JP2000120670A - Rolling bearing - Google Patents
Rolling bearingInfo
- Publication number
- JP2000120670A JP2000120670A JP10296912A JP29691298A JP2000120670A JP 2000120670 A JP2000120670 A JP 2000120670A JP 10296912 A JP10296912 A JP 10296912A JP 29691298 A JP29691298 A JP 29691298A JP 2000120670 A JP2000120670 A JP 2000120670A
- Authority
- JP
- Japan
- Prior art keywords
- outer ring
- inner ring
- elastic body
- ring
- axial
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
- F16C27/066—Ball or roller 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
-
- 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、軸に嵌合される内
輪とハウジングに嵌合される外輪との間に複数の転動体
が介設された転がり軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling bearing having a plurality of rolling elements interposed between an inner ring fitted to a shaft and an outer ring fitted to a housing.
【０００２】[0002]
【従来の技術】例えば図８に示すオルタネータ等の小型
発電機や電動機の軸を支持する転がり軸受では、アキシ
アル方向及びラジアル方向の振動を受けて早期焼付き、
破損、振動音が問題となる場合があるため、図９に示す
ように、軸受ａの嵌合面ｂ（外径面）と相手面ｃ（ハウ
ジング）との間に弾性体ｄを挟み込むような対策をとっ
ている。しかしながら、このような対策では軸ｅの静的
な変位量（この場合、径方向の変位量）が大きくなって
軸ｅの案内精度を損なうという欠点がある。2. Description of the Related Art For example, in a rolling bearing for supporting a shaft of a small generator or an electric motor such as an alternator shown in FIG. 8, an early seizure occurs due to vibrations in axial and radial directions.
Since the damage and the vibration noise may cause a problem, as shown in FIG. 9, the elastic body d is sandwiched between the fitting surface b (outer diameter surface) of the bearing a and the mating surface c (housing). We are taking measures. However, such a measure has a disadvantage that the static displacement of the shaft e (in this case, the displacement in the radial direction) becomes large and the guide accuracy of the shaft e is impaired.
【０００３】そこで、振動を抑制しつつ軸の静的な変位
量を小さくするため、実開平６−２４２３１号公報や実
公平６−４０９８２号公報に示すものが提案されてい
る。In order to reduce the amount of static displacement of the shaft while suppressing vibration, Japanese Unexamined Utility Model Publication No. 6-24231 and Japanese Unexamined Utility Model Publication No. 6-40982 have been proposed.
【０００４】実開平６−２４２３１号公報では、軸受の
嵌合部位に振動吸収部としての複数の環状フィンを形成
し、該環状フィンにより剛性を大きくして静的な変位量
を小さくすると共に、フィンの撓みにより振動を吸収す
るようにしており、一方、実公平６−４０９８２号公報
では、外輪の嵌合部位に弾性体及び支持材を介在させ、
支持材により径方向の剛性を大きくしてラジアル方向の
静的な変位量を小さくすると共に、弾性体の軸方向の変
形によりアキシアル方向の振動を吸収するようにしてい
る。In Japanese Utility Model Application Laid-Open No. 6-24231, a plurality of annular fins are formed as vibration absorbing portions at fitting portions of a bearing, and rigidity is increased by the annular fins to reduce static displacement. Vibration is absorbed by bending of the fins. On the other hand, in Japanese Utility Model Publication No. 6-40982, an elastic body and a supporting material are interposed at the fitting portion of the outer ring,
The rigidity in the radial direction is increased by the support material to reduce the amount of static displacement in the radial direction, and the elastic body absorbs vibration in the axial direction by deformation in the axial direction.
【０００５】しかしながら、実開平６−２４２３１号公
報及び実公平６−４０９８２号公報に開示された技術に
おいては、いずれも剛性を大きくしたラジアル方向の振
動の吸収が殆ど期待できず、また、後者については構造
が複雑となってコスト高になるという不都合がある。However, in the techniques disclosed in Japanese Utility Model Laid-Open No. 6-24231 and Japanese Utility Model Publication No. 6-40982, absorption of radial vibrations with increased rigidity can hardly be expected. However, there is a disadvantage that the structure becomes complicated and the cost increases.
【０００６】[0006]
【発明が解決しようとする課題】本発明はかかる不都合
を解消するためになされたものであり、アキシアル方向
及びラジアル方向の振動を良好に吸収することができる
と共に、静的な変位量を小さくすることができ、しか
も、製作コストを低くすることができる転がり軸受を提
供することを目的とする。SUMMARY OF THE INVENTION The present invention has been made in order to solve such inconvenience, and it is possible to favorably absorb vibrations in the axial and radial directions and to reduce the amount of static displacement. An object of the present invention is to provide a rolling bearing that can be manufactured and that can reduce the manufacturing cost.
【０００７】[0007]
【課題を解決するための手段】かかる目的を達成するた
めに、本発明に係る転がり軸受は、軸に嵌合される内輪
とハウジングに嵌合される外輪との間に複数の転動体が
介設された転がり軸受において、前記内輪若しくは前記
外輪を複数に分割して該分割部の内の少なくとも一方の
表面、又は前記内輪の前記軸との嵌合部及び前記外輪の
前記ハウジングとの嵌合部の内の少なくとも一方の嵌合
部の表面を凹凸状に形成し、該凹凸表面とその相手面と
の間に弾性体を介在させたことを特徴とする。In order to achieve the above object, a rolling bearing according to the present invention comprises a plurality of rolling elements interposed between an inner ring fitted to a shaft and an outer ring fitted to a housing. In the provided rolling bearing, the inner race or the outer race is divided into a plurality of parts and at least one surface of the divided parts, or a fitting part of the inner race with the shaft and a fitting of the outer race with the housing. The surface of at least one of the fitting portions is formed in an uneven shape, and an elastic body is interposed between the uneven surface and its mating surface.
【０００８】[0008]
【発明の実施の形態】以下、本発明の実施の形態を図を
参照して説明する。図１は本発明の第１の実施の形態で
ある転がり軸受を説明するための説明的断面図、図２は
図１のＡ部拡大図、図３〜図７は本発明の第２〜第６の
実施の形態である転がり軸受を説明するための説明的断
面図である。なお、各実施の形態共に、転がり軸受とし
て玉軸受を例に採る。Embodiments of the present invention will be described below with reference to the drawings. 1 is an explanatory sectional view for explaining a rolling bearing according to a first embodiment of the present invention, FIG. 2 is an enlarged view of a portion A in FIG. 1, and FIGS. 3 to 7 are second to second embodiments of the present invention. It is explanatory sectional drawing for demonstrating the rolling bearing which is 6th Embodiment. In each of the embodiments, a ball bearing is taken as an example of the rolling bearing.
【０００９】まず、図１及び図２を参照して、第１の実
施の形態から説明すると、この玉軸受１は外輪２と内輪
３との間に転動体としての玉４が配設されており、内輪
３が軸５に嵌合され、外輪２の外径面はハウジング６に
嵌合されている。外輪２の外径面はランダムな粗さの凹
凸面７（図２参照）とされており、該凹凸面７にはゴム
等の弾性体８が接合されている。これにより、凹凸面７
とその相手面であるハウジング６との間に弾性体８が介
在されている。First, a description will be given of a first embodiment with reference to FIGS. 1 and 2. In this ball bearing 1, a ball 4 as a rolling element is disposed between an outer ring 2 and an inner ring 3. The inner ring 3 is fitted on the shaft 5, and the outer diameter surface of the outer ring 2 is fitted on the housing 6. The outer diameter surface of the outer ring 2 is an uneven surface 7 having a random roughness (see FIG. 2), and an elastic body 8 such as rubber is joined to the uneven surface 7. Thereby, the uneven surface 7
An elastic body 8 is interposed between the housing 6 and its opposing surface.
【００１０】そして、弾性体８の軸方向の変形及び凹凸
面７の凸部の軸方向の撓みにより、アキシアル方向の振
動が吸収される。The axial deformation of the elastic body 8 and the axial bending of the convex portion of the uneven surface 7 absorb the vibration in the axial direction.
【００１１】一方、ラジアル方向については、弾性体８
の径方向の変形により振動が吸収され、また、凹凸面７
の凸部先端で荷重を受けることにより、径方向の変位が
抑制される。On the other hand, in the radial direction, the elastic body 8
Vibration is absorbed by the radial deformation of the
By receiving a load at the tip of the convex portion, displacement in the radial direction is suppressed.
【００１２】次に、図３を参照して、第２の実施の形態
を説明すると、この玉軸受２１は外輪２２と内輪２３と
の間に転動体としての玉２４が配設されており、内輪２
３が軸２５に嵌合され、外輪２２の外径面及び端面はハ
ウジング２６に嵌合されている。外輪２２の外径面は断
面矩形状の凹凸面２７とされており、該凹凸面２７及び
外輪２２の端面にはゴム等の弾性体２８が接合されてい
る。これにより、外輪２２の凹凸面２７及び端面とその
相手面であるハウジング２６との間に弾性体２８が介在
されている。Next, a second embodiment will be described with reference to FIG. 3. In this ball bearing 21, a ball 24 as a rolling element is disposed between an outer ring 22 and an inner ring 23. Inner ring 2
3 is fitted to the shaft 25, and the outer diameter surface and the end surface of the outer ring 22 are fitted to the housing 26. An outer diameter surface of the outer ring 22 is an uneven surface 27 having a rectangular cross section, and an elastic body 28 such as rubber is joined to the uneven surface 27 and an end surface of the outer ring 22. Thereby, the elastic body 28 is interposed between the uneven surface 27 and the end surface of the outer ring 22 and the housing 26 which is the mating surface.
【００１３】そして、外輪２２の外径面及び端面に接合
された弾性体２８の軸方向の変形及び凹凸面２７の凸部
の軸方向の撓みにより、アキシアル方向の振動が吸収さ
れる。Axial vibration is absorbed by the axial deformation of the elastic body 28 joined to the outer diameter surface and the end surface of the outer ring 22 and the axial bending of the projection of the uneven surface 27.
【００１４】一方、ラジアル方向については、外輪２２
の外径面及び端面に接合された弾性体２８の径方向の変
形により振動が吸収され、また、凹凸面２７の凸部先端
で荷重を受けることにより、径方向の変位が抑制され
る。On the other hand, in the radial direction, the outer ring 22
The vibration is absorbed by the radial deformation of the elastic body 28 joined to the outer diameter surface and the end surface of the elastic member 28, and the load is applied to the tip of the convex portion of the uneven surface 27, whereby the radial displacement is suppressed.
【００１５】次に、図４を参照して、第３の実施の形態
を説明すると、この玉軸受３１は外輪３２と内輪３３と
の間に転動体としての玉３４が配設されており、内輪３
３が軸３５に嵌合され、外輪３２の外径面及び端面はハ
ウジング３６に嵌合されている。外輪３２の端面は断面
矩形状の凹凸面３７とされており、該凹凸面３７及び外
輪３２の外径面にはゴム等の弾性体３８が接合されてい
る。これにより、外輪３２の凹凸面３７及び外径面とそ
の相手面であるハウジング３６との間に弾性体３８が介
在されている。Next, a third embodiment will be described with reference to FIG. 4. In this ball bearing 31, a ball 34 as a rolling element is disposed between an outer ring 32 and an inner ring 33. Inner ring 3
3 is fitted to the shaft 35, and the outer diameter surface and the end surface of the outer ring 32 are fitted to the housing 36. An end surface of the outer ring 32 is an uneven surface 37 having a rectangular cross section, and an elastic body 38 such as rubber is joined to the uneven surface 37 and an outer diameter surface of the outer ring 32. Thereby, the elastic body 38 is interposed between the uneven surface 37 and the outer diameter surface of the outer ring 32 and the housing 36 which is the mating surface.
【００１６】そして、外輪３２の外径面及び凹凸面３７
に接合された弾性体３８の径方向の変形及び凹凸面３７
の凸部の径方向の撓みにより、ラジアル方向の振動が吸
収される。The outer diameter surface and the uneven surface 37 of the outer ring 32
Deformation of the elastic body 38 and the uneven surface 37
Radial vibrations are absorbed by the radial deflection of the projections.
【００１７】一方、アキシアル方向については、外輪３
２の凹凸面３７及び外径面に接合された弾性体３８の軸
方向の変形により振動が吸収され、また、凹凸面３７の
凸部先端で荷重を受けることにより、軸方向の変位が抑
制される。On the other hand, in the axial direction, the outer ring 3
Vibration is absorbed by the axial deformation of the elastic body 38 bonded to the second uneven surface 37 and the outer diameter surface, and the axial displacement is suppressed by receiving a load at the tip of the convex portion of the uneven surface 37. You.
【００１８】次に、図５を参照して、第４の実施の形態
を説明すると、この玉軸受４１は外輪４２と内輪４３と
の間に転動体としての玉４４が配設されており、内輪４
３の内径面及び端面が軸４５に嵌合され、外輪４２の外
径面及び端面はハウジング４６に嵌合されている。外輪
４２の外径面及び両端面並びに内輪４３の内径面及び両
端面は断面矩形状の凹凸面４７とされており、該凹凸面
４７にはゴム等の弾性体４８が接合されている。これに
より、外輪４２の凹凸面４７とその相手面であるハウジ
ング４６との間、及び内輪４３の凹凸面４７とその相手
面である軸４５との間に弾性体４８が介在されている。Next, a fourth embodiment will be described with reference to FIG. 5. In this ball bearing 41, a ball 44 as a rolling element is disposed between an outer ring 42 and an inner ring 43. Inner ring 4
The outer diameter surface and the end surface of the outer race 42 are fitted to the housing 46. The outer diameter surface and both end surfaces of the outer ring 42 and the inner diameter surface and both end surfaces of the inner ring 43 are formed as a concave-convex surface 47 having a rectangular cross section, and an elastic body 48 such as rubber is joined to the concave-convex surface 47. Thus, the elastic body 48 is interposed between the uneven surface 47 of the outer ring 42 and the housing 46 as the mating surface thereof, and between the uneven surface 47 of the inner ring 43 and the shaft 45 as the mating surface.
【００１９】そして、外輪４２の嵌合部位（外径面及び
端面）及び内輪４３の嵌合部位（内径面及び端面）に接
合された弾性体４８の軸方向の変形、並びに外輪４２の
外径面及び内輪４３の内径面に設けられた凹凸面４７の
各凸部の軸方向の撓みにより、アキシアル方向の振動が
吸収され、また、外輪４２の嵌合端面及び内輪４３の嵌
合端面に設けられた各凹凸面４７の凸部先端で荷重を受
けることにより、軸方向の変位が抑制される。The axial deformation of the elastic body 48 joined to the fitting portion (outer diameter surface and end surface) of the outer ring 42 and the fitting portion (inner diameter surface and end surface) of the inner ring 43, and the outer diameter of the outer ring 42 The axial deflection of each convex portion of the uneven surface 47 provided on the inner surface of the inner ring 43 absorbs vibration in the axial direction, and is provided on the fitting end surface of the outer ring 42 and the fitting end surface of the inner ring 43. By receiving a load at the tip of the convex portion of each of the concavo-convex surfaces 47, displacement in the axial direction is suppressed.
【００２０】一方、ラジアル方向については、外輪４２
及び内輪４３の各嵌合部位に接合された弾性体４８の径
方向の変形、並びに外輪４２及び内輪４３の各嵌合端面
に設けられた凹凸面４７の凸部の径方向の撓みにより、
振動が吸収され、また、外輪４２の外径面及び内輪４３
の内径面に設けられた凹凸面４７の凸部先端で荷重を受
けることにより、径方向の変位が抑制される。On the other hand, in the radial direction, the outer ring 42
And the radial deformation of the elastic body 48 joined to each fitting portion of the inner ring 43, and the radial bending of the convex portion of the uneven surface 47 provided on each fitting end surface of the outer ring 42 and the inner ring 43.
Vibration is absorbed, and the outer diameter surface of the outer ring 42 and the inner ring 43
By receiving a load at the tip of the convex portion of the concave-convex surface 47 provided on the inner diameter surface, radial displacement is suppressed.
【００２１】更に、この実施の形態では、外輪４２の両
端面及び内輪４３の両端面にそれぞれ凹凸面４７を設け
ているため、玉軸受の取り付けを方向性を考慮せずに行
うことができる。Furthermore, in this embodiment, since the uneven surfaces 47 are provided on both end surfaces of the outer ring 42 and both end surfaces of the inner ring 43, the mounting of the ball bearing can be performed without considering the directionality.
【００２２】次に、図６を参照して、第５の実施の形態
を説明すると、この玉軸受５１は外輪５２と内輪５３と
の間に転動体としての玉５４が配設されており、内輪５
３が軸５５に嵌合され、外輪５２の外径面はハウジング
５６に嵌合されている。Next, a fifth embodiment will be described with reference to FIG. 6. In this ball bearing 51, a ball 54 as a rolling element is disposed between an outer ring 52 and an inner ring 53. Inner ring 5
3 is fitted to the shaft 55, and the outer diameter surface of the outer ring 52 is fitted to the housing 56.
【００２３】外輪５２は軸方向に沿って二つに分割され
ており、一方の分割面には断面矩形状の凹凸面５７ａが
設けられ、他方の分割面には凹凸面５７ａに所定の隙間
を介して挿入される断面矩形状の凹凸面５７ｂが設けら
れ、凹凸面５７ａと該凹凸面５７ａの相手材である凹凸
面５７ｂとのすき間にはゴム等の弾性体５８が介在され
ている。The outer ring 52 is divided into two parts along the axial direction. One of the divided surfaces is provided with a concave-convex surface 57a having a rectangular cross section, and the other divided surface is provided with a predetermined gap in the concave-convex surface 57a. An uneven surface 57b having a rectangular cross-section inserted through the elastic member 57 is provided, and an elastic body 58 such as rubber is interposed between the uneven surface 57a and the uneven surface 57b which is a mating material of the uneven surface 57a.
【００２４】そして、凹凸面５７ａと凹凸面５７ｂとの
間に介在された弾性体５８の軸方向の変形及び凹凸面５
７ａ，５７ｂの凸部の軸方向の撓みにより、アキシアル
方向の振動が吸収され、また、凹凸面５７ａ，５７ｂの
各凸部の軸方向を向く側面どうしで荷重を受けることに
より、軸方向の変位が抑制される。The axial deformation of the elastic body 58 interposed between the uneven surface 57a and the uneven surface 57b and the uneven surface 5
Axial vibration is absorbed by the axial bending of the convex portions 7a and 57b, and a load is applied between the axially facing side surfaces of the convex and concave surfaces 57a and 57b, thereby displacing the axial direction. Is suppressed.
【００２５】一方、ラジアル方向については、凹凸面５
７ａと凹凸面５７ｂとの間に介在された弾性体５８の径
方向の変形により振動が吸収され、また、凹凸面５７
ａ，５７ｂの凸部先端で荷重を受けることにより、径方
向の変位が抑制される。On the other hand, in the radial direction, the uneven surface 5
Vibration is absorbed by the radial deformation of the elastic body 58 interposed between the elastic surface 7a and the uneven surface 57b.
By receiving a load at the tips of the convex portions a and 57b, displacement in the radial direction is suppressed.
【００２６】次に、図７を参照して、第６の実施の形態
を説明すると、この玉軸受６１は外輪６２と内輪６３と
の間に転動体としての玉６４が配設されており、内輪６
３が軸６５に嵌合され、外輪６２の外径面はハウジング
６６に嵌合されている。Next, a sixth embodiment will be described with reference to FIG. 7. In this ball bearing 61, a ball 64 as a rolling element is disposed between an outer ring 62 and an inner ring 63. Inner ring 6
3 is fitted to the shaft 65, and the outer diameter surface of the outer ring 62 is fitted to the housing 66.
【００２７】外輪６２は一方の端面から他方の端面に向
けて軸方向に切断された後に他方の端面の手前で径方向
内方に切断されて二つに分割されており、一方の分割面
には断面矩形状の凹凸面６７ａが設けられ、他方の分割
面には凹凸面６７ａに所定の隙間を介して挿入される断
面矩形状の凹凸面６７ｂが設けられ、凹凸面６７ａと該
凹凸面６７ａの相手材である凹凸面６７ｂとのすき間に
はゴム等の弾性体６８が介在されている。The outer ring 62 is cut in the axial direction from one end face to the other end face, and then cut radially inward just before the other end face to be divided into two parts. Is provided with an uneven surface 67a having a rectangular cross section, and the other divided surface is provided with an uneven surface 67b having a rectangular cross section inserted into the uneven surface 67a through a predetermined gap. An elastic body 68 made of rubber or the like is interposed in a gap between the concave and convex surface 67b which is a counterpart material.
【００２８】そして、凹凸面６７ａと凹凸面６７ｂとの
間に介在された弾性体６８の軸方向の変形及び軸方向に
沿う分割面に設けられた凹凸面６７ａ，６７ｂの凸部の
軸方向の撓みにより、アキシアル方向の振動が吸収さ
れ、また、径方向に沿う分割面に設けられた凹凸面６７
ａ，６７ｂの各凸部先端で荷重を受けることにより、軸
方向の変位が抑制される。Then, the elastic body 68 interposed between the uneven surface 67a and the uneven surface 67b is deformed in the axial direction, and the convex portions of the uneven surfaces 67a and 67b provided on the divided surface along the axial direction are axially deformed. The bending absorbs the vibration in the axial direction, and the uneven surface 67 provided on the divided surface along the radial direction.
By receiving the load at the tips of the convex portions a and 67b, the displacement in the axial direction is suppressed.
【００２９】一方、ラジアル方向については、凹凸面６
７ａと凹凸面６７ｂとの間に介在された弾性体６８の径
方向の変形により振動が吸収され、また、軸方向に沿う
分割面に設けられた凹凸面６７ａ，６７ｂの凸部先端で
荷重を受けることにより、径方向の変位が抑制される。On the other hand, in the radial direction, the uneven surface 6
Vibration is absorbed by the radial deformation of the elastic body 68 interposed between the projection 7a and the uneven surface 67b, and a load is applied to the protrusions of the uneven surfaces 67a and 67b provided on the divided surface along the axial direction. By receiving, the displacement in the radial direction is suppressed.
【００３０】なお、上記各実施の形態では、凹凸面の形
状を断面矩形状としているが、これに限定されず、断面
三角形状、断面円形状等どのような形状でもよく、ま
た、凹凸の配列は規則的なものでも、粗さ形状のように
不規則的なものであってもよい。In each of the above embodiments, the shape of the uneven surface is rectangular in cross section. However, the shape is not limited to this, and may be any shape such as triangular or circular in cross section. May be regular or irregular, such as a roughness profile.
【００３１】更に、凹凸面又は従来と同様の平面状の弾
性体を設ける面は、ここに示した例だけでなく、必要に
応じて、内輪側又は外輪側の内・外径面若しくは両端面
の中から単独又は任意に組み合わせた面とすることがで
きる。Further, the uneven surface or the surface on which the flat elastic body similar to the conventional one is provided is not limited to the example shown here, and if necessary, the inner / outer diameter surface or both end surfaces on the inner ring side or the outer ring side. Can be used alone or arbitrarily combined.
【００３２】更に、凹凸面の加工は機械加工によるのが
コスト的に有利であるが、必ずしもこれに限定する必要
はなく、化学処理等の表面処理技術を適用して凹凸面を
形成してもよい。Further, machining of the uneven surface is advantageously performed by machining, but is not necessarily limited to this. Even if the uneven surface is formed by applying a surface treatment technique such as chemical treatment. Good.
【００３３】更に、凹凸面と相手材との間で弾性体の最
も薄くなる部分の厚さを、凹凸面の高さ以下にするとよ
り効果的である。Further, it is more effective if the thickness of the thinnest portion of the elastic body between the uneven surface and the counterpart material is equal to or less than the height of the uneven surface.
【００３４】更に、外輪又は内輪を分割構造とする場
合、ハウジングまたは軸に嵌合される側の部材を、プレ
ス等の塑性加工が可能な板状のものを用いることによ
り、製作の容易化及び低コスト化を図ることができる。Further, when the outer ring or the inner ring has a divided structure, the member to be fitted to the housing or the shaft is made of a plate-shaped member such as a press which can be subjected to plastic working, thereby facilitating the manufacture and improving the manufacturing efficiency. Cost reduction can be achieved.
【００３５】更に、上記各実施の形態では、転がり軸受
として玉軸受を例に採って説明したが、玉軸受以外の全
ての転がり軸受に本発明を適用できるのは勿論である。Further, in each of the above embodiments, the ball bearing has been described as an example of the rolling bearing. However, it is needless to say that the present invention can be applied to all rolling bearings other than the ball bearing.
【００３６】[0036]
【発明の効果】上記の説明から明らかなように、本発明
によれば、アキシアル方向及びラジアル方向の振動を良
好に吸収することができると共に、静的な変位量を小さ
くすることができ、しかも、製作コストを低くすること
ができるという効果が得られる。As is apparent from the above description, according to the present invention, the axial and radial vibrations can be favorably absorbed, and the static displacement can be reduced. This has the effect of reducing the manufacturing cost.
【図１】本発明の第１の実施の形態である転がり軸受を
説明するための説明的断面図である。FIG. 1 is an explanatory sectional view for explaining a rolling bearing according to a first embodiment of the present invention.
【図２】図１のＡ部拡大図である。FIG. 2 is an enlarged view of a portion A in FIG.
【図３】本発明の第２の実施の形態である転がり軸受を
説明するための説明的断面図である。FIG. 3 is an explanatory sectional view for explaining a rolling bearing according to a second embodiment of the present invention.
【図４】本発明の第３の実施の形態である転がり軸受を
説明するための説明的断面図である。FIG. 4 is an explanatory sectional view for explaining a rolling bearing according to a third embodiment of the present invention.
【図５】本発明の第４の実施の形態である転がり軸受を
説明するための説明的断面図である。FIG. 5 is an explanatory cross-sectional view illustrating a rolling bearing according to a fourth embodiment of the present invention.
【図６】本発明の第５の実施の形態である転がり軸受を
説明するための説明的断面図である。FIG. 6 is an explanatory sectional view for explaining a rolling bearing according to a fifth embodiment of the present invention.
【図７】本発明の第６の実施の形態である転がり軸受を
説明するための説明的断面図である。FIG. 7 is an explanatory sectional view for explaining a rolling bearing according to a sixth embodiment of the present invention.
【図８】オルタネータの一例を示す図である。FIG. 8 is a diagram illustrating an example of an alternator.
【図９】従来の対策例を示した転がり軸受を説明するた
めの説明的断面図である。FIG. 9 is an explanatory cross-sectional view for explaining a rolling bearing showing a conventional countermeasure example.
１…玉軸受（転がり軸受） ２…外輪 ３…内輪 ４…玉（転動体） ５…軸 ６…ハウジング ７…凹凸面 ８…弾性体 DESCRIPTION OF SYMBOLS 1 ... Ball bearing (rolling bearing) 2 ... Outer ring 3 ... Inner ring 4 ... Ball (rolling element) 5 ... Shaft 6 ... Housing 7 ... Uneven surface 8 ... Elastic body
───────────────────────────────────────────────────── フロントページの続き (72)発明者 桃野 達信 神奈川県藤沢市鵠沼神明一丁目５番50号 日本精工株式会社内 (72)発明者 野田 万朶 神奈川県藤沢市鵠沼神明一丁目５番50号 日本精工株式会社内 Ｆターム(参考） 3J012 AB07 BB03 DB07 DB08 DB11 DB12 DB13 DB14 FB10 3J017 AA10 CA06 3J101 AA02 AA42 AA54 AA62 BA53 BA54 BA56 BA64 BA77 FA01 GA24 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Tatsunobu Momono 1-50-50 Kugenuma Shinmei 1-chome, Fujisawa-shi, Kanagawa Nippon Seiko Co., Ltd. No. N-Seiko Co., Ltd. F-term (reference) 3J012 AB07 BB03 DB07 DB08 DB11 DB12 DB13 DB14 FB10 3J017 AA10 CA06 3J101 AA02 AA42 AA54 AA62 BA53 BA54 BA56 BA64 BA77 FA01 GA24
Claims (1)
される外輪との間に複数の転動体が介設された転がり軸
受において、 前記内輪若しくは前記外輪を複数に分割して該分割部の
内の少なくとも一方の表面、又は前記内輪の前記軸との
嵌合部及び前記外輪の前記ハウジングとの嵌合部の内の
少なくとも一方の嵌合部の表面を凹凸状に形成し、該凹
凸表面とその相手面との間に弾性体を介在させたことを
特徴とする転がり軸受。1. A rolling bearing having a plurality of rolling elements interposed between an inner ring fitted to a shaft and an outer ring fitted to a housing, wherein the inner ring or the outer ring is divided into a plurality of parts. The surface of at least one of the parts, or the surface of at least one of the fitting part of the inner ring with the shaft and the fitting part of the outer ring with the housing is formed in an uneven shape, A rolling bearing comprising an elastic body interposed between an uneven surface and its mating surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10296912A JP2000120670A (en) | 1998-10-19 | 1998-10-19 | Rolling bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10296912A JP2000120670A (en) | 1998-10-19 | 1998-10-19 | Rolling bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000120670A true JP2000120670A (en) | 2000-04-25 |
Family
ID=17839786
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10296912A Pending JP2000120670A (en) | 1998-10-19 | 1998-10-19 | Rolling bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000120670A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2820178A1 (en) * | 2001-02-01 | 2002-08-02 | Luk Fahrzeug Hydraulik | BEARING DEVICE |
| US6616337B1 (en) | 2002-02-28 | 2003-09-09 | The Timken Company | Noise-reducing machine component |
| DE102004054974A1 (en) * | 2004-11-13 | 2006-05-18 | Fag Kugelfischer Ag & Co. Ohg | Rotary assembly for use in industrial application, has rolling unit staying in contact with track driven by drive unit, where running nose at rotary assembly is measured as airborne noise and has sound pressure level |
| JP2006351208A (en) * | 2005-06-13 | 2006-12-28 | Tokuden Co Ltd | Induction heating roller device |
| JP2008019991A (en) * | 2006-07-13 | 2008-01-31 | Jtekt Corp | Rolling bearing device |
| JP2009162298A (en) * | 2008-01-07 | 2009-07-23 | Jtekt Corp | Rolling bearing and bearing structure equipped with the same |
| JP2012255504A (en) * | 2011-06-09 | 2012-12-27 | Toyota Motor Corp | Gear device |
| JPWO2012176772A1 (en) * | 2011-06-21 | 2015-02-23 | 日本精工株式会社 | Rolling bearing unit |
| CN109282753A (en) * | 2018-08-27 | 2019-01-29 | 洛阳轴承研究所有限公司 | A kind of double inner ring two-row ball bearing axial deformation measurement toolings |
-
1998
- 1998-10-19 JP JP10296912A patent/JP2000120670A/en active Pending
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2820178A1 (en) * | 2001-02-01 | 2002-08-02 | Luk Fahrzeug Hydraulik | BEARING DEVICE |
| WO2002061296A1 (en) * | 2001-02-01 | 2002-08-08 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Bearing assembly |
| US7223020B2 (en) | 2001-02-01 | 2007-05-29 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Bearing assembly |
| WO2003074892A1 (en) * | 2002-02-28 | 2003-09-12 | The Timken Company | Noise-reducing machine component |
| US6616337B1 (en) | 2002-02-28 | 2003-09-09 | The Timken Company | Noise-reducing machine component |
| DE102004054974A1 (en) * | 2004-11-13 | 2006-05-18 | Fag Kugelfischer Ag & Co. Ohg | Rotary assembly for use in industrial application, has rolling unit staying in contact with track driven by drive unit, where running nose at rotary assembly is measured as airborne noise and has sound pressure level |
| DE102004054974B4 (en) * | 2004-11-13 | 2015-04-02 | Schaeffler Technologies AG & Co. KG | rotary joint |
| JP2006351208A (en) * | 2005-06-13 | 2006-12-28 | Tokuden Co Ltd | Induction heating roller device |
| JP2008019991A (en) * | 2006-07-13 | 2008-01-31 | Jtekt Corp | Rolling bearing device |
| JP2009162298A (en) * | 2008-01-07 | 2009-07-23 | Jtekt Corp | Rolling bearing and bearing structure equipped with the same |
| JP2012255504A (en) * | 2011-06-09 | 2012-12-27 | Toyota Motor Corp | Gear device |
| JPWO2012176772A1 (en) * | 2011-06-21 | 2015-02-23 | 日本精工株式会社 | Rolling bearing unit |
| CN109282753A (en) * | 2018-08-27 | 2019-01-29 | 洛阳轴承研究所有限公司 | A kind of double inner ring two-row ball bearing axial deformation measurement toolings |
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