JP2009156421A - Sealed roll neck bearing - Google Patents

Sealed roll neck bearing Download PDF

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JP2009156421A
JP2009156421A JP2007337770A JP2007337770A JP2009156421A JP 2009156421 A JP2009156421 A JP 2009156421A JP 2007337770 A JP2007337770 A JP 2007337770A JP 2007337770 A JP2007337770 A JP 2007337770A JP 2009156421 A JP2009156421 A JP 2009156421A
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roll neck
radial lip
outer peripheral
neck bearing
sealing device
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JP5098637B2 (en
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Sadayuki Tanaka
貞幸 田中
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NSK Ltd
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NSK Ltd
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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
    • F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • 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
    • F16C19/388—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 four rows, i.e. four 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 sealed roll neck bearing high in mounting stiffness, excellent in assembly property with respect to a roll neck part, and high in sealing performance. <P>SOLUTION: The sealed roll neck bearing 40 has a sealing device 51 installed to outer peripheral faces 43d, 44d of abutment parts of a pair of inner rings 43, 44. The sealing device 51 has an elastic seal member 53 having a fitting part 54 and a radial lip part 55, and a core metal 52 disposed to cover at least the radially outside of the fitting part 54. The fitting part 54 is fitted to an outer peripheral face 43d of one inner ring to give the high mounting stiffness the sealing device 51, and the radial lip part 55 is brought into slide-contact with an outer peripheral face of the other inner ring to follow eccentricity of inner rings 43, 44 and secure high sealing performance. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、密封型ロールネック軸受に関し、より詳細には、例えば、鉄鋼設備の圧延機に使用される優れたシール性能を有する密封型ロールネック軸受に関する。   The present invention relates to a hermetic roll neck bearing, and more particularly to a hermetic roll neck bearing having excellent sealing performance, for example, used in a rolling mill for steel equipment.

鉄鋼設備の熱間圧延機や冷間圧延機に使用される密封型ロールネック軸受（４列円錐ころ軸受）１は、図９に示すように、外輪２及び複列外輪３と、一対の複列内輪４と、外輪２と複列内輪４、及び複列外輪３と複列内輪４間に転動自在に配設された複数の円錐ころ５とを備え、複列内輪４がロール６のロールネック部７にすきまばめ（ルーズフィット）されて使用される。一対の複列内輪４の軸端側の一端には、内輪押え部材であるフィレットリング８が配置されて複列内輪４の軸方向の位置決めを行う。フィレットリング８の内周面には、Ｏリングなどのシール９が配設されてロールネック部７の外周面との間をシールしている。   As shown in FIG. 9, a sealed roll neck bearing (four-row tapered roller bearing) 1 used in a hot rolling mill and a cold rolling mill of a steel facility is composed of an outer ring 2 and a double-row outer ring 3, and a pair of A row inner ring 4, an outer ring 2, a double row inner ring 4, and a plurality of tapered rollers 5 rotatably disposed between the double row outer ring 3 and the double row inner ring 4. The roll neck 7 is used after being loosely fitted (loose fit). At one end of the pair of double-row inner rings 4 on the shaft end side, a fillet ring 8 that is an inner ring pressing member is disposed to position the double-row inner rings 4 in the axial direction. A seal 9 such as an O-ring is disposed on the inner peripheral surface of the fillet ring 8 to seal between the outer peripheral surface of the roll neck portion 7.

チョック（ハウジング）１０の軸側端部とフィレットリング８、及びチョック１０のロール側端部とロールネック部７との間には、それぞれチョックシール１１、１２が配置されている。また、それぞれの外輪２の外方側部には、チョック１０の内周面との間がＯリング１３でシールされたシールホルダー１４が設けられており、シールホルダー１４に固着されるオイルシール１５が、複列内輪４の外周面に摺接して密封型ロールネック軸受１がシールされる。   Chock seals 11 and 12 are disposed between the shaft side end of the chock (housing) 10 and the fillet ring 8, and between the roll side end of the chock 10 and the roll neck 7, respectively. Further, a seal holder 14 sealed with an O-ring 13 between the inner peripheral surface of the chock 10 is provided on the outer side portion of each outer ring 2, and an oil seal 15 fixed to the seal holder 14 is provided. However, the sealed roll neck bearing 1 is sealed in sliding contact with the outer peripheral surface of the double row inner ring 4.

このような密封型ロールネック軸受１は、大きな荷重が作用すると共に、周囲がスケール圧延水に覆われた大変過酷な使用環境で使用される。そのため、Ｏリング９やチョックシール１１、１２が損傷を受けると、複列内輪４の内周面側から密封型ロールネック軸受１内に水、異物などが浸入する場合があり、軸受寿命が短くなる虞がある。従って、両端に備わるシール部材（Ｏリング９やチョックシール１１、１２）の耐久性が課題として挙げられ、ゴム材料の耐熱性向上、リップ形状設計などの改良により、軸受内への水、異物などの浸入に対する改善がなされてきている。   Such a sealed-type roll neck bearing 1 is used in a very severe usage environment in which a large load acts and the periphery is covered with scale-rolled water. Therefore, if the O-ring 9 or the chock seals 11 and 12 are damaged, water, foreign matter, etc. may enter the sealed roll neck bearing 1 from the inner peripheral surface side of the double-row inner ring 4 and the bearing life is shortened. There is a risk of becoming. Therefore, the durability of the seal members (O-ring 9 and chock seals 11 and 12) provided at both ends is cited as an issue. By improving the heat resistance of the rubber material and improving the lip shape design, water in the bearing, foreign matter, etc. Improvements have been made to the penetration of

一方、密封型ロールネック軸受１の複列内輪４は、ロールネック部７とルーズフィットし、フィレットリング８により軸方向位置決めがされているが、フィレットリング８の内周面に設けられたシール９は、メンテナンスなどのためにロールネック部７からの着脱が繰り返されることで破損する可能性がある。シール９が損傷を受けると、軸端側からルーズフィットしている嵌め合い面を通じて水、異物などが浸入し、一対の複列内輪４の突合せ面から密封型ロールネック軸受１内にも浸入してしまう虞がある。そのため、密封型ロールネック軸受１は、複列内輪４端部の突合せ部にもシール装置（中間シール）１６を備えて水などの浸入防止を図った構造が一般的に採用されている。   On the other hand, the double-row inner ring 4 of the sealed roll neck bearing 1 loosely fits with the roll neck portion 7 and is axially positioned by the fillet ring 8, but the seal 9 provided on the inner peripheral surface of the fillet ring 8. May be damaged by repeated attachment and detachment from the roll neck portion 7 for maintenance or the like. When the seal 9 is damaged, water, foreign matter and the like enter through the fitting surface loosely fitted from the shaft end side, and also enter the sealed roll neck bearing 1 from the abutting surfaces of the pair of double-row inner rings 4. There is a risk that. Therefore, the sealed roll neck bearing 1 generally employs a structure in which a sealing device (intermediate seal) 16 is provided at the abutting portion at the end of the double row inner ring 4 to prevent intrusion of water or the like.

また近年の軸受周りの設計構造としては、フィレットリング８の着脱容易性が求められており、フィレットリング８にシール９を備えない構造なども増えてきている。そのため、フィレットリング８の内周面を通過して複列内輪４の内周面（ロールネック部７との嵌め合い面）に浸入する圧延水量も増える傾向にあり、シール装置１６には、更に高い密封性能が求められるようになっている。   Further, as a design structure around the bearing in recent years, easy attachment / detachment of the fillet ring 8 is required, and a structure in which the seal 9 is not provided on the fillet ring 8 is increasing. Therefore, the amount of rolling water that passes through the inner peripheral surface of the fillet ring 8 and enters the inner peripheral surface of the double-row inner ring 4 (the fitting surface with the roll neck portion 7) also tends to increase. High sealing performance is required.

このような密封型ロールネック軸受のシール装置としては、種々の構造が提案されている（例えば、特許文献１〜３参照。）   Various structures have been proposed as sealing devices for such sealed roll neck bearings (see, for example, Patent Documents 1 to 3).

特許文献１に記載の圧延機のロールネック用軸受のシール装置２０は、図１０に示すように、芯金２１と弾性シール部材２２とを備え、内輪２３、２４の環状段部に装着されている。弾性シール部材２２は、その内周面に設けられた２つの径方向突起（ラジアルリップ部）２６、２７と、両側面に設けられた２つの軸方向突起２８、２９とを有する。径方向突起２６、２７は、内輪２３、２４の小径端部外周面２３ａ、２４ａと摺接し、軸方向突起２８、２９は、内輪２３、２４の大径部端面２３ｂ、２４ｂと摺接して、内輪２３、２４の突き合わせ面２５から浸入する水や異物をシールする。   As shown in FIG. 10, a sealing device 20 for a roll neck bearing of a rolling mill described in Patent Document 1 includes a cored bar 21 and an elastic sealing member 22, and is attached to annular stepped portions of inner rings 23 and 24. Yes. The elastic seal member 22 has two radial projections (radial lip portions) 26 and 27 provided on the inner peripheral surface thereof, and two axial projections 28 and 29 provided on both side surfaces. The radial protrusions 26 and 27 are in sliding contact with the small-diameter end outer peripheral surfaces 23a and 24a of the inner rings 23 and 24, and the axial protrusions 28 and 29 are in sliding contact with the large-diameter end surfaces 23b and 24b of the inner rings 23 and 24, Water and foreign matter entering from the butted surfaces 25 of the inner rings 23 and 24 are sealed.

特許文献２に記載の密封四列円錐ころ軸受のシール装置３０は、図１１に示すように、互いに軸方向で向かい合う一対の内輪３１、３２の突き合せ部の周囲に配置されている。シール装置３０では、合成樹脂製の環状のシール部材３３の外周側に芯金３５が一体に設けられ、内周側に一対の環状リブ（ラジアルリップ部）３４が形成されている。環状リブ３４は、内輪３１、３２の延長部の外周面３１ａ、３２ａに摺接して、内輪３１、３２の接合部をシールする。
特開２００２−１７８０１３号公報 特開平６−１７８２４号公報 特開昭５５−４７０１７号公報 As shown in FIG. 11, the sealing device 30 of the sealed four-row tapered roller bearing described in Patent Document 2 is disposed around the butted portion of a pair of inner rings 31 and 32 that face each other in the axial direction. In the sealing device 30, a cored bar 35 is integrally provided on the outer peripheral side of an annular sealing member 33 made of synthetic resin, and a pair of annular ribs (radial lip portions) 34 are formed on the inner peripheral side. The annular rib 34 is in sliding contact with the outer peripheral surfaces 31 a and 32 a of the extension portions of the inner rings 31 and 32 to seal the joint portion of the inner rings 31 and 32.
JP 2002-178013 A JP-A-6-17824 JP 55-47017 A

ところで、図１０、図１１に示すシール装置２０，３０は、金属製の芯金２１，３５と一体成型された弾性シール部材のラジアルリップ部２６，２７，３４を、内輪２３，２４，３１，３２の外周面に摺接させてシールする構造を有しており、シール装置２０，３０に内輪２３，２４，３１，３２を挿入する作業の際、多少の心ズレが生じても、シール内径のリップに沿って内輪２３，２４，３１，３２が挿入されるため、組立性が比較的よい特徴を有する。その一方、ラジアルリップ部２６，２７，３４のみで内輪端部の突合せ部外周面に取付くため、シール装置２０，３０の取付け剛性が低い問題がある。このため、特に圧延機の圧延速度が１８００ｍｐｍを越えるような高速で圧延される場合、内輪２３，２４，３１，３２と共回り（シール嵌合面は殆ど摺動しない）するシール装置２０，３０に遠心力や振動が作用すると、ラジアルリップ部２６，２７，３４の挙動が生じて、ラジアルリップ部２６，２７，３４と内輪外周面との接触状態が不安定となり、シール性能が低下するという問題がある。   By the way, the sealing devices 20 and 30 shown in FIG. 10 and FIG. 11 include radial lip portions 26, 27, and 34 of an elastic seal member integrally molded with metal cores 21 and 35, and inner rings 23, 24, 31, 32 has a structure that is slidably brought into contact with the outer peripheral surface of the seal 32, and even when a slight misalignment occurs during the work of inserting the inner rings 23, 24, 31, 32 into the seal devices 20, 30, the inner diameter of the seal Since the inner rings 23, 24, 31, and 32 are inserted along the lip, the assemblability is relatively good. On the other hand, since only the radial lip portions 26, 27, 34 are attached to the outer peripheral surface of the abutting portion of the inner ring end portion, there is a problem that the mounting rigidity of the seal devices 20, 30 is low. For this reason, particularly when the rolling mill is rolled at a high speed exceeding 1800 mpm, the sealing devices 20 and 30 that rotate together with the inner rings 23, 24, 31, and 32 (the seal fitting surfaces hardly slide). If centrifugal force or vibration acts on the lip, the behavior of the radial lip portions 26, 27, 34 occurs, the contact state between the radial lip portions 26, 27, 34 and the outer peripheral surface of the inner ring becomes unstable, and the sealing performance decreases. There's a problem.

本発明は、前述した課題に鑑みてなされたものであり、その目的は、取付け剛性が高く、ロールネック部に対する組付け性に優れ、且つ高いシール性能を有する密封型ロールネック軸受を提供することにある。   The present invention has been made in view of the above-mentioned problems, and an object thereof is to provide a hermetic roll neck bearing having high mounting rigidity, excellent assemblability to a roll neck portion, and high sealing performance. It is in.

本発明の上記目的は、下記の構成により達成される。
（１）複数の外輪と、
複数の内輪と、
該外輪と該内輪との間に配置される複数のころと、
互いに突き合うように配置される前記内輪の両端部の周囲に配置されて、芯金及び弾性シール部材を有するシール装置と、
を備える密封型ロールネック軸受であって、
前記弾性シール部材の内周面は、前記両端部の一方の外周面と嵌合する嵌合部と、前記両端部の他方の外周面と摺接するラジアルリップ部を有し、
前記芯金は、前記弾性シール部材の外周側で、前記嵌合部の径方向外方を少なくとも覆うことを特徴とする密封型ロールネック軸受。
（２） 前記ラジアルリップ部の内径は、前記嵌合部の内径より小さいことを特徴とする（１）に記載の密封型ロールネック軸受。
（３） 前記嵌合部は、略一様な内径を持った平坦状に形成され、
前記芯金の一端は、軸方向において、前記両端部の突き合せ面と前記ラジアルリップ部との間に位置することを特徴とする（１）又は（２）に記載の密封型ロールネック軸受。
（４） 前記嵌合部は、軸方向において略対称な曲面状に形成され、
前記芯金の一端は、軸方向において、前記両端部の突き合せ面と前記ラジアルリップ部との間に位置することを特徴とする（１）又は（２）に記載の密封型ロールネック軸受。
（５） 前記嵌合部は、前記ラジアルリップ部と反対側に拡径するテーパ形状に形成され、
前記芯金の一端は、軸方向において、前記ラジアルリップ部を越えて延出することを特徴とする（１）又は（２）に記載の密封型ロールネック軸受。 The above object of the present invention is achieved by the following configurations.
(1) a plurality of outer rings;
Multiple inner rings,
A plurality of rollers disposed between the outer ring and the inner ring;
A sealing device disposed around both ends of the inner ring disposed so as to face each other, and having a metal core and an elastic seal member;
A sealed roll neck bearing comprising:
The inner peripheral surface of the elastic seal member has a fitting portion that fits with one outer peripheral surface of the both end portions, and a radial lip portion that makes sliding contact with the other outer peripheral surface of the both end portions,
The cored bar covers at least the outer side in the radial direction of the fitting portion on the outer peripheral side of the elastic seal member.
(2) The sealed roll neck bearing according to (1), wherein an inner diameter of the radial lip portion is smaller than an inner diameter of the fitting portion.
(3) The fitting portion is formed in a flat shape having a substantially uniform inner diameter,
One end of the metal core is located between the butted surfaces of the both end portions and the radial lip portion in the axial direction, and the sealed roll neck bearing according to (1) or (2).
(4) The fitting portion is formed in a substantially symmetrical curved surface shape in the axial direction,
One end of the metal core is located between the butted surfaces of the both end portions and the radial lip portion in the axial direction, and the sealed roll neck bearing according to (1) or (2).
(5) The fitting portion is formed in a tapered shape whose diameter is expanded on the opposite side to the radial lip portion,
One end of the cored bar extends in the axial direction beyond the radial lip, and the sealed roll neck bearing according to (1) or (2).

本発明の密封型ロールネック軸受によれば、突き合わせ配置される内輪の両端部に配置されるシール装置は、内周面に嵌合部及びラジアルリップ部を備える弾性シール部材と、弾性シール部材の外周側で、嵌合部の径方向外方を少なくとも覆う芯金とを有する。そして、嵌合部を一方の内輪外周面に嵌合させることによって、シール装置に高い取付け剛性を持たせて耐久性を向上させる。また、ラジアルリップ部を他方の内輪外周面に摺接させることにより、両内輪の偏芯に追従させて、高速回転時にシール装置に遠心力や振動が作用しても高いシール性能を維持することができる。   According to the sealed roll neck bearing of the present invention, the sealing device disposed at both ends of the inner ring to be butt-arranged includes an elastic seal member having a fitting portion and a radial lip portion on the inner peripheral surface, and an elastic seal member On the outer peripheral side, it has a metal core that covers at least the radially outer side of the fitting portion. Then, by fitting the fitting portion to the outer peripheral surface of one of the inner rings, the seal device has high attachment rigidity and improves durability. In addition, by sliding the radial lip part on the outer peripheral surface of the other inner ring, it can follow the eccentricity of both inner rings and maintain high sealing performance even if centrifugal force or vibration acts on the sealing device during high-speed rotation. Can do.

以下、本発明に係る密封型ロールネック軸受の各実施形態を図面に基づいて詳細に説明する。   Embodiments of a sealed roll neck bearing according to the present invention will be described below in detail with reference to the drawings.

（第１実施形態）
図１は本発明の第１実施形態の密封型ロールネック軸受の要部縦断面図、図２（ａ）は図１における円IIで囲まれた部分の拡大図、図２（ｂ）は、シール装置単品の要部断面図、図３は図２に示すシール装置が取り付けられた状態の断面図である。 (First embodiment)
1 is a longitudinal sectional view of a main part of a sealed roll neck bearing according to a first embodiment of the present invention, FIG. 2A is an enlarged view of a portion surrounded by a circle II in FIG. 1, and FIG. FIG. 3 is a cross-sectional view of a main part of a single seal device, and FIG. 3 is a cross-sectional view of the seal device shown in FIG.

図１に示すように、第１実施形態の密封型ロールネック軸受（密封型４列円錐ころ軸受）４０は、一対の外輪４１及び複列外輪４２と、一対の複列内輪４３，４４と、外輪４１と複列内輪４３，４４、及び複列外輪４２と複列内輪４３，４４間に４列に配設され、保持器４６によって回動自在に保持された複数の円錐ころ４５とを備える。   As shown in FIG. 1, the sealed roll neck bearing (sealed four-row tapered roller bearing) 40 of the first embodiment includes a pair of outer rings 41 and a double-row outer ring 42, a pair of double-row inner rings 43 and 44, An outer ring 41 and double row inner rings 43 and 44, and a plurality of tapered rollers 45 disposed in four rows between the double row outer ring 42 and double row inner rings 43 and 44 and rotatably held by a cage 46 are provided. .

軸方向中央に配置された複列外輪４２と、その軸方向両側に配置された外輪４１との間には、外輪間座４７がそれぞれ配置されて一対の外輪４１及び複列外輪４２の軸方向の位置決めがなされる。また、外輪４１の軸方向外側には、オイルシール４９を内蔵する円環状のシールホルダー４８が配置され、複列内輪４３，４４から軸方向外方に延設された小径部４３ａ，４４ａの外周面との間をオイルシール４９によってシールしている。また、シールホルダー４８の外周面には、Ｏリング５０が装着されて、図示しないチョックとの間を封止する（図９参照）。   Between the double row outer ring 42 arranged in the center in the axial direction and the outer ring 41 arranged on both sides in the axial direction, outer ring spacers 47 are arranged respectively, and the axial direction of the pair of outer rings 41 and the double row outer ring 42 Is positioned. Further, an annular seal holder 48 containing an oil seal 49 is disposed outside the outer ring 41 in the axial direction, and the outer circumferences of the small-diameter portions 43a and 44a extending axially outward from the double-row inner rings 43 and 44. A gap between the surfaces is sealed by an oil seal 49. Further, an O-ring 50 is attached to the outer peripheral surface of the seal holder 48 to seal a gap with a chock (not shown) (see FIG. 9).

図２も参照して、互いに突き合うように配置される一対の複列内輪４３，４４の両端部である肩部は、それぞれ段付形状に形成されており、軸方向内方に延設された小径端部４３ｂ，４４ｂの突き合せ面４３ｃ，４４ｃ同士が互いに突き合うように配置されている。小径端部４３ｂ，４４ｂの外周面側には、シール装置５１が配設されている。シール装置５１は、例えば、金属によってリング状に成形され、断面略Ｌ字状に折り曲げ形成された芯金５２と、該芯金５２に一体に成形された円環状の弾性シール部材５３とを有する。弾性シール部材５３の材料としては、特に限定されないが、弾性の大きなゴム系材料、例えばニトリル系ゴム、アクリル系ゴム、フッ素系ゴム等が使用される。   Referring also to FIG. 2, shoulder portions that are both ends of the pair of double-row inner rings 43 and 44 disposed so as to face each other are formed in a stepped shape and extend inward in the axial direction. Further, the abutting surfaces 43c and 44c of the small diameter end portions 43b and 44b are arranged so as to abut each other. A sealing device 51 is disposed on the outer peripheral surface side of the small diameter end portions 43b and 44b. The sealing device 51 includes, for example, a metal core 52 formed in a ring shape with metal and bent to have a substantially L-shaped cross section, and an annular elastic seal member 53 formed integrally with the metal core 52. . The material of the elastic seal member 53 is not particularly limited, but a rubber material having high elasticity, for example, nitrile rubber, acrylic rubber, fluorine rubber, or the like is used.

弾性シール部材５３の内周面には、略一様な内径を持った平坦状に形成された嵌合部５４と、径方向内方に突出して形成されたラジアルリップ部５５とが、軸方向に並んで形成されている。ラジアルリップ部５５の内径Ｄ２は、嵌合部５４の内径Ｄ１より僅かに小さくなっている（Ｄ２＜Ｄ１）。   On the inner peripheral surface of the elastic seal member 53, a fitting portion 54 formed in a flat shape having a substantially uniform inner diameter, and a radial lip portion 55 formed so as to protrude radially inward are provided in the axial direction. Are formed side by side. The inner diameter D2 of the radial lip portion 55 is slightly smaller than the inner diameter D1 of the fitting portion 54 (D2 <D1).

シール装置５１は、嵌合部５４が一方の複列内輪４３（図２においては左側の複列内輪）の小径端部４３ｂの外周面４３ｄに嵌合し、ラジアルリップ部５５が他方の複列内輪４４（図２においては右側の複列内輪）の小径端部４４ｂの外周面４４ｄに締め代を持って嵌合する。ラジアルリップ部５５は、一定の締め代を持って他方の複列内輪４４の小径端部４４ｂの外周面４４ｄに摺接する。   In the sealing device 51, the fitting portion 54 is fitted to the outer peripheral surface 43d of the small diameter end portion 43b of one double row inner ring 43 (the left side double row inner ring in FIG. 2), and the radial lip portion 55 is the other double row. The inner ring 44 (the double row inner ring on the right side in FIG. 2) is fitted to the outer peripheral surface 44d of the small-diameter end portion 44b with a tightening margin. The radial lip portion 55 is in sliding contact with the outer peripheral surface 44d of the small diameter end portion 44b of the other double-row inner ring 44 with a certain tightening allowance.

芯金５２は、弾性シール部材５３の外周側に設けられ、径方向内向きフランジ部５２ａの外周側から軸方向に延び、その一端（図中右端部）５２ｂは、軸方向において小径端部４３ｂ，４４ｂの突き合せ面４３ｃ，４４ｃとラジアルリップ部５５との間に位置する。即ち、芯金５２は、嵌合部５４の径方向外方を覆うように形成され、ラジアルリップ部５５の径方向外方には設けられていない。   The core metal 52 is provided on the outer peripheral side of the elastic seal member 53, extends in the axial direction from the outer peripheral side of the radially inward flange portion 52a, and one end (right end portion in the figure) 52b has a small diameter end portion 43b in the axial direction. , 44b and the radial lip portion 55 are located between the butted surfaces 43c, 44c. That is, the cored bar 52 is formed so as to cover the outer side in the radial direction of the fitting part 54, and is not provided on the outer side in the radial direction of the radial lip part 55.

このようなシール装置５１の軸受への組付けは、先ず、装着用治具（例えば、当て木、円環リング等）を用いて軟質のハンマー等で叩いてシール装置５１の嵌合部５４を一方の複列内輪４３の小径端部４３ｂの外周面４３ｄに圧入する。略一様な内径を持って平坦状に形成された嵌合部５４が外周面４３ｄに圧入されることによって、シール装置５１は取付け剛性が高い状態で取り付けられる。次いで、ラジアルリップ部５５に他方の複列内輪４４の小径端部４４ｂの外周面４４ｄを嵌合させる。この嵌合に要する力は、複列内輪４４の自重程度の弱い力で嵌合可能である。   The assembly of the seal device 51 to the bearing is performed by first hitting the fitting portion 54 of the seal device 51 with a soft hammer or the like using a mounting jig (for example, a batten, a ring or the like). One double-row inner ring 43 is press-fitted into the outer peripheral surface 43d of the small-diameter end portion 43b. By fitting the fitting portion 54 having a substantially uniform inner diameter into a flat shape into the outer peripheral surface 43d, the sealing device 51 is attached with high attachment rigidity. Next, the outer peripheral surface 44 d of the small diameter end portion 44 b of the other double-row inner ring 44 is fitted to the radial lip portion 55. The force required for this fitting can be fitted with a weak force about the weight of the double row inner ring 44.

また、ラジアルリップ部５５は、適度の締め代を持って小径端部４４ｂの外周面４４ｄに嵌合するので、両複列内輪４３，４４の外周面４３ｄ、４４ｄが多少偏芯していても、これに容易に追従することができ、シール性能が良好に維持される。またこの時、ラジアルリップ部５５は締め代を持って嵌合するため、弾性を有するラジアルリップ部５５が弾性変形する。   Further, since the radial lip portion 55 is fitted to the outer peripheral surface 44d of the small-diameter end portion 44b with an appropriate tightening margin, the outer peripheral surfaces 43d and 44d of the double-row inner rings 43 and 44 are slightly eccentric. This can be followed easily, and the sealing performance is maintained well. At this time, since the radial lip portion 55 is fitted with a tightening margin, the elastic radial lip portion 55 is elastically deformed.

従って、図３（ｂ）に示すように、芯金５２が嵌合部５４及びラジアルリップ部５５の全長に亘って径方向外方を覆うように形成されていると、芯金５２や弾性シール部材５３の構成、ラジアルリップ部５５の締め代の大きさ等によっては、ラジアルリップ部５５の弾性変形によってシール装置５１全体が図中破線で示すように変形した取付け状態となり、嵌合部５４での取付け剛性が若干低下する可能性がある。一方、本実施形態のシール装置５１は、芯金５２がラジアルリップ部５５の径方向外方には設けられていないので、図３（ａ）に破線で示すように、ラジアルリップ部５５近傍のみが局部的に弾性変形（膨らむ）し、嵌合部５４での取付け剛性に影響を及ぼすことが防止される。   Therefore, as shown in FIG. 3B, when the cored bar 52 is formed so as to cover the radially outer side over the entire length of the fitting part 54 and the radial lip part 55, the cored bar 52 and the elastic seal are formed. Depending on the structure of the member 53, the size of the fastening margin of the radial lip portion 55, etc., the entire sealing device 51 is deformed as shown by the broken line in FIG. There is a possibility that the mounting rigidity of the lens slightly decreases. On the other hand, in the sealing device 51 of the present embodiment, since the cored bar 52 is not provided radially outward of the radial lip portion 55, only the vicinity of the radial lip portion 55 is shown as indicated by a broken line in FIG. Is locally elastically deformed (swells), and the mounting rigidity at the fitting portion 54 is prevented from being affected.

以上説明したように、本実施形態の密封型ロールネック軸受４０によれば、シール装置５１は、嵌合部５４が一方の複列内輪４３の外周面４３ｄに圧入されて取り付けられるので、シール装置５１が高い取付け剛性を有する。また、他方の複列内輪４４の外周面４４ｄには、締め代を有するラジアルリップ部５５が嵌合するので、両外周面４３ｄ、４４ｄが多少偏芯していても、これに追従することができ、高いシール性能が確保される。さらに、シール装置５１を複列内輪４４に挿入する際の作業性も良好となる。   As described above, according to the sealed-type roll neck bearing 40 of the present embodiment, the sealing device 51 is attached by fitting the fitting portion 54 into the outer peripheral surface 43d of the one double-row inner ring 43. 51 has a high mounting rigidity. Further, since the radial lip portion 55 having a tightening margin is fitted to the outer peripheral surface 44d of the other double-row inner ring 44, even if both the outer peripheral surfaces 43d and 44d are slightly eccentric, they can follow this. And high sealing performance is ensured. Furthermore, workability when inserting the sealing device 51 into the double-row inner ring 44 is also improved.

また、ラジアルリップ部５５の内径Ｄ２が、嵌合部５４の内径Ｄ１より小さいので、ラジアルリップ部５５が複列内輪４４の外周面４４ｄに大きな締め代を持って嵌合し、両複列内輪４３，４４の偏芯に対してラジアルリップ部５５を追従させて、より高いシール性能が得られる。   Further, since the inner diameter D2 of the radial lip portion 55 is smaller than the inner diameter D1 of the fitting portion 54, the radial lip portion 55 is fitted to the outer peripheral surface 44d of the double row inner ring 44 with a large tightening margin, and both double row inner rings are fitted. By causing the radial lip portion 55 to follow the eccentricity of 43 and 44, higher sealing performance can be obtained.

さらに、嵌合部５４が、略一様な内径を持った平坦状に形成され、芯金５２の一端５２ｂは、軸方向において、小径端部４３ｂ，４４ｂの突き合せ面４３ｃ、４４ｃとラジアルリップ部５５との間に位置するようにしたので、複列内輪４４の外周面４４ｄとラジアルリップ部５５との嵌合によって生じるラジアルリップ部５５の弾性変形が、嵌合部５４の取付け剛性に影響を及ぼすことが抑制され、嵌合部５４での複列内輪４３との確実な嵌合によってシール装置５１は高い取付け剛性を確保することができる。   Further, the fitting portion 54 is formed in a flat shape having a substantially uniform inner diameter, and one end 52b of the cored bar 52 is in the axial direction with the butted surfaces 43c and 44c of the small diameter end portions 43b and 44b and a radial lip. The elastic deformation of the radial lip portion 55 caused by the fitting between the outer peripheral surface 44d of the double-row inner ring 44 and the radial lip portion 55 affects the mounting rigidity of the fitting portion 54. The sealing device 51 can ensure high mounting rigidity by the reliable fitting with the double row inner ring 43 at the fitting portion 54.

（第２実施形態）
次に、第２実施形態の密封型ロールネック軸受に装着されるシール装置について図４を参照して説明する。図４は本発明の第２実施形態であるシール装置が装着された密封型ロールネック軸受の要部拡大断面図である。尚、本実施形態は、シール装置の嵌合部の形状が第１実施形態と異なるのみで、それ以外の構成は、第１実施形態のものと同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 (Second Embodiment)
Next, a sealing device mounted on the sealed roll neck bearing of the second embodiment will be described with reference to FIG. FIG. 4 is an enlarged cross-sectional view of a main part of a hermetic roll neck bearing equipped with a sealing device according to a second embodiment of the present invention. In this embodiment, only the shape of the fitting portion of the sealing device is different from that of the first embodiment, and other configurations are the same as those of the first embodiment. The description will be simplified or omitted with corresponding reference numerals.

第２実施形態のシール装置５１の弾性シール部材５３は、内方に突出する、軸方向において略対称な曲面状に形成された嵌合部５４と、径方向内方に突出して形成されたラジアルリップ部５５とが、軸方向に並んで形成されており、嵌合部５４が一方の複列内輪４３の小径端部４３ｂの外周面４３ｄに嵌合し、ラジアルリップ部５５が他方の複列内輪４４の小径端部４４ｂの外周面４４ｄに一定の締め代を持って摺接する。   The elastic sealing member 53 of the sealing device 51 according to the second embodiment includes a fitting portion 54 that protrudes inward and is formed in a curved surface that is substantially symmetrical in the axial direction, and a radial that protrudes inward in the radial direction. The lip portion 55 is formed side by side in the axial direction, the fitting portion 54 is fitted to the outer peripheral surface 43d of the small diameter end portion 43b of one double row inner ring 43, and the radial lip portion 55 is the other double row. The inner ring 44 is in sliding contact with the outer peripheral surface 44d of the small-diameter end 44b with a certain margin.

芯金５２の一端５２ｂは、軸方向において、小径端部４３ｂ，４４ｂの突き合せ面４３ｃ，４４ｃとラジアルリップ部５５との間に位置する。即ち、芯金５２は、嵌合部５４の径方向外方のみを覆うように形成され、ラジアルリップ部５５の径方向外方には設けられていない。このように、嵌合部５４の断面形状を緩やかなＲ形状とすることにより、外周面４３ｄとの嵌合面積を大きくして高い取付け剛性を確保すると共に、外周面４３ｄの挿入を容易にして組付け性の向上が図られている。   One end 52b of the cored bar 52 is located between the butting surfaces 43c and 44c of the small diameter end portions 43b and 44b and the radial lip portion 55 in the axial direction. That is, the cored bar 52 is formed so as to cover only the radially outer side of the fitting part 54, and is not provided on the radially outer side of the radial lip part 55. Thus, by making the cross-sectional shape of the fitting portion 54 a gentle R shape, the fitting area with the outer peripheral surface 43d is increased to ensure high attachment rigidity and the insertion of the outer peripheral surface 43d is facilitated. The assembly is improved.

従って、本実施形態の密封型ロールネック軸受４０では、嵌合部５４は、軸方向において略対称な曲面状に形成され、芯金５２の一端は、軸方向において、小径端部４３ｂ，４４ｂの突き合せ面４３ｃ，４４ｃとラジアルリップ部５５との間に位置するようにしたので、複列内輪４４の外周面４４ｄとラジアルリップ部５５との嵌合によって生じるラジアルリップ部５５の弾性変形が、嵌合部５４の取付け剛性に影響を及ぼすことが抑制でき、嵌合部５４での複列内輪４３との確実な嵌合によってシール装置の高い取付け剛性を確保することができる。
その他の構成及び効果は、第１実施形態の密封型ロールネック軸受４０と同様であるので説明を省略する。 Accordingly, in the sealed roll neck bearing 40 of the present embodiment, the fitting portion 54 is formed in a curved surface that is substantially symmetrical in the axial direction, and one end of the cored bar 52 is formed by the small diameter end portions 43b and 44b in the axial direction. Since it is located between the abutting surfaces 43c, 44c and the radial lip portion 55, the elastic deformation of the radial lip portion 55 caused by the fitting between the outer peripheral surface 44d of the double row inner ring 44 and the radial lip portion 55 is as follows. The influence on the mounting rigidity of the fitting portion 54 can be suppressed, and the high fitting rigidity of the sealing device can be ensured by the reliable fitting with the double-row inner ring 43 at the fitting portion 54.
Other configurations and effects are the same as those of the sealed roll neck bearing 40 according to the first embodiment, and a description thereof will be omitted.

（第３実施形態）
次に、第３実施形態の密封型ロールネック軸受に装着されるシール装置について図５を参照して説明する。図５は本発明の第３実施形態であるシール装置が装着された密封型ロールネック軸受の要部拡大断面図である。尚、本実施形態は、シール装置の嵌合部の形状が第１実施形態と異なるのみで、それ以外の構成は、第１実施形態のものと同様であるので、同一部分には同一符号又は相当符号を付して説明を簡略化又は省略する。 (Third embodiment)
Next, a sealing device mounted on the hermetic roll neck bearing of the third embodiment will be described with reference to FIG. FIG. 5 is an enlarged cross-sectional view of a main part of a hermetic roll neck bearing equipped with a sealing device according to a third embodiment of the present invention. In this embodiment, only the shape of the fitting portion of the sealing device is different from that of the first embodiment, and other configurations are the same as those of the first embodiment. The description will be simplified or omitted with corresponding reference numerals.

第３実施形態のシール装置５１の弾性シール部材５３は、図５に示すように、その内周面にテーパ形状の嵌合部５４と、径方向内方に突出して形成されたラジアルリップ部５５とを備える。嵌合部５４は、ラジアルリップ部５５と反対側に拡径し、角度θのテーパ形状に形成されている。また、芯金５２は、径方向内向きフランジ部５２ａから軸方向に延び、その一端５２ｂは軸方向においてラジアルリップ部５５を越えて延出して形成されている。即ち、芯金５２は、嵌合部５４及びラジアルリップ部５５に亘って、径方向外方を覆うように形成されている。   As shown in FIG. 5, the elastic sealing member 53 of the sealing device 51 of the third embodiment has a tapered fitting portion 54 on its inner peripheral surface and a radial lip portion 55 that protrudes radially inward. With. The fitting portion 54 has an enlarged diameter on the opposite side to the radial lip portion 55 and is formed in a tapered shape having an angle θ. Further, the cored bar 52 extends in the axial direction from the radially inward flange portion 52a, and one end 52b is formed to extend beyond the radial lip portion 55 in the axial direction. That is, the cored bar 52 is formed so as to cover the outer side in the radial direction across the fitting part 54 and the radial lip part 55.

このようなシール装置５１は、テーパ形状の嵌合部５４が一方の複列内輪４３の外周面４３ｄに嵌合し、ラジアルリップ部５５が他方の複列内輪４４の外周面４４ｄに締め代を持って挿入される。このとき、他方の複列内輪４４の外周面４４ｄと嵌合するラジアルリップ部５５の弾性変形によって、図５（ｂ）に破線で示すように、シール装置５１の取付状態が変化して、テーパ形状の嵌合部５４の略全面が一方の複列内輪４３Ａの外周面４３ｄに接触する。これにより、嵌合部５４が広い面積で外周面４３ｄと嵌合するので、シール装置５１は取付け剛性が高められた状態で取り付けられる。また、嵌合部５４がテーパ形状に形成されているので、複列内輪４３と容易に嵌合させることができ、組付け性能により優れたものとなる。   In such a sealing device 51, the tapered fitting portion 54 is fitted to the outer peripheral surface 43d of one double row inner ring 43, and the radial lip portion 55 is tightened to the outer peripheral surface 44d of the other double row inner ring 44. To be inserted. At this time, due to the elastic deformation of the radial lip portion 55 fitted to the outer peripheral surface 44d of the other double-row inner ring 44, the mounting state of the seal device 51 changes as shown by the broken line in FIG. The substantially entire surface of the fitting portion 54 having a shape comes into contact with the outer peripheral surface 43d of one double row inner ring 43A. Thereby, since the fitting part 54 fits with the outer peripheral surface 43d in a wide area, the sealing device 51 is attached in a state where the attachment rigidity is increased. Moreover, since the fitting part 54 is formed in the taper shape, it can be easily fitted with the double-row inner ring 43, and the assembling performance is excellent.

従って、本実施形態の密封型ロールネック軸受４０では、嵌合部５４は、ラジアルリップ部５５と反対側に拡径するテーパ形状に形成され、芯金５２の一端５２ｂは、軸方向において、ラジアルリップ部５５を越えて延出するようにしたので、ラジアルリップ部５５を複列内輪４４の外周面４４ｄに嵌合させたときのラジアルリップ部５５の弾性変形の力により、シール装置５１の取付け状態を変化させてテーパ状の嵌合部５４の略全面を内輪外周面４３ｄに接触させ、これによりシール装置５１に高い取付け剛性を付与することができる。また、嵌合部５４を複列内輪４３に容易に嵌合させることができるので、組付け性能のより優れたものとなる。
その他の作用及び効果は、第１実施形態の密封型ロールネック軸受４０と同様であるので説明を省略する。 Accordingly, in the sealed roll neck bearing 40 of the present embodiment, the fitting portion 54 is formed in a tapered shape that expands in the opposite direction to the radial lip portion 55, and one end 52b of the cored bar 52 is radially in the axial direction. Since the lip portion 55 is extended beyond the lip portion 55, the sealing device 51 is attached by the elastic deformation force of the radial lip portion 55 when the radial lip portion 55 is fitted to the outer peripheral surface 44d of the double row inner ring 44. By changing the state, the substantially entire surface of the tapered fitting portion 54 is brought into contact with the outer peripheral surface 43d of the inner ring, whereby high attachment rigidity can be imparted to the seal device 51. Moreover, since the fitting part 54 can be easily fitted to the double-row inner ring 43, the assembling performance is further improved.
Since other operations and effects are the same as those of the sealed roll neck bearing 40 of the first embodiment, description thereof is omitted.

尚、本発明は、前述した各実施形態及び実施例に限定されるものではなく、適宜、変形、改良、等が可能である。
例えば、本発明のシール装置は、互いに突き合わされる複数の内輪の両端部の周囲に配置されればよく、両端部である両方の肩部が段付形状を有しない構成であってもよい。また、本発明は、ころとして円筒ころを備えた密封形ロールネック軸受であってもよい。 In addition, this invention is not limited to each embodiment and Example mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
For example, the sealing device of the present invention may be arranged around both ends of a plurality of inner rings that are abutted against each other, and may have a configuration in which both shoulder portions that are both ends do not have a stepped shape. The present invention may also be a sealed roll neck bearing provided with cylindrical rollers as rollers.

本発明の効果を確認するため、図８（ａ）及び（ｂ）に示す本発明のシール装置と、図８（ｃ）に示す従来のシール装置とを用いて、シール性能について２つの試験を行った。   In order to confirm the effect of the present invention, two tests were conducted on the sealing performance using the sealing device of the present invention shown in FIGS. 8 (a) and 8 (b) and the conventional sealing device shown in FIG. 8 (c). went.

図６はシール装置のシール性能を試験するためのシール性能試験装置の概略構成図、図７は回転時におけるシール装置のラジアル振れ量試験装置の概略構成図、図８（ａ）〜（ｃ）は本シール性能試験に用いた各シール装置の断面図である。尚、図８（ａ）に示す実施例１のシール装置は、第１実施形態で説明したものと同一構成を有し、図８（ｂ）に示す実施例２のシール装置は、第２実施形態で説明したものと同一構成を有する。   6 is a schematic configuration diagram of a sealing performance test apparatus for testing the sealing performance of the sealing apparatus, FIG. 7 is a schematic configuration diagram of a radial runout test apparatus of the sealing apparatus during rotation, and FIGS. 8A to 8C. These are sectional views of each sealing device used in the present sealing performance test. The sealing device of Example 1 shown in FIG. 8A has the same configuration as that described in the first embodiment, and the sealing device of Example 2 shown in FIG. 8B is the second embodiment. It has the same configuration as that described in the form.

実施例及び比較例ともに、嵌合部５４及びラジアルリップ部５５が嵌合する複列内輪４３，４４の外周面４３ｄ，４４ｄの直径は３１０ｍｍである。図８（ａ）に示す実施例１、及び図８（ｂ）に示す実施例２の嵌合部５４の締め代は０．４ｍｍ、ラジアルリップ部５５の締め代は０．８ｍｍである。また、図８（ｃ）に示す比較例の嵌合部５４及びラジアルリップ部５５の締め代は、共に０．８ｍｍである。   In both the example and the comparative example, the outer peripheral surfaces 43d and 44d of the double-row inner rings 43 and 44 into which the fitting portion 54 and the radial lip portion 55 are fitted have a diameter of 310 mm. In Example 1 shown in FIG. 8A and Example 2 shown in FIG. 8B, the fastening margin of the fitting portion 54 is 0.4 mm, and the fastening margin of the radial lip portion 55 is 0.8 mm. Moreover, the fastening allowance of the fitting part 54 and the radial lip part 55 of the comparative example shown in FIG.8 (c) is both 0.8 mm.

先ず、図６に示すシール性能試験装置６０によるシール性能試験について説明する。シール性能試験装置６０では、支持軸受６１によって支持され、モータ６２によって回転駆動される回転軸６３の外周面に、密封型ロールネック軸受の一対の内輪を模した第１リング６４及び第２リング６５が、端面同士が突き合わされて嵌合している。第１リング６４と第２リング６５の互いに突き合わされる両端部６４ａ，６５ａの外周面には、試験対象物であるシール装置５１が装着される。また、第１リング６４及び第２リング６５とハウジング６６との間で、シール装置５１の両側には、一対のオイルシール６７が配置されている。供給源（ポンプ）６８から供給される所定量の水は、ロータリジョイントを介して回転軸６２の内部に設けられた水供給路６９を通過して、両端部６４ａ，６５ａの突き合せ面に向けて補給される。補給された水のうち、第１リング６３及び第２リング６４の内周面から逃がされた水は、容器７０によって回収され、シール装置５１を通過した水は、ハウジング６６の下方に設けられた容器７１によって回収される。   First, the seal performance test by the seal performance test apparatus 60 shown in FIG. 6 will be described. In the sealing performance test apparatus 60, a first ring 64 and a second ring 65 imitating a pair of inner rings of a hermetic roll neck bearing are provided on the outer peripheral surface of a rotating shaft 63 supported by a support bearing 61 and driven to rotate by a motor 62. However, the end faces are butted together. A seal device 51, which is a test object, is mounted on the outer peripheral surfaces of both end portions 64a and 65a of the first ring 64 and the second ring 65 that face each other. A pair of oil seals 67 are disposed on both sides of the seal device 51 between the first ring 64 and the second ring 65 and the housing 66. A predetermined amount of water supplied from a supply source (pump) 68 passes through a water supply passage 69 provided inside the rotary shaft 62 via a rotary joint, and is directed to the abutting surfaces of both end portions 64a and 65a. To be replenished. Of the replenished water, water that has escaped from the inner peripheral surfaces of the first ring 63 and the second ring 64 is collected by the container 70, and the water that has passed through the sealing device 51 is provided below the housing 66. Collected by the container 71.

本シール性能試験では、実施例及び比較例ともに、所定の回転数（７５０ｒｐｍ、１０００ｒｐｍ、１３００ｒｐｍ、１６００ｒｐｍの４条件）で第１リング６４及び第２リング６５を回転軸６３と共に回転させながら、供給源６８から両端部６４ａ，６５ａに５０ｃｃ/ｍｉｎの割合で水道水を間欠補給して５時間の試験を行った後、シール装置５１から漏れて容器７１に溜った水量を計測してシール性能の評価を行った。尚、試験はそれぞれ２回ずつ行い、その試験結果を表１に示す。   In this seal performance test, in both the example and the comparative example, while the first ring 64 and the second ring 65 are rotated together with the rotating shaft 63 at a predetermined rotation speed (four conditions of 750 rpm, 1000 rpm, 1300 rpm, and 1600 rpm), the supply source After the tap water is intermittently replenished at a rate of 50 cc / min from 68 to both ends 64a and 65a and the test is performed for 5 hours, the amount of water leaked from the sealing device 51 and accumulated in the container 71 is measured to evaluate the sealing performance. Went. Each test was conducted twice, and the test results are shown in Table 1.

Figure 2009156421
Figure 2009156421

表１から分かるように、比較例のシール装置においては、略１３００ｒｐｍ付近に変極点が見られ、それ以上の高速域で漏れ量が増大している。これに対して、本発明のシール装置（実施例１、２）５１は、いずれも低速域から高速域までの全領域に亘って水漏れ量が少なく、優れたシール性能を有することが分かる。   As can be seen from Table 1, in the sealing device of the comparative example, an inflection point is observed in the vicinity of approximately 1300 rpm, and the amount of leakage increases at a higher speed range than that. On the other hand, it can be seen that the sealing device (Examples 1 and 2) 51 of the present invention has an excellent sealing performance with a small amount of water leakage over the entire region from the low speed region to the high speed region.

次に、上記の結果を検証するため、図７に示すラジアル振れ量試験装置８０により、シール装置の回転速度とラジアル方向振れとの相関関係を測定した。ラジアル振れ量試験装置８０は、所定の回転数で回転する第１リング６４と第２リング６５の両端部６４ａ，６５ａの外周面に装着されたシール装置５１の芯金５２の外周側に、φ５ｍの渦電流センサ８１を取付け、回転時における芯金５２のラジアル方向振れ量を測定した。試験結果を表２に示す。   Next, in order to verify the above results, a correlation between the rotational speed of the sealing device and radial runout was measured using a radial runout test device 80 shown in FIG. The radial run-out test device 80 has a diameter of 5 m on the outer peripheral side of the cored bar 52 of the sealing device 51 mounted on the outer peripheral surfaces of both ends 64a and 65a of the first ring 64 and the second ring 65 rotating at a predetermined rotational speed. The eddy current sensor 81 was attached, and the radial deflection of the cored bar 52 during rotation was measured. The test results are shown in Table 2.

Figure 2009156421
Figure 2009156421

表２から分かるように、実施例、比較例共に低速域での振れは、芯金５２の真円度（精度）に起因するものであり、回転に伴う振れの変化は、１３００ｒｐｍ以上の高速域において見られる。特に、比較例のシール装置の振れは、１３００ｒｐｍ以上の回転数で増加する傾向があるのに対して、実施例１，２のシール装置５１の振れの増大は少なく、シール性能試験装置６０によるシール性能試験結果とよく一致することが確認された。   As can be seen from Table 2, the run-out in the low speed range is caused by the roundness (accuracy) of the cored bar 52 in both the example and the comparative example, and the change in run-out due to the rotation is in the high speed range of 1300 rpm or more. Seen in In particular, the vibration of the sealing device of the comparative example tends to increase at a rotation speed of 1300 rpm or more, while the increase of the vibration of the sealing device 51 of the first and second embodiments is small, and the sealing by the sealing performance test device 60 It was confirmed that the results agree well with the performance test results.

比較例と実施例の試験結果に差が生じた原因は、比較例のシール装置は、２点のラジアルリップ部のみで第１リング６４と第２リング６５に支持されているので取付け剛性が不足し、高速域での遠心力の作用によってシール装置の振れ廻りが生じてシール性能が低下したものと考えられる。   The reason for the difference between the test results of the comparative example and the example is that the sealing device of the comparative example is supported by the first ring 64 and the second ring 65 with only two radial lip portions, so that the mounting rigidity is insufficient. However, it is considered that the sealing performance is lowered due to the swinging of the sealing device due to the centrifugal force in the high speed range.

以上の試験結果から、本発明の密封型ロールネック軸受は、高速回転においても、内輪への取付け剛性が高められ、互いに突き合わされる内輪間で生じる偏芯にも追従して、高いシール性を確保できることが確認された。また、これによって、過酷な条件で使用される圧延装置のロールネック軸受として、長期間に亘って安定した性能を維持することができる。   From the above test results, the sealed-type roll neck bearing of the present invention has a high sealing performance with improved rigidity to be attached to the inner ring even at high speed rotation, following the eccentricity generated between the inner rings abutted against each other. It was confirmed that it could be secured. In addition, this makes it possible to maintain stable performance over a long period of time as a roll neck bearing of a rolling device used under severe conditions.

本発明の第１実施形態の密封型ロールネック軸受の要部縦断面図である。It is a principal part longitudinal cross-sectional view of the sealed roll neck bearing of 1st Embodiment of this invention. 図１における円Ａで囲まれた部分の拡大図（ａ）、及びシール装置の要部断面図（ｂ）である。It is the enlarged view (a) of the part enclosed by the circle A in FIG. 1, and the principal part sectional drawing (b) of a sealing device. 図２に示すシール装置が取り付けられた状態の断面図である。It is sectional drawing of the state in which the sealing apparatus shown in FIG. 2 was attached. 本発明の第２実施形態であるシール装置が装着された密封型ロールネック軸受の要部拡大断面図である。It is a principal part expanded sectional view of the sealing-type roll neck bearing with which the sealing device which is 2nd Embodiment of this invention was mounted | worn. 本発明の第３実施形態であるシール装置が装着された密封型ロールネック軸受の要部拡大断面図である。It is a principal part expanded sectional view of the seal-type roll neck bearing with which the sealing device which is 3rd Embodiment of this invention was mounted | worn. シール装置のシール性能を試験するシール性能試験装置の概略構成図である。It is a schematic block diagram of the sealing performance test apparatus which tests the sealing performance of a sealing apparatus. 回転時におけるシール装置のラジアル振れ量試験装置の概略構成図である。It is a schematic block diagram of the radial shake amount testing apparatus of the sealing device at the time of rotation. （ａ）〜（ｃ）は比較試験に用いたシール装置の断面図である。(A)-(c) is sectional drawing of the sealing device used for the comparative test. ロールネック部に装着された従来の密封型ロールネック軸受の縦断面図である。It is a longitudinal cross-sectional view of the conventional sealed roll neck bearing attached to the roll neck. 一対の内輪に取り付けられた従来のシール装置の縦断面図である。It is a longitudinal cross-sectional view of the conventional sealing device attached to a pair of inner rings. 一対の内輪に取り付けられた他の従来のシール装置の縦断面図である。It is a longitudinal cross-sectional view of the other conventional sealing device attached to a pair of inner ring.

符号の説明Explanation of symbols

４０ 密封型ロールネック軸受
４１ 外輪
４２ 複列外輪（外輪）
４３，４４ 複列内輪（内輪）
４３ｃ，４４ｃ 突き合せ面
４３ｄ，４４ｄ 外周面
４５ 円錐ころ（ころ）
５１ シール装置
５２ 芯金
５３ 弾性シール部材
５４ 嵌合部
５５ ラジアルリップ部
Ｄ１ 嵌合部の内径
Ｄ２ ラジアルリップ部の内径 40 Sealed roll neck bearing 41 Outer ring 42 Double row outer ring (outer ring)
43,44 Double-row inner ring (inner ring)
43c, 44c Abutting surfaces 43d, 44d Outer peripheral surface 45 Tapered rollers (rollers)
51 Sealing Device 52 Core Bar 53 Elastic Seal Member 54 Fitting Portion 55 Radial Lip D1 Fitting Port Diameter D2 Radial Lip Port Diameter

Claims (5)

複数の外輪と、
複数の内輪と、
該外輪と該内輪との間に配置される複数のころと、
互いに突き合うように配置される前記内輪の両端部の周囲に配置されて、芯金及び弾性シール部材を有するシール装置と、
を備える密封型ロールネック軸受であって、
前記弾性シール部材の内周面は、前記両端部の一方の外周面と嵌合する嵌合部と、前記両端部の他方の外周面と摺接するラジアルリップ部を有し、
前記芯金は、前記弾性シール部材の外周側で、前記嵌合部の径方向外方を少なくとも覆うことを特徴とする密封型ロールネック軸受。 A plurality of outer rings,
Multiple inner rings,
A plurality of rollers disposed between the outer ring and the inner ring;
A sealing device disposed around both ends of the inner ring disposed so as to face each other, and having a metal core and an elastic seal member;
A sealed roll neck bearing comprising:
The inner peripheral surface of the elastic seal member has a fitting portion that fits with one outer peripheral surface of the both end portions, and a radial lip portion that makes sliding contact with the other outer peripheral surface of the both end portions,
The cored bar covers at least the outer side in the radial direction of the fitting portion on the outer peripheral side of the elastic seal member. 前記ラジアルリップ部の内径は、前記嵌合部の内径より小さいことを特徴とする請求項１に記載の密封型ロールネック軸受。   The sealed roll neck bearing according to claim 1, wherein an inner diameter of the radial lip portion is smaller than an inner diameter of the fitting portion. 前記嵌合部は、略一様な内径を持った平坦状に形成され、
前記芯金の一端は、軸方向において、前記両端部の突き合せ面と前記ラジアルリップ部との間に位置することを特徴とする請求項１又は２に記載の密封型ロールネック軸受。 The fitting portion is formed in a flat shape having a substantially uniform inner diameter,
3. The sealed roll neck bearing according to claim 1, wherein one end of the cored bar is positioned between the butted surfaces of the both end portions and the radial lip portion in the axial direction. 前記嵌合部は、軸方向において略対称な曲面状に形成され、
前記芯金の一端は、軸方向において、前記両端部の突き合せ面と前記ラジアルリップ部との間に位置することを特徴とする請求項１又は２に記載の密封型ロールネック軸受。 The fitting portion is formed in a curved surface that is substantially symmetrical in the axial direction,
3. The sealed roll neck bearing according to claim 1, wherein one end of the cored bar is positioned between the butted surfaces of the both end portions and the radial lip portion in the axial direction. 前記嵌合部は、前記ラジアルリップ部と反対側に拡径するテーパ形状に形成され、
前記芯金の一端は、軸方向において、前記ラジアルリップ部を越えて延出することを特徴とする請求項１又は２に記載の密封型ロールネック軸受。 The fitting portion is formed in a taper shape that expands to the opposite side to the radial lip portion,
The sealed roll neck bearing according to claim 1 or 2, wherein one end of the core bar extends beyond the radial lip portion in the axial direction.
JP2007337770A 2007-12-27 2007-12-27 Sealed roll neck bearing Expired - Fee Related JP5098637B2 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015220151A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf Bearing arrangement and seal
CN107771252A (en) * 2015-06-29 2018-03-06 舍弗勒技术股份两合公司 Rolling bearing unit
US20240093731A1 (en) * 2019-11-11 2024-03-21 Schaeffler Technologies AG & Co. KG Wheel bearing unit

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55110863U (en) * 1979-01-29 1980-08-04
JPH0617824A (en) * 1992-03-04 1994-01-25 Skf Gmbh Sealed four-row taper-roller bearing
JP2003097724A (en) * 2001-09-26 2003-04-03 Nok Corp Sealing device

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55110863U (en) * 1979-01-29 1980-08-04
JPH0617824A (en) * 1992-03-04 1994-01-25 Skf Gmbh Sealed four-row taper-roller bearing
JP2003097724A (en) * 2001-09-26 2003-04-03 Nok Corp Sealing device

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107771252A (en) * 2015-06-29 2018-03-06 舍弗勒技术股份两合公司 Rolling bearing unit
CN107771252B (en) * 2015-06-29 2020-09-29 舍弗勒技术股份两合公司 Rolling bearing unit
DE102015220151A1 (en) * 2015-10-16 2017-04-20 Aktiebolaget Skf Bearing arrangement and seal
DE102015220151B4 (en) 2015-10-16 2022-07-07 Aktiebolaget Skf Bearing assembly and seal
US20240093731A1 (en) * 2019-11-11 2024-03-21 Schaeffler Technologies AG & Co. KG Wheel bearing unit
US11965554B2 (en) * 2019-11-11 2024-04-23 Schaeffler Technologies AG & Co. KG Wheel bearing unit

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