JP2627885B2 - Rolling bearing - Google Patents
Rolling bearingInfo
- Publication number
- JP2627885B2 JP2627885B2 JP61309526A JP30952686A JP2627885B2 JP 2627885 B2 JP2627885 B2 JP 2627885B2 JP 61309526 A JP61309526 A JP 61309526A JP 30952686 A JP30952686 A JP 30952686A JP 2627885 B2 JP2627885 B2 JP 2627885B2
- Authority
- JP
- Japan
- Prior art keywords
- retainer
- alloy
- bearing
- rolling
- ball
- 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.)
- Expired - Lifetime
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
- 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
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6688—Lubricant compositions or properties, e.g. viscosity
- F16C33/6692—Liquids other than oil, e.g. water, refrigerants, liquid metal
-
- 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
- F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
-
- 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
- F16C33/38—Ball cages
- F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
-
- 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
- F16C33/38—Ball cages
- F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
- F16C33/3843—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
-
- 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
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
-
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
-
- 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
-
- 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
- F16C2210/00—Fluids
- F16C2210/08—Fluids molten metals
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Description
【発明の詳細な説明】 〈産業上の利用分野〉 本発明は、所定温度で融解して液相状態となる金属潤
滑剤を用いた転がり軸受に関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial Application Field> The present invention relates to a rolling bearing using a metal lubricant that melts at a predetermined temperature to be in a liquid phase.
〈従来の技術〉 一般的に、転がり軸受に用いる潤滑剤として、グリー
スなどの流体潤滑剤や軟金属などの固体潤滑剤が知られ
ているが、この他にも所定温度（作動中における温度）
で融解して液相状態となるGaまたはGa合金などの金属潤
滑剤が知られている。<Prior art> Generally, fluid lubricants such as grease and solid lubricants such as soft metals are known as lubricants used in rolling bearings, but other than these, a predetermined temperature (temperature during operation)
There is known a metal lubricant such as Ga or a Ga alloy which melts in a liquid phase state.
ところで、GaまたはGa合金などの金属潤滑剤は、固体
潤滑剤と同様、高温環境や真空環境など厳しい条件下で
の使用に適しているだけでなく、固体潤滑剤に比べても
振動、騒音、回転トルクなど諸特性において優れると考
えられる。By the way, metal lubricants such as Ga or Ga alloy are not only suitable for use under severe conditions such as high temperature environment or vacuum environment, like solid lubricants, but also have vibration, noise, It is considered that various characteristics such as rotational torque are excellent.
〈発明が解決しようとする問題点〉 しかしながら、GaまたはGa合金などの金属潤滑剤は、
内・外軌道輪および転動体が一般的な鋼材であると、そ
れを腐食しやすく短期のうちに転がりや滑りが生じる軌
道部分を荒らすので、内・外軌道輪および転動体の材料
について工夫を施す必要がある。<Problems to be solved by the invention> However, metal lubricants such as Ga or Ga alloy
If the inner and outer races and rolling elements are general steel materials, they are likely to corrode and roughen the raceways where rolling and slippage occur in a short period of time. Need to be applied.
本発明はこのような事情に鑑み、振動、騒音、回転ト
ルクなどの諸特性に優れるようにしながらも、軌道輪や
転動体が腐食されずに済むようにして長寿命化を達成す
ることを目的としている。In view of such circumstances, an object of the present invention is to achieve a long service life by preventing the races and rolling elements from being corroded while improving various characteristics such as vibration, noise, and rotational torque. .
〈問題点を解決するための手段〉 本発明の転がり軸受は、潤滑剤として当該軸受の作動
温度で融解して液相状態となるGaまたはGa合金が軸受内
部に保持されている転がり軸受であって、軌道輪および
転動体が、鋼でなりその表面が前記GaまたはGa合金に対
して耐蝕性を有するセラミックスあるいはＷ、Moまたは
これらの合金材料で構成されているか、あるいは、それ
ら自体が前記GaまたはGa合金に対して耐蝕性を有するセ
ラミックスあるいはＷ、Moまたはこれらの合金材料で構
成されており、前記転動体が保持器により保持されると
ともに、保持器と軌道輪および転動体との隙間に前記Ga
またはGa合金が配設されている。<Means for Solving the Problems> The rolling bearing of the present invention is a rolling bearing in which Ga or a Ga alloy which is molten at the operating temperature of the bearing and becomes a liquid phase is held inside the bearing. The race and the rolling elements are made of steel and the surface thereof is made of ceramics or W, Mo or alloys thereof having corrosion resistance to the Ga or Ga alloy, or they are themselves made of the Ga. Or a ceramic having corrosion resistance to a Ga alloy or W, Mo or an alloy material thereof, and the rolling element is held by a retainer, and a gap is formed between the retainer and the raceway and the rolling element. The Ga
Alternatively, a Ga alloy is provided.
〈作用〉 つまり、所定温度で融解して液相状態となるGaまたは
Ga合金などの金属潤滑剤によって、内・外軌道輪および
転動体が腐食されないようにしているから、固体潤滑剤
を用いる場合に比べて振動、騒音、回転トルクなどの諸
特性において優れた効果を発揮させることができ、長寿
命が達成される。<Function> That is, Ga or
The inner and outer races and rolling elements are prevented from being corroded by metal lubricants such as Ga alloys, so they have superior effects on various characteristics such as vibration, noise, and rotational torque as compared to using solid lubricants. It can be demonstrated and a long life is achieved.
〈実施例〉 以下、本発明の詳細を第１図ないし第５図に示す実施
例に基づいて説明する。<Example> Hereinafter, details of the present invention will be described based on an example shown in FIGS. 1 to 5.
第１図ないし第３図は本発明の第１実施例を示してい
る。第１図および第２図に示す深みぞ玉軸受１は、内輪
2,外輪3,保持器４および転動体としてのボール５を備え
ている。1 to 3 show a first embodiment of the present invention. The deep groove ball bearing 1 shown in FIG. 1 and FIG.
2, an outer ring 3, a retainer 4, and a ball 5 as a rolling element.
この深みぞ玉軸受１は、作動中における温度で液相状
態になる金属潤滑剤が使用されている。この金属潤滑剤
としては、融点が25℃以下のGaまたはGa合金が望まし
い。この場合、内輪2,外輪３およびボール５は、Gaまた
はGa合金に対して耐蝕性を有する材料にするのが望まし
い。具体的には、セラミックス,W,MoまたはＷとMoとの
合金などが考えられる。これらで内輪２、外輪３および
ボール５を構成するか、或いはこれらを通常の鋼で構成
した内輪２、外輪３およびボール５にコーティングする
かは任意である。The deep groove ball bearing 1 uses a metal lubricant that becomes a liquid phase at a temperature during operation. As the metal lubricant, Ga or a Ga alloy having a melting point of 25 ° C. or less is desirable. In this case, it is desirable that the inner ring 2, the outer ring 3 and the ball 5 be made of a material having corrosion resistance to Ga or a Ga alloy. Specifically, ceramics, W, Mo, or an alloy of W and Mo can be considered. It is optional whether the inner ring 2, the outer ring 3 and the ball 5 are formed with these, or the inner ring 2, the outer ring 3 and the ball 5 formed of ordinary steel are coated with these.
内輪２および外輪３は、ボール５と同一曲率の凹状の
軌道面2a,3aを備えている。この各軌道面2a,3aそれぞれ
は、通常の深みぞ玉軸受のそれに比べて浅く構成されて
いる。この軌道面2aと軌道面3aとの間に、保持器４のポ
ケット4aに回動自在に保持されたボール５が介在されて
いる。ボール５と各軌道面2a,3aとの間には、極めて微
小な隙間h1が存在する。The inner race 2 and the outer race 3 are provided with concave raceway surfaces 2a, 3a having the same curvature as the ball 5. Each of the raceway surfaces 2a and 3a is configured to be shallower than that of a normal deep groove ball bearing. A ball 5 rotatably held in a pocket 4a of the retainer 4 is interposed between the raceway surface 2a and the raceway surface 3a. Between the balls 5 and the raceway surfaces 2a, 3a, there is a gap h 1 extremely small.
内輪２の軌道面2aの両側の外周面2b,2cと保持器４の
内周面4bとの間には隙間h2が形成されている。外輪３の
軌道面3aの両側の内周面3b,3cと保持器４の外周面4cと
の間にも隙間h3が形成されている。Gap h 2 is formed between the side of the outer peripheral surface 2b of the inner ring 2 of the raceway surface 2a, 2c and the inner circumferential surface 4b of the cage 4. The inner peripheral surface 3b of both sides of the raceway surface 3a of the outer ring 3 are formed a gap h 3 also between the outer peripheral surface 4c of 3c and cage 4.
保持器４のポケット4aの内面はボール５と同一曲率の
部分円弧状になっており、ボール５との間に微小な隙間
h4が形成されている。The inner surface of the pocket 4a of the retainer 4 has a partial arc shape having the same curvature as the ball 5, and a small gap
h 4 is formed.
前記の隙間h2,h3は、隙間h1と同一寸法に設定するの
が理想的であるとともに、隙間h4は隙間h1よりも小さく
設定するのが理想的である。Gap h 2, h 3 of the, as well to set the same size as the gap h 1 is ideal, gap h 4 is ideal to set smaller than the gap h 1.
内輪２と外輪３は相対的に回転するものであって、本
実施例では内輪２を回転させ、外輪３を固定させるよう
に構成しており、内輪２の回転に伴って保持器４が追従
して回転するので、作動中において、外輪３と保持器４
との間の隙間h3にある液相状態の金属潤滑剤にはボール
５の自転および公転により幅方向の中央側から両脇へ向
かう圧力P1が生じる。一方、内輪２と保持器４との間の
隙間h2にある金属潤滑剤にも前記圧力P1よりも若干小さ
な圧力P2が生ずる。The inner ring 2 and the outer ring 3 rotate relatively. In this embodiment, the inner ring 2 is rotated to fix the outer ring 3, and the retainer 4 follows the inner ring 2 as the inner ring 2 rotates. The outer ring 3 and the retainer 4 during operation.
The pressure P 1 is a metal lubricant liquid state in the gap h 3 extending from the center of the width direction by the rotation and revolution of the ball 5 to both sides between the results. On the other hand, a slightly lower pressure P 2 is generated than the pressure P 1 in the metal lubricant in the gap h 2 between the inner ring 2 and the cage 4.
そして、本実施例においては、保持器４の内周面4bに
複数のスパイラル溝6a,6bが、また保持器４の外周面4c
に複数のスパイラル溝6c,6dがそれぞれ刻設されてい
る。In the present embodiment, a plurality of spiral grooves 6a and 6b are formed on the inner peripheral surface 4b of the retainer 4, and the outer peripheral surface 4c of the retainer 4 is formed.
Are provided with a plurality of spiral grooves 6c and 6d, respectively.
スパイラル溝6aは内輪２の外周面2bに、スパイラル溝
6bは内輪２の外周面2cにそれぞれ対向しているととも
に、スパイラル溝6cは外輪３の内周面3bに、スパイラル
溝6dは外輪３の内周面3cにそれぞれ対向している。The spiral groove 6a is formed on the outer peripheral surface 2b of the inner ring 2 by a spiral groove.
The spiral groove 6c faces the inner peripheral surface 3b of the outer ring 3, and the spiral groove 6d faces the inner peripheral surface 3c of the outer ring 3, respectively.
この各スパイラル溝6a〜6dは、第２図に示すように、
回転方向に対し傾斜する状態に形成されている。各スパ
イラル溝6a〜6dそれぞれの外端部は幅方向の両脇で回転
方向Ａの下手側に位置しているとともに、中央部は幅方
向の中央側で回転方向Ａの上手側に位置している。な
お、第２図は、作図の都合上、スパイラル溝6a〜6dの数
を少なく書いているので、第１図のスパイラル溝6a〜6d
の数に対応していない。These spiral grooves 6a to 6d are, as shown in FIG.
It is formed so as to be inclined with respect to the rotation direction. The outer end of each of the spiral grooves 6a to 6d is located on the lower side in the rotation direction A on both sides in the width direction, and the center portion is located on the upper side in the rotation direction A on the center side in the width direction. I have. In FIG. 2, the number of the spiral grooves 6a to 6d is reduced for convenience of drawing, so that the spiral grooves 6a to 6d in FIG.
Does not correspond to the number of
スパイラル溝6aとスパイラル溝6bとはその各中央部が
連続していて『Ｖ』字形状に構成されており、また、ス
パイラル溝6cとスパイラル溝6dもその各中央部が連続し
ていて『Ｖ』字形状に構成されている。但し、保持器４
のポケット4aがある部分においては各スパイラル溝6a,6
bおよびスパイラル溝6c,6dがそれぞれ連続していない。The spiral groove 6a and the spiral groove 6b are each formed in a “V” shape with their respective center portions being continuous, and the spiral groove 6c and the spiral groove 6d are also formed in a “V” shape. ”-Shaped. However, cage 4
In the part where there is a pocket 4a, each spiral groove 6a, 6
b and the spiral grooves 6c and 6d are not continuous.
そして、回転中において、各スパイラル溝6a〜6dは、
第３図に示すように、保持器４が矢印Ａ方向に回転する
と、隙間h2,h3に存在する液相状態の金属潤滑剤に幅方
向の両脇（内輪2,外輪３および保持器４の幅方向の両端
側）から中央側（内輪２および外輪３の各軌道面2a,3a
側）に向かう圧力P3P4が生じる。And, during the rotation, each spiral groove 6a ~ 6d,
As shown in FIG. 3, when the retainer 4 rotates in the direction of arrow A, the metal lubricant in the liquid phase existing in the gaps h 2 and h 3 is applied to both sides in the width direction (the inner ring 2, the outer ring 3 and the retainer). 4 from both ends in the width direction) to the center side (the respective raceway surfaces 2a, 3a of the inner ring 2 and the outer ring 3).
Pressure P 3 P 4 is generated.
この圧力P3と圧力P4とは、内輪２および外輪３に対す
る保持器４の相対回転速度が異なるので、P3＞P4の関係
になる。The pressure P 3 and the pressure P 4 have a relationship of P 3 > P 4 because the relative rotation speed of the retainer 4 with respect to the inner ring 2 and the outer ring 3 is different.
そして、この圧力P3は前述の圧力P1に、また圧力P4は
前述の圧力P2にそれぞれ拮抗するので、この拮抗作用に
より、隙間h2,h3において前記液相状態の金属潤滑剤が
軸受外部に流出するのが防止されてここに保持される。
したがって、高温環境や高清浄度環境下などでも金属潤
滑剤を使用できるようになっている。Since the pressure P 3 and the pressure P 4 antagonize the pressure P 1 and the pressure P 2 , respectively, the metal lubricant in the liquid state in the gaps h 2 and h 3 due to the antagonism. Is prevented from flowing out of the bearing and is retained here.
Therefore, a metal lubricant can be used even in a high temperature environment or a high cleanliness environment.
第４図は本発明の第２実施例を示している。同図にお
いて第１図に付してある符号と同一のものは同一部品も
しくは対応する部分を指している。FIG. 4 shows a second embodiment of the present invention. In the figure, the same reference numerals as in FIG. 1 indicate the same parts or corresponding parts.
本実施例では、内輪２の軌道面2aおよび外輪３の軌道
面3aの深さが通常の深みぞ玉軸受のそれよりも深く設定
されている。この場合には、保持器４のポケット4aが円
筒形状に構成されているが、保持器４の厚みが薄くてポ
ケット4aとボール５との間の隙間に各スパイラル溝6a〜
6dにより生じる圧力が逃げにくくなるから、第１実施例
のように、ポケット4aの内面4dをボール５の曲率と同一
曲率にしなくてもかまわない。In this embodiment, the depth of the raceway surface 2a of the inner race 2 and the raceway surface 3a of the outer race 3 are set to be deeper than that of a normal deep groove ball bearing. In this case, the pocket 4a of the retainer 4 is formed in a cylindrical shape. However, the thickness of the retainer 4 is small, and the spiral grooves 6a to 6c are formed in the gaps between the pocket 4a and the ball 5.
Since the pressure generated by 6d is difficult to escape, the inner surface 4d of the pocket 4a does not have to have the same curvature as the curvature of the ball 5 as in the first embodiment.
なお、本発明は上記実施例のみに限定されるものでな
い。まず、本発明は深みぞ玉軸受以外の種々な転がり軸
受に適用しうる。また、金属潤滑剤の密封に関して、上
述したように保持器４で対策する他に、密封装置を用い
てもよい。さらに、上記実施例での保持器４のスパイラ
ル溝6a〜6dは『Ｖ』字形状に連続するように構成してい
るものに限定されず、例えば第５図に示すように、互い
違いに配置してもよいし、溝はスパイラル溝に限定され
ず、螺旋状の溝であってもかまわない。この他、保持器
４に設けていたスパイラル溝6a〜6dを、内輪２の外周面
2b,2cと外輪３の内周面3b,3cとにそれぞれ形成してもか
まわないし、保持器４と内・外輪２、３の両方に形成し
てもよいなど、種々な組み合わせが考えられる。内輪２
または外輪３にスパイラル溝を形成した場合には、この
スパイラル溝の両外端部はその中央部に対して回転方向
の上手側に配置させる必要がある。It should be noted that the present invention is not limited to only the above embodiment. First, the present invention can be applied to various rolling bearings other than the deep groove ball bearing. Further, in addition to taking measures against the sealing of the metal lubricant by the retainer 4 as described above, a sealing device may be used. Furthermore, the spiral grooves 6a to 6d of the retainer 4 in the above-described embodiment are not limited to those configured to be continuous in a “V” shape. For example, as shown in FIG. The groove may be a spiral groove, and may be a spiral groove. In addition, the spiral grooves 6a to 6d provided on the retainer 4 are
Various combinations are conceivable, for example, they may be formed on the inner peripheral surfaces 3b, 3c of the outer ring 3 and may be formed on both the retainer 4 and the inner and outer rings 2, 3. Inner ring 2
Alternatively, when a spiral groove is formed in the outer race 3, both outer ends of the spiral groove need to be arranged on the upper side in the rotational direction with respect to the center.
〈発明の効果〉 本発明では、所定温度で融解して液相状態となるGaま
たはGa合金などの金属潤滑剤を用いることで、振動、騒
音、回転トルクなどの諸特性に優れるようにしながら
も、軌道輪や転動体が腐食されずに済むようにして長寿
命化を達成することができる。<Effect of the Invention> In the present invention, by using a metal lubricant such as Ga or a Ga alloy which is melted at a predetermined temperature to be in a liquid phase, vibration, noise, and various characteristics such as rotational torque are improved. In addition, the life of the bearing ring and the rolling elements can be extended without being corroded.
しかも、転がり軸受の内・外輪間に転動体だけでなく
金属潤滑剤が存在することで、熱伝導性が良好となり、
放熱作用が優れることになるので、高温環境での使用に
適するものとなる。In addition, the presence of the metal lubricant as well as the rolling elements between the inner and outer rings of the rolling bearing improves the thermal conductivity,
Since the heat dissipating effect is excellent, it is suitable for use in a high temperature environment.
第１図ないし第３図は本発明の第１実施例にかかり、第
１図は深みぞ玉軸受の縦断面図、第２図は保持器の斜視
図、第３図はスパイラル溝により生ずる圧力の方向を示
す説明図である。 また、第４図は本発明の第２実施例にかかり、第１図に
対応した図である。第５図は本発明にかかる溝の配置状
態の他の例を示す説明図である。 １……深みぞ玉軸受（転がり軸受） ２……内輪 ３……外輪 ５……ボール（転動体）1 to 3 relate to a first embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a deep groove ball bearing, FIG. 2 is a perspective view of a retainer, and FIG. 3 is a pressure generated by a spiral groove. It is explanatory drawing which shows the direction. FIG. 4 is a diagram corresponding to FIG. 1, according to a second embodiment of the present invention. FIG. 5 is an explanatory view showing another example of the arrangement of the grooves according to the present invention. 1 ... deep groove ball bearing (rolling bearing) 2 ... inner ring 3 ... outer ring 5 ... ball (rolling element)
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭60−117531（ＪＰ，Ａ) 特開 昭60−113817（ＪＰ，Ａ) 特開 昭48−100542（ＪＰ，Ａ) 特開 昭61−55410（ＪＰ，Ａ) 特開 昭60−146917（ＪＰ，Ａ) 特開 昭61−112820（ＪＰ，Ａ) 特公 昭36−4403（ＪＰ，Ｂ１) 実公 昭49−37722（ＪＰ，Ｙ１) ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-60-117531 (JP, A) JP-A-60-113817 (JP, A) JP-A-48-100542 (JP, A) JP-A 61-181 55410 (JP, A) JP-A-60-146917 (JP, A) JP-A-61-112820 (JP, A) JP-B-36-4403 (JP, B1) JP-B-49-37722 (JP, Y1)
Claims (1)
て液相状態となるGaまたはGa合金が軸受内部に保持され
ている転がり軸受であって、 軌道輪および転動体が、鋼でなりその表面が前記Gaまた
はGa合金に対して耐蝕性を有するセラミックスあるいは
Ｗ、Moまたはこれらの合金材料で構成されているか、あ
るいは、それら自体が前記GaまたはGa合金に対して耐蝕
性を有するセラミックスあるいはＷ、Moまたはこれらの
合金材料で構成されており、前記転動体が保持器により
保持されるとともに、保持器と軌道輪および転動体との
隙間に前記GaまたはGa合金が配設されていることを特徴
とする転がり軸受。Claims: 1. A rolling bearing in which Ga or a Ga alloy which melts at the operating temperature of the bearing and becomes a liquid phase as a lubricant is held inside the bearing, wherein the race and the rolling element are made of steel. The surface thereof is made of ceramics having corrosion resistance to the Ga or Ga alloy or W, Mo or an alloy material thereof, or the ceramics itself has corrosion resistance to the Ga or Ga alloy or W, Mo or an alloy thereof, the rolling element is held by a retainer, and the Ga or Ga alloy is disposed in a gap between the retainer, a race and a rolling element. A rolling bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61309526A JP2627885B2 (en) | 1986-12-27 | 1986-12-27 | Rolling bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61309526A JP2627885B2 (en) | 1986-12-27 | 1986-12-27 | Rolling bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63167125A JPS63167125A (en) | 1988-07-11 |
| JP2627885B2 true JP2627885B2 (en) | 1997-07-09 |
Family
ID=17994071
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61309526A Expired - Lifetime JP2627885B2 (en) | 1986-12-27 | 1986-12-27 | Rolling bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2627885B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20160108964A1 (en) * | 2013-05-21 | 2016-04-21 | Schaeffler Technologies AG & Co. KG | Rolling element bearing with cage |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6368245B1 (en) * | 1999-04-26 | 2002-04-09 | Nsk Ltd. | Toroidal-type continuously variable transmission |
| DE102008044907A1 (en) * | 2008-08-29 | 2010-03-04 | Schaeffler Kg | Profiling of guide surfaces for rolling bearings with on-board cage |
| KR101989257B1 (en) * | 2014-10-29 | 2019-06-13 | 닛본 세이고 가부시끼가이샤 | Bearing device and spindle device |
| IT202100017096A1 (en) * | 2021-06-30 | 2022-12-30 | Skf Ab | ROLLING BEARING FOR HIGH SPEED EQUIPPED WITH AN OPTIMIZED CAGE TO REDUCE NOISE AT LOW SPEED |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| NL8303832A (en) * | 1983-11-08 | 1985-06-03 | Philips Nv | ROENTGEN TUBE WITH SPIRAL GROOVE BEARING. |
| JPS6155410A (en) * | 1984-08-27 | 1986-03-19 | Nippon Telegr & Teleph Corp <Ntt> | Solid lubricating bearing |
-
1986
- 1986-12-27 JP JP61309526A patent/JP2627885B2/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20160108964A1 (en) * | 2013-05-21 | 2016-04-21 | Schaeffler Technologies AG & Co. KG | Rolling element bearing with cage |
| US9829042B2 (en) * | 2013-05-21 | 2017-11-28 | Schaeffler Technologies AG & Co. KG | Rolling element bearing with cage |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63167125A (en) | 1988-07-11 |
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