JP5944198B2

JP5944198B2 - Rolling bearing device

Info

Publication number: JP5944198B2
Application number: JP2012078607A
Authority: JP
Inventors: 水谷　守; 守水谷; 裕士恩田; 健治玉田
Original assignee: NTN Corp
Current assignee: NTN Corp
Priority date: 2012-03-30
Filing date: 2012-03-30
Publication date: 2016-07-05
Anticipated expiration: 2032-03-30
Also published as: JP2013209996A

Description

この発明は、例えば、工作機械主軸を回転自在に支持する転がり軸受装置に関し、軸受冷却媒体を兼ねる潤滑油を軸受内に供給すると共に、軸受外に排出する給排油機構とを備えた転がり軸受装置に関する。 The present invention relates to a rolling bearing device that rotatably supports a machine tool main shaft, for example, and relates to a rolling bearing provided with a supply / discharge oil mechanism that supplies lubricating oil also serving as a bearing cooling medium into the bearing and discharges it outside the bearing. Relates to the device.

軸受の冷却と、軸受に対する潤滑油の給排油を行う機構を有する潤滑装置が提案されている（特許文献１）。この潤滑装置では、図１５に示すように、内輪端面に接する内輪間座５０を設け、外輪端面に接する潤滑油導入部材５１を設けている。内輪５２のうち前記内輪端面から内輪軌道面に繋がる斜面に円周溝５３を設けると共に、前記潤滑油導入部材５１にノズル５４を設け、このノズル５４から前記円周溝５３内に軸受冷却媒体を兼ねる潤滑油を吐出するようになっている。 There has been proposed a lubricating device having a mechanism for cooling a bearing and supplying and discharging lubricating oil to and from the bearing (Patent Document 1). In this lubricating device, as shown in FIG. 15, an inner ring spacer 50 is provided in contact with the inner ring end face, and a lubricating oil introduction member 51 is provided in contact with the outer ring end face. A circumferential groove 53 is provided on the slope of the inner ring 52 from the inner ring end face to the inner ring raceway surface, a nozzle 54 is provided in the lubricating oil introduction member 51, and a bearing cooling medium is provided from the nozzle 54 into the circumferential groove 53. It is designed to discharge lubricating oil.

特開２００８−２４０９４６号公報JP 2008-240946 A

図１５の構造では、軸受内へ多量の潤滑油が浸入し軸受内で潤滑油が滞留すると、攪拌抵抗が増加し、軸受の温度が上昇して、高速回転が不可能となる場合がある。 In the structure of FIG. 15, when a large amount of lubricating oil enters the bearing and the lubricating oil stays in the bearing, the stirring resistance increases, the temperature of the bearing rises, and high-speed rotation may be impossible.

ここで本件出願人は、図１６に示す転がり軸受装置を提案している。同図に示すように、内輪１には、軸方向に延びる内輪延長部６を設け、外輪２に隣接し且つ内周面が内輪延長部６に対向する間座７を設けている。この場合、軸受運転時、以下の(1)〜(5)のように潤滑油が軸受内部に浸入する。同図における矢符は潤滑油の流れを示す。
(1) 潤滑油を給油路９から供給する。
(2) 潤滑油が内輪円周溝８に当たる。
(3) 潤滑油は、回転中の内輪１から遠心力を受けて、間座７の内周面７ａに当たる。
(4) 潤滑油は、内輪延長部６の外周面と、間座７の内周面との径方向すきまから軸受内に浸入する。このとき転がり軸受装置を例えば立軸の支持に用いる場合には、内周面７ａに当たった潤滑油が、排油口に向かうまでの経路途中で重力等の作用により、排油口であまり排出されずに軸受内に多量に浸入する場合がある。
(5) このように潤滑油が多量に浸入すると、軸受内に潤滑油が滞留する。この滞留した潤滑油が軸受の発熱の原因となり、高速運転が不可能となる。 Here, the present applicant has proposed a rolling bearing device shown in FIG. As shown in the figure, the inner ring 1 is provided with an inner ring extension portion 6 that extends in the axial direction, and a spacer 7 that is adjacent to the outer ring 2 and whose inner peripheral surface faces the inner ring extension portion 6. In this case, during the operation of the bearing, the lubricating oil enters the bearing as shown in (1) to (5) below. The arrows in the figure indicate the flow of the lubricating oil.
(1) Supply lubricating oil from the oil supply passage 9.
(2) The lubricating oil hits the inner ring circumferential groove 8.
(3) The lubricating oil receives centrifugal force from the rotating inner ring 1 and hits the inner peripheral surface 7 a of the spacer 7.
(4) Lubricating oil enters the bearing from the radial clearance between the outer peripheral surface of the inner ring extension 6 and the inner peripheral surface of the spacer 7. At this time, when the rolling bearing device is used for supporting the vertical shaft, for example, the lubricating oil hitting the inner peripheral surface 7a is discharged too much at the oil discharge port due to the action of gravity or the like in the course of going to the oil discharge port. In some cases, a large amount may enter the bearing.
(5) When a large amount of lubricating oil enters in this way, the lubricating oil stays in the bearing. This accumulated lubricating oil causes heat generation of the bearing, and high speed operation becomes impossible.

この発明の目的は、軸受空間内に浸入する潤滑油の油量を抑制し、潤滑油の攪拌抵抗による軸受の温度上昇を抑制することができる転がり軸受装置を提供することである。 An object of the present invention is to provide a rolling bearing device capable of suppressing the amount of lubricating oil entering the bearing space and suppressing an increase in the temperature of the bearing due to the stirring resistance of the lubricating oil.

この発明の転がり軸受装置は、内外輪の軌道面間に、保持器に保持された複数の転動体を介在させた転がり軸受と、軸受冷却媒体を兼ねる潤滑油を軸受内に供給すると共に、軸受外に排出する給排油機構とを備えた転がり軸受装置において、前記内輪の一端面に隣接し且つ外径が外輪の一端面の径方向幅内に位置する内輪間座を設けると共に、外輪の一端面に隣接し且つ内周面が前記内輪間座の外周面に対向する外輪間座を設け、前記給排油機構は、前記内輪間座の外周面に設けられた円周溝と、前記外輪間座に設けられ、潤滑油を前記円周溝へ向けて吐出する給油口を有する給油路と、前記内輪間座の外周面と外輪間座の内周面とのすきま部に設けられ、円周溝から外輪の一端面に導かれる潤滑油の油量を絞る第一絞り部と、前記外輪の一端面に設けられ、第一絞り部に連通してこの第一絞り部から導かれる潤滑油を収容する環状の油保有溝と、前記外輪の一端面と、この外輪の一端面に臨む内輪間座の一端面との間に設けられ、油保有溝および内外輪の軸受空間にそれぞれ連通して、軸受空間内に浸入する潤滑油の油量を絞る第二絞り部とを有することを特徴とする。 The rolling bearing device according to the present invention supplies a rolling bearing in which a plurality of rolling elements held by a cage are interposed between the raceway surfaces of the inner and outer rings, and lubricating oil also serving as a bearing cooling medium into the bearing. In a rolling bearing device having an oil supply / discharge mechanism for discharging to the outside, an inner ring spacer is provided adjacent to one end face of the inner ring and having an outer diameter within the radial width of one end face of the outer ring. An outer ring spacer is provided that is adjacent to one end surface and has an inner circumferential surface facing the outer circumferential surface of the inner ring spacer, and the oil supply / drainage mechanism includes a circumferential groove provided on the outer circumferential surface of the inner ring spacer, Provided in an outer ring spacer, provided in a gap between an oil supply passage having an oil supply port for discharging lubricating oil toward the circumferential groove, and an outer peripheral surface of the inner ring spacer and an inner peripheral surface of the outer ring spacer; A first throttle for reducing the amount of lubricating oil guided from the circumferential groove to one end surface of the outer ring; An annular oil retaining groove that is provided on the surface and that contains the lubricating oil that communicates with the first throttle portion and that is guided from the first throttle portion, one end surface of the outer ring, and an inner ring spacer facing the one end surface of the outer ring And a second constriction portion that restricts the amount of lubricating oil that enters the bearing space and communicates with the oil retaining groove and the bearing space of the inner and outer rings, respectively. .

この構成によると、軸受運転時、外輪間座の給油路から潤滑油を供給すると、内輪間座の外周面の円周溝に沿って潤滑油が流れる。これにより軸受を冷却する。軸受を冷却した油は、例えば、排出されるものと、軸受潤滑のために第一絞り部を通過して油保有溝に流れるものとに分かれる。この油保有溝に流れる潤滑油の少なくとも一部は、第二絞り部を通過して軸受空間内に浸入する。このように第一および第二絞り部を設けることにより、軸受空間内に浸入する潤滑油の油量を抑制することができる。したがって、潤滑油の攪拌抵抗による軸受の温度上昇を抑制して、軸受の高速回転を可能とすることができる。 According to this configuration, when the lubricating oil is supplied from the oil supply passage of the outer ring spacer during the bearing operation, the lubricating oil flows along the circumferential groove on the outer peripheral surface of the inner ring spacer. This cools the bearing. The oil that has cooled the bearing is divided into, for example, one that is discharged and one that passes through the first throttle portion and flows into the oil retaining groove for bearing lubrication. At least a part of the lubricating oil flowing in the oil retaining groove passes through the second throttle portion and enters the bearing space. By providing the first and second throttle portions in this manner, the amount of lubricating oil that enters the bearing space can be suppressed. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.

前記給排油機構は、外輪の外周面に設けられ、油保有溝に連通して潤滑油を排出する排油口を含むものとしても良い。前記第一絞り部を通過して油保有溝に流れ込んだ潤滑油は、外輪の排油口を通り回収されるものと、前記第二絞り部を通過して軸受空間内に浸入するものとに分かれる。このように外輪の外周面に排油口を設けた場合、外輪の外周面に排油口を設けない構成に比べて、排油効率を上げることができる。
前記外輪の排油口を２箇所以上設けても良い。この場合、排油効率の向上をさらに図ることができる。 The oil supply / drainage mechanism may be provided on an outer peripheral surface of the outer ring, and may include an oil discharge port that communicates with the oil retaining groove and discharges the lubricating oil. Lubricating oil that has flowed into the oil retaining groove after passing through the first throttle part is collected through the oil outlet of the outer ring, and that that passes through the second throttle part and enters the bearing space. Divided. When the oil drain port is provided on the outer peripheral surface of the outer ring in this way, the oil drain efficiency can be increased as compared with a configuration in which the oil drain port is not provided on the outer peripheral surface of the outer ring.
Two or more oil outlets of the outer ring may be provided. In this case, the oil drainage efficiency can be further improved.

前記内輪間座の円周溝は、この内輪間座を軸受軸心を含む平面で切断して見た断面が凹形状に形成されたものであっても良い。この場合、給油路から供給された潤滑油は、断面凹形状の円周溝の溝底面に跳ね返って、内輪回転に伴う遠心力により、第一絞り部などへ向かうようになっている。 The circumferential groove of the inner ring spacer may have a concave cross section when the inner ring spacer is cut along a plane including the bearing axis. In this case, the lubricating oil supplied from the oil supply passage is bounced back to the groove bottom surface of the circumferential groove having a concave cross section, and is directed to the first throttle portion or the like by the centrifugal force accompanying the rotation of the inner ring.

前記給排油機構は、前記外輪間座に設けられる排油口を含み、この排油口は、前記給油口とは異なる円周方向位置で円周溝に連通し、潤滑油を排出するものであっても良い。この場合、内輪間座の円周溝に沿って流れた潤滑油は、外輪間座の排油口から排出されるものと、軸受潤滑のために第一絞り部を通過するものとに分かれる。
前記外輪間座の排油口に、潤滑油の円周溝に沿う流れを規制する障壁を設けても良い。この場合、内輪の回転に伴い円周溝に沿って流れる潤滑油は、障壁に当たり、排油口に回収され易くなる。これにより、潤滑油が軸受内部に滞留することを抑制することができ、したがって、軸受内部の攪拌抵抗の増加を防止し得る。 The oil supply / discharge mechanism includes an oil discharge port provided in the outer ring spacer, and the oil discharge port communicates with a circumferential groove at a circumferential position different from the oil supply port, and discharges lubricating oil. It may be. In this case, the lubricating oil that flows along the circumferential groove of the inner ring spacer is divided into one that is discharged from the oil outlet of the outer ring spacer and one that passes through the first throttle part for bearing lubrication.
You may provide the barrier which regulates the flow along the circumferential groove | channel of lubricating oil in the oil outlet of the said outer ring | wheel spacer. In this case, the lubricating oil flowing along the circumferential groove with the rotation of the inner ring hits the barrier and is easily collected at the oil discharge port. Thereby, it can suppress that lubricating oil retains inside a bearing, Therefore, increase of the stirring resistance inside a bearing can be prevented.

前記障壁を、外輪間座の排油口における周方向長さの中央部に配設したものであっても良い。この場合、軸受が正回転する場合に、円周溝に沿って正回転方向に流れる潤滑油を前記障壁で規制し、排油口に円滑に導くことができる。軸受が逆回転する場合にも、円周溝に沿って逆回転方向に流れる潤滑油を前記障壁で規制し、排油口に円滑に導くことができる。 The barrier may be disposed at the central portion of the circumferential length of the oil outlet of the outer ring spacer. In this case, when the bearing rotates in the forward direction, the lubricating oil flowing in the forward rotation direction along the circumferential groove can be regulated by the barrier and smoothly guided to the oil discharge port. Even when the bearing rotates in the reverse direction, the lubricating oil flowing in the reverse rotation direction along the circumferential groove can be regulated by the barrier and smoothly guided to the oil discharge port.

前記障壁は、内輪間座における円周溝の底面付近まで延びる延在部を含むものとしても良い。この場合、内輪間座の円周溝に沿って流れる潤滑油を、障壁により確実に衝突させることができる。これにより、延在部がない障壁に比べて、排油口から回収される潤滑油の回収効率を高めることができる。
前記障壁は、潤滑油の流れ方向に応じて可動する弁構造であっても良い。この場合、軸受の正回転、逆回転にかからわず、潤滑油の流れ方向に応じて障壁を可動させて、潤滑油を排油口に円滑に導くことができる。 The barrier may include an extending portion extending to the vicinity of the bottom surface of the circumferential groove in the inner ring spacer. In this case, the lubricating oil flowing along the circumferential groove of the inner ring spacer can be reliably collided by the barrier. Thereby, the collection | recovery efficiency of the lubricating oil collect | recovered from an oil discharge port can be improved compared with the barrier without an extension part.
The barrier may be a valve structure that can move according to the flow direction of the lubricating oil. In this case, it is possible to smoothly guide the lubricating oil to the oil discharge port by moving the barrier according to the flow direction of the lubricating oil, regardless of whether the bearing rotates forward or backward.

前記障壁は、排油口における半径方向内方の円周方向一側部から、半径方向外方の開口縁に向かうに従って、前記排油口における周方向長さの中央部に至るように傾斜する傾斜部を含むものであっても良い。この場合、潤滑油が傾斜部に沿って円滑に流れるため、排油口から回収される潤滑油の回収効率の向上を図ることができる。
前記障壁は、排油口にて軸方向に並ぶ２つの壁部を有し、各壁部は、排油口における半径方向内方の円周方向一側部から、前記排油口における半径方向外方の円周方向他側部に至るようにそれぞれ傾斜すると共に、これら軸方向に並ぶ２つの壁部が互いに交差するように設けられるものであっても良い。この場合、軸受の正回転、逆回転にかかわらず、潤滑油がいずれか一方の壁部に沿って円滑に流れるため、排油口から回収される潤滑油の回収効率の向上を図ることができる。
前記第一および第二絞り部の各すきまを、一つの前記転がり軸受における軸受空間内に浸入する潤滑油の油量を抑制するように定めることで潤滑油の撹拌抵抗による軸受の温度上昇を抑制可能としても良い。
前記いずれかの転がり軸受装置は、工作機械主軸の支持に用いられるものであっても良い。 The barrier is inclined so as to reach the central portion of the circumferential length of the oil discharge port from one side in the circumferential direction of the oil discharge port toward the opening edge radially outward. An inclined part may be included. In this case, since the lubricating oil flows smoothly along the inclined portion, it is possible to improve the recovery efficiency of the lubricating oil recovered from the oil discharge port.
The barrier has two wall portions arranged in the axial direction at the oil discharge port, and each wall portion extends radially from one side in the radial direction at the oil discharge port to the radial direction at the oil discharge port. The two wall portions arranged in the axial direction may be provided so as to incline so as to reach the outer circumferential other side portion and to cross each other in the axial direction. In this case, the forward rotation of the bearing, regardless of the reverse rotation, the lubricating oil flows smoothly along the wall of either one, is possible to improve the recovery efficiency of the lubricating oil which is recovered from the oil outlet I can .
Temperature rise of the first and the or-out each to the second throttle portion, one of said bearing by agitation resistance of the lubricating oil by determined so as to suppress the amount of lubricating oil entering into the bearing space in the rolling bearing It is good also as suppression is possible.
Before SL one of the rolling bearing device may be one used for the support of the machine tool spindle.

この発明の転がり軸受装置は、内外輪の軌道面間に、保持器に保持された複数の転動体を介在させた転がり軸受と、軸受冷却媒体を兼ねる潤滑油を軸受内に供給すると共に、軸受外に排出する給排油機構とを備えた転がり軸受装置において、前記内輪の一端面に隣接し且つ外径が外輪の一端面の径方向幅内に位置する内輪間座を設けると共に、外輪の一端面に隣接し且つ内周面が前記内輪間座の外周面に対向する外輪間座を設け、前記給排油機構は、前記内輪間座の外周面に設けられた円周溝と、前記外輪間座に設けられ、潤滑油を前記円周溝へ向けて吐出する給油口を有する給油路と、前記内輪間座の外周面と外輪間座の内周面とのすきま部に設けられ、円周溝から外輪の一端面に導かれる潤滑油の油量を絞る第一絞り部と、前記外輪の一端面に設けられ、第一絞り部に連通してこの第一絞り部から導かれる潤滑油を収容する環状の油保有溝と、前記外輪の一端面と、この外輪の一端面に臨む内輪間座の一端面との間に設けられ、油保有溝および内外輪の軸受空間にそれぞれ連通して、軸受空間内に浸入する潤滑油の油量を絞る第二絞り部とを有する。このため、軸受空間内に浸入する潤滑油の油量を抑制し、潤滑油の攪拌抵抗による軸受の温度上昇を抑制することができる。 The rolling bearing device according to the present invention supplies a rolling bearing in which a plurality of rolling elements held by a cage are interposed between the raceway surfaces of the inner and outer rings, and lubricating oil also serving as a bearing cooling medium into the bearing. In a rolling bearing device having an oil supply / discharge mechanism for discharging to the outside, an inner ring spacer is provided adjacent to one end face of the inner ring and having an outer diameter within the radial width of one end face of the outer ring. An outer ring spacer is provided that is adjacent to one end surface and has an inner circumferential surface facing the outer circumferential surface of the inner ring spacer, and the oil supply / drainage mechanism includes a circumferential groove provided on the outer circumferential surface of the inner ring spacer, Provided in an outer ring spacer, provided in a gap between an oil supply passage having an oil supply port for discharging lubricating oil toward the circumferential groove, and an outer peripheral surface of the inner ring spacer and an inner peripheral surface of the outer ring spacer; A first throttle for reducing the amount of lubricating oil guided from the circumferential groove to one end surface of the outer ring; An annular oil retaining groove that is provided on the surface and that contains the lubricating oil that communicates with the first throttle portion and that is guided from the first throttle portion, one end surface of the outer ring, and an inner ring spacer facing the one end surface of the outer ring And a second constriction portion that communicates with the oil retaining groove and the bearing space of the inner and outer rings, respectively, and restricts the amount of lubricating oil that enters the bearing space. For this reason, it is possible to suppress the amount of lubricating oil that enters the bearing space, and to suppress an increase in the temperature of the bearing due to the stirring resistance of the lubricating oil.

この発明の第１の実施形態に係る転がり軸受装置の断面図である。It is sectional drawing of the rolling bearing apparatus which concerns on 1st Embodiment of this invention. 同転がり軸受装置の要部の断面図である。It is sectional drawing of the principal part of the rolling bearing apparatus. 同転がり軸受装置における外輪の正面図である。It is a front view of the outer ring | wheel in the rolling bearing apparatus. 同転がり軸受装置における図２の要部の拡大図である。It is an enlarged view of the principal part of FIG. 2 in the rolling bearing device. 同転がり軸受装置における潤滑油の流れを示す平面図である。It is a top view which shows the flow of the lubricating oil in the rolling bearing apparatus. （Ａ）は、この発明の他の実施形態に係る転がり軸受装置の要部の平面図、（Ｂ）は同図６（Ａ）のVI(B) - VI(B) 線端面図である。(A) is a top view of the principal part of the rolling bearing apparatus which concerns on other embodiment of this invention, (B) is a VI (B) -VI (B) line end view of the same FIG. 6 (A). この発明のさらに他の実施形態に係る転がり軸受装置の要部の平面図である。It is a top view of the principal part of the rolling bearing apparatus which concerns on further another embodiment of this invention. この発明のさらに他の実施形態に係る転がり軸受装置の要部の平面図である。It is a top view of the principal part of the rolling bearing apparatus which concerns on further another embodiment of this invention. この発明のさらに他の実施形態に係る転がり軸受装置の要部の平面図である。It is a top view of the principal part of the rolling bearing apparatus which concerns on further another embodiment of this invention. （Ａ）は、この発明のさらに他の実施形態に係る転がり軸受装置において、内輪が同図反時計回りに回転するときの状態を表す要部の平面図、（Ｂ）は、同内輪が同図時計回りに回転するときの状態を表す要部の平面図である。(A) is a plan view of a main part showing a state when the inner ring rotates counterclockwise in the same figure in a rolling bearing device according to still another embodiment of the present invention, and (B) shows the same inner ring. It is a top view of the principal part showing a state when rotating clockwise. この発明のさらに他の実施形態に係る転がり軸受装置の外輪間座の斜視図である。It is a perspective view of the outer ring | wheel spacer of the rolling bearing apparatus which concerns on further another embodiment of this invention. 同外輪間座の要部を内径側から拡大して示す斜視図である。It is a perspective view which expands and shows the principal part of the outer ring spacer from the inner diameter side. 同外輪間座の要部の平面図である。It is a top view of the principal part of the outer ring spacer. この発明のいずれかの実施形態に係る転がり軸受装置を、工作機械主軸を支持する転がり軸受に適用した例を示す概略断面図である。It is a schematic sectional drawing which shows the example which applied the rolling bearing apparatus which concerns on either embodiment of this invention to the rolling bearing which supports a machine tool main shaft. 従来例の転がり軸受の潤滑装置の要部の断面図である。It is sectional drawing of the principal part of the lubricating device of the rolling bearing of a prior art example. 潤滑油が軸受内部へ浸入する参考提案例を示す要部の断面図である。It is sectional drawing of the principal part which shows the reference proposal example in which lubricating oil permeates into the inside of a bearing.

この発明の第１の実施形態を図１ないし図５と共に説明する。図１に示すように、この実施形態に係る転がり軸受装置は、転がり軸受Ｂｒと、給排油機構Ｋｕとを備えている。
図２に示すように、転がり軸受Ｂｒは、内外輪１，２である一対の軌道輪と、内外輪１，２の軌道面１ａ，２ａ間に介在する複数の転動体３と、これら転動体３を保持するリング状の保持器４とを有する。この転がり軸受Ｂｒはアンギュラ玉軸受からなり、転動体３として、鋼球やセラミックス球等からなる玉が適用される。 A first embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 1, the rolling bearing device according to this embodiment includes a rolling bearing Br and a supply / discharge oil mechanism Ku.
As shown in FIG. 2, the rolling bearing Br includes a pair of bearing rings that are inner and outer rings 1 and 2, a plurality of rolling elements 3 interposed between the raceway surfaces 1 a and 2 a of the inner and outer rings 1 and 2, and these rolling elements. And a ring-shaped cage 4 that holds 3. The rolling bearing Br is an angular ball bearing, and a ball made of a steel ball, a ceramic ball or the like is applied as the rolling element 3.

内輪１の軌道面１ａの軸方向両側に、内輪外径面１ｂおよびこの内輪外径面１ｂに続く斜面１ｃと、斜面状のカウンタボア１ｄとがそれぞれ形成されている。この例の内輪外径面１ｂは、軌道面１ａに対し接触角を成す作用線Ｌの偏り側から幅方向に延びる。この内輪外径面１ｂの軸方向外縁部に続く斜面１ｃは、軸方向一方（図２の上方）に向かうに従って内径側に至るように傾斜する断面形状に形成されている。外輪２の軌道面２ａの軸方向両側に、外輪内径面２ｂ，２ｂがそれぞれ形成され、これら外輪内径面２ｂ，２ｂに保持器４が案内されるように構成されている。 On both sides in the axial direction of the raceway surface 1a of the inner ring 1, an inner ring outer diameter surface 1b, an inclined surface 1c following the inner ring outer diameter surface 1b, and an inclined counter bore 1d are formed. The inner ring outer diameter surface 1b in this example extends in the width direction from the biased side of the action line L that forms a contact angle with the raceway surface 1a. The slope 1c following the axial outer edge of the inner ring outer diameter surface 1b is formed in a cross-sectional shape that is inclined so as to reach the inner diameter side toward one axial direction (upward in FIG. 2). Outer ring inner diameter surfaces 2b and 2b are respectively formed on both axial sides of the raceway surface 2a of the outer ring 2, and the cage 4 is configured to be guided by these outer ring inner diameter surfaces 2b and 2b.

図１に示すように、給排油機構Ｋｕは、軸受冷却媒体を兼ねる潤滑油を潤滑内(軸受内)に供給すると共に、軸受外に排出する機構である。内輪１の一端面に隣接して内輪間座６を設け、この内輪間座６の外径６ａが、外輪２の一端面の径方向幅内に位置するように構成している。さらに外輪２の一端面に隣接して外輪間座７を設け、この外輪間座７の内周面を、内輪間座６の外周面に対向させている。給排油機構Ｋｕは、内輪間座６の外周面に設けられた円周溝８と、外輪間座７に設けられた給油路９と、外輪間座７に設けられた排油口１０と、第一絞り部１１と、環状の油保有溝１２と、外輪２の排油口１３と、第二絞り部１４とを有する。 As shown in FIG. 1, the supply / discharge oil mechanism Ku is a mechanism that supplies lubricating oil that also serves as a bearing cooling medium into the lubrication (inside the bearing) and discharges it outside the bearing. An inner ring spacer 6 is provided adjacent to one end surface of the inner ring 1, and the outer diameter 6 a of the inner ring spacer 6 is positioned within the radial width of the one end surface of the outer ring 2. Further, an outer ring spacer 7 is provided adjacent to one end surface of the outer ring 2, and the inner peripheral surface of the outer ring spacer 7 is opposed to the outer peripheral surface of the inner ring spacer 6. The oil supply / discharge oil mechanism Ku includes a circumferential groove 8 provided on the outer peripheral surface of the inner ring spacer 6, an oil supply passage 9 provided in the outer ring spacer 7, and an oil discharge port 10 provided in the outer ring spacer 7. The first throttle part 11, the annular oil retaining groove 12, the oil outlet 13 of the outer ring 2, and the second throttle part 14 are provided.

内輪間座６の外周面には、この内輪間座６を軸受軸心を含む平面で切断して見た断面が凹形状となる円周溝８が設けられている。図１左側に示すように、外輪間座７のうち円周方向の一部に、潤滑油を前記円周溝８へ向けて吐出する給油口１８を有する給油路９が形成されている。この給油路９は、外輪間座７の外周面から、径方向に貫通する段付きの貫通孔状に形成されている。図５に示すように、給油路９から供給された潤滑油は、給油口１８から吐出されて円周溝８に供給される。この潤滑油は、円周溝８に沿って、内輪１（図１）の回転方向Ｌ１と同一方向に進み、軸受の冷却に供される。冷却に供された潤滑油は、排油口１０，１３（図１）および後述の切欠部１５から排出される。 On the outer peripheral surface of the inner ring spacer 6, there is provided a circumferential groove 8 having a concave cross section when the inner ring spacer 6 is cut along a plane including the bearing axis. As shown on the left side of FIG. 1, an oil supply passage 9 having an oil supply port 18 that discharges lubricating oil toward the circumferential groove 8 is formed in a part of the outer ring spacer 7 in the circumferential direction. The oil supply passage 9 is formed in a stepped through hole shape that penetrates in the radial direction from the outer peripheral surface of the outer ring spacer 7. As shown in FIG. 5, the lubricating oil supplied from the oil supply passage 9 is discharged from the oil supply port 18 and supplied to the circumferential groove 8. This lubricating oil proceeds along the circumferential groove 8 in the same direction as the rotation direction L1 of the inner ring 1 (FIG. 1), and is used for cooling the bearing. The lubricating oil used for cooling is discharged from the oil discharge ports 10 and 13 (FIG. 1) and a notch 15 described later.

外輪間座７のうち、前記給油路９とは異なる円周方向位置には、潤滑油を外部に排出する排油口１０が形成されている。排油口１０は、図１右側に示すように、外輪間座７の外周面から径方向に貫通して円周溝８に連通するように形成されている。図５に示すように、給油路９に対し、排油口１０の位相が所定の位相角度α（この例ではα＝２７０度）となるように設けられている。 In the outer ring spacer 7, an oil discharge port 10 for discharging the lubricating oil to the outside is formed at a circumferential position different from the oil supply passage 9. As shown on the right side of FIG. 1, the oil discharge port 10 is formed so as to penetrate from the outer peripheral surface of the outer ring spacer 7 in the radial direction and communicate with the circumferential groove 8. As shown in FIG. 5, the oil supply passage 9 is provided such that the phase of the oil discharge port 10 is a predetermined phase angle α (α = 270 degrees in this example).

図２に示すように、内輪間座６における、軸受とは軸方向逆側の外周面と、この外周面に対向する外輪間座７の内周面との間には、例えば、隣接する軸受等に潤滑油が漏洩することを抑制するラビリンス機構Ｒｋを設けている。このラビリンス機構Ｒｋは、給油路９および排油口１０（図１）に連通し、広部と狭部とが軸方向に連なるものとしている。広部は、内輪間座６における前記軸方向逆側の外周面に設けられる円周溝６ｂと、この円周溝６ｂに対向する外輪間座７の内周面とを含んで構成される。前記円周溝６ｂは、軸方向に間隔をあけて複数配設される。前記狭部は、内輪間座６における前記外周面の突出先端部と、この突出先端部に対向する外輪間座７の内周面とを含んで構成される。潤滑油が給油路９から供給されラビリンス機構Ｒｋに浸入した場合、この潤滑油は、内輪回転による遠心力により円周溝６ｂに沿って漏れ側とは反対方向に移動するため、隣接する軸受等に潤滑油が漏洩することを抑制し得る。なお、内輪間座６の外周面に円周溝６ｂを設ける構成に代えて、外輪間座７の内周面に、円周溝を設けても良い。また内輪間座６および外輪間座７にそれぞれ円周溝を設けても良い。 As shown in FIG. 2, for example, an adjacent bearing between the outer peripheral surface of the inner ring spacer 6 that is opposite to the bearing in the axial direction and the inner peripheral surface of the outer ring spacer 7 that faces the outer peripheral surface. A labyrinth mechanism Rk that suppresses leakage of the lubricating oil is provided. The labyrinth mechanism Rk communicates with the oil supply passage 9 and the oil discharge port 10 (FIG. 1), and the wide portion and the narrow portion are continuous in the axial direction. The wide portion includes a circumferential groove 6b provided on the outer circumferential surface of the inner ring spacer 6 on the opposite side in the axial direction, and an inner circumferential surface of the outer ring spacer 7 facing the circumferential groove 6b. A plurality of the circumferential grooves 6b are arranged at intervals in the axial direction. The narrow portion includes a protruding tip portion of the outer peripheral surface of the inner ring spacer 6 and an inner peripheral surface of the outer ring spacer 7 facing the protruding tip portion. When the lubricating oil is supplied from the oil supply passage 9 and enters the labyrinth mechanism Rk, the lubricating oil moves in the direction opposite to the leakage side along the circumferential groove 6b due to the centrifugal force generated by the inner ring rotation. It is possible to suppress the leakage of the lubricating oil. Instead of providing the circumferential groove 6 b on the outer peripheral surface of the inner ring spacer 6, a circumferential groove may be provided on the inner peripheral surface of the outer ring spacer 7. Further, circumferential grooves may be provided in the inner ring spacer 6 and the outer ring spacer 7 respectively.

図４は、図２の要部の拡大図である。図２および図５に示すように、内輪間座６における、ラビリンス機構Ｒｋとは軸方向逆側の外周面と、外輪間座７の内周面とのすきま部には、円周溝８から外輪２の一端面に導かれる潤滑油の油量を絞る第一絞り部１１が設けられている。したがって、内輪間座６の円周溝８に沿って流れ軸受を冷却した油は、排油口１０から排出されるものと、軸受潤滑のために第一絞り部１１を通過するものとに分かれる。この第一絞り部１１を成す軸方向のすきまδ１は、例えば、上限値および下限値が管理され、これにより軸受側に導かれる潤滑油の油量を制御可能としている。 FIG. 4 is an enlarged view of a main part of FIG. As shown in FIGS. 2 and 5, in the inner ring spacer 6, a circumferential groove 8 is formed in the clearance between the outer circumferential surface opposite to the labyrinth mechanism Rk in the axial direction and the inner circumferential surface of the outer ring spacer 7. A first throttle portion 11 is provided for reducing the amount of lubricating oil guided to one end surface of the outer ring 2. Therefore, the oil that flows along the circumferential groove 8 of the inner ring spacer 6 and cools the bearing is divided into one that is discharged from the oil discharge port 10 and one that passes through the first throttle portion 11 for bearing lubrication. . For example, an upper limit value and a lower limit value of the axial clearance δ1 forming the first throttle portion 11 are managed, and thereby the amount of lubricating oil guided to the bearing side can be controlled.

図４に示すように、外輪２の一端面には、環状の油保有溝１２が設けられている。この油保有溝１２は、第一絞り部１１に連通してこの第一絞り部１１から導かれる潤滑油を収容する円周溝である。油保有溝１２は、外輪２の一端面における径方向幅内で、且つ、断面矩形状に形成される。
図３は外輪２の正面図である。図３および図４に示すように、外輪２の外周面には、排油口１３が設けられている。この排油口１３は、例えば、円周方向等配に２箇所以上（２箇所の排油口１３，１３が設けられる場合、これら排油口１３，１３は１８０度対角位置にある）設けられている。各排油口１３，１３は、油保有溝１２にそれぞれ連通し、潤滑油を排出する。図３に示すように、この例の各排油口１３は、軸方向長さＬ２よりも円周方向長さＬ３が長い長孔状に形成され、油保有溝１２から円周方向に沿って流れ込む潤滑油を排油口１３における長孔に沿って円滑に排油し得る。よって丸孔状のものより、排油効率が高められている。図２に示すように、外輪２の各排油口１３および油保有溝１２は、外輪２における、軌道面２ａに対し接触角を成す作用線Ｌの偏り側とは逆側の反偏り側に設けられている。なお排油口１３を円周方向不等配に２箇所以上設けることも可能であり、排油口１３を円周方向の一箇所のみに設けることも可能である。 As shown in FIG. 4, an annular oil retaining groove 12 is provided on one end surface of the outer ring 2. The oil retaining groove 12 is a circumferential groove that communicates with the first throttle portion 11 and accommodates the lubricating oil guided from the first throttle portion 11. The oil retaining groove 12 is formed within a radial width at one end surface of the outer ring 2 and has a rectangular cross section.
FIG. 3 is a front view of the outer ring 2. As shown in FIGS. 3 and 4, an oil drain port 13 is provided on the outer peripheral surface of the outer ring 2. The oil discharge ports 13 are provided at, for example, two or more circumferentially equidistant positions (when two oil discharge ports 13 and 13 are provided, the oil discharge ports 13 and 13 are at a diagonal position of 180 degrees). It has been. Each oil discharge port 13, 13 communicates with the oil retaining groove 12 to discharge the lubricating oil. As shown in FIG. 3, each oil discharge port 13 in this example is formed in a long hole shape having a circumferential length L3 longer than the axial length L2, and extends from the oil retaining groove 12 along the circumferential direction. Lubricating oil flowing in can be smoothly drained along the long hole in the oil drain port 13. Therefore, the oil draining efficiency is improved as compared with the round hole shape. As shown in FIG. 2, each oil discharge port 13 and the oil retaining groove 12 of the outer ring 2 are on the opposite side of the outer ring 2 opposite to the biased side of the action line L that forms a contact angle with the raceway surface 2 a. Is provided. Note that it is possible to provide two or more oil drain ports 13 at uneven circumferential distribution, and it is also possible to provide the oil drain ports 13 only at one circumferential direction.

外輪２の一端面と、この外輪２の一端面に臨む内輪間座６の一端面との間には、第二絞り部１４が設けられている。この第二絞り部１４は、油保有溝１２および内外輪１，２の軸受空間Ａ１にそれぞれ連通して、軸受空間Ａ１内に浸入する潤滑油の油量を絞る。つまり内輪間座６の円周溝８から第一絞り部１１、第二絞り部１４を順次、通過した潤滑油のみが、軸受空間Ａ１内に浸入する。このように第一絞り部１１、第二絞り部１４を設けたことで、多量の潤滑油が軸受空間Ａ１内に浸入することを防止し得る。前記「多量の潤滑油」とは、潤滑油が攪拌抵抗となって、例えば、実験やシミュレーション等により定められる温度以上に軸受が温度上昇するような潤滑油の油量を言う。 A second throttle portion 14 is provided between one end surface of the outer ring 2 and one end surface of the inner ring spacer 6 facing the one end surface of the outer ring 2. The second throttle portion 14 communicates with the oil retaining groove 12 and the bearing space A1 of the inner and outer rings 1 and 2, respectively, and throttles the amount of lubricating oil that enters the bearing space A1. That is, only the lubricating oil that has passed sequentially from the circumferential groove 8 of the inner ring spacer 6 through the first throttle portion 11 and the second throttle portion 14 enters the bearing space A1. By providing the first throttle part 11 and the second throttle part 14 in this way, a large amount of lubricating oil can be prevented from entering the bearing space A1. The “large amount of lubricating oil” refers to an amount of lubricating oil that causes the bearing oil to have a stirring resistance, and the temperature of the bearing rises above a temperature determined by experiments, simulations, or the like.

図４に示すように、この例では、外輪２の一端面のうち、油保有溝１２よりも内径側の径方向幅面を全周に渡って削る加工等を施すことにより、外輪２、内輪間座６間に、径方向のすきまδ２を形成する第二絞り部１４が設けられる。この第二絞り部１４を成す径方向のすきまδ２は、例えば、上限値および下限値が管理されている。第一および第二絞り部１１，１４のすきまδ１，δ２を管理することにより、軸受空間Ａ１内に浸入する潤滑油の油量を制御可能としている。なお外輪２の一端面に加工等を施すのに代えて、または、外輪２の一端面に加工等を施すと共に、内輪間座６の一端面に加工等を施すことにより、第二絞り部１４を設けても良い。 As shown in FIG. 4, in this example, the outer ring 2 is separated from the inner ring by performing a process of cutting the radial width surface on the inner diameter side of the oil retaining groove 12 over the entire circumference of one end surface of the outer ring 2. Between the seats 6 is provided a second throttle portion 14 that forms a radial clearance δ2. For example, an upper limit value and a lower limit value of the radial clearance δ 2 forming the second throttle portion 14 are managed. By managing the clearances δ1 and δ2 of the first and second throttle portions 11 and 14, the amount of lubricating oil entering the bearing space A1 can be controlled. Instead of processing the one end surface of the outer ring 2 or processing the one end surface of the outer ring 2 and processing the one end surface of the inner ring spacer 6, the second constriction portion 14. May be provided.

図２に示すように、固定側の軌道輪である外輪２には、軸受空間Ａ１内で潤滑に供された潤滑油を軸受外に排出する切欠部１５が設けられている。外輪２における、外輪間座７が設けられる軸方向逆側の外輪他端面に、切欠部１５が設けられている。この切欠部１５を、図５に示すように、内輪１の回転方向Ｌ１に沿う、給油路９と排油口１０との間に配設している。この例では、切欠部１５は、例えば、給油路９に対し９０度の位相角度をもって配設され、且つ、排油口１０に対し１８０度の位相角度をもって配設されている。 As shown in FIG. 2, the outer ring 2 that is a fixed-side raceway ring is provided with a notch 15 that discharges lubricating oil used for lubrication in the bearing space A1 to the outside of the bearing. In the outer ring 2, the outer ring end surface of the axial opposite side of the outer ring spacer 7 is provided, notch 15 is provided. As shown in FIG. 5, the notch 15 is disposed between the oil supply passage 9 and the oil discharge port 10 along the rotation direction L 1 of the inner ring 1. In this example, the notch 15 is disposed with a phase angle of 90 degrees with respect to the oil supply passage 9 and with a phase angle of 180 degrees with respect to the oil discharge port 10, for example.

作用効果について説明する。
図１に示すように、軸受運転時、外輪間座７の給油路９から潤滑油を供給すると、内輪間座６の円周溝８に沿って潤滑油が流れる。これにより軸受を冷却する。軸受を冷却した油は、外輪間座７の排油口１０から排出されるものと、軸受潤滑のために第一絞り部１１を通過して油保有溝１２に流れるものとに分かれる。さらに油保有溝１２に流れ込んだ潤滑油は、外輪２の排油口１３を通り回収されるものと、第二絞り部１４を通過して軸受空間Ａ１内に浸入するものとに分かれる。このように第一および第二絞り部１１，１４を設けることにより、軸受空間Ａ１内に浸入する潤滑油の油量を抑制することができる。したがって、潤滑油の攪拌抵抗による軸受の温度上昇を抑制して、軸受の高速回転を可能とすることができる。 The effect will be described.
As shown in FIG. 1, when lubricating oil is supplied from the oil supply passage 9 of the outer ring spacer 7 during the bearing operation, the lubricating oil flows along the circumferential groove 8 of the inner ring spacer 6. This cools the bearing. The oil that has cooled the bearing is divided into oil that is discharged from the oil discharge port 10 of the outer ring spacer 7 and oil that flows through the first throttle portion 11 and flows into the oil retaining groove 12 for bearing lubrication. Furthermore, the lubricating oil that has flowed into the oil retaining groove 12 is divided into one that is collected through the oil discharge port 13 of the outer ring 2 and one that passes through the second throttle portion 14 and enters the bearing space A1. By providing the first and second throttle portions 11 and 14 in this way, the amount of lubricating oil that enters the bearing space A1 can be suppressed. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.

また、この例では、外輪２の外周面に排油口１３を設けたため、外輪２の外周面に排油口１３を設けない構成に比べて、排油効率を上げることができる。外輪２の排油口１３を２箇所以上設けた場合、排油効率の向上をさらに図ることができる。内輪間座６の円周溝８は、断面凹形状に形成されたため、給油路９から供給された潤滑油は、断面凹形状の円周溝８の溝底面８ａに跳ね返って、内輪回転に伴う遠心力により、外輪間座７の排油口１０および第１絞り部１１へ向かうようになっている。内輪間座６の外径６ａを、外輪２の一端面の径方向幅内に位置するように径方向に厚肉に設けたうえで、この内輪間座６の円周溝８を径方向外方に開口する断面凹形状に形成したため、内輪間座６の外径６ａが内輪１の一端面の径方向幅内に位置するものより、溝底をより深くして潤滑剤を供給可能な溝断面を大きくすることができる。これにより冷却および潤滑に必要十分な量の潤滑剤を円周溝８に供給することができ、特に冷却効果をより高めることができる。 Further, in this example, since the oil drain port 13 is provided on the outer peripheral surface of the outer ring 2, the oil drain efficiency can be increased as compared with the configuration in which the oil drain port 13 is not provided on the outer peripheral surface of the outer ring 2. When two or more oil discharge ports 13 of the outer ring 2 are provided, the oil discharge efficiency can be further improved. Since the circumferential groove 8 of the inner ring spacer 6 is formed in a concave cross section, the lubricating oil supplied from the oil supply passage 9 rebounds to the groove bottom surface 8a of the circumferential groove 8 having a concave cross section to accompany the rotation of the inner ring. Centrifugal force is directed toward the oil outlet 10 and the first throttle 11 of the outer ring spacer 7. An outer diameter 6a of the inner ring spacer 6 is provided thick in the radial direction so as to be positioned within a radial width of one end surface of the outer ring 2, and the circumferential groove 8 of the inner ring spacer 6 is formed radially outward. Since the outer ring 6a of the inner ring spacer 6 has an outer diameter 6a that is located within the radial width of one end surface of the inner ring 1, the groove bottom can be deepened and the lubricant can be supplied. The cross section can be enlarged. As a result, a sufficient amount of lubricant necessary for cooling and lubrication can be supplied to the circumferential groove 8, and in particular, the cooling effect can be further enhanced.

外輪２の各排油口１３および油保有溝１２は、外輪２における、軌道面２ａに対し接触角を成す作用線Ｌの偏り側とは逆側の反偏り側に設けられているため、外輪２が許容し得る荷重が低下することはない。このため外輪２の剛性を高く維持することができ、軸受寿命の低下を防ぐことができる。 Each oil outlet 13 and the oil retaining groove 12 of the outer ring 2 are provided on the opposite side of the outer ring 2 opposite to the side of the acting line L that forms a contact angle with the raceway surface 2a. The load that 2 can tolerate is not reduced. For this reason, the rigidity of the outer ring 2 can be maintained high, and a reduction in bearing life can be prevented.

他の実施形態について説明する。
以下の説明においては、各形態で先行する形態で説明している事項に対応している部分には同一の参照符を付し、重複する説明を略する。構成の一部のみを説明している場合、構成の他の部分は、特に記載のない限り先行して説明している形態と同様とする。 Another embodiment will be described.
In the following description, the same reference numerals are given to the portions corresponding to the matters described in the preceding forms in each embodiment, and the overlapping description is omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in advance unless otherwise specified.

図６（Ａ），（Ｂ）に示すように、外輪間座７の排油口１０に、潤滑油の円周溝８に沿う流れを規制する障壁１６を設けても良い。この障壁１６は、外輪間座７の排油口１０における周方向長さＬａの中央部に配設される半径方向に延びる矩形板状である。障壁１６は、排油口１０の開口縁から、同排油口１０における半径方向内周付近まで延びる。この障壁１６によると、内輪の回転に伴い円周溝８に沿って流れる潤滑油は、障壁１６に当たり、排油口１０に回収され易くなる。これにより、潤滑油が軸受内部に滞留することを抑制することができ、したがって、軸受内部の攪拌抵抗の増加を防止し得る。また、障壁１６を外輪間座７の排油口１０における周方向長さＬａの中央部に配設したため、軸受が正逆回転いずれの場合にも、円周溝８に沿って潤滑油を前記障壁１６で規制し、排油口１０に円滑に導くことができる。 As shown in FIGS. 6A and 6B, a barrier 16 that restricts the flow of the lubricating oil along the circumferential groove 8 may be provided at the oil outlet 10 of the outer ring spacer 7. The barrier 16 is in the shape of a rectangular plate that extends in the radial direction and is disposed at the center of the circumferential length La of the oil outlet 10 of the outer ring spacer 7. The barrier 16 extends from the opening edge of the oil discharge port 10 to the vicinity of the radially inner periphery of the oil discharge port 10. According to the barrier 16, the lubricating oil flowing along the circumferential groove 8 as the inner ring rotates rotates against the barrier 16 and is easily collected at the oil discharge port 10. Thereby, it can suppress that lubricating oil retains inside a bearing, Therefore, increase of the stirring resistance inside a bearing can be prevented. Further, since the barrier 16 is disposed at the central portion of the circumferential length La in the oil outlet 10 of the outer ring spacer 7, the lubricating oil is supplied along the circumferential groove 8 regardless of whether the bearing is rotating forward or reverse. It is regulated by the barrier 16 and can be smoothly guided to the oil discharge port 10.

図７に示すように、障壁１６は、内輪間座６における円周溝８の底面付近まで延びる延在部１６ａを含むものとしても良い。この場合、円周溝８に沿って流れる潤滑油を、障壁１６により確実に衝突させることができる。これにより、延在部１６ａがない障壁に比べて、排油口１０から回収される潤滑油の回収効率を高めることができる。 As shown in FIG. 7, the barrier 16 may include an extending portion 16 a that extends to the vicinity of the bottom surface of the circumferential groove 8 in the inner ring spacer 6. In this case, the lubricating oil flowing along the circumferential groove 8 can be reliably collided by the barrier 16. Thereby, the collection | recovery efficiency of the lubricating oil collect | recovered from the oil discharge port 10 can be improved compared with the barrier without the extension part 16a.

図８に示すように、障壁１６Ａをテーパ形状にしても良い。この例の障壁１６Ａは、例えば、三角柱形状からなり、排油口１０における周方向長さＬａの中央部Ｐ１に至るように傾斜する傾斜部１６Ａａ，１６Ａａを含む。前記中央部Ｐ１を通る半径方向に対する各傾斜部１６Ａａ，１６Ａａの傾斜角度α１，α１は、同一角度に設定され、且つ、排油の回収を阻害しない角度に規定される。一方の傾斜部１６Ａａの半径方向内方側の端部と、他方の傾斜部１６Ａａの半径方向内方側の端部との距離Ｌｂは、この障壁１６Ａを排油口１０の外径方向から挿入して組み立てる組立性から、排油口１０の周方向長さ（幅寸法）Ｌａと略同一とされている。これら両端部を結ぶ辺が、外輪間座７における前記中央部Ｐ１を通る接線と平行になるように傾斜部１６Ａａ，１６Ａａが設けられる。 As shown in FIG. 8, the barrier 16A may be tapered. The barrier 16A in this example has, for example, a triangular prism shape, and includes inclined portions 16Aa and 16Aa that are inclined so as to reach the central portion P1 of the circumferential length La at the oil discharge port 10. The inclination angles α1 and α1 of the inclined portions 16Aa and 16Aa with respect to the radial direction passing through the central portion P1 are set to the same angle and are defined as angles that do not impede the recovery of waste oil. The distance Lb between the end portion on the radially inner side of one inclined portion 16Aa and the end portion on the radially inner side of the other inclined portion 16Aa is such that this barrier 16A is inserted from the outer diameter direction of the oil discharge port 10 From the assembling property to be assembled, the circumferential length (width dimension) La of the oil discharge port 10 is substantially the same. Inclined portions 16Aa and 16Aa are provided so that sides connecting these both end portions are parallel to a tangent line passing through the central portion P1 in the outer ring spacer 7.

この構成によると、潤滑油が傾斜部１６Ａａに沿って円滑に流れるため、排油口１０から回収される潤滑油の回収効率の向上を図ることができる。また各傾斜部１６Ａａにより、軸受が正逆回転いずれの場合にも、円周溝８に沿って流れる潤滑油を、傾斜部１６Ａａに沿って円滑に流し排油口１０に円滑に導くことができる。 According to this configuration, since the lubricating oil flows smoothly along the inclined portion 16Aa, the recovery efficiency of the lubricating oil recovered from the oil outlet 10 can be improved. In addition, each inclined portion 16Aa can smoothly flow the lubricating oil flowing along the circumferential groove 8 along the inclined portion 16Aa and smoothly guide it to the oil discharge port 10 regardless of whether the bearing rotates forward or backward. .

図９の例は、図８と同様に、障壁１６Ｂをテーパ形状にした例であるが、障壁１６Ｂを２分割構造とすることにより、一方の傾斜部１６Ｂａの半径方向内方側の端部と、他方の傾斜部１６Ｂａの半径方向内方側の端部との距離Ｌｂを、排油口１０の周方向長さＬａよりも大きくしている。各傾斜部１６Ｂａの端部は、それぞれ内輪間座６における円周溝８の底面付近まで延びる。このように障壁１６Ｂが内輪間座６と外輪間座７とにまたがる場合には、障壁１６Ｂは組立性を考慮し排油口１０の外径方向から挿入されるため、排油口１０の幅寸法＜前記距離Ｌｂとすると、障壁１６Ｂを２分割以上の構造にしないと成立しない。図９の例では、各傾斜部１６Ｂａ，１６Ｂａの端部間の距離Ｌｂ＞排油口１０の周方向長さＬａとし、障壁１６Ｂを傾斜部１６Ｂａ，１６Ｂａを含む２分割構造とすることで、図８の例よりも潤滑油の回収効率の向上をさらに図ることができる。また各傾斜部１６Ｂａを排油口１０の外径方向から挿入して障壁１６Ｂを容易に組み立てることができ、製造コストの低減を図れる。 The example of FIG. 9 is an example in which the barrier 16B is tapered like FIG. 8, but by forming the barrier 16B into a two-part structure, the end portion on the radially inner side of one inclined portion 16Ba The distance Lb between the other inclined portion 16Ba and the end portion on the radially inner side is larger than the circumferential length La of the oil discharge port 10. The end of each inclined portion 16Ba extends to the vicinity of the bottom surface of the circumferential groove 8 in the inner ring spacer 6. When the barrier 16B extends over the inner ring spacer 6 and the outer ring spacer 7 in this way, the barrier 16B is inserted from the outer diameter direction of the oil discharge port 10 in consideration of assembling properties. If dimension <the distance Lb, the barrier 16B is not formed unless the structure is divided into two or more. In the example of FIG. 9, the distance Lb between the end portions of the inclined portions 16Ba and 16Ba is set to be the circumferential length La of the oil discharge port 10, and the barrier 16B has a two-part structure including the inclined portions 16Ba and 16Ba. The recovery efficiency of the lubricating oil can be further improved as compared with the example of FIG. Moreover, each inclined part 16Ba can be inserted from the outer diameter direction of the oil discharge port 10, and the barrier 16B can be assembled easily, and the manufacturing cost can be reduced.

図１０に示すように、障壁１６Ｃは、潤滑油の流れ方向に応じて可動する弁構造であっても良い。図１０（Ａ）は、内輪が同図反時計回りに回転するときの状態を表す要部の平面図であり、同図（Ｂ）は、同内輪が同図時計回りに回転するときの状態を表す要部の平面図である。外輪間座７の排油口１０における半径方向内方には、弁体１６Ｃａの長手方向一端が揺動自在に支持されている。内輪が回転する場合、円周溝８に沿って内輪回転方向に流れる潤滑油が、弁体１６Ｃａの長手方向他端を押圧して可動させる。この場合、軸受の正回転、逆回転にかかわらず、潤滑油の流れ方向に応じて障壁１６Ｃを可動させて、潤滑油を排油口１０に円滑に導くことができる。また弁体１６Ｃａを可動させる駆動源等が不要であるため、構造を簡単化することができる。 As shown in FIG. 10, the barrier 16 C may be a valve structure that can move according to the flow direction of the lubricating oil. FIG. 10A is a plan view of the main part showing the state when the inner ring rotates counterclockwise in the figure, and FIG. 10B shows the state when the inner ring rotates clockwise in the figure. It is a top view of the principal part showing. One end in the longitudinal direction of the valve body 16Ca is swingably supported inside the oil outlet 10 of the outer ring spacer 7 in the radial direction. When the inner ring rotates, the lubricating oil flowing in the inner ring rotating direction along the circumferential groove 8 presses and moves the other end in the longitudinal direction of the valve body 16Ca. In this case, the forward rotation of the bearing, regardless of the reverse rotation, by moving the barrier 16C in accordance with the flow direction of the lubricating oil, the lubricating oil can be smoothly guided that the oil drain port 10. Further, since a drive source or the like for moving the valve body 16Ca is unnecessary, the structure can be simplified.

図１１〜図１３の例では、障壁１６Ｄは、排油口１０にて軸方向に並ぶ２つの壁部１６Ｄａ，１６Ｄａを有する。図１２は外輪間座７の要部を内径側から拡大して示す斜視図であり、図１３は同外輪間座７の要部の平面図である。図１２，図１３に示すように、各壁部１６Ｄａ，１６Ｄａは、排油口１０における半径方向内方の円周方向一側部から、前記排油口１０における半径方向外方の円周方向他側部に至るようにそれぞれ傾斜すると共に、これら軸方向に並ぶ２つの壁部１６Ｄａ，１６Ｄａが互いに交差するように設けられる。
この場合、軸受の正回転，逆回転にかかわらず、潤滑油がいずれか一方の壁部１６Ｄａに沿って円滑に流れるため、排油口１０から回収される潤滑油の回収効率の向上を図ることができる。 In the example of FIGS. 11 to 13, the barrier 16 D has two wall portions 16 Da and 16 Da arranged in the axial direction at the oil discharge port 10. 12 is an enlarged perspective view showing the main part of the outer ring spacer 7 from the inner diameter side, and FIG. 13 is a plan view of the main part of the outer ring spacer 7. As shown in FIGS. 12 and 13, each of the wall portions 16 Da and 16 Da extends from the radially inner side of the oil outlet 10 toward the radially outer side of the oil outlet 10. The two wall portions 16Da and 16Da that are inclined so as to reach the other side portion and are arranged in the axial direction are provided so as to intersect each other.
In this case, since the lubricating oil flows smoothly along one of the wall portions 16Da regardless of whether the bearing is rotating forward or backward, the recovery efficiency of the lubricating oil recovered from the oil outlet 10 is improved. Can do.

図１４は、前述のいずれかの転がり軸受装置を、立型の工作機械主軸の支持に用いた例を概略示す断面図である。この例では、アンギュラ玉軸受を含む転がり軸受装置２８，２８を、２個背面組み合わせでハウジング２９に設置し、これらの転がり軸受装置２８，２８により主軸３０を回転自在に支持する。各軸受装置２８における内輪１は、内輪位置決め間座３１，３１および主軸３０の段部３０ａ，３０ａにより軸方向に位置決めされ、内輪固定ナット３２により主軸３０に締め付け固定されている。主軸上側の間座７および主軸下側の外輪２は、外輪押え蓋３４，３４によりハウジング２９内に位置決め固定されている。また主軸上側の外輪端面と、主軸下側の間座幅面との間には、間座３５が介在されている。 FIG. 14 is a cross-sectional view schematically illustrating an example in which any of the above-described rolling bearing devices is used to support a vertical machine tool spindle. In this example, two rolling bearing devices 28 and 28 including angular ball bearings are installed in the housing 29 in a combination of the back surfaces, and the main shaft 30 is rotatably supported by these rolling bearing devices 28 and 28. The inner ring 1 in each bearing device 28 is positioned in the axial direction by inner ring positioning spacers 31, 31 and step portions 30 a, 30 a of the main shaft 30, and is fastened and fixed to the main shaft 30 by an inner ring fixing nut 32. The spacer 7 on the upper side of the main shaft and the outer ring 2 on the lower side of the main shaft are positioned and fixed in the housing 29 by outer ring pressing lids 34 and 34. A spacer 35 is interposed between the outer ring end surface on the upper side of the main shaft and the spacer width surface on the lower side of the main shaft.

ハウジング２９は、ハウジング内筒２９ａとハウジング外筒２９ｂ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２９ｃが設けられている。ハウジング内筒２９ａには、各軸受装置２８にそれぞれ潤滑油を供給する供給油路３６，３６が形成されている。これら供給油路３６，３６は図示外の潤滑油供給源に接続されている。さらにハウジング内筒２９ａには、潤滑に供された潤滑油を排出する排油溝３７および排油路３８が形成されている。排油溝３７は、各軸受装置２８における切欠部１５および排油口１０にそれぞれ連通する。各排油溝３７に、主軸軸方向に延びる排油路３８が繋がり、この排油路３８から潤滑油が排出されるようになっている。 The housing 29 is formed by fitting a housing inner cylinder 29a and a housing outer cylinder 29b, and an oil passage groove 29c for cooling is provided in the fitting portion. Supply oil passages 36 and 36 for supplying lubricating oil to the bearing devices 28 are formed in the housing inner cylinder 29a. These supply oil passages 36 are connected to a lubricating oil supply source (not shown). Further, the housing inner cylinder 29 a is formed with an oil drain groove 37 and an oil drain passage 38 for discharging the lubricating oil used for lubrication. The oil drain groove 37 communicates with the notch 15 and the oil drain port 10 in each bearing device 28. Each oil drain groove 37 is connected to an oil drain passage 38 extending in the main shaft axis direction, and the lubricating oil is discharged from the oil drain passage 38.

このように転がり軸受装置２８，２８を工作機械主軸３０の支持に用いた場合、各転がり軸受装置２８に、第一および第二絞り部１１，１４（図１）を設けることにより、軸受空間内に浸入する潤滑油の油量を抑制することができる。このため、潤滑油の攪拌抵抗による軸受の温度上昇を抑制して、軸受の高速回転を可能とすることができる。
本実施形態に係る転がり軸受装置を、横型の工作機械主軸の支持に用いることも可能である。 When the rolling bearing devices 28 and 28 are used for supporting the machine tool main shaft 30 as described above, the first and second throttle portions 11 and 14 (FIG. 1) are provided in the respective rolling bearing devices 28, whereby the bearing space It is possible to suppress the amount of lubricating oil that penetrates into. For this reason, the temperature rise of the bearing due to the stirring resistance of the lubricating oil can be suppressed, and the bearing can be rotated at high speed.
It is also possible to use the rolling bearing device according to the present embodiment for supporting a horizontal machine tool spindle.

１…内輪
２…外輪
１ａ，２ａ…軌道面
３…転動体
４…保持器
６…内輪間座
７…外輪間座
８…円周溝
９…給油路
１０…排油口
１１…第一絞り部
１２…環状の油保有溝
１３…排油口
１４…第二絞り部
１６〜１６Ｄ…障壁
１８…給油口
３０…主軸
Ｂｒ…転がり軸受
Ｋｕ…給排油機構 DESCRIPTION OF SYMBOLS 1 ... Inner ring 2 ... Outer ring 1a, 2a ... Raceway surface 3 ... Rolling body 4 ... Cage 6 ... Inner ring spacer 7 ... Outer ring spacer 8 ... Circumferential groove 9 ... Oil supply path 10 ... Oil outlet 11 ... First throttle part DESCRIPTION OF SYMBOLS 12 ... Cylindrical oil holding groove 13 ... Oil discharge port 14 ... Second throttle part 16-16D ... Barrier 18 ... Oil supply port 30 ... Main shaft Br ... Rolling bearing Ku ... Supply / discharge oil mechanism

Claims

内外輪の軌道面間に、保持器に保持された複数の転動体を介在させた転がり軸受と、軸受冷却媒体を兼ねる潤滑油を軸受内に供給すると共に、軸受外に排出する給排油機構とを備えた転がり軸受装置において、
前記内輪の一端面に隣接し且つ外径が外輪の一端面の径方向幅内に位置する内輪間座を設けると共に、外輪の一端面に隣接し且つ内周面が前記内輪間座の外周面に対向する外輪間座を設け、
前記給排油機構は、
前記内輪間座の外周面に設けられた円周溝と、
前記外輪間座に設けられ、潤滑油を前記円周溝へ向けて吐出する給油口を有する給油路と、
前記内輪間座の外周面と外輪間座の内周面とのすきま部に設けられ、円周溝から外輪の一端面に導かれる潤滑油の油量を絞る第一絞り部と、
前記外輪の一端面に設けられ、第一絞り部に連通してこの第一絞り部から導かれる潤滑油を収容する環状の油保有溝と、
前記外輪の一端面と、この外輪の一端面に臨む内輪間座の一端面との間に設けられ、油保有溝および内外輪の軸受空間にそれぞれ連通して、軸受空間内に浸入する潤滑油の油量を絞る第二絞り部と、
を有することを特徴とする転がり軸受装置。 A rolling bearing in which a plurality of rolling elements held by a cage are interposed between the raceway surfaces of the inner and outer rings, and a supply / exhaust oil mechanism that supplies lubricating oil also serving as a bearing cooling medium into the bearing and discharges it outside the bearing. In a rolling bearing device with
An inner ring spacer is provided that is adjacent to one end surface of the inner ring and has an outer diameter located within a radial width of one end surface of the outer ring, and an inner peripheral surface that is adjacent to one end surface of the outer ring and is an outer peripheral surface of the inner ring spacer. An outer ring spacer facing the
The oil supply / discharge oil mechanism is
A circumferential groove provided on the outer peripheral surface of the inner ring spacer;
An oil supply passage provided in the outer ring spacer and having an oil supply port for discharging the lubricating oil toward the circumferential groove;
A first throttle portion that is provided in a clearance between the outer peripheral surface of the inner ring spacer and the inner peripheral surface of the outer ring spacer, and squeezes the amount of lubricating oil guided from the circumferential groove to one end surface of the outer ring;
An annular oil retaining groove that is provided on one end surface of the outer ring, communicates with the first throttle portion, and stores lubricating oil guided from the first throttle portion;
Lubricating oil that is provided between one end surface of the outer ring and one end surface of the inner ring spacer facing the one end surface of the outer ring and communicates with the oil retaining groove and the bearing space of the inner and outer rings, and enters the bearing space. A second squeezing part that squeezes the amount of oil,
A rolling bearing device comprising:

請求項１において、前記給排油機構は、外輪の外周面に設けられ、油保有溝に連通して潤滑油を排出する排油口を含む転がり軸受装置。 The rolling bearing device according to claim 1, wherein the oil supply / discharge oil mechanism is provided on an outer peripheral surface of the outer ring and includes an oil discharge port that communicates with the oil retaining groove and discharges the lubricating oil.

請求項１または請求項２において、前記給排油機構は、前記外輪間座に設けられる排油口を含み、この排油口は、前記給油口とは異なる円周方向位置で円周溝に連通し、潤滑油を排出するものである転がり軸受装置。 3. The oil supply and discharge mechanism according to claim 1, wherein the oil supply and discharge mechanism includes an oil discharge port provided in the outer ring spacer, and the oil discharge port is formed in a circumferential groove at a circumferential position different from the oil supply port. Rolling bearing device that communicates and discharges lubricating oil.

請求項３において、前記外輪間座の排油口に、潤滑油の円周溝に沿う流れを規制する障壁を設けた転がり軸受装置。 4. The rolling bearing device according to claim 3, wherein a barrier that restricts the flow of the lubricating oil along the circumferential groove is provided at the oil outlet of the outer ring spacer.

請求項４において、前記障壁を、外輪間座の排油口における周方向長さの中央部に配設した転がり軸受装置。 The rolling bearing device according to claim 4, wherein the barrier is disposed at a central portion of a circumferential length of an oil outlet of the outer ring spacer.

請求項４または請求項５において、前記障壁は、潤滑油の流れ方向に応じて可動する弁構造である転がり軸受装置。 6. The rolling bearing device according to claim 4, wherein the barrier is a valve structure that is movable in accordance with a flow direction of the lubricating oil.

請求項４または請求項５において、前記障壁は、排油口にて軸方向に並ぶ２つの壁部を有し、各壁部は、排油口における半径方向内方の円周方向一側部から、前記排油口における半径方向外方の円周方向他側部に至るようにそれぞれ傾斜すると共に、これら軸方向に並ぶ２つの壁部が互いに交差するように設けられる転がり軸受装置。 6. The barrier according to claim 4, wherein the barrier has two wall portions arranged in the axial direction at the oil discharge port, and each wall portion is a radially inner side portion of the oil discharge port. The rolling bearing device is provided so as to be inclined so as to reach the radially outer side in the circumferential direction at the oil discharge port, and the two wall portions arranged in the axial direction intersect each other.

請求項１ないし請求項７のいずれか１項において、前記第一および第二絞り部の各すきまを、一つの前記転がり軸受における軸受空間内に浸入する潤滑油の油量を抑制するように定めることで潤滑油の撹拌抵抗による軸受の温度上昇を抑制可能とした転がり軸受装置。 In any one of claims 1 to 7, the or-out each to the first and second throttle portion, one suppresses so the amount of lubricating oil entering into the bearing space in the rolling bearing A rolling bearing device that can suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil .

請求項１ないし請求項８のいずれか１項において、工作機械主軸の支持に用いられるものである転がり軸受装置。 9. The rolling bearing device according to claim 1, wherein the rolling bearing device is used for supporting a machine tool spindle.