JP2014167316A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
JP2014167316A
JP2014167316A JP2013038889A JP2013038889A JP2014167316A JP 2014167316 A JP2014167316 A JP 2014167316A JP 2013038889 A JP2013038889 A JP 2013038889A JP 2013038889 A JP2013038889 A JP 2013038889A JP 2014167316 A JP2014167316 A JP 2014167316A
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Prior art keywords
guide wheel
roller
rollers
guide
guide ring
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Pending
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JP2013038889A
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Japanese (ja)
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Kazuya Toyoda
和也 豊田
Kinji Yugawa
謹次 湯川
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NSK Ltd
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NSK Ltd
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Priority to JP2013038889A priority Critical patent/JP2014167316A/en
Publication of JP2014167316A publication Critical patent/JP2014167316A/en
Pending legal-status Critical Current

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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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • 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
    • F16C33/37—Loose spacing bodies
    • 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
    • F16C19/38—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 two or more rows of rollers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a double-row self-aligning roller bearing for preventing the wear of a guide ring existing between rows of rollers, when held between both rows of rollers, due to the occurrence of excessive loads in slide contact areas between each roller and the guide ring.SOLUTION: An annular groove is formed in at least one of the outer diameter face and the inner diameter face of the guide ring so that the guide ring is elastically deformed with its guide face receiving a load. When receiving the load from the rollers, the guide ring is elastically deformed to allow the load to escape, thus preventing the occurrence of excessive loads in the slide contact areas between each roller and the guide ring.

Description

本発明は、産業機械に用いられる転がり軸受、特に、案内輪を有する複列の自動調心ころ軸受に関する。   The present invention relates to a rolling bearing used in an industrial machine, and more particularly to a double row self-aligning roller bearing having a guide wheel.

鉄鋼設備や製紙機械のロール等で用いられる自動調心ころ軸受は、内周面に球面状の軌道面を有する外輪と、外径面に外輪の軌道面と対向する複列の球面状の軌道面を有する内輪と、外輪及び内輪の軌道面の間を転動自在且つ複列に配置される複数のころと、ころの転動方向の間隔を一定に保持する保持器と、を備えている。このような自動調心ころ軸受においては、複列に配置されたのころがスキューすることなく転動できる様、ころの端面を案内する案内輪をころの列間に配置することが行われている。   Self-aligning roller bearings used in steel equipment and papermaking machine rolls have an outer ring having a spherical raceway surface on the inner peripheral surface and a double row spherical raceway facing the outer raceway surface on the outer diameter surface. An inner ring having a surface, a plurality of rollers that can roll between outer races and raceways of the inner ring and arranged in a double row, and a cage that maintains a constant spacing in the rolling direction of the rollers. . In such a self-aligning roller bearing, guide wheels for guiding the end faces of the rollers are arranged between the roller rows so that the rollers arranged in double rows can roll without skew. Yes.

案内輪によるころのスキュー防止の効果は、一般的にころと案内輪との隙間が小さい程大きく、隙間が大きくなるほどスキュー防止の効果が小さくなる。その一方で、ころと案内輪との隙間が小さいと、ころと案内輪との接触部で生じる面圧が高くなり、発熱や磨耗の原因となる虞がある。そのため、ころと案内輪との隙間を一定の範囲に収まるようにする必要があるが、それには軸受及び案内輪に対する高い加工精度が必要であり、加工時間や加工費用の増大を招く虞があった。   In general, the effect of preventing the skew of the roller by the guide wheel is larger as the gap between the roller and the guide wheel is smaller, and the effect of preventing the skew is smaller as the gap is larger. On the other hand, if the gap between the roller and the guide wheel is small, the surface pressure generated at the contact portion between the roller and the guide wheel increases, which may cause heat generation and wear. Therefore, it is necessary to keep the gap between the roller and the guide wheel within a certain range. However, this requires high processing accuracy for the bearing and the guide wheel, which may increase the processing time and processing cost. It was.

案内輪の磨耗対策に関する先行技術として、特許文献１には、案内輪の両側面に周方向の溝を形成し、ころ端面と案内輪側面との間の油膜切れによる案内輪の磨耗を防止する発明が開示されている。また、特許文献２には、内輪案内の案内輪内径に、油溝を形成し、内輪外径面に設けた潤滑油の給油通路から潤滑油を供給してころ端面と案内輪側面との間の油膜切れによる案内輪の磨耗を防止する発明が開示されている。   As a prior art related to measures against wear of the guide wheels, Patent Document 1 discloses that circumferential grooves are formed on both side surfaces of the guide wheels to prevent wear of the guide wheels due to oil film breakage between the roller end surfaces and the guide wheel side surfaces. The invention is disclosed. In Patent Document 2, an oil groove is formed in the inner diameter of the guide ring of the inner ring guide, and the lubricating oil is supplied from the lubricating oil supply passage provided on the outer diameter surface of the inner ring so that the gap between the roller end face and the side face of the guide wheel is reduced. An invention for preventing wear of the guide wheel due to the oil film breakage is disclosed.

特開２００７−３１５４５０号公報JP 2007-315450 A 特開２００８−１２１７５５号公報JP 2008-121755 A

しかし、特許文献１、特許文献２に記載の発明はころ端面と案内輪との間に生じる過大な荷重自体を低減することが出来ないという課題があった。   However, the inventions described in Patent Document 1 and Patent Document 2 have a problem that an excessive load itself generated between the roller end face and the guide wheel cannot be reduced.

そこで、本発明はころ端面と案内輪側面との摺接部に過大な荷重が生じるのを防止し、案内輪の磨耗を防止することを課題とする。   Therefore, an object of the present invention is to prevent an excessive load from being generated at the sliding contact portion between the roller end surface and the guide wheel side surface, and to prevent the guide wheel from being worn.

上記課題を解決するために、請求項１に記載の発明は、内周面に球面状の軌道面を有する外輪と、外周面に前記外輪軌道面に対向する複列の軌道面を有する内輪と、前記複列の軌道面に転動自在に配置される複数のころと、前記ころの列間に配置されて前記ころを案内する案内輪と、を備えた複列自動調心ころ軸受において、案内輪の内径は内輪外径面で案内され、且つ、案内輪の外径面及び、内径面の少なくとも一方に環状溝が形成されていることを特徴としている。   In order to solve the above-mentioned problems, an invention according to claim 1 includes an outer ring having a spherical raceway surface on an inner peripheral surface, and an inner ring having a double-row raceway surface facing the outer ring raceway surface on an outer peripheral surface. In the double-row self-aligning roller bearing, comprising a plurality of rollers arranged to roll on the double-row raceway surface, and a guide wheel arranged between the rows of rollers to guide the rollers, The inner diameter of the guide wheel is guided by the outer diameter surface of the inner ring, and an annular groove is formed on at least one of the outer diameter surface and the inner diameter surface of the guide wheel.

本発明によれば、案内輪の外径面、又は内径面に環状溝を設けることで、案内輪側面がころ端面により押圧される際に案内輪が弾性変形し、ころ端面と案内輪側面との接触部に生じる面圧が過大に上昇するのを防止することで、案内輪の磨耗を防止することができる。
それに伴い、ころ端面と案内輪との隙間をころのスキュー制御に有利となる様小さくすることができる。 According to the present invention, by providing an annular groove on the outer diameter surface or inner diameter surface of the guide wheel, the guide wheel elastically deforms when the guide wheel side surface is pressed by the roller end surface, and the roller end surface and the guide wheel side surface By preventing the surface pressure generated at the contact portion from rising excessively, wear of the guide wheel can be prevented.
Accordingly, the gap between the roller end face and the guide wheel can be reduced so as to be advantageous for roller skew control.

本発明の実施形態の一例を示す図である。It is a figure which shows an example of embodiment of this invention. 図1の案内輪とその周辺を拡大した図であり、（ａ）はころと案内輪との間に隙間を有する状態、（ｂ）は案内輪が両列のころに挟まれた状態を示す。FIG. 2 is an enlarged view of the guide wheel of FIG. 1 and its surroundings, where (a) shows a state in which there is a gap between the roller and the guide wheel, and (b) shows a state in which the guide wheel is sandwiched between both rows of rollers. . 本発明の実施形態のもう一つの例を示す図である。It is a figure which shows another example of embodiment of this invention.

以下に、本発明の実施形態を図に基づいて説明する。
図１は本発明に係る複列自動調心ころ軸受の実施形態の一例である。複列自動調心ころ軸受１０は、内周面に球面状の軌道面を有する外輪１と、外周面に外輪１の軌道面と対向する複列の軌道面を有する内輪２と、前記軌道面の間に転動自在に配置される複数のころ３と、ころを周方向に略等間隔に保持する保持器４と、ころ３の列間に配置される案内輪５と、から構成される。案内輪５の両側面はころ３の端面と対面している。案内輪５の内径面には環状溝５ａが形成されており、案内輪５の弾性変形を可能としている。図２（ａ）に示すように、ころ３に軸方向（図中左右方向）荷重が生じていない場合は、ころ３の端面と、案内輪５の側面との間に隙間を有するが、図２（ｂ）に示すように、ころ３に軸方向荷重が生じる等により案内輪５の側面がころ３の端面で押圧された場合にも、案内輪５が軸方向に弾性変形することでころ３からの荷重を低減し、案内輪５ところ３の端面との接触部６に過大な荷重が生じるのを防ぐことができる。 Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is an example of an embodiment of a double row spherical roller bearing according to the present invention. The double row spherical roller bearing 10 includes an outer ring 1 having a spherical raceway surface on an inner peripheral surface, an inner ring 2 having a double row raceway surface facing the raceway surface of the outer ring 1 on the outer peripheral surface, and the raceway surface. A plurality of rollers 3 that are arranged so as to be able to roll between them, a cage 4 that holds the rollers at substantially equal intervals in the circumferential direction, and a guide wheel 5 that is arranged between the rows of rollers 3. . Both side surfaces of the guide wheel 5 face the end surface of the roller 3. An annular groove 5a is formed on the inner diameter surface of the guide wheel 5 so that the guide wheel 5 can be elastically deformed. As shown in FIG. 2A, when no axial load (left-right direction in the figure) is applied to the roller 3, there is a gap between the end surface of the roller 3 and the side surface of the guide wheel 5. As shown in FIG. 2 (b), even when the side surface of the guide wheel 5 is pressed by the end surface of the roller 3 due to an axial load on the roller 3, the roller is elastically deformed in the axial direction. The load from 3 can be reduced, and an excessive load can be prevented from being generated in the contact portion 6 with the guide wheel 5 and the end face of 3.

案内輪５に形成する環状溝５ａの径方向深さは、案内輪５が軸方向に弾性変形し易いように、案内輪５の側面ところ３の端面との接触部６よりも深くすることが好ましい。また、案内輪５が弾性変形する際に環状溝５ａに応力集中が生じない様、環状溝５ａの底面と、側面との境目が曲面で接続されていることが好ましく、底面が曲面で形成されていることがより好ましい。 The radial depth of the annular groove 5a formed in the guide wheel 5 may be deeper than the contact portion 6 with the side surface of the guide wheel 5 and the end face 3 so that the guide wheel 5 is easily elastically deformed in the axial direction. preferable. Moreover, it is preferable that the boundary between the bottom surface and the side surface of the annular groove 5a is connected with a curved surface so that stress concentration does not occur in the annular groove 5a when the guide wheel 5 is elastically deformed, and the bottom surface is formed with a curved surface. More preferably.

図３に本発明に係る第２の実施形態を示す。
案内輪５の環状溝５ｂを外径面に形成することで、ころ３から荷重を受けた場合に、案内輪５が軸方向に弾性変形することで、荷重を低減することができる。他の構成は図１の実施形態と同様である。これらの実施形態は、ころ３と案内輪５との接触部６の位置により、選択できる。 FIG. 3 shows a second embodiment according to the present invention.
By forming the annular groove 5b of the guide wheel 5 on the outer diameter surface, when the load is received from the roller 3, the load can be reduced by elastically deforming the guide wheel 5 in the axial direction. Other configurations are the same as those of the embodiment of FIG. These embodiments can be selected depending on the position of the contact portion 6 between the roller 3 and the guide wheel 5.

なお、上記に示した案内輪５及び環状溝５ａ、５ｂの形態は図１乃至図３に示したものに限定されるものではない。例えば、上記実施例では案内輪５を内輪外径案内としているが、外輪内径案内としても良い。   The forms of the guide wheel 5 and the annular grooves 5a and 5b described above are not limited to those shown in FIGS. For example, in the above embodiment, the guide wheel 5 is an inner ring outer diameter guide, but may be an outer ring inner diameter guide.

１ 外輪
２ 内輪
３ ころ
４ 保持器
５ 案内輪
５ａ 環状溝（案内輪内径側）
５ｂ 環状溝（案内輪外径側）
６ ころ端面と案内輪側面との接触部
１０ 複列自動調心ころ軸受 DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 3 Roller 4 Cage 5 Guide wheel 5a Annular groove (guide wheel inner diameter side)
5b Annular groove (guide wheel outer diameter side)
6 Contact portion between roller end face and guide wheel side face 10 Double row spherical roller bearing

Claims (1)

内周面に球面状の軌道面を有する外輪と、外周面に前記外輪軌道面に対向する複列の軌道面を有する内輪と、前記複列の軌道面に転動自在に配置される複数のころと、前記ころの列間に配置されて前記ころを案内する案内輪と、を備えた複列自動調心ころ軸受において、
案内輪の内径は内輪外径面で案内され、且つ、案内輪の外径面及び、内径面の少なくとも一方に環状溝が形成されていることを特徴とする複列自動調心ころ軸受。 An outer ring having a spherical raceway surface on an inner peripheral surface, an inner ring having a double row raceway surface facing the outer ring raceway surface on an outer peripheral surface, and a plurality of rollers arranged on the double row raceway surface in a freely rolling manner In a double row self-aligning roller bearing comprising a roller and a guide wheel disposed between rows of the rollers to guide the roller,
A double-row self-aligning roller bearing, characterized in that an inner diameter of the guide wheel is guided by an outer diameter surface of the inner ring, and an annular groove is formed on at least one of the outer diameter surface and the inner diameter surface of the guide wheel.
JP2013038889A 2013-02-28 2013-02-28 Rolling bearing Pending JP2014167316A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3495675A1 (en) * 2017-12-11 2019-06-12 Halmeco AB Bearing device having a spring unit

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3495675A1 (en) * 2017-12-11 2019-06-12 Halmeco AB Bearing device having a spring unit

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