JP2006336752A - Assembling method of self-aligning roller bearing - Google Patents

Assembling method of self-aligning roller bearing Download PDF

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JP2006336752A
JP2006336752A JP2005162204A JP2005162204A JP2006336752A JP 2006336752 A JP2006336752 A JP 2006336752A JP 2005162204 A JP2005162204 A JP 2005162204A JP 2005162204 A JP2005162204 A JP 2005162204A JP 2006336752 A JP2006336752 A JP 2006336752A
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outer ring
inner ring
assembly
roller bearing
self
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JP4788200B2 (en
JP2006336752A5 (en
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Hisakazu Tadokoro
久和 田所
Yoshiro Ide
義郎 井手
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NSK Ltd
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NSK Ltd
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00Assembling bearings
    • F16C43/04Assembling rolling-contact bearings
    • F16C43/06Placing rolling bodies in cages or bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings 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
    • F16C19/34Bearings 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
    • F16C19/38Bearings 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06Ball or roller bearings
    • F16C23/08Ball or roller bearings self-adjusting
    • F16C23/082Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements

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

Abstract

<P>PROBLEM TO BE SOLVED: To automatically assemble various types of self-aligning roller bearings by suppressing a maximum tensile stress occurring in an outer ring 2 by deforming the outer ring 2 in an elliptic shape so that the elastically deformed amount of the outer ring 2 can be increased and deforming the outer ring 2 in the elliptic shape to increase an area allowing an inserting operation. <P>SOLUTION: The outer peripheral surface of the outer ring 2 is inwardly pressed at two positions on one side and two positions on the opposite side totaling four positions in the diameter direction by the tip faces 15, 15 of a pair of pressing tools 14, 14 disposed in the opposed state to each other through the outer ring 2. Abutting positions between the tip faces 15, 15 of these pressing tools 14, 14 and the outer peripheral surface of the outer ring 2 are set at portions displaced by 15 to 30° from the pressing center of the outer ring 2 by the pressing tools 14, 14 to both sides thereof in the circumferential direction. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、各種機械装置に組み込まれ、例えばハウジングの内側に回転軸を支承する、自動調心ころ軸受の組立方法の改良に関する。   The present invention relates to an improvement in an assembling method of a self-aligning roller bearing that is incorporated in various mechanical devices and supports a rotating shaft inside a housing, for example.

例えば重量の嵩む軸をハウジングの内側に回転自在に支承する為に従来から、特許文献1に記載された様な自動調心ころ軸受が使用されている。図7〜8は、この特許文献1に記載される等により、従来から広く知られている自動調心ころ軸受1を示している。この自動調心ころ軸受1は、互いに同心に組み合わされた外輪2と内輪3との間に、複数の球面ころ4、4を転動自在に配列して成る。そして、1対の保持器5、5により、これら複数の球面ころ4、4の分離防止を図っている。   For example, a self-aligning roller bearing as described in Patent Document 1 has been conventionally used to rotatably support a heavy shaft inside a housing. 7 to 8 show a self-aligning roller bearing 1 that has been widely known in the past, as described in Patent Document 1. The self-aligning roller bearing 1 includes a plurality of spherical rollers 4 and 4 arranged in a freely rollable manner between an outer ring 2 and an inner ring 3 that are concentrically combined with each other. A pair of cages 5 and 5 prevent separation of the plurality of spherical rollers 4 and 4.

上記外輪2の内周面には、単一の中心を有する球状凹面である外輪軌道6を形成している。又、内輪3の外周面の幅方向(図7の左右方向)両側には、それぞれが上記外輪軌道6と対向する、1対の内輪軌道7、7を形成している。又、上記複数の球面ころ4、4は、その最大径部が各球面ころ4、4の軸方向長さの中央部にある対称形で、上記外輪軌道6と上記1対の内輪軌道7、7との間に、2列に亙って転動自在に配列されている。   An outer ring raceway 6 that is a spherical concave surface having a single center is formed on the inner peripheral surface of the outer ring 2. Further, a pair of inner ring raceways 7 and 7 are formed on both sides of the outer circumferential surface of the inner ring 3 in the width direction (left and right direction in FIG. 7). The plurality of spherical rollers 4 and 4 have a symmetrical shape in which the maximum diameter portion is at the center of the axial length of each spherical roller 4 and 4, and the outer ring raceway 6 and the pair of inner ring raceways 7, 7 is arranged so as to be freely rollable in two rows.

上記両保持器5、5は、円すい筒状の主部8に、これら各球面ころ4、4をそれぞれ転動自在に保持する複数のポケット9を、円周方向に亙って等間隔に形成している。上記主部8は、上記各球面ころ4、4のピッチ円直径よりも径方向内側に配置しており、この主部8の円周方向に関する上記各ポケット9の幅は、上記各球面ころ4、4の外径よりも小さくしている。従って、これら各ポケット9内に保持されたこれら各球面ころ4、4が、上記両保持器5、5の内径側に抜け出る事はない。又、上記主部8の大径側端縁部に外向フランジ部10を、上記金属板を径方向外方に折り曲げる事により形成している。そして、この外向フランジ部10の内周縁部で上記各ポケット9の円周方向中間部に相当する位置に、それぞれ径方向内方に突出する状態で形成した弾性舌片11を、上記各球面ころ4、4の軸方向両端面の中央部にそれぞれ形成した円形の凹部12に係合させている。これら弾性舌片11と凹部12との係合により、上記各ポケット9内に上記各球面ころ4、4を、上記主部8の径方向外側から組み込めるが、一度組み込んだ後の状態では、これら各球面ころ4、4が、上記両保持器5、5の外径側に抜け出ない様にしている。   In both the cages 5 and 5, a plurality of pockets 9 for holding the spherical rollers 4 and 4 so as to be freely rollable are formed at equal intervals in the circumferential direction in a conical cylindrical main portion 8. is doing. The main portion 8 is disposed radially inside the pitch circle diameter of the spherical rollers 4 and 4, and the width of the pockets 9 in the circumferential direction of the main portion 8 is set so that the spherical rollers 4 4 is smaller than the outer diameter. Therefore, the spherical rollers 4 and 4 held in the pockets 9 do not come out to the inner diameter side of the cages 5 and 5. Further, an outward flange portion 10 is formed at the large-diameter end edge portion of the main portion 8, and the metal plate is bent outward in the radial direction. And the elastic tongue piece 11 formed in the state which protrudes radially inward in the position equivalent to the circumferential direction intermediate part of each said pocket 9 in the inner peripheral part of this outward flange part 10 is each said spherical roller. 4, 4 and 4 are engaged with circular recesses 12 formed at the center of both end faces in the axial direction. Due to the engagement between the elastic tongue 11 and the recess 12, the spherical rollers 4, 4 can be incorporated into the pockets 9 from the outside in the radial direction of the main portion 8. The spherical rollers 4 and 4 are prevented from coming out to the outer diameter side of the cages 5 and 5.

上述の様に構成される自動調心ころ軸受1により、例えばハウジングの内側に回転軸を支承する場合、外輪2をハウジングに内嵌固定し、内輪3を回転軸に外嵌固定する。回転軸と共にこの内輪3が回転する場合には、複数の球面ころ4、4が転動して、この回転を許容する。ハウジングの軸心と回転軸の軸心とが不一致の場合、上記外輪2の内側で上記内輪3が調心する(外輪2の中心軸に対し内輪3の中心軸を傾斜させる)事で、この不一致を補償する。この場合に於いて、外輪軌道6は単一球面状に形成されている為、上記複数の球面ころ4、4の転動は、不一致補償後に於いても、円滑に行なわれる。   For example, when the rotating shaft is supported inside the housing by the self-aligning roller bearing 1 configured as described above, the outer ring 2 is fitted and fixed to the housing, and the inner ring 3 is fitted and fixed to the rotating shaft. When the inner ring 3 rotates together with the rotation shaft, the plurality of spherical rollers 4 and 4 roll to allow this rotation. If the shaft center of the housing and the shaft center of the rotary shaft do not match, the inner ring 3 is aligned inside the outer ring 2 (the central axis of the inner ring 3 is inclined with respect to the central axis of the outer ring 2). Compensate for discrepancies. In this case, since the outer ring raceway 6 is formed in a single spherical shape, the rolling of the plurality of spherical rollers 4 and 4 is performed smoothly even after the mismatch compensation.

上述の様に構成され作用する自動調心ころ軸受1を組み立てる工程に就いては、例えば特許文献2に記載されている。この自動調心ころ軸受1を組み立てる場合には、先ず、図9に示す様な内輪組立体13を、外輪2の外で組み立てる。この内輪組立体13は、内輪3の周囲に複数の球面ころ4、4を、1対の保持器5、5と共に組み付けて成る。この様な内輪組立体13の外径D13は、上記外輪2の開口部の内径R2 よりも大きい(D13>R2 )為、そのままではこの外輪2の内側に挿入できない。そこで、上記特許文献2に記載されている様に、図10に示す如く、上記外輪2を直径方向反対側から径方向内方に押圧して、この外輪2を楕円形に弾性変形させ、この楕円形の長径を上記内輪組立体13の外径よりも大きくする。そして、この状態で、図9〜10に示す様に、この内輪組立体13を上記外輪2の内側に、この内輪組立体13の中心軸O13とこの外輪2の中心軸O2 とを実質的に直交させた状態で、外輪軌道6の曲率中心がこの内輪組立体13の中心軸O13上に位置する状態にまで挿入する。挿入後、この外輪2を径方向反対側から押圧している力を解除し、この外輪2を円形に復元させる。 The process of assembling the self-aligning roller bearing 1 configured and acting as described above is described in Patent Document 2, for example. When the self-aligning roller bearing 1 is assembled, first, an inner ring assembly 13 as shown in FIG. 9 is assembled outside the outer ring 2. The inner ring assembly 13 is formed by assembling a plurality of spherical rollers 4 and 4 together with a pair of cages 5 and 5 around the inner ring 3. Since the outer diameter D 13 of such an inner ring assembly 13 is larger than the inner diameter R 2 of the opening of the outer ring 2 (D 13 > R 2 ), it cannot be inserted inside the outer ring 2 as it is. Therefore, as described in Patent Document 2, as shown in FIG. 10, the outer ring 2 is pressed radially inward from the opposite side in the diametrical direction to elastically deform the outer ring 2 into an elliptical shape. The major axis of the ellipse is made larger than the outer diameter of the inner ring assembly 13. Then, substantially in this state, as shown in FIG. 9-10, the inner ring assembly 13 to the inside of the outer ring 2, the the central axis O 13 of the inner ring assembly 13 and the central axis O 2 of the outer ring 2 In such a state, the center of curvature of the outer ring raceway 6 is inserted so as to be located on the central axis O 13 of the inner ring assembly 13. After the insertion, the force pressing the outer ring 2 from the opposite side in the radial direction is released, and the outer ring 2 is restored to a circular shape.

上述の様にして、上記外輪2内に上記内輪組立体13を、これら外輪2と内輪組立体13との中心軸O2 、O13同士が上記外輪軌道6の曲率中心上で、実質的に直交する状態にまで挿入する挿入作業を行なった後、これら両中心軸O2 、O13同士を一致させる、所謂返し作業と呼ばれる組み込み作業を行なう。即ち、上記内輪組立体13を、この内輪組立体13及び上記外輪2の直径方向を中心に実質的に90度揺動させる。そして、前述の図7〜8に示した如く、上記内輪組立体13を上記外輪2の内側に組み込む。この様な返し作業の手順に就いては、例えば特許文献3に記載されている。 As described above, the inner ring assembly 13 is placed in the outer ring 2 , and the central axes O 2 and O 13 of the outer ring 2 and the inner ring assembly 13 are substantially on the center of curvature of the outer ring raceway 6. After performing an insertion operation for inserting the rods into an orthogonal state, an assembling operation called a so-called return operation is performed in which both the central axes O 2 and O 13 coincide with each other. That is, the inner ring assembly 13 is swung substantially 90 degrees around the diameter direction of the inner ring assembly 13 and the outer ring 2. Then, as shown in FIGS. 7 to 8 described above, the inner ring assembly 13 is assembled inside the outer ring 2. Such a return work procedure is described in Patent Document 3, for example.

上記特許文献2に記載された従来方法の場合、上記外輪2を楕円形に弾性変形させる為、上記図10に示す様に、この外輪2の直径方向反対側2個所位置を、互いに近付く方向に強く押圧している。この様にしてこの外輪2を楕円形に変形させる場合、この外輪2の一部に大きな引っ張り応力が発生する。そして、この引っ張り応力を、この外輪2に亀裂等の損傷を発生させない程度の値に抑える為には、この外輪2の弾性変形量を少なく抑える必要がある。従って、例えば、この外輪2の軸方向の幅寸法が大きい等、この外輪2の寸法・形状によっては、上記図10に示す様な組立方法を採用できない。この様な場合には、前記両保持器5、5に設けた各ポケット9、9のうちの一部のポケットに球面ころを組み込まずに上記外輪2の内側に上記内輪組立体13を挿入した後、この内輪組立体13を少し回転させてから、上記一部のポケット内に球面ころを組み込む。但し、この様な作業を採用した場合には、自動調心ころ軸受の組立作業の自動化を図れない(前記挿入作業を手作業で行なう必要がある)。   In the case of the conventional method described in the above-mentioned Patent Document 2, in order to elastically deform the outer ring 2 into an elliptical shape, as shown in FIG. Pressing strongly. When the outer ring 2 is deformed into an elliptical shape in this way, a large tensile stress is generated in a part of the outer ring 2. In order to suppress the tensile stress to a value that does not cause damage such as cracks in the outer ring 2, it is necessary to reduce the amount of elastic deformation of the outer ring 2. Therefore, for example, depending on the size and shape of the outer ring 2 such as the axial width of the outer ring 2 being large, the assembling method as shown in FIG. 10 cannot be adopted. In such a case, the inner ring assembly 13 is inserted inside the outer ring 2 without incorporating spherical rollers in some of the pockets 9 and 9 provided in the cages 5 and 5. Thereafter, the inner ring assembly 13 is slightly rotated, and then the spherical rollers are assembled into the partial pockets. However, when such an operation is employed, the assembly operation of the self-aligning roller bearing cannot be automated (the insertion operation needs to be performed manually).

特許文献4には、単列深溝型の玉軸受を構成する玉の数を多くすべく、外輪を弾性変形させつつ玉の組み込みを行なう際に、この外輪の直径方向反対側2個所位置ずつを、互いに近付く方向に押圧する技術が記載されている。但し、この様な特許文献4に記載された従来技術は、互いに偏心した状態で配置された内輪の外周面と外輪の内周面との間の空間の一部で上記玉を挿入可能な部分の周方向長さを確保する事を意図したもので、本発明の対象となる自動調心ころ軸受の組立方法とは基本的に異なる。   In Patent Document 4, in order to increase the number of balls constituting a single-row deep groove type ball bearing, when the balls are assembled while elastically deforming the outer ring, two positions on the opposite side in the diameter direction of the outer ring are set. A technique for pressing in directions toward each other is described. However, in the prior art described in Patent Document 4, such a ball can be inserted into a part of the space between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring arranged in an eccentric state. This is intended to ensure the circumferential length of the roller and is basically different from the assembly method of the self-aligning roller bearing which is the subject of the present invention.

特許第3529191号公報Japanese Patent No. 3529191 特開昭54−27644号公報JP 54-27644 A 特開平11−42521号公報Japanese Patent Laid-Open No. 11-42521 特開2004−68985号公報JP 2004-68985 A

本発明は、上述の様な事情に鑑み、外輪を楕円形に変形させる事に伴ってこの外輪に発生する最大引っ張り応力を抑えて、この外輪の弾性変形量を大きくでき、この外輪を楕円形に変形させて挿入作業を行なえる範囲を広くできる、自動調心ころ軸受の組立方法を実現すべく発明したものである。   In view of the circumstances as described above, the present invention suppresses the maximum tensile stress generated in the outer ring as the outer ring is deformed into an elliptical shape, and can increase the elastic deformation amount of the outer ring. The invention was invented to realize a method of assembling a self-aligning roller bearing which can be deformed into a wide range to perform an insertion operation.

本発明の組立方法の対象となる自動調心ころ軸受は、前述の従来から知られている自動調心ころ軸受と同様に、球状凹面である外輪軌道を内周面に形成した外輪と、この外輪軌道と対向する1対の内輪軌道を外周面に形成した内輪と、これら外輪軌道と内輪軌道との間に、2列に亙って転動自在に設けられた複数の球面ころと、これら各球面ころを転動自在に保持する複数のポケットを備えた保持器とから成る。   The self-aligning roller bearing that is an object of the assembling method of the present invention includes an outer ring in which an outer ring raceway that is a spherical concave surface is formed on the inner peripheral surface, similar to the conventional self-aligning roller bearing described above. An inner ring having a pair of inner ring raceways opposed to the outer ring raceway formed on the outer peripheral surface, a plurality of spherical rollers provided between the outer ring raceway and the inner ring raceway so as to be able to roll in two rows, and It comprises a cage having a plurality of pockets for holding each spherical roller in a rollable manner.

又、本発明の自動調心ころ軸受の組立方法は、上述の様な自動調心ころ軸受を組み立てるべく、上記内輪と上記各球面ころと上記保持器とを予め組み合わせて成る内輪組立体を上記外輪の内側に、この内輪組立体の中心軸とこの外輪の中心軸とが、上記外輪軌道の曲率中心部分で実質的に直交する状態にまで挿入する。この挿入作業の際、上記外輪を直径方向反対側部分で互いに近付く方向に押圧し、この外輪を楕円形に、この外輪の開口部の長径が上記内輪組立体を挿入可能な大きさになるまで弾性変形させておく。   Also, in the method of assembling the self-aligning roller bearing according to the present invention, an inner ring assembly in which the inner ring, the spherical rollers and the cage are combined in advance is assembled to assemble the self-aligning roller bearing as described above. Inside the outer ring, the center axis of the inner ring assembly and the center axis of the outer ring are inserted so as to be substantially orthogonal at the center of curvature of the outer ring raceway. During this insertion operation, the outer ring is pressed in the direction opposite to the diametrically opposite portion until the outer ring becomes elliptical, and the long diameter of the opening of the outer ring is large enough to insert the inner ring assembly. Let it elastically deform.

特に、本発明の自動調心ころ軸受の組立方法に於いては、上記外輪を挟んで互いに対向した状態で配置された1対の押圧治具の先端面により、この外輪の外周面の直径方向反対側2個所位置ずつ、合計4個所位置を互いに近付く方向に押圧する。そして、上記両押圧治具の先端面と上記外輪の外周面との当接位置を、これら両押圧治具によるこの外輪の押圧中心から円周方向両側に15〜30度ずつ外れた部分に設定する。
この為に例えば、請求項2に記載した様に、上記両押圧治具の先端面を、挟角が120〜150度のV字形の凹面とする。即ち、本発明を実施する為には、この先端面は必ずしもV字形の凹面である必要はないが、V字形の凹面とすれば、上記当接位置の規制を、容易に、且つ、安定して行なえる。
In particular, in the method of assembling the self-aligning roller bearing according to the present invention, the diameter direction of the outer peripheral surface of the outer ring is determined by the tip surfaces of the pair of pressing jigs arranged so as to face each other with the outer ring interposed therebetween. Each of the two positions on the opposite side is pressed in a direction that brings the total of four positions closer to each other. And the contact position of the front end surface of both the pressing jigs and the outer peripheral surface of the outer ring is set to a portion deviated by 15 to 30 degrees on both sides in the circumferential direction from the pressing center of the outer ring by these pressing jigs. To do.
For this purpose, for example, as described in claim 2, the front end surfaces of the two pressing jigs are V-shaped concave surfaces having an included angle of 120 to 150 degrees. That is, in order to carry out the present invention, the tip surface does not necessarily have to be a V-shaped concave surface, but if it is a V-shaped concave surface, the contact position can be easily and stably regulated. You can do it.

上述の様に構成する本発明の自動調心ころ軸受の組立方法によれば、外輪を楕円形に変形させる事に伴ってこの外輪に発生する最大引っ張り応力を抑えられる。この様に、最大引っ張り応力を抑えられる点に就いて、図1〜2を参照しつつ説明する。尚、自動調心ころ軸受1の構成各部材等の符号に就いては、図1の他、図5〜10に示したものを使用する。   According to the assembling method of the self-aligning roller bearing of the present invention configured as described above, the maximum tensile stress generated in the outer ring when the outer ring is deformed into an elliptical shape can be suppressed. Thus, the point which can suppress the maximum tensile stress is demonstrated, referring FIGS. In addition, about the code | symbol of each structural member etc. of the self-aligning roller bearing 1, what was shown in FIGS. 5-10 other than FIG. 1 is used.

本発明を実施すべく、内輪組立体13を挿入する為に外輪2を楕円形に変形させる為には、それぞれが油圧シリンダや送りねじ機構等のリニアアクチュエータにより平行移動させられる1対の押圧治具14、14により、上記外輪2を直径方向反対側から強く挟持する。これら両押圧治具14、14の先端面15、15を、上記平行移動方向に対し直角方向に存在する平坦面とした場合には、前述の図10に示した従来方法の場合と同様に、上記外輪2の直径方向反対側2個所位置を互いに近付く方向に押圧する状態となる。これに対して、上記両押圧治具14、14の先端面をV字形の凹面とした場合には、上記外輪2の外周面の直径方向反対側2個所位置ずつ、合計4個所位置を、互いに近付く方向に押圧する状態となる。そして、上記両先端面15、15を構成する1対ずつの傾斜面16、16の傾斜角度θを変える事により、これら各傾斜面16、16と上記外輪2の外周面との当接位置を調節できる。即ち、これら各傾斜面16、16を上記平坦面に対しθだけ傾斜させた場合には、これら各傾斜面16、16と上記外輪2の外周面とが、上記両押圧治具14、14によるこの外輪2の押圧中心から円周方向にθだけ外れた位置に当接する。   In order to carry out the present invention, in order to deform the outer ring 2 into an elliptical shape in order to insert the inner ring assembly 13, a pair of pressure treatments each translated by a linear actuator such as a hydraulic cylinder or a feed screw mechanism. The outer ring 2 is firmly held by the tools 14 and 14 from the opposite side in the diameter direction. When the front end surfaces 15 and 15 of both the pressing jigs 14 and 14 are flat surfaces existing in a direction perpendicular to the parallel movement direction, as in the case of the conventional method shown in FIG. The two positions on the opposite side of the outer ring 2 in the diametrical direction are pressed in a direction approaching each other. On the other hand, when the front end surfaces of the pressing jigs 14 and 14 are V-shaped concave surfaces, two positions on the outer peripheral surface of the outer ring 2 opposite to each other in the diametrical direction are arranged at a total of four positions. It will be in the state pressed in the direction which approaches. Then, by changing the inclination angle θ of the pair of inclined surfaces 16, 16 constituting the tip surfaces 15, 15, the contact position between the inclined surfaces 16, 16 and the outer peripheral surface of the outer ring 2 is changed. Can be adjusted. That is, when the inclined surfaces 16 and 16 are inclined by θ with respect to the flat surface, the inclined surfaces 16 and 16 and the outer peripheral surface of the outer ring 2 are formed by the pressing jigs 14 and 14. The outer ring 2 comes into contact with a position deviated by θ in the circumferential direction from the pressing center of the outer ring 2.

そこで、上記傾斜角度θを種々異ならせた場合を想定して、上記外輪2を、同じ量だけ(内側に上記内輪組立体13を挿入可能な程度にまで)楕円形に変形させた場合に、上記外輪2の一部(最も内径が小さくなった外輪軌道6の幅方向端縁部)に生じる引っ張り応力を(FEM解析により)求めた。図2の白抜きで表した棒グラフは、この結果を示している。この図2から明らかな通り、上記傾斜角度θを20度とし、上記各傾斜面16、16と上記外輪2の外周面との当接位置を、上記押圧中心から両側に20度だけずれた位置に設定すれば、上記引っ張り応力を最も低くできる。又、上記傾斜角度θを15〜30度の範囲内に設定し、上記当接位置を上記押圧中心から両側に15〜30度ずれた位置に設定すれば、他の角度範囲に設定した場合に比べて、上記引っ張り応力を十分に低く抑えられる。   Therefore, assuming that the inclination angle θ is variously changed, when the outer ring 2 is deformed into an oval shape by the same amount (to the extent that the inner ring assembly 13 can be inserted inside), The tensile stress generated in a part of the outer ring 2 (the edge in the width direction of the outer ring raceway 6 having the smallest inner diameter) was obtained (by FEM analysis). The bar graph shown in white in FIG. 2 shows this result. As is apparent from FIG. 2, the inclination angle θ is set to 20 degrees, and the contact positions of the inclined surfaces 16, 16 and the outer peripheral surface of the outer ring 2 are shifted by 20 degrees on both sides from the pressing center. If set to, the tensile stress can be minimized. If the inclination angle θ is set within a range of 15 to 30 degrees, and the contact position is set at a position deviated by 15 to 30 degrees on both sides from the pressing center, the angle can be set to another angle range. In comparison, the tensile stress can be suppressed sufficiently low.

例えば、図3は、大きさ(型番)が異なる8種類の外輪2に関して、上記当接位置を押圧中心(直径方向反対側2個所位置のみ)とした場合と、この当接位置を、上記15〜30度の中央値として、押圧中心から円周方向に22.5度ずらした2個所位置ずつ、合計4個所とした場合とに就いて、上記外輪2に生じる最大引っ張り応力の大きさを、FEM解析により求めた結果を示している。この様な図3から明らかな通り、上記外輪2の大きさに関係なく、上記当接位置を押圧中心から円周方向両側に振り分けた場合に、この当接位置を押圧中心に一致させた場合に比べて、最大引っ張り応力の値を30〜38%低減できる。   For example, FIG. 3 shows the case where the contact position is set as the pressing center (only two positions on the opposite side in the diameter direction) for the eight types of outer rings 2 having different sizes (model numbers). As a median value of ˜30 degrees, the magnitude of the maximum tensile stress generated in the outer ring 2 for the case where a total of four positions, two positions shifted by 22.5 degrees in the circumferential direction from the pressing center, The result calculated | required by FEM analysis is shown. As is clear from FIG. 3, when the contact position is distributed from the pressing center to both sides in the circumferential direction regardless of the size of the outer ring 2, the contact position is made to coincide with the pressing center. As compared with the above, the value of the maximum tensile stress can be reduced by 30 to 38%.

この為、上記当接位置を押圧中心から円周方向両側に振り分ける事により、上記外輪2の弾性変形量を大きくできる。そして、例えば軸方向に関する幅寸法が大きく、自由状態での開口部の内径と内輪組立体の外径との差が大きい場合でも、当該外輪2を楕円形に変形させる事による、この外輪2内への前記内輪組立体13の挿入作業を行なえる。この結果、自動組立が可能な自動調心ころ軸受の種類を増やせる。言い換えれば、上記幅寸法が大きな外輪2を有する自動調心ころ軸受の自動組立が可能になる。   For this reason, the amount of elastic deformation of the outer ring 2 can be increased by distributing the contact position from the center of pressing to both sides in the circumferential direction. For example, even when the width dimension in the axial direction is large and the difference between the inner diameter of the opening in the free state and the outer diameter of the inner ring assembly is large, the outer ring 2 is deformed into an elliptical shape by deforming the outer ring 2 into an oval shape. The inner ring assembly 13 can be inserted into the inner ring. As a result, the types of self-aligning roller bearings that can be automatically assembled can be increased. In other words, it is possible to automatically assemble a self-aligning roller bearing having the outer ring 2 having a large width.

本発明を実施する場合で、外輪2の円周方向等間隔偶数個所に、この外輪2の内外両周面同士を連通させる通油孔26、26が存在している場合には、請求項3に記載した様に、1対の押圧治具14、14により上記外輪2を押圧する力の中心位置を、円周方向に隣り合う通油孔26、26の間位置とする。
この様にすれば、応力集中に伴って亀裂等の損傷が発生し易い通油孔26、26部分に応力が集中する事を防止できる。即ち、図2に黒塗りで表した棒グラフから明らかな通り、損傷が発生し易い通油孔26、26部分に発生する応力の最大値を抑えて、これら各通油孔26、26を設けた外輪2を有する自動調心ころ軸受の自動組立も可能にできる。
In the case of carrying out the present invention, when there are oil passage holes 26, 26 communicating the inner and outer peripheral surfaces of the outer ring 2 at evenly spaced circumferential positions of the outer ring 2. As described above, the center position of the force that presses the outer ring 2 by the pair of pressing jigs 14 and 14 is the position between the oil passage holes 26 and 26 adjacent in the circumferential direction.
In this way, it is possible to prevent stress from concentrating on the oil passage holes 26 and 26 where damage such as cracks is likely to occur due to stress concentration. That is, as is apparent from the black bar graph shown in FIG. 2, the maximum value of the stress generated in the oil passage holes 26 and 26 where damage is likely to occur is suppressed, and the oil passage holes 26 and 26 are provided. It is also possible to automatically assemble a self-aligning roller bearing having the outer ring 2.

又、本発明を実施する場合に好ましくは、請求項4に記載した様に、内輪組立体13を外輪2の内側に挿入してから、この内輪組立体13を、これら内輪組立体13及び外輪2の直径方向を中心に実質的に90度揺動させて、この内輪組立体13をこの外輪2の内側に組み込む、所謂返し工程を行なう。この返し工程の際に、この内輪組立体13をこの外輪2の内側に、これら内輪組立体13と外輪2との中心軸同士が、外輪軌道の曲率中心部分で実質的に直交する状態に迄挿入すると共に、上記外輪2を、球状凹部を有する台座に載置する。そして、この状態で、上記内輪組立体13を構成する各球面ころ4、4をこの球状凹部の内面である案内用球状凹面で案内しつつ、この内輪組立体13を上記直径方向を中心に揺動させて、この内輪組立体13の中心軸と上記外輪2の中心軸とを実質的に一致させる。
この様な請求項4に記載した発明を実施する場合に好ましくは、請求項5に記載した様に、内輪3と各球面ころ4、4と保持器5、5とを予め組み合わせて内輪組立体13とする仮組立工程と、この内輪組立体13を上記外輪2の内側に挿入する挿入工程と、この外輪2の内側に挿入したこの内輪組立体13を90度揺動させてこれら内輪組立体13と外輪2との中心軸を実質的に一致させる返し工程とを、人手によらずに自動的に行なう。
この様に構成する事により、自動調心ころ軸受1の組立作業の全自動化が可能になり、この自動調心ころ軸受1の低コスト化を図れる。
Preferably, when the present invention is carried out, as described in claim 4, after the inner ring assembly 13 is inserted into the inner side of the outer ring 2, the inner ring assembly 13 is inserted into the inner ring assembly 13 and the outer ring. The inner ring assembly 13 is incorporated into the inner side of the outer ring 2 by swinging substantially 90 degrees around the diameter direction of No. 2 and performing a so-called returning process. In this returning step, the inner ring assembly 13 is brought into the inner side of the outer ring 2, and the central axes of the inner ring assembly 13 and the outer ring 2 are substantially perpendicular to each other at the center of curvature of the outer ring raceway. While inserting, the said outer ring | wheel 2 is mounted in the base which has a spherical recessed part. In this state, the spherical rollers 4, 4 constituting the inner ring assembly 13 are guided by the guiding spherical concave surface which is the inner surface of the spherical concave portion, and the inner ring assembly 13 is swung around the diametrical direction. By moving, the central axis of the inner ring assembly 13 and the central axis of the outer ring 2 are substantially matched.
When the invention described in claim 4 is carried out, the inner ring assembly is preferably obtained by combining the inner ring 3, the spherical rollers 4, 4 and the cages 5, 5 in advance as described in claim 5. 13, a temporary assembling step, an inserting step of inserting the inner ring assembly 13 into the inner side of the outer ring 2, and an inner ring assembly of the inner ring assembly 13 inserted into the outer ring 2 by swinging by 90 degrees. The return step of substantially matching the central axes of the outer ring 2 and the outer ring 2 is automatically performed without manual intervention.
With this configuration, the assembly operation of the self-aligning roller bearing 1 can be fully automated, and the cost of the self-aligning roller bearing 1 can be reduced.

図4〜6は、本発明の実施例を示している。本実施例に使用する自動調心ころ軸受の組立装置は、台座17と、揺動腕18と、押圧治具14、14とを備える。このうちの台座17は、ステンレス鋼等の金属、或いはポリアミド樹脂、ポリアセタール樹脂等の合成樹脂により造られたもので、図示しない旋回台の上面に支持固定されている。この旋回台は、鉛直方向に配設された回転中心軸を中心に回転するもので、上記台座17は、この回転中心軸と同心に配置されている。又、この台座17は、自動調心ころ軸受1を構成する外輪2をその上面に載置自在であり、且つ、この上面に開口した球状凹部19を有する。この球状凹部19は、上記回転中心軸上の点を曲率中心とする案内用球状凹面20と、底部に、この案内用球状凹面20よりも径方向外方(下方)に凹んだ状態で設けられた、油抜き用の凹部21とから成る。又、この案内用球状凹面20は、外輪2の内周面に形成した外輪軌道6と実質的に同一の曲率半径を有する。そして、この外輪2を上記台座17に載置した状態で、上記外輪軌道6の曲率中心と上記案内用球状凹面20の曲率中心とが実質的に一致する。   4 to 6 show an embodiment of the present invention. The self-aligning roller bearing assembly apparatus used in the present embodiment includes a pedestal 17, a swing arm 18, and pressing jigs 14 and 14. Of these, the pedestal 17 is made of a metal such as stainless steel, or a synthetic resin such as polyamide resin or polyacetal resin, and is supported and fixed on the upper surface of a swivel base (not shown). The swivel base rotates about a rotation center axis disposed in the vertical direction, and the pedestal 17 is disposed concentrically with the rotation center axis. Further, the pedestal 17 has an outer ring 2 constituting the self-aligning roller bearing 1 placed on the upper surface thereof, and has a spherical recess 19 opened on the upper surface. The spherical concave portion 19 is provided with a spherical concave surface for guide 20 having a point on the rotation center axis as a center of curvature, and a concave portion radially outward (downward) from the spherical concave surface 20 for guide at the bottom. And a recess 21 for draining oil. The spherical concave surface 20 for guide has a radius of curvature substantially the same as the outer ring raceway 6 formed on the inner peripheral surface of the outer ring 2. In the state where the outer ring 2 is placed on the pedestal 17, the center of curvature of the outer ring raceway 6 and the center of curvature of the spherical concave surface 20 for guidance substantially coincide.

又、上記揺動腕18の基端部(図4の上端部)は、ロータリアクチュエータ22の出力盤23の前面で、回転中心から外れた位置に結合固定している。この出力盤23は、水平方向に配置された回転中心軸を中心として揺動変位するもので、この回転中心軸の高さ位置は、上記台座17の上面に載置された状態での、上記外輪軌道6の曲率中心の位置と実質的に(誤差を除き可及的に)一致している。又、上記揺動腕18の先端部は、上記台座17の上面に載置された上記外輪2の上方で、この外輪2の内側に挿入された内輪組立体13を構成する何れかの球面ころ4の軸方向端面に係合(突き当て)自在な位置に存在する。   The base end portion (upper end portion in FIG. 4) of the swing arm 18 is coupled and fixed at a position deviating from the center of rotation on the front surface of the output board 23 of the rotary actuator 22. The output board 23 swings and displaces around a rotation center axis arranged in the horizontal direction, and the height position of the rotation center axis is the above-described state in a state where it is placed on the upper surface of the pedestal 17. It substantially matches the position of the center of curvature of the outer ring raceway 6 (as much as possible excluding errors). Further, the tip of the swing arm 18 is either spherical roller constituting the inner ring assembly 13 inserted inside the outer ring 2 above the outer ring 2 placed on the upper surface of the pedestal 17. It exists in the position which can be engaged with (abutted on) the axial direction end surface of 4 freely.

更に、上記両押圧治具14、14はそれぞれ、互いに対向する状態で互いに同心に設けられた、油圧シリンダ、送りねじ機構等の、変位量を厳密に規制可能な直動式のアクチュエータ24の出力ロッド25の先端部に、互いに同心に支持固定されている。この様な両押圧治具14、14は、上記両アクチュエータ24の伸長に伴って互いに近付き合った状態で、上記外輪2を直径方向反対側から抑え付ける。そして、この外輪2を上記台座17の上方に、上記案内用球状凹面20と同心に支持する。   Further, both the pressing jigs 14 and 14 are outputs of a direct-acting actuator 24, which is provided concentrically with each other in a state of being opposed to each other, such as a hydraulic cylinder, a feed screw mechanism, and the like that can strictly regulate the amount of displacement. The rod 25 is supported and fixed concentrically with each other at the distal end portion thereof. The two pressing jigs 14 and 14 hold the outer ring 2 from the opposite side in the diametrical direction while approaching each other as the actuators 24 extend. The outer ring 2 is supported above the pedestal 17 concentrically with the guiding spherical concave surface 20.

又、上記両アクチュエータ24により上記両押圧治具14、14を、上記外輪2を上記案内用球状凹面20と同心に支持する為の位置よりも更に近づけ合う事で、この外輪2を、前述の図10に示した様に、楕円形に変形可能にしている。この為に、上記両押圧治具14、14の先端面15、15に、前述の図1に示した様な傾斜面16、16を、これら各先端面15、15毎に1対ずつ設けている。そして、上記台座17上に載置した上記外輪2を楕円形に変形させて、この外輪2の内側に上記内輪組立体13を挿入する、挿入作業を行なえる様にしている。   Also, the two pressing jigs 14 and 14 are brought closer to the outer ring 2 by the both actuators 24 than the position for supporting the outer ring 2 concentrically with the guiding spherical concave surface 20. As shown in FIG. 10, it can be deformed into an ellipse. For this purpose, a pair of inclined surfaces 16 and 16 as shown in FIG. 1 are provided on the front end surfaces 15 and 15 of the pressing jigs 14 and 14, respectively. Yes. Then, the outer ring 2 placed on the pedestal 17 is deformed into an oval shape, and the inner ring assembly 13 is inserted into the outer ring 2 so that an insertion operation can be performed.

本実施例の場合には、上記外輪2として、図6の上段の(A)に示した様に、円周方向等間隔4個所位置に通油孔26、26を形成したものと、図6の下段の(B)に示す様に通油孔を持たないものとの何れに就いても、自動組立を行なえる様にしている。この為に本実施例の場合には、上記台座17の上面に載置した上記外輪2を直径方向反対側から挟む2個所位置に、光電スイッチ27a、27b(投光器及び受光器)を配置している。これら両光電スイッチ27a、27b同士の間でレーザ光等の光が、上記通油孔26、26を通過する事で授受される。   In the case of the present embodiment, as the outer ring 2, as shown in (A) in the upper part of FIG. 6, oil passage holes 26 and 26 are formed at four positions at equal intervals in the circumferential direction. As shown in the lower part (B), automatic assembly can be performed regardless of whether the oil passage hole is not provided. Therefore, in the case of the present embodiment, photoelectric switches 27a and 27b (light projector and light receiver) are arranged at two positions sandwiching the outer ring 2 placed on the upper surface of the pedestal 17 from the opposite side in the diameter direction. Yes. Light such as laser light is transmitted and received between the photoelectric switches 27a and 27b by passing through the oil passage holes 26 and 26.

本実施例の場合には、上記外輪2を上記台座17の上面に、この台座17と同心に載置した後、上記両押圧治具14、14を互いに近づける以前に、この台座17を最大1/2回転させる。例えば、上記外輪2が上記通油孔26、26を有するものである場合には、図6の(A)(b)に示す様に、上記両押圧治具14、14により上記外輪2を押圧する力の中心位置が、円周方向に隣り合う通油孔26、26の丁度間位置になった瞬間に、上記両光電スイッチ27a、27b同士の間で光の授受が行なわれる。そこで、この瞬間に上記台座17の回転を一度停止させて、図6の(A)(c)に示す様に、上記両押圧治具14、14を互いに近づける。そして、上記外輪2を楕円形に変形させて、前記挿入作業を行なう。   In the case of the present embodiment, after the outer ring 2 is placed on the upper surface of the pedestal 17 and concentrically with the pedestal 17, the pedestal 17 is moved up to 1 before the pressing jigs 14 and 14 are brought close to each other. Rotate twice. For example, when the outer ring 2 has the oil passage holes 26, 26, the outer ring 2 is pressed by the pressing jigs 14, 14 as shown in FIGS. At the moment when the center position of the applied force is just between the circumferentially adjacent oil passage holes 26, 26, light is exchanged between the photoelectric switches 27a, 27b. Therefore, at this moment, the rotation of the pedestal 17 is once stopped, and the pressing jigs 14 and 14 are brought close to each other as shown in FIGS. And the said outer ring | wheel 2 is deform | transformed into an ellipse, and the said insertion operation | work is performed.

一方、図6の下段の(B)に示す様に通油孔を持たないものである場合には、この図6の(B)の(a)→(c)に示す様に、上記台座17を1/2回転させた場合でも、上記両光電スイッチ27a、27b同士の間で光の授受が行なわれる瞬間が発生しない。そこで、この場合には、当該外輪2は通油孔を持たないものであるとして、図6の(B)(c)に示す様に、上記両押圧治具14、14を互いに近づける。そして、上記外輪2を楕円形に変形させて、上記挿入作業を行なう。   On the other hand, in the case where the oil passage hole is not provided as shown in the lower part (B) of FIG. 6, as shown in (a) → (c) of FIG. Even when ½ is rotated, there is no moment when light is exchanged between the photoelectric switches 27a and 27b. Therefore, in this case, it is assumed that the outer ring 2 does not have an oil passage hole, and the pressing jigs 14 and 14 are brought closer to each other as shown in FIGS. Then, the outer ring 2 is deformed into an oval shape and the insertion operation is performed.

本実施例の場合には、この様にして挿入作業を行なった後、前記両アクチュエータ24が上記外輪2を押圧している力を(この外輪2を変形させないが、位置決め可能な程度にまで)弱めてから、上記内輪組立体13を揺動変位させて、この内輪組立体13の中心軸と上記外輪2の中心軸とを一致させる、所謂返し作業工程を行なう。   In the case of the present embodiment, after performing the insertion work in this way, the force that the actuators 24 press the outer ring 2 is applied (to the extent that the outer ring 2 is not deformed but can be positioned). After the weakening, a so-called return operation step is performed in which the inner ring assembly 13 is oscillated and displaced so that the central axis of the inner ring assembly 13 and the central axis of the outer ring 2 coincide with each other.

上記挿入作業により、上記内輪組立体13を上記台座17の上面に載置した外輪2の内側に挿入した状態では、この内輪組立体13を構成する各球面ころ4、4のうち、下半部に存在する球面ころ4、4の転動面が、前記案内用球状凹面20に当接する。そして、上記返し作業の開始状態では、上記内輪組立体13の中心軸O13と上記外輪2の中心軸O2 とが、この外輪2の内周面の外輪軌道6の曲率中心O6 部分で実質的に直交する。又、上記開始状態では、前記揺動腕18の先端部が、図5の(A)に示す様に、上記内輪組立体13の上端部の側方に存在する。 In the state where the inner ring assembly 13 is inserted into the inner side of the outer ring 2 placed on the upper surface of the pedestal 17 by the insertion operation, the lower half of the spherical rollers 4 and 4 constituting the inner ring assembly 13 The rolling surfaces of the spherical rollers 4, 4 present in the contact with the guide spherical concave surface 20. Then, in the starting state of the flashing operation, the central axis O 2 of the center axis O 13 and the outer ring 2 of the inner ring assembly 13, with the center of curvature O 6 parts of the outer ring raceway 6 of the inner peripheral surface of the outer ring 2 Substantially orthogonal. In the start state, the tip end of the swing arm 18 is present on the side of the upper end of the inner ring assembly 13 as shown in FIG.

上記図5の(A)に示す様に、上記台座17の上面に載置した外輪2の内側に上記内輪組立体13を挿入したならば、それまで停止していた上記揺動腕18を、図5の(A)に示した状態から反時計方向に揺動変位させる。そして、上記内輪組立体13を、図5の(A)→(B)→(C)に示す順番で、この内輪組立体13及び上記外輪2の直径方向を中心に揺動変位させる。この揺動変位に伴って、この内輪組立体13が、この外輪2の内側に組み込まれる。   As shown in FIG. 5A, when the inner ring assembly 13 is inserted into the inner side of the outer ring 2 placed on the upper surface of the pedestal 17, the swing arm 18 that has been stopped until then is From the state shown in FIG. 5A, it is oscillated and displaced counterclockwise. Then, the inner ring assembly 13 is oscillated and displaced about the diameter direction of the inner ring assembly 13 and the outer ring 2 in the order shown in FIGS. 5A to 5C. The inner ring assembly 13 is incorporated inside the outer ring 2 along with the swing displacement.

上記図5の(A)→(B)→(C)に示す様に、上記内輪組立体13が上記外輪2の内側に組み込まれる過程で、この内輪組立体13を構成する上記各球面ころ4、4が、上記案内用球状凹面20に案内されつつ、上記外輪軌道6の内側に入り込む。これら案内用球状凹面20の上端開口縁部と外輪軌道6の下端開口縁部との間には、不可避な誤差に基づく微小な段差が存在するが、上記各球面ころ4、4の端面外周縁部に存在する面取りの存在に基づき、これら各球面ころ4、4が上記外輪軌道6の内側に、無理なく送り込まれる。しかも、本実施例の場合には、上記台座17を回転させる事に伴って、上記内輪組立体13及び上記外輪2を振動させている。従って、上記返し作業の過程で互いに接触する、各球面ころ4、4と外輪2との位置関係が不安定になり、この返し作業の途中で、何れかの球面ころ4の軸方向端縁と上記外輪2の開口周縁部とが引っ掛かっても、引っ掛かった状態が安定せずに直ちに解消される。この為、当該球面ころ4を上記外輪軌道6の内側に送り込む事ができる。又、上記各球面ころ4、4がこの外輪軌道6の内側に送り込まれた後の状態でも、これら各球面ころ4、4の転動面とこの外輪軌道6との間に作用する摩擦を小さく抑えられる。この為、これら転動面や外輪軌道6に擦り傷等の損傷を生じさせる事なく、上記内輪組立体13を上記外輪2の内側に組み込める。尚、上記台座17を回転させる理由は、上記各球面ころ4、4と上記外輪2との位置関係を不安定にする為であるから、上記台座17を回転させずに、振動子等により振動させても良い。   As shown in FIGS. 5 (A) → (B) → (C), the spherical rollers 4 constituting the inner ring assembly 13 are assembled in the process of incorporating the inner ring assembly 13 into the inner side of the outer ring 2. 4 enters the inside of the outer ring raceway 6 while being guided by the guiding spherical concave surface 20. There is a minute step based on an unavoidable error between the upper end opening edge of the guide spherical concave surface 20 and the lower end opening edge of the outer ring raceway 6. These spherical rollers 4 and 4 are fed into the outer ring raceway 6 without difficulty based on the presence of chamfering in the portion. In addition, in the case of this embodiment, the inner ring assembly 13 and the outer ring 2 are vibrated as the pedestal 17 is rotated. Accordingly, the positional relationship between the spherical rollers 4 and 4 and the outer ring 2 that are in contact with each other in the course of the above-described returning operation becomes unstable, and in the middle of this returning operation, the axial end edge of any of the spherical rollers 4 Even if the outer periphery of the outer ring 2 is caught, the hooked state is immediately resolved without being stabilized. For this reason, the spherical roller 4 can be fed into the outer ring raceway 6. Further, even when the spherical rollers 4 and 4 are fed into the outer ring raceway 6, the friction acting between the rolling surfaces of the spherical rollers 4 and 4 and the outer ring raceway 6 is reduced. It can be suppressed. Therefore, the inner ring assembly 13 can be incorporated inside the outer ring 2 without causing damage such as scratches on the rolling surfaces and the outer ring raceway 6. The reason for rotating the pedestal 17 is to make the positional relationship between the spherical rollers 4 and 4 and the outer ring 2 unstable, so that the pedestal 17 is vibrated by a vibrator or the like without rotating the pedestal 17. You may let them.

又、図示の実施例の場合には、前記球状凹部19の底部に、上記案内用球状凹面20よりも径方向外方に凹んだ、油抜き用の凹部21を設けている為、上記球状凹部19内に入り込んだ油が上記案内用球状凹面20に留る事を防止できる。但し、上記凹部21を設ける事に伴って、上記返し作業の初期段階で、この凹部21に対向している一部の球面ころ4の軸方向端面外周縁部とこの凹部21の開口周縁部とが引っ掛かる可能性を生じる。この為、本実施例の場合には、前記台座17を、前記外輪2の中心軸を中心として回転させる事により、上記一部の球面ころ4を上記案内用球状凹面20に、無理なく乗り上げさせる様にしている。尚、上記凹部21の開口周縁部に面取りを施せば、上記一部の球面ころ4の上記案内用球状凹面20への乗り上げを、より円滑に行なわせる事ができる。   In the illustrated embodiment, the bottom of the spherical recess 19 is provided with a recess 21 for draining oil that is recessed radially outward from the guide spherical concave surface 20. It is possible to prevent the oil that has entered inside 19 from staying on the guide spherical concave surface 20. However, along with the provision of the concave portion 21, in the initial stage of the returning operation, the outer peripheral edge portion of the axial end surface of a part of the spherical rollers 4 facing the concave portion 21 and the opening peripheral edge portion of the concave portion 21 May be caught. For this reason, in the case of the present embodiment, the pedestal 17 is rotated about the central axis of the outer ring 2 so that the part of the spherical rollers 4 rides on the spherical spherical concave surface 20 without difficulty. Like. If the peripheral edge of the opening of the recess 21 is chamfered, the part of the spherical rollers 4 can run more smoothly onto the guiding spherical concave surface 20.

尚、上記返し作業を行なう際の、前記揺動腕18による前記内輪組立体13の揺動速度、並びに上記台座17の回転速度は、揺動及び回転に伴って、上記返し作業にとって有害な遠心力が発生しない程度の適正な値に収める。この様な適正値に就いては、計算乃至は実験により求める。例えば、上記揺動速度に関しては、圧延機等の産業機械用の自動調心ころ軸受の場合で、90度/3〜4秒程度若しくはこれよりも緩徐に行なう事が適切である。又、上記回転速度に就いては、上記各球面ころ4、4と上記外輪2との位置関係を不安定にする為の振動を得られる限り、低く抑える事が、これら各球面ころ4、4の転動面と上記案内用球状凹面20との摩擦を抑えて、これら各面の損傷を防止する面からは好ましい。   Note that the rocking speed of the inner ring assembly 13 by the rocking arm 18 and the rotational speed of the pedestal 17 when the above-described returning operation is performed are centrifugal that are harmful to the returning operation. Set to an appropriate value that does not generate force. Such an appropriate value is obtained by calculation or experiment. For example, with respect to the rocking speed, in the case of a self-aligning roller bearing for an industrial machine such as a rolling mill, it is appropriate that the swinging speed is about 90 degrees / 3 to 4 seconds or slower. The rotational speed of the spherical rollers 4, 4 can be kept low as long as vibration for destabilizing the positional relationship between the spherical rollers 4, 4 and the outer ring 2 can be obtained. This is preferable from the viewpoint of suppressing the friction between the rolling surface and the guide spherical concave surface 20 and preventing the damage of each surface.

挿入工程を行なう為に外輪を弾性変形させる為に使用する1対の押圧治具を示す斜視図。The perspective view which shows a pair of press jig | tool used in order to elastically deform an outer ring | wheel in order to perform an insertion process. 1対の押圧治具による押圧位置が外輪に生じる応力の大きさに及ぼす影響を知る為に行なった第一の実験の結果を示す棒グラフ。The bar graph which shows the result of the 1st experiment conducted in order to know the influence which the press position by a pair of press jig | tool has on the magnitude | size of the stress which arises in an outer ring | wheel. 同じく第二の実験の結果を示す線図。The diagram which similarly shows the result of a 2nd experiment. 挿入工程に続いて返し工程を行なう装置の実施例を示す要部略平面図。The principal part schematic plan view which shows the Example of the apparatus which performs a return process following an insertion process. 内輪組立体を外輪の内側に組み込むべく、この内輪組立体を旋回させる状態を示す、図4のA−A断面に相当する図。The figure equivalent to the AA cross section of FIG. 4 which shows the state which turns this inner ring assembly in order to incorporate an inner ring assembly inside an outer ring. 外輪を弾性変形させるのに先立ってこの外輪の円周方向に関する位相を規制する状態を示す図。The figure which shows the state which regulates the phase regarding the circumferential direction of this outer ring before elastically deforming an outer ring. 自動調心ころ軸受の1例を示す部分断面図。The fragmentary sectional view which shows one example of a self-aligning roller bearing. 図7の側方から見た図。The figure seen from the side of FIG. 外輪を弾性変形させずに、この外輪に内輪組立体を近づけた状態を示す断面図。Sectional drawing which shows the state which brought the inner ring assembly close to this outer ring without elastically deforming the outer ring. 外輪を弾性変形させた状態で、この外輪の内側に内輪組立体を挿入した状態を示す側面図。The side view which shows the state which inserted the inner ring assembly inside this outer ring | wheel in the state which elastically deformed the outer ring | wheel.

符号の説明Explanation of symbols

1 自動調心ころ軸受
2 外輪
3 内輪
4 球面ころ
5 保持器
6 外輪軌道
7 内輪軌道
8 主部
9 ポケット
10 外向フランジ部
11 弾性舌片
12 凹部
13 内輪組立体
14 押圧治具
15 先端面
16 傾斜面
17 台座
18 揺動腕
19 球状凹部
20 案内用球状凹面
21 凹部
22 ロータリアクチュエータ
23 出力盤
24 アクチュエータ
25 出力ロッド
26 通油孔
27 充電スイッチ
DESCRIPTION OF SYMBOLS 1 Self-aligning roller bearing 2 Outer ring 3 Inner ring 4 Spherical roller 5 Cage 6 Outer ring raceway 7 Inner ring raceway 8 Main part 9 Pocket 10 Outward flange part 11 Elastic tongue piece 12 Recessed part 13 Inner ring assembly 14 Pressing jig 15 End face 16 Inclination Surface 17 Base 18 Oscillating arm 19 Spherical recess 20 Spherical concave surface for guide 21 Recess 22 Rotary actuator 23 Output panel 24 Actuator 25 Output rod 26 Oil passage hole 27 Charge switch

Claims (5)

球状凹面である外輪軌道を内周面に形成した外輪と、この外輪軌道と対向する1対の内輪軌道を外周面に形成した内輪と、これら外輪軌道と内輪軌道との間に、2列に亙って転動自在に設けられた複数の球面ころと、これら各球面ころを転動自在に保持する複数のポケットを備えた保持器とから成る自動調心ころ軸受を組み立てるべく、上記内輪と上記各球面ころと上記保持器とを予め組み合わせて成る内輪組立体を上記外輪の内側に、この外輪を直径方向反対側部分で互いに近付く方向に押圧し、この外輪を楕円形に、この外輪の開口部の長径が上記内輪組立体を挿入可能な大きさになるまで弾性変形させた状態で、この内輪組立体の中心軸とこの外輪の中心軸とが、上記外輪軌道の曲率中心部分で実質的に直交する状態にまで挿入する自動調心ころ軸受の組立方法に於いて、上記外輪を挟んで互いに対向した状態で配置された1対の押圧治具の先端面により、この外輪の外周面の直径方向反対側2個所位置ずつ合計4個所位置を互いに近付く方向に押圧するものとし、上記両押圧治具の先端面と上記外輪の外周面との当接位置を、これら両押圧治具によるこの外輪の押圧中心から円周方向両側に15〜30度ずつ外れた部分に設定した事を特徴とする自動調心ころ軸受の組立方法。   An outer ring in which an outer ring raceway that is a spherical concave surface is formed on the inner peripheral surface, an inner ring in which a pair of inner ring races opposed to the outer ring raceway are formed on the outer peripheral surface, and the outer ring raceway and the inner ring raceway in two rows. In order to assemble a self-aligning roller bearing comprising a plurality of spherical rollers provided so as to be freely rollable, and a cage having a plurality of pockets for holding each of these spherical rollers in a freely rollable manner, An inner ring assembly in which the spherical rollers and the cage are combined in advance is pressed inside the outer ring, and the outer ring is pressed in a direction approaching each other at a portion opposite to the diametrical direction. With the major axis of the opening elastically deformed until the inner ring assembly can be inserted, the central axis of the inner ring assembly and the central axis of the outer ring are substantially at the center of curvature of the outer ring raceway. Automatically inserted even in the orthogonal state In the assembling method of the spherical roller bearing, the positions of two positions opposite to each other in the diametrical direction on the outer peripheral surface of the outer ring are totaled by the tip surfaces of the pair of pressing jigs arranged so as to face each other across the outer ring. The four positions are pressed in a direction approaching each other, and the abutting positions of the tip surfaces of the two pressing jigs and the outer peripheral surface of the outer ring are set on both sides in the circumferential direction from the pressing center of the outer ring by the two pressing jigs. A method of assembling a self-aligning roller bearing, characterized in that it is set at a portion deviated by 15 to 30 degrees. 両押圧治具の先端面が、挟角が120〜150度のV字形の凹面である、請求項1に記載した自動調心ころ軸受の組立方法。   The self-aligning roller bearing assembly method according to claim 1, wherein the front end surfaces of both pressing jigs are V-shaped concave surfaces having an included angle of 120 to 150 degrees. 外輪の円周方向等間隔偶数個所に、この外輪の内外両周面同士を連通させる通油孔が存在しており、1対の押圧治具により上記外輪を押圧する力の中心位置が、円周方向に隣り合う通油孔の間位置である、請求項1〜2のうちの何れか1項に記載した自動調心ころ軸受の組立方法。   There are oil passage holes that allow the inner and outer peripheral surfaces of the outer ring to communicate with each other evenly spaced in the circumferential direction of the outer ring, and the center position of the force that presses the outer ring with a pair of pressing jigs is circular. The method of assembling a self-aligning roller bearing according to any one of claims 1 to 2, wherein the assembly method is a position between oil passage holes adjacent in the circumferential direction. 内輪組立体を外輪の内側に挿入してから、この内輪組立体を、これら内輪組立体及び外輪の直径方向を中心に実質的に90度揺動させ、この内輪組立体をこの外輪の内側に組み込む際に、この内輪組立体をこの外輪の内側に、これら内輪組立体と外輪との中心軸同士が、外輪軌道の曲率中心部分で実質的に直交する状態に迄挿入すると共に、この外輪を、球状凹部を有する台座に載置した状態で、上記内輪組立体を構成する上記各球面ころをこの球状凹部の内面である案内用球状凹面で案内しつつ、この内輪組立体を上記直径方向を中心に揺動させて、この内輪組立体の中心軸と上記外輪の中心軸とを実質的に一致させる、請求項1〜3のうちの何れか1項に記載した自動調心ころ軸受の組立方法。   After inserting the inner ring assembly inside the outer ring, the inner ring assembly is swung substantially 90 degrees around the diameter direction of the inner ring assembly and the outer ring, and the inner ring assembly is moved inside the outer ring. When the inner ring assembly is assembled, the inner ring assembly is inserted inside the outer ring until the central axes of the inner ring assembly and the outer ring are substantially orthogonal at the center of curvature of the outer ring raceway. In the state where it is placed on a pedestal having a spherical recess, the spherical rollers constituting the inner ring assembly are guided by the guide spherical concave surface which is the inner surface of the spherical recess, and the inner ring assembly is moved in the diametrical direction. The self-aligning roller bearing assembly according to any one of claims 1 to 3, wherein the self-aligning roller bearing is pivoted to the center so that the central axis of the inner ring assembly substantially coincides with the central axis of the outer ring. Method. 内輪と各球面ころと保持器とを予め組み合わせて内輪組立体とする仮組立工程と、この内輪組立体を外輪の内側に挿入する挿入工程と、この外輪の内側に挿入したこの内輪組立体を90度揺動させてこれら内輪組立体と外輪との中心軸を実質的に一致させる返し工程とを、人手によらずに自動的に行なう、請求項4に記載した自動調心ころ軸受の組立方法。   A temporary assembly process in which an inner ring, spherical rollers and a cage are combined in advance to form an inner ring assembly, an insertion process in which the inner ring assembly is inserted inside the outer ring, and the inner ring assembly inserted in the outer ring. 5. A self-aligning roller bearing assembly according to claim 4, wherein the returning step of swinging 90 degrees and causing the center axes of the inner ring assembly and the outer ring to substantially coincide with each other is automatically performed without manual intervention. Method.
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JP2012154458A (en) * 2011-01-28 2012-08-16 Jtekt Corp Rolling bearing assembling method
JP2015194193A (en) * 2014-03-31 2015-11-05 Ntn株式会社 Manufacturing method of bearing and manufacturing device
CN108679102A (en) * 2018-05-23 2018-10-19 洛阳轴承研究所有限公司 A kind of rammer ball component and rammer ball trap method for making bearing inner race deform
CN110005716A (en) * 2019-04-30 2019-07-12 聊城西科自动化设备有限公司 Self-aligning roller bearing device for sleeving and its working method

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CN110005716A (en) * 2019-04-30 2019-07-12 聊城西科自动化设备有限公司 Self-aligning roller bearing device for sleeving and its working method
CN110005716B (en) * 2019-04-30 2024-02-27 聊城西科自动化设备有限公司 Self-aligning roller bearing sleeve assembling device and working method thereof

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