JP3879108B2 - Solid lubricated cross roller bearing - Google Patents

Solid lubricated cross roller bearing Download PDF

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Publication number
JP3879108B2
JP3879108B2 JP26797396A JP26797396A JP3879108B2 JP 3879108 B2 JP3879108 B2 JP 3879108B2 JP 26797396 A JP26797396 A JP 26797396A JP 26797396 A JP26797396 A JP 26797396A JP 3879108 B2 JP3879108 B2 JP 3879108B2
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roller
outer ring
inner ring
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JPH1089364A (en
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忠喜 板部
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Yaskawa Electric Corp
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Yaskawa Electric Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6696—Special parts or details in view of lubrication with solids as lubricant, e.g. dry coatings, powder
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/361—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers
    • F16C19/362—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers the rollers being crossed within the single row
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/40—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings with loose spacing bodies between the rollers
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/37—Loose spacing bodies
    • F16C33/3713—Loose spacing bodies with other rolling elements serving as spacing bodies, e.g. the spacing bodies are in rolling contact with the load carrying rolling elements

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、真空中や放射線下あるいは高温または低温環境などの過酷な環境条件で使用される固体潤滑クロスローラ軸受に関する。
【０００２】
【従来の技術】
クロスローラ軸受の第１の従来例をとして、内輪と、外輪のそれぞれ対向する面に設けた円周方向に伸びる二つの転走面からなるＶ形転走溝の間に挿入した複数のローラの保持のために金属製のリング状保持器を用いたものが提案されている。図５において、（ａ）はリング状保持器を用いた軸受の側面図、（ｂ）はリング状保持器の斜視図である。クロスローラ軸受は基本的には、内輪１およびそれに対向する二つ割の外輪２と、内輪１の外周面に設けた内輪Ｖ形転走溝３と、外輪２の内周面に内輪Ｖ形転走溝３と対向して設けた同形の外輪Ｖ形転走溝４と、内輪および外輪Ｖ形転走溝３、４を転動するローラ６で構成されている。
リング状保持器８には、複数個のローラ６を４５°傾斜させて回転自在に保持させるための楕円形状のポケット孔８１が穿設され、各ロ−ラ６をポケット孔８１に通した状態で、その外側に外輪２の各分割片を係合して数箇所をネジ止めしたものである。こうすることにより、外輪２と内輪１との間で各ロ−ラ６は軸受の中心軸線に対して４５°傾斜した軸線を回転軸として転がり運動をするものである。
また、第２の従来例として、ローラの保持用に樹脂製のスペーサリテーナを用いたクロスロ−ラ軸受が提案されている。なお、内輪、外輪、ロ−ラの基本的な軸受の構成は第１の従来例と同じである。図６は第２の従来例のスペーサリテーナの平面図である。複数個のロ−ラ６の間に介装させて保持するスペーサリテーナ９とからなるクロスローラ軸受において、スペーサリテーナ９には、その左右両側面に互いに隣接するロ−ラ６が回転可能に嵌合する曲面溝、すなわち傾斜接触面９１、９２を形成しており、軸受使用時におけるロ−ラのスキュ−（揺れ）を防止し、円滑な回転運動を得る構成にしたものである（実開平１ー１５６３１４）。
また、第３の従来例として、ローラの保持用に樹脂製の円筒形や球形のスペーサを用いたクロスロ−ラ軸受が提案されている。なお、基本的な軸受の構成は第１の従来例と同じである。図７および図８は第３の従来例の円筒形や球形のスペーサを用いたクロスロ−ラ軸受の側面展開図である。内輪Ｖ形転送溝３および図示しない外輪Ｖ形転送溝の間に挿入されたローラ６は円筒形スペーサ１０および球形スペーサ１１と点あるいは一部が線で接触している（実開平２ー７４６２５号公報）。
なお、内輪、外輪およびローラの材料に関しては、一般にＳＵＪ２やＳＵＳ４４０Ｃなどの鉄系金属材料が用いられ、内輪、外輪およびローラの全部または一部の摺動面には、二硫化モリブデン（ＭｏＳ2 ）、二硫化タングステン（ＷＳ2 ）、銀（Ａｇ）などの固体潤滑剤の薄膜が処理されたものが提案されている（例えば、特開昭５５−５７７１７、特開昭５８−１１３６２９、特開昭６１−５５４１０号公報）。
【０００３】
【発明が解決しようとする課題】
ところが、これらの従来技術のうち、リング状保持器を用いる第１の従来例はは、ローラ６の保持性が良くてローラのスキューは起こりにくいが、ローラ６とリング状保持器８のポケット穴８１とがこすれ、ロ−ラ表面の固体潤滑膜が早期に摩耗して潤滑不良となり、ローラ６と内輪１あるいは外輪２が焼き付いて軸受の寿命が短いという問題があった。
また、スペーサーリテーナを用いる第２の従来例は、ローラ６の保持性が良くてローラのスキューは起こりにくいが、ローラ６とスペサーリテーナ９とが面接触状態で滑っていて、そこの摩擦力が大きくなるために、軸受の摩擦トルクが大きいという問題があった。
また、樹脂製の円筒形や球形のスペーサローラを用いる第３の従来例は、ローラ６は円筒形スペーサ１０および球形スペーサ１１と点で接触しているため、ローラ６の保持性が悪くてローラのスキューが起こり易く、軸受摩擦トルクの変動が大きいという問題があった。
そこで本発明は、ロ−ラのスキュ−が起こり難く、軸受摩擦トルクおよびその変動が小さく、そして軸受寿命が長い固体潤滑クロスローラ軸受を提供することを目的とするものである。
【０００４】
【課題を解決するための手段】
上記問題を解決するため、請求項１記載の発明は、内輪と、外輪と、前記内輪と前記外輪のそれぞれ対向する面に設けた周方向に伸びるＶ形転走溝と、前記二つのＶ形転走溝の間に挿入した複数個のローラを備え、前記内輪と前記外輪の転走溝、および前記ロ−ラの表面の一部または全部に固体潤滑材の被膜を形成した固体潤滑クロスローラ軸受において、前記ローラ間に、直径が前記ローラより僅かに小さく、円錐台形状と円柱形状に成形されたものからなる自己潤滑性材料製の疑似円柱状スペーサを挿設してあり、前記ローラと前記疑似円柱状スペーサの一個ずつを一組として、交互に傾斜方向を変えてあり、前記ローラと前記疑似円柱状スペーサのうち、少なくとも一方の部材の前記外輪側の端面を、前記外輪のＶ形転走溝の中央の曲率半径と同一あるいはこれより僅かに小さな曲率半径の球面形状に形成したものである。
また、請求項２記載の発明は、請求項１記載の固体潤滑クロスローラ軸受において、前記ローラおよび前記疑似円柱状スペーサの前記内輪側の端面のコーナ部を、それぞれの端面の直径の約１０％の半径で面取りを施したものである。
【０００５】
【発明の実施の形態】
以下、本発明の具体的実施例を図に基づいて説明する。
図１は本発明の実施例の一部を示す側面展開図で、図２は図１のＡＡ’線に沿う側断面図である。内輪１、外輪２、内輪Ｖ形転走溝３、外輪Ｖ形転走溝４、ローラ６の基本的な構成は従来技術と同じである。５は内輪Ｖ形転走溝３、外輪Ｖ形転走溝４およびローラ６の表面にスパッタ法により付着させた二硫化モリブデンの固体潤滑膜である。７は直径がローラよりわずかに小さく、円錐台状と円柱状の形状をした自己潤滑性材料製の疑似円柱状スペーサである。なお、内輪１、外輪２およびローラ６の材料は金属系およびセラミック系材料を用いたもので、ローラ６と疑似円柱状スペーサ７の一個ずつを一組として、交互に傾斜方向を変えてた構成にしたものである。
図３および図４は、それぞれローラ６、疑似円柱状スペーサ７の側面図である。ローラ６および疑似円柱状スペーサ７の軸方向に位置する両端面のうち、外輪Ｖ形転走溝４に対面する方の球面側端面６２および７２は、外輪２の転走面の中央の曲率半径と同一あるいはこれより僅かに小さな曲率半径を有する球面に成形されており、そして、内輪Ｖ形転走溝３に対面する方の平面状端面６１および７１のコーナ部６３および７３は、それぞれローラ６および疑似円柱状スペーサ７の平面状端面６１および７１の直径の約１０％の半径の円弧で面取りが施されている。
なお、図３のローラ６と疑似円柱状スペーサ７のうち、少なくとも一方の部材の外輪２側の端面を球面形状に成形した構成のものでも良い。
【０００６】
次に動作について説明する。内輪１と外輪２が相対的に回転すると、ローラ６は軸受荷重を負担した状態で回転しながら内輪Ｖ形転走溝３、外輪Ｖ形転走溝４内を移動する。このとき、固体潤滑膜５と自己潤滑性材料製の疑似円柱状スペーサ７の固体潤滑作用により、ローラ６は円滑に転動する。また、ローラ６および疑似円柱状スペーサ７の球面側端面６２、７２は曲面の中央部で外輪Ｖ形転走溝４とは点接触して、ローラ６および疑似円柱状スペーサ７のエッジ部６４、７４が外輪Ｖ形転走溝４と接触することがなくなるために、ローラ６および疑似円柱状スペーサ７の球面側端面６２、７２の局部的な摩耗あるいは外輪Ｖ形転走溝４表面の固体潤滑膜５の過大な摩耗を防ぐことができる。
また、ローラ６は、内輪Ｖ形転走溝３と外輪Ｖ形転走溝４によって軸受の軸方向の動きを、疑似円柱状スペーサ７の円錐面７７によって軸受の円周方向の動きを規制される。そして、疑似円柱状スペーサ７は、内輪Ｖ形転走溝３と外輪Ｖ形転走溝４によって軸受の軸方向の動きを、ローラ６の円柱面６６で軸受の円周方向の動きを規制される。その結果、ローラ６および疑似円柱状スペーサ７はスキューを起こしにくい。
そして、自己潤滑性材料製の疑似円柱状スペーサ７を使用するために、固体潤滑膜５が摩耗しても、ローラ６は焼き付きを起こしにくい。
【０００７】
上記手段によって、固体潤滑クロスローラ軸受において、ローラとローラの間に、直径がローラよりわずかに小さく、円錐台状と円柱状の形状をした自己潤滑性材料製の疑似円柱状スペーサを設置して、ローラと疑似円柱状スペーサのうち、少なくとも一方の部材の外輪側の端面を外輪のＶ形転走溝の中央の曲率半径と同一あるいはこれより僅かに小さな曲率半径の球面状に形成し、かつ、ローラおよび疑似円柱状スペーサの内輪側の端面のコーナ部をローラの直径の約１０％の半径で面取りを施し、内輪と外輪の転走面およびローラの表面の一部あるいは全部に二硫化モリブデン、二硫化タングステン、銀などの固体潤滑剤の薄膜を形成し、さらに、ローラと疑似円柱状スペーサは一個ずつを一組として、交互に傾斜方向を変えて配列されているので、ローラおよび自己潤滑性材料製の疑似円柱状スペ−サがスキュ−することがなくなるとともに、接触面の局部磨耗は少なくなり、長時間に渡って焼き付きを生じることがなくなる。
さらに、ローラと疑似円柱状スペーサはその端面、コーナ部に球面やＲ状の面取りを施した構成にしているので、それらのエッジ部が軌道溝とこすれたり、固体潤滑膜を傷つけることがなく、その結果、軸受摩擦トルクおよびその変動が小さくなるとともに軸受寿命が長くなる。
【０００８】
【発明の効果】
以上述べたように、本発明によれば、固体潤滑クロスローラ軸受において、複数のローラ間に、直径がローラよりわずかに小さい、円錐台状と円柱状の形状をした自己潤滑性材料製の疑似円柱状スペーサを設けるとともに、ローラと疑似円柱状スうーサはその端面、コーナ部に球面やＲ状の面取りを施した構成にしているので、ロ−ラのスキュ−が起こり難い、軸受摩擦トルクおよびその変動が小さい、そして軸受寿命が長い、高信頼性の固体潤滑クロスローラ軸受を得る効果がある。
【図面の簡単な説明】
【図１】 本発明の実施例の一部を示す側面展開図である。
【図２】 図１のＡＡ’線に沿う側断面図である。
【図３】 ローラの側面図である。
【図４】 疑似円柱状スペーサの側面図である。
【図５】 （ａ）は第１の従来例を示すリング状保持器を用いた場合の側面図、（ｂ）はリング状保持器の斜視図である。
【図６】 第２の従来例を示すスペーサリテーナを用いた場合の平面図である。
【図７】 第３の従来例を示す円筒形スペーサを用いた場合の側面展開図である。
【図８】 その他の第３の従来例を示す球形スペーサの側面展開図である。
【符号の説明】
１：内輪、２：外輪、３：内輪Ｖ形転走溝、
４：外輪Ｖ形転走溝、５：固体潤滑膜、
６：ローラ、６１：平面状端面、６２：球面状端面、
６３：コーナ部、６４：エッジ部、６５：面取り、
６６：円筒面、７：疑似円柱状スペーサ、
７１：平面状端面、７２：球面状端面、
７３：コーナ部、７４：エッジ部、７５：面取り、
７６：円柱面，７７：円錐面，８：リング状保持器、
８１：ポケット穴、９；スペーサリテーナ、
９１、９２：傾斜接触面、１０：円筒形スペ−サ、
１１：球形スペーサ[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a solid-lubricated cross-roller bearing that is used in harsh environmental conditions such as in a vacuum, under radiation, or in a high or low temperature environment.
[0002]
[Prior art]
As a first conventional example of a cross roller bearing, a plurality of rollers inserted between V-shaped rolling grooves formed of two rolling surfaces extending in the circumferential direction provided on surfaces facing the inner ring and the outer ring, respectively. A metal ring-shaped cage has been proposed for holding. In FIG. 5, (a) is a side view of a bearing using a ring-shaped cage, and (b) is a perspective view of the ring-shaped cage. The cross roller bearing basically includes an inner ring 1 and a split outer ring 2 facing the inner ring 1, an inner ring V-shaped rolling groove 3 provided on the outer circumferential surface of the inner ring 1, and an inner ring V-shaped on the inner circumferential surface of the outer ring 2. The outer ring V-shaped rolling groove 4 of the same shape provided facing the rolling groove 3 and the roller 6 that rolls the inner ring and the outer ring V-shaped rolling grooves 3 and 4 are configured.
The ring-shaped cage 8 is provided with an elliptical pocket hole 81 for rotatably holding a plurality of rollers 6 inclined at 45 °, and each roller 6 is passed through the pocket hole 81. Thus, the outer ring 2 is engaged with the divided pieces on the outer side, and is screwed at several points. By doing so, each roller 6 rolls between the outer ring 2 and the inner ring 1 about an axis inclined at 45 ° with respect to the central axis of the bearing as a rotation axis.
Further, as a second conventional example, a cross roller bearing using a resin spacer retainer for holding a roller has been proposed. The basic bearing configuration of the inner ring, outer ring, and roller is the same as that of the first conventional example. FIG. 6 is a plan view of a spacer retainer of a second conventional example. In a cross roller bearing comprising a spacer retainer 9 interposed between and held between a plurality of rollers 6, the roller retainers 6 adjacent to each other are rotatably fitted to the left and right side surfaces of the spacer retainer 9. The curved grooves to be joined, that is, the inclined contact surfaces 91 and 92 are formed to prevent the rollers from skewing when using the bearings and to obtain a smooth rotational motion (actually flat) 1-156314).
Further, as a third conventional example, a cross roller bearing using a cylindrical or spherical spacer made of resin for holding a roller has been proposed. The basic bearing configuration is the same as that of the first conventional example. 7 and 8 are side development views of a cross roller bearing using a cylindrical or spherical spacer of a third conventional example. The roller 6 inserted between the inner ring V-shaped transfer groove 3 and the outer ring V-shaped transfer groove (not shown) is in contact with the cylindrical spacer 10 and the spherical spacer 11 at a point or part thereof with a line (Japanese Utility Model Laid-Open No. 2-74625). Publication).
As for the materials of the inner ring, the outer ring and the roller, generally, iron-based metal materials such as SUJ2 and SUS440C are used, and molybdenum disulfide (MoS 2 ) is used on all or part of the sliding surfaces of the inner ring, the outer ring and the roller. , Tungsten disulfide (WS 2 ), silver (Ag) and other solid lubricant thin films treated have been proposed (for example, JP 55-57717, JP 58-11629, JP 61-55410).
[0003]
[Problems to be solved by the invention]
However, among these prior arts, the first conventional example using a ring-shaped cage has good retainability of the roller 6 and hardly causes skewing of the roller, but the pocket hole between the roller 6 and the ring-shaped cage 8 does not occur. 81, and the solid lubricating film on the surface of the roller was worn early, resulting in poor lubrication, and the roller 6 and the inner ring 1 or the outer ring 2 were seized so that the bearing life was short.
The second conventional example using the spacer retainer has good retainability of the roller 6 and hardly causes skew of the roller. However, the roller 6 and the spacer retainer 9 slide in a surface contact state, and the frictional force there is. In order to become large, there existed a problem that the friction torque of a bearing was large.
Further, in the third conventional example using a resin cylindrical or spherical spacer roller, since the roller 6 is in contact with the cylindrical spacer 10 and the spherical spacer 11 at a point, the roller 6 is poorly held and the roller 6 There is a problem that the skew of the bearing is likely to occur and the fluctuation of the bearing friction torque is large.
SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a solid lubricated cross roller bearing in which roller skew is unlikely to occur, bearing friction torque and fluctuation thereof are small, and the bearing life is long.
[0004]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the invention according to claim 1 includes an inner ring, an outer ring, a V-shaped rolling groove extending in a circumferential direction provided on a surface facing each of the inner ring and the outer ring, and the two V-shaped grooves. A solid-lubricated cross roller comprising a plurality of rollers inserted between the rolling grooves, and having a coating film of a solid lubricant on a part or all of the rolling grooves of the inner ring and the outer ring and the surface of the roller In the bearing, a pseudo columnar spacer made of a self-lubricating material having a diameter slightly smaller than that of the roller and formed in a truncated cone shape and a columnar shape is inserted between the rollers, and the roller Each of the pseudo-cylindrical spacers is set as a set, and the inclination direction is alternately changed, and the end surface on the outer ring side of at least one member of the roller and the pseudo-cylindrical spacer is a V-shape of the outer ring. The song at the center of the rolling groove Radius and is obtained by forming the same or it slightly smaller radius of curvature of the spherical shape.
According to a second aspect of the present invention, in the solid lubricated cross roller bearing according to the first aspect, the corner portion of the end surface on the inner ring side of the roller and the pseudo-cylindrical spacer is approximately 10% of the diameter of each end surface. Chamfered with a radius of.
[0005]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, specific embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a developed side view showing a part of the embodiment of the present invention, and FIG. 2 is a side sectional view taken along line AA ′ of FIG. The basic configuration of the inner ring 1, the outer ring 2, the inner ring V-shaped rolling groove 3, the outer ring V-shaped rolling groove 4 and the roller 6 is the same as that of the prior art. 5 is a solid lubricant film of molybdenum disulfide adhered to the surfaces of the inner ring V-shaped rolling groove 3, the outer ring V-shaped rolling groove 4 and the roller 6 by sputtering. Reference numeral 7 denotes a pseudo-cylindrical spacer made of a self-lubricating material having a slightly smaller diameter than the roller and having a truncated cone shape and a cylindrical shape. The inner ring 1, the outer ring 2 and the roller 6 are made of metal and ceramic materials, and each of the rollers 6 and the pseudo columnar spacer 7 is set as one set, and the inclination direction is changed alternately. It is a thing.
3 and 4 are side views of the roller 6 and the pseudo cylindrical spacer 7, respectively. Of the both end surfaces of the roller 6 and the pseudo-cylindrical spacer 7 positioned in the axial direction, the spherical side end surfaces 62 and 72 facing the outer ring V-shaped rolling groove 4 are the radius of curvature at the center of the rolling surface of the outer ring 2. The corner portions 63 and 73 of the planar end faces 61 and 71 facing the inner ring V-shaped rolling groove 3 are respectively formed in a spherical surface having the same or slightly smaller radius of curvature than the roller 6. Further, chamfering is performed with an arc having a radius of about 10% of the diameter of the planar end faces 61 and 71 of the pseudo cylindrical spacer 7.
In addition, the thing of the structure which shape | molded the end surface by the side of the outer ring | wheel 2 of at least one member among the roller 6 of FIG.
[0006]
Next, the operation will be described. When the inner ring 1 and the outer ring 2 rotate relative to each other, the roller 6 moves in the inner ring V-shaped rolling groove 3 and the outer ring V-shaped rolling groove 4 while rotating while bearing load is applied. At this time, the roller 6 rolls smoothly by the solid lubricating action of the solid lubricating film 5 and the pseudo-cylindrical spacer 7 made of a self-lubricating material. In addition, the spherical side end surfaces 62 and 72 of the roller 6 and the pseudo cylindrical spacer 7 are in the center of the curved surface and are in point contact with the outer ring V-shaped rolling groove 4, and the edge portion 64 of the roller 6 and the pseudo cylindrical spacer 7. Since 74 does not come into contact with the outer ring V-shaped rolling groove 4, local wear on the spherical side end surfaces 62, 72 of the roller 6 and the pseudo cylindrical spacer 7 or solid lubrication of the surface of the outer ring V-shaped rolling groove 4 is achieved. Excessive wear of the film 5 can be prevented.
Further, the roller 6 is restricted in the axial movement of the bearing by the inner ring V-shaped rolling groove 3 and the outer ring V-shaped rolling groove 4, and in the circumferential direction of the bearing by the conical surface 77 of the pseudo cylindrical spacer 7. The The pseudo-cylindrical spacer 7 is regulated in the axial movement of the bearing by the inner ring V-shaped rolling groove 3 and the outer ring V-shaped rolling groove 4 and in the circumferential direction of the bearing by the cylindrical surface 66 of the roller 6. The As a result, the roller 6 and the pseudo-cylindrical spacer 7 are less likely to cause skew.
Since the pseudo-cylindrical spacer 7 made of a self-lubricating material is used, even if the solid lubricating film 5 is worn, the roller 6 is unlikely to seize.
[0007]
By the above means, in the solid lubricating cross roller bearing, a pseudo cylindrical spacer made of a self-lubricating material having a diameter slightly smaller than that of the roller and having a truncated cone shape and a cylindrical shape is installed between the rollers. The outer ring side end surface of at least one member of the roller and the pseudo-cylindrical spacer is formed in a spherical shape having a radius of curvature equal to or slightly smaller than the center radius of curvature of the V-shaped rolling groove of the outer ring, and The corner of the inner ring side end face of the roller and the pseudo cylindrical spacer is chamfered with a radius of about 10% of the diameter of the roller, and molybdenum disulfide is applied to a part or all of the rolling surface of the inner ring and the outer ring and the surface of the roller. A thin film of solid lubricant such as tungsten disulfide and silver is formed, and the rollers and pseudo-cylindrical spacers are arranged one by one, alternately changing the inclination direction. Because there, rollers and self-lubricating material made of pseudo-cylindrical space - service is skew - together it is not necessary to the local wear of the contact surface decreases, thereby preventing causing burn for a long time.
Furthermore, since the roller and the pseudo-cylindrical spacer are configured to have a spherical surface or a rounded chamfer at the end surface and corner portion thereof, the edge portion thereof does not rub against the raceway groove or damage the solid lubricating film. As a result, the bearing friction torque and its variation are reduced and the bearing life is extended.
[0008]
【The invention's effect】
As described above, according to the present invention, in a solid lubricated cross roller bearing, a pseudo-made of a self-lubricating material having a truncated cone shape and a cylindrical shape having a diameter slightly smaller than that of a roller between a plurality of rollers. In addition to providing a cylindrical spacer, the roller and pseudo-cylindrical spacer have a spherical surface or a rounded chamfer at the end face and corner, so that roller skew is unlikely to occur, and bearing friction torque Further, there is an effect of obtaining a highly reliable solid-lubricated cross-roller bearing having a small variation and a long bearing life.
[Brief description of the drawings]
FIG. 1 is a side development view showing a part of an embodiment of the present invention.
FIG. 2 is a side sectional view taken along line AA ′ of FIG.
FIG. 3 is a side view of a roller.
FIG. 4 is a side view of a pseudo columnar spacer.
FIG. 5A is a side view when a ring-shaped cage showing a first conventional example is used, and FIG. 5B is a perspective view of the ring-shaped cage.
FIG. 6 is a plan view when a spacer retainer showing a second conventional example is used.
FIG. 7 is a developed side view when a cylindrical spacer showing a third conventional example is used.
FIG. 8 is a side development view of a spherical spacer showing another third conventional example.
[Explanation of symbols]
1: Inner ring, 2: Outer ring, 3: Inner ring V-shaped rolling groove,
4: outer ring V-shaped rolling groove, 5: solid lubricating film,
6: roller, 61: planar end surface, 62: spherical end surface,
63: Corner part, 64: Edge part, 65: Chamfering,
66: cylindrical surface, 7: pseudo-columnar spacer,
71: planar end surface, 72: spherical end surface,
73: Corner part, 74: Edge part, 75: Chamfering,
76: cylindrical surface, 77: conical surface, 8: ring-shaped cage,
81: Pocket hole, 9; Spacer retainer,
91, 92: inclined contact surface, 10: cylindrical spacer,
11: Spherical spacer

Claims (2)

内輪と、外輪と、前記内輪と前記外輪のそれぞれ対向する面に設けた周方向に伸びるＶ形転走溝と、前記二つのＶ形転走溝の間に挿入した複数個のローラを備え、前記内輪と前記外輪の転走溝、および前記ロ−ラの表面の一部または全部に固体潤滑材の被膜を形成した固体潤滑クロスローラ軸受において、
前記ローラ間に、直径が前記ローラより僅かに小さく、円錐台形状と円柱形状に成形されたものからなる自己潤滑性材料製の疑似円柱状スペーサを挿設してあり、
前記ローラと前記疑似円柱状スペーサの一個ずつを一組として、交互に傾斜方向を変えてあり、
前記ローラと前記疑似円柱状スペーサのうち、少なくとも一方の部材の前記外輪側の端面を、前記外輪のＶ形転走溝の中央の曲率半径と同一あるいはこれより僅かに小さな曲率半径の球面形状に形成したことを特徴とする固体潤滑クロスローラ軸受。An inner ring, an outer ring, a V-shaped rolling groove extending in a circumferential direction provided on the opposing surfaces of the inner ring and the outer ring, and a plurality of rollers inserted between the two V-shaped rolling grooves, In a solid lubricating cross roller bearing in which a coating film of a solid lubricant is formed on a part or all of the rolling groove of the inner ring and the outer ring and the surface of the roller,
Between the rollers, a quasi-cylindrical spacer made of a self-lubricating material made of a material that is slightly smaller in diameter than the roller and formed into a truncated cone shape and a cylindrical shape is inserted ,
The roller and the pseudo columnar spacer are each one set as a set, the inclination direction is alternately changed,
The end surface on the outer ring side of at least one member of the roller and the pseudo-cylindrical spacer is formed into a spherical shape having a radius of curvature that is the same as or slightly smaller than the radius of curvature at the center of the V-shaped rolling groove of the outer ring. A solid lubricated cross roller bearing characterized by being formed . 前記ローラおよび前記疑似円柱状スペーサの前記内輪側の端面のコーナ部を、それぞれの端面の直径の約１０％の半径で面取りを施した請求項１に記載の固体潤滑クロスローラ軸受。 2. The solid lubricated cross roller bearing according to claim 1, wherein corner portions of the end faces of the inner ring side of the roller and the pseudo cylindrical spacer are chamfered with a radius of about 10% of a diameter of each end face .
JP26797396A 1996-09-17 1996-09-17 Solid lubricated cross roller bearing Expired - Fee Related JP3879108B2 (en)

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Application Number Priority Date Filing Date Title
JP26797396A JP3879108B2 (en) 1996-09-17 1996-09-17 Solid lubricated cross roller bearing

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JPH1089364A JPH1089364A (en) 1998-04-07
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CN101065589B (en) * 2004-09-30 2011-04-13 Thk株式会社 Rolling guide device
EP1840395B1 (en) * 2005-01-18 2013-04-24 NSK Ltd. Rolling device
CN101818756A (en) * 2010-04-20 2010-09-01 郑达铿 High-precision rolling bearing of double-head cone
CN107401553B (en) * 2016-05-18 2019-04-30 上银科技股份有限公司 Sized cross roller bearings with introns
CN107701582A (en) * 2017-11-15 2018-02-16 营山县臻安机电科技研究所 A kind of point contact type bearing

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