JP2001165177A - Bearing lubricating device - Google Patents
Bearing lubricating deviceInfo
- Publication number
- JP2001165177A JP2001165177A JP34856399A JP34856399A JP2001165177A JP 2001165177 A JP2001165177 A JP 2001165177A JP 34856399 A JP34856399 A JP 34856399A JP 34856399 A JP34856399 A JP 34856399A JP 2001165177 A JP2001165177 A JP 2001165177A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- slit
- raceway surface
- inner ring
- fumarole
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000001050 lubricating effect Effects 0.000 title claims abstract description 9
- 239000010687 lubricating oil Substances 0.000 claims abstract description 39
- 238000005096 rolling process Methods 0.000 claims abstract description 32
- 239000003921 oil Substances 0.000 claims abstract description 24
- 238000005461 lubrication Methods 0.000 claims abstract description 16
- 239000000446 fuel Substances 0.000 claims description 3
- 238000002347 injection Methods 0.000 claims description 3
- 239000007924 injection Substances 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 abstract description 10
- 238000004891 communication Methods 0.000 description 7
- 238000012986 modification Methods 0.000 description 6
- 230000004048 modification Effects 0.000 description 6
- 238000007664 blowing Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000005422 blasting Methods 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は軸受潤滑装置の技術
分野に属し、特に高速回転のころがり軸受のための油潤
滑装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention belongs to the technical field of bearing lubrication systems, and more particularly to an oil lubrication system for a high-speed rolling bearing.
【０００２】[0002]
【従来の技術】工作機械の主軸のような高速回転する部
位に用いられるころがり軸受は油潤滑される。潤滑剤と
して、グリースは取り扱いは簡単であるが高粘度である
点そして寿命の点で不適であるので、主軸では油潤滑さ
れる。この油潤滑にあっては、潤滑油は過不足のないよ
う適量とされた所定量だけ供給されることが要求され
る。この量は微量なので、確実に軸受の軌道面に送り込
むことが必要である。この潤滑油を軌道面へ向け送り込
む手段としては、ノズルから噴気される空気が用いられ
ていた。従来、潤滑油と空気は、ノズル状の同一管ある
いは別の管で送り込まれていたが、いずれの場合も、こ
れらの管は軸受の周方向の一箇所または数箇所で、側方
から軸受の内部空間へ向け軸線方向に噴射等を行うよう
に配設されていた。2. Description of the Related Art Rolling bearings used in high-speed rotating parts such as a main shaft of a machine tool are oil-lubricated. As a lubricant, grease is oil-lubricated on the main shaft because it is easy to handle but unsuitable for its high viscosity and longevity. In this oil lubrication, it is required that the lubricating oil be supplied in an appropriate amount so as not to be excessive or insufficient. Since this amount is very small, it is necessary to reliably feed it into the raceway surface of the bearing. As a means for sending the lubricating oil toward the raceway surface, air blown from a nozzle has been used. Conventionally, lubricating oil and air have been sent in the same nozzle or another pipe in the form of a nozzle.In either case, these pipes are placed at one or several points in the circumferential direction of the bearing, and the It was arranged so as to perform injection or the like in the axial direction toward the internal space.
【０００３】[0003]
【発明が解決しようとする課題】ころがり軸受の複数の
転動体は保持器により周方向に間隔をもって配置されて
おり、軸受の回転に伴い軌道輪の軌道面上で自転しなが
ら公転走行する。また、潤滑油の送り込みのために軸受
内部空間へ向けられた空気は上記のごとく周方向の一箇
所または数箇所の管から噴気されるジェット状で高速で
あり、上記公転走行せる転動体により断続的に遮られ
る。その結果、高周波の騒音を発し、工作機械の使用環
境を害する。A plurality of rolling elements of a rolling bearing are arranged at intervals in a circumferential direction by a retainer, and revolve while rotating on the raceway surface of a bearing ring as the bearing rotates. In addition, the air directed to the bearing internal space for lubricating oil feeding is high-speed in the form of a jet blown from one or several pipes in the circumferential direction as described above, and is intermittent due to the rolling elements that revolve and run. Obstructed. As a result, high-frequency noise is generated, which impairs the use environment of the machine tool.
【０００４】又、上記のごとく側方から軸受内部空間へ
向け噴射される潤滑油は、当然ながら転動体から離れた
位置から噴射供給される訳であり、転動体が転動する軌
道面からは距離がある。したがって、潤滑油が噴気によ
り供給されても、直接には上記軌道面には達せず、しか
も、高速回転による遠心力により流れが外輪側に変向す
るので、内輪側での潤滑が十分でなくなる場合がある。Further, as described above, the lubricating oil injected from the side toward the bearing internal space is naturally injected and supplied from a position distant from the rolling element, and the lubricating oil is injected from the raceway surface on which the rolling element rolls. There is a distance. Therefore, even if the lubricating oil is supplied by the blast, the lubricating oil does not directly reach the raceway surface, and the flow is diverted to the outer ring side by the centrifugal force due to the high speed rotation, so that the lubrication on the inner ring side becomes insufficient. There are cases.
【０００５】本発明はかかる騒音を低減し、かつ微少量
の潤滑油を確実にかつ均一に軌道面、特に内輪軌道面へ
向け送り込むことのできる軸受潤滑装置を提供すること
を目的とする。An object of the present invention is to provide a bearing lubricating device which can reduce such noise and can surely and uniformly feed a small amount of lubricating oil toward a raceway surface, particularly an inner raceway surface.
【０００６】[0006]
【課題を解決するための手段】本発明に係る軸受潤滑装
置は、ころがり軸受の近傍へ所定量だけ潤滑油を供給す
る給油手段と、上記該給油手段からの潤滑油を軸受内部
へ向け移送せしめる空気を噴出する噴気手段とを有して
いる。According to the present invention, there is provided a bearing lubricating apparatus for supplying a predetermined amount of lubricating oil to the vicinity of a rolling bearing, and transferring the lubricating oil from the lubricating oil toward the inside of the bearing. Blowing means for blowing air.
【０００７】かかる軸受潤滑装置において、本発明で
は、噴気手段は、回転せる内輪の軌道面に臨む位置に半
径方向外方に向けて延びて形成されかつ開口せる噴気ス
リットを有し、該噴気スリットは周方向にほぼ連続して
環状をなしていることを特徴としている。In the bearing lubricating device, in the present invention, the fuze means has a fuze slit formed at a position facing the raceway surface of the rotating inner ring so as to extend outward in the radial direction and open. Are characterized in that they form a ring substantially continuously in the circumferential direction.
【０００８】上記噴気スリットから噴出する空気により
搬送される潤滑油は、噴気スリットの開口から至近距離
に位置せる内輪の軌道面に直接供給される。したがっ
て、供給潤滑油は所定供給量が少量であっても確実に上
記軌道面と転走面に到達する。しかも、上記噴気スリッ
トは半径方向外方に向けて延びているため、高速回転す
る軸受の遠心力によるいわゆるポンプ効果が十分に得ら
れ、内輪の軌道面の潤滑後に潤滑油は効果的に外輪の軌
道面へ到達する。これに加え、噴気スリットは周方向に
ほぼ連続しているので、噴気が転動体により断続的に遮
られるということもないので、そのための音も発生せ
ず、しかも周方向に均一に潤滑油が供給される。[0008] The lubricating oil conveyed by the air spouted from the squirt slit is directly supplied to the raceway surface of the inner race located at a short distance from the opening of the squirt slit. Therefore, the supplied lubricating oil reliably reaches the raceway surface and the rolling surface even if the predetermined supply amount is small. Moreover, since the above-mentioned fumarole slit extends radially outward, a so-called pump effect due to the centrifugal force of the high-speed rotating bearing is sufficiently obtained, and after lubrication of the raceway surface of the inner race, the lubricating oil is effectively formed on the outer race. Reach the orbital plane. In addition, since the fumarole slit is almost continuous in the circumferential direction, the fumarole does not intermittently be interrupted by the rolling elements, so that no sound is generated and lubricating oil is evenly distributed in the circumferential direction. Supplied.
【０００９】本発明の一つの形態としては、噴気スリッ
トは、内輪の軌道面の範囲もしくは該範囲の境界域にて
半径内方に延びて内輪の厚さ方向中間部に至るように形
成され、内輪に軸線方向に延びて該内輪の端部に至る孔
部を経て上記噴気スリットが給油手段及び噴気手段の圧
力源側とが連通しているようにすることができ、かくし
て、上記内輪に形成された孔部を経て、噴気手段による
空気で潤滑油を噴気スリットまで搬送できる。In one embodiment of the present invention, the fumarole slit is formed so as to extend radially inward at a range of the raceway surface of the inner race or at a boundary region of the range to reach an intermediate portion in the thickness direction of the inner race, The squirt slit can communicate with the oil supply means and the pressure source side of the squirt means via a hole extending axially to the inner ring and reaching the end of the inner ring, thus forming the inner ring. The lubricating oil can be conveyed to the gusset slit by the air from the gusset means through the formed hole.
【００１０】又、本発明において、噴気スリットは内輪
内に形成することを要せず、軸方向にて、内輪の一端面
が外輪の一端面とほぼ同位置に、他端面が外輪の軌道面
の範囲に位置して内輪の軌道面の縁をなしているように
形成し、内輪の他端面に対面する位置まで軸受空間内に
進入する進入部を有する側部材を軸受の側方に配し、上
記内輪の他端面と該進入部の対向面との間で噴気スリッ
トを形成することとしても良い。Further, in the present invention, the fumarole slit does not need to be formed in the inner race, and one end surface of the inner race is substantially at the same position as one end surface of the outer race in the axial direction, and the other end surface is a raceway surface of the outer race. A side member having an entrance portion which is formed in the range of and forms an edge of the raceway surface of the inner ring and has an entry portion which enters the bearing space to a position facing the other end surface of the inner ring is arranged on the side of the bearing. A fumed slit may be formed between the other end surface of the inner ring and the facing surface of the entrance portion.
【００１１】本発明において、ころがり軸受が玉軸受で
ある場合には、噴気スリットは転動体の作用線と軌道面
との交点位置以外の部位にて軌道面に開口していること
が望ましい。又、ころがり軸受がころ軸受である場合に
は、噴気スリットは転動体の軌道面の境界域に形成され
た逃げ溝に開口しているようにすることもできる。[0011] In the present invention, when the rolling bearing is a ball bearing, it is desirable that the blast slit is open to the raceway surface at a position other than the intersection between the line of action of the rolling element and the raceway surface. Further, when the rolling bearing is a roller bearing, the blast gas slit may be opened to a relief groove formed in a boundary area of the raceway surface of the rolling element.
【００１２】さらには、本発明においては、噴気手段が
給油手段をも兼ねて給油路を形成しているようにするこ
とも可能である。Further, in the present invention, it is possible that the blast means also serves as a fuel supply means to form a fuel supply passage.
【００１３】[0013]
【発明の実施の形態】以下、添付図面にもとづき、本発
明の実施形態を説明する。Embodiments of the present invention will be described below with reference to the accompanying drawings.
【００１４】図１に示される実施形態は、本発明をアン
ギュラコンタクト型の玉軸受に適用し、給油手段と噴気
手段とを別途に設けた例である。The embodiment shown in FIG. 1 is an example in which the present invention is applied to an angular contact type ball bearing, and an oil supply means and a blast means are separately provided.
【００１５】図１において、軸受１はアンギュラコンタ
クト型の玉軸受の形式として構成さされており、外輪
２、内輪３、両輪２，３間に配されて荷重を支持する複
数の転動体（図示の場合、玉）４、隣接せる二つの転動
体４の間の間隔を定めるための保持器５とを有してい
る。該保持器５は転動体４を収容するポケット５Ａが周
方向に等間隔に形成されていて、該保持器５自体は後述
の外輪の円筒状肩部で案内される。In FIG. 1, a bearing 1 is configured as a type of angular contact type ball bearing, and includes a plurality of rolling elements (shown in FIG. 1) which are arranged between an outer ring 2, an inner ring 3, and both wheels 2 and 3 to support a load. In the case of, the ball) 4 and a retainer 5 for determining an interval between two adjacent rolling elements 4 are provided. The retainer 5 has pockets 5A for accommodating the rolling elements 4 formed at equal intervals in the circumferential direction, and the retainer 5 itself is guided by a cylindrical shoulder portion of an outer ring described later.
【００１６】軸受１は、既述したように、アンギュラコ
ンタクト型であり、転動体４を介して外輪２と内輪３と
の間で荷重を伝達する方向、すなわち、これらの接点で
ある荷重点２Ａ，３Ａを結ぶ直線として得られる作用線
６が軸受軸線１Ａに対して傾いている。As described above, the bearing 1 is of an angular contact type, in which the load is transmitted between the outer ring 2 and the inner ring 3 via the rolling elements 4, that is, the load point 2A, which is the point of contact. , 3A are inclined with respect to the bearing axis 1A.
【００１７】上記外輪２は、軸線１Ａ方向にて上記荷重
点２Ａの両側にほぼ等しく拡がる所定幅の環状面をなす
軌道面７が転動体４の転動のために形成されており、こ
の軌道面７の側部には、テーパ状の肩部８と円筒状の肩
部９が形成されている。既述の保持器５はこの肩部９に
て案内される。The outer race 2 has a raceway surface 7 having an annular surface of a predetermined width which extends substantially equally on both sides of the load point 2A in the direction of the axis 1A, and is formed for rolling of the rolling element 4. On the side of the surface 7, a tapered shoulder 8 and a cylindrical shoulder 9 are formed. The above-mentioned retainer 5 is guided by the shoulder 9.
【００１８】これに対し、一般のものよりも肉厚に作ら
れている内輪３は、上記荷重点３Ａの両側に拡がる環状
面をなす軌道面１０が転動体４の転動のために形成され
ているが、一方の側（図示の場合、左側）が拡く、他方
の側が若干狭くなっている。この軌道面１０の一方の側
には円筒状の肩部１１が、そして他方の側にはテーパ状
の肩部１２が形成されている。On the other hand, in the inner ring 3 which is made thicker than a general one, a raceway surface 10 which forms an annular surface extending on both sides of the load point 3A is formed for rolling of the rolling element 4. However, one side (in the illustrated case, the left side) is enlarged, and the other side is slightly narrowed. The raceway surface 10 has a cylindrical shoulder 11 on one side and a tapered shoulder 12 on the other side.
【００１９】上記内輪３には、軌道面１０とテーパ状の
肩部１２との境界位置に、半径方向内方に切り込まれ周
方向に連続形成された噴気スリット１３と、他方の端面
１４に開口せる周方向に連続せる環状凹部１５とが設け
られており、上記噴気スリット１３と環状凹部１５とは
周方向の複数位置に上記肩部１２と平行に穿設された孔
部１６によって連通されている。At the boundary between the raceway surface 10 and the tapered shoulder portion 12, the inner ring 3 has a fumed slit 13 cut radially inward and continuously formed in the circumferential direction, and a second end surface 14. An annular recess 15 is provided which is continuous in the circumferential direction to be opened. The fumarole slit 13 and the annular recess 15 are communicated with each other at a plurality of positions in the circumferential direction by holes 16 formed in parallel with the shoulder 12. ing.
【００２０】かかる軸受１は、段付の軸体１７上に配さ
れ、ハウジング１８内に収められている。この軸受は、
軸線方向では、内輪３が軸体１７の段部１７Ａとスリー
ブ１８により、そして外輪２がスリーブ１９と側部材２
０によりその位置決めがなされている。これらの部材に
ついては、さらに後述する。The bearing 1 is arranged on a stepped shaft 17 and is housed in a housing 18. This bearing is
In the axial direction, the inner race 3 is formed by the step 17A of the shaft 17 and the sleeve 18, and the outer race 2 is formed by the sleeve 19 and the side member 2
0 indicates the positioning. These members will be further described later.
【００２１】上記側部材２０はハウジング１８の内径面
に嵌合され外輪２の端面に当接せる当接面２１を外径側
に有し、又、内径側には、上記内輪３の環状凹部１５内
へ進入する環状の進入部２２を有している。該進入部２
２は上記内輪３の環状凹部１５の壁面とは隙間を形成し
ている。かかる側部材２０の内周面は、軸方向で内輪３
寄りの範囲で内輪３の方に向けて拡がるテーパ部２０Ａ
と、その反対側の範囲に形成される円筒部２０Ｂとを有
し、両者の境界域に周方向に連続せる二つの環状溝２
３，２４が形成されている。The side member 20 has an abutment surface 21 on the outer diameter side which is fitted to the inner diameter surface of the housing 18 and abuts against the end surface of the outer ring 2. 15 has an annular entrance 22. The approach part 2
2 forms a gap with the wall surface of the annular concave portion 15 of the inner ring 3. The inner peripheral surface of the side member 20 is aligned with the inner race 3 in the axial direction.
The tapered portion 20A that expands toward the inner ring 3 in a range closer to the inner ring 3
And a cylindrical portion 20B formed in a region on the opposite side thereof, and two annular grooves 2 circumferentially continuous with a boundary region between the two.
3, 24 are formed.
【００２２】さらに、上記側部材２０には、外周面の隅
部に段状の環状溝２５Ａが形成されており、該側部材２
０の当接面２１に形成された複数の連通路２６Ａによっ
て軸受内部空間と連通している。一方、ハウジング１８
には周方向の複数位置に上記環状溝２５Ａに連通するド
レーン孔２７Ａが形成されている。かくして、上記連通
路２６Ａ，環状溝２５Ａそしてドレーン孔２７Ａは、潤
滑後の潤滑油のドレーン通路を形成する。又、この側部
材２０と同様に、上記スペーサ１８には、環状溝２５
Ｂ、連通路２６Ｂが形成されていると共に、ハウジング
１８にもドレーン孔２７Ｂが形成されていて、上記連通
路２６Ｂ、環状溝２５Ｂそしてドレーン孔２７Ｂは、潤
滑後の潤滑油のドレーン通路を形成する。Further, the side member 20 has a stepped annular groove 25A formed at the corner of the outer peripheral surface.
The plurality of communication passages 26A formed in the abutment surface 21 communicate with the bearing internal space. Meanwhile, the housing 18
A drain hole 27A communicating with the annular groove 25A is formed at a plurality of positions in the circumferential direction. Thus, the communication passage 26A, the annular groove 25A and the drain hole 27A form a drain passage for lubricating oil after lubrication. Similarly to the side member 20, the spacer 18 is provided with an annular groove 25.
B, a communication passage 26B is formed, and a drain hole 27B is also formed in the housing 18. The communication passage 26B, the annular groove 25B, and the drain hole 27B form a drain passage for lubricating oil after lubrication. .
【００２３】本実施形態において、上記側部材２０の内
周面（テーパ部２０Ａ及び円筒部２０Ｂ）内には、軸体
１７との間に、前出のスリーブ１８が配設されている。
該スリーブ部１８は、その円筒内周面２８にて軸体１７
に対して、しまり嵌めにより一体に嵌着されて該軸体１
７と共に回転する。該スリーブ１８の軸方向の一端は上
記内輪３の上記端面１４に当接している。又、該スリー
ブ１８は、上記側部材２０のテーパ部２０Ａ及び円筒部
２０Ｂと近接して対面する外周面を有し、側部材２０の
間で、周方向につながる環状スリット２９が上記内輪３
の環状空間１６に連通して形成される。そして、上記側
部材２０の環状溝２３，２４の範囲では、潤滑油受入れ
のための周方向につながる環状の受入空間３０、加圧空
気の受入れのための環状の受入空間３１がそれぞれ形成
される。In the present embodiment, the sleeve 18 is disposed between the shaft member 17 and the inner peripheral surface (tapered portion 20A and cylindrical portion 20B) of the side member 20.
The sleeve portion 18 has a shaft 17 on its inner peripheral surface 28.
To the shaft body 1 by tight fit.
Rotate with 7. One end of the sleeve 18 in the axial direction is in contact with the end face 14 of the inner race 3. Further, the sleeve 18 has an outer peripheral surface facing the tapered portion 20A and the cylindrical portion 20B of the side member 20, and an annular slit 29 connected between the side members 20 in the circumferential direction is formed between the inner ring 3 and the inner member 3.
Is formed in communication with the annular space 16. And, in the range of the annular grooves 23 and 24 of the side member 20, an annular receiving space 30 for receiving lubricating oil and an annular receiving space 31 for receiving pressurized air are formed, respectively. .
【００２４】上記ハウジング１８と側部材２０には、周
方向の複数位置に、上記ハウジングの外周面と側部材２
０の内周面に形成された二つの受入空間３０，３１とを
それぞれ連通する貫通孔が形成されており、これらに給
油手段としての給油管３２と送気管３３とがそれぞれ挿
入されている。給油管３２には、図示されていない外部
の給油装置から所定量の潤滑油が送られてくるようにな
っている。又、送気管３３には、外部の圧力源から所定
圧の空気が送り込まれてきて、該空気は環状の受入空間
３３へ達して、ここで周方向に均一に分布するようにな
る。この空気は、上記環状の受入空間３３から環状スリ
ット２９を経て噴気手段として内輪３に形成された噴気
スリット１３から軌道面１０へ噴気される。噴気は、上
記給油管３２から受入空間３０へ供給された所定量（少
量）の潤滑油を搬送し、この潤滑油が、内輪３の軌道面
１０上の転動体４に直接供給され、上記軌道面１０を効
果的に潤滑する。The outer peripheral surface of the housing and the side member 2 are provided at a plurality of positions in the circumferential direction on the housing 18 and the side member 20.
A through hole is formed to communicate the two receiving spaces 30 and 31 formed on the inner peripheral surface of the cylinder 0, and an oil supply pipe 32 and an air supply pipe 33 as oil supply means are inserted into these through holes. A predetermined amount of lubricating oil is sent to the oil supply pipe 32 from an external oil supply device (not shown). Air of a predetermined pressure is supplied from an external pressure source to the air supply pipe 33, and the air reaches the annular receiving space 33, where it is uniformly distributed in the circumferential direction. This air is blown from the annular receiving space 33 through the annular slit 29 to the raceway surface 10 from the blowing slit 13 formed in the inner ring 3 as the blowing means. The flammable gas conveys a predetermined amount (a small amount) of lubricating oil supplied from the oil supply pipe 32 to the receiving space 30, and the lubricating oil is directly supplied to the rolling elements 4 on the raceway surface 10 of the inner race 3, The surface 10 is effectively lubricated.
【００２５】しかる後、高速で回転する軸受の遠心力に
よる、いわゆるポンプ効果のもとで、上記潤滑油は外輪
２側に到達し、ここで、外輪２の軌道面７と転動体４と
の接触部位を潤滑する。その際、潤滑油は、外輪２へ至
る過程において、保持器５をも潤滑し転動体４の保持を
円滑にする。Thereafter, the lubricating oil reaches the outer ring 2 under the so-called pump effect due to the centrifugal force of the bearing rotating at a high speed. Lubricate contact areas. At this time, the lubricating oil also lubricates the retainer 5 in the process of reaching the outer ring 2, so that the rolling element 4 is held smoothly.
【００２６】外輪２を潤滑した後の潤滑油は、一端側か
らは連通路２６Ｂ、環状溝２５Ｂ、ドレーン孔２７Ｂで
形成されるドレーン通路を経て、そして他端側からは連
通路２６Ａ、環状溝２５Ａ、ドレーン孔２７Ａで形成さ
れる他のドレーン通路を経て装置外へ排出される。The lubricating oil after lubricating the outer race 2 passes from one end through a communication passage 26B, an annular groove 25B and a drain passage formed by a drain hole 27B, and from the other end, a communication passage 26A and an annular groove. 25A, and is discharged out of the apparatus through another drain passage formed by the drain hole 27A.
【００２７】多くの場合、軸方向で、両方向の力を受け
るようにするために、図示の軸受は、左右対称にもう一
つ設けられ、共通の給油管３２と送気管３３とによっ
て、噴気スリットから少量の潤滑油を上記と同様にもう
一つの軸受にも供給する。In many cases, another bearing shown is provided symmetrically in order to receive a force in both directions in the axial direction, and a common oil supply pipe 32 and an air supply pipe 33 are used to form a squirt slit. Supplies a small amount of lubricating oil to another bearing in the same manner as above.
【００２８】本発明は、図１に図示された形態には限定
されず、種々変形可能である。以下、図２以降にその変
形例を示すが、各図において図１のものと共通部分には
同一符号を付し、その説明を省略する。先ず、軸受形式
であるが、図１のごとくの玉軸受でなくとも、図２に見
られるようなころ軸受、例えば円筒ころ軸受にも適用可
能である。図示の場合、噴気スリット１３は円筒ころ３
４のための軌道面３５のほぼ中央に位置して形成されて
いる。したがって、潤滑油は確実に上記軌道面３５そし
て円筒ころ３４へ直接到達し、これらを有効に潤滑す
る。この場合、高荷重下で運転される際には、噴気スリ
ット１３の開口縁での応力集中を防止するために、開口
縁に若干の丸味を設ける等の工夫を要する。かかる不利
益を回避するには、軌道面３５の両側端に形成されてい
る小さな逃げ溝３５Ａに連通するように、同図で二点鎖
線で示される位置に噴気スリット１３を位置づけること
も良策である。The present invention is not limited to the embodiment shown in FIG. 1, but can be variously modified. Hereinafter, modified examples are shown in FIG. 2 and subsequent figures. In each figure, the same reference numerals are given to the same parts as those in FIG. 1 and the description thereof is omitted. First, the bearing type is not limited to the ball bearing as shown in FIG. 1, but can be applied to a roller bearing as shown in FIG. 2, for example, a cylindrical roller bearing. In the case shown, the fumarole slit 13 is a cylindrical roller 3
4 is formed substantially at the center of the raceway surface 35. Therefore, the lubricating oil reliably reaches the raceway surface 35 and the cylindrical roller 34 directly, and effectively lubricates them. In this case, when operating under a high load, in order to prevent stress concentration at the opening edge of the fumarole slit 13, some measures such as providing a slight roundness to the opening edge are required. In order to avoid such disadvantages, it is also a good idea to position the fumarole slit 13 at a position shown by a two-dot chain line in FIG. is there.
【００２９】次に、内輪に形成される空気受入のための
環状凹部は、図１のごとく軸受端面に形成された溝状で
なくとも、図３のように角部を切り欠いた段状の環状凹
部１５として形成してもよい。この形態は、図１のよう
な肉厚の内輪を用いることができず図３のような通常の
肉厚の内輪の場合に有効である。すなわち、この環状凹
部１５の奥部の位置に対応する位置に軸体１７に段部１
７Ｂを形成し、この段部１７Ｂに当接するようにスリー
ブ１８を配設すれば、内輪３の強度を過度に低下させる
ことなく、十分に上記環状凹部１５を形成することがで
きる。Next, the annular recess formed in the inner race for receiving air is not limited to the groove formed in the bearing end face as shown in FIG. It may be formed as an annular recess 15. This embodiment is effective in the case of a normal thickness inner ring as shown in FIG. 3 because a thick inner ring as shown in FIG. 1 cannot be used. That is, the step 1 is attached to the shaft 17 at a position corresponding to the position of the back of the annular recess 15.
By forming the sleeve 7B and arranging the sleeve 18 so as to abut the step 17B, the annular recess 15 can be sufficiently formed without excessively reducing the strength of the inner race 3.
【００３０】このような環状凹部１５の位置付けは、円
筒ころ軸受けの場合にも適用できる。図４において、実
線で示される例では噴気スリット１３は軌道面３５のほ
ぼ中央に開口し、二点鎖線で示される例では噴気スリッ
ト１３は逃げ溝３５Ａに開口している。この噴気スリッ
ト１３は、内輪３の角部の段状の環状凹部１５に連通し
ている。図４の形態では、内輪３はテーパ内径面３Ｂを
有しているために、テーパスリーブ３６を介して軸体１
７上に装着されている。The positioning of the annular recess 15 can be applied to the case of a cylindrical roller bearing. In FIG. 4, in the example shown by the solid line, the fumarole slit 13 opens substantially at the center of the raceway surface 35, and in the example shown by the two-dot chain line, the fumarole slit 13 opens in the escape groove 35A. This fumarole slit 13 communicates with a stepped annular concave portion 15 at the corner of the inner ring 3. In the embodiment shown in FIG. 4, the inner ring 3 has the tapered inner diameter surface 3B, so that the shaft 1
7 is mounted.
【００３１】又、上記の環状凹部は内輪を加工して形成
しなくとも可能である。例えば、図５に示すように、内
輪３に当接するスリーブ１８にフランジ部３６を設け、
このフランジ部３６に環状凹部１５及び孔部１６とが形
成され、孔部１６Ａが内輪３の孔部１６を介して噴気ス
リット１３と上記環状凹部１５とを連通している。この
図５の形態は、前出の場合と同様に、図６のごとく円筒
ころ軸受にも適用できる。The above annular recess can be formed without forming the inner ring by machining. For example, as shown in FIG. 5, a flange portion 36 is provided on the sleeve 18 in contact with the inner ring 3,
The annular recess 15 and the hole 16 are formed in the flange portion 36, and the hole 16 </ b> A communicates the fumarole slit 13 with the annular recess 15 via the hole 16 of the inner ring 3. The embodiment of FIG. 5 can be applied to a cylindrical roller bearing as shown in FIG. 6, as in the case described above.
【００３２】さらには、噴気スリットは内輪内部に形成
しなくともよい。図７の形態にあっては、軸受１は図１
と同じアンギュラコンタクト玉軸受であるが、内輪３は
幅寸法が図１のものに比しほぼ半分となっていて、内輪
３の右半分が切り落とされて空間を形成している。この
空間内に、側部材２０の進入部２２及びスリーブ１８が
入り込んできている。上記スリーブ１８の端面は内輪３
の端面１４に当接しており、上記側部材２０の進入部２
２は、その端面（対向面）２２Ａが上記内輪３の端面１
４と近接して噴気スリット１３を形成し、又、この側部
材２０の内周テーパ部２０Ａが上記スリーブ１８の外周
面１８Ａに近接して環状スリット２９を形成している。Further, the fumarole slit need not be formed inside the inner ring. In the embodiment shown in FIG.
1, but the width of the inner ring 3 is substantially half that of FIG. 1, and the right half of the inner ring 3 is cut off to form a space. The entrance portion 22 of the side member 20 and the sleeve 18 have entered this space. The end face of the sleeve 18 is the inner ring 3
The end portion 14 of the side member 20
2 is an end surface (opposing surface) 22A of which is the end surface 1 of the inner ring 3;
The side slit 20 has an inner peripheral tapered portion 20A which is adjacent to the outer peripheral surface 18A of the sleeve 18 to form an annular slit 29.
【００３３】このような状態は、作用線６が傾いている
アンギュラコンタクト型の軸受に有効で、噴気スリット
１３は軸受内に奥深く位置しても、荷重点３Ａから離れ
ており、内輪の切り落しの影響は少ない。Such a state is effective for an angular contact type bearing in which the action line 6 is inclined. Even if the fumarole slit 13 is located deep inside the bearing, it is separated from the load point 3A, and the inner ring is cut off. The effect is small.
【００３４】本発明は図１に示したもの以外にも、種々
変形可能である。図示の例では、給油手段たる給油管
と、噴気手段たる噴気スリットに送気するための送気管
が別経路をなすように形成されていたが、送気手段が給
油手段をも兼ねるように、両手段を一つにまとめること
もできる。かかる形態は、給油管の内壁面を微量潤滑油
が這うように移送される、いわゆるエアーオイル形式の
潤滑装置に好適である。The present invention can be variously modified in addition to the one shown in FIG. In the illustrated example, an oil supply pipe serving as an oil supply means and an air supply pipe for supplying air to a fuze slit serving as an injection means are formed so as to form a separate path, but such that the air supply means also serves as the oil supply means. Both means can be combined into one. This configuration is suitable for a so-called air-oil type lubricating device in which a small amount of lubricating oil is transported along the inner wall surface of the oil supply pipe.
【００３５】[0035]
【発明の効果】以上のように、本発明は、潤滑油を軸受
内部へ送り込むための空気を噴気する噴気手段が内輪の
軌道輪へ直接開口する噴気スリットとして形成されるよ
うにしたので、定められた供給潤滑油量がいかに少量で
も、この潤滑油は直接内輪軌道面を有効的に潤滑し、
又、この潤滑油は内輪の潤滑の後に、軸受の遠心力によ
るポンプ効果のもとに外輪をも確実に潤滑する。供給潤
滑油が少量でも、十分に潤滑できるので、潤滑油の量が
少量でなくてはならない高速回転軸受に効果的である。
又、軸受と同心で周方向にほぼ連続する噴気スリットと
したので、転動体の公転走行によって空気を断続的に遮
断することがなく、従来装置のような高周波騒音が著し
く低下されることとなった。As described above, according to the present invention, the blast means for blasting the air for feeding the lubricating oil into the bearing is formed as a flaming slit which directly opens to the raceway of the inner ring. No matter how small the amount of lubricating oil supplied, this lubricating oil directly and effectively lubricates the inner raceway surface,
After lubrication of the inner ring, the lubricating oil also reliably lubricates the outer ring under the pump effect of the centrifugal force of the bearing. Even if the amount of lubricating oil supplied is small, sufficient lubrication can be achieved, which is effective for high-speed rotary bearings in which the amount of lubricating oil must be small.
In addition, since the fumarole slit is concentric with the bearing and is substantially continuous in the circumferential direction, air does not intermittently shut off due to the revolving running of the rolling element, and high-frequency noise as in the conventional device is significantly reduced. Was.
【図１】本発明の一実施形態としてのアンギュラコンタ
クト玉軸受装置を示す断面図である。FIG. 1 is a sectional view showing an angular contact ball bearing device as one embodiment of the present invention.
【図２】図１の変形例で円筒ころ軸受の場合の断面図で
ある。FIG. 2 is a sectional view of a modification of FIG. 1 in the case of a cylindrical roller bearing.
【図３】図１の装置についての環状凹部の位置の変更例
を示す断面図である。FIG. 3 is a cross-sectional view showing a modification of the position of the annular concave portion in the apparatus of FIG.
【図４】図２の変形例で円筒ころ軸受の場合の断面図で
ある。FIG. 4 is a sectional view of a modification of FIG. 2 in the case of a cylindrical roller bearing.
【図５】図１の装置についての環状凹部の位置の他の変
更例を示す断面図である。FIG. 5 is a sectional view showing another modification of the position of the annular concave portion in the apparatus of FIG. 1;
【図６】図５の変形例で円筒ころ軸受の場合の断面図で
ある。6 is a sectional view of a modification of FIG. 5 in the case of a cylindrical roller bearing.
【図７】図１の装置の噴気スリットについての変形例を
示す断面図である。FIG. 7 is a cross-sectional view showing a modification of the fumarole slit of the apparatus of FIG. 1;
１ ころがり軸受 ２ 外輪 ３ 内輪 ４ 転動体（玉） ６ 作用線 ７ 外輪の軌道面 １０ 内輪の軌道面 １３ 噴気手段（噴気スリット） １４ 内輪の端部（端面） １６ 孔部 ２０ 側部材 ２２ 進入部 ２２Ａ 対向面（端面） ３２ 給油手段（給油管） ３４ 転動体（円筒ころ） ３５Ａ 逃げ溝 DESCRIPTION OF SYMBOLS 1 Roller bearing 2 Outer ring 3 Inner ring 4 Rolling element (ball) 6 Action line 7 Outer ring raceway surface 10 Inner ring raceway surface 13 Fumarolic means (Flare slit) 14 Inner ring end (end surface) 16 Hole 20 Side member 22 Entry portion 22A Opposing surface (end surface) 32 Oil supply means (oil supply pipe) 34 Rolling element (cylindrical roller) 35A Relief groove
Claims (6)
を供給する給油手段と、上記該給油手段からの潤滑油を
軸受内部へ向け移送せしめる空気を噴出する噴気手段と
を有する軸受潤滑装置において、噴気手段は、回転せる
内輪の軌道面に臨む位置に半径方向外方に向けて延びて
形成されかつ開口せる噴気スリットを有し、該噴気スリ
ットは周方向にほぼ連続して環状をなしていることを特
徴とする軸受潤滑装置。1. A bearing lubrication system comprising: an oil supply means for supplying a predetermined amount of lubricating oil to a vicinity of a rolling bearing; and a blast means for jetting air for transferring the lubricating oil from the oil supply means to the inside of the bearing. The fumarole means has a fumarole slit extending radially outward at a position facing the raceway surface of the rotating inner race and having an opening, and the fumarile slit forms an annular shape substantially continuously in the circumferential direction. A bearing lubrication device.
しくは該範囲の境界域にて半径内方に延びて内輪の厚さ
方向中間部に至るように形成され、内輪に軸線方向に延
びて該内輪の端部に至る孔部を経て上記噴気スリットが
給油手段及び噴気手段の圧力源側とが連通していること
とする請求項１に記載の軸受潤滑装置。2. A fumarole slit is formed so as to extend radially inward in a range of a raceway surface of an inner race or a boundary region of the range so as to reach an intermediate portion in a thickness direction of the inner race. 2. The bearing lubrication device according to claim 1, wherein said gusset slit communicates with the oil supply means and the pressure source side of the gusset means via a hole reaching the end of said inner ring.
端面とほぼ同位置に、他端面が外輪の軌道面の範囲に位
置して内輪の軌道面の縁をなしており、内輪の他端面に
対面する位置まで軸受空間内に進入する進入部を有する
側部材を軸受の側方に配し、上記内輪の他端面と該進入
部の対向面との間で噴気スリットを形成していることと
する請求項１に記載の軸受潤滑装置。3. The inner ring has one end face located substantially at the same position as the one end face of the outer ring and the other end face located in the range of the raceway surface of the outer ring in the axial direction, and forms an edge of the raceway surface of the inner ring. A side member having an entry portion that enters the bearing space up to a position facing the other end surface of the inner ring is arranged on the side of the bearing, and a fumarole slit is formed between the other end surface of the inner ring and a facing surface of the entry portion. The bearing lubrication device according to claim 1, wherein
ットは転動体の作用線と軌道面との交点位置以外の部位
にて軌道面に開口していることとする請求項１ないし請
求項３のうちの一つに記載の軸受潤滑装置。4. The rolling bearing is a ball bearing, and the fumarole slit is open to the raceway surface at a position other than the intersection between the action line of the rolling element and the raceway surface. A bearing lubrication device according to one of the preceding claims.
リットは転動体の軌道面の境界域に形成された逃げ溝に
開口していることとする請求項１又は請求項２に記載の
軸受潤滑装置。5. The bearing lubrication according to claim 1, wherein the rolling bearing is a roller bearing, and the fumarole slit is opened in a clearance groove formed in a boundary area of the raceway surface of the rolling element. apparatus.
形成していることとする請求項１又は請求項２に記載の
軸受潤滑装置。6. The bearing lubricating device according to claim 1, wherein the fuel injection means also serves as an oil supply means to form an oil supply passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34856399A JP2001165177A (en) | 1999-12-08 | 1999-12-08 | Bearing lubricating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34856399A JP2001165177A (en) | 1999-12-08 | 1999-12-08 | Bearing lubricating device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2001165177A true JP2001165177A (en) | 2001-06-19 |
Family
ID=18397870
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP34856399A Pending JP2001165177A (en) | 1999-12-08 | 1999-12-08 | Bearing lubricating device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2001165177A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6733181B2 (en) | 2000-10-27 | 2004-05-11 | Nsk Ltd. | Bearing unit |
| JP2006022865A (en) * | 2004-07-07 | 2006-01-26 | Koyo Seiko Co Ltd | Lubricant supply device for bearing |
| EP1903230A1 (en) * | 2006-09-25 | 2008-03-26 | Jtekt Corporation | Rolling bearing apparatus |
| JP2008240938A (en) * | 2007-03-28 | 2008-10-09 | Ntn Corp | Lubrication device for rolling bearing |
| JP2014062619A (en) * | 2012-09-24 | 2014-04-10 | Ntn Corp | Cooling structure of bearing device |
| US9541137B2 (en) | 2012-09-24 | 2017-01-10 | Ntn Corporation | Cooling structure for bearing device |
| CN108412903A (en) * | 2018-05-22 | 2018-08-17 | 张家港汉升机械科技有限公司 | A kind of bearing with self-lubricating and dust reduction capability |
-
1999
- 1999-12-08 JP JP34856399A patent/JP2001165177A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6733181B2 (en) | 2000-10-27 | 2004-05-11 | Nsk Ltd. | Bearing unit |
| JP2006022865A (en) * | 2004-07-07 | 2006-01-26 | Koyo Seiko Co Ltd | Lubricant supply device for bearing |
| JP4569747B2 (en) * | 2004-07-07 | 2010-10-27 | 株式会社ジェイテクト | Lubricant supply device for bearings |
| EP1903230A1 (en) * | 2006-09-25 | 2008-03-26 | Jtekt Corporation | Rolling bearing apparatus |
| US8529134B2 (en) | 2006-09-25 | 2013-09-10 | Jtekt Corporation | Rolling bearing apparatus |
| JP2008240938A (en) * | 2007-03-28 | 2008-10-09 | Ntn Corp | Lubrication device for rolling bearing |
| JP2014062619A (en) * | 2012-09-24 | 2014-04-10 | Ntn Corp | Cooling structure of bearing device |
| US9541137B2 (en) | 2012-09-24 | 2017-01-10 | Ntn Corporation | Cooling structure for bearing device |
| US10280980B2 (en) | 2012-09-24 | 2019-05-07 | Ntn Corporation | Cooling structure for bearing device |
| CN108412903A (en) * | 2018-05-22 | 2018-08-17 | 张家港汉升机械科技有限公司 | A kind of bearing with self-lubricating and dust reduction capability |
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