JP4442610B2 - Bearing structure - Google Patents
Bearing structure Download PDFInfo
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- JP4442610B2 JP4442610B2 JP2007011013A JP2007011013A JP4442610B2 JP 4442610 B2 JP4442610 B2 JP 4442610B2 JP 2007011013 A JP2007011013 A JP 2007011013A JP 2007011013 A JP2007011013 A JP 2007011013A JP 4442610 B2 JP4442610 B2 JP 4442610B2
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- bearing
- housing
- cut
- outer ring
- washer
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
- F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/10—Force connections, e.g. clamping
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Motor Or Generator Frames (AREA)
Description
本発明は、モータ等に使われる軸受構造、特に予圧をかけた状態でクリープを防止する軸受構造の改善に関する。 The present invention relates to a bearing structure used for a motor or the like, and more particularly to an improvement of a bearing structure that prevents creep in a state where a preload is applied.
産業用機器の駆動源に用いられるモータは、メンテナンスフリーが求められ、両持ち軸受構造のブラシレスモータが一般的であり、軸受にボールベアリング（以下、ベアリング）が用いられている。 A motor used as a drive source for industrial equipment is required to be maintenance-free, and a brushless motor having a double-sided bearing structure is generally used, and a ball bearing (hereinafter referred to as a bearing) is used as a bearing.
一般的にベアリングは、内輪と回転軸との間、外輪とハウジング内周面との間に隙間がある場合、伝達負荷によって回転軸にラジアル方向の力（側圧）が発生する。このとき、径方向の相対差によって滑り現象が発生しやすく、内輪を回転軸に圧入、外輪をハウジングに固定している（例えば、特許文献１参照）。 Generally, in the bearing, when there is a gap between the inner ring and the rotating shaft and between the outer ring and the inner peripheral surface of the housing, radial force (side pressure) is generated on the rotating shaft by the transmission load. At this time, a slip phenomenon is likely to occur due to a relative difference in the radial direction, the inner ring is press-fitted into the rotating shaft, and the outer ring is fixed to the housing (for example, see Patent Document 1).
ベアリングの長寿命化のためには、内輪および外輪のレース面とボールを安定した状態で同一軌道にて転動させる必要があり、軸方向に波形バネなどを用いて予圧をかけている。 In order to extend the life of the bearing, it is necessary to roll the race surfaces of the inner and outer rings and the ball in a stable state on the same track, and preload is applied in the axial direction using a wave spring or the like.
一方、軸受のクリープ防止及び軸受押えの抜け防止のため、ブラケットの軸受部内周に溝を設け、その溝に弾性体でできた軸受押えを挿入し、弾性体でできた軸受押えは、ブラケットの軸受部の外周より内側に多少突出させ、弾性力でベアリング外輪を固定する方式が提案されている(例えば、特許文献２参照)。
解決しようとする問題点は、ベアリングの適正予圧の確保とクリープ防止の両立が困難な点である。 The problem to be solved is that it is difficult to ensure proper preload of the bearing and prevent creep.
一般的に波形の板バネを用いて適正予圧を確保するが、予圧は軸方向に付勢されるため、予圧バネと外輪（あるいは内輪）とは点接触になる。 In general, a corrugated leaf spring is used to ensure an appropriate preload. However, since the preload is biased in the axial direction, the preload spring and the outer ring (or inner ring) are in point contact.
一方、予圧バネが当接する外輪（あるいは内輪）は、装着するハウジング（あるいは回転軸）に対して軸方向の移動が容易にできるように、径方向にわずかな隙間を設けている。 On the other hand, the outer ring (or inner ring) with which the preload spring contacts is provided with a slight gap in the radial direction so that it can be easily moved in the axial direction with respect to the housing (or rotating shaft) to be mounted.
予圧バネによる軸方向の付勢力に対して、負荷伝達により発生するラジアル方向の力が勝ると、外輪はハウジング内周面に押し付けられ、滑り接触してクリープを発生する。すなわち、ラジアル方向の力と隙間が大きいほどクリープが発生しやすくなり、防止するのが困難であった。 When the radial force generated by load transmission is greater than the axial biasing force generated by the preload spring, the outer ring is pressed against the inner peripheral surface of the housing, and slips to generate creep. That is, the larger the radial force and gap, the easier it is for creep to occur and it is difficult to prevent it.
これに対して、波形の予圧バネを平板のゴムに変更して接触面積を確保することも考えられる。しかし、圧縮量（変位）に対する予圧（圧縮力）のバラツキが大きくなり、適正予圧の確保ができにくい上、耐候性の面でも課題があった。 On the other hand, it is also conceivable to secure the contact area by changing the corrugated preload spring to a flat rubber. However, the dispersion of the preload (compression force) with respect to the compression amount (displacement) becomes large, and it is difficult to ensure an appropriate preload, and there is also a problem in terms of weather resistance.
また、特許文献２に開示された軸受構造は、外輪のクリープ防止には効果があるものの、外輪に対して弾性体の付勢力が印加されるため軸方向に負荷となり、安定した予圧をかけることができず、騒音や信頼性の面で課題があった。 Moreover, although the bearing structure disclosed in Patent Document 2 is effective in preventing creep of the outer ring, an urging force of an elastic body is applied to the outer ring, so that an axial load is applied and a stable preload is applied. There was a problem in terms of noise and reliability.
さらに、両側のベアリングを定位置に固定する定位置予圧方式は、軸隙間の調整が難しく、ベアリングを固定した構造物や回転軸の熱膨張によってベアリング固定間の寸法が変化して、予圧が変化する。予圧がなくなると回転精度が悪化し、振動や騒音が大きくなる。また、予圧が大きくなるとベアリングの寿命が短くなる。 In addition, the fixed position preload system that fixes the bearings on both sides in a fixed position makes adjustment of the shaft clearance difficult, and the structure between the bearings and the thermal expansion of the rotating shaft changes the dimensions between the fixed bearings, changing the preload. To do. When the preload is lost, the rotational accuracy deteriorates, and vibration and noise increase. In addition, when the preload is increased, the life of the bearing is shortened.
本発明は上記従来の課題を解決するものであり、過酷な使用環境に耐え、簡単な構成で適正予圧の確保とクリープを防止できる信頼性の高い軸受構造およびモータを提供することを目的とする。 SUMMARY OF THE INVENTION The present invention solves the above-described conventional problems, and an object thereof is to provide a highly reliable bearing structure and motor that can withstand harsh use environments and can ensure proper preload and prevent creep with a simple configuration. .
上記課題を解決するために本発明は、内輪に回転軸を固着したベアリングと、前記ベアリングを収納するハウジングと、前記ハウジングの底部に当接する波形の予圧バネと、前記ベアリングの外輪の端面と前記予圧バネに当接するワッシャとを備え、前記ワッシャは、環状の薄板にベアリング外周より板厚分だけ外側に突出した複数の切り起し部を有し、
前記切り起し部に対応する溝部を前記ハウジング内周面の軸方向に設け、前記溝部の幅は前記切り起し部が軸方向に容易に移動でき、前記溝部の深さは前記切り起し部に対して径方向に隙間を持ち、前記ベアリング外輪に圧入固定した前記切り起し部を前記溝部に係合させた軸受構造である。
The present invention in order to solve the above problems, the the bearing which is fixed to the rotating shaft to the inner ring, a housing for accommodating the bearing, and the preload spring abutting waveform at the bottom of the housing, the end face of the outer ring of the bearing and and a washer abutting the preload spring, the washer has a plurality of cut-and-raised portion protruding outward by the plate thickness amount than the bearing outer periphery to an annular thin plate,
A groove portion corresponding to the cut-and-raised portion is provided in the axial direction of the inner peripheral surface of the housing, the width of the groove portion is such that the cut-and-raised portion can easily move in the axial direction, and the depth of the groove portion is the cut-and-raised portion. The bearing structure has a gap in the radial direction with respect to the portion, and the cut and raised portion press-fitted and fixed to the bearing outer ring is engaged with the groove portion .
本発明の軸受構造によれば、ベアリング外輪に固定した突出部を有するワッシャとハウジング内周面に設けた溝部との凹凸係合によってベアリング外輪のクリープを防止でき、予圧バネによって適正予圧を確保することができる。 According to the bearing structure of the present invention, it is possible to prevent creep of the bearing outer ring by the concave and convex engagement between the washer having the protruding portion fixed to the bearing outer ring and the groove provided on the inner peripheral surface of the housing, and ensure proper preload by the preload spring. be able to.
また、突出部を、ワッシャの外周部に設けた切り起し部で構成したので、ベアリング外輪に圧入固定することができ、ハウジングへの装着が容易化できる。 Further, since the projecting portion is constituted by the cut-and-raised portion provided on the outer peripheral portion of the washer, it can be press-fitted and fixed to the bearing outer ring, and the mounting to the housing can be facilitated.
したがって、適正予圧をかけながらクリープを防止でき、安価で信頼性の高い軸受構造およびモータが得られる。 Therefore, creep can be prevented while applying an appropriate preload, and an inexpensive and highly reliable bearing structure and motor can be obtained.
内輪に回転軸を固着したベアリングと、前記ベアリングを収納するハウジングと、前記ハウジングの底部に当接する波形の予圧バネと、前記ベアリングの外輪の端面と前記予圧バネに当接するワッシャとを備え、前記ワッシャは、環状の薄板にベアリング外周より板厚分だけ外側に突出した複数の切り起し部を有し、前記切り起し部に対応する溝部を前記ハウジング内周面の軸方向に設け、前記溝部の幅は前記切り起し部が軸方向に容易に移動でき、前記溝部の深さは前記切り起し部に対して径方向に隙間を持ち、前記ベアリング外輪に圧入固定した前記切り起し部を前記溝部に係合させることで、適正予圧の確保と外輪クリープの防止を両立させることができる。 Comprising a bearing which is fixed to the rotating shaft to the inner ring, a housing for accommodating the bearing, and the preload spring abutting waveform at the bottom of the housing, the abutting washer on the end face and the preload spring of the outer ring of the bearing, The washer has a plurality of cut-and-raised portions protruding outward from the outer periphery of the bearing by a plate thickness on an annular thin plate, and a groove corresponding to the cut-and-raised portion is provided in the axial direction of the inner peripheral surface of the housing . The width of the groove is such that the cut-and-raised portion can easily move in the axial direction, and the depth of the groove has a radial gap with respect to the cut-and-raised portion, and the cut-and-raised Engaging the groove portion with the groove portion makes it possible to achieve both proper preload and prevention of outer ring creep.
以下、図を参照しながら説明する。図１は本発明の実施例１における軸受構造の要部断面図であり、ワッシャの外周に突起部として切り起し部を設けたものである。 Hereinafter, description will be given with reference to the drawings. FIG. 1 is a cross-sectional view of a main part of a bearing structure in Embodiment 1 of the present invention, in which a cut-and-raised portion is provided as a protrusion on the outer periphery of a washer.
図１において、１はベアリング、２は波形の予圧バネ、３はワッシャ、４はブラケットに一体構成したハウジング、５は回転軸である。 In FIG. 1, 1 is a bearing, 2 is a wave-like preload spring, 3 is a washer, 4 is a housing integrated with a bracket, and 5 is a rotating shaft.
まず、本発明の軸受構造の特徴について述べる。ワッシャ３は環状の薄板で、ベアリング１の外輪１ａと当接する位置に、ベアリング１の外径方向に突出する突出部３ａを、均等間隔に３箇所設けている。 First, the characteristics of the bearing structure of the present invention will be described. The washer 3 is an annular thin plate, and is provided with three protruding portions 3a projecting in the outer diameter direction of the bearing 1 at equal intervals at positions where the washer 3 is in contact with the outer ring 1a of the bearing 1.
この突出部３ａを平板で径方向に設ける場合、ワッシャ３と外輪１ａの当接部を溶接固定する必要があるため、溶接に適した材料を選定する。 When providing this protrusion part 3a in the radial direction with a flat plate, since it is necessary to weld-fix the contact part of the washer 3 and the outer ring | wheel 1a, the material suitable for welding is selected.
一方、ハウジング４にベアリング１を装着する際に、ワッシャ３の外周に設けた突出部３ａが邪魔をするため、突出部３ａを逃げるための溝部４ａを設ける必要がある。このため、ハウジング４の内周面の軸方向に、突出部３ａに対応するよう溝部４ａを設けている。この溝部４ａの幅は、突出部３ａが軸方向に容易に移動でき、深さは突出部３ａに対して径方向に逃げる程度でよい。 On the other hand, when the bearing 1 is mounted on the housing 4, the protrusion 3 a provided on the outer periphery of the washer 3 interferes with the groove 4 a for escaping the protrusion 3 a. For this reason, the groove part 4a is provided in the axial direction of the inner peripheral surface of the housing 4 so as to correspond to the protruding part 3a. The width of the groove portion 4a may be such that the protruding portion 3a can easily move in the axial direction and the depth can escape from the protruding portion 3a in the radial direction.
また、ハウジング４には、予圧バネ２が当接する底部４ｂを設ける。ハウジング４が出力軸側であれば、回転軸用の貫通孔を設ければよい。 Further, the housing 4 is provided with a bottom portion 4b with which the preload spring 2 abuts. If the housing 4 is on the output shaft side, a through hole for the rotating shaft may be provided.
実施例１では、溶接固定をしなくてもよいように、突出部３ａを切り起し部で構成する
。このため、ベアリング１の外周からの突出寸法は、板厚分である。この切り起し部を設けることで、あらかじめワッシャ３を外輪１ａに圧入固定することができる。
In Example 1, the protrusion part 3a is comprised by a raising part so that welding fixation may not be carried out. For this reason, the protrusion dimension from the outer periphery of the bearing 1 is a plate | board thickness part. By providing this cut and raised portion, the washer 3 can be press-fitted and fixed to the outer ring 1a in advance.
なお、ワッシャ３の突出部３ａの軸方向寸法（実施例１では折り曲げ長さ）をＸとし、ベアリング外輪１ａの軸方向長さをＬとしたとき、Ｘ＝０.３Ｌ程度を目安とするが、使
用環境温度などを考慮して、クリープの発生を防止できる程度の保持力が確保できるように設定する。
Note that when the axial dimension of the protruding portion 3a of the washer 3 (bending length in the first embodiment) is X and the axial length of the bearing outer ring 1a is L, X is about 0.3L. In consideration of the operating environment temperature, etc., it is set so as to secure a holding force that can prevent the occurrence of creep.
ここで組み付けについて説明する。まず、ベアリング１の外輪１ａとワッシャ３の突出部である切り起し部３ａをあらかじめ圧入により機械的に固定する。これにより、ベアリング１の外輪１ａ片端に突起が付いた状態となる。 Here, assembly will be described. First, the outer ring 1a of the bearing 1 and the cut-and-raised portion 3a that is the protruding portion of the washer 3 are mechanically fixed in advance by press-fitting. Thereby, it will be in the state where the projection was attached to the one end of outer ring 1a of bearing 1.
次に、外輪１ａにワッシャ３を装着したベアリング１の内輪１ｂを、回転軸５に設けた段付部まで圧入する。そして、ワッシャ３の上に予圧バネ２をのせ、ハウジング４に設けた溝４ａと、ワッシャ３の突出部３ａとを回転方向に合わせた状態で所定位置まで挿入し、ハウジング４の底部４ｂに当接させる。なお、予圧バネ２が軸方向に圧縮される量は、従来と同様に各部品寸法を考慮して初期的に決定している。 Next, the inner ring 1 b of the bearing 1 with the washer 3 attached to the outer ring 1 a is press-fitted to the stepped portion provided on the rotating shaft 5. Then, the preload spring 2 is placed on the washer 3, and the groove 4 a provided in the housing 4 and the protruding portion 3 a of the washer 3 are inserted to a predetermined position in the rotational direction, and contacted with the bottom 4 b of the housing 4. Make contact. Note that the amount by which the preload spring 2 is compressed in the axial direction is initially determined in consideration of the dimensions of each component as in the prior art.
ワッシャ３と一体化されたベアリング１の外輪１ａは、ハウジング４の内周面に設けた溝部４ａ以外で保持することになるため、突出部３ａの幅は、ハウジング４の内周面への組み付け精度を考慮して小さく設定するのが好ましい。これにより、通常と同様にブラケットのハウジング４に高精度で挿入することができる。 Since the outer ring 1 a of the bearing 1 integrated with the washer 3 is held by a portion other than the groove 4 a provided on the inner peripheral surface of the housing 4, the width of the protruding portion 3 a is set to the inner peripheral surface of the housing 4. It is preferable to set a small value in consideration of accuracy. Thereby, it can insert in the housing 4 of a bracket with high precision like usual.
この構成により、ワッシャ３を外輪１ａに圧入したベアリング１は、溝部４ａに沿ってハウジング４内を軸方向に移動させることができる。そして、予圧バネ２は、ワッシャ３の端面とハウジング４の底部４ｂ間で圧縮される。ベアリング１の内輪１ｂは回転軸５に圧入固着されているので、予圧バネ２の反発力はベアリング１に予圧として作用する。 With this configuration, the bearing 1 in which the washer 3 is press-fitted into the outer ring 1a can be moved in the housing 4 in the axial direction along the groove 4a. The preload spring 2 is compressed between the end face of the washer 3 and the bottom 4 b of the housing 4. Since the inner ring 1 b of the bearing 1 is press-fitted and fixed to the rotating shaft 5, the repulsive force of the preload spring 2 acts on the bearing 1 as a preload.
一方、ワッシャ３の突出部３ａは、外輪１ａに圧入固定されており、かつ、溝部４ａと凹凸係合している。したがって、側圧などで回転方向に作用するトルクが、突出部３ａの圧入保持力によって得られるトルク以下であれば、ワッシャ３が回転方向に動くことはなく、確実にクリープを防止することができる。 On the other hand, the protruding portion 3a of the washer 3 is press-fitted and fixed to the outer ring 1a, and is engaged with the groove portion 4a. Therefore, if the torque acting in the rotational direction by the side pressure or the like is equal to or less than the torque obtained by the press-fitting holding force of the protrusion 3a, the washer 3 does not move in the rotational direction, and creep can be reliably prevented.
なお、実施例１では、突出部を３ケ所で説明したが、クリープ防止に必要な保持力とハウジング内周の保持面積を考慮して決定すればよい。また、ハウジングは、ブラケットと別体で構成してもよい。 In the first embodiment, the three protrusions have been described. However, the protrusion may be determined in consideration of the holding force necessary for preventing creep and the holding area of the inner periphery of the housing. The housing may be configured separately from the bracket.
実施例２の軸受構造は、実施例１のワッシャと予圧バネを一体化し、ワッシャの突起部を予圧バネ側に設けたものであり、それ以外は、実施例１と同様である。 The bearing structure of the second embodiment is the same as that of the first embodiment except that the washer of the first embodiment and the preload spring are integrated and the washer protrusion is provided on the preload spring side.
図２は、その要部断面図を示したものであり、図２において、２１はベアリング、２２は予圧バネ、２２ａは突出部としての切り起し部、２４はブラケットに一体構成したハウジング、２５は回転軸である。 FIG. 2 shows a cross-sectional view of the main part. In FIG. 2, 21 is a bearing, 22 is a preload spring, 22a is a cut-and-raised part as a projecting part, 24 is a housing integrated with a bracket, 25 Is a rotation axis.
ワッシャと予圧バネを一体化し、突起部を予圧バネ側に設ける実施例２では、予圧バネをベアリング２１の外輪に溶接することは困難である。 In the second embodiment in which the washer and the preload spring are integrated and the protrusion is provided on the preload spring side, it is difficult to weld the preload spring to the outer ring of the bearing 21.
そこで、突起部としての切り起し部２２ａを、波形の予圧バネ２２がベアリング２１の外輪と当接する底部（３ケ所）に設けて、ベアリング２１の外周に対して圧入となるよう
に寸法を設定する。なお、切り起し部２２ａの幅と軸方向の寸法については、実施例１と同様であり、ここでは説明を省略する。
Therefore, the cut-and-raised part 22a as a protrusion is provided at the bottom (three places) where the wave-shaped preload spring 22 comes into contact with the outer ring of the bearing 21, and the dimensions are set so as to be press-fitted to the outer periphery of the bearing 21. To do. Note that the width and the axial dimension of the cut-and-raised portion 22a are the same as those in the first embodiment, and the description thereof is omitted here.
一方、ハウジング２４の内周面には、切り起し部２２ａが軸方向に移動できるように溝部２４ａを備えている。 On the other hand, a groove portion 24a is provided on the inner peripheral surface of the housing 24 so that the cut and raised portion 22a can move in the axial direction.
まず、切り起し部２２ａを有する予圧バネ２２を、あらかじめベアリング２１の外輪に圧入固定しておき、次に、ベアリング２１の内輪を回転軸２５に圧入する。 First, the preload spring 22 having the cut-and-raised part 22 a is press-fitted and fixed to the outer ring of the bearing 21 in advance, and then the inner ring of the bearing 21 is press-fitted into the rotary shaft 25.
この後、切り起し部２２ａをハウジング２４の溝部２４ａに位置合わせして、所定位置まで挿入して固定すれば、予圧バネ２２は底部２４ｂに当接して圧縮され、反発力がベアリング２１の予圧として作用する。 Thereafter, if the cut and raised portion 22a is aligned with the groove portion 24a of the housing 24 and is inserted and fixed to a predetermined position, the preload spring 22 is compressed by contacting the bottom portion 24b and the repulsive force is applied to the preload of the bearing 21. Acts as
実施例３は、両持ち軸受モータの出力軸側に、本発明の軸受構造を用いたものである。軸受構造は実施例１と同じであり、ここでは、代表的な組立工程を中心にして説明する。 In the third embodiment, the bearing structure of the present invention is used on the output shaft side of the double-end bearing motor. The bearing structure is the same as that of the first embodiment, and here, a description will be given focusing on a typical assembly process.
図３において、３１はベアリング、３２は予圧バネ、３３はワッシャ、３４は出力軸側ブラケットに一体構成したハウジング、３５はロータで回転軸を備えている。３６は固定子、３７はフレーム、３８は反出力軸側のベアリング、３９は反出力軸側ブラケット、４０は押さえ板、４１は固定ネジである。 In FIG. 3, 31 is a bearing, 32 is a preload spring, 33 is a washer, 34 is a housing integrated with the output shaft side bracket, 35 is a rotor and has a rotating shaft. 36 is a stator, 37 is a frame, 38 is a bearing on the side opposite to the output shaft, 39 is a bracket on the side opposite to the output shaft, 40 is a pressing plate, and 41 is a fixing screw.
まず、出力軸側に使用するベアリング３１の外輪３１ａの片端側に、ワッシャ３３の切り起し部３３ａを圧入固定しておく。 First, the cut and raised portion 33a of the washer 33 is press-fitted and fixed to one end side of the outer ring 31a of the bearing 31 used on the output shaft side.
次に、ブラケット３９のハウジングに反出力軸側のベアリング３８を挿入し、押さえ板４０と固定ネジ４１で、ベアリング３８の外輪３８ａをブラケット３９に固定して、外輪３８ａのクリープを防止する。そして、ブラケット３９にベアリング３８を装着した状態で、内輪３８ｂの端面を押しながらロータ３５の反出力軸側の回転軸３５ａに圧入する。 Next, the bearing 38 on the side opposite to the output shaft is inserted into the housing of the bracket 39, and the outer ring 38a of the bearing 38 is fixed to the bracket 39 with the pressing plate 40 and the fixing screw 41, thereby preventing the outer ring 38a from creeping. Then, while the bearing 38 is mounted on the bracket 39, the bearing is pressed into the rotating shaft 35 a on the side opposite to the output shaft of the rotor 35 while pushing the end surface of the inner ring 38 b.
さらに、出力軸側の回転軸３５ａに、ワッシャ３３を圧入固定したベアリング３１の内輪３１ｂを圧入する。このとき、内輪３８ｂの端面を受けた状態で、内輪３１ｂを押しながら圧入する。これにより、ブラケット３９とロータ３５とはベアリング３８を介して連結された状態となる。 Further, the inner ring 31b of the bearing 31 with the washer 33 press-fitted and fixed is press-fitted into the rotary shaft 35a on the output shaft side. At this time, in a state where the end face of the inner ring 38b is received, the inner ring 31b is pressed and pressed. As a result, the bracket 39 and the rotor 35 are connected via the bearing 38.
この回転軸３５ａには、両方のベアリング内輪が所定位置で止まるように段付加工を施しており、内輪端面が当接するまで圧入する。 The rotating shaft 35a is stepped so that both bearing inner rings stop at a predetermined position, and press-fit until the inner ring end face comes into contact.
固定子３６の外周には、予めフレーム３７を焼バメなどで固定しておき、ロータ３５の外周を固定子３６の内周部に収納し、フレーム３７とブラケット３９とを所定位置で係合固定する。 The frame 37 is fixed to the outer periphery of the stator 36 in advance by shrinkage or the like, the outer periphery of the rotor 35 is stored in the inner peripheral portion of the stator 36, and the frame 37 and the bracket 39 are engaged and fixed at a predetermined position. To do.
最後に、出力軸側ブラケットのハウジング３４にベアリング３１の外輪３１ａを収納して、所定位置でフレーム３７と出力軸側ブラケットを固定する。このとき、ブラケットのハウジング３４に設けた溝３４ａとベアリング３１の外輪３１ａに圧入固定したワッシャ３３の切り起し部３３ａを係合させた上で、ベアリングの外輪３１ａをハウジング３４に収納する。 Finally, the outer ring 31a of the bearing 31 is housed in the housing 34 of the output shaft side bracket, and the frame 37 and the output shaft side bracket are fixed at a predetermined position. At this time, the outer ring 31a of the bearing is accommodated in the housing 34 after engaging the groove 34a provided in the housing 34 of the bracket and the cut-and-raised portion 33a of the washer 33 press-fitted into the outer ring 31a of the bearing 31.
これにより予圧バネ３２は、ワッシャ３３の端面と、ハウジング３４の底部３４ｂで所定寸法に圧縮され、ベアリング３１とベアリング３８の予圧として作用し、適正予圧を確
保することができる。
As a result, the preload spring 32 is compressed to a predetermined size by the end face of the washer 33 and the bottom 34b of the housing 34, and acts as a preload for the bearing 31 and the bearing 38 to ensure an appropriate preload.
また、ベアリング３１の内輪３１ｂおよびベアリング３８の内輪３８ｂは、回転軸３５ａに圧入固定されており、両内輪のクリープを防止することができる。一方、ベアリング３１の外輪３１ａは、圧入固定したワッシャ３３の切り起し部３３ａを介してハウジング３４の溝３４ａに回転方向に係合しており、外輪３１ａのクリープを防止することができる。さらに、ベアリング３８の外輪３８ａは、ブラケット３９に押え板４０でネジ固定され、クリープを防止することができる。 Further, the inner ring 31b of the bearing 31 and the inner ring 38b of the bearing 38 are press-fitted and fixed to the rotary shaft 35a, and creeping of both inner rings can be prevented. On the other hand, the outer ring 31a of the bearing 31 is engaged with the groove 34a of the housing 34 via the cut-and-raised portion 33a of the washer 33 that is press-fitted and fixed, so that the outer ring 31a can be prevented from creeping. Further, the outer ring 38a of the bearing 38 is screwed to the bracket 39 with a presser plate 40, thereby preventing creep.
したがって、適正予圧を保持しながらクリープを防止できる信頼性の高い両持ち軸受構造のモータを得ることができる。 Therefore, it is possible to obtain a highly reliable motor having a double-end bearing structure capable of preventing creep while maintaining an appropriate preload.
本発明の軸受構造は、過酷な環境、条件下で使用される大型のサーボモータなどのクリープ防止に有用である。 The bearing structure of the present invention is useful for preventing creep of a large servo motor used under severe environments and conditions.
１，２１，３１，３８ ベアリング
１ａ，３１ａ，３８ａ 外輪
１ｂ，３１ｂ，３８ｂ 内輪
２，２２，３２ 予圧バネ
３ａ，２２ａ，３３ａ 突出部（切り起し部）
３，３３ ワッシャ
４，２４，３４ ハウジング(ブラケット)
４ａ，２４ａ，３４ａ 溝部
４ｂ，２４ｂ，３４ｂ 底部
５，２５，３５ａ 回転軸
３５ ロータ
３６ 固定子
３７ フレーム
３８ ベアリング
３９ ブラケット
４０ 押さえ板
４１ 固定ネジ
1, 21, 31, 38 Bearing 1a, 31a, 38a Outer ring 1b, 31b, 38b Inner ring 2, 22, 32 Preload spring 3a, 22a, 33a Protruding part (cut-up part)
3,33 Washer 4,24,34 Housing (bracket)
4a, 24a, 34a Groove 4b, 24b, 34b Bottom 5, 25, 35a Rotating shaft 35 Rotor 36 Stator 37 Frame 38 Bearing 39 Bracket 40 Holding plate 41 Fixing screw
Claims (1)
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| JP2007011013A JP4442610B2 (en) | 2007-01-22 | 2007-01-22 | Bearing structure |
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| Application Number | Priority Date | Filing Date | Title |
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| JP2007011013A JP4442610B2 (en) | 2007-01-22 | 2007-01-22 | Bearing structure |
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| JP4442610B2 true JP4442610B2 (en) | 2010-03-31 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11353061B1 (en) | 2020-12-14 | 2022-06-07 | Schaeffler Technologies AG & Co. KG | Preloaded shaft assembly |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6437950B2 (en) * | 2016-04-13 | 2018-12-12 | ミネベアミツミ株式会社 | motor |
| DE102016211306A1 (en) * | 2016-06-23 | 2017-12-28 | Robert Bosch Gmbh | Electric machine with a rotor and manufacturing process for the electric machine |
| CN111937277A (en) * | 2018-03-29 | 2020-11-13 | 日本电产株式会社 | Motor with a stator having a stator core |
| KR102020727B1 (en) * | 2018-04-26 | 2019-09-10 | 엘지전자 주식회사 | A Fan Motor |
| KR102396910B1 (en) * | 2018-04-26 | 2022-05-13 | 엘지전자 주식회사 | A Fan Motor |
| US20230061724A1 (en) * | 2020-02-28 | 2023-03-02 | Mitsubishi Electric Corporation | Motor, blower, and air conditioner |
| DE102020204579A1 (en) * | 2020-04-09 | 2021-10-14 | Aktiebolaget Skf | Storage unit and method for manufacturing a storage unit |
| KR102608743B1 (en) * | 2021-02-24 | 2023-12-01 | 엘지전자 주식회사 | Electric motor |
| US11933357B2 (en) * | 2021-06-16 | 2024-03-19 | Schaeffler Technologies AG & Co. KG | Bearing with integrated axial preload and method thereof |
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2007
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11353061B1 (en) | 2020-12-14 | 2022-06-07 | Schaeffler Technologies AG & Co. KG | Preloaded shaft assembly |
| WO2022132365A1 (en) * | 2020-12-14 | 2022-06-23 | Schaeffler Technologies AG & Co. KG | Preloaded shaft assembly |
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