JP2009197978A - Fixture for assembling bearing and bearing assembling method - Google Patents

Fixture for assembling bearing and bearing assembling method Download PDF

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JP2009197978A
JP2009197978A JP2008043073A JP2008043073A JP2009197978A JP 2009197978 A JP2009197978 A JP 2009197978A JP 2008043073 A JP2008043073 A JP 2008043073A JP 2008043073 A JP2008043073 A JP 2008043073A JP 2009197978 A JP2009197978 A JP 2009197978A
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bearing
shaft
thimble
graduated
scaled
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Shingo Sakata
慎吾 坂田
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To effectively execute axial preload adjustment work of an assembled rolling bearing in a short time. <P>SOLUTION: A graduated sleeve 12 graduated in the axial direction of an outer diameter and a graduated thimble 13 graduated in the peripheral direction of the outer diameter are screwed with each other, and assembled in a rotary section. One end of a bearing inner ring is made to protrude from the other end face of a shaft 23 with an assemble rolling bearing installed thereon. Then, the shaft 23 and the bearing inner ring is held by the graduated sleeve 12 and the graduated thimble 13, and a bearing gap is measured by using the scale of the graduated sleeve 12 and the graduated thimble 13. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は、予圧調整が必要な組合わせ転がり軸受の組立用治具及び組立方法に関する。   The present invention relates to an assembling jig and an assembling method for a combined rolling bearing requiring preload adjustment.

組合わせ転がり軸受（以下、「組合わせ軸受」と称する。）の予圧方式には、定位置予圧方式と定圧予圧方式の二種類がある。定位置予圧方式で軸受を使用する場合は、大別して、ナットプレートの締め込み量により予圧を調整する予圧調整方式（例えば、特許文献１参照）と、薄板（シムプレート）の挿入枚数を加減して組合わせ軸受のアキシアル隙間（軸受隙間）を調整する予圧調整方式とに分けられる。高い回転精度、位置決め精度等を実現するためには、軸受隙間を適切に管理する必要がある。適切な軸受隙間とは、零より僅かな負隙間であり、予圧過多による回転精度劣化が発生しない一定範囲内の軸受隙間をいう。   There are two types of preload systems for combined rolling bearings (hereinafter referred to as “combined bearings”): a fixed position preload system and a constant pressure preload system. When using bearings in the fixed position preload method, roughly divide the preload adjustment method (for example, see Patent Document 1) that adjusts the preload by the tightening amount of the nut plate and the number of inserted thin plates (shim plates). And a preload adjustment method for adjusting the axial gap (bearing gap) of the combined bearing. In order to achieve high rotation accuracy, positioning accuracy, etc., it is necessary to appropriately manage the bearing gap. An appropriate bearing clearance is a negative clearance slightly smaller than zero, and refers to a bearing clearance within a certain range in which deterioration of rotational accuracy due to excessive preload does not occur.

特開２００７−２１８４２７号公報JP 2007-218427 A

一方、航空機搭載用の光学機器やレーダにおいては、その光軸方向を高精度に安定化させるための多軸のジンバル機構が用いられる。このような高精度ジンバル機構は高い回転精度を有した回転部を必要とし、回転部を構成する軸受においては均一に予圧を加えている。特許文献１に示すようなナットプレートの締め込み量で予圧を調整する場合、ナットプレートが軸受に片当たりし易く、予圧が偏ってしまうという問題がある。このため、通常、シムプレートの挿入枚数を調整して予圧調整が行われている。   On the other hand, a multi-axis gimbal mechanism for stabilizing the optical axis direction with high accuracy is used in an optical device or radar mounted on an aircraft. Such a high-precision gimbal mechanism requires a rotating part with high rotational accuracy, and a preload is uniformly applied to the bearings constituting the rotating part. When adjusting the preload by the tightening amount of the nut plate as shown in Patent Document 1, there is a problem that the preload is biased because the nut plate easily comes into contact with the bearing. For this reason, the preload adjustment is normally performed by adjusting the number of shim plates inserted.

しかしながら、シムプレートを用いた調整方式では、回転部の構成部品の寸法ばらつきや、軸受の仕上り状態、嵌合状態等の変動により、適切な予圧量が軸受や構成部品毎に異なり、回転部を回転させるときの摩擦トルクも変動する。このため、摩擦トルク及びその変動値を確認しながら、軸受隙間を変更し、シプレートの挿入枚数の調整を繰り返す必要がある。この軸受隙間を変更する為には、回転部の保持部品を分解し、軸受隙間を調整するためのシムプレートの厚さを数μｍ単位で再設定した後、回転部を再組立する。このため、予圧調整に長時間要し、製造コストの増大につながってしまうという課題があった。   However, in the adjustment method using shim plates, the appropriate preload amount differs for each bearing and component due to variations in the dimensions of the components of the rotating part and variations in the finish and fitting state of the bearing. The friction torque at the time of rotation also varies. For this reason, it is necessary to change the bearing gap and repeatedly adjust the number of inserted sheets while confirming the friction torque and its fluctuation value. In order to change the bearing gap, the holding part of the rotating part is disassembled, the thickness of the shim plate for adjusting the bearing gap is reset in units of several μm, and then the rotating part is reassembled. For this reason, it took a long time to adjust the preload, resulting in an increase in manufacturing cost.

例えば、航空機搭載用の高精度ジンバル機構等の厳密な予圧調整を必要とする回転装置では、運用中に空力荷重等の大きな外力が加わった際も、高い回転精度、位置決め精度を保つことが必要となるため、軸受の内部隙間が発生し難い、シムプレートを用いた定位置予圧が有効であり、この定位置予圧の調整作業を効率的に行うことが望まれている。   For example, in a rotating device that requires strict preload adjustment, such as a high-precision gimbal mechanism mounted on an aircraft, it is necessary to maintain high rotational accuracy and positioning accuracy even when a large external force such as an aerodynamic load is applied during operation. Therefore, a fixed position preload using a shim plate is effective because an internal clearance of the bearing is unlikely to occur, and it is desired to perform an adjustment operation of the fixed position preload efficiently.

この発明は係る課題を解決するためになされたものであり、組合わせ軸受における予圧調整作業を、より短時間で効率的に行うことを目的とする。   The present invention has been made to solve the above-described problems, and an object of the present invention is to perform preload adjustment work in a combined bearing efficiently in a shorter time.

この発明による軸受組立治具は、シャフトの外径に装着された一対の転がり軸受から成る組合わせ軸受について、軸受内輪間の軸受隙間を調整する軸受組立治具であって、外径の軸方向に目盛の刻まれた目盛付きスリーブと、外径の円周方向に目盛が刻まれた目盛付きシンブルとを具備し、上記目盛付きスリーブが上記シャフトの内径に挿入され、上記目盛付きシンブルと目盛付きスリーブを双方の目盛を向き合わせて螺合し、上記シャフトの端面から上記軸受内輪が突出した状態で、上記目盛付きスリーブと目盛付きシンブルとで上記シャフトおよび軸受内輪を挟み、上記軸受に予圧を与えるものである。   A bearing assembly jig according to the present invention is a bearing assembly jig that adjusts a bearing gap between inner ring of bearings for a combined bearing composed of a pair of rolling bearings mounted on an outer diameter of a shaft, and has an axial direction of an outer diameter. A graduated sleeve having a scale and a graduated thimble with a scale in the circumferential direction of the outer diameter, the graduated sleeve being inserted into the inner diameter of the shaft, and the graduated thimble and scale Screw the sleeve with both scales facing each other, and with the bearing inner ring protruding from the end face of the shaft, the shaft and the bearing inner ring are sandwiched between the scaled sleeve and the scaled thimble, and the bearing is preloaded. Is to give.

また、この発明による軸受組立方法は、シャフトの外径に装着された一対の転がり軸受から成る組合わせ軸受について、軸受内輪間の軸受隙間を調整する軸受組立方法であって、外径の軸方向に目盛の刻まれた目盛付きスリーブを上記シャフトの内径に挿入し、当該目盛付きスリーブと外径の円周方向に目盛が刻まれた目盛付きシンブルを螺合させ、上記シャフトの端面から上記軸受内輪が突出した状態で、当該目盛付きスリーブと目盛付きシンブルとで上記シャフトおよび軸受内輪を挟み、上記目盛付きシンブルを回しながら上記目盛の値を計測するとともに、上記シャフトと軸受外輪を相対的に回転させて起動トルクを計測し、計測結果に基づいて軸受隙間に対する起動トルクの変化特性を求め、求めた変化特性から軸受隙間を設定することを特徴とする。   A bearing assembling method according to the present invention is a bearing assembling method for adjusting a bearing gap between bearing inner rings for a combined bearing including a pair of rolling bearings mounted on an outer diameter of a shaft, and is an axial direction of the outer diameter. Insert a graduated sleeve with a scale into the inner diameter of the shaft, screw the graduated sleeve with a graduated thimble with a scale in the circumferential direction of the outer diameter, and insert the bearing from the end face of the shaft. With the inner ring protruding, the shaft and the bearing inner ring are sandwiched between the scaled sleeve and the scaled thimble, and the value of the scale is measured while the scaled thimble is rotated. Rotate to measure the starting torque, find the change characteristic of the starting torque with respect to the bearing gap based on the measurement result, and set the bearing gap from the obtained change characteristic And wherein the door.

この発明によれば、組合わせ軸受における予圧調整作業の際、適切な軸受隙間をより短時間で効率的に計測することができる、という効果が得られる。   According to the present invention, it is possible to obtain an effect that an appropriate bearing clearance can be efficiently measured in a shorter time during the preload adjustment work in the combined bearing.

実施の形態１．
以下、この発明に係る実施の形態１について説明する。図１は、実施の形態１による組立用治具を説明するための図であり、（ａ）は正面図、（ｂ）は断面図を示している。図２は、実施の形態１の組立用治具により組立てられた回転部の構成例を示す図であり、（ａ）は正面図、（ｂ）は断面図を示している。 Embodiment 1 FIG.
Embodiment 1 according to the present invention will be described below. 1A and 1B are diagrams for explaining an assembly jig according to Embodiment 1, wherein FIG. 1A is a front view and FIG. 1B is a cross-sectional view. 2A and 2B are diagrams illustrating a configuration example of a rotating unit assembled by the assembling jig of the first embodiment, where FIG. 2A is a front view and FIG. 2B is a cross-sectional view.

図１において、本実施の形態１による組立用治具１０は、目盛付きスリープ１２と、目盛付きシンブル１３と、挿入穴を有した穴付き平板としての２枚のワッシャ１１を備えて構成される。目盛付きスリープ１２は、一端側に鍔を有し、他端側の外径に軸方向に均等間隔で配列された目盛が設けられる。また、目盛付きスリープ１２の他端側の外径には、精密雄ねじが形成されている。目盛付きシンブル１３は、一端側の外径の円周方向に沿って、均等間隔で配列された目盛が設けられている。また、目盛付きシンブル１３は、内径に精密雌ねじが形成されるとともに、外径には人力で目盛付きシンブル１３を回すための操作用グリップ５０が設けられている。目盛付きスリープ１２と目盛付きシンブル１３は、目盛付きスリープ１２の精密雄ねじと目盛付きシンブル１３の精密雌ねじとが互いに螺合し、操作用グリップ５０を介して目盛付きシンブル１３を回転させることで、目盛付きスリープ１２の鍔と目盛付きシンブル１３の他端面との間隔を１０μｍ単位で精度良く調整することのできる、マイクロメータを構成する。目盛付きスリープ１２および目盛付きシンブル１３は、公知のマイクロメータの如くそれぞれが突き合う目盛が刻まれている。２枚のワッシャ１１は、その挿入穴に嵌め込むように目盛付きスリープ１２の外径を挿入することで、目盛付きスリープ１２の鍔と目盛付きシンブル１３の他端面の間に配置することができる。   In FIG. 1, the assembly jig 10 according to the first embodiment includes a sleep 12 with a scale, a thimble 13 with a scale, and two washers 11 as a flat plate with a hole having an insertion hole. . The scale-equipped sleep 12 has a ridge on one end side, and is provided with a scale arranged at equal intervals in the axial direction on the outer diameter on the other end side. A precision male screw is formed on the outer diameter of the other end of the graduated sleep 12. The scaled thimble 13 is provided with scales arranged at equal intervals along the circumferential direction of the outer diameter on one end side. The scaled thimble 13 has a precision female screw formed on the inner diameter, and the outer diameter is provided with an operation grip 50 for manually turning the scaled thimble 13. The scaled sleep 12 and the scaled thimble 13 are configured such that the precision male screw of the scaled sleep 12 and the precision female thread of the scaled thimble 13 are screwed together, and the scaled thimble 13 is rotated via the operation grip 50. The micrometer which can adjust the space | interval of the collar of the scaled sleep 12 and the other end surface of the scaled thimble 13 with a precision of 10 μm is configured. The scaled sleep 12 and the scaled thimble 13 are engraved with scales that face each other like a known micrometer. The two washers 11 can be arranged between the flange of the graduated sleep 12 and the other end face of the calibrated thimble 13 by inserting the outer diameter of the graduated sleep 12 so as to fit into the insertion hole. .

図２において、組立用治具１０を用いて組合わせ軸受の予圧調整を行い組立てられた回転部３０は、シャフト２３と、組合せ軸受を構成する軸受２４と、ハウジング２５と、リテーナ２６と、ボルトねじなどの締結部品２２および２７と、シムプレート２８を備えて構成される。軸受２４は互いに対向配置された一対の転がり軸受から構成され、各転がり軸受けは軸受内輪２４ａ、軸受外輪２４ｂを具備している。軸受内輪２４ａは複数の転動体２４ｃが接して嵌合され、軸受内輪２４ａの外側に軸受外輪２４ｂが設けられる。また、軸受外輪２４ｂは、軸受内輪２４ａと反対側の接触点で転動体２４ｃに接している。シャフト２３は、一端側に鍔としてのリテーナ２１が設けられている。シャフト２３は、その外径に軸受２４を構成する一対の軸受内輪２４ａが挿入され、一方の軸受内輪２４ａの端面がリテーナ２１に当接し、他方の軸受内輪２４ａの端面はシャフト２３の他端面から突き出ている。シャフト２３の他端側では、他方の軸受内輪２４ａの端面に当接してリテーナ２６が取付けられ、リテーナ２６は複数の締結部品２７によりシャフト２３に締結されている。また、シャフト２３の他端面とリテーナ２６との間隙に、シムプレート２８が挿入されている。ハウジング２５の内径には軸受外輪２４ｂが挿入されている。ここで、シャフト２３のリテーナ２１が一方の軸受外輪２４ｂの端面に接するように、リテーナ２１がハウジング２５に取付けられ、複数の締結部品２２により締結される。また、他方の軸受外輪２４ｂの端面はハウジング２５の内径に突出した段部に接している。このようにして、軸受２４は回転部３０に装着され、軸受２４を介してハウジング２５に対してシャフト２３が回転可能に軸支される。なお、複数の締結部品２２、２７は、それぞれ取付けられるリテーナに対し円周状に均等配置されてシャフト２３に固定されるので、軸受２４の予圧印加時に、軸受内輪２４ａへの片当たりを防止することができる。   In FIG. 2, the rotating part 30 assembled by performing preload adjustment of the combined bearing using the assembly jig 10 includes a shaft 23, a bearing 24 constituting the combined bearing, a housing 25, a retainer 26, and a bolt. Fastening parts 22 and 27 such as screws and a shim plate 28 are provided. The bearing 24 is composed of a pair of rolling bearings arranged to face each other, and each rolling bearing includes a bearing inner ring 24a and a bearing outer ring 24b. The bearing inner ring 24a is fitted in contact with a plurality of rolling elements 24c, and a bearing outer ring 24b is provided outside the bearing inner ring 24a. Further, the bearing outer ring 24b is in contact with the rolling element 24c at a contact point opposite to the bearing inner ring 24a. The shaft 23 is provided with a retainer 21 as a flange on one end side. A pair of bearing inner rings 24 a constituting the bearing 24 is inserted into the outer diameter of the shaft 23, the end face of one bearing inner ring 24 a abuts the retainer 21, and the end face of the other bearing inner ring 24 a is from the other end face of the shaft 23. Stick out. On the other end side of the shaft 23, a retainer 26 is attached in contact with the end face of the other bearing inner ring 24 a, and the retainer 26 is fastened to the shaft 23 by a plurality of fastening parts 27. A shim plate 28 is inserted in the gap between the other end surface of the shaft 23 and the retainer 26. A bearing outer ring 24 b is inserted into the inner diameter of the housing 25. Here, the retainer 21 is attached to the housing 25 and fastened by a plurality of fastening parts 22 so that the retainer 21 of the shaft 23 is in contact with the end face of one bearing outer ring 24 b. Further, the end surface of the other bearing outer ring 24 b is in contact with a stepped portion that protrudes to the inner diameter of the housing 25. In this way, the bearing 24 is mounted on the rotating portion 30, and the shaft 23 is rotatably supported with respect to the housing 25 via the bearing 24. Since the plurality of fastening parts 22 and 27 are equally arranged circumferentially with respect to the retainers to be attached and fixed to the shaft 23, the bearing inner ring 24a is prevented from being hit when the bearing 24 is preloaded. be able to.

次に、組立用治具１０を用いて、回転部３０に装着される軸受２４の予圧調整を行う手順について説明する。組立用治具１０は、シャフト２３の外径に対向配置された一対の転がり軸受から成る組合わせ軸受２４を装着し、一対の軸受内輪２４ａの一方をシャフト２３のリテーナ２１に当てた状態で、一対の軸受内輪２４ａ間の軸受隙間（アキシアル隙間）を調整する。以下、その手順の一例を述べる。   Next, a procedure for adjusting the preload of the bearing 24 attached to the rotating unit 30 using the assembly jig 10 will be described. The assembly jig 10 is mounted with a combination bearing 24 composed of a pair of rolling bearings arranged opposite to the outer diameter of the shaft 23, and one of the pair of bearing inner rings 24 a is in contact with the retainer 21 of the shaft 23. A bearing gap (axial gap) between the pair of bearing inner rings 24a is adjusted. An example of the procedure will be described below.

まず、ハウジング２５およびシャフト２３に軸受２４を嵌合し、リテーナ２１、締結部品２２で軸受外輪２４ｂを固定する。シャフト２３には、１対の軸受２４の軸受内輪２４ａが嵌合している。この状態では、２つの軸受内輪２４ａ間に間隙が有り、予圧が印加されていない（無予圧状態）。また、ハウジング２５は何らかの固定具により回り止めされた状態で、固定されている。   First, the bearing 24 is fitted to the housing 25 and the shaft 23, and the bearing outer ring 24 b is fixed by the retainer 21 and the fastening component 22. A bearing inner ring 24 a of a pair of bearings 24 is fitted to the shaft 23. In this state, there is a gap between the two bearing inner rings 24a, and no preload is applied (no preload state). Further, the housing 25 is fixed in a state in which the housing 25 is prevented from rotating by any fixing tool.

次に、シャフト２３に２枚のワッシャ１１と、目盛付きスリーブ１２および目盛付きシンブル１３を取付ける。このとき、目盛付きスリーブ１２の外径に１つ目のワッシャ１１を挿入後、シャフト２３の内径に目盛付きスリーブ１２の外径を挿入してから、目盛付きスリーブ１２の外径に２つ目のワッシャ１１を挿入する。なお、シャフト２３との片当たりが問題なければ、ワッシャ１１は１枚でも良い。   Next, the two washers 11, the scaled sleeve 12 and the scaled thimble 13 are attached to the shaft 23. At this time, after the first washer 11 is inserted into the outer diameter of the graduated sleeve 12, the outer diameter of the graduated sleeve 12 is inserted into the inner diameter of the shaft 23, and then the second outer diameter of the graduated sleeve 12 is added. Insert the washer 11. If there is no problem with the contact with the shaft 23, one washer 11 may be used.

その後、操作用グリップ５０を摘んで目盛付きシンブル１３を回しながら、目盛付きスリーブ１２の雄ねじを目盛付きシンブル１３の雄ねじに螺合させる。こうして、シャフト２３の鍔を１つ目のワッシャ１１に突き当て、目盛付きシンブル１３の他端面を２つ目のワッシャ１１に突き当て、目盛付きスリーブ１２の鍔と目盛付きシンブル１３の他端面とでシャフト２３およびワッシャ１１を挟み込む。この状態で、軸受内輪２４ａの端面がワッシャ１１に突当たり、一対の軸受内輪２４ａに予圧が加わる。   Thereafter, the male screw of the graduated sleeve 12 is screwed into the male screw of the graduated thimble 13 while picking the operation grip 50 and turning the graduated thimble 13. Thus, the flange of the shaft 23 is abutted against the first washer 11, the other end surface of the scaled thimble 13 is abutted against the second washer 11, the collar 12 of the scaled sleeve 12 and the other end surface of the scaled thimble 13 are Then, the shaft 23 and the washer 11 are sandwiched. In this state, the end surface of the bearing inner ring 24a abuts against the washer 11, and preload is applied to the pair of bearing inner rings 24a.

次に、操作用グリップ５０を摘んで目盛付きシンブル１３を少しずつ段階的に回し、軸受内輪２４ａに加える予圧を少しずつ上げる。このとき、目盛付きシンブル１３を少し回す毎に、目盛付きシンブル１３と目盛付きスリーブ１２が突き合った位置で、公知のマイクロメータと同様に目盛りの値ｘを読み取る。この目盛の読取値ｘの変化量は、軸受隙間（アキシアル隙間）の変化量に対応する。
また、読み取った値に対する回転部３０の摩擦トルクを測定する。目盛の読取値ｘは軸受隙間と同じ精度となるので、読取値ｘが数μｍで変化するように、目盛付きシンブル１３を回すと良い。この測定後、目盛の読取値ｘとその読取値ｘでの摩擦トルクの値Ｔｒとを対応付けて、同時に記録する。この摩擦トルクの測定は、例えば次のように行う。 Next, the operating grip 50 is picked and the scaled thimble 13 is gradually turned to gradually increase the preload applied to the bearing inner ring 24a. At this time, every time the scaled thimble 13 is turned a little, the scale value x is read at the position where the scaled thimble 13 and the scaled sleeve 12 face each other in the same manner as a known micrometer. The change amount of the scale reading value x corresponds to the change amount of the bearing gap (axial gap).
Further, the friction torque of the rotating unit 30 with respect to the read value is measured. Since the scale reading value x has the same accuracy as the bearing gap, the scaled thimble 13 may be rotated so that the reading value x changes by several μm. After this measurement, the scale reading value x and the friction torque value Tr at the reading value x are associated and recorded simultaneously. The friction torque is measured as follows, for example.

ａ）シャフト２３にトルク測定器具を取付ける。
ｂ）シャフト２３をハウジング２５に対して回転させるようにトルクを与え、シャフト２３が回転し始めたときの起動トルクをトルク測定器具により求め、この起動トルクを軸受２４の摩擦トルクＴｒとする。 a) A torque measuring instrument is attached to the shaft 23.
b) A torque is applied so as to rotate the shaft 23 with respect to the housing 25, the starting torque when the shaft 23 starts to rotate is obtained by a torque measuring instrument, and this starting torque is set as the friction torque Tr of the bearing 24.

トルク測定器具としては、例えばプッシュプルゲージや、トルク測定用モータを用いると良い。なお、トルク測定用モータを用いる場合は、モータの駆動電流を計測することでシャフト２３の起動トルクを求めて静止摩擦力を測定することができるが、モータを一定回転で回転させたときのモータの駆動電流を計測することで動摩擦トルクを求め、求めた動摩擦トルクを摩擦トルクとしても良い。   For example, a push-pull gauge or a torque measuring motor may be used as the torque measuring instrument. When a torque measuring motor is used, the starting frictional force of the shaft 23 can be obtained by measuring the driving current of the motor to measure the static frictional force. However, the motor when the motor is rotated at a constant rotation is used. Alternatively, the dynamic friction torque may be obtained by measuring the drive current, and the obtained dynamic friction torque may be used as the friction torque.

かくして、記録された目盛の読取値と摩擦トルク値に基づいて、適切な軸受隙間を求めることができる。
また、操作用グリップ５０を目盛付きシンブル１３に設けることで、モータを用いることなく、人力で軸受２４に予圧を加えることができる。 Thus, an appropriate bearing clearance can be obtained based on the recorded scale reading and friction torque value.
Further, by providing the operating grip 50 on the scaled thimble 13, the preload can be applied to the bearing 24 manually without using a motor.

なお、予め軸受内輪２４ａにおけるリテーナ２６側の端面と、シャフト２３におけるリテーナ２６側の他端面との間の距離をマイクロメータなどで寸法計測し、この求めた距離を軸受内輪２４ａがシャフト２３の他端面から突出する突出寸法Ｃとしておく。   The distance between the end surface of the bearing inner ring 24a on the retainer 26 side and the other end surface of the shaft 23 on the retainer 26 side is measured in advance with a micrometer or the like, and the obtained distance is determined by the bearing inner ring 24a other than the shaft 23. It is set as the protrusion dimension C which protrudes from an end surface.

次に、組立用治具１０を用いて、軸受２４の適切な軸受隙間を、簡単且つ短期間で求める手順について、次の１）〜６）の順に、図を用いて説明する。図３は組立時に取得する、（ａ）軸受の特性曲線と、（ｂ）軸受の挙動を示す図である。   Next, a procedure for obtaining an appropriate bearing gap of the bearing 24 using the assembly jig 10 in a simple and short period will be described in the order of the following 1) to 6) with reference to the drawings. FIG. 3 is a diagram showing (a) the characteristic curve of the bearing and (b) the behavior of the bearing acquired at the time of assembly.

１）まず、図３（ｂ）のＩの組立状態（無予圧時）における軸受２４の摩擦トルクを測定する。
２）次に、目盛付きシンブル１３を目盛付きスリーブ１２に螺合して軸受内輪２４ａに押し当てた際、目盛付きシンブル１３を回すことで数μｍ毎に得られる摩擦トルクの測定値を、目盛付きシンブル１３および目盛付きスリーブ１２の目盛の読取値と対応付けてグラフにプロットする。このプロット点から最小自乗法などで近似直線を求めて、図３（ａ）のII、IIIに示す軸受の特性曲線を得る。このとき、軸受２４の状態は、図３（ｂ）に示すようなIIまたはIIIの組立状態となる。なお、IIの組立状態は、軸受２４に予圧が加わった状態を示し、IIIの組立状態は、１対の軸受内輪２４ａが完全に接触した状態を示している。 1) First, the friction torque of the bearing 24 in the assembly state I in FIG. 3B (no preload) is measured.
2) Next, when the scaled thimble 13 is screwed onto the scaled sleeve 12 and pressed against the bearing inner ring 24a, the measured value of the friction torque obtained every few μm by turning the scaled thimble 13 is The graph is plotted in association with the readings of the scales of the scaled thimble 13 and the scaled sleeve 12. An approximate straight line is obtained from the plotted points by the method of least squares or the like, and the characteristic curves of the bearings shown in FIGS. At this time, the state of the bearing 24 becomes an assembled state of II or III as shown in FIG. The assembled state II indicates a state in which a preload is applied to the bearing 24, and the assembled state III indicates a state in which the pair of bearing inner rings 24a are completely in contact with each other.

３）次に、得られた特性曲線から、図３（ｂ）におけるII、IIIの直線の交点（折れ線部）に相当する組立状態（IIの組立状態からIIIの組立状態への遷移点）を求める。また、この折れ線部での摩擦トルクと軸受隙間を確認する。さらに、図３（ｂ）におけるI、IIの直線の交差点（折れ線部）に相当する組立状態（無予圧から予圧状態への遷移点）を求める。   3) Next, from the obtained characteristic curve, an assembly state (transition point from the assembly state of II to the assembly state of III) corresponding to the intersection (a broken line portion) of lines II and III in FIG. Ask. In addition, the friction torque and the bearing gap at this broken line portion are confirmed. Furthermore, the assembly state (transition point from the no preload to the preload state) corresponding to the intersection (broken line portion) of the straight lines I and II in FIG.

４）続いて、求められた２つの折れ線部から、軸受隙間の上限値および下限値を設定する。ここで、下限値は、図３（ａ）におけるIとIIの交点の値を示す。上限値は、図３（ａ）におけるIIとIIIの交点の値を示す。
この際、上記上限値から下限値の範囲内にて、軸受隙間を調整すれば、組合せ軸受２４の予圧不足（予圧抜け）や、予圧過多を防ぐことが可能となる。また、軸受を使用する部位によって、上記範囲内での予圧の大小を設定することが可能となる。
なお、図３（ａ）では図示の都合上、目盛の読取値ｘの記載を省略しているが、実際には目盛の読取値ｘを同グラフの横軸に併記し、軸受隙間０ｍｍに対応する目盛の読取値ｘ１、軸受隙間０．０１ｍｍに対応する目盛の読取値ｘ２などと記述しておく。 4) Subsequently, an upper limit value and a lower limit value of the bearing clearance are set from the two broken line portions obtained. Here, the lower limit value indicates the value of the intersection of I and II in FIG. The upper limit value indicates the value of the intersection of II and III in FIG.
At this time, if the bearing clearance is adjusted within the range from the upper limit value to the lower limit value, insufficient preload (preload loss) of the combined bearing 24 and excessive preload can be prevented. Moreover, it becomes possible to set the magnitude | size of the preload within the said range by the site | part which uses a bearing.
In FIG. 3 (a), the scale reading x is omitted for convenience of illustration, but actually, the scale reading x is shown along the horizontal axis of the graph, corresponding to a bearing clearance of 0 mm. The scale reading value x1 and the scale reading value x2 corresponding to the bearing gap of 0.01 mm are described.

５）４）にて設定した上限値から下限値の範囲内に収まるように軸受隙間δの値を設定し、設定した軸受隙間δに基づいて必要なシムプレートの厚さを求め、挿入するシムプレート２８を用意する。例えば、軸受隙間がδの場合、必要なシムプレート２８の厚さ（挿入量）ｔは次のように求められる。
シムプレート挿入量ｔ＝軸受内輪の突出寸法Ｃ−軸受隙間δ 5) The value of the bearing gap δ is set so that it falls within the range from the upper limit value set in 4) to the lower limit value, the required shim plate thickness is obtained based on the set bearing gap δ, and the shim to be inserted A plate 28 is prepared. For example, when the bearing clearance is δ, the necessary thickness (insertion amount) t of the shim plate 28 is obtained as follows.
Shim plate insertion amount t = projection dimension of bearing inner ring C−bearing clearance δ

なお、前述した軸受内輪の突出寸法Ｃは、例えば次のように求めることができる。
軸受２４を外した状態でワッシャ１１、目盛付きシンブル１３および目盛付きスリーブ１２をシャフト２３に組み付け、ワッシャ１１がシャフト２３の他端面に突当たる位置まで目盛付きシンブル１３を回し、このときの目盛の読取値ｘ０を記録しておく。
次に、目盛付きシンブル１３および目盛付きスリーブ１２を一旦取り外し、軸受２４を取付けた後、ワッシャ１１、目盛付きシンブル１３および目盛付きスリーブ１２をシャフト２３に再度組み付けてから、上記４）にて軸受隙間δを設定し、この設定した軸受隙間δに対応する目盛付きスリーブ１２の目盛りの読取値ｘｃを求めて、この目盛りの読取値ｘｃと目盛の読取値をｘ０との差分を、軸受内輪の突出寸法Ｃとする。
この際、目盛付きシンブル１３および目盛付きスリーブ１２の再組み付け時に、双方の目盛の突合せ位置がずれないように、組み付け位置合わせマーカを設けるなどして注意して組み付けを行う。 In addition, the protrusion dimension C of the bearing inner ring described above can be obtained, for example, as follows.
With the bearing 24 removed, the washer 11, the scaled thimble 13 and the scaled sleeve 12 are assembled to the shaft 23, and the scaled thimble 13 is turned to a position where the washer 11 abuts against the other end surface of the shaft 23. The read value x0 is recorded.
Next, after removing the scaled thimble 13 and the scaled sleeve 12 once and attaching the bearing 24, the washer 11, the scaled thimble 13 and the scaled sleeve 12 are assembled again to the shaft 23, and then the bearing in 4) above. A clearance δ is set, a scale reading xc of the scaled sleeve 12 corresponding to the set bearing clearance δ is obtained, and the difference between the scale reading xc and the scale reading x0 is set to The protruding dimension is C.
At this time, when reassembling the scaled thimble 13 and the scaled sleeve 12, the assembly is performed with care by providing an assembly alignment marker so that the abutment positions of both scales do not shift.

６）次に、ワッシャ１１、スリーブ１２、目盛付きシンブル１３を取り外し、用意したシムプレート２８をシャフト２３の他端面に当てるように、軸受内輪２４ａの内径に挿入する。続いて、リテーナ２６および締結部品２７をシャフト２３に取付け、締結部品２７をシャフト２３のねじ穴に締結して、軸受内輪２４ａを固定する。その後、再び摩擦トルクを測定し、摩擦トルクが所要の値となっていることを確認する。   6) Next, the washer 11, the sleeve 12, and the scaled thimble 13 are removed, and the prepared shim plate 28 is inserted into the inner diameter of the bearing inner ring 24a so as to contact the other end surface of the shaft 23. Subsequently, the retainer 26 and the fastening part 27 are attached to the shaft 23, and the fastening part 27 is fastened to the screw hole of the shaft 23 to fix the bearing inner ring 24a. Thereafter, the friction torque is measured again, and it is confirmed that the friction torque has a required value.

以上説明したとおり、この実施の形態１による軸受組立治具は、一端側に鍔の設けられたシャフトの外径に装着され、対向配置された一対の転がり軸受から成る組合わせ軸受について、一対の軸受内輪の一方を当該シャフトの鍔に当てた状態で、当該軸受内輪間の軸受隙間を調整するための軸受組立治具であって、一端面が当該軸受内輪の他方に当接する穴付き平板と、一端に鍔が設けられるとともに、他端側の外径の軸方向に目盛の刻まれた目盛付きスリーブと、一端側の外径の円周方向に目盛が刻まれ、他端面が上記穴付き平板の他端面に当接する目盛付きシンブルとを具備し、上記目盛付きスリーブが上記シャフトの内径および穴付き平板の穴に挿入され、上記シャフトの他端面から上記軸受内輪の他方が突出した状態で上記目盛付きスリーブの鍔と目盛付きシンブルの他端面の間に上記シャフトおよび穴付き平板を挟み、上記目盛付きシンブルと目盛付きスリーブとが互いの目盛を向き合わせて螺合したことを特徴とする。   As described above, the bearing assembly jig according to the first embodiment is a pair of rolling bearings mounted on the outer diameter of a shaft provided with a flange on one end side and arranged opposite to each other. A bearing assembly jig for adjusting a bearing clearance between the bearing inner rings in a state where one of the bearing inner rings is in contact with the flange of the shaft, and a flat plate with a hole whose one end surface abuts against the other of the bearing inner ring, A sleeve with a scale that is provided with a flange at one end and a scale is engraved in the axial direction of the outer diameter on the other end side, and a scale is engraved in the circumferential direction of the outer diameter on the one end side, and the other end surface has the above-mentioned hole A scaled thimble abutting against the other end surface of the flat plate, the sleeve with the scale being inserted into the inner diameter of the shaft and the hole of the holed flat plate, and the other end of the bearing inner ring protruding from the other end surface of the shaft With the above scale Sandwiching the rib of the flange and graduated other end face the shaft and the hole flat plate between the thimble, and the graduated thimble and graduated sleeve, characterized in that the screwed by opposed the scale of each other.

また、この実施の形態１による軸受の組立方法は、シャフトの他端面から上記軸受内輪の他方が突出した状態で穴付き平板の一端面を上記軸受内輪に当接させ、外径の軸方向に目盛の刻まれた目盛付きスリーブを、上記シャフトの内径および穴付き平板の挿入穴に挿入して、当該目盛付きスリーブと、外径の円周方向に目盛が刻まれた目盛付きシンブルとの間に、上記シャフトおよび穴付き平板を挟んで、当該目盛付きシンブルと目盛付きスリーブを螺合させ、上記目盛付きシンブルの操作用グリップを回しながら上記目盛の値を計測するとともに、上記シャフトもしくは組合わせ軸受の外輪側を回して起動トルクを計測し、計測結果に基づいて軸受隙間に対する起動トルクの変化率特性を求め、求めた変化率特性から適切な軸受隙間を設定して、シムプレートの挿入量を決定することを特徴とする。   Further, in the bearing assembly method according to the first embodiment, one end surface of the flat plate with holes is brought into contact with the bearing inner ring in a state where the other end of the bearing inner ring protrudes from the other end surface of the shaft, and the axial direction of the outer diameter is increased. Insert the graduated sleeve with the scale into the inner diameter of the shaft and the insertion hole of the flat plate with the hole, and between the graduated sleeve and the graduated thimble with the scale in the circumferential direction of the outer diameter In addition, the scaled thimble and the scaled sleeve are screwed together with the shaft and the flat plate with a hole interposed therebetween, and the value of the scale is measured while turning the operation grip of the scaled thimble, and the shaft or combination Rotate the outer ring side of the bearing to measure the starting torque, determine the change rate characteristic of the starting torque with respect to the bearing gap based on the measurement result, and set the appropriate bearing gap from the obtained change rate characteristic Te, and determines the insertion amount of the shim plate.

これにより、組合わせ軸受における予圧調整作業の際、適切な軸受隙間（アキシアル隙間）をより短時間で効率的に計測することができる、という効果が得られる。   Thereby, in the preload adjustment work in the combined bearing, an effect that an appropriate bearing gap (axial gap) can be efficiently measured in a shorter time is obtained.

なお、特開２００７−１８７２６４号公報には、軸受隙間を寸法管理しながら予圧を調整する装置が開示されている。しかし、この装置では、油圧サーボや直動シリンダ等の調整設備を要し、装置が複雑となり、大型化してしまう。このため、軸受を回転部に組み込んだ後、入り組んだ状態での調整が不可能となる。また、通常の圧入方法にて圧入し、ダイヤルゲージ等で軸受隙間を管理する手法では、圧入手段、測定手段が別々となってしまうために取り扱い性が悪くなる他、ダイヤルゲージ等の測定手段の設置方法によっては測定値に誤差が生じる恐れがある。これに対し、この実施の形態１では、組立用治具に予めマイクロメータが組み込まれているので、高精度に軸受隙間を測定することができる。また、油圧サーボや直動シリンダ等の大掛かりな調整設備が不要なので、装置構成が簡潔になるという利点がある。   Japanese Patent Application Laid-Open No. 2007-187264 discloses an apparatus for adjusting the preload while managing the size of the bearing gap. However, this apparatus requires adjustment equipment such as a hydraulic servo and a linear cylinder, which complicates the apparatus and increases its size. For this reason, after incorporating the bearing into the rotating part, adjustment in an intricate state becomes impossible. In addition, in the method of press-fitting by a normal press-fitting method and managing the bearing gap with a dial gauge or the like, the press-fitting means and the measuring means become separate, so that handling becomes worse, and the measuring means such as the dial gauge Depending on the installation method, an error may occur in the measured value. On the other hand, in this Embodiment 1, since the micrometer is previously incorporated in the assembling jig, the bearing gap can be measured with high accuracy. In addition, since a large-scale adjustment facility such as a hydraulic servo or a direct acting cylinder is unnecessary, there is an advantage that the apparatus configuration is simplified.

本発明に係る実施形態１による組立用治具の構成を示す図である。It is a figure which shows the structure of the assembly jig | tool by Embodiment 1 which concerns on this invention. 実施形態１による組立用治具を用いて、シムプレートによる定位置予圧にて軸受を組み込んだ例を示す図である。It is a figure which shows the example which incorporated the bearing by the fixed position preload by a shim plate using the assembly jig | tool by Embodiment 1. FIG. 本発明に係る実施形態１による組立時に取得する軸受の特性曲線及び軸受の挙動を示す図である。It is a figure which shows the characteristic curve of the bearing acquired at the time of the assembly by Embodiment 1 which concerns on this invention, and the behavior of a bearing.

符号の説明Explanation of symbols

１０ 組立用治具、１１ ワッシャ（穴付き平板）、１２ 目盛付きスリーブ、１３ 目盛付きシンブル、２１ リテーナ、２２ 締結部品、２３ シャフト、２４ 軸受、２４ａ 軸受内輪、２４ｂ 軸受外輪、２４ｃ 転動体、２５ ハウジング、２６ リテーナ、２７ 締結部品、２８ シムプレート、３０ 回転部、５０ 操作用グリップ。   10 assembly jig, 11 washer (flat plate with hole), 12 scaled sleeve, 13 scaled thimble, 21 retainer, 22 fastening parts, 23 shaft, 24 bearing, 24a bearing inner ring, 24b bearing outer ring, 24c rolling element, 25 Housing, 26 Retainer, 27 Fastener, 28 Shim plate, 30 Rotating part, 50 Grip for operation.

Claims (3)

シャフトの外径に装着された一対の転がり軸受から成る組合わせ軸受について、軸受内輪間の軸受隙間を調整する軸受組立治具であって、
外径の軸方向に目盛の刻まれた目盛付きスリーブと、
外径の円周方向に目盛が刻まれた目盛付きシンブルと、
を具備し、
上記目盛付きスリーブが上記シャフトの内径に挿入され、上記目盛付きシンブルと目盛付きスリーブを双方の目盛を向き合わせて螺合し、上記シャフトの端面から上記軸受内輪が突出した状態で、上記目盛付きスリーブと目盛付きシンブルとで上記シャフトおよび軸受内輪を挟み、上記軸受に予圧を与える軸受組立治具。 A bearing assembly jig for adjusting a bearing gap between inner bearing rings for a combined bearing comprising a pair of rolling bearings mounted on the outer diameter of the shaft,
A graduated sleeve engraved with a scale in the axial direction of the outer diameter;
A scaled thimble with a scale in the circumferential direction of the outer diameter,
Comprising
The graduated sleeve is inserted into the inner diameter of the shaft, the graduated thimble and the graduated sleeve are threaded with the scales facing each other, and the bearing inner ring protrudes from the end surface of the shaft. A bearing assembly jig for preloading the bearing by sandwiching the shaft and the bearing inner ring between a sleeve and a thimble with a scale. 上記目盛付きシンブルは操作用グリップを備えたことを特徴とする請求項１記載の軸受組立用治具。 2. The bearing assembly jig according to claim 1, wherein the scaled thimble includes an operation grip. シャフトの外径に装着された一対の転がり軸受から成る組合わせ軸受について、軸受内輪間の軸受隙間を調整する軸受組立方法であって、
外径の軸方向に目盛の刻まれた目盛付きスリーブを上記シャフトの内径に挿入し、当該目盛付きスリーブと外径の円周方向に目盛が刻まれた目盛付きシンブルを螺合させ、上記シャフトの端面から上記軸受内輪が突出した状態で、当該目盛付きスリーブと目盛付きシンブルとで上記シャフトおよび軸受内輪を挟み、
上記目盛付きシンブルを回しながら上記目盛の値を計測するとともに、上記シャフトと軸受外輪を相対的に回転させて起動トルクを計測し、計測結果に基づいて軸受隙間に対する起動トルクの変化特性を求め、求めた変化特性から軸受隙間を設定することを特徴とした軸受組立方法。 A combined bearing comprising a pair of rolling bearings mounted on the outer diameter of a shaft is a bearing assembly method for adjusting a bearing gap between bearing inner rings,
Insert a graduated sleeve with a scale in the axial direction of the outer diameter into the inner diameter of the shaft, and screw the graduated sleeve and a graduated thimble with a scale in the circumferential direction of the outer diameter into the shaft. With the bearing inner ring protruding from the end surface of the shaft, the shaft and the bearing inner ring are sandwiched between the scaled sleeve and the scaled thimble,
While measuring the value of the scale while turning the thimble with the scale, the starting torque is measured by relatively rotating the shaft and the bearing outer ring, and the change characteristic of the starting torque with respect to the bearing gap is obtained based on the measurement result, A bearing assembling method characterized in that a bearing clearance is set from the obtained change characteristics.
JP2008043073A 2008-02-25 2008-02-25 Fixture for assembling bearing and bearing assembling method Pending JP2009197978A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109027012A (en) * 2018-09-03 2018-12-18 平湖迪工机械制造有限公司 A kind of fixation thimble structure of cage winch
CN109443155A (en) * 2018-11-15 2019-03-08 广西汽车集团有限公司 A kind of method and tooling obtaining differential bearing spacer thickness
CN110238646A (en) * 2019-06-11 2019-09-17 广州铁路职业技术学院（广州铁路机械学校） Rail traction motor driving gear, which is surveyed, fills integrated tooling and its installation method
SE2151340A1 (en) * 2021-11-01 2023-05-02 Scania Cv Ab Method and control arrangement for quality assurance when mounting bearings
CN110238646B (en) * 2019-06-11 2024-06-04 广州铁路职业技术学院（广州铁路机械学校） Railway traction motor driving gear testing and assembling integrated tool and installing method thereof

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109027012A (en) * 2018-09-03 2018-12-18 平湖迪工机械制造有限公司 A kind of fixation thimble structure of cage winch
CN109443155A (en) * 2018-11-15 2019-03-08 广西汽车集团有限公司 A kind of method and tooling obtaining differential bearing spacer thickness
CN109443155B (en) * 2018-11-15 2023-12-12 广西汽车集团有限公司 Method and tool for obtaining thickness of differential bearing gasket
CN110238646A (en) * 2019-06-11 2019-09-17 广州铁路职业技术学院（广州铁路机械学校） Rail traction motor driving gear, which is surveyed, fills integrated tooling and its installation method
CN110238646B (en) * 2019-06-11 2024-06-04 广州铁路职业技术学院（广州铁路机械学校） Railway traction motor driving gear testing and assembling integrated tool and installing method thereof
SE2151340A1 (en) * 2021-11-01 2023-05-02 Scania Cv Ab Method and control arrangement for quality assurance when mounting bearings
SE545453C2 (en) * 2021-11-01 2023-09-19 Scania Cv Ab Method and control arrangement for quality assurance when mounting bearings

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