JP4876843B2 - Rolling bearing device - Google Patents

Rolling bearing device Download PDF

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JP4876843B2
JP4876843B2 JP2006282470A JP2006282470A JP4876843B2 JP 4876843 B2 JP4876843 B2 JP 4876843B2 JP 2006282470 A JP2006282470 A JP 2006282470A JP 2006282470 A JP2006282470 A JP 2006282470A JP 4876843 B2 JP4876843 B2 JP 4876843B2
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outer ring
ring
radial direction
seal cover
rolling bearing
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JP2008101641A (en
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潤一 久保
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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
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a 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
    • F16C19/22—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
    • F16C19/383—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing device wherein a life of an O-ring is long, water hardly permeates in a bearing and a rated load is large. <P>SOLUTION: Annular recessed parts 76, 86 are formed at sides of sealing devices 8, 9 in shaft directions of outer rings 2, 3 and at an outside end in a radial direction. Bases 70, 80 of seal covers 50, 60 of the sealing devices 8, 9 contact with end surfaces 30, 31 at the sides of the sealing devices 8, 9 in the shaft directions of the outer rings 2, 3 and fitting parts 71, 81 of the seal covers 50, 60 are fit with the annular recessed parts 76, 86 of the outer rings 2, 3. Annular grooves 76, 86 are formed at positions radially overlapped with the end surfaces 30, 31 of the outer rings 2, 3 on an outer circumference surface which is radially outside of the seal covers 50, 60. The O-rings 76, 86 for sealing the seal covers 50, 60 and outer ring fixing members are provided in the annular grooves 76, 86. <P>COPYRIGHT: (C)2008,JPO&amp;INPIT

Description

本発明は、転がり軸受と、Ｏリングとを備える転がり軸受装置に関し、特に、圧延機のワークロールに使用されれば好適な転がり軸受装置に関する。   The present invention relates to a rolling bearing device including a rolling bearing and an O-ring, and more particularly to a rolling bearing device suitable for use in a work roll of a rolling mill.

従来、転がり軸受装置としては、特開昭５４−６９６３９号公報（特許文献１）に記載されているものがある。   Conventionally, as a rolling bearing device, there is one described in Japanese Patent Application Laid-Open No. 54-69639 (Patent Document 1).

この転がり軸受装置は、圧延機のワークロールの一部をなしている。この転がり軸受装置は、内輪と、外輪と、内輪と外輪との間に配置された円錐ころと、外輪に固定されると共に、外輪と内輪との間における外輪の軸方向の一方の側の開口を密封する密封装置とを備えている。上記密封装置は、シールカバーと、シール部とを有している。上記シールカバーは、外輪の軸方向の一方の側の端面に固定されている。また、上記シール部は、一端部が、シールカバーに固定されている一方、他端部は、内輪の外周面に接触している。   This rolling bearing device forms part of a work roll of a rolling mill. The rolling bearing device includes an inner ring, an outer ring, a tapered roller disposed between the inner ring and the outer ring, and an opening on one side in the axial direction of the outer ring between the outer ring and the inner ring. And a sealing device for sealing. The sealing device includes a seal cover and a seal portion. The seal cover is fixed to an end surface on one side of the outer ring in the axial direction. Further, one end portion of the seal portion is fixed to the seal cover, and the other end portion is in contact with the outer peripheral surface of the inner ring.

シールカバーの外輪側とは反対側には、シールカバーの外輪側とは反対側の端面に当接するカバー当接部材が存在している。外輪とカバー当接部材によりシールカバーを軸方向に挟み込んで、シールカバーに軸方向の予圧を付与している。   A cover abutting member that abuts on an end surface of the seal cover opposite to the outer ring side is present on the side opposite to the outer ring side of the seal cover. The seal cover is sandwiched between the outer ring and the cover abutting member in the axial direction, and an axial preload is applied to the seal cover.

シールカバーの外周面における外輪よりも軸方向の外方に位置する部分には、環状溝が形成されている。上記環状溝には、Ｏリングが配置されている。   An annular groove is formed in a portion of the outer peripheral surface of the seal cover that is positioned axially outward from the outer ring. An O-ring is disposed in the annular groove.

外輪の径方向の外方には、外輪を覆うように筒状のハウジングが配置されている。上記Ｏリングは、シールカバーと、上記ハウジングとの間を密封している。このようして、シールカバーと、上記ハウジングとの間から水が軸受装置内に浸入することを防止している。   A cylindrical housing is disposed outside the outer ring in the radial direction so as to cover the outer ring. The O-ring seals between the seal cover and the housing. In this way, water is prevented from entering the bearing device from between the seal cover and the housing.

このような背景において、従来、圧延機のワークロールの一部をなす転がり軸受装置において、Ｏリングの寿命が短くて、水が、シールカバーと、ハウジングとの間から軸受内に浸入し易いという問題がある。   In such a background, conventionally, in a rolling bearing device forming a part of a work roll of a rolling mill, the life of the O-ring is short, and water can easily enter the bearing from between the seal cover and the housing. There's a problem.

また、圧延機のワークロールの一部をなす転がり軸受装置において、転動体の容量を大幅に大きくして、転がり軸受装置の定格荷重を大幅に大きくして欲しいという要請がある。また、転がり軸受装置の寿命を長くして欲しいという要請がある。
特開昭５４−６９６３９号公報（第１図） In addition, there is a demand for a rolling bearing device that forms part of a work roll of a rolling mill to greatly increase the capacity of the rolling element and greatly increase the rated load of the rolling bearing device. There is also a demand for extending the life of rolling bearing devices.
JP 54-69639 A (FIG. 1)

そこで、本発明の課題は、Ｏリングの寿命が長くて、水が内部に浸入しにくく、かつ、定格荷重が大きい転がり軸受装置を提供することにある。   Therefore, an object of the present invention is to provide a rolling bearing device in which the life of an O-ring is long, water hardly enters the inside, and the rated load is large.

上記課題を解決するため、この発明の転がり軸受装置は、
内輪と、環状の外輪固定部材に内嵌される外輪と、上記内輪と上記外輪との間に配置された転動体とを有する転がり軸受と、
上記外輪に固定されると共に、上記外輪と上記内輪との間における上記外輪の軸方向の一方の側の開口を密封する密封装置と
を備え、
上記外輪は、上記外輪の上記軸方向の上記密封装置側かつ上記外輪の径方向の外方側の端部に環状の凹部を有し、
上記密封装置は、上記外輪の上記軸方向の上記密封装置側の端面に当接している基部と、上記基部から上記軸方向に突出すると共に、上記環状の凹部に嵌合している環状の嵌合部とを有する固定部と、上記固定部に固定されると共に、上記開口を密封する密封部とを有し、
上記固定部は、上記固定部の上記径方向の外方の外周面における上記外輪の上記端面と上記径方向に重なる部分に環状溝を有し、
上記環状溝に配置されると共に、上記固定部と上記外輪固定部材との間を密封するＯリングを備えることを特徴としている。 In order to solve the above problems, the rolling bearing device of the present invention is
A rolling bearing having an inner ring, an outer ring fitted in an annular outer ring fixing member, and a rolling element disposed between the inner ring and the outer ring;
A sealing device that is fixed to the outer ring and seals an opening on one side in the axial direction of the outer ring between the outer ring and the inner ring,
The outer ring has an annular recess at an end of the outer ring on the sealing device side in the axial direction and on the outer side in the radial direction of the outer ring,
The sealing device includes a base portion that is in contact with an end surface of the outer ring in the axial direction on the sealing device side, and an annular fitting that protrudes from the base portion in the axial direction and is fitted in the annular recess. A fixing part having a joint part, and a sealing part fixed to the fixing part and sealing the opening,
The fixing portion has an annular groove in a portion overlapping the end surface of the outer ring and the radial direction on the outer peripheral surface in the radial direction of the fixing portion,
An O-ring that is disposed in the annular groove and seals between the fixing portion and the outer ring fixing member is provided.

本発明によれば、上記固定部の上記径方向の外方の外周面における上記外輪の上記端面と上記径方向に重なる部分に、Ｏリングを配置するための環状溝が形成されているから、Ｏリングが外輪の軸方向の外方に位置する従来の構成と比較して、固定部の軸方向の厚さを薄くできる。したがって、固定部の厚さを薄くできる分、転がり軸受の軸方向の長さを長くすることができるから、外輪および内輪の軌道面の軸方向の長さを長くすることができる。したがって、転動体の軸方向の寸法を長くすることができるから、転動体の容量を大きくすることができて、転がり軸受の定格荷重を格段に大きくすることができる。   According to the present invention, an annular groove for arranging an O-ring is formed in a portion overlapping the end surface of the outer ring and the radial direction on the outer peripheral surface in the radial direction of the fixing portion. Compared to the conventional configuration in which the O-ring is positioned outward in the axial direction of the outer ring, the axial thickness of the fixed portion can be reduced. Therefore, since the axial length of the rolling bearing can be increased by the amount that the thickness of the fixed portion can be reduced, the axial lengths of the raceways of the outer ring and the inner ring can be increased. Therefore, since the axial dimension of the rolling element can be increased, the capacity of the rolling element can be increased and the rated load of the rolling bearing can be significantly increased.

また、本発明によれば、上記固定部の上記径方向の外方の外周面における上記外輪の上記端面と上記径方向に重なる部分に、Ｏリングを配置するための環状溝が形成されていて、Ｏリングを配置するための環状溝が、固定部の径方向の外方の外周面における外輪の軸方向の外方に形成されず、かつ、固定部の径方向の外方の外周面における、外輪の端面と径方向に重なる部分よりも上記軸方向の外方とは反対側に形成されていないから、後述するように、Ｏリングの寿命を格段に長くすることができる。したがって、水が、外輪の外周側から軸受内に浸入することを抑制できて、長期に亘って、外輪とハウジングの間から水や圧延油が軸受装置内に浸入することを防止できる。   Further, according to the present invention, an annular groove for arranging an O-ring is formed in a portion overlapping the end surface of the outer ring and the radial direction on the radially outer peripheral surface of the fixing portion. The annular groove for disposing the O-ring is not formed on the outer periphery in the axial direction of the outer ring on the outer peripheral surface in the radial direction of the fixed portion, and on the outer peripheral surface in the radial direction of the fixed portion. Since it is not formed on the side opposite to the outer side in the axial direction from the portion overlapping the end face of the outer ring in the radial direction, the life of the O-ring can be significantly prolonged as will be described later. Accordingly, water can be prevented from entering the bearing from the outer peripheral side of the outer ring, and water and rolling oil can be prevented from entering the bearing device from between the outer ring and the housing over a long period of time.

本発明の転がり軸受によれば、固定部の径方向の外方の外周面における外輪の端面と径方向に重なる部分に、Ｏリングを配置するための環状溝が形成されているから、Ｏリングが外輪の軸方向の外方に位置する構成と比較して、固定部の軸方向の厚さを薄くできて、固定部の厚さを薄くできる分、転がり軸受の軸方向の長さを長くすることができる。したがって、外輪および内輪の軌道面の軸方向の長さを長くすることができて、転動体の軸方向の寸法を長くすることができるから、転がり軸受の定格荷重を格段に大きくすることができる。   According to the rolling bearing of the present invention, since the annular groove for disposing the O-ring is formed in a portion overlapping the end surface of the outer ring in the radial direction on the outer peripheral surface in the radial direction of the fixed portion. Compared with the configuration in which the outer ring is positioned outward in the axial direction, the axial thickness of the rolling bearing can be increased by reducing the axial thickness of the fixed portion and reducing the thickness of the fixed portion. can do. Accordingly, the axial lengths of the raceways of the outer ring and the inner ring can be increased and the axial dimension of the rolling element can be increased, so that the rated load of the rolling bearing can be significantly increased. .

また、本発明の転がり軸受装置によれば、固定部の径方向の外方の外周面における外輪の端面と径方向に重なる部分に、Ｏリングを配置するための環状溝が形成されているから、Ｏリングの寿命を格段に長くすることができて、水が、外輪の外周側から軸受内に浸入することを長期に亘って防止できる。   Further, according to the rolling bearing device of the present invention, the annular groove for disposing the O-ring is formed in a portion overlapping the end surface of the outer ring in the radial direction on the outer peripheral surface in the radial direction of the fixed portion. The life of the O-ring can be remarkably increased, and water can be prevented from entering the bearing from the outer peripheral side of the outer ring over a long period of time.

以下、本発明を図示の形態により詳細に説明する。   Hereinafter, the present invention will be described in detail with reference to the drawings.

図１は、本発明の一実施形態の転がり軸受装置の軸方向の断面図である。   FIG. 1 is an axial sectional view of a rolling bearing device according to an embodiment of the present invention.

この転がり軸受装置は、圧延機のワークロールの一部をなしている。この転がり軸受装置は、内輪１、第１外輪２、第２外輪３、円錐ころ５,６、第１密封装置８、および、第２密封装置９を備える。上記内輪１は、ワークロールの軸（図示せず）の外周面に外嵌されている一方、第１および第２外輪２,３は、筒状のハウジング（図示せず）の内周面に内嵌されている。   This rolling bearing device forms part of a work roll of a rolling mill. The rolling bearing device includes an inner ring 1, a first outer ring 2, a second outer ring 3, tapered rollers 5 and 6, a first sealing device 8, and a second sealing device 9. The inner ring 1 is externally fitted on the outer peripheral surface of a work roll shaft (not shown), while the first and second outer rings 2 and 3 are provided on the inner peripheral surface of a cylindrical housing (not shown). It is fitted inside.

この転がり軸受装置は、圧延機のワークロールで使用される転がり軸受装置特有の嵌合いで、軸およびハウジングに嵌合している。詳しくは、軸に対する内輪１の嵌合いが比較的緩く、すなわち、すきまをもって嵌合し、かつ、ハウジングに対する第１外輪２および第２外輪３の嵌合いが比較的緩い条件で、すなわち、すきまをもって嵌合している。   This rolling bearing device is fitted to a shaft and a housing by a fitting unique to the rolling bearing device used in a work roll of a rolling mill. Specifically, the inner ring 1 is relatively loosely fitted to the shaft, that is, fitted with a gap, and the first outer ring 2 and the second outer ring 3 are fitted to the housing relatively loosely, that is, with a gap. It is mated.

上記内輪１は、図１の軸方向の断面図において、内輪１の中心軸の垂直二等分面に対して左右対称の形状を有している。上記内輪１の外周面は、軸方向互いに隣接する第１円錐軌道面１０および第２円錐軌道面１１を有している。上記内輪１は、外周面の軸方向の両端部にシールリップ摺動溝を有している。   The inner ring 1 has a symmetrical shape with respect to a perpendicular bisector of the central axis of the inner ring 1 in the axial sectional view of FIG. The outer peripheral surface of the inner ring 1 has a first conical track surface 10 and a second conical track surface 11 that are adjacent to each other in the axial direction. The inner ring 1 has seal lip sliding grooves at both ends in the axial direction of the outer peripheral surface.

上記第１および第２外輪２,３は、上記垂直二等分面に対して左右対称に配置されている。上記第１外輪２と第２外輪３との軸方向の間には、外輪間座２０が配置されている。第１密封装置８の軸方向の外方には、第１密封装置８に軸方向に当接している第１軸受当接部材（図示せず）が配置されている一方、第２密封装置９の軸方向の外方には、第２密封装置９に軸方向に当接する第２軸受当接部材（図示せず）が配置されている。第１軸受当接部材と第２軸受当接部材とで面接触で転がり軸受装置を軸方向に挟み込むことによって、転がり軸受装置に軸方向の予圧を付与するようになっている。   The first and second outer rings 2, 3 are arranged symmetrically with respect to the vertical bisector. An outer ring spacer 20 is disposed between the first outer ring 2 and the second outer ring 3 in the axial direction. A first bearing abutting member (not shown) that abuts the first sealing device 8 in the axial direction is disposed outside the first sealing device 8 in the axial direction, while the second sealing device 9. A second bearing abutting member (not shown) that abuts the second sealing device 9 in the axial direction is disposed on the outside in the axial direction. An axial preload is applied to the rolling bearing device by sandwiching the rolling bearing device in the axial direction by surface contact between the first bearing abutting member and the second bearing abutting member.

上記円錐ころ５は、内輪１の第１円錐軌道面１０と第１外輪２の円錐軌道面２４との間に、保持器２０に保持された状態で、周方向に所定間隔を隔てられて複数配置されている。また、円錐ころ６は、内輪１の第２円錐軌道面１１と第２外輪３の円錐軌道面２５との間に、保持器２１に保持された状態で、周方向に所定間隔を隔てられて複数配置されている。   A plurality of the tapered rollers 5 are provided at a predetermined interval in the circumferential direction while being held by the cage 20 between the first conical raceway surface 10 of the inner ring 1 and the conical raceway surface 24 of the first outer ring 2. Has been placed. Further, the tapered roller 6 is spaced apart from the second conical raceway surface 11 of the inner ring 1 and the conical raceway surface 25 of the second outer ring 3 by a predetermined distance in the circumferential direction while being held by the cage 21. Several are arranged.

上記第１密封装置８と、上記第２密封装置９とは、上記垂直二等分面に対して左右対称に配置されている。上記第１密封装置８は、第１外輪２の円錐軌道面２４の小径側の端面３０に当接するように配置される一方、第２密封装置９は、第２外輪３の円錐軌道面２５の小径側の端面３１に当接するように配置されている。第１外輪２は、第１外輪２の軸方向の第１密封装置８側かつ径方向の外方側の端部に、環状の凹部４１を有し、第２外輪３は、第２外輪３の軸方向の第２密封装置９側かつ径方向の外方側の端部に、環状の凹部４２を有している。   The first sealing device 8 and the second sealing device 9 are arranged symmetrically with respect to the vertical bisector. The first sealing device 8 is disposed so as to contact the end surface 30 on the small diameter side of the conical raceway surface 24 of the first outer ring 2, while the second sealing device 9 is provided on the conical raceway surface 25 of the second outer ring 3. It arrange | positions so that it may contact | abut to the end surface 31 of a small diameter side. The first outer ring 2 has an annular recess 41 at the end on the first sealing device 8 side in the axial direction of the first outer ring 2 and on the outer side in the radial direction, and the second outer ring 3 is the second outer ring 3. An annular recess 42 is provided at the end portion on the second sealing device 9 side in the axial direction and on the outer side in the radial direction.

上記第１密封装置８は、第１外輪２に固定された固定部としての第１シールカバー５０と、この第１シールカバー５０に固定されると共に、内輪１と第１外輪２との間を密封する第１シールリップ５２を備える第１密封部５１とを有し、第２密封装置９は、第２外輪３に固定された固定部としての第２シールカバー６０と、この第２シールカバー６０に固定されると共に、内輪１と第２外輪３との間を密封する第２シールリップ６２を備える第２密封部６１とを有している。   The first sealing device 8 is fixed to the first seal cover 50 as a fixing portion fixed to the first outer ring 2 and between the inner ring 1 and the first outer ring 2. The second sealing device 9 includes a second sealing cover 60 as a fixing portion fixed to the second outer ring 3, and the second sealing cover. And a second sealing portion 61 including a second seal lip 62 that seals between the inner ring 1 and the second outer ring 3.

上記第１シールカバー５０は、上記ハウジングと径方向にすきまをもって配設されるものであり、第１外輪２の軸方向の第１密封装置８側の端面３０に当接している第１基部７０と、第１基部７０から軸方向に突出すると共に、環状の凹部４１に径方向にすきまをもって嵌合している環状の第１嵌合部７１とを有している。上記第１シールカバー５０は、第１シールカバー５０の径方向の外方の外周面における第１外輪２の端面３０と径方向に重なる部分に環状溝７６を有している。この環状溝７６には、第１シールカバー５０と上記ハウジングの間を密封するＯリング７８が配置されている。   The first seal cover 50 is disposed with a clearance in the radial direction with respect to the housing, and a first base portion 70 that is in contact with the end surface 30 on the first sealing device 8 side in the axial direction of the first outer ring 2. And an annular first fitting portion 71 that protrudes in the axial direction from the first base portion 70 and is fitted into the annular recess 41 with a clearance in the radial direction. The first seal cover 50 has an annular groove 76 at a portion overlapping the end surface 30 of the first outer ring 2 in the radial direction on the outer circumferential surface of the first seal cover 50 in the radial direction. An O-ring 78 that seals between the first seal cover 50 and the housing is disposed in the annular groove 76.

上記第２シールカバー６０は、上記ハウジングと径方向にすきまをもって配設されるものであり、第２外輪３の軸方向の第２密封装置９側の端面３１に当接している第２基部８０と、第２基部８０から軸方向に突出すると共に、環状の凹部４２に径方向にすきまをもって嵌合している環状の第２嵌合部８１とを有している。上記第２シールカバー６０は、第２シールカバー６０の径方向の外方の外周面における第２外輪３の端面３１と径方向に重なる部分に環状溝８６を有している。この環状溝８６には、第２シールカバー６０と上記ハウジングの間を密封するＯリング８８が配置されている。   The second seal cover 60 is disposed with a clearance in the radial direction with respect to the housing, and a second base portion 80 that is in contact with the end surface 31 on the second sealing device 9 side in the axial direction of the second outer ring 3. And an annular second fitting portion 81 that protrudes in the axial direction from the second base portion 80 and is fitted to the annular recess 42 with a gap in the radial direction. The second seal cover 60 has an annular groove 86 at a portion overlapping the end surface 31 of the second outer ring 3 in the radial direction on the outer circumferential surface of the second seal cover 60 in the radial direction. An O-ring 88 that seals between the second seal cover 60 and the housing is disposed in the annular groove 86.

圧延機のワークロールでは、ワークロールを圧延材が通過する際、転がり軸受装置の外輪の中心軸が、圧延材が通過していない場合の中心軸の位置に対して、傾くことがある。   In the work roll of the rolling mill, when the rolled material passes through the work roll, the central axis of the outer ring of the rolling bearing device may be inclined with respect to the position of the central axis when the rolled material does not pass.

このとき、第１シールカバー５０と第２シールカバー６０とは、第１外輪２、円錐ころ５、内輪１、円錐ころ６、第２外輪３を介して、上記第１軸受当接部材と上記第２軸受当接部材とで軸方向に面接触で狭み固定されている。ワークの通過に伴いワークロールの軸が軸方向に略同一の方向から図１に矢印Ａで示す方向に傾き、ワークの通過後にＢで示す方向に軸方向に略同一の方向に戻るよう揺動した場合、内輪１が傾き、転動体としての円錐ころ５,６を介して第１外輪２、第２外輪３が傾くことになる。しかし、第１シールカバー５０と第１軸受当接部材との間は面接触で接触し、第１シールカバー５０は傾きにくいものとなっている。また、第２シールカバー６０と第２軸受当接部材との間は面接触で接触し、第２シールカバー６０は傾きにくいものとなっている。   At this time, the first seal cover 50 and the second seal cover 60 are connected to the first bearing abutting member and the second outer ring 3 via the first outer ring 2, the tapered roller 5, the inner ring 1, the tapered roller 6, and the second outer ring 3. The second bearing contact member is fixed in a narrow manner by surface contact in the axial direction. As the workpiece passes, the axis of the workpiece roll tilts in the direction indicated by arrow A in FIG. 1 from the substantially same direction in the axial direction, and swings so as to return to the direction indicated by B in the axial direction after passing the workpiece. In this case, the inner ring 1 is inclined, and the first outer ring 2 and the second outer ring 3 are inclined via the tapered rollers 5 and 6 as rolling elements. However, the first seal cover 50 and the first bearing contact member are in surface contact with each other, and the first seal cover 50 is not easily tilted. Further, the second seal cover 60 and the second bearing contact member are in surface contact with each other, and the second seal cover 60 is not easily tilted.

このような動作に対し、Ｏリングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面よりも軸方向の外方に形成されている場合や軸方向の内方に形成されている場合、第１外輪２の径方向外方にある第１シールカバーの第１嵌合部は第１シールカバーの第１基部との取り付け部の剛性が高いため、上記の揺動に対し第１シールカバーの第１基部は第１外輪２の傾き、特に端面３０の外周部の径方向の変位により、第１軸受当接部材と大きな摩擦を伴い径方向一方に移動し、外輪２の軸心とずれた位置に移動する。このとき、環状溝に配設されるＯリングも径方向一方側に押さえつけられるため、Ｏリングの部分的な圧縮が生じる。第２外輪３の径方向外方にある第２シールカバーの第２嵌合部についても第２シールカバーの第２基部との取り付け部の剛性が高いため、上記の揺動に対し第２シールカバーの第２基部は第２外輪３の傾き、特に端面３１の外周部の径方向の変位により、第２軸受当接部材と大きな摩擦を伴い径方向一方側とは周方向に略１８０°反対側である径方向他方側に移動し、外輪３の軸心とずれた位置に移動する。このとき、環状溝に配設されるＯリングも径方向他方側に押さえつけられるため、Ｏリングの部分的な圧縮が生じる。   For such an operation, when the annular groove for arranging the O-ring is formed axially outward from the end surface of the outer ring on the radially outer peripheral surface of the seal cover, or in the axial direction The first fitting portion of the first seal cover located radially outward of the first outer ring 2 has a high rigidity of the attachment portion with the first base portion of the first seal cover. The first base portion of the first seal cover moves in one radial direction with great friction with the first bearing contact member due to the inclination of the first outer ring 2, particularly the radial displacement of the outer peripheral portion of the end face 30, with respect to the swing. Then, it moves to a position shifted from the axis of the outer ring 2. At this time, since the O-ring disposed in the annular groove is also pressed against one side in the radial direction, partial compression of the O-ring occurs. The second fitting portion of the second seal cover that is radially outward of the second outer ring 3 is also highly rigid in the attachment portion with the second base portion of the second seal cover. The second base portion of the cover is opposite to the second bearing contact member by a large amount of friction due to the inclination of the second outer ring 3, in particular the radial displacement of the outer peripheral portion of the end face 31, and is approximately 180 ° opposite to the radial direction. It moves to the other side in the radial direction which is the side, and moves to a position shifted from the axis of the outer ring 3. At this time, since the O-ring disposed in the annular groove is also pressed against the other side in the radial direction, partial compression of the O-ring occurs.

これに対し、Ｏリングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面と径方向に重なる部分に形成されている場合、第１外輪２の径方向外方にある第１シールカバー５０の第１嵌合部７１は第１シールカバーの第１基部７０との取り付け部の剛性が適切なものとなり、上記の揺動に対し、第１シールカバー５０の第１嵌合部７１の弾性変形によって、第１外輪２の傾きは吸収され、第１シールカバーの第１基部７０は第１外輪２の傾き、特に端面３０の外周部の径方向の変位によっても、第１基部７０と第１軸受当接部材との間の大きな摩擦により、ほとんど径方向には動かない。このため、第１シールカバー５０の環状溝７６も径方向にほとんど移動せず、Ｏリング７８が径方向一方側へ移動することによるＯリング７８の部分的な圧縮が生じることを抑制できる。同様に、第２外輪３の径方向外方にある第２シールカバー６０の第２嵌合部８１は第２シールカバーの第２基部８０との取り付け部の剛性が適切なものとなり、上記の揺動に対し、第２シールカバー６０の第２嵌合部８１の弾性変形によって、第２外輪３の傾きは吸収され、第２シールカバーの第２基部８０は第２外輪３の傾き、特に端面３１の外周部の径方向の変位によっても、第２基部８０と第２軸受当接部材との間の大きな摩擦により、ほとんど径方向には動かない。このため、第２シールカバー６０の環状溝８６も径方向にほとんど移動せず、Ｏリング８８が径方向一方側とは周方向に略１８０°反対側である径方向他方側へ移動することによるＯリング８８の部分的な圧縮が生じることを抑制できる。   On the other hand, when the annular groove for placing the O-ring is formed in a portion overlapping the end surface of the outer ring in the radial direction on the outer peripheral surface in the radial direction of the seal cover, The first fitting portion 71 of the first seal cover 50 on the side has an appropriate rigidity of the attachment portion with the first base portion 70 of the first seal cover, and the first seal cover 50 has the rigidity of the first seal cover 50 against the above-mentioned swinging. By the elastic deformation of the first fitting portion 71, the inclination of the first outer ring 2 is absorbed, and the first base portion 70 of the first seal cover is inclined by the inclination of the first outer ring 2, particularly the radial displacement of the outer peripheral portion of the end face 30. However, it hardly moves in the radial direction due to a large friction between the first base portion 70 and the first bearing contact member. For this reason, the annular groove 76 of the first seal cover 50 hardly moves in the radial direction, and partial compression of the O-ring 78 due to the movement of the O-ring 78 to one side in the radial direction can be suppressed. Similarly, the second fitting portion 81 of the second seal cover 60 located radially outward of the second outer ring 3 has an appropriate rigidity of the attachment portion with the second base portion 80 of the second seal cover, and the above-mentioned The inclination of the second outer ring 3 is absorbed by the elastic deformation of the second fitting portion 81 of the second seal cover 60 with respect to the swing, and the second base 80 of the second seal cover is inclined by the inclination of the second outer ring 3, particularly Even the radial displacement of the outer peripheral portion of the end surface 31 hardly moves in the radial direction due to the large friction between the second base portion 80 and the second bearing contact member. For this reason, the annular groove 86 of the second seal cover 60 hardly moves in the radial direction, and the O-ring 88 moves to the other side in the radial direction that is substantially 180 ° opposite to the one side in the radial direction. Occurrence of partial compression of the O-ring 88 can be suppressed.

すなわち、第１および第２外輪が、図１に矢印ＡおよびＢで示す方向に揺動した場合、Ｏリングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面よりも軸方向の外方に形成されている場合のＯリングの径方向の変位は、Ｏリングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面と径方向に重なる部分に形成されている場合のＯリングの径方向の変位よりも大きくなる。   That is, when the first and second outer rings are swung in the directions indicated by arrows A and B in FIG. 1, the annular groove for arranging the O-ring is formed on the outer ring on the outer circumferential surface in the radial direction of the seal cover. The radial displacement of the O-ring when it is formed axially outward from the end surface is such that the annular groove for disposing the O-ring is different from the end surface of the outer ring on the radially outer peripheral surface of the seal cover. It becomes larger than the displacement in the radial direction of the O-ring when it is formed in a portion overlapping in the radial direction.

また、同様に、第１および第２外輪が、図１に矢印ＡおよびＢで示す方向に揺動した場合、Ｏリングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面よりも軸方向の内方に形成されている場合のＯリングの径方向の変位は、Ｏリングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面と径方向に重なる部分に形成されている場合のＯリングの径方向の変位よりも大きくなる。   Similarly, when the first and second outer rings swing in the directions indicated by arrows A and B in FIG. 1, the annular groove for placing the O-ring is an outer peripheral surface in the radial direction of the seal cover. The radial displacement of the O-ring in the case where the O-ring is formed inward in the axial direction relative to the end surface of the outer ring in the outer ring in the outer ring on the outer peripheral surface in the radial direction of the seal cover It becomes larger than the displacement in the radial direction of the O-ring when it is formed in a portion overlapping with the end surface of the O-ring in the radial direction.

すなわち、Ｏリングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面と径方向に重なる部分に形成されている場合が、図１に矢印ＡおよびＢで示す方向の揺動に対して、最もＯリングの径方向の変位が少なくなる。このことから、リングを配置するための環状溝がシールカバーの径方向の外方の外周面における外輪の端面と径方向に重なる部分に形成されている場合に、Ｏリングのへたりが最も小さくなる。   That is, the case where the annular groove for arranging the O-ring is formed in a portion overlapping the end surface of the outer ring in the radial direction on the radially outer peripheral surface of the seal cover is indicated by arrows A and B in FIG. The displacement in the radial direction of the O-ring is the smallest with respect to the swing in the direction. Therefore, when the annular groove for disposing the ring is formed in a portion overlapping the end surface of the outer ring in the radial direction on the outer peripheral surface in the radial direction of the seal cover, the sag of the O-ring is the smallest. Become.

上記実施形態の転がり軸受装置によれば、シールカバー５０,６０の径方向の外方の外周面における外輪２,３の端面と上記径方向に重なる部分に、Ｏリング７８,８８を配置するための環状溝７６,８６が形成されているから、Ｏリング７８,８８が外輪２,３の軸方向の外方に位置する従来の構成と比較して、シールカバー５０,６０の軸方向の厚さを薄くできる。したがって、シールカバー５０,６０の厚さを薄くできる分、円錐ころ軸受の軸方向の長さを長くすることができるから、外輪２,３および内輪１の円錐軌道面１０,１１,２４,２５の軸方向の長さを長くすることができる。したがって、円錐ころ５,６の軸方向の寸法を長くすることができるから、転がり軸受装置の定格荷重を格段に大きくすることができる。   According to the rolling bearing device of the above-described embodiment, the O-rings 78 and 88 are disposed on the radially outer peripheral surfaces of the seal covers 50 and 60 on the end surfaces of the outer rings 2 and 3 and overlapping with the radial direction. Since the annular grooves 76 and 86 are formed, the axial thicknesses of the seal covers 50 and 60 are compared with the conventional configuration in which the O-rings 78 and 88 are positioned outwardly in the axial direction of the outer rings 2 and 3. Can be thin. Accordingly, the axial length of the tapered roller bearing can be increased by the amount that the thickness of the seal covers 50, 60 can be reduced, so that the conical raceway surfaces 10, 11, 24, 25 of the outer rings 2, 3 and the inner ring 1 can be obtained. The length in the axial direction can be increased. Therefore, since the axial dimension of the tapered rollers 5 and 6 can be increased, the rated load of the rolling bearing device can be significantly increased.

また、上記実施形態の転がり軸受装置によれば、シールカバー５０,６０の径方向の外方の外周面における外輪２,３の端面３０,３１と径方向に重なる部分に、Ｏリング７８,８８を配置するための環状溝７６,８６が形成されていて、Ｏリング７８,８８を配置するための環状溝７６,８６が、シールカバー５０,６０の径方向の外方の外周面における外輪２,３の軸方向の外方に形成されず、かつ、シールカバー５０,６０の径方向の外方の外周面における、外輪２,３の端面と径方向に重なる部分よりも軸方向の内側（外方とは反対側）に形成されていないから、Ｏリング７８,８８の寿命を格段に長くすることができる。したがって、冷却水および圧延油が、外輪２,３の外周側から軸受装置内に浸入することを抑制できる。   Further, according to the rolling bearing device of the above-described embodiment, the O-rings 78 and 88 are disposed on the radially outer peripheral surfaces of the seal covers 50 and 60 on the portions overlapping the end surfaces 30 and 31 of the outer rings 2 and 3 in the radial direction. Annular grooves 76, 86 for arranging the O-rings 78, 88 are formed, and the annular grooves 76, 86 for arranging the O-rings 78, 88 are formed on the outer ring 2 on the radially outer peripheral surface of the seal cover 50, 60. 3 on the outer peripheral surface in the radial direction of the seal covers 50, 60 and on the inner side in the axial direction with respect to the end surfaces of the outer rings 2, 3 in the radial direction ( Since it is not formed on the side opposite to the outer side, the service life of the O-rings 78 and 88 can be significantly increased. Therefore, it is possible to suppress the cooling water and the rolling oil from entering the bearing device from the outer peripheral side of the outer rings 2 and 3.

尚、上記転がり軸受装置では、円錐軌道面２４,２５を一つ有する外輪２,３を２つ有し、かつ、内輪１が、内輪１の中心軸の垂直二等分面に対して左右対称な２つの円錐軌道面を有していたが、この発明では、内輪は、転動体が転動する環状の軌道面を一つだけ、または、３つ以上有していても良い。また、軸方向に隣接配置される複数の内輪からなる複合内輪を採用しても良い。また、外輪は、一つの外輪に軌道面を２つ以上有していても良い。また、外輪は、この実施形態のように、軸方向に隣接する２つの外輪２,３からなる複合外輪でなくても良く、軸方向に隣接する３つ以上の外輪からなる複合外輪であっても良い。また、外輪は、一つの外輪のみで構成されていても良い。また、転動体は、この実施形態のように、円錐ころ５,６でなくても良く、例えば、円筒ころ、玉であっても良く、円すいころ、円筒ころおよび玉のうちの２つ以上で構成されていても良い。   The rolling bearing device has two outer rings 2 and 3 each having one conical raceway surface 24 and 25, and the inner ring 1 is symmetrical with respect to a vertical bisector of the central axis of the inner ring 1. In the present invention, the inner ring may have only one or three or more annular raceway surfaces on which the rolling elements roll. Moreover, you may employ | adopt the composite inner ring | wheel which consists of a some inner ring | wheel arrange | positioned adjacent to an axial direction. The outer ring may have two or more raceway surfaces in one outer ring. Further, the outer ring may not be a composite outer ring composed of two outer rings 2 and 3 adjacent in the axial direction as in this embodiment, but a composite outer ring composed of three or more outer rings adjacent in the axial direction. Also good. Further, the outer ring may be composed of only one outer ring. Further, the rolling element may not be the tapered rollers 5 and 6 as in this embodiment, and may be, for example, a cylindrical roller or a ball, and may be two or more of a tapered roller, a cylindrical roller and a ball. It may be configured.

また、上記転がり軸受装置では、密封装置８,９が、転がり軸受装置の軸方向の両端部に位置していたが、この発明では、密封装置が、転がり軸受装置の軸方向の片側のみに位置していても良い。   Further, in the rolling bearing device, the sealing devices 8 and 9 are positioned at both ends in the axial direction of the rolling bearing device. However, in the present invention, the sealing device is positioned only on one side in the axial direction of the rolling bearing device. You may do it.

本発明の一実施形態の転がり軸受装置の軸方向の断面図である。It is sectional drawing of the axial direction of the rolling bearing apparatus of one Embodiment of this invention.

符号の説明Explanation of symbols

１ 内輪
２ 第１外輪
３ 第２外輪
５,６ 円錐ころ
８ 第１密封装置
９ 第２密封装置
３０,３１ 端面
５０ 第１シールカバー
６０ 第２シールカバー
７０,８０ 基部
７１,８１ 嵌合部
７６,８６ 環状溝
７８,８８ Ｏリング DESCRIPTION OF SYMBOLS 1 Inner ring 2 1st outer ring 3 2nd outer ring 5,6 Tapered roller 8 1st sealing device 9 2nd sealing device 30,31 End surface 50 1st seal cover 60 2nd seal cover 70,80 Base 71,81 Fitting part 76 , 86 Annular groove 78,88 O-ring

Claims (1)

内輪と、環状の外輪固定部材に内嵌される外輪と、上記内輪と上記外輪との間に配置された転動体とを有する転がり軸受と、
上記外輪に固定されると共に、上記外輪と上記内輪との間における上記外輪の軸方向の一方の側の開口を密封する密封装置と
を備え、
上記外輪は、上記外輪の上記軸方向の上記密封装置側かつ上記外輪の径方向の外方側の端部に環状の凹部を有し、
上記密封装置は、上記外輪の上記軸方向の上記密封装置側の端面に当接している基部と、上記基部から上記軸方向に突出すると共に、上記環状の凹部に嵌合している環状の嵌合部とを有する固定部と、上記固定部に固定されると共に、上記開口を密封する密封部とを有し、
上記固定部は、上記固定部の上記径方向の外方の外周面における上記外輪の上記端面と上記径方向に重なる部分に環状溝を有し、
上記環状溝に配置されると共に、上記固定部と上記外輪固定部材との間を密封するＯリングを備えることを特徴とする転がり軸受装置。 A rolling bearing having an inner ring, an outer ring fitted in an annular outer ring fixing member, and a rolling element disposed between the inner ring and the outer ring;
A sealing device that is fixed to the outer ring and seals an opening on one side in the axial direction of the outer ring between the outer ring and the inner ring,
The outer ring has an annular recess at an end of the outer ring on the sealing device side in the axial direction and on the outer side in the radial direction of the outer ring,
The sealing device includes a base portion that is in contact with the end surface of the outer ring on the sealing device side in the axial direction, and an annular fitting that protrudes from the base portion in the axial direction and is fitted in the annular recess. A fixing part having a joint part, and a sealing part fixed to the fixing part and sealing the opening,
The fixing portion has an annular groove in a portion overlapping the end surface of the outer ring and the radial direction on the outer peripheral surface in the radial direction of the fixing portion,
A rolling bearing device comprising an O-ring that is disposed in the annular groove and seals between the fixing portion and the outer ring fixing member.
JP2006282470A 2006-10-17 2006-10-17 Rolling bearing device Active JP4876843B2 (en)

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Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5886921A (en) * 1981-11-18 1983-05-24 Mitsubishi Electric Corp Speed controlling system of carrying and winding equipment of steel plate
JPS5986418A (en) * 1982-11-10 1984-05-18 株式会社東芝 Stationary protecting relay
JPS639776A (en) * 1986-06-30 1988-01-16 Mitsubishi Atom Power Ind Inc Carrier ring
JP3687199B2 (en) * 1996-07-05 2005-08-24 日本精工株式会社 Rolling bearing unit with rotational speed detector
JPH11257361A (en) * 1998-01-08 1999-09-21 Nippon Seiko Kk Sealing device for rolling bearing
JP4240197B2 (en) * 2002-07-22 2009-03-18 株式会社ジェイテクト SEALING DEVICE FOR ROLLING BEARING AND ROLLING BEARING DEVICE
JP4234127B2 (en) * 2004-10-08 2009-03-04 Ｎｔｎ株式会社 Rolling bearing

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