JPS63255634A - Apparatus for measuring friction torque of magnetic disk - Google Patents
Apparatus for measuring friction torque of magnetic diskInfo
- Publication number
- JPS63255634A JPS63255634A JP8912487A JP8912487A JPS63255634A JP S63255634 A JPS63255634 A JP S63255634A JP 8912487 A JP8912487 A JP 8912487A JP 8912487 A JP8912487 A JP 8912487A JP S63255634 A JPS63255634 A JP S63255634A
- Authority
- JP
- Japan
- Prior art keywords
- torque
- magnetic disk
- disk
- friction torque
- power source
- 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
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- 230000007246 mechanism Effects 0.000 claims abstract description 15
- 238000001514 detection method Methods 0.000 claims abstract description 9
- 230000005540 biological transmission Effects 0.000 claims description 11
- 238000000034 method Methods 0.000 abstract description 4
- 238000005452 bending Methods 0.000 abstract 1
- 230000000052 comparative effect Effects 0.000 description 17
- 238000005259 measurement Methods 0.000 description 7
- 230000003068 static effect Effects 0.000 description 5
- 239000002131 composite material Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000003014 reinforcing effect Effects 0.000 description 2
- 239000011324 bead Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001595 contractor effect Effects 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000691 measurement method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
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- Force Measurement Appropriate To Specific Purposes (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は磁気ディスク摩擦トルク測定装置に関し、さ
らに詳しくは、フロッピーディスク等のようにジャケッ
トの内側に貼り付けられたライナーあるいは磁気ヘッド
等と摺接する磁気ディスクの、回転起動時の最大摩擦ト
ルクを測定する磁気ディスク摩擦トルク測定装置に関す
る。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a magnetic disk friction torque measuring device, and more specifically, it relates to a magnetic disk friction torque measuring device, and more specifically, it relates to a magnetic disk friction torque measuring device, and more specifically, a magnetic disk friction torque measuring device that measures friction torque with a liner attached to the inside of a jacket such as a floppy disk, or with a magnetic head. The present invention relates to a magnetic disk friction torque measuring device that measures the maximum friction torque of adjacent magnetic disks at the time of starting rotation.
従来、一般に使用されている磁気ディスク摩擦１〜ルク
測定装置は、たとえば、第５図に示すように、フロッピ
ーディスクへのジャケット１１を支持部ＩＯで固定し、
ジャケット１１内に収納した磁気ディスク９を、回転軸
７とディスク・クランプ機構８とで挟持して、回転軸７
とｌ・ルク検出器３を介して連動連結した回転軸駆動動
力源１の駆動によって回転させ、磁気ディスク９とジャ
ケソ１〜１１の内側面に貼着したライナー１２あるいは
磁気ヘッド１３などと摺接する際の摩ｔ％ｉ抵抗による
摩擦トルクを、１−ルク検出器３で測定している。Conventionally, a generally used magnetic disk friction 1~lux measuring device, for example, as shown in FIG. 5, fixes a jacket 11 to a floppy disk with a support IO,
The magnetic disk 9 housed in the jacket 11 is held between the rotating shaft 7 and the disk clamp mechanism 8, and the rotating shaft 7
It is rotated by the drive of the rotary shaft drive power source 1 which is interlocked and connected via the l·lux detector 3 and comes into sliding contact with the liner 12 or the magnetic head 13 attached to the inner surface of the magnetic disk 9 and the jackets 1 to 11. The friction torque due to the actual friction t%i resistance is measured by a 1-lux detector 3.
ところが、この従来の磁気ディスクＦＪ擦トルク測定装
置では、トルク検出器３が回転軸７と回転軸駆動動力源
１との間に直接連結されて挿入されているため、伝達誤
差をできるだけ少なくするようトルク検出器３の剛性が
出来る限り大きく設計されており、特に高感度のもので
は精度との兼ね合いからおよそ数十ｋｇ−ｃｍ／ｒａｄ
に設定されてぃる。However, in this conventional magnetic disk FJ friction torque measuring device, since the torque detector 3 is directly connected and inserted between the rotating shaft 7 and the rotating shaft driving power source 1, it is necessary to minimize transmission errors. The rigidity of the torque detector 3 is designed to be as large as possible, and especially for highly sensitive ones, the rigidity is approximately several tens of kg-cm/rad due to accuracy.
It is set to .
このため、この種の磁気ディスク摩擦トルク測定装置で
もって、たとえば、使用中高い頻度で磁気ディスク９の
回転起動・停止が行われるフし１ッピ−ディスク記録装
置の、回転起動時の最大摩擦Ｉ・ルクを測定しようとす
ると、］・ルク検出器３が回転軸駆動動力源１と回転軸
７間に直接連結されているため回転動力伝達系のねしれ
剛性が高く、また回転軸駆動動力源１の回転数が一般に
は数百ｒｐｍと高速であることから、起動時に磁気ディ
スク９に急激なねしり力が働いて磁気ディスク９の平面
にゆがみが生じ、その凸面部かライナー１２に強く押し
当てられて摩擦抗力が増大するとともに、回転軸駆動動
力源Ｉやディスク・クランプ機構８および磁気ディスク
９の慣性抵抗が大きく作用するため、測定ずへき最大摩
擦トルクに大きな誤差が生しるというｌｉｔ点がある。Therefore, with this type of magnetic disk friction torque measuring device, the maximum friction at the time of rotation start-up of a disk recording device in which the rotation of the magnetic disk 9 is started and stopped frequently during use, for example. When trying to measure I-Luke, the]-Luke detector 3 is directly connected between the rotary shaft drive power source 1 and the rotary shaft 7, so the torsional rigidity of the rotary power transmission system is high, and the rotary shaft drive power Since the rotational speed of the source 1 is generally a high speed of several hundred rpm, a sudden twisting force acts on the magnetic disk 9 at startup, causing distortion in the plane of the magnetic disk 9, and the convex surface of the liner 12 is strongly damaged. As the frictional resistance increases due to the pressing, the inertial resistance of the rotating shaft drive power source I, the disk clamp mechanism 8, and the magnetic disk 9 acts greatly, resulting in a large error in the maximum frictional torque measured. There is a lit point.
しかして、このような従来の磁気ディスク摩擦トルク測
定装置を使用したのでは、使用中高い頻度で磁気ディス
ク９０回転起動・停止が行われるフロッピーディスク記
録装置の最大摩擦トルクを正確に測定することかできず
、このような不正確な測定値を基準にしては、磁気ディ
スクの潤屑性等を改善したり、起動時の最大トルクを低
減したりして、磁気ディスクが、回転起動する際の静止
最大摩擦係数によって著しく１７耗されるのを有効に防
止したり、また、駆動モータ、制御回路を小型省電力化
して、フロッピーディスクドライブ装置を小型化するこ
とかできない。However, using such a conventional magnetic disk friction torque measuring device, it is difficult to accurately measure the maximum friction torque of a floppy disk recording device in which the magnetic disk frequently starts and stops 90 revolutions during use. Therefore, using such inaccurate measurement values as a standard, it is necessary to improve the lubricity of the magnetic disk, reduce the maximum torque at startup, etc., and increase the speed at which the magnetic disk starts rotating. It is not possible to effectively prevent the wear caused by the static maximum coefficient of friction, or to downsize the floppy disk drive device by making the drive motor and control circuit smaller and more power efficient.
この発明は、かかる欠点を改善するため種々検討を行っ
た結果なされたもので、従来の磁気ディスク摩擦１−ル
ク測定装置を改善し、磁気ディスク回転軸駆動動力源と
ディスク・クランプ機構とを、トルク検出手段を介在さ
せてバネ特性を兼ね備えた回転動力伝達手段で連結し、
これら回転軸駆動動力源とディスク・クランプ機構とト
ルク検出手段と回転動力伝達手段との合成ねじり剛性を
１５００ ｇ−ｃｍ／ｒａｄ以下にすることによって、
回転起動時の最大摩擦トルクを、高い精度で正確に測定
できるようにしたものである。The present invention was made as a result of various studies to improve these drawbacks.The present invention improves the conventional magnetic disk friction 1-lux measuring device, and improves the magnetic disk rotating shaft drive power source and disk clamp mechanism. Connected by a rotary power transmission means with spring characteristics with a torque detection means interposed,
By setting the combined torsional rigidity of the rotary shaft drive power source, disk clamp mechanism, torque detection means, and rotary power transmission means to 1500 g-cm/rad or less,
This allows the maximum friction torque at the start of rotation to be accurately measured with high precision.
以下、この発明の磁気ディスク摩擦トルク測定装置の一
実施例を示す図面を参照しながら説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the magnetic disk friction torque measuring device of the present invention will be described below with reference to the drawings.
第１図は、この発明の磁気ディスク摩擦トルク測定装置
の櫃略を示したものであり、■は回転軸駆動動力源であ
って、回転結合部２を介してトルク検出器３と連結され
、さらに回転結合部４、ねじりバネ５、回転結合部６を
介して回転軸７およびディスク・クランプ機構８と連動
連結されている。FIG. 1 shows a schematic diagram of the magnetic disk friction torque measuring device of the present invention, where ◯ indicates a rotating shaft driving power source, which is connected to a torque detector 3 via a rotating coupling portion 2; Furthermore, it is operatively connected to a rotating shaft 7 and a disk clamp mechanism 8 via a rotating coupling part 4, a torsion spring 5, and a rotating coupling part 6.
９は回転軸７とディスク・クランプ機構８とて挟持され
た磁気う一イスクであり、支持部■０で固定されたフロ
ッピーディスクＡのジャケットｌｌ内に収納され、回転
軸駆動動力源ｌの駆動によってトルク検出器３、ねじり
バネ５および回転軸７を介して連動回転される。このと
き２、磁気ディスク９はジャケットＩＩの内側面に貼着
したライ−Ｊ−−１２あるいは磁気ヘッド１３などと摺
接し、この摺接の際の摩擦抵抗による１ソ擦トルクが、
Ｉ・ルク検出器３で測定される。１４は磁気ヘッド１３
と対抗する位置に配設された押圧部材であり、Ｉ５は回
転軸駆動動力源１に接続された動力制御部、１６は］・
ルク検出器３に接続された検出指示部である。Reference numeral 9 denotes a magnetic disc held between the rotating shaft 7 and the disk clamp mechanism 8, which is housed in the jacket 1 of the floppy disk A fixed by the support part 0, and is used to drive the rotating shaft drive power source 1. is rotated in conjunction with the torque detector 3, torsion spring 5, and rotating shaft 7. At this time 2, the magnetic disk 9 comes into sliding contact with the Li-J-12 or the magnetic head 13 attached to the inner surface of the jacket II, and the frictional torque due to the frictional resistance during this sliding contact is
It is measured by the I-lux detector 3. 14 is a magnetic head 13
I5 is a power control unit connected to the rotary shaft drive power source 1, and 16 is a pressing member disposed at a position opposite to the rotary shaft drive power source 1.
This is a detection instruction unit connected to the torque detector 3.
この発明の磁気ディスク摩擦トルク測定装置はこのよう
にして構成され、磁気ディスク摩擦トルクの測定に際し
ては、第２図（ａ）に示すように回転軸駆動動力源Ｉの
回転数が起動とともに瞬時に一定値に達する。ところが
、磁気ディスク９にかかる駆動力１；＋：、ねしりバネ
５の（ｌび縮み効果のために、第２図（ｂ）のごとく直
線的に徐々に増加し、駆動力が磁気ディスク９の静ｌｒ
擦抗力を超えるまでは駆動エネルギーはずべてねじりバ
ネ５の伸びあるいは縮みに費やされる。そしζ、静摩擦
抗力を超えた直後に、磁気ディスク９が回転して動摩擦
抗力へ移行する。この磁気ディスク９の静止状態が破ら
れるとき駆動力が最大となり、この時の抗力は最大静止
摩擦力に等しくトルク換算する七最大トルク値となる。The magnetic disk friction torque measuring device of the present invention is constructed in this way, and when measuring the magnetic disk friction torque, the rotational speed of the rotating shaft drive power source I changes instantly upon startup, as shown in FIG. 2(a). reaches a certain value. However, due to the compression effect of the torsion spring 5, the driving force applied to the magnetic disk 9 gradually increases linearly as shown in FIG. Shizuka lr
Until the frictional force is exceeded, all driving energy is spent on expanding or contracting the torsion spring 5. Immediately after the static frictional drag force is exceeded, the magnetic disk 9 rotates and the force shifts to a dynamic frictional drag force. When the static state of the magnetic disk 9 is broken, the driving force reaches its maximum, and the drag force at this time is equal to the maximum static frictional force and becomes the maximum torque value converted into torque.
第２図（Ｃ，）は、このような過程でのトルク検出器３
で測定した測定トルク値の変化を示したものであり、］
・ルク変化曲線のピークから最大トルクを読み取ること
ができる。なお、この第２図（Ｃ）に示すように、静止
状態が破られた後のトルク曲線は、実線で示されるよう
な定常トルク値の一定値をとる場合と、点線で示される
ように起動・停止をくり返すスティック・スリップ状の
回転を示す場合があり、磁気ディスク９の摩擦係数が高
い場合、スティック・スリップ状の回転を示す。Figure 2 (C,) shows the torque detector 3 during this process.
It shows the change in the measured torque value measured at ]
・The maximum torque can be read from the peak of the torque change curve. As shown in Fig. 2 (C), the torque curve after the stationary state is broken is the case where the steady torque value is a constant value as shown by the solid line, and the case where the torque curve is a constant value as shown by the dotted line. - It may exhibit stick-slip rotation with repeated stops, and if the coefficient of friction of the magnetic disk 9 is high, stick-slip rotation may be exhibited.
このように、この発明の磁気ディスク摩擦トルク測定装
置によれば、ねじりバネ５の伸び縮み効果によってねし
り剛性が左右され、ねじりバネ５のねじり剛性が犬きす
きると、第２図（ｂ）のグラフＡで示されるように磁気
ディスク駆動力の立ち上がりが急となり、静摩擦状態が
破られた時に発生する慣性抵抗が強く重畳される。また
小さずぎると、第２図（ｂ）のグラフＢで示されるよう
に立ち上がりが緩慢になり、測定時間の長大化あるいは
ねしりバネ５が細＜長くなるなどして、たわみやバネの
自励振動が発生し、測定誤差を生ずる危険がある。As described above, according to the magnetic disk friction torque measuring device of the present invention, the torsional rigidity is influenced by the expansion and contraction effect of the torsion spring 5, and when the torsional rigidity of the torsion spring 5 becomes too small, the torsional rigidity shown in FIG. As shown in graph A, the rise of the magnetic disk driving force becomes rapid, and the inertial resistance generated when the static friction state is broken is strongly superimposed. If it is too small, the rise will be slow as shown in graph B in Figure 2 (b), the measurement time will become longer, or the torsion spring 5 will become thinner and longer, resulting in deflection and self-excitation of the spring. There is a risk of vibrations and measurement errors.
このため、この発明の磁気ディスク摩擦トルク測定装置
は、回転軸７と１−ルク検出器３との間に挿入されたね
じりバネ５のねじり剛性を適当に調整することによって
、第２図（ｂ）のグラフＣで示されるように磁気ディス
ク駆動力の立ち上がりを適度なものとするのが好ましい
。このようにして調整されるねじり剛性としては、回転
軸駆動動力源ｌと、トルク検出器３と、ねじりバネ５と
、回転軸７と、ディスク・クランプ機構８とからなる動
力伝達系の合成ねじり剛性を、１５００ｇ・ｃｍ／ｒａ
ｄ以下にするのが好ましく、特に、高精度、迅速な測定
のためには、３０ ｇ−ｃｍ／ｒａｄ以下Ｑ、 ｌ ｇ
−ｃｍ ／ ｒａｄ以上の範囲内に調整するのが望まし
い。Therefore, the magnetic disk friction torque measuring device of the present invention is constructed by appropriately adjusting the torsional rigidity of the torsion spring 5 inserted between the rotating shaft 7 and the 1-lux detector 3, as shown in FIG. ), it is preferable that the rise of the magnetic disk driving force be moderate. The torsional rigidity adjusted in this way is the composite torsion of the power transmission system consisting of the rotating shaft drive power source 1, the torque detector 3, the torsion spring 5, the rotating shaft 7, and the disk clamp mechanism 8. Rigidity: 1500g・cm/ra
It is preferable to keep it below 30 g-cm/rad, especially for high precision and rapid measurement.
It is desirable to adjust within the range of -cm/rad or more.
このように、この発明の磁気ディスク摩擦トルク測定装
置は、回転軸７とトルク検出器３との間に挿入したねじ
りハ＊５のねしり剛性を適当に調整することにより、回
転軸駆動動力源１と、トルク検出器３と、ねじりバネ５
と、回転軸７と、ディスク・クランプ機構８とからなる
動力伝達系の合成ねじり剛性を自在に調整することがで
き、この合成ねじり剛性を１５００ ｇ−ｃｍ／ｒａｄ
以下にして、最大摩擦トルクを、高い精度で正確に測定
することができる。As described above, the magnetic disk friction torque measuring device of the present invention can measure the power source for driving the rotating shaft by appropriately adjusting the torsional rigidity of the torsional shaft inserted between the rotating shaft 7 and the torque detector 3. 1, torque detector 3, and torsion spring 5
The combined torsional rigidity of the power transmission system consisting of the rotating shaft 7 and the disk clamp mechanism 8 can be adjusted freely, and the combined torsional rigidity can be adjusted to 1500 g-cm/rad.
The maximum friction torque can be accurately measured with high precision as follows.
なお、この発明は上記実施例に限られるものではなく、
前記実施例のトルク検出器３とねじりバネ５に代えて、
第３図に示すように、回転軸７にプーリ１７を取り付け
、プーリ１７に巻きつｃｔたベルト１８を直線バネ１つ
と連結し、この直線バネ１９をさらに圧力センサ２０を
介してリニアモータ２１に連結してもよく、この場合は
、直線バネ１９のねじり剛性を適当に調蛯することによ
って、合成ねしり阿り性を自在に調整することができ、
前記実施例のトルク検出器３とねじりバネ５を、直線バ
ネＩ９と圧力センサ２Ｉで置き換えることができる。Note that this invention is not limited to the above embodiments,
In place of the torque detector 3 and torsion spring 5 of the above embodiment,
As shown in FIG. 3, a pulley 17 is attached to the rotating shaft 7, a CT belt 18 wound around the pulley 17 is connected to a linear spring, and this linear spring 19 is further connected to a linear motor 21 via a pressure sensor 20. In this case, by appropriately adjusting the torsional rigidity of the linear spring 19, the synthetic stiffness can be adjusted freely.
The torque detector 3 and torsion spring 5 of the previous embodiment can be replaced by a linear spring I9 and a pressure sensor 2I.
また、ねしりバネ５や直線バネＩ９を用いなくとも、磁
気ディスク回転軸駆動動力源の電子制御によりバネ特性
を発揮させて、動力伝達系の合成ねじり剛性を１５００
ｇ−ｃｍ／ｒａｄ以下に制御することも可能である。In addition, even without using the torsion spring 5 or the linear spring I9, the spring characteristics can be exhibited by electronic control of the power source for driving the magnetic disk rotating shaft, and the combined torsional rigidity of the power transmission system can be increased to 1500.
It is also possible to control it to below g-cm/rad.
次に、ごの発明の実施例について説明する。 Next, embodiments of the invention will be described.
実施例１
第４図に示すように、ミニフロッピ・ディスクドライブ
（］］立閏作所社製、ＩＩＦＩ）５１６Ｃ） ２２の
ディスク・クランプ２３と、磁気ディスク回転用ダイレ
クトドライブモータ２４との間に、モータ２４側から順
にトルク計２５ （小野測器社靭、ＭＤ−０２ＯＲ）と
、ねじりバネ２６とを回転軸２７でもって直列に連結し
、トルク計２５の出力は高速応答型レコーダに記録して
そのチャー１−からビーり１１４を読ｅ７：Ｉ取り、起
動ｄＮの最大摩擦口１／りを測定できるように構成した
磁気ディスクの摩Ｉｆ’： トルク測定装置を使用し、
わしのバネ２Ｇのねじり剛性をｌ ｇ−ｃｍ／ｒａｄに
調整した後、ミニフロッピ・ディスクト′ライブ２２に
、ミニフロッピーディスク２８を装着して、ダイレクト
トライブモータ２４を３０ Ｏｒｐｍで回転駆動させ、
磁気ヘッドを摺接させた場合（ヘッド着）と、摺接させ
ない場合（ヘッド脱）とに分けて起動時の最大摩擦トル
クを測定した。なお、ミニフロ・ノビ−ディスク２８と
しては、ミニフロッピーディスクＭＤ２−Ｄ、ＭＤ２−
２５６ＨＤの２種類のミニフロッピーディスクを使用し
て、それぞれの最大摩擦トルクを測定した。Embodiment 1 As shown in FIG. 4, between the disk clamp 23 of the mini-floppy disk drive (manufactured by Risunsakusho Co., Ltd., IIFI) 516C) and the direct drive motor 24 for rotating the magnetic disk. From the motor 24 side, a torque meter 25 (MD-02OR, manufactured by Ono Sokki Co., Ltd.) and a torsion spring 26 are connected in series with a rotating shaft 27, and the output of the torque meter 25 is recorded on a high-speed response recorder. Read the bead 114 from the char 1-, take e7:I, and use a torque measuring device If': of the magnetic disk configured to measure the maximum friction opening 1/r of the starting dN.
After adjusting the torsional rigidity of the spring 2G to 1 g-cm/rad, the mini-floppy disk 28 is attached to the mini-floppy disk drive 22, and the direct drive motor 24 is driven to rotate at 30 Orpm.
The maximum friction torque at startup was measured separately when the magnetic head was in sliding contact (head attached) and when it was not in sliding contact (head removed). In addition, the mini floppy disk MD2-D, MD2-
Two types of 256HD mini-floppy disks were used to measure their respective maximum friction torques.
実施例２
実施例１において、ミニフロッピーディスク２８のセン
タホール周辺に外径３８１舷厚み２００μｍのアルミニ
ューム盟補強リングを貼りつけた以外は、実施例１と同
様にして最大摩擦１−ルクを測定した。Example 2 The maximum friction 1-lux was measured in the same manner as in Example 1, except that an aluminum reinforcing ring with an outer diameter of 381 and a shipboard thickness of 200 μm was attached around the center hole of the mini-floppy disk 28. did.
比較例１
実施例１において、ねじりバネ２６のねしり剛性をｌ
ｇ ・ｃｍ／ ｒａｄから１６５０ ｇ−ｃｍ／ｒａｄ
に変更した以外は、実施例１と同様にして最大摩擦トル
クを測定した。Comparative Example 1 In Example 1, the torsional rigidity of the torsion spring 26 was
g-cm/rad to 1650 g-cm/rad
The maximum friction torque was measured in the same manner as in Example 1, except for changing to.
比較例２
実施例１において、ねじりバネ２６を取り外し、トルク
計２５とディスク・クランプ２３を直接ジヨイントにて
剛体結合した以外は、実施例１と同様にして最大摩擦ト
ルクを測定した。なお、この場合の合成ねしり剛性は１
７９０５ Ｂ −ｃｍ／ｒａｄであった。Comparative Example 2 The maximum friction torque was measured in the same manner as in Example 1, except that the torsion spring 26 was removed and the torque meter 25 and disk clamp 23 were rigidly connected directly at a joint. In addition, the composite shear stiffness in this case is 1
It was 7905 B-cm/rad.
比較例３
比較例２において、ミニフロッピーディスク２８のセン
タボール周辺に外径３８ＩＩｍ、厚み２００μｍのアル
ミニューム歴補強リングを貼りつけた以外は、比較例２
と同様にして最大塵ｔＭ ）ルクを測定した。Comparative Example 3 Comparative Example 2 was performed except that an aluminum history reinforcing ring with an outer diameter of 38 IIm and a thickness of 200 μm was attached around the center ball of the mini-floppy disk 28.
The maximum dust tM) was measured in the same manner as above.
比較例４
実施例１において、ミニフロッピーディスク２８を装着
せず、磁気ヘソＩＳの摺接を外した状態にした以外は、
実施例１と同様にして最大摩擦トルクを測定した。Comparative Example 4 In Example 1, except that the mini-floppy disk 28 was not installed and the magnetic navel IS was disconnected from the sliding contact.
The maximum friction torque was measured in the same manner as in Example 1.
比較例５
比較例２において、ミニフロッピーディスク２８を装着
せず、磁気へ・２ドの摺接を外した状態にした以外は、
比較例２と同様にして最大摩擦トルクを測定した。Comparative Example 5 In Comparative Example 2, except that the mini-floppy disk 28 was not installed and the sliding contact of the 2nd drive to the magnetic field was removed.
The maximum friction torque was measured in the same manner as Comparative Example 2.
下記第１表はその結果である。Table 1 below shows the results.
第１表 上記第１表から次のことが明らかである。Table 1 The following is clear from Table 1 above.
（１）実施例１、比較例１および２は、順に動力伝達系
のねじり剛性が高くなっており、この発明による最適な
ねしり剛性か与えられた実施例１に比べ、比較例１およ
び２のようにねじり剛性が高くなるほと最大摩擦トルク
が増大する。(1) In Example 1 and Comparative Examples 1 and 2, the torsional rigidity of the power transmission system increases in that order. As the torsional rigidity increases, the maximum friction torque increases.
（２）比較例３は、ねじり剛性が非常に高い比較例２に
比して起動時の磁気ディスクの平面にゆがみが生しやす
いセンタ・ポール周辺を補強したものであり、この補強
効果によって磁気ディスクのゆがみが減少してライナー
との接触圧が低圧に保たれ、最大摩擦トルクも比較的小
さくなる。(2) Compared to Comparative Example 2, which has extremely high torsional rigidity, Comparative Example 3 has the area around the center pole reinforced, where the flat surface of the magnetic disk is likely to be distorted during startup. Disk distortion is reduced, contact pressure with the liner is kept low, and maximum frictional torque is also relatively small.
（３）比較例４および５は、それぞれ実施例１、比較例
２に対し摩擦抵抗源の磁気ディスクを除いたものであり
、測定値そのものは慣性抵抗によって生したトルクに等
しい。従って、比較例５で示されるように、動的なトル
クを測定する一般的なトルク測定法の構成を持つ比較例
２ば、非常に大きな慣性１〜ルクが働き最大摩擦トルク
の計測には適さない。また、比較例４で示されるように
この発明による最大厚１ｊｊ ＋−ルク測定法では、慣
性トルクによる誤差がない。(3) Comparative Examples 4 and 5 are obtained by removing the magnetic disk as a source of frictional resistance from Example 1 and Comparative Example 2, respectively, and the measured values themselves are equal to the torque generated by inertial resistance. Therefore, as shown in Comparative Example 5, Comparative Example 2, which has a configuration of a general torque measurement method for measuring dynamic torque, has a very large inertia of 1 to 100 mph and is not suitable for measuring the maximum friction torque. do not have. Further, as shown in Comparative Example 4, the maximum thickness 1jj +-luk measuring method according to the present invention has no error due to inertial torque.
（４）実施例２ば、実施例１に比較して磁気ディスクを
補強したものであるが、測定された最大厚ｔＭ トルク
は大差ない。従って、この発明による最大摩擦トルク測
定法によれば、磁気ディスクのたわみがなく、このたわ
みによる測定誤差が生しない。(4) Example 2 Although the magnetic disk was reinforced compared to Example 1, the measured maximum thickness tM and torque were not significantly different. Therefore, according to the maximum friction torque measuring method according to the present invention, there is no deflection of the magnetic disk, and measurement errors due to this deflection do not occur.
（５）比較例１によれば、合成ねじり剛性が１６５ Ｑ
ｇ −ｃｍ ／ ｒａｄ稈度程度と実施例１に比較し
、およそ１０％以十以上差があり、測定精度ヒの限界を
超える。(5) According to Comparative Example 1, the composite torsional rigidity is 165 Q
There is a difference of about 10% or more compared to the g-cm/rad culm degree of Example 1, which exceeds the limit of measurement accuracy.
以上の結果から、動力伝達系の合成ねしり剛性を１５０
０ ｇ−ｃｍ／ｒａｄ以下となるように構成したこの発
明の磁気ディスク摩擦トルク測定装置によれば、磁気デ
ィスクのたわみによる誤差、あるいは慣性抵抗を全く無
視できるほどに低減することが可能であり、最大１９擦
１−ルクを高い精度で正確に測定できることがわかる。From the above results, the composite shear stiffness of the power transmission system is set to 150
According to the magnetic disk friction torque measuring device of the present invention configured to be 0 g-cm/rad or less, it is possible to reduce errors caused by deflection of the magnetic disk or inertial resistance to a completely negligible level, It can be seen that it is possible to accurately measure a maximum of 19 rubs and 1-lux with high precision.
第１図はこの発明の磁気ディスクの摩擦トルク測定装置
の−・実施例を示ず概略断面説明図、第２図（ａ）は磁
気ディスクの摩擦１〜ルク測定時における回転軸駆動動
力源回転数と時間の関係図、第２図（ｂ）は磁気ディス
クの摩擦Ｉ・ルク測定時における磁気ディスク駆動力と
時間の関係図、第２図（Ｃ）は磁気ディスク摩Ｌｉｄ
Ｉ・ルク測定時における１−ルクと時間の関係図、第３
図はこの発明の磁気ディスクの摩擦トルク測定装置の他
の実施例を示す要部概略説明図、第４図はミニフロッピ
ーディスクの摩ｆ’ｊ トルクを測定する測定装置の具
体例を示す要部斜視図、第５図は従来の磁気ディスクの
摩擦１ヘルク測定装置の一実施例を示す概略断面説明図
である。
■・・・回転軸駆動動力源、３・・・１−ルク検出器（
トルク検出手段）、５．２６・・・ねしリハ不、７，２
７・・・回転軸（回転動力伝達手段）、８・・・ディス
ク・クランプ機構、９・・・磁気ディスク、１９・・・
直線バネ、２０・・・圧カセンザ（トルク検出手段）、
２４・・・ダイレフ］・ドライブモーフ、２３山デイス
ク・クランプ、２５・・・トルク計（トルク検出手段）
、２８・・・ミニフロッピーディスク。Fig. 1 is a schematic cross-sectional explanatory view (not showing an embodiment) of the magnetic disk friction torque measuring device of the present invention, and Fig. 2 (a) shows the rotation of the rotating shaft drive power source when measuring the friction of the magnetic disk from 1 to 1. Figure 2 (b) is a diagram of the relationship between magnetic disk drive force and time when measuring the friction I and torque of the magnetic disk, and Figure 2 (C) is a diagram of the relationship between magnetic disk friction I and time.
Relationship diagram between 1-Luke and time during I-Luke measurement, Part 3
The figure is a schematic explanatory view of the main parts of another embodiment of the magnetic disk friction torque measuring device of the present invention, and FIG. 4 is the main part showing a specific example of the measuring device for measuring the frictional torque of a mini-floppy disk. The perspective view and FIG. 5 are schematic cross-sectional explanatory views showing one embodiment of a conventional magnetic disk friction one-herk measuring device. ■...Rotary shaft drive power source, 3...1-lux detector (
Torque detection means), 5.26... No rehabilitation, 7,2
7... Rotating shaft (rotary power transmission means), 8... Disk clamp mechanism, 9... Magnetic disk, 19...
Straight spring, 20...pressure sensor (torque detection means),
24... Dairef] Drive morph, 23-mounted disc clamp, 25... Torque meter (torque detection means)
, 28...Mini floppy disk.
Claims (1)
プ機構とを、トルク検出手段を介在させてバネ特性を兼
ね備えた回転動力伝達手段で連結し、これら回転軸駆動
動力源とディスク・クランプ機構とトルク検出手段と回
転動力伝達手段との合成ねじり剛性を１５００ｇ・ｃｍ
／ｒａｄ以下にしたことを特徴とする磁気ディスク摩擦
トルク測定装置。1. The magnetic disk rotating shaft driving power source and the disk clamping mechanism are connected by a rotating power transmitting means having spring characteristics with a torque detecting means interposed, and the torque between these rotating shaft driving power source, the disk clamping mechanism, and the torque detection means is interposed. The combined torsional rigidity of the detection means and rotational power transmission means is 1500 g cm.
1. A magnetic disk friction torque measuring device characterized in that the friction torque is less than /rad.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8912487A JPS63255634A (en) | 1987-04-11 | 1987-04-11 | Apparatus for measuring friction torque of magnetic disk |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8912487A JPS63255634A (en) | 1987-04-11 | 1987-04-11 | Apparatus for measuring friction torque of magnetic disk |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63255634A true JPS63255634A (en) | 1988-10-21 |
Family
ID=13962136
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8912487A Pending JPS63255634A (en) | 1987-04-11 | 1987-04-11 | Apparatus for measuring friction torque of magnetic disk |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63255634A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111089667A (en) * | 2019-12-20 | 2020-05-01 | 深圳市山卓谐波传动科技有限公司 | Torque testing method and system for harmonic reducer |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56163429A (en) * | 1980-05-20 | 1981-12-16 | Citizen Watch Co Ltd | Device for measuring torque |
-
1987
- 1987-04-11 JP JP8912487A patent/JPS63255634A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS56163429A (en) * | 1980-05-20 | 1981-12-16 | Citizen Watch Co Ltd | Device for measuring torque |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111089667A (en) * | 2019-12-20 | 2020-05-01 | 深圳市山卓谐波传动科技有限公司 | Torque testing method and system for harmonic reducer |
| CN111089667B (en) * | 2019-12-20 | 2021-01-12 | 深圳市山卓谐波传动科技有限公司 | Torque testing method and system for harmonic reducer |
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