JP2013002469A - Rolling bearing mounting structure in rotating shaft device - Google Patents

Rolling bearing mounting structure in rotating shaft device Download PDF

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Publication number
JP2013002469A
JP2013002469A JP2011131249A JP2011131249A JP2013002469A JP 2013002469 A JP2013002469 A JP 2013002469A JP 2011131249 A JP2011131249 A JP 2011131249A JP 2011131249 A JP2011131249 A JP 2011131249A JP 2013002469 A JP2013002469 A JP 2013002469A
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Japan
Prior art keywords
ring
rotating shaft
housing
end surface
rolling bearing
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JP2011131249A
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Japanese (ja)
Inventor
Takahiro Shimano
貴大 島野
Kunihiro Yamaguchi
晋弘 山口
Nao Inazaki
奈雄 稲▲崎▼
Yoshitaka Waseda
義孝 早稲田
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JTEKT Corp
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JTEKT Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Turning (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing mounting structure that eliminates wear on the raceway surfaces of the inner and outer rings and that of on the rolling contact surfaces of rolling elements, and also, eliminates the occurrence of fretting and creep.SOLUTION: A first projecting part 63 or 73 capable of abutting on at least either one of one side end surface of an inner ring 20 and one side end surface of an outer ring 11 is formed on at least either one of a rotating shaft 70 and a housing 61. A second projecting part 80 or 85 capable of abutting on at least either one of the other side end surface of the inner ring 20 and the other side end surface of the outer ring 11 is provided on at least either one of the rotating shaft 70 and the housing 61. A chamfering 14 or 24 is formed at least at either one of the inner edge of the one side end surface of the inner ring 20 and the outer edge of the one side end surface of the outer ring 11. A ring-like elastic member 84 or 89 made of rubber is inserted between the first projecting part 63 or 73 and the chamfering 14 or 24 and abutted on at least either one of the rotating shaft 70 and the housing 61. A work hardened layer 24a is provided on a pair of engaging tapers 24.

Description

本発明は、内輪、外輪、転動体とからなる転がり軸受を、回転軸およびハウジングの少なくともどちらか一方に取付けるための回転軸装置における転がり軸受の取付け構造に関する。   The present invention relates to a mounting structure for a rolling bearing in a rotating shaft device for mounting a rolling bearing including an inner ring, an outer ring, and a rolling element to at least one of a rotating shaft and a housing.

図６（特許文献１）に示すように、ハウジング１００に対し回転軸１１０を回転可能に軸支するためには、ハウジング１００および回転軸１１０間に一対の転がり軸受１２０、１３０が使用されている。一方の転がり軸受１２０の外輪１２１が、ハウジング１００の段部１０１に当接し、他方の転がり軸受１３０の外輪１３１が、ハウジング１００の段部１０２に当接し、他方の転がり軸受１３０の内輪１３２が回転軸１１０の段部１１２に当接し、一方の転がり軸受１２０の内輪１２２および回転軸１１０の段部１１１間にウェーブワッシャ１４０を介挿することにより、ハウジング１００に対する回転軸１１０の軸方向の位置を決めている。前記ウェーブワッシャ１４０は、回転軸１１０を軸方向に押し付ける役目を持つとともに、ハウジング１００および回転軸１１０の加工誤差を吸収するとともにこれらの熱膨張を吸収する役目を持つ。   As shown in FIG. 6 (Patent Document 1), a pair of rolling bearings 120 and 130 are used between the housing 100 and the rotating shaft 110 in order to rotatably support the rotating shaft 110 with respect to the housing 100. . The outer ring 121 of one rolling bearing 120 abuts on the step 101 of the housing 100, the outer ring 131 of the other rolling bearing 130 abuts on the step 102 of the housing 100, and the inner ring 132 of the other rolling bearing 130 rotates. The position of the rotating shaft 110 in the axial direction with respect to the housing 100 is determined by abutting the stepped portion 112 of the shaft 110 and inserting the wave washer 140 between the inner ring 122 of the rolling bearing 120 and the stepped portion 111 of the rotating shaft 110. I have decided. The wave washer 140 has a role of pressing the rotating shaft 110 in the axial direction, a function of absorbing a processing error of the housing 100 and the rotating shaft 110 and a function of absorbing these thermal expansions.

ウェーブワッシャ１４０の回転軸１１０を軸方向に押し付ける力によって、外輪１２１および段部１０１間、外輪１３１および段部１０２間、内輪１２２および段部１１１間、内輪１３２および段部１１２間に摩擦力が発生し、ハウジング１００に対する回転軸１１０の半径方向の移動を不能にしている。   A frictional force is generated between the outer ring 121 and the stepped portion 101, between the outer ring 131 and the stepped portion 102, between the inner ring 122 and the stepped portion 111, and between the inner ring 132 and the stepped portion 112 by the force pressing the rotating shaft 110 of the wave washer 140 in the axial direction. And the radial movement of the rotating shaft 110 relative to the housing 100 is disabled.

実開昭６０−１０３７１３号公報Japanese Utility Model Publication No. 60-103713

ハウジング１００の内周に外輪１２１、１３１が半径方向にごく僅かな隙間を持って嵌合され、回転軸１１０の外周に内輪１２２、１３２が半径方向にごく僅かな隙間を持って嵌合されているため、ハウジング１００の内周の軸線に対し回転軸１１０の軸線が半径方向に若干ずれた位置に取付けられる。この結果、ハウジング１００の内周に対し回転軸１１０が振れ回り回転し、回転軸１１０の遠心力によって内輪１２２、１３２、外輪１２１、１３１の軌道面および転動体１２３、１３３の転動面が摩耗しやすい。   The outer rings 121 and 131 are fitted to the inner circumference of the housing 100 with a very small gap in the radial direction, and the inner rings 122 and 132 are fitted to the outer circumference of the rotating shaft 110 with a little gap in the radial direction. Therefore, the axis of the rotating shaft 110 is attached to a position slightly shifted in the radial direction with respect to the inner peripheral axis of the housing 100. As a result, the rotating shaft 110 swings and rotates with respect to the inner periphery of the housing 100, and the raceways of the inner rings 122 and 132, the outer rings 121 and 131 and the rolling surfaces of the rolling elements 123 and 133 are worn by the centrifugal force of the rotating shaft 110. It's easy to do.

ウェーブワッシャ１４０および段部１１１に代えて、回転軸１１０に係合溝を形成し、この係合溝にＣリングを嵌め込んだものは、構造が簡単なため組み付けやすいメリットがある反面、軸方向に隙間があるため、外部からの振動により回転軸１１０が軸方向に繰り返し移動し、内輪１２２、１３２、外輪１２１、１３１の段部１１１、１１２、１０１、１０２側の端面にフレッチングが発生する。また、ハウジング１００の内周および外輪１２１、１３１間、回転軸１１０の外周および内輪１２２、１３２間にそれぞれ半径方向に隙間があるため、ハウジング１００に対し外輪１２１、１３１が回転し、内輪１２２、１３２に対し回転軸１１０が回転することによって、クリープが発生する。   In place of the wave washer 140 and the stepped portion 111, an engagement groove is formed in the rotating shaft 110, and a C-ring is fitted in the engagement groove has a merit that it is easy to assemble because of its simple structure, but in the axial direction. Therefore, the rotation shaft 110 repeatedly moves in the axial direction due to external vibration, and fretting occurs on the end surfaces of the inner rings 122 and 132 and the outer rings 121 and 131 on the side of the step portions 111, 112, 101, and 102. Further, since there are gaps in the radial direction between the inner circumference and outer rings 121 and 131 of the housing 100 and between the outer circumference of the rotary shaft 110 and the inner rings 122 and 132, the outer rings 121 and 131 rotate relative to the housing 100, and the inner rings 122, As the rotating shaft 110 rotates with respect to 132, creep occurs.

本発明は、上述した問題点を解決するためになされたもので、その目的とするところは、振れ回り回転を無くして内輪、外輪の軌道面および転動体の転動面の摩耗を無くすとともに、フレッチングおよびクリープの発生を無くした回転軸装置における転がり軸受の取付け構造を提供する。   The present invention has been made to solve the above-described problems, and the object of the present invention is to eliminate wear-out of the inner ring, the raceway surface of the outer ring and the rolling surface of the rolling element by eliminating the whirling rotation, Provided is a rolling bearing mounting structure in a rotary shaft device that eliminates occurrence of fretting and creep.

請求項１に記載の発明は、ハウジングに転がり軸受を介して回転軸を回転可能に軸支した回転軸装置において、内輪、外輪、転動体とからなる前記転がり軸受を、前記回転軸および前記ハウジングの少なくともどちらか一方に取付けるための転がり軸受の取付け構造であって、前記内輪の一側端面および前記外輪の一側端面の少なくともどちらか一方に当接可能な第１の突出部を、前記回転軸および前記ハウジングの少なくともどちらか一方に形成し、前記内輪の他側端面および前記外輪の他側端面の少なくともどちらか一方に当接可能な第２の突出部を、前記回転軸および前記ハウジングの少なくともどちらか一方に設け、前記内輪の一側端面の内縁および前記外輪の一側端面の外縁の少なくともどちらか一方に面取りを形成し、前記第１の突出部および面取り間にゴム製のリング状の弾性部材を介挿するとともにこの弾性部材を回転軸およびハウジングの少なくともどちらか一方に当接させ、前記面取りに加工硬化処理を施すことにより加工硬化層を設けたものである。   According to a first aspect of the present invention, in the rotary shaft device in which the rotary shaft is rotatably supported on the housing via the rolling bearing, the rolling bearing including the inner ring, the outer ring, and the rolling element is connected to the rotary shaft and the housing. A rolling bearing mounting structure for mounting to at least one of the first protrusion and the first protrusion that can contact at least one of the one end face of the inner ring and the one end face of the outer ring, A second projecting portion formed on at least one of the shaft and the housing and capable of contacting at least one of the other end surface of the inner ring and the other end surface of the outer ring; Chamfering is provided on at least one of the inner edge of the one end face of the inner ring and the outer edge of the one end face of the outer ring. A work hardening layer is formed by inserting a rubber ring-shaped elastic member between the protruding portion and the chamfer and bringing the elastic member into contact with at least one of the rotating shaft and the housing and subjecting the chamfer to work hardening. Is provided.

この構成により、ハウジングの内周の軸線に対し回転軸の軸線が同軸に配置されることにより、回転軸の振れ回りが無くなり、内輪、外輪の軌道面および転動体の転動面の摩耗が無くなる。さらに、ハウジングに対して外輪が軸方向および半径方向に移動不能に固定されるか、内輪に対して回転軸が軸方向および半径方向に移動不能に固定されることにより、フレッチングおよびクリープの発生を無くすことができる。またさらに、加工硬化層により面取りが摩耗しにくくなる。   With this configuration, the axis of the rotating shaft is arranged coaxially with the inner peripheral axis of the housing, so that the rotating shaft does not swing and wear of the inner ring, outer ring raceway surface and rolling element rolling surface is eliminated. . Furthermore, the outer ring is fixed to the housing in an axially and radially immovable manner, or the rotating shaft is fixed to the inner ring in an axially and radially immovable manner to prevent fretting and creep. It can be lost. Furthermore, the work-hardened layer makes it difficult to wear the chamfer.

請求項２に記載の発明は、前記加工硬化処理として、ローレット加工を施したものである。これにより、ハウジングに対して外輪が軸方向および半径方向により一層移動不能に固定されるか、内輪に対して回転軸が軸方向および半径方向により一層移動不能に固定されることにより、フレッチングおよびクリープの発生をより一層無くすことができる。   The invention according to claim 2 is one in which knurling is performed as the work hardening treatment. As a result, the outer ring is fixed to the housing more immovably in the axial direction and the radial direction, or the rotating shaft is fixed to the inner ring more immovable in the axial direction and the radial direction, thereby fretting and creeping. Can be further eliminated.

請求項３に記載の発明は、前記加工硬化処理として、ショットピーニング加工を施したものである。これにより、面取りが摩耗しにくくなる。   The invention according to claim 3 is obtained by performing shot peening as the work hardening treatment. Thereby, chamfering becomes difficult to wear.

本発明によれば、ハウジングの内周の軸線に対し回転軸の軸線が同軸に配置されることにより、回転軸の振れ回りが無くなり、内輪、外輪の軌道面および転動体の転動面の摩耗が無くなる。さらに、ハウジングに対して外輪が軸方向および半径方向に移動不能に固定されるか、内輪に対して回転軸が軸方向および半径方向に移動不能に固定されることにより、フレッチングおよびクリープの発生を無くすことができる。またさらに、加工硬化層により面取りが摩耗しにくくなる。   According to the present invention, the axis of the rotating shaft is arranged coaxially with the inner peripheral axis of the housing, so that the rotating shaft does not run out, and the inner ring, the outer ring raceway surface, and the rolling element rolling surface wear. Disappears. Furthermore, the outer ring is fixed to the housing in an axially and radially immovable manner, or the rotating shaft is fixed to the inner ring in an axially and radially immovable manner to prevent fretting and creep. It can be lost. Furthermore, the work-hardened layer makes it difficult to wear the chamfer.

本発明の実施形態における転がり軸受の取付け構造を示す縦断面図である。It is a longitudinal cross-sectional view which shows the attachment structure of the rolling bearing in embodiment of this invention. 本発明の実施形態における転がり軸受の取付け構造を示す図１のＡ矢視図である。It is A arrow directional view of FIG. 1 which shows the attachment structure of the rolling bearing in embodiment of this invention. 本発明の実施形態における転がり軸受の取付け構造を示す図１のＢ方向から見た面取りの展開図である。It is the development view of the chamfering seen from the B direction of FIG. 1 which shows the attachment structure of the rolling bearing in embodiment of this invention. 本発明の他の実施形態における図３相当の面取りの展開図である。FIG. 4 is a development view of a chamfer corresponding to FIG. 3 in another embodiment of the present invention. 本発明の他の実施形態における転がり軸受の取付け構造を示す縦断面図である。It is a longitudinal cross-sectional view which shows the attachment structure of the rolling bearing in other embodiment of this invention. 従来における転がり軸受の取付け構造を示す縦断面図である。It is a longitudinal cross-sectional view which shows the attachment structure of the conventional rolling bearing.

本発明の一実施形態について、図１および図３を参酌しつつ説明する。図１は転がり軸受の取付け構造を示す縦断面図であり、図２は図１のＡ矢視図であり、図３は図１のＢ方向から見た面取りの円周方向の展開図である。   An embodiment of the present invention will be described with reference to FIGS. 1 and 3. FIG. 1 is a longitudinal sectional view showing a mounting structure of a rolling bearing, FIG. 2 is a view taken in the direction of arrow A in FIG. 1, and FIG. 3 is a development view in the circumferential direction of chamfering as seen from the direction B in FIG. .

回転軸装置６０は、ハウジング６１と、このハウジング６１に取り付けられる転がり軸受１０と、この転がり軸受１０を介して回転可能に軸支される回転軸７０とからなっている。転がり軸受は、転動体として玉を使った玉軸受１０である。玉軸受１０は、リング状の外輪１１と、外輪１１の内周側に配置されるリング状の内輪２０と、外輪１１と内輪２０間に配置されるリング状の保持器３０と、保持器３０に保持される複数の玉４０とからなっている。   The rotating shaft device 60 includes a housing 61, a rolling bearing 10 attached to the housing 61, and a rotating shaft 70 that is rotatably supported via the rolling bearing 10. The rolling bearing is a ball bearing 10 that uses balls as rolling elements. The ball bearing 10 includes a ring-shaped outer ring 11, a ring-shaped inner ring 20 disposed on the inner peripheral side of the outer ring 11, a ring-shaped cage 30 disposed between the outer ring 11 and the inner ring 20, and a cage 30. And a plurality of balls 40 held on the surface.

前記外輪１１の内周には、断面円弧状の外輪側軌道面１２が形成され、外輪１１の外周には、円筒状の被嵌合面１３が形成され、被嵌合面１３の軸方向の両端の外縁には、一対のＣ面取り１４が形成されている。前記内輪２０の外周には、断面円弧状の内輪側軌道面２２が形成され、内輪２０の内周には、円筒状の被嵌合面２３が形成され、被嵌合面２３の軸方向の両端の内縁には、一対のＣ面取り２４が形成されている。   An outer ring side raceway surface 12 having a circular arc cross section is formed on the inner circumference of the outer ring 11, and a cylindrical fitted surface 13 is formed on the outer circumference of the outer ring 11. A pair of C chamfers 14 are formed on the outer edges of both ends. An inner ring side raceway surface 22 having a circular arc cross section is formed on the outer periphery of the inner ring 20, and a cylindrical fitted surface 23 is formed on the inner circumference of the inner ring 20. A pair of C chamfers 24 are formed at the inner edges of both ends.

前記保持器３０は円周方向に複数のポケット部３１を有し、各ポケット部３１に玉４０が回転可能に保持されている。前記玉４０は、金属製で、球形状を有し、外面が転動面となる。   The cage 30 has a plurality of pocket portions 31 in the circumferential direction, and a ball 40 is rotatably held in each pocket portion 31. The ball 40 is made of metal and has a spherical shape, and the outer surface is a rolling surface.

前記ハウジング６１には、回転軸７０の回転軸線と同軸に円筒状の内周面６２が形成され、この内周面６２は、外輪１１の被嵌合面１３が径方向に僅かな隙間を持って嵌合できるような内径を有する。内周面６２には玉軸受１０側へ突出した第１の突出部６３が形成され、この第１の突出部６３は外輪１１の一側端面と対向する第１の内側端面６４を有する。また内周面６２には、外輪１１の他側端面に対応する位置に係合溝６５が形成され、この係合溝６５にはＣリング８０が嵌め込まれている。Ｃリング８０は外輪１１の他側端面に当接する第２の内側端面８１を有する。Ｃリング８０は、図１の状態よりもさらに外径方向に拡張しようとする弾性力を有し、円周上1箇所に切欠き８３を有する。   The housing 61 is formed with a cylindrical inner peripheral surface 62 coaxially with the rotation axis of the rotary shaft 70, and the inner peripheral surface 62 has a slight gap in the radial direction of the fitted surface 13 of the outer ring 11. It has an inner diameter that can be fitted. A first protrusion 63 that protrudes toward the ball bearing 10 is formed on the inner peripheral surface 62, and the first protrusion 63 has a first inner end face 64 that faces one end face of the outer ring 11. An engagement groove 65 is formed in the inner peripheral surface 62 at a position corresponding to the other end surface of the outer ring 11, and a C ring 80 is fitted in the engagement groove 65. The C ring 80 has a second inner end surface 81 that abuts against the other end surface of the outer ring 11. The C ring 80 has an elastic force to expand further in the outer diameter direction than the state of FIG. 1 and has a notch 83 at one place on the circumference.

前記回転軸７０には、これの回転軸線と同軸に円筒状の外周面７２が形成され、この外周面７２は、内輪２０の被嵌合面２３が径方向に僅かな隙間を持って嵌合できるような外径を有する。外周面７２には玉軸受１０側へ突出した第１の突出部７３が形成され、この第１の突出部７３は内輪２０の一側端面と対向する第１の内側端面７４を有する。また外周面７２には、内輪２０の他側端面に対応する位置に係合溝７５が形成され、この係合溝７５には、Ｃリング８５が嵌め込まれている。Ｃリング８５は内輪２０の他側端面に当接する第２の内側端面８６を有する。Ｃリング８５は、図１の状態よりもさらに内径方向に縮小しようとする弾性力を有し、円周上1箇所に切欠き８８を有する。   The rotary shaft 70 is formed with a cylindrical outer peripheral surface 72 coaxially with the rotation axis thereof, and the outer peripheral surface 72 is fitted to the fitted surface 23 of the inner ring 20 with a slight gap in the radial direction. It has an outer diameter that can be used. A first protrusion 73 protruding toward the ball bearing 10 is formed on the outer peripheral surface 72, and the first protrusion 73 has a first inner end surface 74 that faces one end surface of the inner ring 20. An engagement groove 75 is formed in the outer peripheral surface 72 at a position corresponding to the other end surface of the inner ring 20, and a C ring 85 is fitted in the engagement groove 75. The C ring 85 has a second inner end face 86 that abuts against the other end face of the inner ring 20. The C-ring 85 has an elastic force that tends to be further reduced in the inner diameter direction than the state of FIG. 1, and has a notch 88 at one place on the circumference.

前記被嵌合面１３、２３には、樹脂製の吸収被膜１５、２５が固着されている。吸収被膜１５、２５は、例えばナイロン６６等のように外輪１１および内輪２０よりも軟らかい材料が用いられる。吸収被膜１５、２５は、粘着系の接着剤によって被嵌合面１３、２３に貼り付けられる。前記粘着系の接着剤は、時間の経過とともに硬化するタイプのものが望ましい。吸収被膜１５は、外輪１１の被嵌合面１３およびハウジング６１の内周面６２間の隙間を埋める程度の肉厚を有し、吸収被膜２５は、内輪２０の被嵌合面２３および回転軸７０の外周面７２間の隙間を埋める程度の肉厚を有する。   Resin-made absorption films 15 and 25 are fixed to the mated surfaces 13 and 23. The absorbent coatings 15 and 25 are made of a material softer than the outer ring 11 and the inner ring 20 such as nylon 66, for example. The absorption films 15 and 25 are affixed to the mating surfaces 13 and 23 by an adhesive adhesive. The pressure-sensitive adhesive is preferably of a type that cures over time. The absorbent coating 15 has a thickness sufficient to fill a gap between the fitted surface 13 of the outer ring 11 and the inner peripheral surface 62 of the housing 61, and the absorbent coating 25 is fitted with the fitted surface 23 of the inner ring 20 and the rotating shaft. It has a thickness enough to fill the gap between the outer peripheral surfaces 72 of 70.

吸収被膜１５、２５は、内輪２０の軸線方向に幅を有するので、後述するＯリング８４、８９単独に比べて、外輪１１はハウジング６１の内周面６２と同軸になるよう配置されやすくなり、内輪２０は回転軸７０の外周面７２と同軸になるよう配置されやすくなる。吸収被膜１５、２５の肉厚を、外輪１１の被嵌合面１３およびハウジング６１の内周面６２間の隙間、内輪２０の被嵌合面２３および回転軸７０の外周面７２間の隙間よりも若干大きくしてこれらの隙間へ圧入すれば、ハウジング６１に対し外輪１１が回転しようとする動きを止めることができ、回転軸７０に対し内輪２０が回転しようとする動きを止めることができ、クリープの発生が抑えられる。   Since the absorption coatings 15 and 25 have a width in the axial direction of the inner ring 20, the outer ring 11 can be easily arranged so as to be coaxial with the inner peripheral surface 62 of the housing 61 as compared with the O-rings 84 and 89 described later. The inner ring 20 is easily arranged so as to be coaxial with the outer peripheral surface 72 of the rotating shaft 70. The thickness of the absorption coatings 15 and 25 is determined by the gap between the fitted surface 13 of the outer ring 11 and the inner peripheral surface 62 of the housing 61, and the gap between the fitted surface 23 of the inner ring 20 and the outer peripheral surface 72 of the rotating shaft 70. If it is slightly larger and press-fitted into these gaps, the movement of the outer ring 11 with respect to the housing 61 can be stopped and the movement of the inner ring 20 with respect to the rotation shaft 70 can be stopped. Creeping is suppressed.

ハウジング６１の内周面６２にはゴム製でリング状のＯリング８４が嵌め込まれ、Ｏリング８４は第１の内側端面６４、Ｃ面取り１４および内周面６２に当接する。Ｏリング８４の弾性力によって、外輪１１の他側端面がＣリング８０の第２の内側端面８１に当接し、外輪１１の一側端面および第１の突出部６３の第１の内側端面６４間に隙間が形成される。また、Ｏリング８４の弾性力およびＣ面取り１４によって、外輪１１はハウジング６１の内周面６２と同軸になるよう配置される。   A ring-shaped O-ring 84 made of rubber is fitted into the inner peripheral surface 62 of the housing 61, and the O-ring 84 contacts the first inner end surface 64, the C chamfer 14, and the inner peripheral surface 62. Due to the elastic force of the O-ring 84, the other end surface of the outer ring 11 abuts on the second inner end surface 81 of the C ring 80, and between the one end surface of the outer ring 11 and the first inner end surface 64 of the first protrusion 63. A gap is formed. Further, the outer ring 11 is arranged so as to be coaxial with the inner peripheral surface 62 of the housing 61 by the elastic force of the O-ring 84 and the C chamfer 14.

回転軸７０の外周面７２にはゴム製でリング状のＯリング８９が嵌め込まれ、Ｏリング８９は第１の内側端面７４、Ｃ面取り２４および外周面７２に当接する。Ｏリング８９の弾性力によって、内輪２０の他側端面がＣリング８５の第２の内側端面８６に当接し、内輪２０の一側端面および第１の突出部７３の第１の内側端面７４間に隙間が形成される。また、Ｏリング８９の弾性力およびＣ面取り２４によって、内輪２０は回転軸７０の外周面７２と同軸になるよう配置される。   A ring-shaped O-ring 89 made of rubber is fitted into the outer peripheral surface 72 of the rotating shaft 70, and the O-ring 89 abuts on the first inner end surface 74, the C chamfer 24 and the outer peripheral surface 72. Due to the elastic force of the O-ring 89, the other end surface of the inner ring 20 abuts on the second inner end surface 86 of the C ring 85, and between the one end surface of the inner ring 20 and the first inner end surface 74 of the first protrusion 73. A gap is formed. Further, the inner ring 20 is arranged to be coaxial with the outer peripheral surface 72 of the rotating shaft 70 by the elastic force of the O-ring 89 and the C chamfer 24.

前記Ｃ面取り１４、２４には、加工硬化処理が施され、加工硬化層１４ａ、２４ａが設けられている。図３は、加工硬化処理としてローレット加工を施した例であり、一対の係合テーパ２４の表面には、格子状の溝２４ｂが形成されている。この格子状の溝２４ｂにＯリング８９が喰い込むことによって、Ｏリング８９に対してＣ面取り２４が、軸方向および半径方向に不動不能となる。この格子状の溝２４ｂを形成することにより、溝２４ｂおよび溝２４ｂ間の山が硬くなり、加工硬化層２４ａが作られる。   The C chamfers 14 and 24 are subjected to a work hardening process, and work hardened layers 14a and 24a are provided. FIG. 3 shows an example in which knurl processing is performed as work hardening processing, and lattice-like grooves 24 b are formed on the surfaces of the pair of engagement tapers 24. When the O-ring 89 bites into the lattice-shaped grooves 24 b, the C chamfer 24 becomes immovable in the axial direction and the radial direction with respect to the O-ring 89. By forming the lattice-like grooves 24b, the peaks between the grooves 24b and the grooves 24b become hard, and the work hardened layer 24a is formed.

続いて、回転軸装置６０へ玉軸受１０を取付ける動作について説明する。   Subsequently, an operation of attaching the ball bearing 10 to the rotary shaft device 60 will be described.

まず外輪１１の被嵌合面１３に吸収被膜１５を貼り付け、内輪２０の被嵌合面２３に吸収被膜２５を貼り付ける。続いて、回転軸７０の外周面７２に、Ｏリング８９を第１の突出部７３の第１の内側端面７４に当接する位置まで嵌め込む。次に、回転軸７０の外周面７２に吸収被膜２５を圧縮させながら被嵌合面２３とともに吸収被膜２５を嵌め込み、Ｏリング８９に玉軸受１０の一対のＣ面取り２４の一方を面接触させる。回転軸７０の外周面７２にＣリング８５を嵌め込み、内輪２０の他側端面にＣリング８５の第２の内側端面８６を押し付ける。Ｏリング８９が圧縮され、Ｃリング８５が係合溝７５に対応する位置まで来ると、係合溝７５にＣリング８５が嵌め込まれる。内輪２０の他側端面にＣリング８５の第２の内側端面８６を押し付ける力を解除すると、Ｏリング８９の弾性力によって、内輪２０およびＣリング８５が押し戻され、係合溝７５の他側端面にＣリング８５が接触し、内輪２０およびＣリング８５のこれ以上の押し戻しが阻止される。Ｏリング８９の弾性力およびＣ面取り２４によって、内輪２０は回転軸７０の外周面７２と同軸になるよう配置される。   First, the absorbent coating 15 is applied to the fitted surface 13 of the outer ring 11, and the absorbent coating 25 is applied to the fitted surface 23 of the inner ring 20. Subsequently, the O-ring 89 is fitted into the outer peripheral surface 72 of the rotating shaft 70 to a position where it comes into contact with the first inner end surface 74 of the first protrusion 73. Next, the absorbing coating 25 is fitted together with the fitted surface 23 while compressing the absorbing coating 25 on the outer peripheral surface 72 of the rotating shaft 70, and one of the pair of C chamfers 24 of the ball bearing 10 is brought into surface contact with the O-ring 89. The C ring 85 is fitted into the outer peripheral surface 72 of the rotating shaft 70, and the second inner end surface 86 of the C ring 85 is pressed against the other end surface of the inner ring 20. When the O-ring 89 is compressed and the C-ring 85 reaches a position corresponding to the engaging groove 75, the C-ring 85 is fitted into the engaging groove 75. When the force that presses the second inner end face 86 of the C ring 85 against the other end face of the inner ring 20 is released, the inner ring 20 and the C ring 85 are pushed back by the elastic force of the O ring 89, and the other end face of the engagement groove 75. The C-ring 85 comes into contact with the inner ring 20 and further pushing back of the inner ring 20 and the C-ring 85 is prevented. The inner ring 20 is arranged so as to be coaxial with the outer peripheral surface 72 of the rotating shaft 70 by the elastic force of the O-ring 89 and the C chamfer 24.

続いてハウジング６１の内周面６２に、Ｏリング８４を第１の突出部６３の第１の内側端面６４に当接する位置まで嵌め込み、続いて吸収被膜１５を圧縮させながら被嵌合面１３とともに吸収被膜１５を嵌め込み、Ｏリング８４に玉軸受１０の一対のＣ面取り１４の一方を面接触させる。ハウジング６１の内周面６２にＣリング８０を嵌め込み、外輪１１の他側端面にＣリング８０の第２の内側端面８１を押し付ける。Ｏリング８４が圧縮され、Ｃリング８０が係合溝６５に対応する位置まで来ると、係合溝６５にＣリング８０が嵌め込まれる。外輪１１の他側端面にＣリング８０の第２の内側端面８１を押し付ける力を解除すると、Ｏリング８４の弾性力によって、外輪１１およびＣリング８０が押し戻され、係合溝６５の他側端面にＣリング８０が接触し、外輪１１およびＣリング８０のこれ以上の押し戻しが阻止される。Ｏリング８４の弾性力およびＣ面取り１４によって、外輪１１はハウジング６１の内周面６２と同軸になるよう配置される。   Subsequently, the O-ring 84 is fitted into the inner peripheral surface 62 of the housing 61 until it comes into contact with the first inner end face 64 of the first projecting portion 63, and then, together with the fitted surface 13 while compressing the absorbent coating 15. The absorption coating 15 is fitted, and one of the pair of C chamfers 14 of the ball bearing 10 is brought into surface contact with the O-ring 84. The C ring 80 is fitted into the inner peripheral surface 62 of the housing 61, and the second inner end surface 81 of the C ring 80 is pressed against the other end surface of the outer ring 11. When the O-ring 84 is compressed and the C-ring 80 reaches a position corresponding to the engaging groove 65, the C-ring 80 is fitted into the engaging groove 65. When the force for pressing the second inner end surface 81 of the C ring 80 against the other end surface of the outer ring 11 is released, the outer ring 11 and the C ring 80 are pushed back by the elastic force of the O ring 84, and the other end surface of the engagement groove 65. The C-ring 80 comes into contact with the outer ring 11 and further pushing back of the outer ring 11 and the C-ring 80 is prevented. The outer ring 11 is arranged to be coaxial with the inner peripheral surface 62 of the housing 61 by the elastic force of the O-ring 84 and the C chamfer 14.

Ｏリング８４、８９の弾性力およびＣ面取り１４、２４によって、外輪１１はハウジング６１の内周面６２と同軸になるよう配置され、内輪２０は回転軸７０の外周面７２と同軸になるよう配置されるようにするためには、吸収被膜１５、２５の圧縮量よりも、Ｏリング８４、８９の圧縮量を大きくするのが望ましい。   The outer ring 11 is arranged so as to be coaxial with the inner peripheral face 62 of the housing 61 and the inner ring 20 is arranged so as to be coaxial with the outer peripheral face 72 of the rotating shaft 70 by the elastic forces of the O-rings 84 and 89 and the C chamfers 14 and 24. In order to achieve this, it is desirable to make the compression amount of the O-rings 84 and 89 larger than the compression amount of the absorption coatings 15 and 25.

このようにして取付けられた回転軸７０を回転させると、ハウジング６１の内周面６２の軸線に対し、回転軸７０の軸線が同軸となっているため、回転軸７０の振れ回りが無く、外輪１１の外輪側軌道面１２、内輪２０の内輪側軌道面２２、および玉４０の転動面の摩耗が無い。また外部から回転軸装置６０に振動が作用しても、Ｏリング８４、９２はゴム製を使用しているので摩擦係数が高く、Ｏリング８４、９２およびＣ面取り１４、２４間の摩擦力によりハウジング６１に対して外輪１１が、軸方向および半径方向に移動不能に固定され、内輪２０に対して回転軸７０が、軸方向および半径方向に移動不能に固定されているので、フレッチングおよびクリープの発生が無い。またゴム製のＯリング８４、９２を使用しているので、外部から回転軸装置６０に作用する振動により回転軸７０が軸方向に振動しても、この振動を吸収し、フレッチングの発生を抑えることができる。   When the rotating shaft 70 attached in this way is rotated, the axis of the rotating shaft 70 is coaxial with the axis of the inner peripheral surface 62 of the housing 61. 11, the outer race side raceway surface 12, the inner race 20 inner race side raceway surface 22, and the rolling surface of the ball 40 are not worn. Even if vibration is applied to the rotary shaft device 60 from the outside, since the O-rings 84 and 92 are made of rubber, the friction coefficient is high, and the frictional force between the O-rings 84 and 92 and the C chamfers 14 and 24 Since the outer ring 11 is fixed to the housing 61 so as not to move in the axial direction and the radial direction, and the rotary shaft 70 is fixed to the inner ring 20 so as not to move in the axial direction and the radial direction, fretting and creep are prevented. There is no occurrence. Further, since the rubber O-rings 84 and 92 are used, even if the rotary shaft 70 vibrates in the axial direction due to the vibration acting on the rotary shaft device 60 from the outside, this vibration is absorbed and the occurrence of fretting is suppressed. be able to.

さらに、Ｃ面取り１４、２４には、ローレット加工が施され、これによってできた格子状の溝２４ｂにＯリング８４、８９が喰い込むことによって、ハウジング６１に対して外輪１１が、軸方向および半径方向により一層移動不能に固定され、内輪２０に対して回転軸７０が、軸方向および半径方向により一層移動不能に固定され、フレッチングおよびクリープの発生がより一層無い。溝２４ｂの形成により、Ｃ面取り１４、２４の表面が加工硬化し、外部から回転軸装置６０に振動が作用しても、摩耗しにくい効果が多少ある。   Further, the C chamfers 14 and 24 are knurled, and the O-rings 84 and 89 bite into the lattice-like grooves 24 b formed thereby, so that the outer ring 11 is axially and radially displaced from the housing 61. The rotation shaft 70 is fixed to the inner ring 20 so as to be immovable further depending on the direction, and is further immovably fixed to the inner ring 20 in the axial direction and the radial direction, so that fretting and creep are further prevented. Due to the formation of the groove 24b, the surfaces of the C chamfers 14, 24 are work-hardened, and even if vibration is applied to the rotary shaft device 60 from the outside, there is an effect that it is difficult to wear.

上述した実施形態は、一つの玉軸受１０でハウジング６１に対する回転軸７０の軸方向位置を拘束した例について述べた。この場合、玉軸受１０と共に図略の針状ころ軸受が使用され、この針状ころ軸受と共に玉軸受１０によりハウジング６１に対し回転軸７０を回転可能に軸支するのが一般的である。   In the embodiment described above, the example in which the position of the rotating shaft 70 in the axial direction with respect to the housing 61 is restricted by the single ball bearing 10 has been described. In this case, a needle roller bearing (not shown) is used together with the ball bearing 10, and the rotation shaft 70 is generally rotatably supported with respect to the housing 61 by the ball bearing 10 together with the needle roller bearing.

他の実施形態として、図５に示すように、一対の玉軸受５０、５５でハウジング９０に対する回転軸９５の軸方向位置を拘束する例について述べる。   As another embodiment, an example in which the axial position of the rotating shaft 95 with respect to the housing 90 is restrained by a pair of ball bearings 50 and 55 as shown in FIG. 5 will be described.

玉軸受５０、５５は、リング状の外輪５１、５６と、外輪５１、５６の内周側に配置されるリング状の内輪５２、５７と、外輪５１、５６と内輪５２、５７間に配置されるリング状の保持器５３、５８と、保持器５３、５８に保持される複数の玉５４、５９とからなっている。外輪５１の外周には、軸方向の両端の外縁で一対のＣ面取り５１ａが形成されている。保持器５３、５８は円周方向に複数のポケット部を有し、各ポケット部に玉５４、５９が回転可能に保持されている。前記玉５４、５９は、金属製で、球形状を有し、外面が転動面となる。   The ball bearings 50 and 55 are disposed between the ring-shaped outer rings 51 and 56, the ring-shaped inner rings 52 and 57 disposed on the inner peripheral side of the outer rings 51 and 56, and the outer rings 51 and 56 and the inner rings 52 and 57. Ring-shaped cages 53 and 58, and a plurality of balls 54 and 59 held by the cages 53 and 58. On the outer periphery of the outer ring 51, a pair of C chamfers 51a are formed at outer edges at both ends in the axial direction. The cages 53 and 58 have a plurality of pocket portions in the circumferential direction, and balls 54 and 59 are rotatably held in the respective pocket portions. The balls 54 and 59 are made of metal and have a spherical shape, and the outer surface is a rolling surface.

前記ハウジング９０には、回転軸９５の回転軸線と同軸に円筒状の内周面９１が形成され、この内周面９１は、外輪５１が径方向に僅かな隙間を持って嵌合できるような内径を有する。内周面９１には玉軸受５０の一側端面へ突出した第１の突出部９２が形成され、この第１の突出部９２は外輪５１の一側端面と対向する第１の内側端面９２ａを有する。また内周面９１には、玉軸受５５の他側端面に対応する位置に係合溝９３が形成され、この係合溝９３にはＣリング９４が嵌め込まれている。Ｃリング９４は外輪５６の他側端面に当接する第２の内側端面９４ａを有する。Ｃリング９４は、図３の状態よりもさらに外径方向に拡張しようとする弾性力を有する。   The housing 90 is formed with a cylindrical inner peripheral surface 91 coaxially with the rotational axis of the rotary shaft 95, and the inner peripheral surface 91 can be fitted to the outer ring 51 with a slight gap in the radial direction. Has an inner diameter. The inner peripheral surface 91 is formed with a first protrusion 92 that protrudes to one end surface of the ball bearing 50, and the first protrusion 92 has a first inner end surface 92 a that faces the one end surface of the outer ring 51. Have. An engagement groove 93 is formed in the inner peripheral surface 91 at a position corresponding to the other end surface of the ball bearing 55, and a C ring 94 is fitted in the engagement groove 93. The C ring 94 has a second inner end surface 94 a that abuts on the other end surface of the outer ring 56. The C-ring 94 has an elastic force to expand further in the outer diameter direction than in the state of FIG.

前記回転軸９５には、これの回転軸線と同軸に円筒状の外周面９６が形成され、この外周面９６は、内輪５２が径方向に僅かな隙間を持って嵌合できるような外径を有する。外周面９６には玉軸受５０の他側端面へ突出した第２の突出部９７が形成され、この第２の突出部９７は内輪５２の他側端面と接触する第２の内側端面９７ａを有する。また外周面９６には玉軸受５１の一側端面へ突出した第１の突出部９８が形成され、この第１の突出部９８は内輪５７の一側端面と接触する第１の内側端面９８ａを有する。   The rotary shaft 95 is formed with a cylindrical outer peripheral surface 96 coaxially with the rotation axis thereof, and the outer peripheral surface 96 has an outer diameter that allows the inner ring 52 to be fitted with a slight gap in the radial direction. Have. A second projecting portion 97 projecting to the other end surface of the ball bearing 50 is formed on the outer peripheral surface 96, and the second projecting portion 97 has a second inner end surface 97 a that contacts the other end surface of the inner ring 52. . The outer peripheral surface 96 is formed with a first projecting portion 98 projecting to one end surface of the ball bearing 51, and the first projecting portion 98 has a first inner end surface 98 a in contact with one end surface of the inner ring 57. Have.

前記外輪５１、５６の外周および前記内輪５２、５７の内周には、樹脂製の吸収被膜５１ｃ、５６ｃ、５２ｃ、５７ｃが固着されている。吸収被膜５１ｃ、５６ｃ、５２ｃ、５７ｃは、例えばナイロン６６等のように外輪５１、５６および内輪５２、５７よりも軟らかい材料が用いられる。吸収被膜５１ｃ、５６ｃ、５２ｃ、５７ｃは、粘着系の接着剤によって外輪５１、５６の外周および前記内輪５２、５７の内周に貼り付けられる。前記粘着系の接着剤は、時間の経過とともに硬化するタイプのものが望ましい。吸収被膜５１ｃ、５６ｃは、外輪５１、５６の外周およびハウジング９０の内周面９１間の隙間を埋める程度の肉厚を有し、吸収被膜５２ｃ、５７ｃは、内輪５２、５７の内周および回転軸９５の外周面９６間の隙間を埋める程度の肉厚を有する。   Resin-made absorption coatings 51c, 56c, 52c, and 57c are fixed to the outer periphery of the outer rings 51 and 56 and the inner periphery of the inner rings 52 and 57, respectively. For the absorbent coatings 51c, 56c, 52c, and 57c, a material softer than the outer rings 51 and 56 and the inner rings 52 and 57, such as nylon 66, is used. The absorption coatings 51c, 56c, 52c, and 57c are attached to the outer periphery of the outer rings 51 and 56 and the inner periphery of the inner rings 52 and 57 by an adhesive adhesive. The pressure-sensitive adhesive is preferably of a type that cures over time. The absorption coatings 51c and 56c have a thickness sufficient to fill the gap between the outer periphery of the outer rings 51 and 56 and the inner peripheral surface 91 of the housing 90. The absorption coatings 52c and 57c are the inner periphery and rotation of the inner rings 52 and 57. It has a thickness sufficient to fill a gap between the outer peripheral surfaces 96 of the shaft 95.

吸収被膜５１ｃ、５６ｃ、５２ｃ、５７ｃは、内輪５２、５７の軸線方向に幅を有するので、後述するＯリング９９単独に比べて、外輪５１、５６はハウジング９０の内周面９１と同軸になるよう配置されやすくなり、内輪５２、５７は回転軸９５の外周面９６と同軸になるよう配置されやすくなる。吸収被膜５１ｃ、５６ｃ、５２ｃ、５７ｃの肉厚を、外輪５１、５６の外周およびハウジング９０の内周面９１間の隙間、内輪５２、５７の内周および回転軸９５の外周面９６間の隙間よりも若干大きくしてこれらの隙間へ圧入すれば、ハウジング９０に対し外輪５１、５６が回転しようとする動きを止めることができ、回転軸９５に対し内輪５２、５７が回転しようとする動きを止めることができ、クリープの発生が抑えられる。   Since the absorption coatings 51 c, 56 c, 52 c, 57 c have a width in the axial direction of the inner rings 52, 57, the outer rings 51, 56 are coaxial with the inner peripheral surface 91 of the housing 90 compared to an O-ring 99 alone described later. The inner rings 52 and 57 are easily arranged so as to be coaxial with the outer peripheral surface 96 of the rotating shaft 95. The thickness of the absorption coatings 51c, 56c, 52c, and 57c is set so that the clearance between the outer periphery of the outer rings 51 and 56 and the inner peripheral surface 91 of the housing 90, the inner periphery of the inner rings 52 and 57, and the outer peripheral surface 96 of the rotary shaft 95 is reduced. If the outer rings 51 and 56 are pressed into these gaps slightly larger than the outer ring 51 and 56, the movement of the outer rings 51 and 56 to rotate with respect to the housing 90 can be stopped, and the movement of the inner rings 52 and 57 to rotate with respect to the rotation shaft 95 can be stopped. It can be stopped and the occurrence of creep is suppressed.

ハウジング９０の内周面９１にはゴム製でリング状のＯリング９９が嵌め込まれ、Ｏリング９９は第１の内側端面９２ａ、Ｃ面取り５１ａおよび内周面９１に当接する。Ｏリング９９の弾性力によって、内輪５２の他側端面が第２の突出部９７の第２の内側端面９７ａに当接し、第１の突出部９８の第１の内側端面９８ａが内輪５７の一側端面に当接し、外輪５６の他側端面がＣリング９４の第２の内側端面９４ａに当接し、外輪５１の一側端面および第１の突出部９２の第１の内側端面９２ａ間に隙間が形成される。また、Ｏリング９９の弾性力およびＣ面取り５１ａによって、外輪５１はハウジング９０の内周面９１と同軸になるよう配置される。   A ring-shaped O-ring 99 made of rubber is fitted into the inner peripheral surface 91 of the housing 90, and the O-ring 99 abuts on the first inner end surface 92 a, the C chamfer 51 a and the inner peripheral surface 91. Due to the elastic force of the O-ring 99, the other end surface of the inner ring 52 abuts on the second inner end surface 97 a of the second projecting portion 97, and the first inner end surface 98 a of the first projecting portion 98 is one of the inner rings 57. Abutting on the side end face, the other end face of the outer ring 56 abuts on the second inner end face 94a of the C ring 94, and a gap between the one end face of the outer ring 51 and the first inner end face 92a of the first protrusion 92. Is formed. Further, the outer ring 51 is arranged to be coaxial with the inner peripheral surface 91 of the housing 90 by the elastic force of the O-ring 99 and the C chamfer 51a.

外輪５１、玉５４を介して内輪５２が、ハウジング９０の内周面９１に対し同軸に配置されるので、外輪５１、内輪５２の軌道面、玉５４の転動面の摩耗が少ない。吸収被膜５２ｃによって、内輪５２に対し回転軸９５ができるだけ同軸に配置されるので、回転軸９５の振れ回りが少なくなって外輪５１、内輪５２の軌道面、玉５４の転動面への摩耗の影響を少なくできる。Ｏリング９９はゴム製を使用しているので摩擦係数が高く、Ｏリング９９およびＣ面取り５１ａ間の摩擦力によりハウジング９０に対して外輪５１が、軸方向および半径方向に移動不能に固定され、内輪５２に対して回転軸９５が、軸方向および半径方向に移動不能に固定されているので、フレッチングおよびクリープの発生が無い。またゴム製のＯリング９９を使用しているので、外部から回転軸装置に作用する振動により回転軸９５が軸方向に振動しても、この振動を吸収し、フレッチングの発生を抑えることができる。   Since the inner ring 52 is disposed coaxially with the inner peripheral surface 91 of the housing 90 via the outer ring 51 and the ball 54, the outer ring 51, the raceway surface of the inner ring 52, and the rolling surface of the ball 54 are less worn. Since the rotation shaft 95 is arranged as coaxially as possible with respect to the inner ring 52 by the absorption coating 52c, the swinging of the rotation shaft 95 is reduced, and the outer ring 51, the raceway surface of the inner ring 52, and the wear surface on the rolling surface of the ball 54 are reduced. The influence can be reduced. Since the O-ring 99 is made of rubber, the friction coefficient is high, and the outer ring 51 is fixed to the housing 90 so as to be immovable in the axial direction and the radial direction by the frictional force between the O-ring 99 and the C chamfer 51a. Since the rotation shaft 95 is fixed so as not to move in the axial direction and the radial direction with respect to the inner ring 52, fretting and creep do not occur. Further, since the rubber O-ring 99 is used, even if the rotating shaft 95 vibrates in the axial direction due to vibrations acting on the rotating shaft device from the outside, this vibration can be absorbed and occurrence of fretting can be suppressed. .

前記Ｃ面取り５１ａには、加工硬化処理が施され、加工硬化層５１ｂが設けられている。加工硬化処理として図３に示すようなローレット加工を施しても良いし、図４に示すようなショットピーニング加工を施しても良い。加工硬化層５１ｂによって、Ｃ面取り５１ａの摩耗が抑えられる。   The C chamfer 51a is subjected to a work hardening process, and a work hardened layer 51b is provided. As the work hardening process, a knurling process as shown in FIG. 3 may be performed, or a shot peening process as shown in FIG. 4 may be performed. The work hardened layer 51b suppresses the wear of the C chamfer 51a.

本発明はこうした実施形態に何等限定されるものではなく、本発明の要旨を逸脱しない範囲において、種々なる態様で実施し得ることは勿論である。   The present invention is not limited to these embodiments, and can of course be implemented in various modes without departing from the gist of the present invention.

一番最初に述べた実施形態は、外輪１１および内輪２０の両方にＯリング８４、９２を用いた例について述べた。他の実施形態として、内輪２０のみＯリング８９を用いても良いし、外輪１１のみＯリング８４を用いても良い。   In the first embodiment, an example in which O-rings 84 and 92 are used for both the outer ring 11 and the inner ring 20 has been described. As another embodiment, the O-ring 89 may be used only for the inner ring 20, or the O-ring 84 may be used only for the outer ring 11.

一番最初に述べた実施形態は、Ｃ面取り１４、２４に、ローレット加工を施した例について述べた。他の実施形態として、Ｃ面取り１４、２４にショットピーニング加工を施しても良い。この場合、図４に示すように、Ｃ面取り２４の表面に細かい窪み２４ｃが多数形成される。窪み２４ｃにＯリング８４、８９が喰い込むことによって、Ｏリング８４、８９に対してＣ面取り１４、２４が、軸方向および半径方向に不動不能となる効果も少なからずあるが、窪み２４ｃを形成することにより、一対の係合テーパ１４、２４の表面が加工硬化し、外部から回転軸装置６０に振動が作用しても、摩耗しにくい効果の方が大きい。   In the first embodiment, the example in which the C chamfers 14 and 24 are knurled is described. As another embodiment, the C chamfers 14 and 24 may be subjected to shot peening. In this case, as shown in FIG. 4, many fine recesses 24 c are formed on the surface of the C chamfer 24. Although the O-rings 84 and 89 bite into the recesses 24c, the C chamfers 14 and 24 with respect to the O-rings 84 and 89 have an effect of being immovable in the axial direction and the radial direction, but the recesses 24c are formed. As a result, the surface of the pair of engagement tapers 14 and 24 is work-hardened, and even when vibration is applied to the rotary shaft device 60 from the outside, the effect of being less likely to be worn is greater.

一番最初に述べた実施形態は、外輪１１および内輪２０の両方にテーパ状のＣ面取り１４、２４を形成した例について述べた。他の実施形態として、外輪１１および内輪２０の両方にＲ形状のＲ面取りを形成しても良い。   In the first embodiment, an example in which tapered C chamfers 14 and 24 are formed on both the outer ring 11 and the inner ring 20 has been described. As another embodiment, an R-shaped R chamfer may be formed on both the outer ring 11 and the inner ring 20.

上述した実施形態は、玉軸受１０に上述した取付け構造を適用した。他の実施形態として、円すいころ軸受、円筒ころ軸受等の他の軸受にも、上述した取付け構造を適用しても良い。   In the embodiment described above, the mounting structure described above is applied to the ball bearing 10. As another embodiment, the mounting structure described above may be applied to other bearings such as a tapered roller bearing and a cylindrical roller bearing.

１０：玉軸受（転がり軸受）、１１：外輪、１４：Ｃ面取り、１４ａ：加工硬化層、２０：内輪、２４：Ｃ面取り、２４ａ：加工硬化層、４０：玉（転動体）、６０：回転軸装置、６１：ハウジング、６３：第１の突出部、６５：係合溝、７０：回転軸、７３：第１の突出部、７５：係合溝、８０：Ｃリング（第２の突出部）、８４：Ｏリング（弾性部材）、８５：Ｃリング（第２の突出部）、８９：Ｏリング（弾性部材）   10: Ball bearing (rolling bearing), 11: Outer ring, 14: C chamfer, 14a: Work hardened layer, 20: Inner ring, 24: C chamfer, 24a: Work hardened layer, 40: Ball (rolling element), 60: Rotation Shaft device, 61: housing, 63: first protrusion, 65: engagement groove, 70: rotating shaft, 73: first protrusion, 75: engagement groove, 80: C ring (second protrusion) ), 84: O-ring (elastic member), 85: C-ring (second protrusion), 89: O-ring (elastic member)

Claims (3)

ハウジングに転がり軸受を介して回転軸を回転可能に軸支した回転軸装置において、内輪、外輪、転動体とからなる前記転がり軸受を、前記回転軸および前記ハウジングの少なくともどちらか一方に取付けるための転がり軸受の取付け構造であって、前記内輪の一側端面および前記外輪の一側端面の少なくともどちらか一方に当接可能な第１の突出部を、前記回転軸および前記ハウジングの少なくともどちらか一方に形成し、前記内輪の他側端面および前記外輪の他側端面の少なくともどちらか一方に当接可能な第２の突出部を、前記回転軸および前記ハウジングの少なくともどちらか一方に設け、前記内輪の一側端面の内縁および前記外輪の一側端面の外縁の少なくともどちらか一方に面取りを形成し、前記第１の突出部および面取り間にゴム製のリング状の弾性部材を介挿するとともにこの弾性部材を回転軸およびハウジングの少なくともどちらか一方に当接させ、前記面取りに加工硬化処理を施すことにより加工硬化層を設けたことを特徴とする回転軸装置における転がり軸受の取付け構造。   In a rotating shaft device in which a rotating shaft is rotatably supported by a housing via a rolling bearing, the rolling bearing including an inner ring, an outer ring, and a rolling element is attached to at least one of the rotating shaft and the housing. A rolling bearing mounting structure, wherein a first projecting portion capable of contacting at least one of one end face of the inner ring and one end face of the outer ring is provided with at least one of the rotating shaft and the housing. A second projecting portion formed on the inner ring and capable of contacting at least one of the other end surface of the inner ring and the other end surface of the outer ring is provided on at least one of the rotating shaft and the housing; Forming a chamfer on at least one of an inner edge of the one end face and an outer edge of the one end face of the outer ring, and between the first protrusion and the chamfer A ring-shaped elastic member made of rubber is inserted, and the elastic member is brought into contact with at least one of the rotating shaft and the housing, and a work hardening layer is provided by subjecting the chamfer to a work hardening treatment. The mounting structure of the rolling bearing in the rotary shaft device. 前記加工硬化処理は、ローレット加工であることを特徴とする請求項１に記載の回転軸装置における転がり軸受の取付け構造。   The rolling bearing mounting structure in the rotary shaft device according to claim 1, wherein the work hardening process is a knurling process. 前記加工硬化処理は、ショットピーニング加工であることを特徴とする請求項１に記載の回転軸装置における転がり軸受の取付け構造。   The structure for mounting a rolling bearing in a rotary shaft device according to claim 1, wherein the work hardening process is a shot peening process.
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