JPH068005A - Main spindle unit - Google Patents
Main spindle unitInfo
- Publication number
- JPH068005A JPH068005A JP4193468A JP19346892A JPH068005A JP H068005 A JPH068005 A JP H068005A JP 4193468 A JP4193468 A JP 4193468A JP 19346892 A JP19346892 A JP 19346892A JP H068005 A JPH068005 A JP H068005A
- Authority
- JP
- Japan
- Prior art keywords
- main spindle
- intermediate housing
- bearing
- housing
- front side
- 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.)
- Granted
Links
Landscapes
- Automatic Control Of Machine Tools (AREA)
- Turning (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は工作機械において軽切削
から主軸系の動剛性が要求される重切削に対応可能な主
軸ユニットに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a spindle unit capable of coping with heavy cutting, which requires dynamic rigidity of a spindle system in a machine tool.
【０００２】[0002]
【従来の技術】従来工作機械の主軸１は一般にころがり
軸受が使用されるが軸受剛性が高く、保守性及び価格の
点で優れている。しかし減衰性が充分でないという欠点
を有する。このため耐びびり性を向上させるために前軸
受２と後軸受３の間、主軸１のほぼ中央に図２に示すよ
うにスクィーズフィルムダンパの役目をさせるためにす
べり軸受４が併置されたものがある。2. Description of the Related Art Conventionally, a rolling bearing is generally used for the main spindle 1 of a machine tool, but the bearing rigidity is high and it is excellent in maintainability and cost. However, it has a drawback that the damping property is not sufficient. Therefore, in order to improve chatter resistance, a slide bearing 4 is provided between the front bearing 2 and the rear bearing 3 and in the approximate center of the main shaft 1 so as to function as a squeeze film damper as shown in FIG. is there.
【０００３】[0003]
【発明が解決しようとする課題】しかしこのものはすべ
り軸受を使用しているので高速回転すると発熱の原因に
ある。また主軸とのすき間調整が困難であり、組立時の
ミスアライメントがあるとすべり軸受幅が広いので片当
たりする。そしてすべり軸受けがびびりに対して減衰作
用として最も効果がある前軸受より離れているので充分
な効果が得られない。加工中ほぼ一定にダンピング作用
を行っているが振動と関連して主軸の支持剛性を自動調
整するものでないので広範囲な加工に対して満足すべき
効果が得られていなかった。本発明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
するところはころがり軸受の減衰性を改善してびびり発
生を抑制して軽切削から重切削迄可能とする主軸ユニッ
トを提供しようとするものである。However, since this bearing uses a slide bearing, it causes heat generation when it is rotated at a high speed. In addition, it is difficult to adjust the clearance with the main shaft, and if there is misalignment during assembly, the sliding bearing width will be wide, which will cause one-sided contact. Further, since the sliding bearing is separated from the front bearing, which has the most effective damping effect on chatter, a sufficient effect cannot be obtained. Although the damping action is performed almost constantly during machining, it does not automatically adjust the support rigidity of the main shaft in relation to vibration, so a satisfactory effect was not obtained for a wide range of machining. The present invention has been made in view of the above problems of the prior art, and an object of the present invention is to improve damping characteristics of a rolling bearing and suppress chattering to enable light cutting to heavy cutting. It is intended to provide a spindle unit.
【０００４】[0004]
【課題を解決するための手段】上述の目的を達成するた
めに本発明は、主軸が主軸台にころがり軸受によって前
部と後部を軸承された主軸ユニットにおいて、前部ころ
がり軸受と主軸台部材との間に中間ハウジングを介装
し、該中間ハウジングを主軸台部材にラジアル方向及び
スラスト方向の静圧軸受で支承し、前記中間ハウジング
には同心にブレーキディスクを設け、前記主軸台部材側
には前記静圧軸受の圧油供給に関連して該ブレーキディ
スクに作動する電磁ブレーキを設け、前記主軸台の振動
を検出する振動計を取付け、該振動計の出力にもとづい
て前記静圧軸受の供給油圧を調整する制御手段を備えて
なり、振動レベルに対応して静圧軸受の減衰性を改善す
るものである。In order to achieve the above-mentioned object, the present invention is directed to a spindle unit in which a spindle has a front bearing and a rear portion supported by a rolling bearing on a headstock, and a front rolling bearing and a headstock member are provided. An intermediate housing is interposed between the intermediate housing and the headstock member, and the bearings are supported by radial and thrust static pressure bearings, and a brake disc is concentrically provided on the intermediate housing. An electromagnetic brake that operates in relation to the pressure oil supply of the hydrostatic bearing is provided, and a vibrometer that detects vibration of the headstock is attached, and the hydrostatic bearing is supplied based on the output of the vibrometer. The control means for adjusting the hydraulic pressure is provided to improve the damping property of the hydrostatic bearing according to the vibration level.
【０００５】[0005]
【作用】静圧軸受に圧油が供給されその確認後ディスク
ブレーキを作動させる。加工による振動計の振動レベル
があるしきい値を越えるとき制御手段により静圧用供給
の油圧力を調整して静圧軸受の減衰性を改善して主軸系
の動剛性を高める。[Function] After the pressure oil is supplied to the hydrostatic bearing, the disc brake is activated after the confirmation. When the vibration level of the vibrometer due to machining exceeds a certain threshold value, the hydraulic pressure of the static pressure supply is adjusted by the control means to improve the damping property of the static pressure bearing and enhance the dynamic rigidity of the spindle system.
【０００６】[0006]
【実施例】以下本発明の実施例を図１にもとづき説明す
る。例えば周知の旋盤の主軸台１１に後側ハウジング１
２と前側ハウジング１３とが同心に設けられており、前
側ハウジング１３には後述のころがり軸受１５の位置に
対応して小径部１３ａが形成されている。そして小径部
１３ａに対応する外周に深い環状溝１４ａが削設された
中間ハウジング１４が同心に介装されている。中間ハウ
ジング１４に嵌装されたころがり軸受１５及び同心の後
側ハウジング１２に嵌装されたころがり軸受１６により
主軸１７が回転可能に軸承されている。この主軸１７の
後方延長テーパ部にはビルトインモータ１９のロータ１
９Ｂが同心に嵌着されている。ステータ１９Ａは外周に
冷却用ジャケット１８ａを設けたモータハウジング１８
によって主軸台１１に嵌装されている。Embodiment An embodiment of the present invention will be described below with reference to FIG. For example, the rear housing 1 is attached to the headstock 11 of a known lathe.
2 and the front housing 13 are concentrically provided, and the front housing 13 is formed with a small diameter portion 13a corresponding to the position of a rolling bearing 15 described later. An intermediate housing 14 having a deep annular groove 14a formed in the outer periphery corresponding to the small diameter portion 13a is concentrically provided. The main shaft 17 is rotatably supported by a rolling bearing 15 fitted in the intermediate housing 14 and a rolling bearing 16 fitted in the concentric rear housing 12. A rotor 1 of the built-in motor 19 is provided at the rearward extension taper portion of the main shaft 17.
9B is fitted concentrically. The stator 19A is a motor housing 18 provided with a cooling jacket 18a on the outer periphery.
Is fitted to the headstock 11.
【０００７】さらに重要なことは中間ハウジング１４の
環状溝１４ａと前側ハウジング１３の小径部１３ａとの
間に静圧軸受が形成されていることである。即ち前側ハ
ウジング１３の小径部１３ａの内周面の円周方向数等分
角度位置に、中間ハウジング１４の環状溝の底に対向し
て静圧パッド２１ａが削設され、絞り２２ａを介して流
路２３に接続されている。また前側ハウジング１３の小
径部の前後の側面１３ｂ，１３ｃには中間ハウジング１
４の環状溝１４ａの側面１４ｂ，１４ｃに対向して且静
圧パッド２１ａに対応して静圧パッド２１ｂ，２１ｃが
削設され、それぞれ絞り２２ｂ，２２ｃを介して流路２
３に接続されている。さらにまた中間ハウジング１４の
内側端面にはブレーキディスク２５が同心に取付けられ
ており、主軸台１１側にはブレーキをかける電磁ブレー
キ２６が対設されている。また加工中の主軸台の振動レ
ベルを検出する振動計３０が主軸台１１の前部ハウジン
グ上に設置されている。More importantly, a hydrostatic bearing is formed between the annular groove 14a of the intermediate housing 14 and the small diameter portion 13a of the front housing 13. That is, the static pressure pad 21a is cut at a number of angular positions in the circumferential direction of the inner peripheral surface of the small-diameter portion 13a of the front housing 13 so as to face the bottom of the annular groove of the intermediate housing 14, and the static pressure pad 21a flows through the throttle 22a. It is connected to the path 23. Further, the intermediate housing 1 is provided on the front and rear side surfaces 13b and 13c of the small diameter portion of the front housing 13.
The static pressure pads 21b and 21c are formed facing the side surfaces 14b and 14c of the annular groove 14a of No. 4 and corresponding to the static pressure pad 21a. The static pressure pads 21b and 21c are respectively cut through the throttles 22b and 22c.
Connected to 3. Further, a brake disc 25 is concentrically attached to the inner end surface of the intermediate housing 14, and an electromagnetic brake 26 for applying a brake is provided opposite to the headstock 11 side. A vibrometer 30 for detecting the vibration level of the headstock being machined is installed on the front housing of the headstock 11.
【０００８】図１のブロック線図中、３１は油圧ポン
プ、３２はビルトインモータ１９及び静圧パッドへの供
給油温を調整する油温コントローラ、３３は静圧パッド
への供給油圧を調整する電磁比例式圧力調整弁、３４は
安全リリーフ弁である。４０は制御装置で以下の回路が
含まれている。４１は振動レベルがある値になったとき
主軸系の減衰性を上げる為に静圧パッドへの供給油圧Ｐ
ｓを上げるしきい値Ｖ0、及び静圧軸受の供給油圧の最
大値Ｐｓｍでも振動計３０の振動レべルがしきい値以下
とならないときの警戒しきい値ＶｍをＭＤＩ等で入力さ
れ記憶する記憶回路。４２は振動計３０の振動レベルＶ
ｉが、Ｖ0 とＶｍの間にあるかどうかを比較してこの間
にあるとき電磁比例式圧力調整弁３３を作動して対応す
る圧油Ｐｓを供給し、ＶｉがＶｍより大きくなったとき
アラームを出力して機械運転を停止する比較回路。４３
は静圧軸受に圧油が供給されたことが確認されたときデ
ィスクブレーキを作動させる電磁ブレーキ作動回路、４
４はビルトインモータ１９の駆動回路でこれ等を含むも
のである。In the block diagram of FIG. 1, 31 is a hydraulic pump, 32 is an oil temperature controller for adjusting the oil temperature supplied to the built-in motor 19 and the static pressure pad, and 33 is an electromagnetic valve for adjusting the oil pressure supplied to the static pressure pad. The proportional pressure regulating valve 34 is a safety relief valve. A control device 40 includes the following circuits. Reference numeral 41 indicates the hydraulic pressure P supplied to the static pressure pad in order to improve the damping of the spindle system when the vibration level reaches a certain value.
The threshold value V 0 for increasing s and the warning threshold value Vm when the vibration level of the vibrometer 30 does not fall below the threshold value even with the maximum value Psm of the hydraulic pressure supplied to the hydrostatic bearing are input and stored by MDI or the like. Memory circuit. 42 is the vibration level V of the vibrometer 30
When i is between V 0 and Vm, it is compared, and when it is in this range, the electromagnetic proportional pressure regulating valve 33 is operated to supply the corresponding pressure oil Ps, and when Vi becomes larger than Vm, an alarm is issued. Is output to stop the machine operation. 43
Is an electromagnetic brake activation circuit that activates the disc brake when it is confirmed that pressure oil has been supplied to the hydrostatic bearings.
Reference numeral 4 denotes a drive circuit for the built-in motor 19, which includes these.
【０００９】このように構成されたものにおいて、予め
振動レベルの加工精度との関係で決定された基準となる
しきい値Ｖ0 及び静圧軸受の供給最大圧Ｐｓｍに上げて
も振動レベルが下がらないとき警戒しきい値Ｖｍを決定
して記憶回路４１に記憶しておく。主軸１７の先端の図
示しないチャックに工作物が把持されビルトインモータ
１９がビルトインモータ駆動回路４４によって駆動され
主軸１７が回転される。また油温コントローラ３２で適
温とされ、油圧ポンプ３１で送られる圧油は電磁比例式
圧力調整弁３３により決定された初期油圧Ｐｓ1 で油路
２３からそれぞれの絞り２２ａ，２２ｂ，２２ｃを経て
静圧パッドに供給され、静圧によって中間ハウジング１
４を軸承する。静圧軸受に供給圧油が送られた確認が出
力されると電磁ブレーキ作動回路４３が電磁ブレーキ２
６を作動してブレーキディスク２５にブレーキをかけ中
間ハウジング１４のつれ回りを止める。In such a structure, the vibration level is lowered even if it is increased to the reference threshold value V 0 previously determined in relation to the processing accuracy of the vibration level and the maximum supply pressure Psm of the hydrostatic bearing. When there is no warning threshold value Vm, it is determined and stored in the memory circuit 41. The workpiece is gripped by a chuck (not shown) at the tip of the main shaft 17, the built-in motor 19 is driven by the built-in motor drive circuit 44, and the main shaft 17 is rotated. Further, the pressure oil that is adjusted to an appropriate temperature by the oil temperature controller 32 and is sent by the hydraulic pump 31 is discharged from the oil passage 23 through the respective throttles 22a, 22b, 22c at the initial oil pressure Ps 1 determined by the electromagnetic proportional pressure adjusting valve 33. Supplied to the pressure pad, by static pressure the intermediate housing 1
Bearing 4 When the confirmation that the supplied pressure oil is sent to the hydrostatic bearing is output, the electromagnetic brake operating circuit 43 causes the electromagnetic brake 2 to operate.
6 is actuated to brake the brake disc 25 and stop the suspension of the intermediate housing 14.
【００１０】さらに圧油は流路２４によりビルトインモ
ータ１９のモータハウジングの冷却用ジャケット１８ａ
に供給されステータ１９Ａを冷却する。この状態におい
て図示しない刃物台がＮＣ制御され主軸１７に嵌着した
チャックに把持された工作物の加工が行われる。切削に
より主軸台１１上に設置された振動計３０が加工中の振
動をインプロセスで検出し、その振動レベルが制御装置
４０の比較回路４２に刻々入力されている。比較回路４
２では記憶回路４１の記憶値Ｖ0 ・Ｖｍとの間でＶ0 ＜
Ｖｉ＜Ｖｍが判断され、Ｖ0 ＞Ｖｉであれば電磁比例式
圧力調整弁３３は引続き初期油圧Ｐｓ1 となる状態を続
ける。切削が重切削となり振動計３０の振動レベルがＶ
0 ＜Ｖｉ＜Ｖｍの状態と比較回路４２で判断されれば、
電磁比例式圧力調整弁は振動レベルＶｉの大きさに対応
して供給圧Ｐｓ2 に増大して静圧軸受の減衰性を増大し
て振動レベルを低下させるように作用する。そして主軸
系としての減衰性を改善して主軸系の動剛性を上げる。
比較回路４２において、Ｖｉ＞Ｖｍとなればアラームが
出力されビルトインモータ駆動回路４４でビルトインモ
ータが制御され主軸回転が停止される。Further, the pressure oil is passed through the flow path 24 to the cooling jacket 18a of the motor housing of the built-in motor 19.
To cool the stator 19A. In this state, the tool rest (not shown) is NC controlled, and the workpiece gripped by the chuck fitted to the spindle 17 is machined. The vibration meter 30 installed on the headstock 11 by cutting detects the vibration during processing in-process, and the vibration level is constantly input to the comparison circuit 42 of the control device 40. Comparison circuit 4
2, V 0 <with the stored value V 0 · Vm of the storage circuit 41.
If Vi <Vm is judged and if V 0 > Vi, the electromagnetic proportional pressure regulating valve 33 continues to be in the state of the initial hydraulic pressure Ps 1 . The cutting is heavy cutting and the vibration level of the vibrometer 30 is V
If the comparison circuit 42 determines that 0 <Vi <Vm,
The electromagnetic proportional pressure regulating valve acts to increase the supply pressure Ps 2 corresponding to the magnitude of the vibration level Vi to increase the damping property of the hydrostatic bearing and reduce the vibration level. Then, the damping property of the spindle system is improved to increase the dynamic rigidity of the spindle system.
In the comparison circuit 42, when Vi> Vm, an alarm is output, the built-in motor drive circuit 44 controls the built-in motor, and the spindle rotation is stopped.
【００１１】[0011]
【発明の効果】上述のように構成したので本発明は以下
の効果を奏する。静圧軸受の供給圧が振動レベルに対応
して変化され主軸系の減衰性が改善され軸受剛性が向上
される。また切削による主軸台の加工中の振動をインプ
ロセスで検出できてびびりの発生を抑制することがで
き、軽切削から重切削までの加工が可能となる。Since the present invention is constructed as described above, the present invention has the following effects. The supply pressure of the hydrostatic bearing is changed according to the vibration level, the damping property of the main shaft system is improved, and the bearing rigidity is improved. In addition, vibration during machining of the headstock due to cutting can be detected in-process to suppress chattering, and machining from light cutting to heavy cutting becomes possible.
【図１】本発明の主軸ユニットの説明図である。FIG. 1 is an explanatory diagram of a spindle unit of the present invention.
【図２】従来の主軸ユニットの説明図である。FIG. 2 is an explanatory view of a conventional spindle unit.
１１ 主軸台 １２ 後側ハウ
ジング １３ 前側ハウジング １４ 中間ハウ
ジング １５，１６ ころがり軸受 １７ 主軸 １９ ビルトインモータ ２１ａ，２１
ｂ，２１ｃ 静圧パッド ２２ａ，２２ｂ，２２ｃ 絞り ２５ ブレーキ
ディスク ２６ 電磁ブレーキ ３０ 振動計 ３１ 油圧ポンプ ３２ 油温コン
トローラ ４０ 制御装置11 Headstock 12 Rear Housing 13 Front Housing 14 Intermediate Housing 15, 16 Rolling Bearing 17 Spindle 19 Built-in Motor 21a, 21
b, 21c Static pressure pad 22a, 22b, 22c Throttle 25 Brake disc 26 Electromagnetic brake 30 Vibrometer 31 Hydraulic pump 32 Oil temperature controller 40 Control device
Claims (1)
部と後部を軸承された主軸ユニットにおいて、前部ころ
がり軸受と主軸台部材との間に中間ハウジングを介装
し、該中間ハウジングを主軸台部材にラジアル方向及び
スラスト方向の静圧軸受で支承し、前記中間ハウジング
には同心にブレーキディスクを設け、前記主軸台部材側
には前記静圧軸受の圧油供給に関連して該ブレーキディ
スクに作動する電磁ブレーキを設け、前記主軸台の振動
を検出する振動計を取付け、該振動計の出力にもとづい
て前記静圧軸受の供給油圧を調整する制御手段を備えて
なり、振動レベルに対応して静圧軸受の減衰性を改善す
ることを特徴とする主軸ユニット。1. In a spindle unit in which a spindle is supported on a headstock by a rolling bearing at a front portion and a rear portion, an intermediate housing is interposed between a front rolling bearing and a headstock member, and the intermediate housing is provided. The member is supported by radial and thrust static pressure bearings, the intermediate housing is provided with a concentric brake disc, and the headstock member side is provided with the brake disc in relation to the pressure oil supply of the static pressure bearing. An electromagnetic brake that operates is provided, a vibrometer that detects the vibration of the headstock is attached, and a control means that adjusts the hydraulic pressure supplied to the hydrostatic bearing based on the output of the vibrometer is provided. Spindle unit characterized by improving the damping of hydrostatic bearings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4193468A JP2867373B2 (en) | 1992-06-26 | 1992-06-26 | Spindle unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4193468A JP2867373B2 (en) | 1992-06-26 | 1992-06-26 | Spindle unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH068005A true JPH068005A (en) | 1994-01-18 |
| JP2867373B2 JP2867373B2 (en) | 1999-03-08 |
Family
ID=16308518
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4193468A Expired - Fee Related JP2867373B2 (en) | 1992-06-26 | 1992-06-26 | Spindle unit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2867373B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2308635A1 (en) | 2009-10-06 | 2011-04-13 | Jtekt Corporation | Spindle device for machine tool |
| JP2011235404A (en) * | 2010-05-11 | 2011-11-24 | Jtekt Corp | Spindle device of machine tool |
| JP2013059824A (en) * | 2011-09-13 | 2013-04-04 | Ihi Corp | Working device, and method for designing structural specification of working machine |
| EP2676765A1 (en) | 2012-06-19 | 2013-12-25 | Jtekt Corporation | Spindel unit with a damper bearing |
| EP2813317A1 (en) * | 2013-06-10 | 2014-12-17 | Jtekt Corporation | Main spindle unit with damper bearing |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5560603B2 (en) * | 2009-07-21 | 2014-07-30 | 株式会社ジェイテクト | Spindle device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0374628A (en) * | 1989-08-11 | 1991-03-29 | Kuroda Precision Ind Ltd | Static pressure air bearing |
| JPH03111103A (en) * | 1989-09-27 | 1991-05-10 | Okuma Mach Works Ltd | Spindle stock with hybrid bearing |
-
1992
- 1992-06-26 JP JP4193468A patent/JP2867373B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0374628A (en) * | 1989-08-11 | 1991-03-29 | Kuroda Precision Ind Ltd | Static pressure air bearing |
| JPH03111103A (en) * | 1989-09-27 | 1991-05-10 | Okuma Mach Works Ltd | Spindle stock with hybrid bearing |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2308635A1 (en) | 2009-10-06 | 2011-04-13 | Jtekt Corporation | Spindle device for machine tool |
| JP2011079078A (en) * | 2009-10-06 | 2011-04-21 | Jtekt Corp | Spindle device of machine tool |
| CN102029407A (en) * | 2009-10-06 | 2011-04-27 | 株式会社捷太格特 | Spindle device for machine tool |
| US8827609B2 (en) | 2009-10-06 | 2014-09-09 | Jtekt Corporation | Spindle device for machine tool |
| CN102029407B (en) * | 2009-10-06 | 2014-10-08 | 株式会社捷太格特 | Spindle device for machine tool |
| JP2011235404A (en) * | 2010-05-11 | 2011-11-24 | Jtekt Corp | Spindle device of machine tool |
| JP2013059824A (en) * | 2011-09-13 | 2013-04-04 | Ihi Corp | Working device, and method for designing structural specification of working machine |
| EP2676765A1 (en) | 2012-06-19 | 2013-12-25 | Jtekt Corporation | Spindel unit with a damper bearing |
| JP2014000637A (en) * | 2012-06-19 | 2014-01-09 | Jtekt Corp | Main spindle device |
| US9011007B2 (en) | 2012-06-19 | 2015-04-21 | Jtekt Corporation | Spindle unit |
| EP2813317A1 (en) * | 2013-06-10 | 2014-12-17 | Jtekt Corporation | Main spindle unit with damper bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2867373B2 (en) | 1999-03-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8827609B2 (en) | Spindle device for machine tool | |
| US4527661A (en) | Adaptive control system for machine tool or the like | |
| US8740523B2 (en) | Spindle device | |
| US4519734A (en) | High speed spindle with preloaded bearings | |
| US4514123A (en) | Adaptive control system for machine tool or the like | |
| JP2011079078A5 (en) | ||
| WO2011037140A1 (en) | Spindle device of machining center | |
| JPH068005A (en) | Main spindle unit | |
| JP5499328B2 (en) | Variable preload spindle | |
| CN101941083B (en) | Spindle device for machine tool | |
| EP1080829B1 (en) | Hybrid hydrostatic spindle | |
| JP2015020254A (en) | Spindle device | |
| CN108326326B (en) | A kind of intelligence electro spindle grinding processing method and system | |
| JP7001813B2 (en) | Machine tool spindle device | |
| JP3415174B2 (en) | Spindle braking system for multi-task machine tools | |
| JPS58196319A (en) | Pneumatic bearing device | |
| JP4646380B2 (en) | Continuously variable transmission having electro-hydraulic control system and control method of the transmission | |
| JP3874400B2 (en) | Machine tool spindle equipment | |
| JPH03111103A (en) | Spindle stock with hybrid bearing | |
| JPH0641796Y2 (en) | Spindle unit | |
| JP2857061B2 (en) | Spindle device using hydrodynamic bearing | |
| JP2002005169A (en) | Fluid bearing device | |
| JPH0392233A (en) | Static pressure deciding method and its control device for air half-floating slide surface of machine tool | |
| SU308810A1 (en) | A METHOD FOR ELIMINATING VIBRATIONS ARISING IN THE CUTTING PROCESS | |
| JP2000190167A (en) | Spindle braking method and device of lathe for combined machining |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |