JP2005219154A - Seal structure of spindle device - Google Patents

Seal structure of spindle device Download PDF

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Publication number
JP2005219154A
JP2005219154A JP2004028801A JP2004028801A JP2005219154A JP 2005219154 A JP2005219154 A JP 2005219154A JP 2004028801 A JP2004028801 A JP 2004028801A JP 2004028801 A JP2004028801 A JP 2004028801A JP 2005219154 A JP2005219154 A JP 2005219154A
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Prior art keywords
bearing
spacer
annular
ball bearing
outer ring
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JP4764605B2 (en
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Yoshimi Sato
好美 佐藤
Hisashi Kobayashi
久志 小林
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Okamoto Machine Tool Works Ltd
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Okamoto Machine Tool Works Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • 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
    • F16C2322/00—Apparatus used in shaping articles
    • F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
  • Turning (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a seal structure extending a service life by extremely reducing infiltration of a machining fluid into a labyrinth of a bearing of a spindle device. <P>SOLUTION: The spindle device is formed of a spindle 1 with a rotary tool 2 stuck to the tip by a flange 3, and a ball bearing 9 provided at a bearing storage part 5 of a housing 4. The seal structure of the spindle device is provided with the labyrinth formed of an annular outer ring pressing spacer 10 clamping an outer ring end face 6a of the ball bearing 9, and an annular inner ring pressing spacer 11 clamping an inner ring end face of the ball bearing 9. Even if a grinding fluid sticks to the inner ring clamping spacer 11 of the ball bearing 9, the grinding fluid is scattered outward from a bearing part through a spiral groove 11d and a groove 11f of the inner ring clamping spacer 11 by the centrifugal force of rotation of the spindle. Opportunities of the grinding fluid infiltrating into the labyrinth of the bearing 9 are thereby reduced. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、研削装置や切削装置等の主軸装置のシ−ル構造に関する。特に、主軸装置の軸受の寿命が長いオイルシ−ル構造に関する。   The present invention relates to a seal structure of a spindle device such as a grinding device or a cutting device. In particular, the present invention relates to an oil seal structure having a long bearing life of a spindle device.

研削装置や切削装置等の工作機械の主軸装置１００としては、図５に示すように、回転工具（例えば砥石車）２をフランジ３により先端に固着した主軸１をハウジング４の軸受収容部５に配置された複数の玉８を設けた玉軸受９に軸受し、この玉軸受９の回転工具側を締付けナット１１で蓋をし、前記主軸１を図示されていないモ−タで駆動する構造が一般的に採られている。図５中、１６はシ−リングスリ−ブ、１７は工具締付ナット、１８は安全カバ−である。   As a spindle device 100 of a machine tool such as a grinding device or a cutting device, as shown in FIG. 5, a spindle 1 having a rotary tool (for example, a grinding wheel) 2 fixed to a tip by a flange 3 is attached to a bearing housing portion 5 of a housing 4. The ball bearing 9 is provided with a plurality of balls 8 arranged, the rotating tool side of the ball bearing 9 is covered with a tightening nut 11, and the spindle 1 is driven by a motor (not shown). Generally adopted. In FIG. 5, 16 is a sealing sleeve, 17 is a tool clamping nut, and 18 is a safety cover.

玉軸受には、主軸の回転を円滑にするため、グリ−ス等の潤滑油が供給される。玉軸受内に供給された潤滑油が回転工具側外部に漏れないよう玉軸受を構成する外輪と内輪と玉から形成される空間に外輪端面の軌道面から内輪の軌道面に向けてシ−ル材を設けたラビリンス構造によるオイルシ−ルド機構が採られている。例えば、図４に示すように、オイルシ−ルド機構を有するアンギュラ玉軸受１１１として、内周の軸方向略中央に軌道面１１２ａを有すると共に前記軌道面の軸方向片側の内径面にカウンタボア１１２ｂを備えた外輪１１２と、外周に軌道面１１３ａを有する内輪１１３と、前記外輪１１２の軌道面と内輪１１３の軌道面との間に転動自在に配置された複数の玉１１４と、これらの玉を周方向において所定間隔に保持する保持器１１５とを具備するアンギュラ玉軸受１１１において、前記外輪１１２のカウンタボア側の内径面１１２ｂに装着され、前記保持器の外周面との間でラビリンスを形成するシ−ル１１６を設けたアンギュラ玉軸受が提案されている（例えば、特許文献１参照。）。
また、軸受の外輪端面と主軸装置の締付けナット間にオイルリングを用いてオイルシ−ルする主軸装置も通常、使用されている。
特開２００２−２６６８８３号公報 The ball bearing is supplied with lubricating oil such as grease in order to smoothly rotate the main shaft. Sealing from the raceway surface of the outer ring end surface to the raceway surface of the inner ring in the space formed by the outer ring, the inner ring and the ball constituting the ball bearing so that the lubricating oil supplied into the ball bearing does not leak to the outside of the rotary tool side An oil shield mechanism with a labyrinth structure provided with materials is employed. For example, as shown in FIG. 4, as an angular ball bearing 111 having an oil shield mechanism, a raceway surface 112a is provided at the substantially axial center of the inner circumference, and a counter bore 112b is provided on an inner diameter surface on one axial side of the raceway surface. The outer ring 112 provided, the inner ring 113 having a raceway surface 113a on the outer periphery, a plurality of balls 114 arranged to roll between the raceway surface of the outer ring 112 and the raceway surface of the inner ring 113, and these balls In an angular ball bearing 111 having a retainer 115 that is held at a predetermined interval in the circumferential direction, it is mounted on an inner diameter surface 112b on the counter bore side of the outer ring 112 and forms a labyrinth with the outer periphery surface of the retainer. An angular ball bearing provided with a seal 116 has been proposed (see, for example, Patent Document 1).
In addition, a spindle device that uses an oil ring between the outer ring end face of the bearing and a tightening nut of the spindle device is usually used.
JP 2002-266883 A

前記特許文献１に記載されるオイルシ−ル構造を有する主軸装置や従来使用されているアンギュラ軸受を用いている主軸装置を含め、オイルシ−ルの効果は十分である。しかし、主軸に回転工具を取り付け、ワ−クと回転工具間の加工点に研削液や切削液等の加工液を供給してワ−クを機械加工するに用いる主軸装置においては、加工点に供給された加工液がラビリンスの隙間を伝わって軸受内に侵入し、また、加工液が加工屑を含んで侵入することもあり、軸受の寿命を縮小するため、１〜２年で軸受を交換する必要があった。本発明は、軸受のラビリンスへの加工液の侵入が極めて減少する主軸装置のシ−ル構造を提供し、軸受の寿命を３〜５年と長くすることを目的とする。   The effect of the oil seal is sufficient, including the main shaft device having the oil seal structure described in Patent Document 1 and the main shaft device using a conventionally used angular bearing. However, in a spindle device used for machining a workpiece by attaching a rotary tool to the spindle and supplying a machining fluid such as grinding fluid or cutting fluid to the machining point between the workpiece and the rotary tool, Replace the bearing in 1 to 2 years in order to reduce the life of the bearing because the supplied machining fluid may enter the bearing through the gap in the labyrinth, and the machining fluid may also enter the machining waste. There was a need to do. An object of the present invention is to provide a seal structure of a main shaft device in which the penetration of machining fluid into the labyrinth of a bearing is extremely reduced, and an object of the present invention is to extend the life of the bearing to 3 to 5 years.

請求項１の発明は、回転工具２をフランジ３により先端に固着した主軸１、該主軸のハウジング４の軸受収容部５に外輪６の内部軌道面６ｂと内輪７の内部軌道面７ｂ間に転動自在に配置された複数の玉８を設けた玉軸受９、前記玉軸受９の外輪端面６ａを締付ける環状の外輪押さえ間座１０、外周に螺旋状ネジ溝１１ｄを設けた外周環状体１１ａと内側の内周環状体１１ｂとで中央に主軸１を通す円筒状空間１１ｃを有する円環状筒体を成し、この円環状筒体の裏面に前記外周環状体１１ａと内周環状体１１ｂとで前記外輪押さえ間座１０を収納する環状凹部１１ｅを形成し、かつ、この円環状筒体の表側に表部の途中から外周に通じる溝１１ｆが設けられている内輪締付間座１１、および、前記玉軸受９の外輪６の内部軌道面と内輪７の内部軌道面と前記外輪押さえ間座１０で形成されるラビリンス１２とを備えることを特徴とする主軸装置のシ−ル構造を提供するものである。   According to the first aspect of the present invention, the main shaft 1 having the rotary tool 2 fixed to the tip thereof by the flange 3 and the bearing receiving portion 5 of the housing 4 of the main shaft are transferred between the inner raceway surface 6 b of the outer ring 6 and the inner raceway surface 7 b of the inner ring 7. A ball bearing 9 provided with a plurality of balls 8 movably arranged, an annular outer ring holding spacer 10 for tightening the outer ring end face 6a of the ball bearing 9, an outer ring body 11a provided with a helical thread groove 11d on the outer circumference; An annular cylindrical body having a cylindrical space 11c through which the main shaft 1 passes is formed in the center with the inner circumferential annular body 11b, and the outer circumferential annular body 11a and the inner circumferential annular body 11b are formed on the back surface of the annular cylindrical body. An inner ring tightening spacer 11 that forms an annular recess 11e that accommodates the outer ring holding spacer 10 and is provided with a groove 11f that leads to the outer periphery from the middle of the front portion on the front side of the annular cylindrical body; and The inner raceway surface of the outer ring 6 of the ball bearing 9 and the inner ring 7 Shi spindle device, characterized in that it comprises parts raceway surface and with said labyrinth 12 formed by the outer ring retainer spacers 10 - is intended to provide a Le structure.

回転工具２とワ−クが接する加工点に供給された研削液が飛散して軸受９側に付着しても、研削液は軸受９の内輪締付間座１１の外周に設けられた螺旋状ネジ溝１１ｄを伝わって回転工具２の裏面側へと主軸１の回転による遠心力により戻され、螺旋状ネジ溝１１ｄの先端に到ると主軸１の回転による遠心力により主軸から遠ざかる外方へ飛散される。また、内輪締付間座１１の表側（回転工具側）に付着した研削液は、表面を伝わって外周に通じる溝１１ｆに貯られ、主軸１の回転による遠心力により主軸から遠ざかる外方へ飛散される。よって、ラビリンス１２への研削液の侵入がない、または侵入の機会が極めて少なくなるので軸受の寿命を長くすることができる。   Even if the grinding fluid supplied to the machining point where the rotary tool 2 and the workpiece are in contact is scattered and adheres to the bearing 9 side, the grinding fluid is spirally provided on the outer periphery of the inner ring tightening spacer 11 of the bearing 9. It is returned to the back side of the rotary tool 2 by the centrifugal force due to the rotation of the main shaft 1 through the screw groove 11d, and outwards away from the main shaft by the centrifugal force due to the rotation of the main shaft 1 when reaching the tip of the helical screw groove 11d. Be scattered. In addition, the grinding fluid adhering to the front side (rotary tool side) of the inner ring tightening spacer 11 is stored in a groove 11f that travels along the surface and communicates with the outer periphery, and scatters outward away from the main shaft due to centrifugal force due to the rotation of the main shaft 1. Is done. Therefore, there is no penetration of the grinding fluid into the labyrinth 12, or the chance of entry is extremely reduced, so the life of the bearing can be extended.

（実施例）
以下、図を用いて本発明をさらに詳細に説明する。
図１は本発明の主軸装置軸受部のシ−ル構造を示す断面図、図２は内輪締付間座の断面図、および図３は内輪締付間座を回転工具側から見た正面図である。 (Example)
Hereinafter, the present invention will be described in more detail with reference to the drawings.
1 is a cross-sectional view showing a seal structure of a spindle device bearing portion of the present invention, FIG. 2 is a cross-sectional view of an inner ring tightening spacer, and FIG. 3 is a front view of the inner ring tightening spacer as viewed from the rotary tool side. It is.

図１に示す主軸装置１００において、１は主軸、２は回転工具、３はフランジ、４はハウジング、５は軸受収容部、６は外輪、６ａは外輪端面、６ｂは外輪内部軌道面、７は内輪、７ｂは内輪内部軌道面、８は玉、９は玉軸受、１０は環状の外輪押さえ間座で前記玉軸受９の外輪端面６ａを締付ける。１１は内輪締付間座、１２はラビリンスで前記玉軸受９の外輪６の内部軌道面と内輪７の内部軌道面と前記外輪押さえ間座１０で形成される。１３は締付けボルト、１４は押さえ蓋、１７は締付けナットである。   In the spindle device 100 shown in FIG. 1, 1 is a spindle, 2 is a rotary tool, 3 is a flange, 4 is a housing, 5 is a bearing housing, 6 is an outer ring, 6a is an end surface of the outer ring, 6b is an inner raceway surface of the outer ring, and 7 is An inner ring, 7b is an inner ring inner raceway surface, 8 is a ball, 9 is a ball bearing, and 10 is an annular outer ring holding spacer to fasten the outer ring end surface 6a of the ball bearing 9. Reference numeral 11 denotes an inner ring tightening spacer, and 12 is a labyrinth formed by the inner raceway surface of the outer ring 6 of the ball bearing 9, the inner raceway surface of the inner ring 7, and the outer ring holding spacer 10. 13 is a tightening bolt, 14 is a pressing lid, and 17 is a tightening nut.

図２および図３に示されるように、内輪締付間座１１は、外周に螺旋状ネジ溝１１ｄを設けた外周環状体１１ａと内側の内周環状体１１ｂとで中央に主軸１を通す円筒状空間１１ｃを有する円環状筒体を成し、この円環状筒体の裏面に前記外周環状体１１ａと内周環状体１１ｂとで前記外輪押さえ間座１０を収納する環状凹部１１ｅを形成し、かつ、この円環状筒体の表側（回転工具側に対向する前側）に表部の途中から外周に通じる複数の溝１１ｆが設けられている。外周環状体１１ａと内周環状体１１ｂは段部１１ｇで一体化されており、この段部１１ｇは前記環状凹部１１ｅを形成する。前記外周環状体１１ａの外周には表面から裏面に到る螺旋状ネジ１１ｄが例えばピッチ間隔１〜３ｍｍのネジ山で設けられている。   As shown in FIG. 2 and FIG. 3, the inner ring tightening spacer 11 is a cylinder through which the main shaft 1 passes in the center by an outer peripheral annular body 11a provided with a helical thread groove 11d on the outer periphery and an inner inner peripheral annular body 11b. An annular cylindrical body having an annular space 11c is formed, and an annular recess 11e for accommodating the outer ring holding spacer 10 is formed on the back surface of the annular cylindrical body with the outer circumferential annular body 11a and the inner circumferential annular body 11b; In addition, a plurality of grooves 11f that communicate with the outer periphery from the middle of the front portion are provided on the front side (front side facing the rotary tool side) of the annular cylindrical body. The outer peripheral annular body 11a and the inner peripheral annular body 11b are integrated by a step portion 11g, and this step portion 11g forms the annular recess 11e. A spiral screw 11d extending from the front surface to the back surface is provided on the outer periphery of the outer peripheral ring body 11a, for example, with a thread pitch of 1 to 3 mm.

図３に示すように、内輪締付間座１１の表側には表部の途中から外周に通じる３本の直線状溝１１ｆが設けられている。この溝１１ｆは、その出口と内輪締付間座１１の軸心Ｏを結ぶ線と、溝１１ｆの出口と溝の中心線を結ぶ交差角度αが３０度となるように設けられている。この溝１１ｆは、線対称または点対称に２〜８本としてもよい。また直線状であっても波状あるいは弧状であってもよい。溝１１ｆの深さは１〜５ｍｍ、溝幅は２〜８ｍｍで、溝の方向は、溝１１ｆの出口と溝の中心線を結ぶ交差角度αが３０〜６０度となるように設ける。図２に示す高さが２０ｍｍの内輪締付間座１１は、外周環状体１１ａの外径が９０ｍｍ、内径が８０ｍｍ、高さ５ｍｍ、内周環状体１１ｂの外径が７０ｍｍ、内径（円筒状空間の外径でもある）が５０ｍｍ、高さ１０ｍｍ、段部１１ｇの外径が８０ｍｍ、内径が７０ｍｍのものである。 As shown in FIG. 3, on the front side of the inner ring tightening spacer 11, there are provided three linear grooves 11f that lead from the middle of the front part to the outer periphery. The groove 11f is provided so that the intersection angle α connecting the outlet and the axis O of the inner ring tightening spacer 11 and the outlet of the groove 11f and the center line of the groove is 30 degrees. The number of the grooves 11f may be 2 to 8 in line symmetry or point symmetry. Further, it may be linear, wavy or arcuate. The depth of the groove 11f is 1 to 5 mm, the groove width is 2 to 8 mm, and the direction of the groove is set so that the intersection angle α connecting the outlet of the groove 11f and the center line of the groove is 30 to 60 degrees. The inner ring tightening spacer 11 having a height of 20 mm shown in FIG. 2 has an outer circumferential ring body 11a having an outer diameter of 90 mm, an inner diameter of 80 mm, a height of 5 mm, an inner circumferential ring body 11b having an outer diameter of 70 mm, and an inner diameter (cylindrical shape). The outer diameter of the space is 50 mm, the height is 10 mm, the outer diameter of the step portion 11g is 80 mm, and the inner diameter is 70 mm.

回転工具２、例えば砥石とワ−クが接する加工点に供給された研削液が飛散して軸受９側に付着しても、研削液は軸受９の内輪締付間座１１の外周に設けられた螺旋状ネジ溝１１ｄを伝わって回転工具２の裏面側へと主軸１の回転による遠心力により戻され、螺旋状ネジ溝１１ｄの先端に到ると主軸１の回転による遠心力により主軸から遠ざかる外方へ飛散される。また、内輪締付間座１１の表側（回転工具側）に付着した研削液は、表面を伝わって外周に通じる溝１１ｆに貯られ、主軸１の回転による遠心力により主軸から遠ざかる外方へ飛散される。よって、ラビリンス１２への研削液の侵入がない、または侵入の機会が極めて少なくなるので軸受の寿命を向上することができる。   Even if the grinding fluid supplied to the processing point where the rotary tool 2, for example, the grindstone and the workpiece contact, scatters and adheres to the bearing 9 side, the grinding fluid is provided on the outer periphery of the inner ring tightening spacer 11 of the bearing 9. The spiral screw groove 11d is transmitted back to the back side of the rotary tool 2 by the centrifugal force due to the rotation of the main shaft 1, and when it reaches the tip of the spiral screw groove 11d, it is moved away from the main shaft by the centrifugal force due to the rotation of the main shaft 1. It is scattered outward. In addition, the grinding fluid adhering to the front side (rotary tool side) of the inner ring tightening spacer 11 is stored in a groove 11f that travels along the surface and communicates with the outer periphery, and is scattered outwardly away from the main shaft by centrifugal force due to the rotation of the main shaft 1. Is done. Therefore, since the grinding fluid does not enter the labyrinth 12 or the opportunity for intrusion becomes extremely small, the life of the bearing can be improved.

本発明の主軸装置軸受部のシ−ル構造を示す断面図である。It is sectional drawing which shows the seal structure of the spindle apparatus bearing part of this invention. 内輪締付間座の断面図である。It is sectional drawing of an inner ring clamping spacer. 内輪締付間座を表側から見た正面図である。It is the front view which looked at the inner ring fastening spacer from the front side. アンギュラ軸受のシ−ル構造を示す断面図である（公知）。It is sectional drawing which shows the seal structure of an angular bearing (known). 主軸装置の断面図である（公知）。It is sectional drawing of a main shaft apparatus (known).

符号の説明Explanation of symbols

１ 主軸
１００ 主軸装置
２ 回転工具
３ フランジ
４ ハウジング
５ 軸受収容部
６ 外輪
７ 内輪
８ 玉
９ 玉軸受
１０ 外輪押さえ間座
１１ 内輪締付間座
１１ｄ 螺旋状ネジ
１１ｆ 溝
１２ ラビリンス
１４ 押さえ蓋 DESCRIPTION OF SYMBOLS 1 Main axis | shaft 100 Main axis | shaft apparatus 2 Rotating tool 3 Flange 4 Housing 5 Bearing accommodating part 6 Outer ring 7 Inner ring 8 Ball 9 Ball bearing 10 Outer ring press spacer 11 Inner ring clamp spacer 11d Spiral screw 11f Groove 12 Labyrinth 14 Press cover

Claims (1)

回転工具２をフランジ３により先端に固着した主軸１、該主軸のハウジング４の軸受収容部５に外輪６の内部軌道面６ｂと内輪７の内部軌道面７ｂ間に転動自在に配置された複数の玉８を設けた玉軸受９、前記玉軸受９の外輪端面６ａを締付ける環状の外輪押さえ間座１０、外周に螺旋状ネジ溝１１ｄを設けた外周環状体１１ａと内側の内周環状体１１ｂとで中央に主軸１を通す円筒状空間１１ｃを有する円環状筒体を成し、この円環状筒体の裏面に前記外周環状体１１ａと内周環状体１１ｂとで前記外輪押さえ間座１０を収納する環状凹部１１ｅを形成し、かつ、この円環状筒体の表側に表部の途中から外周に通じる溝１１ｆが設けられている内輪締付間座１１、および、前記玉軸受９の外輪６の内部軌道面と内輪７の内部軌道面と前記外輪押さえ間座１０で形成されるラビリンス１２、とを備えることを特徴とする、主軸装置のシ−ル構造。   A plurality of main shafts 1 each having a rotary tool 2 fixed to the tip thereof by a flange 3 and a plurality of bearings 5 in a housing 4 of the main shaft that are rotatably disposed between the inner raceway surface 6b of the outer ring 6 and the inner raceway surface 7b of the inner ring 7. A ball bearing 9 provided with a ball 8; an annular outer ring holding spacer 10 for tightening an outer ring end face 6a of the ball bearing 9; an outer peripheral annular body 11a provided with a helical thread groove 11d on the outer periphery; and an inner inner annular body 11b. And an annular cylindrical body having a cylindrical space 11c through which the main shaft 1 passes in the center, and the outer ring holding spacer 10 is formed on the back surface of the annular cylindrical body by the outer circumferential annular body 11a and the inner circumferential annular body 11b. An inner ring tightening spacer 11 having an annular recess 11e to be accommodated and provided with a groove 11f leading from the middle of the front part to the outer periphery on the front side of the annular cylindrical body, and the outer ring 6 of the ball bearing 9 Inner raceway surface, inner raceway inner raceway surface and the outer Labyrinth 12 is formed by pressing spacer 10, characterized in that it comprises the city, the spindle device sheet - le structure.
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103953652A (en) * 2014-04-25 2014-07-30 中国重型机械研究院股份公司 Eccentric bearing seal sleeve and assemblies thereof
CN106272046A (en) * 2016-09-14 2017-01-04 航天精工股份有限公司 The aligning device of grinding bearing filling slot and to correction method
CN114714531A (en) * 2022-05-06 2022-07-08 无锡阳光精机股份有限公司 High-speed and long-life spindle box for high-end equipment

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4618061Y1 (en) * 1967-11-27 1971-06-23
JPH08168202A (en) * 1994-12-16 1996-06-25 Toshiba Corp Bearing lubricating oil leakage preventing device
JPH08312557A (en) * 1995-03-13 1996-11-26 Mitsubishi Heavy Ind Ltd Compressor
JPH11277362A (en) * 1998-03-30 1999-10-12 Toyo Advanced Technologies Co Ltd Sealing structure

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4618061Y1 (en) * 1967-11-27 1971-06-23
JPH08168202A (en) * 1994-12-16 1996-06-25 Toshiba Corp Bearing lubricating oil leakage preventing device
JPH08312557A (en) * 1995-03-13 1996-11-26 Mitsubishi Heavy Ind Ltd Compressor
JPH11277362A (en) * 1998-03-30 1999-10-12 Toyo Advanced Technologies Co Ltd Sealing structure

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103953652A (en) * 2014-04-25 2014-07-30 中国重型机械研究院股份公司 Eccentric bearing seal sleeve and assemblies thereof
CN106272046A (en) * 2016-09-14 2017-01-04 航天精工股份有限公司 The aligning device of grinding bearing filling slot and to correction method
CN114714531A (en) * 2022-05-06 2022-07-08 无锡阳光精机股份有限公司 High-speed and long-life spindle box for high-end equipment

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