JPH09126234A - Spherical sliding bearing - Google Patents
Spherical sliding bearingInfo
- Publication number
- JPH09126234A JPH09126234A JP7284910A JP28491095A JPH09126234A JP H09126234 A JPH09126234 A JP H09126234A JP 7284910 A JP7284910 A JP 7284910A JP 28491095 A JP28491095 A JP 28491095A JP H09126234 A JPH09126234 A JP H09126234A
- Authority
- JP
- Japan
- Prior art keywords
- inner ring
- sleeve
- ring
- fitting
- plain bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
- F16C23/043—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings
- F16C23/045—Sliding-contact bearings self-adjusting with spherical surfaces, e.g. spherical plain bearings for radial load mainly, e.g. radial spherical plain bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、球面すべり軸受に
関する。TECHNICAL FIELD The present invention relates to a spherical plain bearing.
【０００２】[0002]
【従来の技術】この種の球面すべり軸受は、各種の機械
構造の揺動部分の軸受として使用されている。2. Description of the Related Art Spherical plain bearings of this type are used as bearings for rocking parts of various mechanical structures.
【０００３】ここで、球面すべり軸受の内輪や外輪は、
これら両者のはめ合わせを可能とするために、外輪にそ
の内周一端側に内輪入れ溝を形成したり、あるいは内輪
または外輪のいずれかを径方向に沿うとともに軸心を通
る面で半割り状に二分割するようになっている。Here, the inner ring and outer ring of the spherical plain bearing are
In order to enable these two to fit together, an inner ring insertion groove is formed on the outer ring on one end side of its inner circumference, or either the inner ring or the outer ring is halved along the radial direction and through the axial center. It is designed to be divided into two.
【０００４】なお、内・外輪の素材は、例えば金属素材
で形成することが一般的である。この他、本願発明者ら
は、高温環境での使用を踏まえ、冷却とか潤滑などの特
別な装置を用いずに、すべり面での焼き付け寿命を延ば
すために、内・外輪の素材をセラミックスとすることを
提案し、その実用化を可能とするような研究を鋭意重ね
ている。The materials for the inner and outer rings are generally made of, for example, a metal material. In addition to this, the inventors of the present application use ceramics as the material of the inner and outer rings in order to extend the baking life on the sliding surface without using a special device such as cooling or lubrication in consideration of use in a high temperature environment. We are proactively researching ways to make it practical.
【０００５】[0005]
【発明が解決しようとする課題】ところで、近年では、
常温超電導体の実用化に伴い超電導磁石などを支える部
分に球面すべり軸受を使用することが要求される場合が
ある。この使用環境は、超電導磁石に関連して液体窒素
や液体ヘリウムなどの冷却要素が存在することになり、
環境温度が超低温となる。However, in recent years,
With the commercialization of room-temperature superconductors, it may be required to use spherical plain bearings in the portions that support superconducting magnets. This use environment means that there are cooling elements such as liquid nitrogen and liquid helium in association with the superconducting magnet.
The ambient temperature becomes extremely low.
【０００６】このような超低温環境では、適当な潤滑剤
が存在しないため、軸受の摩耗や動作不良などの不具合
を発生しやすい。軸受の内輪と外輪を同種の材料で製作
した場合、いわゆる“とも擦り”という現象により摩耗
が増加することが考えられる。これを防ぐため、軸受の
内・外輪のどちらかをセラミック材料、他を金属材料と
する組み合わせが考えられるが、両者の熱収縮率の違い
により超低温環境では、軸受のがたつきあるいは隙間詰
りを発生する危険性がある。つまり、軸受の初期隙間の
管理が重要となる。[0006] In such an ultra-low temperature environment, since no suitable lubricant is present, problems such as wear and malfunction of the bearing are likely to occur. When the inner ring and the outer ring of the bearing are made of the same kind of material, it is conceivable that the wear increases due to the phenomenon of "rubbing". In order to prevent this, a combination of either the inner or outer ring of the bearing with a ceramic material and the other with a metal material is conceivable.However, due to the difference in heat shrinkage between the bearings, rattling or gap clogging of the bearing may occur in ultra-low temperature environments. There is a risk of this occurring. That is, it is important to manage the initial clearance of the bearing.
【０００７】これに対して、組み立て時に、予め、熱収
縮に伴う内・外輪間の嵌め合い隙間の広がりを見込ん
で、外輪と揺動軸との間の組立隙間を小さく設定してお
いて内・外輪間の嵌め合い隙間を可及的に小さくするこ
とが考えられる。この調整のために、組み立て時に内・
外輪を組み合わせた状態でその内輪に対して揺動軸を圧
入するのであるが、この球面すべり軸受の内・外輪が分
離する構造であるために組立作業の取り扱いが煩雑にな
ることが指摘される。また、前述の組立隙間を小さくす
る量によっては圧入そのものの作業が無理になるなど、
組み立て時の嵌め合い隙間の管理に限界があることが指
摘される。On the other hand, at the time of assembly, the assembly gap between the outer ring and the swing shaft is set to a small value in advance by anticipating the expansion of the fitting gap between the inner ring and the outer ring due to heat shrinkage. -It is possible to make the fitting gap between the outer rings as small as possible. Due to this adjustment,
It is pointed out that the swing shaft is pressed into the inner ring with the outer ring combined, but the assembly work is complicated because the inner and outer rings of this spherical plain bearing are separated. . Also, depending on the amount to reduce the assembly gap described above, the work of press fitting itself becomes impossible,
It is pointed out that there is a limit to the control of the fitting gap during assembly.
【０００８】したがって、本発明は、熱収縮した状態に
おいて内・外輪の嵌め合い隙間を適正にするための組立
作業を簡略化できるようにするとともに、組み立て時の
嵌め合い隙間の調整幅を拡大できるようにすることを目
的としている。Therefore, according to the present invention, it is possible to simplify the assembling work for making the fitting gap between the inner and outer rings proper in the heat-shrinked state, and to expand the adjustment width of the fitting gap at the time of assembly. The purpose is to do so.
【０００９】[0009]
【課題を解決するための手段】本発明の球面すべり軸受
は、凸球面状の外周面を有しかつ径方向に沿うとともに
軸心を通る面で分割されてなる内輪と、内輪の外径側に
相対的に滑動可能に嵌合される外輪と、内輪の内径側に
嵌合されるとともに軸に外嵌されるスリーブとを含む構
成である。A spherical plain bearing of the present invention has an inner ring having an outer peripheral surface of a convex spherical surface, which is divided by a surface extending in the radial direction and passing through the axial center, and an outer diameter side of the inner ring. The outer ring is slidably fitted to the inner ring, and the sleeve is fitted on the inner diameter side of the inner ring and is fitted on the shaft.
【００１０】なお、前述の内輪とスリーブとの両嵌合面
は、軸方向に傾斜するテーパ状に形成するのが好まし
い。また、前述の内輪を非磁性金属とし、外輪を内輪よ
りも線膨張係数の小さい材料とし、スリーブを内輪の線
膨張係数とほぼ同じかあるいは大きい材料とするのが好
ましい。It is preferable that both the fitting surfaces of the inner ring and the sleeve described above are formed in a tapered shape inclined in the axial direction. Further, it is preferable that the inner ring is made of a non-magnetic metal, the outer ring is made of a material having a smaller linear expansion coefficient than the inner ring, and the sleeve is made of a material which is substantially the same as or larger than the linear expansion coefficient of the inner ring.
【００１１】このような本発明では、スリーブを備える
ことによって球面すべり軸受の各要素を非分離に組み合
わせることができ、その取り扱いが良好となる。しか
も、組み立て時において、内・外輪間の嵌め合い隙間は
スリーブの外径寸法により調整できるようになり、軸と
スリーブとの間のはめ合い隙間はスリーブの内径寸法に
より調整できるようになる。つまり、これら２カ所の隙
間調整でもって、使用環境での各部の熱収縮を見込む調
整を行うことができるから、組み立て時の嵌め合い隙間
の調整幅を拡大できるようになる。In the present invention as described above, by providing the sleeve, the respective elements of the spherical plain bearing can be combined in a non-separable manner, and the handling thereof becomes good. Moreover, during assembly, the fitting gap between the inner and outer rings can be adjusted by the outer diameter dimension of the sleeve, and the fitting clearance between the shaft and the sleeve can be adjusted by the inner diameter dimension of the sleeve. In other words, by adjusting the clearance between these two locations, it is possible to adjust the heat shrinkage of each part in the environment of use, so that the adjustment range of the fitting clearance at the time of assembly can be expanded.
【００１２】また、上述したように、内輪とスリーブと
の両嵌合面を軸方向に傾斜するテーパ状に形成していれ
ば、組み立て時においてスリーブの軸方向での位置を調
整することにより内・外輪間の嵌め合い隙間を調整でき
るようになるなど、作業を簡略化できる。Further, as described above, if both fitting surfaces of the inner ring and the sleeve are formed in a tapered shape that is inclined in the axial direction, the inner position can be adjusted by adjusting the position of the sleeve in the axial direction during assembly. -Since the fitting clearance between outer rings can be adjusted, the work can be simplified.
【００１３】さらに、上述したように、各要素の線膨張
係数を設定すれば、各要素の熱収縮による内・外輪間の
嵌め合い隙間の広がり度合いを抑制できるようになり、
組み立て時の嵌め合い隙間の調整幅を小さくできるよう
になる。Further, as described above, by setting the linear expansion coefficient of each element, it becomes possible to suppress the extent of expansion of the fitting gap between the inner and outer rings due to the thermal contraction of each element,
The adjustment width of the fitting gap during assembly can be reduced.
【００１４】[0014]
【発明の実施の形態】以下、本発明の詳細を図１ないし
図４に示す実施例に基づいて説明する。図１および図２
は本発明の実施例１にかかり、図１は球面すべり軸受の
側面図、図２は、図１の（２）−（２）線断面の矢視図
である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of the present invention will be described below with reference to the embodiments shown in FIGS. 1 and 2
1 relates to Example 1 of the present invention, FIG. 1 is a side view of a spherical plain bearing, and FIG. 2 is a sectional view taken along line (2)-(2) of FIG.
【００１５】図中、１はハウジング、２は揺動軸、３は
球面すべり軸受である。球面すべり軸受３は、揺動軸２
をハウジング１に対して揺動可能に支持するもので、内
輪４、外輪５、スリーブ６で構成されている。In the figure, 1 is a housing, 2 is a swing shaft, and 3 is a spherical plain bearing. The spherical plain bearing 3 has a swing shaft 2
Is supported by the housing 1 so as to be swingable, and includes an inner ring 4, an outer ring 5, and a sleeve 6.
【００１６】二分割の内輪４は、凸球面状の外周面を有
する円筒形のものを、径方向に沿うとともに軸心を通る
面で半割りして形状に形成される。外輪５は、凹球面状
の内周面を有する円筒形に形成されており、内輪４の外
径側に相対的に滑動可能に嵌合される。スリーブ６は、
内輪４の内径側に嵌合されて揺動軸２に外嵌されるもの
で、軸方向一端には径方向外向きの鍔部７が設けられて
いる。The two-divided inner ring 4 is formed in a cylindrical shape having an outer peripheral surface of a convex spherical surface, which is halved by a surface passing along the axial direction along the radial direction. The outer ring 5 is formed in a cylindrical shape having a concave spherical inner peripheral surface, and is slidably fitted to the outer diameter side of the inner ring 4. The sleeve 6
It is fitted on the inner diameter side of the inner ring 4 and is externally fitted on the swing shaft 2, and a flange portion 7 is provided at one end in the axial direction so as to face outward in the radial direction.
【００１７】そして、例えば超低温環境での使用時に
は、内・外輪４，５、スリーブ６、揺動軸２の熱収縮を
見込んで、内・外輪４，５間の嵌め合い隙間をほぼ隙間
なしの状態に、また、内輪４と揺動軸２との嵌め合い隙
間は、ほぼ隙間なしの状態あるいは適宜規定する所要の
正の隙間を持つ状態に、それぞれ設定される。Then, for example, when used in an ultra-low temperature environment, the heat shrinkage of the inner / outer rings 4, 5, the sleeve 6, and the swing shaft 2 is taken into consideration, and the fitting gap between the inner / outer rings 4, 5 is almost zero. The state, and the fitting gap between the inner ring 4 and the swing shaft 2 is set to a state where there is almost no gap or a state where there is a required positive gap that is appropriately specified.
【００１８】このような使用状態での嵌め合い隙間を実
現するためには、組み立て時のスリーブ６の内・外径寸
法を、内輪４の内径寸法、揺動軸２の外径寸法に対して
適宜設定することにより行うことができる。つまり、組
み立て時において、スリーブ６の外径寸法により内・外
輪４，５間の嵌め合い隙間を調整し、スリーブ６の内径
寸法により揺動軸２とスリーブ６との間の嵌め合い隙間
を調整し、これら２カ所の嵌め合い隙間の合計で内・外
輪４，５間の嵌め合い隙間を最終的に調整するのであ
る。したがって、熱収縮による内・外輪４，５間の嵌め
合い隙間の広がり度合いが大きくなる場合でも、この広
がりの見込みに関する調整を、組み立て時における外輪
５とスリーブ６との組立隙間と、スリーブ６と揺動軸２
との嵌め合い隙間とに振り分ければよくなるから、内・
外輪４，５、スリーブ６の組み立て作業やこれらの組み
立て体と揺動軸２との組み立て作業の各圧入動作を簡単
に行えるようになる。また、熱収縮による広がりの見込
みに関する調整幅を大きくとることができるようにな
る。In order to realize the fitting gap in such a use condition, the inner and outer diameter dimensions of the sleeve 6 at the time of assembly are set with respect to the inner diameter dimension of the inner ring 4 and the outer diameter dimension of the swing shaft 2. This can be done by setting appropriately. That is, at the time of assembly, the fitting gap between the inner and outer rings 4, 5 is adjusted by the outer diameter of the sleeve 6, and the fitting gap between the swing shaft 2 and the sleeve 6 is adjusted by the inner diameter of the sleeve 6. Then, the fitting gap between the inner and outer rings 4, 5 is finally adjusted by the total of these two fitting gaps. Therefore, even when the degree of expansion of the fitting gap between the inner and outer rings 4, 5 due to heat shrinkage increases, the adjustment regarding the prospect of this expansion is performed by adjusting the assembly gap between the outer ring 5 and the sleeve 6 at the time of assembly and the sleeve 6. Swing axis 2
Since it will be better to divide it into the fitting gap with
Each press-fitting operation of the assembling work of the outer rings 4, 5 and the sleeve 6 and the assembling work of these assembled bodies and the swing shaft 2 can be easily performed. In addition, it is possible to make a large adjustment range regarding the prospect of expansion due to heat contraction.
【００１９】ところで、上述した各部の寸法調整に加え
て、内・外輪４，５、揺動軸２、スリーブ６の各熱膨張
率を相対的に管理すれば、使用環境特に超低温環境での
熱収縮による内・外輪４，５間の嵌め合い隙間の広がり
度合いを抑制できるようになるので、前述の寸法調整時
における各嵌め合い隙間の調整幅を小さくできるように
なって、組み立て時の圧入の度合いを緩くできるように
なるなど、組立作業を簡略化できるようになる。この熱
膨張率の相対設定としては、例えば次のような関係にす
ればよい。By the way, in addition to the above-mentioned dimensional adjustment of the respective parts, if the respective thermal expansion coefficients of the inner and outer rings 4, 5, the swing shaft 2, and the sleeve 6 are relatively controlled, the heat in the working environment, especially in the ultra-low temperature environment can be improved. Since it is possible to suppress the degree of expansion of the fitting gap between the inner and outer rings 4 and 5 due to the contraction, the adjustment width of each fitting gap at the time of the above-mentioned dimension adjustment can be made small, and the press-fitting at the time of assembly can be prevented. As a result, the degree of assembly can be relaxed, and the assembly work can be simplified. As the relative setting of the coefficient of thermal expansion, for example, the following relationship may be established.
【００２０】内輪４の線膨張係数を外輪５に対して大き
く、スリーブ６の線膨張係数を内輪４とほぼ同じかある
いは大きくするのがよい。例えば、外輪５の線膨張係数
を「１」としたとき、内輪４の線膨張係数を「２〜３」
と大きくし、スリーブ６の線膨張係数を「０．５」と小
さく設定する。It is preferable that the linear expansion coefficient of the inner ring 4 is larger than that of the outer ring 5, and the linear expansion coefficient of the sleeve 6 is substantially the same as or larger than that of the inner ring 4. For example, when the linear expansion coefficient of the outer ring 5 is "1", the linear expansion coefficient of the inner ring 4 is "2-3".
And the linear expansion coefficient of the sleeve 6 is set to a small value of "0.5".
【００２１】このような線膨張係数の関係とするには、
下記するような素材が考えられる。つまり、内輪４は、
ベリリウム銅あるいはＪＩＳ規格ＳＵＳ３０４などのオ
ーステナイト系ステンレス材といった非磁性材で形成す
る。ＪＩＳ規格ＳＵＳ３０４の平均線膨張係数は、１
７．１×１０-6（℃-1）である。外輪５は、窒化けい
素、アルミナ、ジルコニアなどセラミックス材料で形成
する。なお、セラミックス材料としては、具体的に、セ
ラミックス粉体（窒化ケイ素）に稀土類元素を焼結助剤
として混合したものを用いて、まず、それぞれ所定形状
に成形し、その後、この成形品を、ＨＰ（ホット・プレ
ス）、ＨＩＰ（ホット・アイソスタテック・プレス）、
ＣＩＰ（コールド・アイソスタテック・プレス）と称す
る方法でもって焼結したものが好ましい。セラミックス
（窒化けい素）の平均線膨張係数は、３．２×１０
-6（℃-1）である。スリーブ６は、例えばベリリウム銅
あるいはＪＩＳ規格ＳＵＳ３０４などのオーステナイト
系ステンレス材や、例えばＣ１７２０などで形成する。
Ｃ１７２０の平均線膨張係数は、１７．８×１０-6（℃
-1）である。In order to establish the relationship of such linear expansion coefficient,
The following materials are possible. That is, the inner ring 4 is
It is formed of a non-magnetic material such as beryllium copper or an austenitic stainless steel material such as JIS standard SUS304. The average linear expansion coefficient of JIS standard SUS304 is 1.
It is 7.1 × 10 −6 (° C. −1 ). The outer ring 5 is made of a ceramic material such as silicon nitride, alumina or zirconia. As the ceramic material, specifically, a mixture of ceramic powder (silicon nitride) with a rare earth element as a sintering aid is used to first form each into a predetermined shape, and then form the formed product. , HP (hot press), HIP (hot isostatic press),
What was sintered by the method called CIP (Cold Isostatic Press) is preferable. The average linear expansion coefficient of ceramics (silicon nitride) is 3.2 x 10
-6 (° C -1 ). The sleeve 6 is made of, for example, beryllium copper, an austenitic stainless steel material such as JIS standard SUS304, or C1720.
The average linear expansion coefficient of C1720 is 17.8 × 10 −6 (° C.
-1 ).
【００２２】そして、ハウジング１や揺動軸２は、ＪＩ
Ｓ規格ＳＵＳ３０４などの材料でそれぞれ形成する。The housing 1 and the swing shaft 2 are JI
It is formed of a material such as S standard SUS304.
【００２３】以上説明したように、組み立て時に使用環
境例えば超低温環境での熱収縮を見込んで調整すること
により、使用環境での内・外輪４，５間の嵌め合い隙間
を適正に管理していれば、揺動軸２の動作の安定化を図
ることができ、信頼性の向上に貢献できるようになる。As described above, the fitting clearance between the inner and outer races 4 and 5 in the use environment is properly managed by adjusting the heat shrinkage in the use environment, for example, the ultra-low temperature environment, during the assembly. In this case, the operation of the swing shaft 2 can be stabilized, and the reliability can be improved.
【００２４】図３および図４は本発明の実施例２にかか
り、図３は、球面すべり軸受の側面図、図４は、図３の
（４）−（４）線断面の矢視図である。3 and 4 relate to a second embodiment of the present invention. FIG. 3 is a side view of a spherical plain bearing, and FIG. 4 is a sectional view taken along line (4)-(4) of FIG. is there.
【００２５】この実施例２において上記実施例１と異な
る構成は、スリーブ６と内輪４との両嵌合面を軸方向に
傾斜するテーパ状に形成していることである。つまり、
スリーブ６の外周面および二分割の内輪４の内周面を円
錐形状に設定している。もちろん、角錐形状としてもよ
い。The second embodiment differs from the first embodiment in that both fitting surfaces of the sleeve 6 and the inner ring 4 are formed in a tapered shape which is inclined in the axial direction. That is,
The outer peripheral surface of the sleeve 6 and the inner peripheral surface of the two-divided inner ring 4 are set in a conical shape. Of course, the shape may be a pyramid.
【００２６】この場合、内輪４に対するスリーブ６の押
し込み量により、内・外輪４，５間の嵌め合い隙間を管
理することができる。つまり、組み立て時には、内・外
輪４，５とスリーブ６との組み立てが上記実施例１に比
べて容易となる。In this case, the fitting gap between the inner and outer races 4 and 5 can be controlled by the pushing amount of the sleeve 6 against the inner race 4. That is, at the time of assembly, the assembly of the inner / outer rings 4, 5 and the sleeve 6 is easier than in the first embodiment.
【００２７】また、この球面すべり軸受３をハウジング
１と揺動軸２との間に組み込んだ状態において、球面す
べり軸受３のスリーブ６に対してスリーブ６を押し込む
側へアキシャル荷重を連続的に付与する構造にしていれ
ば、使用環境において各部の熱収縮に伴い内・外輪４，
５間の嵌め合い隙間が広がったときに、スリーブ６がア
キシャル荷重により軸方向に変位させられて、前記広が
りを吸収するなど、熱収縮の隙間変化に対する自動補正
機能を持たせることができるようになる。この他、内・
外輪４，５間の経時的な摩耗に伴う嵌め合い隙間の広が
りに対しても有効となる。なお、このアキシャル荷重
は、球面すべり軸受３に対する荷重付与手段を用いた
り、あるいはアキシャル荷重が作用するように球面すべ
り軸受３の組み込み形態を設定したりするなどして得る
ことができる。Further, in a state where the spherical plain bearing 3 is assembled between the housing 1 and the swing shaft 2, an axial load is continuously applied to the sleeve 6 of the spherical plain bearing 3 on the side where the sleeve 6 is pushed. With such a structure, the inner / outer ring 4, due to the heat shrinkage of each part in the use environment,
When the fitting gap between the five is widened, the sleeve 6 is axially displaced by the axial load to absorb the widening, and thus an automatic correction function for the change in the gap due to heat shrinkage can be provided. Become. In addition,
It is also effective for expanding the fitting gap between the outer rings 4 and 5 due to wear over time. The axial load can be obtained by using a load applying means for the spherical plain bearing 3, or by setting the built-in form of the spherical plain bearing 3 so that the axial load acts.
【００２８】[0028]
【発明の効果】本発明の球面すべり軸受では、その構成
要素を非分離に組み合わせることができるから、超低温
環境での使用において内・外輪間の嵌め合い隙間を適正
な状態に管理するための組み立て時の調整作業での取り
扱いが容易になるなど、作業性を改善することができ
る。しかも、前述の組み立て時において、スリーブの外
径寸法により内・外輪間の嵌め合い隙間を、また、スリ
ーブの内径寸法により軸とスリーブとの間のはめ合い隙
間をそれぞれ調整できるようにしているから、これら２
カ所の隙間調整でもって、組み立て時の嵌め合い隙間の
調整幅を拡大できるようになる。したがって、使用環境
での各部の熱収縮を見込む調整を広範囲に行えるように
なる。In the spherical plain bearing of the present invention, the constituent elements thereof can be combined in a non-separable manner, so that the assembly for controlling the fitting gap between the inner and outer rings in an appropriate state in use in an ultra-low temperature environment. It is possible to improve workability by facilitating handling during adjustment work. Moreover, at the time of the above-mentioned assembly, the fitting gap between the inner and outer rings can be adjusted by the outer diameter of the sleeve, and the fitting clearance between the shaft and the sleeve can be adjusted by the inner diameter of the sleeve. , These 2
By adjusting the clearances at the locations, it is possible to expand the adjustment range of the fitting clearances during assembly. Therefore, it is possible to make a wide range of adjustments in consideration of heat shrinkage of each part in the use environment.
【００２９】また、請求項２のように、内輪とスリーブ
との両嵌合面を軸方向に傾斜するテーパ状に形成してい
れば、組み立て時においてスリーブの軸方向での位置を
調整することにより内・外輪間の嵌め合い隙間の調整で
きるようになるなど、作業を簡略化できる。Further, when the fitting surfaces of the inner ring and the sleeve are formed in a taper shape which is inclined in the axial direction, the position of the sleeve in the axial direction can be adjusted during assembly. By doing so, the work can be simplified, such as adjusting the fitting gap between the inner and outer rings.
【００３０】さらに、請求項３のように、各要素の線膨
張係数を設定すれば、各要素の熱収縮による内・外輪間
の嵌め合い隙間の広がり度合いを抑制できるようにな
り、組み立て時の嵌め合い隙間の調整幅を小さくできる
ようになる。Furthermore, by setting the linear expansion coefficient of each element as in claim 3, it is possible to suppress the extent of expansion of the fitting gap between the inner and outer rings due to the thermal contraction of each element, and at the time of assembly. The adjustment width of the fitting gap can be reduced.
【図１】本発明の実施例１の球面すべり軸受の側面図FIG. 1 is a side view of a spherical plain bearing according to a first embodiment of the present invention.
【図２】図１の（２）−（２）線断面の矢視図FIG. 2 is a sectional view taken along the line (2)-(2) of FIG.
【図３】本発明の実施例２の球面すべり軸受の側面図FIG. 3 is a side view of a spherical plain bearing according to a second embodiment of the present invention.
【図４】図３の（４）−（４）線断面の矢視図FIG. 4 is a cross-sectional view taken along the line (4)-(4) of FIG.
２ 揺動軸 ３ 球面すべり軸受 ４ 内輪 ５ 外輪 ６ スリーブ 2 Swing shaft 3 Spherical plain bearing 4 Inner ring 5 Outer ring 6 Sleeve
Claims (3)
うとともに軸心を通る面で分割されてなる内輪と、内輪
の外径側に相対的に滑動可能に嵌合される外輪と、内輪
の内径側に嵌合されるとともに軸に外嵌されるスリーブ
とを含む、ことを特徴とする球面すべり軸受。1. An inner ring, which has a convex spherical outer peripheral surface and is divided by a surface that extends along the radial direction and passes through an axis, and an outer ring that is relatively slidably fitted to the outer diameter side of the inner ring. And a sleeve fitted on the inner diameter side of the inner ring and fitted on the shaft, and a spherical plain bearing characterized by the above.
に傾斜するテーパ状に形成されている、請求項１に記載
の球面すべり軸受。2. The spherical plain bearing according to claim 1, wherein both fitting surfaces of the inner ring and the sleeve are formed in a tapered shape inclined in the axial direction.
りも線膨張係数の小さい材料とされ、スリーブが内輪の
線膨張係数とほぼ同じかあるいは大きい材料とされてい
る、請求項１または２に記載の球面すべり軸受。3. The inner ring is made of a non-magnetic metal, the outer ring is made of a material having a smaller linear expansion coefficient than that of the inner ring, and the sleeve is made of a material substantially the same as or larger than the linear expansion coefficient of the inner ring. The spherical plain bearing according to item 2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28491095A JP3674721B2 (en) | 1995-11-01 | 1995-11-01 | Spherical plain bearing for ultra low temperature environment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28491095A JP3674721B2 (en) | 1995-11-01 | 1995-11-01 | Spherical plain bearing for ultra low temperature environment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09126234A true JPH09126234A (en) | 1997-05-13 |
| JP3674721B2 JP3674721B2 (en) | 2005-07-20 |
Family
ID=17684640
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28491095A Expired - Fee Related JP3674721B2 (en) | 1995-11-01 | 1995-11-01 | Spherical plain bearing for ultra low temperature environment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3674721B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000027854A (en) * | 1998-05-15 | 2000-01-25 | Rexnord Corp | Diametrally divided composite spherical bearing and manufacture therefor |
| JP2007054865A (en) * | 2005-08-24 | 2007-03-08 | Asahi Diamond Industrial Co Ltd | Die device for wire drawing |
| CN102862019A (en) * | 2012-10-09 | 2013-01-09 | 苏州苏万万向节有限公司 | Ball and ball bowl assembling process |
| WO2015127087A1 (en) * | 2014-02-19 | 2015-08-27 | Google Inc. | Biased compound radial plain bearing for increased life in oscillating pivot motion |
-
1995
- 1995-11-01 JP JP28491095A patent/JP3674721B2/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000027854A (en) * | 1998-05-15 | 2000-01-25 | Rexnord Corp | Diametrally divided composite spherical bearing and manufacture therefor |
| JP4515554B2 (en) * | 1998-05-15 | 2010-08-04 | レックスノード コーポレイション | Diametrically divided composite spherical bearing and manufacturing method thereof |
| JP2007054865A (en) * | 2005-08-24 | 2007-03-08 | Asahi Diamond Industrial Co Ltd | Die device for wire drawing |
| CN102862019A (en) * | 2012-10-09 | 2013-01-09 | 苏州苏万万向节有限公司 | Ball and ball bowl assembling process |
| WO2015127087A1 (en) * | 2014-02-19 | 2015-08-27 | Google Inc. | Biased compound radial plain bearing for increased life in oscillating pivot motion |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3674721B2 (en) | 2005-07-20 |
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