WO2009107340A1

WO2009107340A1 - Rolling bearing and spindle device using the same

Info

Publication number: WO2009107340A1
Application number: PCT/JP2009/000627
Authority: WO
Inventors: 李ソン雨
Original assignee: Ntn株式会社
Priority date: 2008-02-29
Filing date: 2009-02-17
Publication date: 2009-09-03
Also published as: TW200942706A; JP2009204139A

Abstract

A rolling bearing has high-speed, long-life, and maintenance-free characteristics achieved only by using grease sealed in the bearing and is effectively lubricated. The rolling bearing has an inner ring (1), an outer ring (2), and rolling bodies (3). The outer ring (2) can be the stationary raceway ring. The outer ring (2) has a step surface (2b) contiguous to a raceway surface (2a) of the outer ring (2) and extending in the direction away from the rolling bodies (3). The rolling bearing has a gap forming piece (7) having an annular shape. The gap forming piece (7) has a front end surface facing the step surface (2b) with a gap (15) in between, and also has a peripheral wall forming a flow path (14) between the peripheral wall and the outer ring (2). The rolling bearing further has a grease pool (9) communicating with the flow path (14), and also has a circular arc piece (16) at the front end surface of the gap forming piece (7). The circular arc piece (16) closes a circumferential part of the gap (15) between the front end surface and the step surface (2b).

Description

転がり軸受、およびそれを用いた主軸装置Rolling bearing and spindle device using the same

関連出願Related applications

　本願は２００８年２月２９日出願の特願２００８－０４９２４３の優先権を主張するものであり、その全体を参照により本出願の一部をなすものとして引用する。 This application claims the priority of Japanese Patent Application No. 2008-049243 filed on Feb. 29, 2008, which is incorporated herein by reference in its entirety as a part of this application.

　この発明は、工作機械主軸等のグリース潤滑とされる潤滑機構付きの転がり軸受、およびそれを用いた主軸装置に関する。 The present invention relates to a rolling bearing with a lubrication mechanism used as grease lubrication for a machine tool spindle and the like, and a spindle apparatus using the same.

　工作機械主軸軸受の潤滑方法として、メンテナンスフリーで使用可能なグリース潤滑、搬送エアに潤滑オイルを混合してオイルをノズルより軸受内に噴射するエアオイル潤滑、軸受内に潤滑油を直接に噴射するジェット潤滑等の方法がある。最近の工作機械は、加工能率を上げるために、ますます高速化の傾向にあり、主軸軸受の潤滑も比較的安価で簡単に高速化が可能なエアオイル潤滑が多く用いられてきている。しかし、このエアオイル潤滑法は、付帯設備としてエアオイル供給装置が必要であることと、多量のエアを必要とすることから、コスト、騒音、省エネ、省資源の観点から問題がある。また、オイルの飛散によって環境を悪化させる問題もある。これらの問題を回避するために、最近ではグリース潤滑による高速化が注目され始め、要望も多くなってきている。 As a lubrication method for machine tool spindle bearings, grease lubrication that can be used maintenance-free, air-oil lubrication in which lubricating oil is mixed with carrier air and oil is injected into the bearing from the nozzle, jet that injects lubricating oil directly into the bearing There are methods such as lubrication. In recent machine tools, in order to increase machining efficiency, there is a tendency for higher speed, and lubrication of main shaft bearings is also relatively inexpensive and air-oil lubrication that can be speeded up easily is often used. However, this air oil lubrication method has a problem from the viewpoint of cost, noise, energy saving, and resource saving because it requires an air oil supply device as ancillary equipment and requires a large amount of air. There is also a problem of deteriorating the environment due to the scattering of oil. In order to avoid these problems, recently, speeding up by grease lubrication has begun to attract attention, and requests are increasing.

　このような試みの一つに、例えば特許文献１が挙げられる。特許文献１に記載の転がり軸受は、図７に示すように、内部にグリース溜まり９を形成したグリース溜まり形成部品６を固定側軌道輪２（例えば外輪）に接して設けると共に、このグリース溜まり形成部品６から固定側軌道輪２の軌道面２ａの付近まで延びて、固定側軌道輪２との間に隙間１５を形成する隙間形成片７を設け、前記グリース溜まり９と固定側軌道輪２の軌道面２ａとの間を前記隙間１５を介して連通させたものである。 One example of such attempts is Patent Document 1. As shown in FIG. 7, the rolling bearing described in Patent Document 1 is provided with a grease pool forming component 6 having a grease pool 9 formed therein in contact with the stationary race 2 (for example, the outer ring), and this grease pool formation. A gap forming piece 7 extending from the component 6 to the vicinity of the raceway surface 2 a of the fixed side raceway 2 and forming a gap 15 with the fixed side raceway ring 2 is provided, and the grease reservoir 9 and the fixed side raceway ring 2 are The track surface 2 a is communicated with the gap 15.

　上記転がり軸受によると、軸受の停止時には、グリース中の増稠剤および前記隙間１５の毛細管現象によりグリースの基油が隙間１５に移動する。軸受を運転すると、隙間１５に貯油されていた基油は、運転で生じる固定側軌道輪２の温度変化と、転動体３の公転・自転で生じる空気流とにより隙間１５から吐出されて、固定側軌道輪２の軌道面２ａに付着しながら移動して転動体接触部に連続的に補給される。
特開２００６－１３２７６５号公報 According to the rolling bearing, when the bearing is stopped, the base oil of the grease moves to the gap 15 due to the thickener in the grease and the capillary phenomenon of the gap 15. When the bearing is operated, the base oil stored in the clearance 15 is discharged from the clearance 15 due to the temperature change of the stationary-side raceway ring 2 generated by the operation and the air flow generated by the revolution / rotation of the rolling element 3 and fixed. It moves while adhering to the raceway surface 2a of the side raceway ring 2 and is continuously supplied to the rolling element contact portion.
JP 2006-132765 A

　特許文献１に記載のものは、前記隙間１５の隙間量δの寸法を例えばδ＝５０～１００μｍに設定することで、固定側軌道輪２の軌道面２ａに適量の潤滑油を供給するようにしている。しかし、隙間１５の隙間量δは微小であり、設定上の許容範囲も狭いため、その調整が難しい。隙間量δが小さすぎると、軌道面２ａへの潤滑油の供給が不十分となる。また、隙間量δが大きすぎると、初期に軸受に封入されたグリースに、運転時に隙間１５から吐出される潤滑油が加わることで、軸受空間の潤滑油が過剰となり、運転中の攪拌抵抗が大きくなる。 In the device described in Patent Document 1, an appropriate amount of lubricating oil is supplied to the raceway surface 2a of the fixed side raceway ring 2 by setting the size of the gap amount δ of the gap 15 to, for example, δ = 50 to 100 μm. ing. However, since the gap amount δ of the gap 15 is very small and the setting allowable range is narrow, it is difficult to adjust. When the gap amount δ is too small, the supply of lubricating oil to the raceway surface 2a becomes insufficient. On the other hand, if the gap amount δ is too large, the lubricating oil discharged from the gap 15 during operation is added to the grease initially sealed in the bearing, so that the lubricating oil in the bearing space becomes excessive, and the stirring resistance during operation is reduced. growing.

　この発明の目的は、軸受内に封入したグリースと軸受に設けたグリース溜まりに封入したグリースとを使用して高速化と長寿命化、メンテナンスフリーを達成でき、かつ効果的な潤滑ができる転がり軸受を提供することである。
　この発明の他の目的は、上記転がり軸受を主軸装置に用いた場合に、その主軸装置に合わせて転がり軸受の隙間から吐出される潤滑油を適正に調整することである。 An object of the present invention is to provide a rolling bearing capable of achieving high speed, long life, maintenance-free, and effective lubrication by using grease sealed in the bearing and grease sealed in a grease reservoir provided in the bearing. Is to provide.
Another object of the present invention is to appropriately adjust the lubricating oil discharged from the clearance of the rolling bearing in accordance with the main spindle device when the rolling bearing is used in the main spindle device.

　この発明にかかる転がり軸受は、内輪、外輪、およびこれら内外輪の軌道面間に介在する複数の転動体を有する転がり軸受において、軌道輪である内輪および外輪のうち、回転しない固定側軌道輪に、軌道面に続く段差面を転動体から離れる方向に設け、先端面が前記段差面に隙間を介して対面し周壁で前記固定側軌道輪との間に流路を形成する環状の隙間形成片を設け、前記流路に連通するグリース溜まりを設け、前記隙間形成片の先端面に、この先端面と前記段差面との間の前記隙間の円周方向の一部を塞ぐ円弧状片を設けた。
　この発明において、前記円弧状片を、前記隙間形成片の先端面の円周方向複数箇所に設けて、前記隙間の隣合う円弧状片間に位置して前記円弧状片によって塞がれていない箇所である潤滑油吐出部を円周方向の複数箇所に形成してもよい。
　また、前記隙間形成片の先端面のうち、円弧状片が設けられている円周方向範囲の方が、円弧状片が設けられていない円周方向範囲よりも広くしてもよい。 The rolling bearing according to the present invention is a rolling bearing having an inner ring, an outer ring, and a plurality of rolling elements interposed between the raceways of the inner and outer rings. An annular gap forming piece that is provided with a step surface that follows the raceway surface in a direction away from the rolling element, and whose tip surface faces the step surface via a gap and forms a flow path between the peripheral wall and the fixed-side raceway. A grease reservoir that communicates with the flow path, and an arcuate piece that closes a portion of the gap between the tip surface and the stepped surface in the circumferential direction is provided on the tip surface of the gap forming piece. It was.
In the present invention, the arc-shaped pieces are provided at a plurality of locations in the circumferential direction on the distal end surface of the gap forming piece, and are positioned between adjacent arc-shaped pieces of the gap and are not blocked by the arc-shaped pieces. You may form the lubricating oil discharge part which is a location in the multiple places of the circumferential direction.
Moreover, you may make the direction of the circumferential direction in which the arc-shaped piece is provided among the front end surfaces of the said gap formation piece wider than the circumferential range in which the arc-shaped piece is not provided.

　この構成の転がり軸受装置は、グリース溜まりおよび流路にグリースを充填して使用される。軸受空間には初期潤滑用としてグリースを封入しておく。これにより、軸受の停止時には、グリース中の増稠剤および隙間の毛細管現象により、グリース中の基油が流路から隙間へ移動し、この毛細管現象と油の表面張力とが相まって隙間に基油が油状で保持される。軸受を回転すると、隙間に貯油されていた基油は、運転で生じる固定側軌道輪の温度変化と、転動体の公転・自転で生じる空気流とにより隙間から吐出されて、固定側軌道輪の軌道面に付着しながら移動して転動体接触部に連続的に供給される。よって、軸受内に封入したグリースと軸受に設けたグリース溜まりに封入したグリースとを使用して高速化と長寿命化、メンテナンスフリーを達成できる。 ¡The rolling bearing device with this configuration is used by filling the grease reservoir and flow passage with grease. Grease is sealed in the bearing space for initial lubrication. As a result, when the bearing is stopped, the base oil in the grease moves from the flow path to the gap due to the thickener in the grease and the capillary phenomenon in the gap, and this capillary phenomenon and the surface tension of the oil combine to cause the base oil in the gap. Is retained oily. When the bearing is rotated, the base oil stored in the gap is discharged from the gap due to the temperature change of the fixed side raceway that occurs during operation and the air flow that occurs due to the revolution and rotation of the rolling element, and the base side of the fixed side raceway It moves while adhering to the raceway surface and is continuously supplied to the rolling element contact portion. Therefore, it is possible to achieve high speed, long life and maintenance-free by using the grease sealed in the bearing and the grease sealed in the grease reservoir provided in the bearing.

　円弧状片の軸方向長さを目標とする隙間量の寸法に設定しておけば、円弧状片の先端が段差面に当接するように隙間形成片を固定側軌道輪に組み付けることにより、目標とする隙間量の隙間が容易に得られる。また、隙間形成片の先端面における円弧状片の設けられている円周方向範囲を変えることで、円弧状片によって塞がれていない隙間部分すなわち潤滑油吐出部の断面積を変えることができ、隙間から吐出される潤滑油の量を調整できる。それにより、軸受空間の潤滑油が過剰となり、運転中の攪拌抵抗が大きくなることを防げる。 If the axial length of the arc-shaped piece is set to the target gap amount dimension, the gap-forming piece is assembled to the stationary side ring so that the tip of the arc-shaped piece contacts the step surface. A gap having a gap amount of In addition, by changing the circumferential range in which the arc-shaped piece is provided on the tip surface of the gap forming piece, the cross-sectional area of the gap portion that is not blocked by the arc-shaped piece, that is, the lubricating oil discharge portion can be changed. The amount of lubricating oil discharged from the gap can be adjusted. Thereby, it is possible to prevent the lubricating oil in the bearing space from becoming excessive and increase the stirring resistance during operation.

　潤滑油吐出部を円周方向の複数箇所に形成すれば、潤滑油を円周方向にバランスよく供給することができる。また、隙間形成片の先端面のうち、円弧状片が設けられている円周方向範囲の方が、円弧状片が設けられていない円周方向範囲よりも広くすれば、隙間から吐出される潤滑油量を抑制する効果が高く、隙間を極端に狭くしなくても潤滑油量を適性に調整することが可能になる。そのため、固定側軌道輪および隙間形成片の加工や組立が容易になる。 Lubricating oil can be supplied in a balanced manner in the circumferential direction by forming the lubricating oil discharge portions at a plurality of locations in the circumferential direction. Moreover, if the circumferential direction range in which the arc-shaped piece is provided is wider than the circumferential range in which the arc-shaped piece is not provided in the tip surface of the gap forming piece, the gap is discharged from the gap. The effect of suppressing the amount of lubricating oil is high, and the amount of lubricating oil can be adjusted appropriately without making the gap extremely narrow. Therefore, processing and assembly of the fixed-side track ring and the gap forming piece are facilitated.

　この発明において、前記固定側軌道輪が外輪であってもよい。
　固定側軌道輪が外輪である場合、外輪に前記段差面が設けられるが、グリース封入状態で軸受を回転させたときに、封入グリースが遠心力で外輪内径部に飛散するため、前記隙間と軌道輪との間の基油の繋がりが確実となる。そのため、転動体接触部で潤滑油として消費される分の基油が、グリース溜まりから上記隙間を経て軌道面に補給される作用が高められ、より安定した潤滑油の補給が行われる。 In this invention, the fixed-side race may be an outer ring.
When the stationary ring is an outer ring, the stepped surface is provided on the outer ring, but when the bearing is rotated in a grease-filled state, the sealed grease scatters to the inner diameter of the outer ring by centrifugal force. The connection of the base oil to the wheel is ensured. Therefore, the base oil that is consumed as the lubricating oil in the rolling element contact portion is replenished to the raceway surface from the grease reservoir through the gap, and the lubricating oil is more stably replenished.

　転がり軸受が横型主軸の支持に使用される場合は、前記隙間のうちの前記潤滑油吐出部を円周の下側半分に位置させるのがよい。
　横型主軸の主軸装置では、重力の影響により、隙間の下部に潤滑油が多量に偏在しやすい。潤滑油が多量に偏在すると、軸受回転時の攪拌抵抗が大きくなる。そこで、隙間形成片の先端面において円弧状片の設けられていない箇所、すなわち潤滑油吐出部を円周の下側半分に位置させ、上側半分を塞ぐことで、上側半分の箇所から吐出される余分な潤滑油が下側に移動して下部に潤滑油の多量の偏在が生じることを解消する。なお、潤滑油吐出部が上側半分に位置すると、潤滑油吐出部からの潤滑油の吐出が生じ難くなるが、下側半分の潤滑油吐出部を位置させることで、潤滑油の円滑な吐出を可能としている。このように、多量の潤滑油が隙間の下部に多量に偏在して攪拌抵抗が大きくなることを回避しながら、円滑な潤滑油の供給を可能としている。 When a rolling bearing is used to support a horizontal main shaft, the lubricating oil discharge part in the gap is preferably located in the lower half of the circumference.
In a main spindle device of a horizontal main spindle, a large amount of lubricating oil tends to be unevenly distributed below the gap due to the influence of gravity. If a large amount of lubricating oil is unevenly distributed, the stirring resistance during rotation of the bearing increases. Therefore, the portion where the arc-shaped piece is not provided on the front end surface of the gap forming piece, that is, the lubricating oil discharge portion is positioned in the lower half of the circumference, and the upper half is closed to discharge from the upper half. This eliminates the occurrence of excessive distribution of lubricant oil in the lower part due to the excess lubricant oil moving downward. If the lubricating oil discharge part is located in the upper half, it is difficult for the lubricating oil discharge to occur from the lubricating oil discharge part.However, by positioning the lower half lubricating oil discharge part, the lubricating oil can be smoothly discharged. It is possible. In this way, a smooth supply of lubricating oil is possible while avoiding a large amount of lubricating oil being unevenly distributed in the lower part of the gap and increasing the stirring resistance.

　例えば、前記潤滑油吐出部を、転がり軸受の中心と通る垂線上に１箇所だけ形成することができる。
　これにより、重力方向に多量の潤滑油が偏って吐出することを防ぐ効果が期待できる。 For example, the lubricating oil discharge part can be formed only at one place on a perpendicular passing through the center of the rolling bearing.
Thereby, the effect which prevents that a large amount of lubricating oil discharges biased in the direction of gravity can be expected.

　前記潤滑油吐出部を、転がり軸受の中心と通る垂線を挟んで対称となる２箇所に形成してもよい。
　潤滑油吐出部が１箇所であると、潤滑不良になる可能性がある。その場合には、このように潤滑油吐出部を２箇所に設けるとよい。 You may form the said lubricating oil discharge part in two places which become symmetrical on both sides of the perpendicular passing through the center of a rolling bearing.
If there is only one lubricating oil discharge part, there is a possibility of poor lubrication. In that case, it is preferable to provide the lubricating oil discharge portions in two places as described above.

　前記潤滑油吐出部を、転がり軸受の中心と通る垂線上の１箇所、および前記垂線を挟んで対称となる２箇所の計３箇所に形成し、前記垂線上の１箇所に位置する潤滑油吐出部の断面積を、垂線を挟んで対称となる２箇所にそれぞれ位置する潤滑油吐出部の断面積よりも狭くしてもよい。
　前記垂線上の１箇所、すなわち円周の下端に位置する潤滑油吐出部は、垂線を挟んで対称となる２箇所にそれぞれ位置する潤滑油吐出部よりも重力の影響を受けやすい。そこで、上記のように潤滑油吐出部を３箇所に設けた場合、下端の潤滑油吐出部の断面積を他の潤滑油吐出部の断面積よりも小さくすることで、各潤滑油吐出部からほぼ同量の潤滑油が吐出されるようにするのが好ましい。 The lubricating oil discharge portion is formed at a total of three locations, one on the perpendicular passing through the center of the rolling bearing and two symmetrical with respect to the vertical, and the lubricating oil discharge located at one location on the vertical The cross-sectional area of the portion may be made narrower than the cross-sectional area of the lubricating oil discharge portion located at two locations that are symmetrical with respect to the vertical line.
The lubricating oil discharge part located at one position on the perpendicular line, that is, at the lower end of the circumference, is more susceptible to gravity than the lubricating oil discharge parts located at two symmetrical positions across the vertical line. Therefore, when the lubricating oil discharge portions are provided in three places as described above, the cross-sectional area of the lower lubricating oil discharge portion is made smaller than the cross-sectional area of the other lubricating oil discharge portions, so that It is preferable that approximately the same amount of lubricating oil be discharged.

　この発明の主軸装置は、上記転がり軸受を用いて縦型主軸を支持した主軸装置であって、一対の転がり軸受を有し、主軸の上部を支持する転がり軸受の上側、および下部を支持する転がり軸受の下側にそれぞれ前記隙間形成片を設け、前記主軸の上部を支持する転がり軸受は、下部を支持する転がり軸受よりも、前記隙間形成片の先端面における前記円弧状片の設けられている円周方向範囲が広い。 A main spindle device according to the present invention is a main spindle device that supports a vertical main spindle using the above-described rolling bearing, and has a pair of rolling bearings, and supports the upper and lower portions of the rolling bearing that supports the upper portion of the main shaft. The rolling bearings that provide the gap forming pieces on the lower sides of the bearings and support the upper part of the main shaft are provided with the arc-shaped pieces on the front end surface of the gap forming pieces, rather than the rolling bearings that support the lower part. Wide circumferential range.

　縦型主軸の主軸装置では、重力の影響により、下部の転がり軸受よりも上部の軸受の方が、前記隙間から吐出される潤滑油の量が多い。そこで、主軸の上部を支持する転がり軸受は、下部を支持する転がり軸受よりも、隙間形成片の先端面における円弧状片の設けられている円周方向範囲を広くする。円弧状片の設けられている円周方向範囲が広いということは、隙間の潤滑油吐出部の面積が小さいということである。これにより、主軸の上部を支持する転がり軸受と下部を支持する転がり軸受とで、隙間から吐出される潤滑油の量を同程度にすることができる。 In the main spindle device of the vertical spindle, the amount of lubricating oil discharged from the gap is larger in the upper bearing than in the lower rolling bearing due to the influence of gravity. Therefore, the rolling bearing that supports the upper portion of the main shaft has a wider circumferential range in which the arc-shaped piece is provided on the tip surface of the gap forming piece than the rolling bearing that supports the lower portion. The wide circumferential range in which the arc-shaped pieces are provided means that the area of the lubricating oil discharge portion in the gap is small. As a result, the amount of lubricating oil discharged from the gap can be made comparable between the rolling bearing that supports the upper portion of the main shaft and the rolling bearing that supports the lower portion.

　この発明は、添付の図面を参考にした以下の好適な実施形態の説明からより明瞭に理解されるであろう。しかしながら、実施形態および図面は単なる図示および説明のためのものであり、この発明の範囲を定めるために利用されるべきでない。この発明の範囲は添付のクレームによって定まる。添付図面において、複数の図面における同一の部品番号は、同一部分を示す。
（Ａ）はこの発明の実施形態に係る転がり軸受の断面図、（Ｂ）はその部分拡大図である。同転がり軸受の隙間形成片の側面図である。縦型主軸の主軸装置の断面図である。（Ａ）は同主軸装置の主軸の上部を支持する転がり軸受の隙間形成片の側面図、（Ｂ）は下部を支持する転がり軸受の隙間形成片の側面図である。横型主軸の主軸装置の断面図である。（Ａ），（Ｂ），（Ｃ）は同主軸装置の主軸の支持に適した転がり軸受の隙間形成片の側面図である。従来の潤滑機構付きの転がり軸受の断面図である。隙間形成片における潤滑油の偏りを示す説明図である。 The present invention will be more clearly understood from the following description of preferred embodiments with reference to the accompanying drawings. However, the embodiments and drawings are merely for illustration and description and should not be used to define the scope of the present invention. The scope of the invention is defined by the appended claims. In the accompanying drawings, the same part number in a plurality of drawings indicates the same part.
(A) is sectional drawing of the rolling bearing which concerns on embodiment of this invention, (B) is the elements on larger scale. It is a side view of the clearance gap formation piece of the rolling bearing. It is sectional drawing of the main axis | shaft apparatus of a vertical main axis | shaft. (A) is a side view of the gap forming piece of the rolling bearing that supports the upper part of the spindle of the spindle device, and (B) is a side view of the gap forming piece of the rolling bearing that supports the lower part. It is sectional drawing of the main axis | shaft apparatus of a horizontal type main axis | shaft. (A), (B), (C) is a side view of a gap forming piece of a rolling bearing suitable for supporting the main shaft of the main shaft device. It is sectional drawing of the conventional rolling bearing with a lubrication mechanism. It is explanatory drawing which shows the bias | inclination of the lubricating oil in a clearance gap formation piece.

符号の説明Explanation of symbols

１　内輪
１ａ　軌道面
２　外輪（固定側軌道輪）
２ａ　軌道面
２ｂ　段差面
３　転動体
６　グリース溜まり形成部品
７　隙間形成片
９　グリース溜まり
１０　外輪位置決め
１１　グリース溜まり形成部品本体
１４　流路
１５　隙間
１６　円弧状片
１７　潤滑油吐出部
３０Ａ，３０Ｂ　転がり軸受
３１　主軸 1 Inner ring 1a Raceway surface 2 Outer ring (fixed side raceway)
2a Raceway surface 2b Stepped surface 3 Rolling element 6 Grease pool forming part 7 Gap forming piece 9 Grease pool 10 Outer ring positioning 11 Grease pool forming part main body 14 Channel 15 Clearance 16 Arc-shaped piece 17 Lubricating

oil discharge parts

30A, 30B Rolling bearing 31 Spindle

　この発明の実施形態を図１および図２と共に説明する。図１において、この転がり軸受は、内輪１、外輪２、および内外輪１，２の軌道面１ａ，２ａ間に介在する複数の転動体３を有し、グリース溜まり形成部品６と、隙間形成片７とを備える。複数の転動体３は、保持器４に保持され、内外輪１，２間の軸受空間の一端は、シール５によって密封されている。軸受空間に封入したグリースの外部への漏れをシール５によって防止する。この転がり軸受はアンギュラ玉軸受であり、シール５は軸受背面側の端部に設けられ、グリース溜まり形成部品６および隙間形成片７は軸受正面側に設けられる。軸受正面側ではグリース溜まり形成部品６がシールを兼ねており、軸受正面側からのグリースの漏れが防止される。図において、交差したハッチングで示す部分は、グリースの充填された部分を示す。 An embodiment of the present invention will be described with reference to FIGS. In FIG. 1, this rolling bearing has a plurality of rolling elements 3 interposed between

raceways

1a and 2a of an inner ring 1, an outer ring 2, and inner and

outer rings

1 and 2, and a grease pool forming component 6 and a gap forming piece. 7. The plurality of rolling elements 3 are held by a cage 4, and one end of the bearing space between the inner and

outer rings

1 and 2 is sealed with a seal 5. The seal 5 prevents leakage of grease sealed in the bearing space to the outside. This rolling bearing is an angular ball bearing, the seal 5 is provided at the end on the back side of the bearing, and the grease reservoir forming component 6 and the gap forming piece 7 are provided on the front side of the bearing. The grease reservoir forming component 6 also serves as a seal on the front side of the bearing, so that leakage of grease from the front side of the bearing is prevented. In the figure, the portion indicated by crossed hatching indicates a portion filled with grease.

　固定側軌道輪となる外輪２には、その軌道面２ａに続く段差面２ｂが、転動体３から離れる外輪正面側、つまり軌道面２ａにおける接触角が生じる方向と反対側の縁部に続いて設けられている。この段差面２ｂは、軌道面２ａから外径側に延びて外輪正面側に対面する面であり、外輪２の正面側の内径面部分２ｃに続いている。 On the outer ring 2 serving as a fixed-side raceway, a step surface 2b following the raceway surface 2a follows the outer ring front side away from the rolling elements 3, that is, the edge on the opposite side to the direction in which the contact angle occurs on the raceway surface 2a. Is provided. The step surface 2 b extends from the raceway surface 2 a to the outer diameter side and faces the outer ring front side, and continues to the inner diameter surface portion 2 c on the front side of the outer ring 2.

　グリース溜まり形成部品６は、内部にグリース溜まり９を形成したリング状の部品であり、外輪２の正面側の幅面に接して設けられる。この例では、グリース溜まり形成部品６は、外輪２の正面側の幅面に接して設けられる外輪位置決め間座１０と、この外輪位置決め間座１０の内径面に嵌合する外向き溝形のグリース溜まり形成部品本体１１とからなる。外輪位置決め間座１０とグリース溜まり形成部品本体１１とで挟まれる内部空間がグリース溜まり９とされる。外輪位置決め間座１０は、内径面における外輪２と反対側端に、グリース溜まり形成部品本体１１の側壁部１１ａが当接する側壁部１０ａを有している。グリース溜まり形成部品本体１１は、グリース溜まり９にグリースを封入した後に上記側壁部１１ａを外輪位置決め間座１０の側壁部１０ａの内側に当接させることにより、外輪位置決め間座１０に対して軸方向に位置決めされる。 The grease reservoir forming component 6 is a ring-shaped component having a grease reservoir 9 formed therein, and is provided in contact with the front side width surface of the outer ring 2. In this example, the grease reservoir forming component 6 includes an outer ring positioning spacer 10 provided in contact with the front-side width surface of the outer ring 2 and an outward groove-shaped grease reservoir fitted to the inner diameter surface of the outer ring positioning spacer 10. It consists of a molded part body 11. An internal space sandwiched between the outer ring positioning spacer 10 and the grease reservoir forming component main body 11 is a grease reservoir 9. The outer ring positioning spacer 10 has a side wall portion 10a with which the side wall portion 11a of the grease reservoir forming component main body 11 abuts at the end opposite to the outer ring 2 on the inner diameter surface. The grease reservoir forming component main body 11 is axially oriented with respect to the outer ring positioning spacer 10 by bringing the side wall portion 11a into contact with the inside of the side wall portion 10a of the outer ring positioning spacer 10 after the grease is filled in the grease reservoir 9. Is positioned.

　グリース溜まり形成部品本体１１における上記側壁部１１ａの外径面とこれに対向する外輪位置決め間座１０の内径面との間には、図示しない密封材が介在させられ、またはグリース溜まり形成部品本体１１と外輪位置決め間座１０とは、接着剤により接着される。外輪位置決め間座１０と外輪２との合わせ面には、密封材２１が介在させてある。密封材２１はＯリングからなり、外輪位置決め間座１０の上記合わせ面に形成された円周溝２２内に嵌め込んである。これらにより、グリース漏れ防止が図られている。 A sealant (not shown) is interposed between the outer diameter surface of the side wall portion 11a of the grease pool forming component main body 11 and the inner diameter surface of the outer ring positioning spacer 10 opposed thereto, or the grease pool forming component main body 11 The outer ring positioning spacer 10 is bonded with an adhesive. A sealing material 21 is interposed between the mating surfaces of the outer ring positioning spacer 10 and the outer ring 2. The sealing material 21 is formed of an O-ring and is fitted in a circumferential groove 22 formed on the mating surface of the outer ring positioning spacer 10. As a result, grease leakage is prevented.

　隙間形成片７は、外輪２の内径面部分２ｃに沿って配置され、先端が前記段差面２ｂに対向し、外輪２との間に流路１４および隙間１５を形成するリング状の部材である。この隙間形成片７は、グリース溜まり形成部品本体１１に一体に形成されている。すなわち、グリース溜まり形成部品本体１１の軸受隣接側の側壁部１１ｂにおける外径端部から一体に延びている。 The gap forming piece 7 is a ring-shaped member that is disposed along the inner diameter surface portion 2 c of the outer ring 2, has a tip opposed to the step surface 2 b, and forms a flow path 14 and a gap 15 between the outer ring 2. . The gap forming piece 7 is formed integrally with the grease reservoir forming component main body 11. In other words, the grease reservoir forming component main body 11 extends integrally from the outer diameter end portion of the side wall portion 11b on the bearing adjacent side.

　図１（Ｂ）の部分拡大図に示すように、隙間形成片先端部７ａの周壁と、これに対向する外輪２の内径面部分２ｃとで上記流路１４が形成される。隙間形成片７は、その先端部７ａが外輪２の段差面２ｂに近接した位置まで延びており、隙間形成片先端部７ａの端面と、これに対面する外輪段差面２ｂとで軸方向に微小な隙間量δとなる前記隙間１５が形成される。隙間１５は、前記流路１４に連通し、軌道面２ａの端部に開口する。隙間１５の隙間量δは、毛細管現象を作用させることができる５０～１００μｍとされている。 As shown in the partial enlarged view of FIG. 1B, the flow path 14 is formed by the peripheral wall of the tip 7a of the gap forming piece and the inner diameter surface portion 2c of the outer ring 2 facing this. The gap forming piece 7 has a tip portion 7a extending to a position close to the step surface 2b of the outer ring 2, and the gap forming piece tip portion 7a and the outer ring step surface 2b facing the gap surface are minute in the axial direction. The gap 15 is formed with a small gap amount δ. The gap 15 communicates with the flow path 14 and opens at the end of the track surface 2a. The gap amount δ of the gap 15 is set to 50 to 100 μm that can cause a capillary action.

　さらに、前記隙間形成片先端部７ａの端面には、この端面と外輪２の段差面２ｂとの間の隙間１５の円周方向の一部を塞ぐ円弧状片１６が設けられている。各円弧状片１６間の箇所が潤滑油吐出部１７となる。図２に示すように、この例では、円弧状片１６は円周方向に等配で４箇所に設けられている。図において、ハッチングで示す部分が、円弧状片１６の存在する箇所である。以下の隙間形成片７を示す図（図４、図６）についても同様である。各円弧状片１６の円周上の範囲を示す位相αの最適値は、転がり軸受が使用される箇所によって異なる。円弧状片１６は必ずしも等配で設ける必要はなく、円周上に偏って設けてもよい。また、図１に示すように、この例では、円弧状片１６の先端を段差面２ｂに当接させているが、必ずしも当接させる必要はない。 Furthermore, an arc-shaped piece 16 is provided at the end face of the gap forming piece tip 7a to block a part of the gap 15 between the end face and the stepped surface 2b of the outer ring 2 in the circumferential direction. A location between the arc-shaped pieces 16 becomes the lubricating oil discharge portion 17. As shown in FIG. 2, in this example, the arc-shaped pieces 16 are provided at four locations equally in the circumferential direction. In the figure, hatched portions are portions where the arc-shaped pieces 16 are present. The same applies to the drawings (FIGS. 4 and 6) showing the gap forming pieces 7 below. The optimum value of the phase α indicating the range on the circumference of each arc-shaped piece 16 varies depending on the location where the rolling bearing is used. The arc-shaped pieces 16 do not necessarily have to be provided at equal intervals, and may be provided in a deviated manner on the circumference. Further, as shown in FIG. 1, in this example, the tip of the arcuate piece 16 is brought into contact with the step surface 2b, but it is not always necessary to make contact.

　隙間形成片先端部７ａの端面に続く内径面は、転動体３に近接したテーパ面７ａａとされ、このテーパ面７ａａと転動体３との間に潤滑油が溜まり易くなるようにしている。テーパ面７ａａと転動体３との距離ｄは、テーパ面７ａａに付着した油が転動体３の表面に転移可能な大きさの極小隙間とすることが好ましく、０．２ｍｍ以下としてある。隙間形成片７の基部７ｂは、先端部７ａに比べ小径とされる。この基部７ｂの外径面と外輪２の内径面部分２ｃとで囲まれる部分はグリース溜まり９の一部となっており、このグリース溜まり９に前記流路１４が連通している。 The inner diameter surface following the end face of the gap forming piece tip 7 a is a tapered surface 7 aa close to the rolling element 3, so that the lubricating oil can easily accumulate between the tapered surface 7 aa and the rolling element 3. The distance d between the taper surface 7aa and the rolling element 3 is preferably a minimal gap of 0.2 mm or less with a size that allows oil attached to the taper surface 7aa to transfer to the surface of the rolling element 3. The base 7b of the gap forming piece 7 has a smaller diameter than the tip 7a. A portion surrounded by the outer diameter surface of the base portion 7 b and the inner diameter surface portion 2 c of the outer ring 2 is a part of the grease reservoir 9, and the flow path 14 communicates with the grease reservoir 9.

　上記構成の作用を説明する。軸受組立時に、グリース溜まり９および流路１４にグリースを充填しておく。また、軸受内へは初期潤滑用としてグリースを封入しておく。軸受の停止時には、グリース中の増稠剤および隙間１５の毛細管現象により、グリースの基油が流路１４から隙間１５へ移動し、毛細管現象と油の表面張力とが相まって隙間１５に基油が油状で保持されている。軸受を運転すると、隙間１５に貯油されていた基油は、運転で生じる外輪２の温度変化と、転動体３の公転・自転で生じる空気流とにより隙間１５から吐出されて、外輪２の軌道面２ａに付着しながら移動して転動体接触部に連続的に補給される。これにより、軸受内に封入したグリースと軸受に設けたグリース溜まり９に封入したグリースとを使用して高速化と長寿命化、メンテナンスフリーを達成できる。 The operation of the above configuration will be described. When the bearing is assembled, the grease reservoir 9 and the flow path 14 are filled with grease. In addition, grease is sealed in the bearing for initial lubrication. When the bearing is stopped, the base oil of the grease moves from the flow path 14 to the gap 15 due to the thickener in the grease and the capillary phenomenon of the gap 15, and the base oil flows into the gap 15 due to the capillary phenomenon and the surface tension of the oil. Retained in oil. When the bearing is operated, the base oil stored in the clearance 15 is discharged from the clearance 15 due to the temperature change of the outer ring 2 generated by the operation and the air flow generated by the revolution and rotation of the rolling element 3, and the track of the outer ring 2. It moves while adhering to the surface 2a and is continuously supplied to the rolling element contact portion. As a result, using the grease sealed in the bearing and the grease sealed in the grease reservoir 9 provided in the bearing, speeding up, long life, and maintenance-free can be achieved.

　円弧状片１６の軸方向長さを目標とする隙間量δの寸法に設定しておけば、円弧状片１６の先端が外輪２の段差面２ｂに当接するように隙間形成片７を外輪２に組み付けることにより、目標とする隙間量δの隙間１５が容易に得られる。また、円弧状片１６の円周方向範囲を変えることで、隙間１５の潤滑油吐出部１７の断面積を変えることができ、隙間１５から吐出される潤滑油の量を調整できる。そのため、軸受空間の潤滑油が過剰となり、運転中の攪拌抵抗が大きくなることを防げる。 If the axial length of the arc-shaped piece 16 is set to the target dimension of the gap amount δ, the gap-forming piece 7 is moved to the outer ring 2 so that the tip of the arc-shaped piece 16 contacts the stepped surface 2b of the outer ring 2. As a result, the gap 15 having the target gap amount δ can be easily obtained. Further, by changing the circumferential range of the arcuate piece 16, the cross-sectional area of the lubricating oil discharge portion 17 in the gap 15 can be changed, and the amount of lubricating oil discharged from the gap 15 can be adjusted. For this reason, it is possible to prevent the lubricating oil in the bearing space from becoming excessive and increase the stirring resistance during operation.

　隙間形成片先端部７ａの端面に続く内径面を転動体３に近接したテーパ面７ａａとしたため、次の利点が得られる。すなわち、テーパ面７ａａと転動体３との距離ｄが大きい場合、隙間１５から吐出したグリース基油は、軸受潤滑油として使用されずに、グリース溜まり形成部品本体１１の外径面に付着しながら流出してしまうことがある。前記距離ｄが極小隙間（０．２ｍｍ以下）である場合は、グリース溜まり形成部品本体１１の外径面に付着しながら流出してしまう油を、上記極小隙間の箇所で転動体３の表面に付着させ、潤滑油として有効利用することができる。 Since the inner diameter surface following the end surface of the gap forming piece tip portion 7a is the tapered surface 7aa close to the rolling element 3, the following advantages are obtained. That is, when the distance d between the tapered surface 7aa and the rolling element 3 is large, the grease base oil discharged from the gap 15 is not used as a bearing lubricating oil, but adheres to the outer diameter surface of the grease reservoir forming component body 11. May leak. When the distance d is a minimum gap (0.2 mm or less), oil that flows out while adhering to the outer diameter surface of the grease reservoir forming component body 11 is applied to the surface of the rolling element 3 at the location of the minimum gap. It can be attached and used effectively as a lubricating oil.

　この実施形態では、固定側軌道輪が外輪２であり、この外輪２に前記段差面２ｂが設けられるが、グリース封入状態で軸受を回転させたときに、封入グリースが遠心力で外輪内径部に飛散するため、前記隙間１５と軌道面２ａとの間の基油の繋がりが確実となる。そのため、転動体接触部で潤滑油として消費される分の基油が、グリース溜まり９から隙間１５を経て軌道面２ａに補給される作用が高められ、より安定した潤滑油の補給が行われる。 In this embodiment, the fixed-side raceway is the outer ring 2, and the stepped surface 2b is provided on the outer ring 2, but when the bearing is rotated in a grease-filled state, the sealed grease is applied to the inner diameter of the outer ring by centrifugal force. Because of the scattering, the base oil is reliably connected between the gap 15 and the raceway surface 2a. As a result, the base oil that is consumed as the lubricating oil in the rolling element contact portion is replenished to the raceway surface 2a from the grease reservoir 9 through the gap 15, and the lubricating oil is more stably replenished.

　また、この実施形態では、転がり軸受がアンギュラ玉軸受であり、前記段差面２ｂが、軌道面２ａにおける接触角が生じる方向とは反対側の縁部に続いて形成されているので、段差面２ｂをより転動体３の直下に配置し易くなる。これにより、転動体３の中心付近に段差面２ｂを近づけることができ、隙間１５から軌道面２ａへの潤滑油の補給がより効率良く行える。 In this embodiment, the rolling bearing is an angular ball bearing, and the stepped surface 2b is formed following the edge on the side opposite to the direction in which the contact angle occurs on the raceway surface 2a. Can be more easily disposed immediately below the rolling elements 3. Thereby, the step surface 2b can be brought close to the center of the rolling element 3, and the lubricating oil can be replenished from the gap 15 to the raceway surface 2a more efficiently.

　図３は、上記実施形態の転がり軸受を用いた工作機械用主軸装置の例を示す。この主軸装置は、主軸３１が縦型タイプであり、ハウジング３２内で主軸３１の下部と上部を２個の転がり軸受３０Ａ，３０Ｂで回転自在に支持している。２個の転がり軸受３０Ａ，３０Ｂは、背面組合せで用いられている。各転がり軸受３０Ａ，３０Ｂの内輪１は、内輪位置決め間座３６および内輪間座３７により位置決めされ、内輪固定ナット３９により主軸３１に締め付け固定されている。外輪２は、外輪位置決め間座６、外輪間座４０および外輪押え蓋４１，４２によりハウジング３２内に位置決め固定されている。ハウジング３２は、ハウジング内筒３２Ａとハウジング外筒３２Ｂとを嵌合させたものであり、その嵌合部に冷却のための通油溝４３が設けられている。 FIG. 3 shows an example of a spindle device for a machine tool using the rolling bearing of the above embodiment. In this spindle apparatus, the spindle 31 is of a vertical type, and a lower part and an upper part of the spindle 31 are rotatably supported in a housing 32 by two rolling

bearings

30A and 30B. The two rolling

bearings

30A and 30B are used in combination with the back surface. The inner ring 1 of each of the rolling

bearings

30A and 30B is positioned by an inner ring positioning spacer 36 and an inner ring spacer 37, and is fastened and fixed to the main shaft 31 by an inner ring fixing nut 39. The outer ring 2 is positioned and fixed in the housing 32 by an outer ring positioning spacer 6, an outer ring spacer 40, and outer

ring pressing lids

41 and 42. The housing 32 is formed by fitting a housing inner cylinder 32A and a housing outer cylinder 32B, and an oil passage groove 43 for cooling is provided in the fitting portion.

　主軸３１は、その下端部３１ａに工具またはワーク（図示せず）を着脱自在に取付けるチャック（図示せず）が設けられ、上端部３１ｂは、モータ等の駆動源が回転伝達機構（図示せず）を介して連結される。モータは、ハウジング３２に内蔵してもよい。この主軸装置は、例えばマニシングモータ、旋盤、フライス盤、研削盤等の各種工作機械に適用できる。 The spindle 31 is provided with a chuck (not shown) for detachably attaching a tool or a workpiece (not shown) to the lower end 31a, and the upper end 31b is driven by a rotation transmission mechanism (not shown) such as a motor. ). The motor may be built in the housing 32. This spindle device can be applied to various machine tools such as a machining motor, a lathe, a milling machine, and a grinding machine.

　主軸３１の上部と下部を同じ転がり軸受で支持した場合、両軸受３０Ａ，３０Ｂの軸方向の外側、つまり主軸３１の上部を支持する転がり軸受３０Ａの上側、および下部を支持する転がり軸受３０Ｂの下側に、それぞれ隙間形成片７を設けているから、重力の影響により、下部の転がり軸受３０Ｂよりも上部の転がり軸受３０Ａの方が隙間１５から吐出される潤滑油の量が多くなる。そこで、図４に示すように、主軸３１の上部を支持する転がり軸受３０Ａの隙間形成片７（同図（Ａ））は、主軸３１の下部を支持する転がり軸受３０Ｂの隙間形成片７（同図（Ｂ））に比べて、各円弧状片１６の円周方向範囲を広くしてある。つまり、隙間１５の潤滑油吐出部１７の面積が狭いということである。これにより、両転がり軸受３０Ａ，３０Ｂにおいて、隙間１５から吐出される潤滑油の量を同程度にすることができる。 When the upper and lower parts of the main shaft 31 are supported by the same rolling bearing, the outer sides of both

bearings

30A and 30B, that is, the upper side of the rolling bearing 30A that supports the upper part of the main shaft 31 and the lower side of the rolling bearing 30B that supports the lower part. Since the gap forming pieces 7 are provided on the respective sides, the amount of lubricating oil discharged from the gap 15 is larger in the upper rolling bearing 30A than in the lower rolling bearing 30B due to the influence of gravity. Therefore, as shown in FIG. 4, the gap forming piece 7 of the rolling bearing 30 </ b> A that supports the upper part of the main shaft 31 (FIG. 4A) is the gap forming piece 7 of the rolling bearing 30 </ b> B that supports the lower part of the main shaft 31. Compared to the figure (B)), the circumferential range of each arc-shaped piece 16 is widened. That is, the area of the lubricating oil discharge part 17 in the gap 15 is narrow. Thereby, in both rolling bearing 30A, 30B, the quantity of the lubricating oil discharged from the clearance gap 15 can be made comparable.

　図５は、上記実施形態の転がり軸受を用いた工作機械用主軸装置の異なる例を示す。この主軸装置は、主軸３１が横型タイプであり、ハウジング３２内で主軸３１の両端を２個の転がり軸受３０Ａ，３０Ｂで回転自在に支持している。構造自体は図３の縦型タイプと全く同じである。 FIG. 5 shows a different example of a spindle device for a machine tool using the rolling bearing of the above embodiment. In this spindle apparatus, the spindle 31 is a horizontal type, and both ends of the spindle 31 are supported in a housing 32 by two rolling

bearings

30A and 30B so as to be rotatable. The structure itself is exactly the same as the vertical type in FIG.

　このような横型主軸３１の主軸装置では、図８のように、重力Ｆの影響により全周の潤滑油が矢印の方向に移動して、各転がり軸受３０Ａ，３０Ｂの隙間１５の下部１８に潤滑油が多量に偏在しやすい。潤滑油が多量に偏在すると、軸受回転時の攪拌抵抗が大きくなる。そこで、図６に示すように、隙間形成片７の先端面において円弧状片１６の設けられていない箇所、すなわち潤滑油吐出部１７を円周の下側半分に位置させ、上側半分を塞ぐことで、上側半分の箇所から吐出される余分な潤滑油が下側に移動して下部に潤滑油の多量の偏在が生じることを解消する。なお、潤滑油吐出部１７が上側半分に位置すると、潤滑油吐出部１７からの潤滑油の吐出が生じ難くなるが、下側半分の潤滑油吐出部１７を位置させることで、潤滑油の円滑な吐出を可能としている。このように、多量の潤滑油が隙間１５の下部に多量に偏在して攪拌抵抗が大きくなることを回避しながら、円滑な潤滑油の供給を可能としている。 In such a main spindle device of the horizontal main spindle 31, as shown in FIG. 8, the lubricating oil on the entire circumference moves in the direction of the arrow due to the influence of gravity F, and lubricates the lower portion 18 of the gap 15 between the rolling

bearings

30A and 30B. A large amount of oil tends to be unevenly distributed. If a large amount of lubricating oil is unevenly distributed, the stirring resistance during rotation of the bearing increases. Therefore, as shown in FIG. 6, a position where the arc-shaped piece 16 is not provided on the tip surface of the gap forming piece 7, that is, the lubricating oil discharge portion 17 is positioned in the lower half of the circumference and the upper half is closed. Thus, it is possible to eliminate the occurrence of a large amount of uneven distribution of the lubricating oil in the lower portion due to the excess lubricating oil discharged from the upper half portion moving downward. If the lubricating oil discharge portion 17 is located in the upper half, it is difficult for the lubricating oil discharge portion 17 to be discharged. However, by positioning the lower half lubricating oil discharge portion 17, the lubricating oil can be smoothly discharged. Discharge is possible. In this way, a smooth supply of lubricating oil is possible while avoiding a large amount of lubricating oil being unevenly distributed in the lower part of the gap 15 and increasing the stirring resistance.

　図６（Ａ）は、円周上の下端の１箇所に潤滑油吐出部１７を設けた例である。これにより、重力方向に多量の潤滑油が偏って吐出することを防ぐ効果が期待できる。
　図６（Ｂ）は、円周上の下部の２箇所に潤滑油吐出部１７を設けた例である。２箇所の潤滑油吐出部１７は、円周の中心Ｏを通る垂線１９を挟んで対称位置にある。潤滑油吐出部１７が１箇所であると、潤滑不良になる可能性がある場合には、このように潤滑油吐出部１７を２箇所に設けるとよい。
　図６（Ｃ）は、円周上の下端の１箇所、および円周上の下部における垂線１９を挟んで対称位置にある２箇所の計３箇所に、潤滑油吐出部１７Ａ，１７Ｂ，１７Ｃを設けた例である。この場合、下端の潤滑油吐出部１７Ａは他の潤滑油吐出部１７Ｂ，１７Ｃよりも重力の影響を受けやすいため、潤滑油吐出部１７Ａの断面積を潤滑油吐出部１７Ｂ，１７Ｃの断面積よりも小さくすることで（αＡ＜αＢ，αＣ）、各潤滑油吐出部１７Ａ，１７Ｂ，１７Ｃからほぼ同量の潤滑油が吐出されるようにするのが好ましい。 FIG. 6A shows an example in which the lubricating oil discharge portion 17 is provided at one place at the lower end on the circumference. Thereby, the effect which prevents that a large amount of lubricating oil discharges biased in the direction of gravity can be expected.
FIG. 6B is an example in which lubricating oil discharge portions 17 are provided at two locations on the lower circumference. The two lubricating oil discharge portions 17 are in symmetrical positions across a perpendicular line 19 passing through the center O of the circumference. If there is a possibility of poor lubrication when the lubricating oil discharge part 17 is at one place, the lubricating oil discharge part 17 may be provided at two places in this way.
FIG. 6 (C) shows that the lubricating

oil discharge portions

17A, 17B, and 17C are placed at a total of three locations, one at the lower end on the circumference and two at the symmetrical position across the vertical line 19 at the lower portion on the circumference. This is an example. In this case, the lower-lubricating oil discharge portion 17A is more susceptible to gravity than the other lubricating

oil discharge portions

17B and 17C, so the cross-sectional area of the lubricating oil discharge portion 17A is larger than the cross-sectional area of the lubricating

oil discharge portions

17B and 17C. Also, it is preferable that the same amount of lubricating oil is discharged from each of the lubricating

oil discharge portions

17A, 17B, and 17C by making it smaller (αA <αB, αC).

　上記各構成の主軸装置によると、転がり軸受３０Ａ，３０Ｂの隙間１５から吐出される潤滑油の量を適正に調整することで、転がり軸受３０Ａ，３０Ｂにおける高速化、長寿命化、メンテナンスフリー化の作用が効果的に発揮される。 According to the spindle device of each of the above configurations, by appropriately adjusting the amount of lubricating oil discharged from the gap 15 between the rolling

bearings

30A and 30B, the rolling

bearings

30A and 30B can be increased in speed, extended life and maintenance-free. The effect is exhibited effectively.

　以上のとおり、図面を参照しながら好適な実施例を説明したが、当業者であれば、本件明細書を見て、自明な範囲内で種々の変更および修正を容易に想定するであろう。
　したがって、そのような変更および修正は、請求の範囲から定まる発明の範囲内のものと解釈される。 As described above, the preferred embodiments have been described with reference to the drawings. However, those skilled in the art will readily understand various changes and modifications within the obvious scope by looking at the present specification.
Accordingly, such changes and modifications are to be construed as within the scope of the invention as defined by the appended claims.

Claims

　内輪、外輪、およびこれら内外輪の軌道面間に介在する複数の転動体を有する転がり軸受において、軌道輪である内輪および外輪のうち、回転しない固定側軌道輪に、軌道面に続く段差面を転動体から離れる方向に設け、先端面が前記段差面に隙間を介して対面し周壁で前記固定側軌道輪との間に流路を形成する環状の隙間形成片を設け、前記流路に連通するグリース溜まりを設け、前記隙間形成片の先端面に、この先端面と前記段差面との間の前記隙間の円周方向の一部を塞ぐ円弧状片を設けた転がり軸受。 In a rolling bearing having an inner ring, an outer ring, and a plurality of rolling elements interposed between the raceways of the inner and outer rings, a stepped surface following the raceway is provided on the stationary raceway that does not rotate among the inner ring and the outer ring that are raceways. An annular gap forming piece is provided in a direction away from the rolling element, the tip surface faces the stepped surface through a gap, and a flow path is formed between the peripheral wall and the fixed-side raceway, and communicates with the flow path. A rolling bearing in which a grease reservoir is provided, and an arc-shaped piece that closes a part of the gap between the tip surface and the step surface in the circumferential direction is provided on the tip surface of the gap forming piece.
　請求項１において、前記円弧状片を、前記隙間形成片の先端面の円周方向複数箇所に設けて、前記隙間の隣合う円弧状片間に位置して前記円弧状片によって塞がれていない箇所である潤滑油吐出部を円周方向の複数箇所に形成した転がり軸受。 2. The arcuate piece according to claim 1, wherein the arcuate piece is provided at a plurality of locations in the circumferential direction of the tip surface of the gap forming piece, and is located between the arcuate pieces adjacent to the gap and is blocked by the arcuate piece. A rolling bearing in which lubricating oil discharge parts, which are not present, are formed at a plurality of locations in the circumferential direction.
　請求項１において、前記隙間形成片の先端面のうち、円弧状片が設けられている円周方向範囲の方が、円弧状片が設けられていない円周方向範囲よりも広い転がり軸受。 2. The rolling bearing according to claim 1, wherein, in the front end surface of the gap forming piece, a circumferential range in which the arc-shaped piece is provided is wider than a circumferential range in which the arc-shaped piece is not provided.
　請求項１において、前記固定側軌道輪が外輪である転がり軸受。 The rolling bearing according to claim 1, wherein the fixed-side race is an outer ring.
　請求項１において、横型主軸の支持に使用され、前記隙間のうちの前記潤滑油吐出部が円周の下側半分に位置する転がり軸受。 2. The rolling bearing according to claim 1, which is used for supporting a horizontal main shaft and in which the lubricating oil discharge portion in the gap is located in the lower half of the circumference.
　請求項５において、前記潤滑油吐出部を、転がり軸受の中心と通る垂線上に１箇所だけ形成した転がり軸受。 6. The rolling bearing according to claim 5, wherein the lubricating oil discharge portion is formed only at one place on a perpendicular passing through the center of the rolling bearing.
　請求項５において、前記潤滑油吐出部を、転がり軸受の中心と通る垂線を挟んで対称となる２箇所に形成した転がり軸受。 6. The rolling bearing according to claim 5, wherein the lubricating oil discharge portion is formed in two symmetrical positions with a perpendicular passing through the center of the rolling bearing.
　請求項５において、前記潤滑油吐出部を、転がり軸受の中心と通る垂線上の１箇所、および前記垂線を挟んで対称となる２箇所の計３箇所に形成し、前記垂線上の１箇所に位置する潤滑油吐出部の断面積を、垂線を挟んで対称となる２箇所にそれぞれ位置する潤滑油吐出部の断面積よりも狭くした転がり軸受。 In Claim 5, the said lubricating oil discharge part is formed in a total of three places of one place on the perpendicular which passes along the center of a rolling bearing, and two places which become symmetrical across the said perpendicular, and one place on the said perpendicular A rolling bearing in which the cross-sectional area of the lubricating oil discharge portion is narrower than the cross-sectional area of the lubricating oil discharge portion positioned at two locations that are symmetrical with respect to the vertical line.
　請求項１に記載の転がり軸受を用いて縦型主軸を支持した主軸装置であって、
　一対の転がり軸受を有し、主軸の上部を支持する転がり軸受の上側、および下部を支持する転がり軸受の下側にそれぞれ前記隙間形成片を設け、
　前記主軸の上部を支持する転がり軸受は、下部を支持する転がり軸受よりも、前記隙間形成片の先端面における前記円弧状片の設けられている円周方向範囲が広い主軸装置。 A spindle device that supports a vertical spindle using the rolling bearing according to claim 1,
A pair of rolling bearings are provided, and the gap forming pieces are respectively provided on the upper side of the rolling bearing that supports the upper part of the main shaft and on the lower side of the rolling bearing that supports the lower part,
The rolling bearing that supports the upper part of the main shaft has a wider circumferential range in which the arc-shaped piece is provided on the tip surface of the gap forming piece than the rolling bearing that supports the lower part.