場合と比べ、保持器の周速が遅くなった分だけ、保持器の内周面の摺動摩擦による発熱量を抑制することができる。 According to the said structure, the outer peripheral surface of the cylindrical protrusion part of the outer ring | wheel side fixed body arrange | positioned at the edge part inner peripheral surface of an outer ring | wheel is used as a cage guide surface, The inner peripheral surface of a cage | basket with respect to this cage guide surface is set. The amount of heat generated by sliding friction can be suppressed.
That is, during the rotation of the bearing, the peripheral speed due to the rotation of the cage is slower than the outer peripheral surface of the cage by the smaller rotation radius (corresponding to the radial thickness of the cage). Become.
For this reason, compared with the conventional case where the outer peripheral surface of the cage is rotated and guided using the inner peripheral surface of the raceway shoulder of the outer ring as the cage guide surface, the inner circumference of the cage is reduced by the amount that the peripheral speed of the cage is slower. The amount of heat generated by the sliding friction of the surface can be suppressed.

請求項２に係る転がり軸受は、請求項１に記載の転がり軸受であって、
外輪側固定体の内周面は、内輪の端部外周面に対し僅かな隙間を隔てて対向していることを特徴とする。 A rolling bearing according to claim 2 is the rolling bearing according to claim 1,
The inner peripheral surface of the outer ring side fixed body is opposed to the outer peripheral surface of the end portion of the inner ring with a slight gap.

前記構成によると、外輪側固定体の内周面が内輪の端部外周面に対し僅かな隙間を隔てて対向することでラビリンス（非接触のシール部）を構成することができる。これによって、外輪側固定体がシール部材としても機能するため、専用のシール部材を製作して組み付ける手間を省くことができ、コスト低減に効果が大きい。   According to the said structure, a labyrinth (non-contact seal | sticker part) can be comprised because the inner peripheral surface of an outer ring | wheel side stationary body opposes the outer peripheral surface of the edge part of an inner ring through a slight clearance. As a result, the outer ring side fixed body also functions as a seal member, so that it is possible to save the trouble of manufacturing and assembling a dedicated seal member, which is highly effective for cost reduction.

請求項３に係る転がり軸受は、請求項１に記載の転がり軸受であって、
外輪側固定体は、外周部が外輪の端部内周面に固定され内周部が内輪の端部外周面に対するシール部を有するシール部材によって構成され、
円筒突出部は、前記シール部材の内側部に一体に形成されていることを特徴とする。 A rolling bearing according to claim 3 is the rolling bearing according to claim 1,
The outer ring side fixed body is configured by a seal member having an outer peripheral portion fixed to the inner peripheral surface of the end portion of the outer ring and an inner peripheral portion having a seal portion with respect to the outer peripheral surface of the end portion of the inner ring,
The cylindrical protruding portion is formed integrally with the inner portion of the seal member.

前記構成によると、シール部材が外輪側固定体として機能するため、部品点数や組付工数が増加することがなく、コスト低減に効果が大きい。   According to the said structure, since a sealing member functions as an outer ring | side stationary body, a number of parts and an assembly man-hour do not increase, and an effect is large at cost reduction.

この発明の実施例１に係る転がり軸受を示す縦断面図である。It is a longitudinal cross-sectional view which shows the rolling bearing which concerns on Example 1 of this invention. 同じく要部を拡大して示す縦断面図である。It is the longitudinal cross-sectional view which similarly expands and shows the principal part. この発明の実施例２に係る転がり軸受を示す縦断面図である。It is a longitudinal cross-sectional view which shows the rolling bearing which concerns on Example 2 of this invention. この発明の実施例３に係る転がり軸受を示す縦断面図である。It is a longitudinal cross-sectional view which shows the rolling bearing which concerns on Example 3 of this invention.

この発明を実施するための形態について実施例にしたがって説明する。   A mode for carrying out the present invention will be described in accordance with an embodiment.

この発明の実施例１を図１と図２にしたがって説明する。
図１と図２に示すように、転がり軸受（この実施例１ではアンギュラ玉軸受）は、回転輪としての内輪１１と、この内輪１１の外周面に環状空間を隔てて同一中心線上に配設された固定輪としての外輪２０と、内輪１１と外輪２０との間に転動可能に配設された複数の転動体２８（この実施例１では玉）と、これら複数の転動体２８を保持する保持器３０とを備える。 A first embodiment of the present invention will be described with reference to FIGS.
As shown in FIGS. 1 and 2, a rolling bearing (angular ball bearing in this embodiment 1) is disposed on the same center line with an inner ring 11 as a rotating ring and an outer peripheral surface of the inner ring 11 with an annular space therebetween. The outer ring 20 as a fixed ring, a plurality of rolling elements 28 (balls in this embodiment 1) disposed so as to be able to roll between the inner ring 11 and the outer ring 20, and the plurality of rolling elements 28 are held. The retainer 30 is provided.

内輪１１は円筒状に形成され、その中心孔が回転軸１（例えば、工作機のスピンドル）の外周面に嵌合（圧入）されて一体回転可能に配設される。
図２に示すように、内輪１１の外周面には、その軸方向略中央部に内輪軌道面１２が形成されると共に、内輪軌道面１２の両側部に軌道肩部１３、１４が形成されている。
この実施例１において、両軌道肩部１３、１４のうち、図２に向かって右側に位置する軌道肩部１４の外周面の径寸法は、左側に位置する軌道肩部１３の外周面の径寸法よりも設定寸法だけ大きく形成されている。また、左側に位置する軌道肩部１３の軸方向外側部には、軌道肩部１３の外径寸法よりも小さい外径寸法のシール面１３ａが形成されている。
また、内輪１１の右側端部には、後述するシール部材４０とラビリンス（非接触シール部）を構成する環状溝１６が形成されている。 The inner ring 11 is formed in a cylindrical shape, and its central hole is fitted (press-fitted) to the outer peripheral surface of the rotary shaft 1 (for example, a spindle of a machine tool) so as to be integrally rotatable.
As shown in FIG. 2, an inner ring raceway surface 12 is formed on the outer peripheral surface of the inner ring 11 at a substantially central portion in the axial direction, and track shoulder portions 13 and 14 are formed on both sides of the inner ring raceway surface 12. Yes.
In the first embodiment, of the both shoulders 13 and 14, the diameter of the outer peripheral surface of the track shoulder 14 positioned on the right side in FIG. 2 is the diameter of the outer peripheral surface of the track shoulder 13 positioned on the left side. It is formed larger than the dimension by a set dimension. A seal surface 13 a having an outer diameter smaller than the outer diameter of the track shoulder 13 is formed on the outer side in the axial direction of the track shoulder 13 located on the left side.
In addition, an annular groove 16 that forms a labyrinth (non-contact seal portion) to be described later and a seal member 40 is formed at the right end portion of the inner ring 11.

図１と図２に示すように、外輪２０は、内輪１１の外周面との間に環状空間を隔てて同一中心線上に配設される円筒状に形成され、その外周面がハウジング２に嵌合されて固定状態で配設される。
外輪２０の内周面には、その軸方向略中央部に外輪軌道面２１が形成されると共に、外輪軌道面２１の両側部に軌道肩部２２、２３が形成されている。
この実施例１において、両軌道肩部２２、２３のうち、右側の軌道肩部２２の内周面の径寸法は、左側の軌道肩部２３の外周面の径寸法よりも大きく形成されいる。また、左側の軌道肩部２３の軸方向外側部には軌道肩部２３の内径寸法よりも大きい内径寸法の嵌合孔部２３ａが形成されている。
また、外輪２０の右側の軌道肩部２２側の内周面端部には、後述するシール部材４０を固定する環状溝２４が形成されている。 As shown in FIGS. 1 and 2, the outer ring 20 is formed in a cylindrical shape that is disposed on the same center line with an annular space between the outer ring 20 and the outer ring surface of the inner ring 11, and the outer ring surface is fitted into the housing 2. Combined and arranged in a fixed state.
On the inner peripheral surface of the outer ring 20, an outer ring raceway surface 21 is formed at a substantially central portion in the axial direction, and track shoulder portions 22 and 23 are formed on both sides of the outer ring raceway surface 21.
In the first embodiment, the radial dimension of the inner peripheral surface of the right track shoulder 22 is larger than the radial dimension of the outer peripheral surface of the left track shoulder 23 of both the track shoulders 22 and 23. A fitting hole 23 a having an inner diameter larger than the inner diameter of the track shoulder 23 is formed on the outer side in the axial direction of the left track shoulder 23.
Further, an annular groove 24 for fixing a seal member 40 to be described later is formed at the inner peripheral surface end of the outer ring 20 on the right side of the track shoulder 22.

複数の転動体２８は、内輪軌道面１２と外輪軌道面２１との間に保持器３０によって保持された状態で転動可能に配設されている。
また、保持器３０は、耐熱性及び耐摩耗性を有する樹脂材料、又は金属材料によって円筒状に形成され、その周方向には、複数の転動体２８が個別に配置されるポケットが形成されている。 The plurality of rolling elements 28 are disposed between the inner ring raceway surface 12 and the outer ring raceway surface 21 so as to be able to roll while being held by a cage 30.
The cage 30 is formed in a cylindrical shape from a heat-resistant and wear-resistant resin material or metal material, and a pocket in which a plurality of rolling elements 28 are individually arranged is formed in the circumferential direction. Yes.

図２に示すように、シール部材４０は、芯金４１と弾性体４５とを有する。芯金４１は、外輪２０の内周面の端部に嵌込み可能な外径寸法に形成された円筒部４２と、この円筒部４２の端部から径方向内方へ向けて直角状に曲げられた環状部４３とを有する。
芯金４１の環状部４３の外側面には、弾性体４５よりなる被覆部４６が形成され、芯金４１の円筒部４２の外周面には、外輪２０の環状溝２４に弾性圧縮されて嵌込まれることで固定される弾性体４５よりなる固定部４７が形成されている。
また、芯金４１の環状部４３の内周部には、内輪１１の環状溝１６に僅かな隙間をもって嵌込まれ環状溝１６と協働してラビリンス（非接触のシール部）を構成するシール部４８が形成されている。 As shown in FIG. 2, the seal member 40 includes a cored bar 41 and an elastic body 45. The cored bar 41 is bent at a right angle from the end of the cylindrical part 42 to the radially inner side, with a cylindrical part 42 having an outer diameter dimension that can be fitted into the end of the inner peripheral surface of the outer ring 20. An annular portion 43.
A covering portion 46 made of an elastic body 45 is formed on the outer surface of the annular portion 43 of the core metal 41, and the outer peripheral surface of the cylindrical portion 42 of the core metal 41 is elastically compressed and fitted into the annular groove 24 of the outer ring 20. A fixing portion 47 made of an elastic body 45 fixed by being inserted is formed.
Further, a seal that is fitted into the annular groove 16 of the inner ring 11 with a slight clearance on the inner peripheral part of the annular part 43 of the core metal 41 and forms a labyrinth (non-contact seal part) in cooperation with the annular groove 16. A portion 48 is formed.

図２に示すように、外輪２０の嵌合部２３ａの内周面には、内・外輪１１、２０の間の環状空間の開口部を塞ぐようにして外輪側固定体６０が配設されている。
外輪側固定体６０は、樹脂材料又は金属材料よりなり、環状部６１と円筒突出部６２とを一端に有して軸方向断面で略Ｌ字状に形成されている。
そして、外輪側固定体６０は、その環状部６１の外周面において、外輪２０の嵌合部２３ａの内周面に圧入固定されている。
円筒突出部６２は、環状部６１の内周端から保持器３０の内周面に向けて円筒状に突出されている。そして、円筒突出部６２の外周面は、保持器３０の内周面と僅かな隙間を隔てて対向することで、保持器３０の径方向の動きを抑制しながら保持器３０を回転案内する保持器案内面６３としている。 As shown in FIG. 2, an outer ring side fixed body 60 is disposed on the inner peripheral surface of the fitting portion 23 a of the outer ring 20 so as to close the opening of the annular space between the inner and outer rings 11 and 20. Yes.
The outer ring side fixed body 60 is made of a resin material or a metal material, and has an annular portion 61 and a cylindrical protruding portion 62 at one end, and is formed in an approximately L shape in the axial cross section.
The outer ring side fixed body 60 is press-fitted and fixed to the inner peripheral surface of the fitting portion 23 a of the outer ring 20 on the outer peripheral surface of the annular portion 61.
The cylindrical protruding portion 62 protrudes in a cylindrical shape from the inner peripheral end of the annular portion 61 toward the inner peripheral surface of the cage 30. And the outer peripheral surface of the cylindrical protrusion 62 is opposed to the inner peripheral surface of the retainer 30 with a slight gap therebetween, so that the retainer 30 rotates and guides the retainer 30 while suppressing the radial movement of the retainer 30. A vessel guide surface 63 is provided.

また、この実施例１において、外輪側固定体６０の円筒突出部６２の内周面６４は、内輪１１の端部のシール面１３ａに対し僅かな隙間を隔てて対向している。これによって、外輪側固定体６０の円筒突出部６２の内周面と、内輪１１の端部のシール面１３ａとの間にラビリンス（非接触のシール部）を構成している。   In the first embodiment, the inner peripheral surface 64 of the cylindrical protrusion 62 of the outer ring side fixed body 60 faces the seal surface 13a at the end of the inner ring 11 with a slight gap therebetween. Thereby, a labyrinth (non-contact seal portion) is formed between the inner peripheral surface of the cylindrical protrusion 62 of the outer ring side fixed body 60 and the seal surface 13 a at the end of the inner ring 11.

この実施例１に係る転がり軸受は上述したように構成される。
したがって、外輪側固定体６０の円筒突出部６２の外周面を保持器案内面６３とすることで、この保持器案内面６３に対する保持器３０の内周面の摺動摩擦による発熱量を抑制することができる。
すなわち、軸受回転時において、保持器３０の回転による周速は、保持器３０の外周面よりも内周面の方が回転半径が小さい分（およそ保持器３０の径方向の肉厚に相当する分）だけ遅くなる。
このため、従来の外輪の軌道肩部の内周面を保持器案内面として保持器の外周面を回転案内する場合と比べ、保持器３０の周速が遅くなった分だけ、保持器３０の内周面の摺動摩擦による発熱量を抑制することができる。 The rolling bearing according to the first embodiment is configured as described above.
Therefore, by setting the outer peripheral surface of the cylindrical protrusion 62 of the outer ring side fixed body 60 as the cage guide surface 63, the amount of heat generated by sliding friction of the inner peripheral surface of the cage 30 with respect to the cage guide surface 63 is suppressed. Can do.
That is, during the rotation of the bearing, the circumferential speed due to the rotation of the cage 30 is equivalent to the thickness of the inner circumferential surface being smaller than the outer circumferential surface of the cage 30 (approximately the radial thickness of the cage 30). Min)).
For this reason, compared with the conventional case where the outer peripheral surface of the cage is rotated and guided by using the inner peripheral surface of the raceway shoulder of the outer ring as the cage guide surface, The amount of heat generated by sliding friction on the inner peripheral surface can be suppressed.

また、この実施例１において、外輪側固定体６０の内周面６４は、内輪１１のシール面１３ａに対し僅かな隙間を隔てて対向することで、外輪側固定体６０の円筒突出部６２の内周面と、内輪１１の端部のシール面１３ａとの間にラビリンス（非接触のシール部）を構成している。これによって、外輪側固定体６０はシール部材としても機能するため、専用のシール部材を製作して組み付ける手間を省くことができ、コスト低減に効果が大きい。   In the first embodiment, the inner peripheral surface 64 of the outer ring side fixed body 60 is opposed to the seal surface 13a of the inner ring 11 with a slight gap therebetween, so that the cylindrical protruding portion 62 of the outer ring side fixed body 60 is A labyrinth (non-contact seal portion) is formed between the inner peripheral surface and the seal surface 13 a at the end of the inner ring 11. As a result, the outer ring side fixed body 60 also functions as a seal member, so that it is possible to save the trouble of manufacturing and assembling a dedicated seal member, which is highly effective in reducing costs.

次に、この発明の実施例２を図３にしたがって説明する。
この実施例２においては、図３に示すように、内輪１１と外輪２０との環状空間の両端開口部に組み付けられる両シール部材４０、１４０のうち、一方のシール部材４０は、実施例１で述べたシール部材４０と同様にして構成されるため、実施例１のシール部材４０と同一符号を付記してその説明は省略する。 Next, a second embodiment of the present invention will be described with reference to FIG.
In the second embodiment, as shown in FIG. 3, one of the seal members 40, 140 assembled in the opening portions at both ends of the annular space between the inner ring 11 and the outer ring 20 is the same as that of the first embodiment. Since it is configured in the same manner as the sealing member 40 described above, the same reference numerals as those of the sealing member 40 of the first embodiment are added and description thereof is omitted.

他方のシール部材１４０は、芯金１４１と弾性体１４５とを有する。このシール部材１４０において、芯金１４１は、外輪２０の内周面の端部に嵌込み可能な外径寸法に形成された円筒部１４２と、この円筒部１４２の端部から径方向内方へ向けて直角状に曲げられた環状部１４３と、この環状部１４３の内径端から転動体２８に向けて軸方向へ円筒状に曲げられた内径筒部１４４とを有する。
芯金１４１の環状部１４３の外側面には、弾性体１４５よりなる被覆部１４６が形成され、芯金１４１の円筒部１４２の外周面には、外輪２０の環状溝２４に弾性圧縮されて嵌込まれることで固定される弾性体１４５よりなる固定部１４７が形成されている。
また、芯金１４１の環状部１４３と内径筒部１４４との曲げ部分には、内輪１１の環状溝１６に僅かな隙間をもって嵌込まれ環状溝１６と協働してラビリンス（非接触シール部）を構成するシール部１４８が形成されている。 The other seal member 140 has a cored bar 141 and an elastic body 145. In the seal member 140, the core metal 141 has a cylindrical portion 142 formed to have an outer diameter dimension that can be fitted into an end portion of the inner peripheral surface of the outer ring 20, and radially inward from the end portion of the cylindrical portion 142. An annular portion 143 that is bent at a right angle toward the surface, and an inner diameter cylindrical portion 144 that is bent in a cylindrical shape in the axial direction from the inner diameter end of the annular portion 143 toward the rolling element 28.
A covering portion 146 made of an elastic body 145 is formed on the outer surface of the annular portion 143 of the core metal 141, and the outer peripheral surface of the cylindrical portion 142 of the core metal 141 is elastically compressed and fitted into the annular groove 24 of the outer ring 20. A fixing portion 147 made of an elastic body 145 that is fixed by being inserted is formed.
A bent portion between the annular portion 143 and the inner diameter cylindrical portion 144 of the cored bar 141 is fitted into the annular groove 16 of the inner ring 11 with a slight gap, and cooperates with the annular groove 16 to form a labyrinth (non-contact seal portion). Is formed.

シール部材１４０の内側には、内輪１１の外周面と保持器３０の内周面との間の環状隙間内に挿入される円筒突出部１６２が形成されている。
円筒突出部１６２は、芯金１４１の内径筒部１４４と、この内径筒部１４４で補強され、かつ内径筒部１４４を覆うようにして弾性体１４５によって一体に形成された弾性体部分１６２ａとを有している。
また、円筒突出部１６２の外周面は、保持器３０の内周面と僅かな隙間を隔てて対向することで、保持器３０の径方向の動きを抑制しながら保持器３０を回転案内する保持器案内面１６３としている。
この実施例２のその他の構成は、実施例１と同様に構成されるため、同一構成部分に対し同一符号を付記してその説明は省略する。 A cylindrical projecting portion 162 that is inserted into an annular gap between the outer peripheral surface of the inner ring 11 and the inner peripheral surface of the cage 30 is formed inside the seal member 140.
The cylindrical projecting portion 162 includes an inner diameter cylindrical portion 144 of the metal core 141 and an elastic portion 162a that is reinforced by the inner diameter cylindrical portion 144 and integrally formed by the elastic body 145 so as to cover the inner diameter cylindrical portion 144. Have.
In addition, the outer peripheral surface of the cylindrical protrusion 162 faces the inner peripheral surface of the retainer 30 with a slight gap therebetween, so that the retainer 30 rotates and guides the retainer 30 while suppressing the radial movement of the retainer 30. The container guide surface 163 is used.
Since the other configuration of the second embodiment is configured in the same manner as the first embodiment, the same components are denoted by the same reference numerals and the description thereof is omitted.

上述したように構成されるこの実施例２に係る転がり軸受は、シール部材１４０の円筒突出部１６２の外周面を保持器案内面１６３とすることで、この保持器案内面１６３に対する保持器３０の内周面の摺動摩擦による発熱量を抑制することができる。
すなわち、軸受回転時において、保持器３０の回転による周速は、保持器３０の外周面よりも内周面の方が回転半径が小さい分（およそ保持器３０の径方向の肉厚に相当する分）だけ遅くなる。
このため、従来の外輪の軌道肩部の内周面を保持器案内面として保持器の外周面を回転案内する場合と比べ、保持器３０の周速が遅くなった分だけ、保持器３０の内周面の摺動摩擦による発熱量を抑制することができる。
また、この実施例２において、シール部材１４０が実施例１の外輪側固定体６０として機能するため、部品点数や組付工数が増加することがなく、コスト低減に効果が大きい。 In the rolling bearing according to the second embodiment configured as described above, the outer peripheral surface of the cylindrical projecting portion 162 of the seal member 140 is the retainer guide surface 163, so that the retainer 30 is supported with respect to the retainer guide surface 163. The amount of heat generated by sliding friction on the inner peripheral surface can be suppressed.
That is, during the rotation of the bearing, the circumferential speed due to the rotation of the cage 30 is equivalent to the thickness of the inner circumferential surface being smaller than the outer circumferential surface of the cage 30 (approximately the radial thickness of the cage 30). Min)).
For this reason, compared with the conventional case where the outer peripheral surface of the cage is rotated and guided by using the inner peripheral surface of the raceway shoulder of the outer ring as the cage guide surface, The amount of heat generated by sliding friction on the inner peripheral surface can be suppressed.
Further, in the second embodiment, since the seal member 140 functions as the outer ring side fixed body 60 of the first embodiment, the number of parts and the number of assembling steps are not increased, and the cost is greatly reduced.

次に、この発明の実施例３を図４にしたがって説明する。
この実施例３においては、図４に示すように、内輪１１と外輪２０との環状空間の両端開口部に組み付けられる両シール部材１４０が共に、前記実施例２で述べたシール部材１４０と同様にして構成されるため、実施例２のシール部材１４０と同一符号を付記してその説明は省略する。
また、その他の構成も実施例１及び２と同様に構成されるため、同一構成部分に対し同一符号を付記してその説明は省略する。 Next, Embodiment 3 of the present invention will be described with reference to FIG.
In the third embodiment, as shown in FIG. 4, both the sealing members 140 assembled to the opening portions at both ends of the annular space between the inner ring 11 and the outer ring 20 are the same as the sealing member 140 described in the second embodiment. Therefore, the same reference numerals as those of the seal member 140 of the second embodiment are added and the description thereof is omitted.
In addition, since the other configurations are configured in the same manner as in the first and second embodiments, the same components are denoted by the same reference numerals and description thereof is omitted.

上述したように構成されるこの実施例３に係る転がり軸受は、両シール部材１４０の円筒突出部１６２の外周面を保持器案内面１６３とすることで、実施例２と同様の作用効果を奏する。
特に、この実施例３においては、両シール部材１４０の円筒突出部１６２の外周面の保持器案内面１６３によって保持器３０の内周面の軸方向両側部を回転案内することができるため、保持器３０の傾き抑制に効果が大きい。 The rolling bearing according to the third embodiment configured as described above has the same operational effects as the second embodiment by using the outer peripheral surface of the cylindrical protrusion 162 of both seal members 140 as the cage guide surface 163. .
In particular, in the third embodiment, since the both sides in the axial direction of the inner peripheral surface of the retainer 30 can be rotationally guided by the retainer guide surfaces 163 on the outer peripheral surfaces of the cylindrical projecting portions 162 of the both seal members 140, The effect of suppressing the inclination of the vessel 30 is great.

なお、この発明は前記実施例１に限定するものではなく、この発明の要旨を逸脱しない範囲内において、種々の形態で実施することができる。
例えば、前記実施例１においては、外輪側固定体６０が、その環状部６１の外周面において、外輪２０の嵌合部２３ａの内周面に圧入固定される場合を例示したが、外輪２０の一端側に外輪側固定体６０を一体に形成して外輪２０と外輪側固定体６０とを一部品で構成することも可能である。この場合には、部品点数や組付工数を削減することができる。 In addition, this invention is not limited to the said Example 1, In the range which does not deviate from the summary of this invention, it can implement with a various form.
For example, in the first embodiment, the case where the outer ring side fixing body 60 is press-fitted and fixed to the inner peripheral surface of the fitting portion 23a of the outer ring 20 on the outer peripheral surface of the annular portion 61 is illustrated. It is also possible to form the outer ring side fixed body 60 integrally on one end side and to configure the outer ring 20 and the outer ring side fixed body 60 as a single component. In this case, the number of parts and assembly man-hours can be reduced.

１１ 内輪
１２ 内輪軌道面
２０ 外輪
２１ 外輪軌道面
３０ 保持器
３２ 第１ポケット
３３ 第１案内孔部
３４ 第１空間構成孔部
３５ 潤滑剤通路
３６ 第２ポケット
３７ 第２案内孔部
３８ 第２空間構成孔部
３９ 潤滑剤通路
４０ シール部材
６０ 外輪側固定体
６２ 円筒突出部
６３ 保持器案内面
１４０ シール部材
１６２ 円筒突出部
１６３ 保持器案内面 DESCRIPTION OF SYMBOLS 11 Inner ring 12 Inner ring raceway surface 20 Outer ring 21 Outer ring raceway surface 30 Cage 32 1st pocket 33 1st guide hole part 34 1st space structure hole part 35 Lubricant passage 36 2nd pocket 37 2nd guide hole part 38 2nd space Constituent hole 39 Lubricant passage 40 Seal member 60 Outer ring side fixed body 62 Cylindrical protrusion 63 Cage guide surface 140 Seal member 162 Cylinder protrusion 163 Cage guide surface

Claims (3)

回転輪としての内輪と、この内輪の外周面に環状空間を隔てて同一中心線上に配設された固定輪としての外輪と、前記内輪と前記外輪との間に転動可能に配設された複数の転動体と、これら複数の転動体を保持する保持器とを備えた転がり軸受であって、
前記外輪の端部内周面には、前記環状空間の開口部を塞ぐようにして外輪側固定体が配設され、
前記外輪側固定体には、前記保持器の内周面に対向する円筒突出部が形成され、
前記円筒突出部の外周面は、前記保持器を回転案内する保持器案内面としていることを特徴とする転がり軸受。 An inner ring as a rotating ring, an outer ring as a fixed ring arranged on the same center line with an annular space on the outer peripheral surface of the inner ring, and a rollable arrangement between the inner ring and the outer ring A rolling bearing comprising a plurality of rolling elements and a cage for holding the plurality of rolling elements,
An outer ring side fixed body is disposed on the inner peripheral surface of the end portion of the outer ring so as to close the opening of the annular space,
The outer ring side fixed body is formed with a cylindrical protrusion that faces the inner peripheral surface of the cage.
The rolling bearing according to claim 1, wherein an outer peripheral surface of the cylindrical protruding portion is a cage guide surface for rotating and guiding the cage. 請求項１に記載の転がり軸受であって、
外輪側固定体の内周面は、内輪の端部外周面に対し僅かな隙間を隔てて対向していることを特徴とする転がり軸受。 The rolling bearing according to claim 1,
A rolling bearing characterized in that the inner peripheral surface of the outer ring side fixed body is opposed to the outer peripheral surface of the end portion of the inner ring with a slight gap. 請求項１に記載の転がり軸受であって、
外輪側固定体は、外周部が外輪の端部内周面に固定され内周部が内輪の端部外周面に対するシール部を有するシール部材によって構成され、
円筒突出部は、前記シール部材の内側部に一体に形成されていることを特徴とする転がり軸受。 The rolling bearing according to claim 1,
The outer ring side fixed body is configured by a seal member having an outer peripheral portion fixed to the inner peripheral surface of the end portion of the outer ring and an inner peripheral portion having a seal portion with respect to the outer peripheral surface of the end portion of the inner ring,
The rolling bearing according to claim 1, wherein the cylindrical projecting portion is formed integrally with an inner portion of the seal member.
JP2012270293A 2012-12-11 2012-12-11 Rolling bearing Pending JP2014114904A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016044758A (en) * 2014-08-22 2016-04-04 株式会社ジェイテクト Rolling bearing
JP2016056842A (en) * 2014-09-08 2016-04-21 日本精工株式会社 Dental air turbine bearing unit and dental air turbine
JP2021014907A (en) * 2019-07-16 2021-02-12 株式会社ジェイテクト Rolling bearing
JP2022112006A (en) * 2021-01-20 2022-08-01 ミネベアミツミ株式会社 Bearing for medical or cosmetic instrument

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Publication number Priority date Publication date Assignee Title
JPH1078038A (en) * 1996-08-09 1998-03-24 Skf Gmbh Sealed rolling bearing
JP2011133000A (en) * 2009-12-24 2011-07-07 Ntn Corp Cylindrical roller bearing device
JP2013204617A (en) * 2012-03-27 2013-10-07 Nsk Ltd Rolling bearing

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1078038A (en) * 1996-08-09 1998-03-24 Skf Gmbh Sealed rolling bearing
JP2011133000A (en) * 2009-12-24 2011-07-07 Ntn Corp Cylindrical roller bearing device
JP2013204617A (en) * 2012-03-27 2013-10-07 Nsk Ltd Rolling bearing

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016044758A (en) * 2014-08-22 2016-04-04 株式会社ジェイテクト Rolling bearing
JP2016056842A (en) * 2014-09-08 2016-04-21 日本精工株式会社 Dental air turbine bearing unit and dental air turbine
JP2021014907A (en) * 2019-07-16 2021-02-12 株式会社ジェイテクト Rolling bearing
JP2022112006A (en) * 2021-01-20 2022-08-01 ミネベアミツミ株式会社 Bearing for medical or cosmetic instrument
JP7645206B2 (en) 2021-01-20 2025-03-13 ミネベアミツミ株式会社 Rolling bearings for medical or cosmetic devices

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