JP2007032674A - Rolling bearing - Google Patents

Rolling bearing Download PDF

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JP2007032674A
JP2007032674A JP2005215908A JP2005215908A JP2007032674A JP 2007032674 A JP2007032674 A JP 2007032674A JP 2005215908 A JP2005215908 A JP 2005215908A JP 2005215908 A JP2005215908 A JP 2005215908A JP 2007032674 A JP2007032674 A JP 2007032674A
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Prior art keywords
cage
bearing
rolling bearing
rolling
convex portion
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Koji Kobayashi
孝司 小林
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NSK Ltd
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NSK Ltd
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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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6685—Details of collecting or draining, e.g. returning the liquid to a sump
    • 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
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F16C2300/22—High-speed rotation

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing capable of preventing occurrence of change of precision and seizure caused by heat generation due to stirring resistance of lubricant during rotation at high speed. <P>SOLUTION: If lubricating oil is accumulated and remains in the inside of the bearing, change of precision and seizure may occur by thermal expansion of each part by heat generation due to stirring resistance of lubricating oil. Although a cage may be deformed so as to be twisted from a claw part side (a supply side) due to the influence of centrifugal force generated by rotation at high speed, partial contact of a rolling body with the cage and contact of a bearing ring with the cage may occur, and heat generation, wear, and noise may occur, it is possible to discharge the lubricating oil accumulated and remaining in the inside of the rolling bearing by using venturi effect to prevent occurrence of these defects. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、例えば高速回転する装置に用いられると好適な転がり軸受に関する。   The present invention relates to a rolling bearing suitable for use in, for example, an apparatus that rotates at high speed.

一般的な転がり軸受において、軌道輪と転動体との転がり接触面における摩擦は、オイルやグリースによって潤滑される。潤滑グリースを利用した転がり軸受には、軸受内にあらかじめグリースを封入したものや更には密封板で軸受外部とを遮断したものがあり、一方、潤滑剤が軸受の一方の端面（アンギュラ玉軸受の場合は通常背面側）から供給され、軸受の他の一方の端面から排出される給油方式の装置に用いられる転がり軸受も存在する。このような転がり軸受は、工作機械の主軸等高速で回転する軸を支承することに利用されている。   In a general rolling bearing, the friction on the rolling contact surface between the race and the rolling element is lubricated by oil or grease. Rolling bearings that use lubricating grease include those that are pre-sealed with grease and that are sealed off from the outside with a sealing plate. In some cases, there are also rolling bearings that are supplied from the back surface side) and used for oil supply type devices that are discharged from the other end face of the bearing. Such a rolling bearing is used to support a shaft that rotates at high speed, such as a main shaft of a machine tool.

ところで、工作機械の主軸、電子計算機用磁気ドラム、歯科用スピンドル、内面研削用高周波スピンドル、また、ジェットエンジン用軸受等では、概ね毎分１万回転以上の高速回転が要求されている。このような高速回転用の転がり軸受には、潤滑を良好に達成、維持するために、潤滑剤を外部から軸受内に供給するタイプの潤滑方式のものが採用されている。特に、近年、オイルジェット、オイルミスト、オイルエア等によって、軸受の外部から軸受の内部に潤滑剤を強制的に供給し、軸受内を潤滑する方式が実現されている。   By the way, the spindle of a machine tool, a magnetic drum for an electronic computer, a dental spindle, a high-frequency spindle for internal grinding, a bearing for a jet engine, and the like are required to rotate at a high speed of approximately 10,000 revolutions per minute. Such a rolling bearing for high-speed rotation employs a type of lubrication system in which a lubricant is supplied from the outside into the bearing in order to achieve and maintain good lubrication. In particular, in recent years, a system has been realized in which a lubricant is forcibly supplied from the outside of the bearing to the inside of the bearing by an oil jet, oil mist, oil air, or the like to lubricate the inside of the bearing.

既述の高速回転用の転がり軸受では、潤滑剤が軸受内に滞留すると、潤滑剤を撹拌するときの撹拌抵抗により軸受が発熱し、軸受を構成する軌道輪や転動体が熱膨張して軸受の精度変化やひいては焼き付きの可能性が高くなるといった問題がある。そこで、特許文献１に記載の転がり軸受においては、内輪内周をテーパ形状とし、それにより潤滑剤の排出を促進させている。
特開平１１−２０１１７３号公報 In the above-described rolling bearing for high-speed rotation, if the lubricant stays in the bearing, the bearing generates heat due to the stirring resistance when the lubricant is stirred, and the bearing rings and rolling elements constituting the bearing thermally expand to cause the bearing to move. However, there is a problem that the accuracy change and the possibility of seizure increase. Therefore, in the rolling bearing described in Patent Document 1, the inner circumference of the inner ring is tapered, thereby promoting the discharge of the lubricant.
Japanese Patent Laid-Open No. 11-201173

しかるに、特許文献１の技術によれば、潤滑剤の排出を効果的に行えるが、更に排出を効率化させたいという要求がある。一方で、別個の排出手段を設けて、潤滑剤の排出を促進させることも考えられるが、それによりコスト増を招き、また軸受を装着する装置の設計の自由度を制限するといった問題が予想される。   However, according to the technique of Patent Document 1, the lubricant can be effectively discharged, but there is a demand for further improving the efficiency of the discharge. On the other hand, it is conceivable to provide a separate discharge means to promote the discharge of the lubricant. However, this increases the cost and limits the degree of freedom in the design of the apparatus for mounting the bearing. The

本発明は、かかる従来技術の問題点に鑑みてなされたものであり、高速回転下で、潤滑剤の撹拌抵抗による発熱により精度変化や焼き付きのおそれが少ない転がり軸受を提供することを目的とするものである。   The present invention has been made in view of the problems of the prior art, and an object of the present invention is to provide a rolling bearing that is less likely to cause a change in accuracy or seizure due to heat generated by a stirring resistance of a lubricant under high-speed rotation. Is.

本発明の転がり軸受は、外輪と、内輪と、前記外輪と前記内輪との間をそれぞれ転動可能な複数の転動体と、前記転動体を保持する保持器とを有し、
前記保持器には、その周面において前記外輪と前記内輪の少なくとも一方に向かって形成された凸部と、前記凸部と前記一方との間に開口した油路とが設けられていることを特徴とする。 The rolling bearing of the present invention includes an outer ring, an inner ring, a plurality of rolling elements that can roll between the outer ring and the inner ring, and a cage that holds the rolling element,
The retainer is provided with a convex portion formed on its peripheral surface toward at least one of the outer ring and the inner ring, and an oil passage opened between the convex portion and the one. Features.

本発明の転がり軸受によれば、前記保持器には、その周面において前記外輪と前記内輪の少なくとも一方に向かって形成された凸部と、前記凸部と前記一方との間に開口した油路とが設けられているので、前記凸部が前記外輪と前記内輪の少なくとも一方に対して相対回転したときに、ベンチュリー効果によって、前記凸部と前記一方との間が負圧になることを利用し、そこに開口した油路内に差圧を生じさせ、油路内において潤滑油の移動を行わせ、もって潤滑油の排出を行わせることができる。このようにすることで、別個の排出手段を設ける必要がなく、コストを抑え、軸受を装着する装置の設計の自由度を確保できる。   According to the rolling bearing of the present invention, the retainer includes a convex portion formed on its peripheral surface toward at least one of the outer ring and the inner ring, and an oil that opens between the convex portion and the one. Since the road is provided, when the convex portion rotates relative to at least one of the outer ring and the inner ring, a negative pressure is generated between the convex portion and the one due to the venturi effect. By utilizing this, a differential pressure is generated in the oil passage opened there, and the lubricating oil is moved in the oil passage, so that the lubricating oil can be discharged. By doing in this way, it is not necessary to provide a separate discharge means, cost can be reduced, and the freedom degree of design of the apparatus which mounts a bearing can be ensured.

前記外輪と前記内輪の少なくとも一方に凸部が設けられていると好ましい。   It is preferable that a convex portion is provided on at least one of the outer ring and the inner ring.

以下、図面を参照して本発明の実施の形態について説明する。図１は、本実施の形態にかかる転がり軸受の軸線方向断面図である。図２は、保持器の周辺を拡大して示す図であり、図３は、図２の構成を矢印III方向に見た図である。   Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is an axial sectional view of a rolling bearing according to the present embodiment. 2 is an enlarged view of the periphery of the cage, and FIG. 3 is a view of the configuration of FIG. 2 as viewed in the direction of arrow III.

図１において、転がり軸受は、外輪１と、内輪２と、外輪１と内輪２との間をそれぞれ転動可能な複数の転動体であるボール３と、ボール３を保持する保持器４とを有している。   In FIG. 1, the rolling bearing includes an outer ring 1, an inner ring 2, a ball 3 that is a plurality of rolling elements capable of rolling between the outer ring 1 and the inner ring 2, and a cage 4 that holds the ball 3. Have.

図２に示すように、保持器４は、周方向に連続した環状部４ａと、環状部４ａから軸線方向に延在する複数の爪部４ｂとを有している。隣接する爪部４ｂにより、ボール３を保持している。   As shown in FIG. 2, the retainer 4 includes an annular portion 4 a that is continuous in the circumferential direction, and a plurality of claw portions 4 b that extend from the annular portion 4 a in the axial direction. The ball 3 is held by the adjacent claw portion 4b.

図３に示すように、保持器４の環状部４ａの内周面には、周方向に少なくとも１カ所の凸部４ｃが形成されている。凸部４ｄは、周方向に進むにつれて徐々に盛り上がるがごとき形状を有している。凸部４ｃの内周面に一端が開口するようにして、油路４ｄが形成されている。油路４ｄは、環状部４ａと爪部４ｂの内部を延在し、図２に示すように、爪部４ｂの先端において他端が開口している。このような油路４ｄを有する保持器４は、樹脂などにより容易に形成できる。なお、本実施の形態では、保持器４の環状部４ａに対向する内輪２の外周面に、少なくとも１カ所の凸部２ａを設けているが、必ずしも必要なものではない。   As shown in FIG. 3, at least one convex portion 4 c is formed in the circumferential direction on the inner peripheral surface of the annular portion 4 a of the cage 4. The convex portion 4d has a shape that rises gradually as it proceeds in the circumferential direction. An oil passage 4d is formed so that one end is opened on the inner peripheral surface of the convex portion 4c. The oil passage 4d extends inside the annular portion 4a and the claw portion 4b, and the other end is opened at the tip of the claw portion 4b as shown in FIG. The cage 4 having such an oil passage 4d can be easily formed of resin or the like. In the present embodiment, at least one convex portion 2a is provided on the outer peripheral surface of the inner ring 2 facing the annular portion 4a of the cage 4, but this is not always necessary.

ここで、凸部４ｃと内輪２との間のスキマは、それ以外の環状部４ａと内輪２との間のスキマより小さくなっている。従って、外輪１と内輪２とが相対回転した場合において、保持器４の環状部４ａの回転と共に、凸部４ｃが内輪２の外周に沿って移動すると、それに伴ってスキマの狭い領域が周方向に移動するから、スキマの狭い領域を通過する流体（ここでは空気もしくは潤滑油）の速度が速まる。すると、ベンチュリ効果により、凸部４ｃと内輪２との間の圧力Ｐｖは、それ以外の環状部４ａと内輪２との間の圧力Ｐより低くなる。   Here, the clearance between the convex portion 4 c and the inner ring 2 is smaller than the clearance between the other annular portion 4 a and the inner ring 2. Therefore, when the outer ring 1 and the inner ring 2 are rotated relative to each other, when the convex portion 4c moves along the outer periphery of the inner ring 2 along with the rotation of the annular portion 4a of the retainer 4, a narrow region of the clearance is caused in the circumferential direction. Therefore, the speed of the fluid (in this case, air or lubricating oil) passing through a narrow area of the gap increases. Then, the pressure Pv between the convex part 4c and the inner ring 2 becomes lower than the pressure P between the other annular part 4a and the inner ring 2 due to the venturi effect.

しかるに、油路４ｄの一端は、凸部４ｃと内輪２との間に開口しているので、その他端との間にΔＰ＝Ｐ−Ｐｖの差圧が生じる。かかる差圧を利用して、図２に示すように、油路４ｄ内に潤滑油の移動を生じさせ、それにより油路４ｄの他端側に存在する潤滑油を、油路４ｄの一端側すなわち凸部４ｃと内輪２との間から排出することができる。又、保持器４の凸部４ｃは、内輪２の凸部２ａに周期的に対向するが、その都度、圧力Ｐｖが変動するので、ゴミなどの異物が油路に堆積しにくい構造となっている。   However, since one end of the oil passage 4d is open between the convex portion 4c and the inner ring 2, a differential pressure of ΔP = P−Pv is generated between the other end. Using this differential pressure, as shown in FIG. 2, the lubricating oil is caused to move in the oil passage 4d, so that the lubricating oil present on the other end side of the oil passage 4d is moved to one end side of the oil passage 4d. That is, it can be discharged from between the convex portion 4 c and the inner ring 2. The convex portion 4c of the cage 4 periodically faces the convex portion 2a of the inner ring 2. However, since the pressure Pv fluctuates each time, foreign matter such as dust does not easily accumulate on the oil passage. Yes.

潤滑油が軸受内部で滞留すると、潤滑油の撹幹抵抗による発熱から各部品の熱膨張による精度変化や焼付きを生じる恐れがある。また、高速回転による遠心力の影響により、保持器が爪部側（供給側）から捩られるように変形し、転動体と保持器の局部接触や軌道輪と保持器の接触を生じ、発熱や摩耗、騒音などを生じる恐れもあるが、本実施の形態によれば、ベンチュリ効果によって、転がり軸受の内部に滞留した潤滑油を排出させ、かかる不具合を未然に防止することができる。   If the lubricating oil stays inside the bearing, there is a risk that accuracy changes or seizure may occur due to thermal expansion of each component due to heat generated by the stirrer resistance of the lubricating oil. Also, due to the centrifugal force due to high-speed rotation, the cage is deformed so as to be twisted from the claw side (supply side), causing local contact between the rolling element and the cage and contact between the race and the cage, Although there is a risk of causing wear, noise, and the like, according to the present embodiment, the lubricating oil staying inside the rolling bearing can be discharged by the venturi effect, and such a problem can be prevented.

図４は、変形例にかかる転がり軸受の軸線方向断面図である。本変形例においては、ボール３の軌道位置をオフセット（δ）させ、潤滑油排出側の領域を広げたことにより、ベンチュリ効果をより明確にしている。なお、それ以外の構成については、上述した実施の形態と同様であるので説明を省略する。   FIG. 4 is an axial sectional view of a rolling bearing according to a modification. In this modification, the Venturi effect is made clearer by offsetting (δ) the orbital position of the ball 3 and widening the region on the lubricating oil discharge side. Since other configurations are the same as those in the above-described embodiment, the description thereof is omitted.

図５は、別な変形例にかかる転がり軸受の軸線方向断面図である。本変形例においては、保持器４の環状部４ａの外周面にも凸部４ｃを設け、且つ外輪１の内周面にも凸部１ａを設けた点が異なっている。図示していないが、凸部４ｃの外周面に一端が開口し、爪部４ｂの先端において他端が開口している油路が設けられているので、同様な作用効果が期待できる。なお、本例において、保持器４の環状部４ａの内周面の凸部４ｃは省略しても良い。   FIG. 5 is an axial sectional view of a rolling bearing according to another modification. This modification is different in that a convex portion 4 c is provided on the outer peripheral surface of the annular portion 4 a of the cage 4 and a convex portion 1 a is provided on the inner peripheral surface of the outer ring 1. Although not shown, since an oil passage having one end opened on the outer peripheral surface of the convex portion 4c and the other end opened at the tip of the claw portion 4b is provided, a similar effect can be expected. In this example, the convex portion 4c on the inner peripheral surface of the annular portion 4a of the cage 4 may be omitted.

図６は、別な変形例にかかる保持器の環状部を半径方向内方から見た図である。図６に示すように、環状部４ａの内周面に複数本の螺旋状の溝４ｆを形成することで、保持器４の回転に伴って潤滑油の排出効果を高めることができる。なお、螺旋状の溝４ｆは、環状部４ａの外周面に形成しても良い。   FIG. 6 is a view of the annular portion of the cage according to another modification as viewed from the inside in the radial direction. As shown in FIG. 6, by forming a plurality of spiral grooves 4 f on the inner peripheral surface of the annular portion 4 a, the effect of discharging the lubricating oil can be enhanced with the rotation of the cage 4. In addition, you may form the helical groove | channel 4f in the outer peripheral surface of the cyclic | annular part 4a.

以上、本発明を実施例を参照して説明してきたが、本発明は上記実施の形態に限定して解釈されるべきではなく、適宜変更・改良が可能であることはもちろんである。   The present invention has been described with reference to the embodiments. However, the present invention should not be construed as being limited to the above-described embodiments, and can be modified or improved as appropriate.

本実施の形態にかかる転がり軸受の軸線方向断面図である。It is an axial direction sectional view of a rolling bearing concerning this embodiment. 保持器の周辺を拡大して示す図である。It is a figure which expands and shows the periphery of a holder | retainer. 図２の構成を矢印III方向に見た図である。It is the figure which looked at the structure of FIG. 2 in the arrow III direction. 変形例にかかる転がり軸受の軸線方向断面図である。It is sectional drawing of the axial direction of the rolling bearing concerning a modification. 別な変形例にかかる転がり軸受の軸線方向断面図である。It is an axial sectional view of a rolling bearing according to another modification. 別な変形例にかかる保持器の環状部を半径方向内方から見た図である。It is the figure which looked at the annular part of the cage concerning another modification from the radial inside.

符号の説明Explanation of symbols

１ 外輪
２ 内輪
３ ボール
４ 保持器
４ａ 環状部
４ｂ 爪部
４ｃ 凸部
DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 3 Ball 4 Cage 4a Annular part 4b Claw part 4c Convex part

Claims (2)

外輪と、内輪と、前記外輪と前記内輪との間をそれぞれ転動可能な複数の転動体と、前記転動体を保持する保持器とを有し、
前記保持器には、その周面において前記外輪と前記内輪の少なくとも一方に向かって形成された凸部と、前記凸部と前記一方との間に開口した油路とが設けられていることを特徴とする転がり軸受。 An outer ring, an inner ring, a plurality of rolling elements capable of rolling between the outer ring and the inner ring, and a cage for holding the rolling element,
The retainer is provided with a convex portion formed on its peripheral surface toward at least one of the outer ring and the inner ring, and an oil passage opened between the convex portion and the one. Characteristic rolling bearing. 前記外輪と前記内輪の少なくとも一方に凸部が設けられていることを特徴とする請求項１に記載の転がり軸受。

The rolling bearing according to claim 1, wherein a convex portion is provided on at least one of the outer ring and the inner ring.

JP2005215908A 2005-07-26 2005-07-26 Rolling bearing Pending JP2007032674A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010067852A1 (en) * 2008-12-10 2010-06-17 日本精工株式会社 Ball bearing, and transmission for hybrid vehicle
JP2011001990A (en) * 2009-06-17 2011-01-06 Jtekt Corp Roller bearing device and rolling bearing used therefor
DE102015207660A1 (en) * 2015-04-27 2016-10-27 Schaeffler Technologies AG & Co. KG Ball snap cage for a rolling bearing

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010067852A1 (en) * 2008-12-10 2010-06-17 日本精工株式会社 Ball bearing, and transmission for hybrid vehicle
CN102119281A (en) * 2008-12-10 2011-07-06 日本精工株式会社 Ball bearing, and transmission for hybrid vehicle
US8523450B2 (en) 2008-12-10 2013-09-03 Nsk Ltd. Ball bearing and hybrid vehicle transmission
JP5531966B2 (en) * 2008-12-10 2014-06-25 日本精工株式会社 Ball bearing and hybrid vehicle transmission
US8777489B2 (en) 2008-12-10 2014-07-15 Nsk Ltd. Ball bearing and hybrid vehicle transmission
USRE49737E1 (en) 2008-12-10 2023-11-28 Nsk Ltd. Ball bearing
JP2011001990A (en) * 2009-06-17 2011-01-06 Jtekt Corp Roller bearing device and rolling bearing used therefor
DE102015207660A1 (en) * 2015-04-27 2016-10-27 Schaeffler Technologies AG & Co. KG Ball snap cage for a rolling bearing

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