JPH0746450Y2 - Spindle bearing cooling structure - Google Patents
Spindle bearing cooling structureInfo
- Publication number
- JPH0746450Y2 JPH0746450Y2 JP862690U JP862690U JPH0746450Y2 JP H0746450 Y2 JPH0746450 Y2 JP H0746450Y2 JP 862690 U JP862690 U JP 862690U JP 862690 U JP862690 U JP 862690U JP H0746450 Y2 JPH0746450 Y2 JP H0746450Y2
- Authority
- JP
- Japan
- Prior art keywords
- main shaft
- flow path
- bearing
- cylinder
- hole
- 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.)
- Expired - Fee Related
Links
Landscapes
- Auxiliary Devices For Machine Tools (AREA)
Description
【考案の詳細な説明】 産業上の利用分野 本考案は工作機械の主軸軸受の冷却構造に関する。The present invention relates to a cooling structure for a main shaft bearing of a machine tool.
従来の技術 工作機械の主軸は益々高速回転される傾向にあるが、高
速専用ではなく低速域も使用可能のように低速回転も必
要である。このため軸受の隙間調整には給油方式ととも
に設計者の頭をつかうところである。高速回転時の軸受
の発熱はかなり大きな値であり精度を維持するためには
冷却が不可欠である。このため種々の冷却手段がとられ
ているが一般には外輪を冷却するようになされたものが
圧倒的に多く知られており、内輪を冷却するものには例
えば実開平1-85528号がある。2. Description of the Related Art Spindles of machine tools tend to rotate at higher speeds, but low-speed rotation is also necessary so that low-speed regions can be used instead of high-speed dedicated ones. For this reason, the designer's head should be used along with the oil supply system for adjusting the bearing clearance. The heat generated by the bearing during high-speed rotation is quite large, and cooling is essential to maintain accuracy. For this reason, various cooling means have been taken, but it is generally known that the outer ring is generally cooled, and the inner ring is, for example, Japanese Utility Model Publication No. 1-85528.
考案が解決しようとする課題 このため低速回転時に適当な隙間に調整しておくと高速
回転時には過小隙間となり発熱が大きく焼付現象が発生
する。逆に高速回転時に適当な隙間に調整されていれば
低速回転時に過大隙間となり重切削，精密切削共に不能
となる問題がある。For this reason, if an appropriate gap is adjusted at low speed rotation, an excessively small gap will be generated at high speed rotation, resulting in large heat generation and a seizure phenomenon. On the other hand, if the clearance is adjusted to an appropriate value when rotating at high speed, there is a problem that the clearance becomes too large when rotating at low speed, making heavy cutting and precision cutting impossible.
また軸受の潤滑油を大量に流して内外輪同時に冷却を行
うジェット潤滑では高速回転時に攪拌抵抗が非常に大き
くなり損失もこれにともなって大きくなるという問題が
ある。例えば内径100mmのアンギュラ玉軸受６個を潤滑
油粘度1.5cstの潤滑油で15.000r.p.mの場合の出力損失
約8kwが20.000r.p.mとなる約15kwと大幅に増大する結果
が出ている。Further, in jet lubrication in which a large amount of bearing lubricating oil is made to flow to cool the inner and outer rings simultaneously, there is a problem that the stirring resistance becomes extremely high at high speed and the loss also increases accordingly. For example, when six angular ball bearings with an inner diameter of 100 mm are lubricated with a lubricating oil viscosity of 1.5 cst at 15.000 rpm, the output loss of about 8 kw is significantly increased to about 20 kw, which is about 20 kw.
さらに実開平1-85528号のものではドローバ中心より主
軸中心穴の螺旋溝を経てテーパ穴の横穴より排出してい
るが螺旋溝が内輪より離れており排出口が近いので充分
な冷却効果が得られないという問題がある。In addition, in the actual Kaihei No. 1-85528, it is discharged from the drawbar center through the spiral groove of the spindle center hole and from the lateral hole of the tapered hole, but the spiral groove is far from the inner ring and the discharge port is close, so a sufficient cooling effect is obtained. There is a problem that you can not.
本考案は従来の技術の有するこのような問題点に鑑みな
されたもので、その目的とするところは低損失のオイル
エア潤滑が採用でき、しかも冷却効率の高い構造によっ
て低速から高速迄加工に不都合のない良好な軸受隙間が
保たれる主軸軸受の冷却構造を提供しようとするもので
ある。The present invention has been made in view of the above problems of the prior art. The purpose of the present invention is to employ low-loss oil-air lubrication, and the structure with high cooling efficiency is not suitable for machining from low speed to high speed. An object of the present invention is to provide a cooling structure for a main shaft bearing in which a good bearing gap is maintained.
課題を解決するための手段 上述の目的を達成するために本考案は、主軸の軸承部位
に外筒を嵌合させ、該外筒を軸受によって回転可能に軸
承し、前記主軸または外筒の少なくとも一方の嵌合面に
螺旋状の溝若しくはスプライン溝を削設して流路を形成
し、主軸中心穴に挿通されたドローバの工具引上げ用の
弾性部材収容筒の外周と中心穴との間に流路となる隙間
を形成して嵌装し、前記ドローバの外周に通じる流路か
ら前記収容筒外周の隙間、前記螺旋若しくはスプライン
溝，還流路に連なる流路を形成してなるものである。Means for Solving the Problems In order to achieve the above-mentioned object, the present invention provides an outer cylinder fitted to a bearing portion of a main shaft, rotatably bearing the outer cylinder by a bearing, and at least the main shaft or the outer cylinder. A spiral groove or spline groove is cut on one mating surface to form a flow path, and between the outer circumference of the elastic member accommodating cylinder for pulling up the tool of the drawbar inserted in the spindle center hole and the center hole. It is configured to be fitted with a gap serving as a flow passage, and to form a flow passage extending from the flow passage leading to the outer periphery of the drawbar to the gap on the outer circumference of the storage cylinder, the spiral or spline groove, and the return passage.
作用 取入れジョイント16より主軸中心部に送られた冷却水は
皿ばね収容筒９の外周隙間9a,主軸６の外周の螺旋溝6a
より穴6c,17a,2b,1aを経て排出ジョイント18に流され、
主軸６の回転による遠心力によって流れ良く循環され
る。The cooling water sent from the intake joint 16 to the center of the spindle is the outer peripheral gap 9a of the disc spring housing cylinder 9 and the spiral groove 6a of the outer periphery of the main spindle 6.
More through the holes 6c, 17a, 2b, 1a, flow into the discharge joint 18,
It is circulated well by the centrifugal force generated by the rotation of the main shaft 6.
実施例 以下実施例を第１図にもとづき説明する。Example An example will be described below with reference to FIG.
主軸頭１の穴に外周に冷却液流路の螺旋溝2aを削設した
軸受ハウジング２が嵌装されている。この軸受ハウジン
グ２には主軸の前軸受群３と後軸受群４とで外筒５が回
転可能に軸承されている。そして外筒５の前軸受側を大
径とするテーパの中心穴5aに主軸６が嵌合されて二重構
造の主軸を形成している。A bearing housing 2 in which a spiral groove 2a of a cooling liquid flow path is cut on the outer periphery is fitted in the hole of the spindle head 1. An outer cylinder 5 is rotatably supported in the bearing housing 2 by a front bearing group 3 and a rear bearing group 4 of a main shaft. The main shaft 6 is fitted in the tapered central hole 5a having a large diameter on the front bearing side of the outer cylinder 5 to form a double structure main shaft.
この主軸６は外周嵌合面全面に螺旋溝6aが削設されてい
る。この螺旋溝に替えてスプライン溝として各スプライ
ン溝を連通する円周溝を流入側と流出側とに削設したも
のとすることも自由である。主軸６の中心穴は周知のよ
うに工具嵌着のテーパ穴6dにつづく穴にコレット７を内
蔵し、コレット作動用のドローバ８が後方に貫通してい
る。ドローバ８の中程のフランジの後側には特に皿ばね
若しくは弾性部材10を内蔵する弾性部材収容筒９が嵌挿
され、皿ばね10は皿ばね受カラー11を介してナット12に
よって圧縮量が調整されている。The main shaft 6 has a spiral groove 6a formed on the entire outer peripheral fitting surface. Instead of the spiral groove, it is also possible to use a spline groove, which is a circumferential groove that communicates with each spline groove and is provided on the inflow side and the outflow side. As is well known, the center hole of the main shaft 6 has a collet 7 built in a hole following a taper hole 6d for tool fitting, and a draw bar 8 for operating the collet penetrates rearward. In the middle of the flange of the drawbar 8, an elastic member housing cylinder 9 containing a disc spring or an elastic member 10 is fitted and inserted, and the disc spring 10 is compressed by a nut 12 via a disc spring receiving collar 11. Has been adjusted.
皿ばね収容筒９は後端のフランジ部において主軸６の後
端に固定され、外周中央部が流路となる隙間9aを形成す
る小径部で両端部が主軸中心穴内面に密嵌合し、奥のド
ローバ８との嵌合面にはＯリングによって液蜜とされて
いる。カラー11も弾性部材収容筒９及びドローバ８との
嵌合部はＯリングによって液蜜とされ皿ばね収容筒９内
に冷却液が侵入しないようになされている。The disc spring accommodating cylinder 9 is fixed to the rear end of the main shaft 6 at the rear flange portion, and both ends are tightly fitted to the inner surface of the main shaft center hole with a small diameter portion forming a gap 9a in which the outer peripheral central portion serves as a flow path. The mating surface with the drawbar 8 at the back is made into liquid honey by an O-ring. In the collar 11 as well, the fitting portion between the elastic member housing cylinder 9 and the drawbar 8 is made to be liquid by an O-ring so that the cooling liquid does not enter the disc spring housing cylinder 9.
主軸後端部にはモータのロータ13が取付けられ、ステー
タ14を嵌装するモータ外筒15が主軸頭１に同心に固設さ
れている。そしてモータ外筒15とカラー11との間には流
路となる隙間11aが形成され、モータ外筒15とカラー11
との間及び皿ばね収容筒９との間は図示しないシールが
介装されている。モータ外筒15には冷却水の取入ジョイ
ント16を取付けた流路15aがカラー11の外周の隙間11aに
連通されている。また皿ばね収容筒９には隙間9aと11a
と連通する穴9bが穿設されている。主軸６には螺旋溝6a
後端と皿ばね収容筒９の隙間9aと連通する穴6bと、螺旋
溝6aの前端から流出する穴6cとが穿設されている。軸受
ハウジング２には穴6cと連通する穴2bが穿設されてお
り、軸受ハヴジング２の前端部に主軸６との間に介装し
たシール部材17の穴17aを介して連通されている。主軸
頭１には冷却液の排出用ジョイント18を取付けた穴1aが
軸受ハウジング２の穴2bと連通するように穿設されてい
る。A rotor 13 of the motor is attached to the rear end of the main shaft, and a motor outer cylinder 15 into which a stator 14 is fitted is fixed to the main spindle head 1 concentrically. A gap 11a serving as a flow path is formed between the motor outer cylinder 15 and the collar 11, and the motor outer cylinder 15 and the collar 11 are formed.
A seal (not shown) is interposed between and and and the disc spring accommodating cylinder 9. A flow passage 15a, to which a cooling water intake joint 16 is attached, is connected to the motor outer cylinder 15 through a gap 11a on the outer circumference of the collar 11. Further, the disc spring accommodating cylinder 9 has gaps 9a and 11a.
A hole 9b communicating with the hole is formed. The main shaft 6 has a spiral groove 6a
A hole 6b that communicates with the rear end and the gap 9a between the disc spring housing cylinder 9 and a hole 6c that flows out from the front end of the spiral groove 6a are formed. The bearing housing 2 is formed with a hole 2b communicating with the hole 6c, and is communicated with the front end portion of the bearing housing 2 through a hole 17a of a seal member 17 interposed between the bearing housing 2 and the main shaft 6. The spindle head 1 is provided with a hole 1a in which a coolant discharge joint 18 is attached so as to communicate with the hole 2b of the bearing housing 2.
このように構成されたものにおいて、主軸６に工具が装
着され切削加工指令が出されると軸受3,4はオイルエア
で潤滑され、主軸６はビルトインモータで回転される。
図示しない冷却液供給源から取入ジョイント16より冷却
液が送られ穴15a,カラー11の隙間11a,弾性部材収容筒９
の穴9b,隙間9a,主軸６の穴6b,螺旋溝6a,穴6c,シール部
材17の穴17a,軸受ハウジング２の穴2b,主軸頭１の穴1a,
排出ジョイント18よりタンクに排液する循環によって外
筒５を介して軸受3,4の内輪が冷却される。冷却水は主
軸中心部から外側に向かって流れ且テーパ状となった螺
旋溝により主軸の回転による遠心力によって冷却液は流
れ良く循環される。また軸受ハウジング２の外の螺旋溝
2aに図示しない流路を経て冷却液が送られ軸受外輪が冷
却される。なお必要により排出ジョイント18側から吸引
するようになされる。In such a structure, when a tool is mounted on the main shaft 6 and a cutting command is issued, the bearings 3 and 4 are lubricated with oil air, and the main shaft 6 is rotated by a built-in motor.
Cooling liquid is fed from an unillustrated cooling liquid supply source through the intake joint 16, the hole 15a, the gap 11a of the collar 11, the elastic member housing cylinder 9
Hole 9b, gap 9a, spindle 6 hole 6b, spiral groove 6a, hole 6c, seal member 17 hole 17a, bearing housing 2 hole 2b, spindle head 1 hole 1a,
The inner rings of the bearings 3 and 4 are cooled via the outer cylinder 5 by the circulation of the liquid discharged from the discharge joint 18 to the tank. The cooling water flows outward from the center of the main shaft, and the tapered spiral groove allows the cooling liquid to circulate well by the centrifugal force generated by the rotation of the main shaft. Also, the spiral groove outside the bearing housing 2
Coolant is sent to 2a through a flow path (not shown) to cool the bearing outer ring. If necessary, suction is performed from the discharge joint 18 side.
効果 上述のように構成したので本考案は以下の効果を奏す
る。Effects Since the present invention is configured as described above, the present invention has the following effects.
軸受の外輪の冷却とともに内輪側が近くから冷却され
て、主軸の広い回転範囲で軸受隙間の変動を抑えて重切
削から仕上切削まで広い範囲の加工をすることができ
る。また冷却水の供給を中心側から外側へ流すようにな
したので主軸回転の遠心力を利用して冷却水の流れが良
くなり効率的な冷却効果が得られる。またオイルエア潤
滑によって高速から低速まで支障のよい潤滑ができ損失
の少ない潤滑法が採用できる。As the outer ring of the bearing is cooled, the inner ring side is cooled from near, so that the variation of the bearing clearance can be suppressed in a wide rotation range of the main shaft, and a wide range of machining from heavy cutting to finish cutting can be performed. Further, since the supply of the cooling water is made to flow from the center side to the outside, the flow of the cooling water is improved by utilizing the centrifugal force of the main shaft rotation, and an efficient cooling effect can be obtained. In addition, oil-air lubrication can be used for high-speed to low-speed lubrication, and a lubrication method with less loss can be adopted.
第１図は本考案の主軸構造を示す断面図である。 １……主軸頭、２……軸受ハウジング ５……外筒、６……主軸、6a……螺旋溝 ８……ドローバ、９……皿ばね収容筒 9a……隙間、11……カラー 11a……隙間 FIG. 1 is a sectional view showing a spindle structure of the present invention. 1 ... Spindle head, 2 ... Bearing housing 5 ... Outer cylinder, 6 ... Spindle, 6a ... Spiral groove 8 ... Drawbar, 9 ... Disc spring accommodating cylinder 9a ... Gap, 11 ... Collar 11a ... … Gap
Claims (1)
を軸受によって回転可能に軸承し、前記主軸または外筒
の少なくとも一方の嵌合面に溝状の流路を形成し、主軸
中心穴に挿通されたドローバの工具引上げ用の弾性部材
収容筒の外周と中心穴との間に流路となる隙間を形成し
て嵌装し、前記ドローバの外周に通じる流路から前記収
容筒外周の隙間、前記溝状流路，還流路に連なる流路を
形成してなり、主軸中心側より冷却液を通して軸受内輪
側を冷却するようにしたことを特徴とする主軸軸受の冷
却構造。1. An outer cylinder is fitted to a bearing portion of a main shaft, the outer cylinder is rotatably supported by a bearing, and a groove-like flow path is formed on at least one fitting surface of the main shaft or the outer cylinder. The flow path leading to the outer circumference of the draw bar is fitted by forming a gap that serves as a flow path between the outer circumference of the elastic member accommodating cylinder for pulling up the tool of the draw bar inserted in the spindle center hole and the center hole. A cooling structure for a main shaft bearing, characterized in that a gap is formed around the outer circumference of the housing cylinder, a groove-like flow path, and a flow path that connects to the return flow path are formed to cool the bearing inner ring side through a cooling liquid from the main shaft center side. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP862690U JPH0746450Y2 (en) | 1990-01-31 | 1990-01-31 | Spindle bearing cooling structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP862690U JPH0746450Y2 (en) | 1990-01-31 | 1990-01-31 | Spindle bearing cooling structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03100051U JPH03100051U (en) | 1991-10-18 |
| JPH0746450Y2 true JPH0746450Y2 (en) | 1995-10-25 |
Family
ID=31512250
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP862690U Expired - Fee Related JPH0746450Y2 (en) | 1990-01-31 | 1990-01-31 | Spindle bearing cooling structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0746450Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011156597A (en) * | 2010-01-29 | 2011-08-18 | Mitsubishi Heavy Ind Ltd | Main shaft device for boring machine |
| JP2011235403A (en) * | 2010-05-11 | 2011-11-24 | Nagase Integrex Co Ltd | Spindle device for machine tool |
-
1990
- 1990-01-31 JP JP862690U patent/JPH0746450Y2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03100051U (en) | 1991-10-18 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |