JPS618245A - Spindle support device - Google Patents
Spindle support deviceInfo
- Publication number
- JPS618245A JPS618245A JP12761784A JP12761784A JPS618245A JP S618245 A JPS618245 A JP S618245A JP 12761784 A JP12761784 A JP 12761784A JP 12761784 A JP12761784 A JP 12761784A JP S618245 A JPS618245 A JP S618245A
- Authority
- JP
- Japan
- Prior art keywords
- spindle
- magnets
- bearing
- bearings
- force
- 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
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 238000004321 preservation Methods 0.000 abstract 1
- 238000003754 machining Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000007935 neutral effect Effects 0.000 description 4
- 238000005520 cutting process Methods 0.000 description 2
- 230000020169 heat generation Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000005498 polishing Methods 0.000 description 1
- 230000001846 repelling effect Effects 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0406—Magnetic bearings
- F16C32/0408—Passive magnetic bearings
- F16C32/0423—Passive magnetic bearings with permanent magnets on both parts repelling each other
- F16C32/0429—Passive magnetic bearings with permanent magnets on both parts repelling each other for both radial and axial load, e.g. conical magnets
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/70—Stationary or movable members for carrying working-spindles for attachment of tools or work
-
- 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 buildup of machine tools, e.g. spindles, slides, actuators
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Machine Tool Units (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
「産業上の利用分野」
本発明は、工具の位置を正確にでき、高精度な加工がで
きるスピンドル支持装置に関する。DETAILED DESCRIPTION OF THE INVENTION "Field of Industrial Application" The present invention relates to a spindle support device that allows accurate tool positioning and highly accurate machining.
「従来の技術」
従来より、スピンドルを支持する装置としては、すべり
軸受やころがり軸受を用いたものがあった。"Prior Art" Conventionally, devices for supporting a spindle have used sliding bearings or rolling bearings.
特に高精度の加工用のものとしては、静圧軸受や空気軸
受等を利用したものがあった。Particularly for high-precision machining, there are those that utilize static pressure bearings, air bearings, and the like.
[発明が解決しようとする問題点]
しかるに1、すべり軸受やころがり軸受を用いた支持装
置では、高精度な加工は困難であった。それは、軸受自
体の精度に一定の限界があることにより、工具の位置に
狂いが生ずるためである。この他、軸受の発熱や摩耗も
原因となっている。又、静圧軸受や空気軸受等を用いた
支持装置は精密加工に向いているが、構造が複雑であり
、又、一定の回転域でしか使用されないという欠点があ
った。[Problems to be Solved by the Invention] However, 1. High precision machining is difficult with support devices using sliding bearings or rolling bearings. This is because the accuracy of the bearing itself has a certain limit, which causes the tool to be misaligned. Other causes include heat generation and wear of the bearings. Further, support devices using static pressure bearings, air bearings, etc. are suitable for precision machining, but they have the disadvantage that they have complicated structures and can only be used within a certain rotation range.
[問題点を解決するための手段」
そこで発明者は前記の諸欠点を解決すべり、鋭意、研究
を重ねた結果、本発明を、軸用磁石を斜設したフランジ
を軸方向に一対設けたスピンドルを、その軸用磁石と反
発する向きに軸受用磁石を斜設した軸受にて支持したス
ピンドル支持装置としたことにより、前述の諸欠点を解
決し、極めて精密な加工を可能にしたものである。[Means for Solving the Problems] Therefore, the inventor sought to solve the above-mentioned drawbacks, and as a result of intensive research, the present invention was developed to provide a spindle having a pair of flanges with shaft magnets disposed obliquely in the axial direction. By using a spindle support device in which the spindle is supported by a bearing in which a bearing magnet is installed diagonally in a direction that repels the shaft magnet, the above-mentioned drawbacks are solved and extremely precise machining becomes possible. .
「実施例」
以下、本発明の一実施例を第1図及び第2図に基づき説
明する。Aはスピンドルであり、軸方向に適宜の間隔を
有して一対のフランジ1,1が固着されている。このフ
ランジ1.1には、軸用磁石1a、1aが斜設されてい
る。この軸用磁石la、laは、そのフランジ1の斜面
(弧状面も含む)の一部分の法線方向に着磁された永久
磁石である。この場合、傾斜面を設けたフランジ1゜l
に軸用磁石1a、laが埋設されることが多いが、軸用
磁石1a、laのみが斜設されていることもある(第3
図参照)。又、フランジ1,1及び軸用磁石1a、la
の形状は、円錐台状(第1図、第2図参照)のみならず
、半球状等としてもよい(第4図参照)。又、円周方向
にチップ状にその軸用磁石1a、laを所定間隔に配設
することもある。さらに、フランジ1.1に別体とした
軸用磁石1a、laを斜設せず、傾斜面を設けたフラン
ジ1,1内体が着磁されて、軸用磁石1a。“Example” An example of the present invention will be described below with reference to FIGS. 1 and 2. A is a spindle, and a pair of flanges 1, 1 are fixedly spaced apart from each other in the axial direction. Shaft magnets 1a, 1a are obliquely installed on this flange 1.1. The shaft magnets la, la are permanent magnets magnetized in the normal direction of a part of the slope (including the arcuate surface) of the flange 1. In this case, the flange with an inclined surface 1゜l
The shaft magnets 1a and la are often buried in the shaft, but sometimes only the shaft magnets 1a and la are installed obliquely (the third
(see figure). Moreover, the flanges 1, 1 and the shaft magnets 1a, la
The shape may be not only a truncated cone (see FIGS. 1 and 2) but also a hemispherical shape (see FIG. 4). Further, the shaft magnets 1a and 1a may be arranged in the form of chips in the circumferential direction at predetermined intervals. Further, the separate shaft magnets 1a, 1a are not provided obliquely on the flange 1.1, but the inner bodies of the flanges 1, 1 having inclined surfaces are magnetized to form the shaft magnet 1a.
1aを兼ねていることもある(第5図参照)。It may also serve as 1a (see Figure 5).
2は軸受であり、クイル3に取付けられている。2 is a bearing, which is attached to the quill 3.
軸受2,2は、前記フランジ1.1に各々対向して設け
られている。この軸受2,2は、特にクイル3と別体と
されず、クイル3の一部を軸受2゜2として用いること
もある。この軸受2,2には、前記軸用磁石1a、la
と反発力する向きに着磁された軸受用磁石2a、2aが
斜設されている。Bearings 2, 2 are provided opposite each other to the flange 1.1. The bearings 2, 2 are not particularly separate from the quill 3, and a part of the quill 3 may be used as the bearing 2°2. The shaft magnets 1a, la are attached to the bearings 2, 2.
Bearing magnets 2a, 2a magnetized in a direction that produces a repulsive force are diagonally disposed.
この軸受用磁石2a、2aは、その軸受2.2の斜面(
弧状面も含む)の一部分の法線方向に着磁された永久磁
石である。この軸受用磁石2a、2aは、固定式のため
、場合によっては電磁石が用いられることもある。又、
この軸受用磁石2a。These bearing magnets 2a, 2a are connected to the slope (
It is a permanent magnet that is magnetized in the normal direction of a part of the surface (including arcuate surfaces). Since the bearing magnets 2a, 2a are fixed, electromagnets may be used in some cases. or,
This bearing magnet 2a.
2aは軸受2.2と別体とされず、軸受2.2内体が着
磁されて軸受用磁石’la、 2aを兼ねることもあ
る(第5図参照)。この場合にも、軸受用磁石2a、
2aは、前記軸用磁石1a、laに対応した形状を有
している。2a is not separate from the bearing 2.2, and the inner body of the bearing 2.2 may be magnetized to serve as the bearing magnet 'la, 2a (see FIG. 5). Also in this case, the bearing magnet 2a,
2a has a shape corresponding to the shaft magnets 1a and la.
前記クイル3内に前記スピンドルAが挿入されており、
このスピンドルAは、フランジ1.1に斜設された軸用
磁石1a、laと前記軸受2,2に斜設された軸受用軸
受2a、2aとの反発力にて支持されている。このとき
、スピンドル八がクイル3内番ど挿入された後に、片方
のフランジ1がスピンドルAに挿入されて取付けられる
ことが多い(第2図乃至第5図参照)。又、片方の軸受
2を外しておいて、スピンドルAを挿入後に、その軸受
2が頓着できるようにした実施例もある(第6図参照)
。The spindle A is inserted into the quill 3,
This spindle A is supported by the repulsive force of shaft magnets 1a, la obliquely installed on the flange 1.1 and bearings 2a, 2a obliquely installed on the bearings 2, 2. At this time, after the spindle 8 is inserted into the quill 3, one flange 1 is often inserted and attached to the spindle A (see FIGS. 2 to 5). There is also an embodiment in which one of the bearings 2 is removed and the bearing 2 can be left in place after inserting the spindle A (see Figure 6).
.
図中4は前記スピンドルAにフランジ1を取付ける取付
ナンド、5は砥石等の切削又は研削用の工具、6は工具
取付用ナツトである。In the figure, 4 is a mounting nut for attaching the flange 1 to the spindle A, 5 is a cutting or grinding tool such as a grindstone, and 6 is a tool mounting nut.
「作用」
本発明の作用状態を第2図及び第7図乃至第11図に基
づいて説明する。第2図では、スピンドルAが中立状態
にある。このとき、磁石1a、1aと軸受用磁石2a、
2aが反発している。この反発力によりスピンドルAが
そのフランジ1.1において受ける力は、スピンドルA
の前方(図では左方)のフランジ1の上部、前方のフラ
ンジ1の下部、後方(図では右方)のフランジ1の上部
及び後方のフランジ1の下部において釣り合っている。"Operation" The operation state of the present invention will be explained based on FIG. 2 and FIGS. 7 to 11. In FIG. 2, spindle A is in a neutral state. At this time, the magnets 1a, 1a and the bearing magnet 2a,
2a is repelling. The force that spindle A experiences at its flange 1.1 due to this repulsive force is
The upper part of the front (left side in the figure) flange 1, the lower part of the front flange 1, the upper part of the rear (right side in the figure) flange 1, and the lower part of the rear flange 1 are balanced.
即ちF 1 、F 2 + F 3 + F 4は大き
さが等しい(第7図参照)。ここで、そのF1+FII
+F3.F4はそのスピンドルAを中心にして各々積分
して得られた反発力を略示している。従ってそれらの水
平方向の分力の和も垂直方向の分力の和も零となる。即
ち、スピンドルAは、第2図に示すようにクイル3の略
センターの中立位置で保持されている。That is, F 1 and F 2 + F 3 + F 4 have the same size (see FIG. 7). Here, that F1+FII
+F3. F4 schematically represents the repulsion force obtained by integrating each around the spindle A. Therefore, the sum of the component forces in the horizontal direction and the sum of the component forces in the vertical direction become zero. That is, the spindle A is held at a neutral position approximately at the center of the quill 3, as shown in FIG.
第8図では、スピンドルAに負荷等が加わり、スピンド
ルAが同図において上方に変位した状態を示す。このと
き、軸用磁石1a、laと軸受用磁石2a、 2aと
の反発力によりスピンドルAがそのフランジ1.1にお
いて受ける力は以下のようになる。即ち、両フランジ1
.1の上部においては、軸用磁石1a、laと軸受用磁
石2a、2aとの間の距離が両フランジ1.1の下部に
おける距離よりも小さくなる。このため前方のフランジ
1の上部及び後方のフランジ1の上部における反発力は
、前方のフランジ1の下部及び後方のフランジ1の下部
における反発力よりも大きくなる。FIG. 8 shows a state in which a load or the like is applied to the spindle A and the spindle A is displaced upward in the figure. At this time, the force that the spindle A receives at its flange 1.1 due to the repulsive force between the shaft magnets 1a, la and the bearing magnets 2a, 2a is as follows. That is, both flanges 1
.. In the upper part of 1.1, the distance between the shaft magnets 1a, la and the bearing magnets 2a, 2a is smaller than in the lower part of both flanges 1.1. Therefore, the repulsive force at the upper part of the front flange 1 and the upper part of the rear flange 1 is larger than the repulsive force at the lower part of the front flange 1 and the lower part of the rear flange 1.
これらの反発力Fl、F2.F31 F4を水平方向
と垂直方向に1分解して、
Fu =FSi 十FRt
Fa =FSa +FR3
Ft −FSt +FRII
F4 −F S4 +F R4
とする。水平方向についてみると、スピンドルAが水平
方向に受ける力Fsは、
FS=FS1 +FS3 +FS2 +FS4となる。These repulsive forces Fl, F2. F31 F4 is decomposed into 1 part in the horizontal direction and vertical direction to obtain Fu = FSi + FRt Fa = FSa + FR3 Ft - FSt + FRII F4 - F S4 + FR4. Looking at the horizontal direction, the force Fs that the spindle A receives in the horizontal direction is FS=FS1 +FS3 +FS2 +FS4.
ここでFSu = −FSa、Fs2−−Fs4である
ので、Fs =0となる。即ち、スピンドルAは水平方
向に力を受けない。Here, since FSu=-FSa, Fs2--Fs4, Fs=0. That is, spindle A receives no force in the horizontal direction.
一方垂直方向についてみると、スピンドルAが垂直方向
に受けるちからFrは、
F r=FRi +FRa +FR2+FR4となる。On the other hand, in the vertical direction, the force Fr that the spindle A receives in the vertical direction is Fr=FRi +FRa +FR2+FR4.
ここでFRi =FRa 、FR2=FR4であり、且
つIFRI l>IFR21である。従ってスピンドル
Aは、前後で等しい下向きの力を受けることになる。即
ち、スピンドルAが上方に移動したときは、軸角磁石1
a、laと軸受用磁石2a、2aとの反発力により、ス
ピンドルAは 。Here, FRi=FRa, FR2=FR4, and IFRI>IFR21. Therefore, the spindle A will be subjected to an equal downward force on both sides. That is, when the spindle A moves upward, the shaft angle magnet 1
Due to the repulsive force between a and la and the bearing magnets 2a and 2a, the spindle A moves as follows.
下方(旧位)に戻されるような力を受ける(第9図参照
)。It is subjected to a force that causes it to return downward (to its old position) (see Figure 9).
又、スピンドルAに負荷等が加わり、スピンドルAが後
方(第10図では右方)に変位した状態が第10図に示
されている。このとき軸角磁石1a、laと軸受用磁石
2a、2aとの反発力により、スピンドルAがそのフラ
ンジ1.1において受ける力は以下のようになる。即ち
、前方のフランジ1の上部及び下部においては、軸角磁
石1a。Further, FIG. 10 shows a state in which the spindle A is displaced rearward (to the right in FIG. 10) due to a load applied to the spindle A. At this time, the force that the spindle A receives at its flange 1.1 due to the repulsive force between the shaft angle magnets 1a, la and the bearing magnets 2a, 2a is as follows. That is, in the upper and lower parts of the front flange 1, there are shaft angle magnets 1a.
1aと軸受用磁石2a、2aとの間の距離は、後方のフ
ランジ1の上部及び下部における距離よりも小さくなる
。このため前方のフランジ1の上部及び下部における反
発力は、後方のフランジ1の上部及び下部における反発
力よりも大きくなる。The distance between 1a and the bearing magnets 2a, 2a is smaller than the distance at the upper and lower parts of the rear flange 1. Therefore, the repulsive force at the upper and lower parts of the front flange 1 is larger than the repulsive force at the upper and lower parts of the rear flange 1.
これらの反発力F11 F2 r F3.F4を水
平方向と垂直方向に分解して、
Fz =FSX IFRI
F2 =FS2+FR2
Fa −FSa +FR3
F4 =FS4+FR4
とする。垂直方向についてみると、スピンドルAが垂直
方向に受ける力Frは、
F r=FRz +FR2+FR3+FR4となる。These repulsive forces F11 F2 r F3. F4 is decomposed into the horizontal direction and the vertical direction, and Fz =FSX IFRI F2 =FS2+FR2 Fa -FSa +FR3 F4 =FS4+FR4. In the vertical direction, the force Fr that the spindle A receives in the vertical direction is Fr=FRz +FR2+FR3+FR4.
ここでFRI =−FR2、FR3=−ドR4であるの
でFr =0となる。即ち、スピンドルAは、垂直方向
に力を受けない。Here, since FRI=-FR2 and FR3=-R4, Fr=0. That is, spindle A is not subjected to any force in the vertical direction.
一方水平方向についてみると、スピンドルAが水平方向
に受ける力Fsは、
Fs−FSi +FS2 +FS3+FS4となる。こ
こでFSz =FS2 、FSs =FS4であり、且
つ1Fsz l>1Fsa lである。従うてスピンド
ルAは、上下で等しい前向きの力を受けることになる。On the other hand, in the horizontal direction, the force Fs that the spindle A receives in the horizontal direction is Fs-FSi +FS2 +FS3+FS4. Here, FSz = FS2, FSs = FS4, and 1Fsz l>1Fsa l. Therefore, spindle A will receive equal forward force on the top and bottom.
即ち、スピンドルAが後方に移動したときは、軸角磁石
1a、laと軸受用磁石2a、2aとの反発力により、
スピンドルAは、前方(旧位)に戻されるような力を受
ける(第11図参照)。That is, when the spindle A moves backward, due to the repulsive force between the shaft angle magnets 1a, la and the bearing magnets 2a, 2a,
Spindle A receives a force that causes it to return to the front (old position) (see FIG. 11).
以上説明したことから明らかなように、スピンドルAに
は、半径方向又は軸方向の何れに変位した場合でも常に
元の位置へ戻そうとする復元力が作用する。As is clear from the above explanation, a restoring force always acts on the spindle A to return it to its original position even if it is displaced in either the radial direction or the axial direction.
「発明の効果」
本発明においては、軸角磁石1a、laを斜設したフラ
ンジ1,1を軸方向に一対設けたスピンドルAを、その
軸角磁石1a、laと反発する向きに軸受用磁石2a、
2aを斜設した軸受2,2にて支持したスピンドル支持
装置とした構成により、以下の効果を奏する。即ち、第
1に取付時のみならず、負荷が加わる加工中であっても
工具5の位置を正確にでき、第2に特にクイル3の軸心
にスピンドルAを支持できるし、第3に騒音、振動等を
極めて小さくでき、第4に製造、保守等が容易にできる
等の効果を奏する。"Effects of the Invention" In the present invention, a spindle A is provided with a pair of flanges 1, 1 on which shaft angle magnets 1a, la are disposed obliquely. 2a,
The configuration in which spindle support device 2a is supported by oblique bearings 2, 2 provides the following effects. That is, firstly, the tool 5 can be positioned accurately not only during installation but also during machining where a load is applied; secondly, the spindle A can be supported particularly at the axis of the quill 3; and thirdly, the noise can be reduced. , vibration, etc. can be extremely reduced, and fourthly, manufacturing, maintenance, etc. can be facilitated.
以上について詳述すると、まず、本発明のスピンドル支
持装置は、軸角磁石1a、laと軸受用磁石2a、
2aとの間に、反発力が作用する。これにより半径方向
及び軸方向とも、定位置から少しでも移動する(ずれる
)とスピンドルAに定位置に戻そうとする力が作用する
。従って、取付時に半径方向や軸方向にずれることなく
極めて正確な位置に取付けることができる。又、切削や
研削等の加工中に負荷が加わり工具5と共1にスピンド
ルAが半径方向や軸方向に移動することがある。この場
合は前記復元力により、スピンドルAが正確な位置に復
元する。特にその復元力は移動変化が大きければ、大き
い程復元力が増大し、旧位に復元できる大きな利点があ
る。従って工具5は、どのような回転域においても常に
正確な位置に保たれる。このため艙面加工のような高精
度の要求される加工に極めて好適である。To explain the above in detail, first, the spindle support device of the present invention includes shaft angle magnets 1a, la, a bearing magnet 2a,
2a, a repulsive force acts between it and 2a. As a result, when the spindle A moves (deviates) even slightly from the home position in both the radial and axial directions, a force acts on the spindle A to return it to the home position. Therefore, it can be installed in an extremely accurate position without shifting in the radial or axial direction during installation. Further, during machining such as cutting or grinding, a load is applied and the spindle A together with the tool 5 may move in the radial or axial direction. In this case, the restoring force restores the spindle A to the correct position. In particular, the larger the change in movement, the greater the restoring power, which has the great advantage of being able to restore it to its previous position. Therefore, the tool 5 is always kept in an accurate position in any rotation range. For this reason, it is extremely suitable for machining that requires high precision, such as machining of roof surfaces.
又、本発明のスピンドル支持装置によれば、摩擦部分が
ないため摩耗、発熱等の生ずる恐れがない。このため、
これらによる位置の狂いも生じない。従って、工具5を
正確な位置に保ちつづけることができる。Further, according to the spindle support device of the present invention, since there is no frictional part, there is no possibility of wear, heat generation, etc. occurring. For this reason,
Misalignment due to these does not occur. Therefore, the tool 5 can be kept in an accurate position.
第2に、スピンドルAの軸方向に、軸角磁石1a、la
を斜設したフランジ1.1を一対設け、これに対応して
軸受用磁石2a、 2aを斜設した軸受2,2を設け
たことで、そのスピンドルAの軸方向に所定間隔を有し
て軸受支持構造が2箇所設けられたこととなり、そのク
イル3に対してスピンドルAの軸心が著しくぶれないよ
うにでき、常に高精度のセンター支持が可能である。従
って前述の磁力による復元力の作用と、その軸受構造を
一対設けたこととが相乗的に作用して負荷状態であって
も、従来の静圧軸受支持構造や空気軸受支持構造とは異
なり、常に高精度の中立位置を保つことができ、これに
よって高精度の研摩、研削が可能であるという大きな効
果を発揮しうる。Second, in the axial direction of the spindle A, the shaft angle magnets 1a, la
By providing a pair of flanges 1.1 with obliquely installed flanges 1.1, and correspondingly providing bearings 2, 2 with obliquely installed bearing magnets 2a, 2a, a predetermined interval is provided in the axial direction of the spindle A. Since the bearing support structure is provided at two locations, the axis of the spindle A can be prevented from shifting significantly with respect to the quill 3, and highly accurate center support is always possible. Therefore, the above-mentioned restoring force due to the magnetic force and the provision of the pair of bearing structures act synergistically, and even under load, unlike conventional hydrostatic bearing support structures and air bearing support structures, A highly accurate neutral position can be maintained at all times, which has the great effect of enabling highly accurate polishing and grinding.
第3に、本発明のスピンドル支持装置によれば、前述の
ように摩擦部分がないため、加工中に騒音、振動等が生
じない。従って作業を快適に進めることができ、作業能
率も向上できるという効果も有する。Thirdly, according to the spindle support device of the present invention, since there is no frictional part as described above, no noise, vibration, etc. are generated during processing. Therefore, it has the effect that work can be carried out comfortably and work efficiency can also be improved.
第4に、本発明のスピンドル支持装置は極めて簡単な部
品より構成されているため、前述のように極めて高性能
ながら製造、保守が容易であるという著しい利点も有す
る。Fourthly, since the spindle support device of the present invention is constructed from extremely simple parts, it also has the remarkable advantage of being easy to manufacture and maintain, although it has extremely high performance as described above.
なお、フランジ1を取付ける際に取付ナツト4を用いて
行うならば、この取付ナツト4を締付けることにより、
両フランジ1.1と両軸受2.2との間の距離を変化さ
せることができる。これがため軸角磁石1a、laと軸
受用磁石2a、2aとによる反発力を適宜調整すること
ができるという効果も生ずる。このとき、第2図乃至第
5図において水平方向の前後の軸角磁石1a、laと軸
受用磁石2a、 2aとの反発力が等しく保たれて調
整され、片寄り等が生ずることもない効果もある。In addition, if the mounting nut 4 is used when installing the flange 1, by tightening the mounting nut 4,
The distance between the flanges 1.1 and the bearings 2.2 can be varied. This also brings about the effect that the repulsive force generated by the shaft angle magnets 1a, la and the bearing magnets 2a, 2a can be adjusted as appropriate. At this time, as shown in FIGS. 2 to 5, the repulsive force between the front and rear shaft angle magnets 1a, la and the bearing magnets 2a, 2a in the horizontal direction is maintained equal and adjusted, and there is an effect that no deviation occurs. There is also.
図面は本発明の一実施例を示すものであって、第1図は
本発明の一部切除した斜視図、第2図は第1部の断面図
、第3図乃至第6図は本発明の他の実施例を示す断面図
、第7図はスピンドルが中立状態にあるときにスピンド
ルに作用する力を示す作用図、第8図はスピンドルが上
方に変位した状態の断面図、第9図は第8図の状態にお
いてスピンドルに作用する力を示す作用図、第10図は
スピンドルが下方に変位した状態の断面図、第11図は
第10図の状態においてスピンドルに作用する力を示す
作用図である。
A・・・・・・スピンドル、 1・・・・・・フラ
ンジ、la・・・・・・軸角磁石、 2・・・・・
・軸受、2a・・・・・・軸受用磁石。The drawings show one embodiment of the present invention, in which FIG. 1 is a partially cutaway perspective view of the present invention, FIG. 2 is a sectional view of the first part, and FIGS. 3 to 6 are illustrations of the present invention. 7 is an action diagram showing the force acting on the spindle when the spindle is in a neutral state, FIG. 8 is a sectional view showing the spindle in an upwardly displaced state, and FIG. 9 is a sectional view showing another embodiment of the present invention. is an action diagram showing the force acting on the spindle in the state shown in Fig. 8, Fig. 10 is a cross-sectional view of the state in which the spindle is displaced downward, and Fig. 11 is an action diagram showing the force acting on the spindle in the state shown in Fig. 10. It is a diagram. A... Spindle, 1... Flange, la... Shaft angle magnet, 2...
・Bearing, 2a...Bearing magnet.
Claims (1)
たスピンドルを、その軸用磁石と反発する向きに軸受用
磁石を斜設した軸受にて支持したことを特徴とするスピ
ンドル支持装置。(1) A spindle support device characterized in that a spindle having a pair of flanges arranged in the axial direction on which shaft magnets are disposed is supported by a bearing on which bearing magnets are disposed diagonally in a direction that repels the shaft magnets. .
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12761784A JPS618245A (en) | 1984-06-22 | 1984-06-22 | Spindle support device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12761784A JPS618245A (en) | 1984-06-22 | 1984-06-22 | Spindle support device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS618245A true JPS618245A (en) | 1986-01-14 |
Family
ID=14964515
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP12761784A Pending JPS618245A (en) | 1984-06-22 | 1984-06-22 | Spindle support device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS618245A (en) |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6439926U (en) * | 1987-09-04 | 1989-03-09 | ||
JPH03213717A (en) * | 1990-01-16 | 1991-09-19 | Seiko Electronic Components Ltd | Magnetic bearing |
JPH0473619U (en) * | 1990-11-07 | 1992-06-29 | ||
US5193953A (en) * | 1990-08-13 | 1993-03-16 | Fortuna-Werke Maschinenfabrik Gmbh | High-speed drilling or milling spindle |
WO2004022988A1 (en) * | 2002-09-03 | 2004-03-18 | Seiko Epson Corporation | Magnetic bearing device |
WO2006074070A2 (en) * | 2004-12-30 | 2006-07-13 | Rozlev Corp., Llc | A magnetic bearing assembly using repulsive magnetic forces |
WO2006134180A1 (en) * | 2005-06-10 | 2006-12-21 | Loxin 2002, S.L. | Toolholder comprising a suction system |
WO2007049084A1 (en) * | 2005-10-25 | 2007-05-03 | Oroszi Janos | Magnetic bearing for radial and axial load with repulsive permanent magnets |
WO2011154623A1 (en) * | 2010-06-09 | 2011-12-15 | Eric Vangraefschepe | Rotating machine comprising a device for supporting and centring the rotor thereof |
WO2011158382A1 (en) * | 2010-06-16 | 2011-12-22 | Ikeda Kazuhiro | Magnetic shaft bearing assembly and system incorporating same |
CN103016526A (en) * | 2012-12-28 | 2013-04-03 | 贵州新天地设备有限公司 | Bearing bush type magnetic levitation supporting mechanism and ball-milling device |
CN103133531A (en) * | 2012-12-28 | 2013-06-05 | 贵州新天地设备有限公司 | Bearing type magnetic suspension bearing mechanism and ball-milling equipment |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5050530A (en) * | 1973-09-07 | 1975-05-07 |
-
1984
- 1984-06-22 JP JP12761784A patent/JPS618245A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5050530A (en) * | 1973-09-07 | 1975-05-07 |
Cited By (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6439926U (en) * | 1987-09-04 | 1989-03-09 | ||
JPH0518495Y2 (en) * | 1987-09-04 | 1993-05-17 | ||
JPH03213717A (en) * | 1990-01-16 | 1991-09-19 | Seiko Electronic Components Ltd | Magnetic bearing |
US5193953A (en) * | 1990-08-13 | 1993-03-16 | Fortuna-Werke Maschinenfabrik Gmbh | High-speed drilling or milling spindle |
JPH0473619U (en) * | 1990-11-07 | 1992-06-29 | ||
WO2004022988A1 (en) * | 2002-09-03 | 2004-03-18 | Seiko Epson Corporation | Magnetic bearing device |
WO2006074070A3 (en) * | 2004-12-30 | 2006-11-09 | Rozlev Corp Llc | A magnetic bearing assembly using repulsive magnetic forces |
US7126244B2 (en) | 2004-12-30 | 2006-10-24 | Rozlev Corp., Llc | Magnetic bearing assembly using repulsive magnetic forces |
WO2006074070A2 (en) * | 2004-12-30 | 2006-07-13 | Rozlev Corp., Llc | A magnetic bearing assembly using repulsive magnetic forces |
WO2006134180A1 (en) * | 2005-06-10 | 2006-12-21 | Loxin 2002, S.L. | Toolholder comprising a suction system |
ES2293775A1 (en) * | 2005-06-10 | 2008-03-16 | Loxin 2002, S.L. | Toolholder comprising a suction system |
WO2007049084A1 (en) * | 2005-10-25 | 2007-05-03 | Oroszi Janos | Magnetic bearing for radial and axial load with repulsive permanent magnets |
WO2011154623A1 (en) * | 2010-06-09 | 2011-12-15 | Eric Vangraefschepe | Rotating machine comprising a device for supporting and centring the rotor thereof |
FR2961278A1 (en) * | 2010-06-09 | 2011-12-16 | Eric Vangraefschepe | ROTATING MACHINE COMPRISING A DEVICE FOR SUSTAINING AND CENTERING ITS ROTOR |
WO2011158382A1 (en) * | 2010-06-16 | 2011-12-22 | Ikeda Kazuhiro | Magnetic shaft bearing assembly and system incorporating same |
CN103016526A (en) * | 2012-12-28 | 2013-04-03 | 贵州新天地设备有限公司 | Bearing bush type magnetic levitation supporting mechanism and ball-milling device |
CN103133531A (en) * | 2012-12-28 | 2013-06-05 | 贵州新天地设备有限公司 | Bearing type magnetic suspension bearing mechanism and ball-milling equipment |
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