JPH0448516Y2 - - Google Patents

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Publication number
JPH0448516Y2
JPH0448516Y2 JP18055985U JP18055985U JPH0448516Y2 JP H0448516 Y2 JPH0448516 Y2 JP H0448516Y2 JP 18055985 U JP18055985 U JP 18055985U JP 18055985 U JP18055985 U JP 18055985U JP H0448516 Y2 JPH0448516 Y2 JP H0448516Y2
Authority
JP
Japan
Prior art keywords
main shaft
flange
rotating main
rotating
motor
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
Application number
JP18055985U
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Japanese (ja)
Other versions
JPS62115119U (en
Priority date (The priority date 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 date listed.)
Filing date
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Priority to JP18055985U priority Critical patent/JPH0448516Y2/ja
Publication of JPS62115119U publication Critical patent/JPS62115119U/ja
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Expired legal-status Critical Current

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  • Testing Of Balance (AREA)

Description

【考案の詳細な説明】 産業上の利用分野 本考案は、小形精密回転部品用の動釣合試験機
に関する。
[Detailed Description of the Invention] Industrial Application Field The present invention relates to a dynamic balance testing machine for small precision rotating parts.

従来の技術 第5図、第6図に従来の竪形動釣合試験機の主
要部を示した。
Prior Art Figures 5 and 6 show the main parts of a conventional vertical dynamic balance tester.

この図において、上端部に供試体取付台30お
よびプーリ31を備えた回転主軸32は、玉軸受
33,33によりボデイ34に支持されている。
ボデイ34は基板35から突出した2枚の板ばね
36,36に支持されている。回転主軸32はベ
ルト37、プーリ31を介してモータ(図示せ
ず)により回転する。このとき、供試体38のア
ンバランス量により遠心力が発生し、板ばね36
のたわみを伴つてボデイ34がX方向に変位し、
その変位量が変位センサ39により検出され供試
体38のアンバランス量が求められる。
In this figure, a rotating main shaft 32 having a specimen mount 30 and a pulley 31 at its upper end is supported by a body 34 by ball bearings 33, 33.
The body 34 is supported by two leaf springs 36, 36 protruding from a base plate 35. The rotating main shaft 32 is rotated by a motor (not shown) via a belt 37 and a pulley 31. At this time, centrifugal force is generated due to the unbalance amount of the specimen 38, and the leaf spring 36
The body 34 is displaced in the X direction with a deflection of
The amount of displacement is detected by the displacement sensor 39, and the amount of unbalance of the specimen 38 is determined.

考案が解決しようとする問題点 しかし、従来構成では、玉軸受33,33のボ
ール転動面の凹凸による振動発生、ベルト37の
張力の変動や振れ、そしてベルト37の曲げ剛性
の不一様性等による振動発生があり、高精度の試
験機においては、この振動レベルがアンバランス
による変位量と同程度になり、振動レベルによ
り、試験精度が規定されるという問題があつた。
Problems to be solved by the invention However, in the conventional configuration, vibrations occur due to unevenness of the ball rolling surfaces of the ball bearings 33, 33, fluctuations and vibrations in the tension of the belt 37, and non-uniformity in the bending rigidity of the belt 37. In high-precision testing machines, the level of this vibration is comparable to the amount of displacement due to unbalance, and there was a problem that the test accuracy was determined by the vibration level.

したがつて、本考案は試験精度の向上化の障害
となる振動ノイズを低減する動釣合試験機を提供
することを目的としている。
Therefore, it is an object of the present invention to provide a dynamic balance tester that reduces vibration noise that is an obstacle to improving test accuracy.

問題点を解決するための手段 上記目的を達成するため、本考案は、一端部に
供試体取付台を有する回転主軸と、この回転主軸
をラジアル動圧流体軸受およびスラスト動圧流体
軸受を介して支持するボデイと、このボデイを直
径一方向に変位自在に支持する板ばねと、その直
径一方向の変位量を検出する変位センサと、上記
回転主軸の他端部とモータの出力回転軸間を非接
触で連結する磁気継手とを備えた。
Means for Solving the Problems In order to achieve the above object, the present invention includes a rotating main shaft having a specimen mount at one end, and a rotating main shaft connected to the rotating main shaft through a radial hydrodynamic bearing and a thrust hydrodynamic bearing. A supporting body, a leaf spring that supports the body so as to be displaceable in one diametrical direction, a displacement sensor that detects the amount of displacement in one diametrical direction, and a connection between the other end of the rotating main shaft and the output rotating shaft of the motor. Equipped with a magnetic joint that connects without contact.

作 用 モータの出力回転軸が駆動すると、回転主軸
は、磁気継手の磁気力により非接触で上記出力回
転軸に追従して回転する。このとき、ラジアルお
よびスラストの油動圧軸受により動圧が発生し、
回転主軸は油膜に支持されて回転する。また、こ
の回転時、回転主軸に取りつけられた供試体のア
ンバランス量により遠心力が発生し、板ばねのた
わみを伴つてボデイが直径一方向に変位し、その
変位量が変位センサにより検出され、供試体のア
ンバランス量が求められる。
Operation When the output rotation shaft of the motor is driven, the rotation main shaft rotates following the output rotation shaft without contact due to the magnetic force of the magnetic coupling. At this time, dynamic pressure is generated by the radial and thrust hydraulic pressure bearings,
The rotating main shaft rotates while being supported by an oil film. Also, during this rotation, centrifugal force is generated due to the unbalanced amount of the specimen attached to the rotating main shaft, and the body is displaced in one diameter direction with the deflection of the leaf spring, and the amount of displacement is detected by the displacement sensor. , the amount of unbalance of the specimen is determined.

実施例 第1図は本考案の一実施例にかかる竪形動釣合
試験機の一部切欠正面図である。
Embodiment FIG. 1 is a partially cutaway front view of a vertical dynamic balance tester according to an embodiment of the present invention.

この図において、回転主軸1は大径部1aと小
径部1bから構成されている。大径部1aは有底
の軸受箱2に嵌合されて鉛直に支持され、かつ大
径部1aの上端には供試体取付台3が設けられて
いる。軸受箱2はボデイ4に嵌合されねじ5によ
り固定されている。ボデイ4の内周面と軸受箱2
の外周面との〓間6aは、回転主軸1の大径部1
aの外周面と軸受箱2の内周面との〓間6bおよ
び大径部1aの下端面と軸受箱2の底面との〓間
6cに通路6dにより連通し、〓間6aから〓間
6b,6cに油が補給される。回転主軸1の小径
部1bの外周面には油もれを防止するシールド部
材7が設けられている。小径部1bの下端部は、
基板8に支持されたモータ9の出力回転軸9aに
磁気継手10を介して連結されている。詳しく
は、磁気継手10は、小径部1bの下端部にねじ
10aにより設けられた第1フランジ10bと、
この第1フランジ10bに円周方向に等ピツチで
間欠的に配置された複数のポール10cと、モー
タ9の出力回転軸9aの上端部にねじ10jによ
り設けられた下部第2フランジ10dと、この下
部第2フランジ10dにカラー10iおよびねじ
10eにより設けられた上部第2フランジ10f
と、両第2フランジ10d,10fに円周方向に
等ピツチで間欠的に設けられ、各ポール10cの
上下(軸方向)両端面にエアギヤツプを有して
個々に対向した上下複数の永久磁石10g,10
hとから構成されている。各位置で上下に対向し
た永久磁石10g,10hは互いに異極で対向し
ている。ポール10cは高透磁率材料からなり、
永久磁石10gと同一径である。ポール10cと
永久磁石10gとの〓間はポール10cと永久磁
石10hとの〓間よりも小さく設定され、もつて
回転主軸1、供試体取付台3、供試体11、第1
フランジ10b、ポール10c、ねじ10a、の
自重をキヤンセルし、軸方向(上下方向)の発生
力を極力小さくしている。
In this figure, the rotating main shaft 1 is composed of a large diameter portion 1a and a small diameter portion 1b. The large diameter portion 1a is fitted into a bottomed bearing box 2 and supported vertically, and a specimen mounting base 3 is provided at the upper end of the large diameter portion 1a. The bearing box 2 is fitted into the body 4 and fixed with screws 5. Inner peripheral surface of body 4 and bearing box 2
The distance 6a between the outer circumferential surface and the large diameter portion 1 of the rotating main shaft 1 is
A passage 6d communicates with the gap 6b between the outer circumferential surface of a and the inner circumferential surface of the bearing box 2 and the gap 6c between the lower end surface of the large diameter portion 1a and the bottom surface of the bearing box 2, and between the gap 6a and the bottom surface 6b. , 6c are supplied with oil. A shield member 7 is provided on the outer peripheral surface of the small diameter portion 1b of the rotating main shaft 1 to prevent oil leakage. The lower end of the small diameter portion 1b is
It is connected to an output rotating shaft 9a of a motor 9 supported by a substrate 8 via a magnetic coupling 10. Specifically, the magnetic coupling 10 includes a first flange 10b provided at the lower end of the small diameter portion 1b by a screw 10a,
A plurality of poles 10c are arranged intermittently at equal pitches in the circumferential direction on this first flange 10b, a lower second flange 10d is provided on the upper end of the output rotation shaft 9a of the motor 9 with a screw 10j, and An upper second flange 10f provided on the lower second flange 10d by a collar 10i and a screw 10e.
A plurality of upper and lower permanent magnets 10g are provided intermittently at equal pitches in the circumferential direction on both second flanges 10d and 10f, and are individually opposed to each other with air gaps on both upper and lower (axially) end surfaces of each pole 10c. ,10
It is composed of h. Permanent magnets 10g and 10h, which are vertically opposed at each position, are opposite to each other with different polarities. The pole 10c is made of a high magnetic permeability material,
It has the same diameter as a 10g permanent magnet. The distance between the pole 10c and the permanent magnet 10g is set smaller than the distance between the pole 10c and the permanent magnet 10h, and the distance between the rotating main shaft 1, the specimen mounting base 3, the specimen 11, and the first
The weight of the flange 10b, pole 10c, and screw 10a is canceled to minimize the force generated in the axial direction (vertical direction).

第2図のように、前記ボデイ4の両側部は、ボ
デイ4の直径一方向つまり矢印X方向に変位自在
な板ばね12,12の一端部にねじ16により支
持され、板ばね12,12の他端部はねじ17に
より基板8に取りつけられている。また、ボデイ
4の一側部には矢印X方向の変位量を検出する変
位センサ13が設けられている。変位センサ13
には作動トランスやムービングコイル形ピツクア
ツプ等が用いられる。
As shown in FIG. 2, both sides of the body 4 are supported by screws 16 at one ends of leaf springs 12, 12, which are movable in one direction of the diameter of the body 4, that is, in the direction of the arrow X. The other end is attached to the substrate 8 with screws 17. Furthermore, a displacement sensor 13 is provided on one side of the body 4 to detect the amount of displacement in the direction of arrow X. Displacement sensor 13
A working transformer, moving coil type pick-up, etc. are used for this.

第3図のように、回転主軸1の大径部1aの外
周面には、ラジアル動圧流体軸受としてのヘリン
グボーン溝14が形成され、また第4図のよう
に、大径部1aの下端面にはスラスト動圧流体軸
受としての放射渦巻溝15が形成されている。な
お、ヘリングボーン溝14および放射渦巻溝15
は軸受箱2の方に設けてもよく、あるいは回転主
軸1と軸受箱2との両方に設けてもよい。
As shown in FIG. 3, a herringbone groove 14 as a radial dynamic pressure fluid bearing is formed on the outer peripheral surface of the large diameter portion 1a of the rotating main shaft 1, and as shown in FIG. A radial spiral groove 15 is formed on the end face as a thrust dynamic pressure fluid bearing. Note that the herringbone groove 14 and the radial spiral groove 15
may be provided on the bearing box 2, or may be provided on both the rotating main shaft 1 and the bearing box 2.

次に前記構成の動作を説明する。 Next, the operation of the above configuration will be explained.

モータ9の出力回転軸9aが駆動すると、永久
磁石10g,10hがポール10cに対して円周
方向にずれることにより、永久磁石10g,10
hポール10c、フランジ10d,10fにより
作られている磁気通路の磁気抵抗が変化し、ポー
ル10cは永久磁石10g,10hの動きにつれ
て次第に同期して回転し始める。ポール10cが
回転つまり回転主軸1が回転すると、予め回転主
軸1の供試体取付台3に取りつけられた供試体1
1のアンバランス量により遠心力が発生し、板ば
ね12のたわみを伴つてボデイ4がX方向に変位
し、その変位量が変位センサ13により検出さ
れ、供試体11のアンバランス量が求められる。
When the output rotation shaft 9a of the motor 9 is driven, the permanent magnets 10g, 10h are displaced in the circumferential direction with respect to the pole 10c.
The magnetic resistance of the magnetic path formed by the h-pole 10c and the flanges 10d, 10f changes, and the pole 10c gradually begins to rotate synchronously with the movement of the permanent magnets 10g, 10h. When the pole 10c rotates, that is, when the rotating main shaft 1 rotates, the specimen 1 attached in advance to the specimen mounting base 3 of the rotating main shaft 1 rotates.
Centrifugal force is generated by the unbalance amount of 1, and the body 4 is displaced in the X direction with the deflection of the leaf spring 12. The displacement amount is detected by the displacement sensor 13, and the unbalance amount of the specimen 11 is determined. .

ところで、前記のように回転主軸1が回転する
と、この回転に伴つてヘリングボーン溝14およ
び放射渦巻溝15により動圧が発生し、回転主軸
1は〓間6bおよび〓間6cを満たす油膜によ
り、ラジアル方向およびスラスト方向に非接触で
軸受箱2に支持される。ここで、非圧縮性の油に
よる動圧軸受は剛性および減衰効果が大きいの
で、回転主軸1は非常に安定して回転し、その振
動は殆ど零か非常に微小となる。したがつて、試
験精度は大幅に向上する。
By the way, when the rotating main shaft 1 rotates as described above, dynamic pressure is generated by the herringbone groove 14 and the radial spiral groove 15 along with this rotation, and the rotating main shaft 1 is moved by the oil film filling the outer space 6b and the outer space 6c. It is supported by the bearing box 2 in a non-contact manner in the radial and thrust directions. Here, since the hydrodynamic bearing using incompressible oil has great rigidity and damping effect, the rotating main shaft 1 rotates very stably, and its vibration is almost zero or very small. Therefore, test accuracy is significantly improved.

なお、実施例では竪形の動釣合試験機で説明し
たが、この動釣合試験機は横形として使用するこ
ともできる。
Although the embodiments have been described using a vertical dynamic balance tester, this dynamic balance tester can also be used as a horizontal type.

また、この実施例では、ポール10cに高透磁
率材料を用いたが、これを永久磁石にかえて、1
0c,10g,10hの永久磁石が異極で対向す
るようにすれば、磁気継手10の動力伝達性がさ
らに向上する。
In addition, in this embodiment, a high magnetic permeability material was used for the pole 10c, but this was replaced with a permanent magnet.
If the permanent magnets of 0c, 10g, and 10h are arranged to face each other with different polarities, the power transmission performance of the magnetic joint 10 will be further improved.

考案の効果 本考案の動釣合試験機によれば、回転主軸をラ
ジアル動圧流体軸受およびスラスト動圧流体軸受
により支持する一方、回転主軸とモータの出力回
転軸との間を磁気継手により非接触で連結するの
で、試験精度の向上化の障害となる振動ノイズを
低減することができる。
Effects of the invention According to the dynamic balance tester of the present invention, the rotating main shaft is supported by a radial dynamic pressure fluid bearing and a thrust dynamic pressure fluid bearing, while a magnetic coupling is used to connect the rotating main shaft and the output rotating shaft of the motor. Since they are connected through contact, it is possible to reduce vibration noise, which is an obstacle to improving test accuracy.

【図面の簡単な説明】[Brief explanation of the drawing]

第1図は本考案の一実施例にかかる動釣合試験
機の一部破断正面図、第2図は第1図の平面図、
第3図は回転主軸の正面図、第4図は第3図の底
面図、第5図は従来の動釣合試験機の一部破断正
面図、第6図は第5図の平面図である。 1……回転主軸、4……ボデイ、9……モー
タ、9a……出力回転軸、10……磁気継手、1
0b……第1フランジ、10c……ポール、10
d,10f……第2フランジ、10g,10h…
…永久磁石、11……供試体、12……板ばね、
13……変位センサ、14……ラジアル動圧流体
軸受、15……スラスト動圧流体軸受。
FIG. 1 is a partially cutaway front view of a dynamic balance tester according to an embodiment of the present invention, FIG. 2 is a plan view of FIG. 1,
Figure 3 is a front view of the rotating main shaft, Figure 4 is a bottom view of Figure 3, Figure 5 is a partially cutaway front view of a conventional dynamic balance tester, and Figure 6 is a plan view of Figure 5. be. 1...Rotating main shaft, 4...Body, 9...Motor, 9a...Output rotating shaft, 10...Magnetic coupling, 1
0b...First flange, 10c...Pole, 10
d, 10f...second flange, 10g, 10h...
...Permanent magnet, 11...Specimen, 12...Plate spring,
13... Displacement sensor, 14... Radial dynamic pressure fluid bearing, 15... Thrust dynamic pressure fluid bearing.

Claims (1)

【実用新案登録請求の範囲】 (1) 一端部に供試体取付台を有する回転主軸と、
この回転主軸をラジアル動圧流体軸受およびス
ラスト動圧流体軸受を介して支持するボデイ
と、このボデイを直径一方向に変位自在に支持
する板ばねと、その直径一方向の変位量を検出
する変位センサと、上記回転主軸の他端部とモ
ータの出力回転軸間を非接触で連結する磁気継
手とを備えたことを特徴とする動釣合試験機。 (2) 上記磁気継手は、上記回転主軸の他端部に設
けられる第1フランジと、この第1フランジに
円周方向に間欠的に設けられる複数のポール
と、上記モータの出力回転軸端部に設けられる
第2フランジと、上記各ポールの軸方向両端面
にエアギヤツプを有して個々に対向し上記第2
フランジに設けられる複数の永久磁石とを備え
た実用新案登録請求の範囲第1項記載の動釣合
試験機。
[Claims for Utility Model Registration] (1) A rotating spindle having a specimen mount at one end;
A body that supports this rotating main shaft via a radial hydrodynamic bearing and a thrust hydrodynamic bearing, a leaf spring that supports this body so as to be displaceable in one diametrical direction, and a displacement sensor that detects the amount of displacement in one diametrical direction. A dynamic balance tester comprising: a sensor; and a magnetic coupling that connects the other end of the rotating main shaft and the output rotating shaft of the motor in a non-contact manner. (2) The magnetic joint includes a first flange provided at the other end of the rotating main shaft, a plurality of poles provided intermittently in the circumferential direction on the first flange, and an output rotating shaft end of the motor. a second flange provided on the pole, and a second flange provided on each of the poles with air gaps provided on both end faces in the axial direction and facing each other.
A dynamic balance testing machine according to claim 1, comprising a plurality of permanent magnets provided on the flange.
JP18055985U 1985-11-21 1985-11-21 Expired JPH0448516Y2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP18055985U JPH0448516Y2 (en) 1985-11-21 1985-11-21

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP18055985U JPH0448516Y2 (en) 1985-11-21 1985-11-21

Publications (2)

Publication Number Publication Date
JPS62115119U JPS62115119U (en) 1987-07-22
JPH0448516Y2 true JPH0448516Y2 (en) 1992-11-16

Family

ID=31124625

Family Applications (1)

Application Number Title Priority Date Filing Date
JP18055985U Expired JPH0448516Y2 (en) 1985-11-21 1985-11-21

Country Status (1)

Country Link
JP (1) JPH0448516Y2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003121289A (en) * 2001-10-16 2003-04-23 Honda Motor Co Ltd Elastic deformation amount measurement device of rod- like member, correction device and correction method

Also Published As

Publication number Publication date
JPS62115119U (en) 1987-07-22

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