JP2015121236A - Self-aligning roller bearing - Google Patents

Self-aligning roller bearing Download PDF

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Publication number
JP2015121236A
JP2015121236A JP2013263787A JP2013263787A JP2015121236A JP 2015121236 A JP2015121236 A JP 2015121236A JP 2013263787 A JP2013263787 A JP 2013263787A JP 2013263787 A JP2013263787 A JP 2013263787A JP 2015121236 A JP2015121236 A JP 2015121236A
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Prior art keywords
ring
inner ring
cage
self
roller bearing
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JP2013263787A
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Japanese (ja)
Inventor
幹隆 佐波
Masataka Sanami
幹隆 佐波
翔悟 田畑
Shogo Tabata
翔悟 田畑
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2013263787A priority Critical patent/JP2015121236A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers

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

Abstract

PROBLEM TO BE SOLVED: To provide a self-aligning roller bearing that has no center rib on an inner ring and does not increase in torque even when an axial load is placed.SOLUTION: A self-aligning roller bearing includes an inner ring 1 which has two raceway grooves 2, an outer ring 3 which has a spherical raceway surface 4, rollers 5 interposed between each raceway groove 2 and the raceway surface 4, a retainer 6 which accommodates and holds the rollers 5, and a center rib 11 provided on an inner ring bearing outer side. The self-aligning roller bearing has a step part 12, provided with a projection part 12a projecting in an outer ring direction, at a roller-side outer diameter of the center rib 11, the retainer 6 has a retainer width-side ring part 61, a bearing center part-side retainer ring part 62, and a column part 60 connecting both the ring parts 61, 62, and the self-aligning roller bearing has a step part 63, provided with a recessed part 63a, at an inner diameter of a retainer width-side ring part 61 so as to correspond to the step part 12 provided at the outer diameter of the center rib 11.

Description

この発明は、自動調心ころ軸受に関するもので、より詳しくは、内輪中鍔無しの自動調心ころ軸受に関するものである。   The present invention relates to a self-aligning roller bearing, and more particularly, to a self-aligning roller bearing having no inner ring intermediate flange.

自動調心ころ軸受は、転動体として凸面ころを用い、通常、球面軌道の外輪を持ち、２列の凸面ころが組み込まれている。凸面ころとは、ころの中心軸を含む平面において、外径面が凸の曲率を持っているころをいい、球面ころともいう。   Spherical roller bearings use convex rollers as rolling elements, and usually have an outer ring with a spherical raceway, and two rows of convex rollers are incorporated. The convex roller refers to a roller whose outer diameter surface has a convex curvature on a plane including the central axis of the roller, and is also referred to as a spherical roller.

自動調心ころ軸受は、一方の軌道が球状であることによって、両軌道の中心軸間の角ミスアライメント及び角運動に適用できる。自動調心ころ軸受には、代表的な例として、中鍔付き内輪に非対称ころ、即ち、ころの中央を通り、ころの中心軸に垂直な平面に関して、ころの外径面が非対称である凸面ころを組み込んだ形式と、中鍔無し内輪に対称ころ、即ち、ころの中央を通り、ころの中心軸に垂直な平面に関して、外径面が対称である凸面ころを組み込んだ形式とがある。   Spherical roller bearings can be applied to angular misalignment and angular motion between the central axes of both raceways because one raceway is spherical. A typical example of a self-aligning roller bearing is an asymmetrical roller with an inner ring with a center flange, that is, a convex surface whose outer diameter surface of the roller is asymmetrical with respect to a plane that passes through the center of the roller and is perpendicular to the center axis of the roller. There are a type incorporating a roller and a type in which a convex roller whose outer diameter surface is symmetric with respect to a plane that passes through the center of the roller and is perpendicular to the central axis of the roller is incorporated into the inner ring without a center flange.

図９に示したように、従来の内輪中鍔無しの自動調心ころ軸受は、内輪１０１に二列の軌道溝１０２、外輪１０３に球面の軌道面１０４が形成され、各軌道溝１０２と軌道面１０４の間にたる型のころ１０５が介在される。ころ１０５は、保持器１０６で周方向に等間隔で保持されている。保持器１０６の形式としては、金属板にプレス加工を施すことによって製作された打ち抜き保持器、くし型もみ抜き保持器１０６（特許文献１）等が知られている。また、内輪１０１には、小鍔１１１が設けられている。   As shown in FIG. 9, the conventional self-aligning roller bearing without the center ring of the inner ring has two rows of raceway grooves 102 formed on the inner ring 101 and a spherical raceway surface 104 formed on the outer ring 103. A barrel roller 105 is interposed between the surfaces 104. The rollers 105 are held at equal intervals in the circumferential direction by a cage 106. As a type of the cage 106, a punching cage manufactured by pressing a metal plate, a comb type punched cage 106 (Patent Document 1), and the like are known. Further, the inner ring 101 is provided with a gavel 111.

図１０に示すように、内輪中鍔無しの自動調心ころ軸受を縦軸に使用し、図中矢印で示すように、アキシアル荷重が付加された場合、極低速下では下列ころ１０５のスキューにより、内輪１０１が下降し、内輪１０１の食い込みが大きくなり、トルクが大きくなる。   As shown in FIG. 10, when a self-aligning roller bearing with no inner ring center flange is used on the vertical axis, and an axial load is applied as shown by an arrow in the figure, the skew of the lower row roller 105 is caused under extremely low speed. The inner ring 101 is lowered, the biting of the inner ring 101 is increased, and the torque is increased.

トルクが大きくなるメカニズムにつき、図１１〜図１３を参照して説明する。縦軸での静止時は、図１１に示すように、内輪１０１ところ１０５は、最大径位置で接触する（図中×印参照）。   A mechanism for increasing the torque will be described with reference to FIGS. When stationary on the vertical axis, as shown in FIG. 11, the inner ring 101 and 105 are in contact with each other at the maximum diameter position (see “X” in the figure).

図１２に示すように、内輪に、図中矢印方向にアキシアル荷重が付加されると、内輪１０１は食い込み勝手となるため、内輪１０１は図中矢印方向に下降し、内輪１０１ところ１０５の接触部（Ａ）は上方向に移動する。また、外輪１０３ところ１０５の接触部（Ｂ）は下方向に移動することになる。   As shown in FIG. 12, when an axial load is applied to the inner ring in the direction of the arrow in the figure, the inner ring 101 bites in, so the inner ring 101 descends in the direction of the arrow in the figure, and the contact portion between the inner ring 101 and 105 (A) moves upward. Further, the contact portion (B) of the outer ring 103 and 105 moves downward.

この状態で、内輪１０１を極低速度で起動させると、図１３に示すように、内輪１０１が矢印Ｃ方向に回転する。そして、ころ１０５が引っ張られて図中矢印Ｄ方向にスキューする。この結果、内輪１０１が図中矢印方向に更に下降し、より内輪１０１が食い込み勝手となり、内輪の食い込みが大きくなってトルクが大きくなる。   When the inner ring 101 is started at an extremely low speed in this state, the inner ring 101 rotates in the direction of arrow C as shown in FIG. Then, the rollers 105 are pulled to skew in the direction of arrow D in the figure. As a result, the inner ring 101 further descends in the direction of the arrow in the figure, the inner ring 101 bites more easily, the biting of the inner ring increases, and the torque increases.

自動調心ころ軸受においては、内輪に中鍔が設けられているものがある。図に示すように、内輪に中鍔が存在すると、上記したトルクが大きくなるという問題は起こらない。   In some self-aligning roller bearings, an inner ring is provided in the inner ring. As shown in the figure, when the inner ring exists in the inner ring, the above-described problem that the torque becomes large does not occur.

図１４に示すように、内輪１０１に中鍔１１２が存在すると、縦軸での静止時は、内輪１０１ところ１０５は最大径位置で接触し、ころ１０５の大端面は中鍔１１２と接触している。   As shown in FIG. 14, when the inner ring 101 is present on the inner ring 101, the inner ring 101 and 105 are in contact with each other at the maximum diameter position when the axis is stationary, and the large end surface of the roller 105 is in contact with the inner ring 112. Yes.

図１５に示すように、内輪１０１に、図中矢印方向にアキシアル荷重が付加されると、内輪１０１が下降する方向に力が加わることになるが、中鍔１１２が図中矢印方向にころ１０５の大端面を押すことになる。中鍔１１２がころ１０５を押し下げることにより、内輪１０１、外輪１０３ところ１０５は、ころ最大径位置で接触し、接触位置の関係は変わらないため、内輪１０１は食い込まず、トルクは大きくならない。   As shown in FIG. 15, when an axial load is applied to the inner ring 101 in the direction of the arrow in the figure, a force is applied in the direction in which the inner ring 101 descends. Will push the large end face. When the intermediate collar 112 pushes the roller 105 down, the inner ring 101 and the outer ring 103 contact 105 at the maximum roller diameter position, and the relationship between the contact positions does not change, so the inner ring 101 does not bite and the torque does not increase.

特開２００４−３４６９７１号公報JP 2004-346971 A

この発明は、内輪に中鍔が無い自動調心ころ軸受において、アキシアル荷重が加わっても、トルクが大きくならない自動調心ころ軸受を提供することを課題とするものである。   SUMMARY OF THE INVENTION An object of the present invention is to provide a self-aligning roller bearing in which the torque does not increase even when an axial load is applied to a self-aligning roller bearing having no inner ring in the inner ring.

前記の課題を解決するために、二列の軌道溝を有する内輪と、球面の軌道面を有する外輪と、各軌道溝と軌道面との間に介在されるころと、ころを収容保持する保持器と、前記内輪軸受外部側に設けられた内輪小鍔とを備えた自動調心ころ軸受において、前記内輪小鍔のころ側の外径には、外輪方向に突出する凸部を設けた段差部を有し、前記保持器は、保持器幅側リング部と、軸受中央部側保持器リング部と、両リング部とを連結する柱部とを備え、前記内輪小鍔の外径に設けられた段差部に対応するように、前記保持器幅側リング部の内径に凹部を設けた段差部を有するように構成した。   In order to solve the above problems, an inner ring having two rows of raceway grooves, an outer ring having a spherical raceway surface, a roller interposed between each raceway groove and the raceway surface, and a holder for housing and holding the roller And a self-aligning roller bearing comprising an inner ring gavel provided on the outer side of the inner ring bearing, wherein the outer diameter on the roller side of the inner ring gaver is provided with a step protruding in the outer ring direction. The cage includes a cage width side ring portion, a bearing center side cage ring portion, and a column portion connecting both the ring portions, and is provided on the outer diameter of the inner ring gavel. In order to correspond to the stepped portion, the stepped portion provided with a recess in the inner diameter of the cage width side ring portion was configured.

また、前記内輪小鍔の凸部と前記保持器幅側リング部の凹部との隙間を、前記内輪小鍔と前記保持器幅側リング部との他の段差部の隙間より大きくすると良い。   In addition, the gap between the convex portion of the inner ring gavel and the concave portion of the cage width side ring portion may be made larger than the gap between the other stepped portions of the inner ring gavel and the cage width side ring portion.

また、前記保持器の保持器幅側リング部の凹部の摺動面に径方向に溝を放射状に設けると良い。   Moreover, it is good to provide a radial groove | channel on the sliding surface of the recessed part of the holder width side ring part of the said holder | retainer radially.

また、前記保持器の保持器幅側リング部の凹部の摺動面に周方向に溝を放射状に設けると良い。   Moreover, it is good to provide a groove | channel radially on the sliding surface of the recessed part of the holder width side ring part of the said holder | retainer in the circumferential direction.

また、前記内輪軌道面の延長上に段差部を設けると良い。   Further, a stepped portion may be provided on the extension of the inner ring raceway surface.

また、前記ころの大端面をＲ形状とし、軸受中央部側保持器リング部と点接触するように構成するとよい。   Moreover, it is good to comprise so that the large end surface of the said roller may be made into R shape, and a point contact may be carried out with a bearing center part side retainer ring part.

以上のように、この発明によれば、アキシアル荷重が加わっても静止時の内輪ところの関係を保ったまま内輪ところが軸方向へ移動するため、トルクが大きくならない自動調心ころ軸受を提供することができる。   As described above, according to the present invention, there is provided a self-aligning roller bearing in which torque does not increase because the inner ring portion moves in the axial direction while maintaining the relationship between the inner ring portions at rest even when an axial load is applied. Can do.

この発明の実施形態にかかる自動調心ころ軸受の要部を拡大した断面図である。It is sectional drawing to which the principal part of the self-aligning roller bearing concerning embodiment of this invention was expanded. 図１の一部を拡大した断面図である。It is sectional drawing to which a part of FIG. 1 was expanded. この発明の実施形態にかかる自動調心ころ軸受にアキシアル荷重か付加された状態を示す断面図である。It is sectional drawing which shows the state by which the axial load was added to the self-aligning roller bearing concerning embodiment of this invention. この発明の第２の実施形態を示す拡大模式図である。It is an expansion schematic diagram which shows 2nd Embodiment of this invention. この発明の第３の実施形態を示し、（ａ）は拡大模式図、（ｂ）は（ａ）のＡ矢印方向からの保持器の模式図である。The 3rd Embodiment of this invention is shown, (a) is an expansion schematic diagram, (b) is a schematic diagram of the holder | retainer from the A arrow direction of (a). この発明の第４の実施形態を示す拡大模式図である。It is an expansion schematic diagram which shows 4th Embodiment of this invention. この発明の第５の実施形態を示す拡大模式図である。It is an expansion schematic diagram which shows 5th Embodiment of this invention. この発明の第６の実施形態を示す拡大模式図である。It is an expansion schematic diagram which shows 6th Embodiment of this invention. 従来の内輪中鍔無しの自動調心ころ軸受を示す断面図である。It is sectional drawing which shows the conventional self-aligning roller bearing without an inner ring intermediate collar. 従来の内輪中鍔無しの自動調心ころ軸受にアキシアル荷重を加えた状態を示す断面図である。It is sectional drawing which shows the state which applied the axial load to the conventional self-aligning roller bearing without an inner ring intermediate collar. 従来の内輪中鍔無しの自動調心ころ軸受にアキシアル荷重を加えた状態を示す拡大図である。FIG. 6 is an enlarged view showing a state in which an axial load is applied to a conventional self-aligning roller bearing without an inner ring intermediate flange. 従来の内輪中鍔無しの自動調心ころ軸受にアキシアル荷重を加えた状態を示す拡大図である。FIG. 6 is an enlarged view showing a state in which an axial load is applied to a conventional self-aligning roller bearing without an inner ring intermediate flange. 従来の内輪中鍔無しの自動調心ころ軸受にアキシアル荷重を加えた状態を示す拡大図である。FIG. 6 is an enlarged view showing a state in which an axial load is applied to a conventional self-aligning roller bearing without an inner ring intermediate flange. 従来の内輪中鍔有りの自動調心ころ軸受を示す拡大断面図である。It is an expanded sectional view which shows the conventional self-aligning roller bearing with an inner ring intermediate collar. 従来の内輪中鍔有りの自動調心ころ軸受を示すにアキシアル荷重を加えた状態を示す拡大図である。FIG. 7 is an enlarged view showing a state where an axial load is applied to a conventional self-aligning roller bearing with an inner ring intermediate flange.

以下、この発明の実施形態を添付図面に基づいて説明する。
この発明が適用される自動調心ころ軸受は、図１に示すように、内輪１に二列の軌道溝２、外輪３に球面の軌道面４が形成され、各軌道溝２と軌道面４の間にたる型のころ５が介在される。ころ５は、保持器６で周方向に等間隔で保持されている。 Embodiments of the present invention will be described below with reference to the accompanying drawings.
As shown in FIG. 1, the self-aligning roller bearing to which the present invention is applied has two rows of raceway grooves 2 on the inner ring 1 and a spherical raceway surface 4 on the outer ring 3, and each raceway groove 2 and raceway surface 4. A roller 5 of a barrel type is interposed between the two. The rollers 5 are held at equal intervals in the circumferential direction by a cage 6.

この自動調心ころ軸受は、内輪１に中鍔が無い構造であり、内輪１の軸受外部側には内輪小鍔１１が設けられている。この小鍔１１のころ５側の外径には外輪３方向に突出する凸部１２ａが設けられ、小鍔１１の外径に段差１２が設けられている。   This self-aligning roller bearing has a structure in which the inner ring 1 has no center flange, and an inner ring small flange 11 is provided on the bearing outer side of the inner ring 1. A protrusion 12 a that protrudes in the direction of the outer ring 3 is provided on the outer diameter of the gavel 11 on the roller 5 side, and a step 12 is provided on the outer diameter of the gavel 11.

保持器６は、保持器幅側リング部６１と軸受中央部側保持器リング部６２と、両リング部６１、６２とを連結する柱部６０とを備えたかご形保持器である。そして、柱部６０は、周方向に沿って等ピッチで配置され、周方向に沿って隣り合う柱部６０間に設けられる収容部（ポケット）にころ５が回転自在に収容される。   The cage 6 is a cage cage including a cage width side ring portion 61, a bearing center portion side cage ring portion 62, and a column portion 60 that connects both the ring portions 61 and 62. And the pillar part 60 is arrange | positioned at equal pitch along the circumferential direction, and the roller 5 is rotatably accommodated in the accommodating part (pocket) provided between the pillar parts 60 adjacent along the circumferential direction.

そして、この実施形態の保持器６は、前記小鍔１１の外径に設けられた段差１２に対応するように、保持器幅側リング部６１の内径に凹部６３ａが設けられ、保持器６のリング部６１の内径には、段差６３が設けられている。   And the holder | retainer 6 of this embodiment is provided with the recessed part 63a in the internal diameter of the holder | retainer width side ring part 61 so as to correspond to the level | step difference 12 provided in the outer diameter of the said gavel 11, and the holder | retainer 6's A step 63 is provided on the inner diameter of the ring portion 61.

保持器６を内輪１に嵌め込むと、図１に示すように、内輪１の小鍔１１の外径の凸部１２ａと保持器６の凹部６３ａとが対向し、小鍔１１の外径の段差１２と、保持器６の保持器幅側リング部６１の内径の段差６３が係合した状態となる。   When the cage 6 is fitted into the inner ring 1, as shown in FIG. 1, the outer diameter convex portion 12 a of the small collar 11 of the inner ring 1 and the concave portion 63 a of the cage 6 face each other, and the outer diameter of the small collar 11 The step 12 and the step 63 of the inner diameter of the cage width side ring portion 61 of the cage 6 are engaged.

この実施形態の自動調心ころ軸受を縦軸に使用し、アキシアル荷重が付加された場合につき、図２及び図３を参照して説明する。図２に示すように、縦軸での静止時は、従来の軸受同様に、内輪１ところ５は、最大径位置で接触する（図中×印参照）。   The case where the self-aligning roller bearing of this embodiment is used for the vertical axis and an axial load is applied will be described with reference to FIGS. As shown in FIG. 2, when stationary on the vertical axis, the inner ring 1 and 5 are in contact with each other at the maximum diameter position as in the conventional bearing (see the cross in the figure).

図３に示すように、内輪１にアキシアル荷重(図中白抜き矢印)を付加した場合、内輪１が軸方向へ動くと、内輪１の小鍔１１の外径に設けられた段差１２が、保持器幅側リング部６１の段差６３に当接し、図中矢印方向に力が加わり、保持器６は内輪１に押し下げられる。この結果、保持器６と内輪１は一体となって軸方向に動く。保持器６が軸方向に動くと、軸受中央部側保持器リング部６２がころ５を図中矢印方向へ押し下げるため、内輪１ところ５は一体となって軸方向に移動する。そのため、内輪中鍔付の軸受と同様に、内輪１ところ５は最大径位置で接触することになる。   As shown in FIG. 3, when an axial load (open arrow in the figure) is applied to the inner ring 1, when the inner ring 1 moves in the axial direction, a step 12 provided on the outer diameter of the gavel 11 of the inner ring 1 is Abutting against the step 63 of the cage width side ring portion 61, a force is applied in the direction of the arrow in the figure, and the cage 6 is pushed down by the inner ring 1. As a result, the cage 6 and the inner ring 1 move together in the axial direction. When the cage 6 moves in the axial direction, the bearing center side cage ring portion 62 pushes the roller 5 down in the direction of the arrow in the figure, so that the inner ring 1 and 5 move together in the axial direction. Therefore, the inner ring 1 and 5 are in contact with each other at the maximum diameter position in the same manner as the bearing with the inner ring intermediate flange.

従って、静止時の内輪１ところ５の関係を保ったまま内輪１ところ５が軸方向へ移動するため、内輪１は食い込まず、トルクが大きくならない。   Accordingly, since the inner ring 1 and 5 move in the axial direction while maintaining the relationship between the inner ring 1 and 5 at rest, the inner ring 1 does not bite and torque does not increase.

図４は、この発明の第２の実施形態を示す拡大模式図である。図４に示すように、内輪１の小鍔１１の段差１２と保持器幅側リング部６１の段差６３とが摺接する箇所の潤滑性を良くするため、小鍔１１の大径部側（凸部１２ａ）の保持器幅側リング部６１の凹部６３ａとの隙間８１を小鍔１１と保持器幅側リング部６１との他の段差側の隙間８２より大きくした構造としても良い。このように、小鍔１１の大径部側（凸部１２ａ）の隙間８１を大きくすることで、小鍔１１の段差１２と保持器幅側リング部６１の段差６３とが摺接する箇所に潤滑油が入りやすくなり、潤滑性が向上する。   FIG. 4 is an enlarged schematic view showing a second embodiment of the present invention. As shown in FIG. 4, in order to improve the lubricity of the portion where the step 12 of the small collar 11 of the inner ring 1 and the step 63 of the cage width side ring portion 61 are in sliding contact with each other, The gap 81 between the cage width side ring portion 61 of the portion 12a) and the recess 63a may be larger than the gap 82 on the other step side between the gavel 11 and the cage width side ring portion 61. Thus, by enlarging the gap 81 on the large-diameter portion side (convex portion 12a) of the small rod 11, lubrication is provided at a location where the step 12 of the small rod 11 and the step 63 of the cage width side ring portion 61 are in sliding contact. Oil easily enters and improves lubricity.

図５は、この発明の第３の実施形態を示し、（ａ）は拡大模式図、（ｂ）は（ａ）のＡ矢印方向からの保持器の模式図である。この図５に示すように、内輪１の小鍔１１の段差１２と保持器幅側リング部６１の段差６３とが摺接する箇所の潤滑性を良くするため、保持器６の保持器幅側リング部６１の凹部６３ａの摺動面６３ｂに径方向に溝６４を放射状に設け、潤滑油を入りやすくした構造としても良い。同様に内輪小鍔１１の凸部１２ａの摺接面に溝を設けても良い。   5A and 5B show a third embodiment of the present invention, in which FIG. 5A is an enlarged schematic diagram, and FIG. 5B is a schematic diagram of a cage from the direction of arrow A in FIG. As shown in FIG. 5, the cage width side ring of the cage 6 is improved in order to improve the lubricity of the portion where the step 12 of the gavel 11 of the inner ring 1 and the step 63 of the cage width side ring portion 61 are in sliding contact. It is good also as a structure which provided the groove | channel 64 radially on the sliding surface 63b of the recessed part 63a of the part 61, and was easy to enter lubricating oil. Similarly, a groove may be provided on the sliding contact surface of the convex portion 12a of the inner ring gavel 11.

図６は、この発明の第４の実施形態を示す拡大模式図である。図６に示すように、内輪小鍔１１の段差１２と保持器幅側リング部６１の段差６３とが摺接する箇所の潤滑性を良くするため、保持器６の保持器幅側リング部６１の凹部６３ａの摺動面６３ｂに周方向に溝６５を放射状に設け、潤滑油を入りやすくした構造としても良い。同様に内輪小鍔１１の凸部１２ａの摺接面に溝を設けても良い。   FIG. 6 is an enlarged schematic view showing a fourth embodiment of the present invention. As shown in FIG. 6, in order to improve the lubricity of the portion where the step 12 of the inner ring gavel 11 and the step 63 of the cage width side ring portion 61 are in sliding contact with each other, the cage width side ring portion 61 of the cage 6 is improved. A structure may be adopted in which grooves 65 are provided radially in the sliding surface 63b of the recess 63a so that the lubricating oil can easily enter. Similarly, a groove may be provided on the sliding contact surface of the convex portion 12a of the inner ring gavel 11.

図７は、この発明の第５の実施形態を示す拡大模式図である。図７に示すように、内輪１、保持器６の段差６３の摺動部での潤滑性を良くするため、図７に示すように、内輪１の軌道溝２の延長上に段差１２を設けることで、内輪１の軌道溝２から潤滑油が入りやすくした構造としても良い。   FIG. 7 is an enlarged schematic view showing a fifth embodiment of the present invention. As shown in FIG. 7, in order to improve the lubricity at the sliding portion of the step 63 of the inner ring 1 and the cage 6, a step 12 is provided on the extension of the raceway groove 2 of the inner ring 1 as shown in FIG. Thus, a structure in which lubricating oil can easily enter from the raceway groove 2 of the inner ring 1 may be adopted.

図８は、この発明の第６の実施形態を示す拡大模式図である。図８に示すように、ころ５と軸受中央側の軸受中央部側保持器リング部６２の摺動部での潤滑性を良くするため、ころ５の大端面５１をＲ形状とし、軸受中央部側保持器リング部６２と点接触する構造としても良い。   FIG. 8 is an enlarged schematic view showing the sixth embodiment of the present invention. As shown in FIG. 8, in order to improve the lubricity in the sliding part of the roller 5 and the bearing center side cage ring part 62 on the bearing center side, the large end surface 51 of the roller 5 is formed in an R shape, It is good also as a structure which carries out point contact with the side holder ring part 62. FIG.

この発明では、内輪中鍔無しの自動調心ころ軸受において、内輪小鍔１１の外径部と保持器幅側リング部６１の内径部に段差を設けたかご型保持器を採用することで、軸受を縦軸に使用し、アキシアル荷重が付加された場合、極低速回転時に内輪の食い込みによるトルクが大きくなることを防ぐことができる。   In this invention, in the self-aligning roller bearing without the inner ring inner flange, by adopting a cage type retainer in which a step is provided in the outer diameter part of the inner ring gavel 11 and the inner diameter part of the cage width side ring part 61, When the bearing is used for the vertical axis and an axial load is applied, it is possible to prevent the torque due to the biting of the inner ring from increasing during extremely low speed rotation.

今回開示された実施形態はすべての点で例示であって制限的なものではないと考えられるべきである。この発明の範囲は、上記した実施形態の説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。   It should be thought that embodiment disclosed this time is an illustration and restrictive at no points. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims for patent.

１ 内輪
２ 軌道溝
３ 外輪
４ 軌道面
６ 保持器
１１ 小鍔
１２ 段差
１２ａ 凸部
５１ 大端面
６０ 柱部
６１ リング部
６１ 保持器幅側リング部
６２ 軸受中央部側保持器リング部
６３ 段差
６３ａ 凹部
６３ｂ 摺動面
DESCRIPTION OF SYMBOLS 1 Inner ring 2 Raceway groove 3 Outer ring 4 Raceway surface 6 Cage 11 Gadget 12 Step 12a Convex part 51 Large end face 60 Column part 61 Ring part 61 Cage width side ring part 62 Bearing center part side cage ring part 63 Step 63a Concave part 63b Sliding surface

Claims (6)

二列の軌道溝を有する内輪と、球面の軌道面を有する外輪と、各軌道溝と軌道面との間に介在されるころと、ころを収容保持する保持器と、前記内輪軸受外部側に設けられた内輪小鍔とを備えた自動調心ころ軸受において、
前記内輪小鍔のころ側の外径には、外輪方向に突出する凸部を設けた段差部を有し、
前記保持器は、保持器幅側リング部と、軸受中央部側保持器リング部と、両リング部とを連結する柱部とを備え、前記内輪小鍔の外径に設けられた段差部に対応するように、前記保持器幅側リング部の内径に凹部を設けた段差部を有することを特徴とする自動調心ころ軸受。 An inner ring having two rows of raceway grooves, an outer ring having a spherical raceway surface, a roller interposed between each raceway groove and the raceway surface, a retainer for accommodating and holding the rollers, and an outer side of the inner ring bearing In a self-aligning roller bearing provided with an inner ring gavel,
The outer diameter on the roller side of the inner ring gavel has a stepped portion provided with a convex portion protruding in the direction of the outer ring,
The cage includes a cage width side ring portion, a bearing center side cage ring portion, and a column portion connecting both the ring portions, and a step portion provided on an outer diameter of the inner ring gavel. Correspondingly, a self-aligning roller bearing having a step portion provided with a recess in an inner diameter of the cage width side ring portion. 前記内輪小鍔の凸部と前記保持器幅側リング部の凹部との隙間を、前記内輪小鍔と前記保持器幅側リング部との他の段差部の隙間より大きくしたことを特徴とする請求項１に記載の自動調心ころ軸受。   The gap between the convex part of the inner ring gavel and the concave part of the cage width side ring part is made larger than the gap between the other step part between the inner ring gavel and the cage width side ring part. The self-aligning roller bearing according to claim 1. 前記保持器の保持器幅側リング部の凹部の摺動面に径方向に溝を放射状に設けたことを特徴とする請求項１に記載の自動調心ころ軸受。   2. The self-aligning roller bearing according to claim 1, wherein grooves are provided radially in a sliding direction of the concave portion of the cage width side ring portion of the cage. 前記保持器の保持器幅側リング部の凹部の摺動面に周方向に溝を放射状に設けたことを特徴とする請求項１に記載の自動調心ころ軸受。   The self-aligning roller bearing according to claim 1, wherein grooves are provided radially in a circumferential direction on a sliding surface of the concave portion of the cage width side ring portion of the cage. 前記内輪軌道面の延長上に段差部を設けたことを特徴とする請求項１〜４のいずれか１項に記載の自動調心ころ軸受。   The self-aligning roller bearing according to any one of claims 1 to 4, wherein a step portion is provided on an extension of the inner ring raceway surface. 前記ころの大端面をＲ形状とし、軸受中央部側保持器リング部と点接触することを特徴とする請求項１〜５のいずれか１項に記載の自動調心ころ軸受。
The self-aligning roller bearing according to any one of claims 1 to 5, wherein a large end surface of the roller has an R shape and is in point contact with a bearing central portion side cage ring portion.
JP2013263787A 2013-12-20 2013-12-20 Self-aligning roller bearing Pending JP2015121236A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106246720A (en) * 2016-09-21 2016-12-21 上海理工大学 The automatic aligning roller of suppression flow induced vibrations seals structure
CN106704359A (en) * 2016-11-18 2017-05-24 江苏方天电力技术有限公司 Automatic centering ball sealing mechanism restraining fluid exciting force
CN112594281A (en) * 2019-10-02 2021-04-02 斯凯孚公司 Self-aligning roller bearing

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106246720A (en) * 2016-09-21 2016-12-21 上海理工大学 The automatic aligning roller of suppression flow induced vibrations seals structure
CN106704359A (en) * 2016-11-18 2017-05-24 江苏方天电力技术有限公司 Automatic centering ball sealing mechanism restraining fluid exciting force
CN112594281A (en) * 2019-10-02 2021-04-02 斯凯孚公司 Self-aligning roller bearing

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