JPH11138305A - Spindle device - Google Patents
Spindle deviceInfo
- Publication number
- JPH11138305A JPH11138305A JP32052597A JP32052597A JPH11138305A JP H11138305 A JPH11138305 A JP H11138305A JP 32052597 A JP32052597 A JP 32052597A JP 32052597 A JP32052597 A JP 32052597A JP H11138305 A JPH11138305 A JP H11138305A
- Authority
- JP
- Japan
- Prior art keywords
- spring
- springs
- preload
- axis
- laminated
- 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
Landscapes
- Turning (AREA)
- Support Of The Bearing (AREA)
- Motor Or Generator Frames (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、切削加工や研削加
工に使用されるスピンドル装置に関し、特に軸受に予圧
荷重を与える定圧予圧構造のスピンドル装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a spindle device used for cutting and grinding, and more particularly to a spindle device having a constant-pressure preload structure for applying a preload to a bearing.
【0002】[0002]
【従来の技術】従来のスピンドル装置として、軸方向に
可動な一対の軸受間に軸方向に一定の予圧荷重を与え一
対の軸受に支持された回転軸の熱膨張等を吸収する定圧
予圧構造のスピンドル装置が知られている。2. Description of the Related Art As a conventional spindle device, a constant-pressure preload structure for applying a constant preload in the axial direction between a pair of bearings movable in the axial direction and absorbing thermal expansion of a rotating shaft supported by the pair of bearings. Spindle devices are known.
【0003】図4は、従来例のスピンドル装置の構造を
示す断面図である。このスピンドル装置は、回転部材2
とこの回転部材2を包む筒状の静止部材4とを備える。
回転部材2の外周面にはロータ20が固定され、静止部
材4の内周面にはステータ40が固定されている。静止
部材4は、一対の軸受5、6を介して、回転部材2を軸
RAの回りに回転自在に支持する。静止部材4は、一方
の軸受5を内部に保持する外筒部材41と、他方の軸受
6を内部に固定する内筒部材42とを備える。両部材4
1、42は、摺動面44を介して互いに軸RA方向に移
動可能となっており、両部材41、42の位置変化に応
じて両軸受5、6の間隔も変化する。また、外筒部材4
1の端部にはコイルバネ45を収容するスプリング穴4
1aが形成されており、スプリング穴41aに収納され
たコイルバネ45の一端は、内筒部材42に設けたフラ
ンジ部42aに当接している。このコイルバネ45によ
り、外筒部材41と内筒部材42が軸RAに沿った反対
方向に相対的に付勢される。これにより、回転部材2と
静止部材4との熱膨張差を吸収するとともに両軸受5、
6相互間に軸RA方向に沿ったほぼ一定の負荷を与える
ことができる。なお、このスピンドル装置では、コイル
バネ45のバネ定数を軸受5、6自体のバネ定数よりも
相当小さく(約1/1000程度)して、回転部材2の
伸び等に起因する軸受予圧荷重の変化を防止している。FIG. 4 is a sectional view showing the structure of a conventional spindle device. This spindle device includes a rotating member 2
And a cylindrical stationary member 4 enclosing the rotating member 2.
The rotor 20 is fixed to the outer peripheral surface of the rotating member 2, and the stator 40 is fixed to the inner peripheral surface of the stationary member 4. The stationary member 4 supports the rotating member 2 rotatably about the axis RA via a pair of bearings 5 and 6. The stationary member 4 includes an outer cylinder member 41 that holds one bearing 5 inside, and an inner cylinder member 42 that fixes the other bearing 6 inside. Both members 4
The members 1 and 42 can move in the direction of the axis RA via the sliding surface 44, and the distance between the bearings 5 and 6 changes according to the change in the position of the members 41 and 42. In addition, the outer cylinder member 4
A spring hole 4 for accommodating the coil spring 45 is provided at one end.
1 a is formed, and one end of the coil spring 45 housed in the spring hole 41 a is in contact with a flange portion 42 a provided on the inner cylinder member 42. By the coil spring 45, the outer cylinder member 41 and the inner cylinder member 42 are relatively urged in opposite directions along the axis RA. As a result, the difference in thermal expansion between the rotating member 2 and the stationary member 4 is absorbed, and the two bearings 5,
6, a substantially constant load along the direction of the axis RA can be applied. In this spindle device, the spring constant of the coil spring 45 is considerably smaller than the spring constant of the bearings 5 and 6 (about 1/1000), so that the change in the bearing preload caused by elongation of the rotating member 2 and the like can be reduced. Preventing.
【0004】また、一対の軸受に予圧荷重を与えて回転
軸の熱膨張等を吸収するスピンドル装置として、実公平
6−15484号公報に開示のものが存在する。このス
ピンドル装置では、上記のような予圧荷重を与える手段
として、一対の対向する皿バネを用いている。A spindle device disclosed in Japanese Utility Model Publication No. 6-15484 discloses a spindle device which applies a preload to a pair of bearings and absorbs thermal expansion of a rotary shaft. In this spindle device, a pair of opposed disc springs is used as a means for applying the above preload.
【0005】[0005]
【発明が解決しようとする課題】しかし、図4に示す前
者のスピンドル装置では、切削や研削等に際して、回転
部材2に加わっている荷重が軸RA方向に押し引き交互
に変化した場合、回転部材2が軸RA方向に自励振動し
てビビリと呼ばれる共振が生じてしまう場合がある。However, in the former spindle device shown in FIG. 4, when the load applied to the rotating member 2 is alternately pushed and pulled in the direction of the axis RA during cutting, grinding, or the like, the rotating member is not rotated. 2 may self-excitedly vibrate in the direction of the axis RA to cause resonance called chatter.
【0006】また、実公平6−15484号公報に開示
された後者のスピンドル装置においても、回転部材に加
わる荷重が軸方向に押し引き交互に変化した場合、上記
と同様に回転部等が軸方向に自励振動してビビリが発生
し得る。Also, in the latter spindle device disclosed in Japanese Utility Model Publication No. 6-15484, when the load applied to the rotating member alternately changes in the axial direction by pushing and pulling, the rotating portion and the like move in the axial direction similarly to the above. Self-excited vibration may cause chatter.
【0007】そこで、本発明は、様々な使用状態で自励
振動の発生を抑制することができるスピンドル装置を提
供することを目的とする。Accordingly, an object of the present invention is to provide a spindle device capable of suppressing the occurrence of self-excited vibration in various use states.
【0008】[0008]
【課題を解決するための手段】上記課題を解決するた
め、本発明のスピンドル装置は、第1の部材と、当該第
1の部材をともに回転可能に支持するとともに、互いに
軸方向に相対的に摺動可能な第2及び第3部材と、前記
第2部材を前記第3部材に対し軸方向に付勢する予圧荷
重を発生する予圧部材とを備える予圧構造のスピンドル
装置であって、前記予圧部材が、前記第2部材と前記第
3部材との間に挟持されるとともに、複数の板状のバネ
を面接触させるように積層した積層バネであることを特
徴とする。In order to solve the above-mentioned problems, a spindle device according to the present invention supports a first member and the first member so as to be rotatable together, and relatively rotates in the axial direction with each other. A spindle device having a preload structure, comprising: a slidable second and third member; and a preload member that generates a preload that axially urges the second member against the third member. The member is a laminated spring that is sandwiched between the second member and the third member, and is a laminated spring in which a plurality of plate-shaped springs are laminated so as to make surface contact.
【0009】また、好ましい態様では、前記積層バネ
が、凸方向を揃えて重ねた複数の皿バネであることを特
徴とする。In a preferred aspect, the laminated spring is a plurality of coned disc springs stacked in the same convex direction.
【0010】[0010]
【発明の実施の形態】以下、本発明の一実施形態である
スピンドル装置について図面を参照しつつ説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a spindle device according to an embodiment of the present invention will be described with reference to the drawings.
【0011】図1は、実施形態のスピンドル装置の構造
を示す縦断面図である。このスピンドル装置は、スピン
ドル軸である回転部材2とこの回転部材2を回転可能に
支持する筒状の静止部材4とを備える。FIG. 1 is a longitudinal sectional view showing the structure of the spindle device of the embodiment. This spindle device includes a rotating member 2 that is a spindle shaft and a cylindrical stationary member 4 that rotatably supports the rotating member 2.
【0012】静止部材4は、一組の軸受5を内部に固定
する外筒部材41と、一組の軸受6を内部に固定した軸
受スリーブである内筒部材42とを備える。内筒部材4
2は、軸RAの回りに対して図示を省略する回り止め機
構により回転しないようにしてあり、軸RA方向には移
動可能になっている。両部材41、42は、軸RAの回
りに同心に配置され互いに軸RA方向に相対的に移動可
能となっている。このように、両部材41、42の相対
位置を可変にすることにより、回転部材2が熱膨張によ
って軸RA方向に伸びた場合にもその伸長分だけ両軸受
5、6の間隔を変化させることができ、両軸受5、6に
不要な歪み負荷が発生することを防止できる。The stationary member 4 includes an outer cylindrical member 41 for fixing a set of bearings 5 therein, and an inner cylindrical member 42 as a bearing sleeve for fixing a set of bearings 6 therein. Inner tube member 4
Numeral 2 is prevented from rotating around the axis RA by a detent mechanism (not shown), and is movable in the direction of the axis RA. The two members 41 and 42 are arranged concentrically around the axis RA and are relatively movable in the direction of the axis RA. In this way, by making the relative positions of the two members 41 and 42 variable, even when the rotating member 2 extends in the direction of the axis RA due to thermal expansion, the interval between the two bearings 5 and 6 is changed by the amount of the extension. Thus, it is possible to prevent unnecessary distortion loads from being generated in the dual bearings 5 and 6.
【0013】両部材41、42の相対位置を可変にする
機構についてより詳細に説明する。外筒部材41の本体
41aの一端に固定した後蓋41bの内周は、複数のボ
ール7を介在させつつ、内筒部材42の外周に対向して
いる。すなわち、後蓋41bの内周と内筒部材42の外
周とは等距離に保たれ、後蓋41bと内筒部材42とは
軸RA方向に互いに滑らかに移動してこの軸RA方向の
相対位置が変化するようになっている。なお、後蓋41
bと内筒部材42との間隙に配置されたボール7は、図
示を省略する保持器に案内されている。A mechanism for making the relative positions of the two members 41 and 42 variable will be described in more detail. The inner circumference of the rear lid 41b fixed to one end of the main body 41a of the outer cylinder member 41 faces the outer circumference of the inner cylinder member 42 with a plurality of balls 7 interposed therebetween. In other words, the inner circumference of the rear lid 41b and the outer circumference of the inner cylinder member 42 are kept at the same distance, and the rear lid 41b and the inner cylinder member 42 move smoothly in the direction of the axis RA and move relative to each other in the direction of the axis RA. Is changing. Note that the rear cover 41
The ball 7 arranged in the gap between the inner cylinder member 42 and the inner cylinder member 42 is guided by a holder (not shown).
【0014】予圧部材9、両部材41、42を軸RAに
沿った反対方向に付勢する。これにより、外筒部材41
に固定された軸受5と、内筒部材42に固定された軸受
6相互間に軸RA方向に沿って離間するほぼ一定の荷重
を与えることができる。The preload member 9 and the two members 41 and 42 are urged in opposite directions along the axis RA. Thereby, the outer cylinder member 41
The bearing 5 fixed to the inner cylinder member 42 and the bearing 6 fixed to the inner cylinder member 42 can apply a substantially constant load that is separated in the direction of the axis RA.
【0015】予圧部材9は、内筒部材42の外周に、後
蓋41bの後端面である第1バネ座81と内筒部材42
に設けたフランジ部42aの前端面である第2バネ座8
2との間に挟持されいる第1及び第2の積層バネ91、
92を備える。各積層バネ91、92は、同一形状の一
対の皿バネをその凸方向を揃えて積層した環状体であ
り、その内径側で対向するように互いに接しており、そ
の外径側で両バネ座81、82と接している。The preload member 9 is provided on the outer periphery of the inner cylinder member 42 with a first spring seat 81 which is a rear end face of the rear lid 41b and an inner cylinder member 42
Spring seat 8, which is the front end face of flange portion 42a provided at
2, a first and a second laminated spring 91 sandwiched between
92. Each of the laminated springs 91 and 92 is an annular body formed by laminating a pair of disc springs of the same shape with their convex directions aligned, and is in contact with each other so as to face each other on the inner diameter side. 81 and 82 are in contact.
【0016】回転部材2の外周面にはロータ20が固定
され、外筒部材41の本体41aの内周面にはロータ2
0に対向してステータ40が固定されている。これらロ
ータ20とステータ40とでモータが構成される。な
お、ステータ40には、誘導用のコイル40aが巻設さ
れている。コイル40aに適当なタイミングで電力を供
給することにより、静止部材4に対して回転部材2が回
転する。なお、回転部材2の延長上には、例えば加工具
を接続することができ、この場合切削や研削といった加
工が可能になる。The rotor 20 is fixed on the outer peripheral surface of the rotating member 2, and the rotor 2 is fixed on the inner peripheral surface of the main body 41 a of the outer cylindrical member 41.
The stator 40 is fixed so as to face 0. The rotor 20 and the stator 40 constitute a motor. In addition, an induction coil 40 a is wound around the stator 40. By supplying power to the coil 40a at an appropriate timing, the rotating member 2 rotates with respect to the stationary member 4. A processing tool, for example, can be connected to the extension of the rotating member 2, and in this case, processing such as cutting and grinding becomes possible.
【0017】図2及び図3は、積層バネ92の構造を説
明する図である。図2は図1の積層バネ92を構成する
1つの皿バネ92aの構造を説明するためのものであ
り、図2(a)は平面図であり、図2(b)は側方断面
図である。この皿バネ92aは、環状で一方が凸になっ
ている板状体であり、凸側の外面USと凹側の内面IS
とを備える。FIGS. 2 and 3 are views for explaining the structure of the laminated spring 92. FIG. FIG. 2 is a view for explaining the structure of one disc spring 92a constituting the laminated spring 92 of FIG. 1. FIG. 2 (a) is a plan view, and FIG. 2 (b) is a side sectional view. is there. The disc spring 92a is an annular plate-like body having one convex side, and has a convex outer surface US and a concave inner surface IS.
And
【0018】図3は、積層バネ92の側方断面図であ
る。図1の積層バネ92は、図2に示す構造の一対の皿
バネ92a、92bを図3に示すように積層して構成し
たもので、皿バネ92aの内面ISと皿バネ92bの外
面USとを面接触させている。このように、両皿バネ9
2a、92bを面接触させて積層することにより、図1
に示す回転部材2が軸RA方向に自励振動してビビリと
呼ばれる共振が生じてしまうことを防止できる。すなわ
ちバネ座81、82間に挟まれて両積層バネ91、92
が圧縮された場合、例えば第2の積層バネ92は扁平に
変形する。これにより、第2の積層バネ92では、一対
の皿バネ92a、92b間の面接触によって摩擦力が発
生する。この摩擦力が回転部材2に軸RA方向の正逆荷
重を加えた場合の自励振動をダンピングさせてビビリ発
生を効果的に抑制する。なお、一対の皿バネ92a、9
2bを重ねないで外径同士が当接するように配置した場
合、一対の皿バネ92a、92b間で摩擦力が発生しな
いので、軸RA方向の正逆荷重に応じてを自励振動が発
生してしまう。FIG. 3 is a side sectional view of the laminated spring 92. The laminated spring 92 in FIG. 1 is configured by laminating a pair of disc springs 92a and 92b having the structure shown in FIG. 2 as shown in FIG. 3, and includes an inner surface IS of the disc spring 92a and an outer surface US of the disc spring 92b. Are in surface contact. Thus, both disc springs 9
2a and 92b are brought into surface contact with each other and
Can be prevented from causing the resonance called chatter due to the self-excited vibration of the rotating member 2 in the direction of the axis RA. That is, both laminated springs 91, 92 are sandwiched between the spring seats 81, 82.
Is compressed, for example, the second laminated spring 92 deforms flat. Thus, in the second laminated spring 92, a frictional force is generated due to surface contact between the pair of disc springs 92a and 92b. This frictional force damps self-excited vibration when a forward / reverse load is applied to the rotating member 2 in the direction of the axis RA, thereby effectively suppressing chatter. Note that a pair of disc springs 92a, 9
If the outer diameters are not overlapped with each other and the outer diameters are in contact with each other, no frictional force is generated between the pair of disc springs 92a and 92b. Would.
【0019】また、皿バネ92a、92bを積層して積
層バネ92を構成したことにより、コイルバネ等に比し
て軸RA方向のバネ定数を大きくすることができ、その
圧縮変形量を比較的小さくして、自励振動の発生を防止
する効果を高めることができる。なお、一対の積層バネ
91、92からなる予圧部材9のバネ定数は、軸受5、
6自体のバネ定数の約1/20〜1/70程度の範囲に
入るように調整してある。つまり、予圧部材9を構成す
る皿バネの材質及び形状やこれらを挟持するバネ座8
1、82の間隔等を適宜調節して予圧部材9のバネ定数
を適宜設定している。Further, by forming the laminated spring 92 by laminating the disc springs 92a and 92b, the spring constant in the direction of the axis RA can be increased as compared with a coil spring or the like, and the amount of compressive deformation thereof is relatively small. Thus, the effect of preventing the occurrence of self-excited vibration can be enhanced. The spring constant of the preloading member 9 including the pair of laminated springs 91 and 92 is
6 is adjusted so as to fall within a range of about 1/20 to 1/70 of the spring constant of itself. That is, the material and shape of the coned disc spring constituting the preload member 9 and the spring seat 8 for sandwiching them
The spring constant of the preloading member 9 is appropriately set by appropriately adjusting the intervals and the like of 1, 82.
【0020】以上、実施形態に即してこの発明を説明し
たが、この発明は、上記実施形態に限定されるものでは
ない。例えば、一対のバネ座81、82の間に挟持され
る予圧部材9は、単一の積層バネ91のみから構成した
ものであっても良く、さらに3つ以上の積層バネを連結
したものであってもよい。Although the present invention has been described with reference to the embodiment, the present invention is not limited to the above embodiment. For example, the preload member 9 sandwiched between the pair of spring seats 81 and 82 may be constituted by only a single laminated spring 91, and may be a combination of three or more laminated springs. You may.
【0021】また、積層バネ91、92は、2枚の皿バ
ネを積層したものに限らず、3枚以上の皿バネを凸方向
を揃えて積層したものであってもよい。Further, the laminated springs 91 and 92 are not limited to a laminate of two disc springs, but may be a laminate of three or more disc springs with their convex directions aligned.
【0022】また、積層バネ91、92は、内筒部材4
2と同心に配置する必要はなく、例えば両部材41、4
2のバネ座81、82の半径方向の幅にほぼ等しい直径
を有する小型の積層バネを複数準備し、これらを適当な
間隔で配置することとしても良い。The laminated springs 91 and 92 are connected to the inner cylindrical member 4.
It is not necessary to arrange concentrically with 2;
A plurality of small laminated springs having a diameter substantially equal to the radial width of the two spring seats 81 and 82 may be prepared, and these may be arranged at appropriate intervals.
【0023】また、積層バネ91、92は、皿バネを積
層したものに限らず、各種板状のバネを積層したものと
することができる。Further, the laminated springs 91 and 92 are not limited to laminated disc springs, but may be composed of laminated various plate-shaped springs.
【0024】また、両部材41、42の相対位置を可変
にする機構は、図1に示すボールブッシュタイプの摺動
機構に限らず、面接触で摺動する滑りタイプ等の各種機
構に置き換えることができる。The mechanism for making the relative positions of the two members 41 and 42 variable is not limited to the ball bush type sliding mechanism shown in FIG. Can be.
【0025】[0025]
【発明の効果】以上の説明から明らかなように、本発明
のスピンドル装置によれば、前記予圧部材が、前記第2
部材と前記第3部材との間に挟持されるとともに、複数
の板状のバネを面接触させるように積層した積層バネで
あるので、前記第2及び第3部材の相対的位置が変化し
て各バネが変形する際に各バネ間の面接触によって摩擦
力が発生する。この摩擦力が自励振動を減衰させて第1
部材に軸方向の正逆荷重を加えた場合の自励振動を減衰
させてビビリ発生を抑制する。As is apparent from the above description, according to the spindle device of the present invention, the preload member is provided with the second preload member.
Since it is a laminated spring that is sandwiched between a member and the third member and is laminated so that a plurality of plate-shaped springs are brought into surface contact, the relative position of the second and third members changes. When each spring is deformed, a frictional force is generated due to surface contact between the springs. This frictional force attenuates the self-excited vibration,
The self-excited vibration when a forward / reverse load in the axial direction is applied to the member is attenuated to suppress chatter.
【0026】また、好ましい態様では、前記積層バネ
が、凸方向を揃えて重ねた複数の皿バネであるので、簡
易な構造で効果的に自励振動の発生を防止できる。In a preferred embodiment, since the laminated spring is a plurality of disc springs stacked in the same convex direction, the self-excited vibration can be effectively prevented with a simple structure.
【図1】本発明の一実施形態のスピンドル装置の構造を
説明する縦断面図である。FIG. 1 is a longitudinal sectional view illustrating the structure of a spindle device according to an embodiment of the present invention.
【図2】(a),(b)は、図1のスピンドル装置の要
部を構成する皿バネの構造を示す正面図及び側方断面図
である。FIGS. 2 (a) and 2 (b) are a front view and a side sectional view showing a structure of a disc spring constituting a main part of the spindle device of FIG. 1;
【図3】図2の皿バネを積層した積層体の構造を説明す
る図である。FIG. 3 is a diagram illustrating a structure of a laminated body in which the disc springs of FIG. 2 are laminated.
【図4】従来のスピンドル装置の構造を説明する縦断面
図である。FIG. 4 is a longitudinal sectional view illustrating the structure of a conventional spindle device.
2 回転部材 4 静止部材 5,6 軸受 9 予圧部材 41 外筒部材 41a 本体 41b 後蓋 42 内筒部材 42a フランジ部 81、82 バネ座 91,92 第1及び第2の積層バネ 92a,92b 皿バネ RA 軸 Reference Signs List 2 rotating member 4 stationary member 5, 6 bearing 9 preload member 41 outer cylinder member 41a main body 41b back lid 42 inner cylinder member 42a flange portion 81, 82 spring seat 91, 92 first and second laminated springs 92a, 92b coned spring RA axis
Claims (1)
回転可能に支持するとともに、互いに軸方向に相対的に
摺動可能な第2及び第3部材と、前記第2部材を前記第
3部材に対し軸方向に付勢する予圧荷重を発生する予圧
部材とを備える予圧構造のスピンドル装置であって、 前記予圧部材は、前記第2部材と前記第3部材との間に
挟持されるとともに、複数の板状のバネを面接触させる
ように積層した積層バネであることを特徴とするスピン
ドル装置。1. A first member, a second member and a third member which rotatably support the first member together and are slidable relative to each other in the axial direction, and the second member A preload structure spindle device comprising: a preload member that generates a preload that urges a third member in an axial direction, wherein the preload member is sandwiched between the second member and the third member. And a stacked spring in which a plurality of plate-shaped springs are stacked so as to make surface contact.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32052597A JPH11138305A (en) | 1997-11-07 | 1997-11-07 | Spindle device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32052597A JPH11138305A (en) | 1997-11-07 | 1997-11-07 | Spindle device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH11138305A true JPH11138305A (en) | 1999-05-25 |
Family
ID=18122415
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP32052597A Pending JPH11138305A (en) | 1997-11-07 | 1997-11-07 | Spindle device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH11138305A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7311482B2 (en) | 2003-03-31 | 2007-12-25 | Nsk Ltd. | Main shaft device and machine tool with the same |
JP2011104743A (en) * | 2009-11-19 | 2011-06-02 | Sodick Co Ltd | Spindle device |
US20110255933A1 (en) * | 2008-12-24 | 2011-10-20 | Soraluce, S. Coop. | System for compensating for the ram drop in a machine-tool |
-
1997
- 1997-11-07 JP JP32052597A patent/JPH11138305A/en active Pending
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7311482B2 (en) | 2003-03-31 | 2007-12-25 | Nsk Ltd. | Main shaft device and machine tool with the same |
US7690873B2 (en) | 2003-03-31 | 2010-04-06 | Nsk Ltd. | Main shaft device and machine tool with the same |
US8052362B2 (en) | 2003-03-31 | 2011-11-08 | Nsk, Ltd. | Main shaft device and machine tool with the same |
US20110255933A1 (en) * | 2008-12-24 | 2011-10-20 | Soraluce, S. Coop. | System for compensating for the ram drop in a machine-tool |
US9033627B2 (en) * | 2008-12-24 | 2015-05-19 | Soraluce, S. Coop. | System for compensating for the ram drop in a machine-tool |
JP2011104743A (en) * | 2009-11-19 | 2011-06-02 | Sodick Co Ltd | Spindle device |
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