JPS59215072A - Magnetic head support mechanism - Google Patents

Abstract

PURPOSE:To improve the effect of vibration proof by providing a wind shield plate near a side face of a disc opposed thereto supported elastically so as to decrease the amplitude of vibration for the elastic support. CONSTITUTION:A slider 3 is fitted to a free end part 8a of the elastic support 8 and a base 8b of the elastic support 8 is fitted to a guide arm 10 via a spacer 9. The elastic support 8 is fitted at both sides of the guide arm 10 and two positions, rear and front positions. The wind shield plate 12 made of a thin plate with an area covering sufficiently the elastic support 8 is fitted to a wind shield plate fitting part 13 by a screw 14. The wind shield fitting part 13 is formed incorporatedly with the guide arm 10 and the thickness t' of the wind shield fitting part 13 is smaller than a thickness (t) of the guide arm 10, then the contact between the wind shield plate 12 and the elastic support 8 is prevented. The amplitude of vibration of the elastic support 8 is reduced remarkably by providing the wind shield plate 12 near a face 8a opposite to the disc 1 of the elastic support 8 and a side face 8b opposite thereto so as to allow the elastic support 8 to shield the flow in a direction at a right angle F.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a magnetic head support mechanism used in a magnetic disk device, particularly a high-density magnetic disk device that requires highly accurate positioning of the magnetic head.

[Background of the invention]

As shown in FIGS. 1 to 3, a conventional magnetic head mechanism with a windbreak arm is disposed opposite to a disk 1 which is attached to a main shaft (not shown) by laminating a large number of disks, and has a magnetic head 2. The slider 3, the elastic support 8 that elastically supports the slider 3, and the guide arm 10 that rigidly supports the base of the elastic support 80, that is, the end opposite to the end to which the slider 3 is attached. The elastic support 8 is the slider 3
It is composed of a gimbal 4 that provides a restoring force against the rolling and pitching movements of the slider, a support spring 5 that supports the gimbal 4, and a load par 6 and a load spring 7 that press the slider 3 against the disk 1. There is.

The slider 3 has a pressing force applied to the disc 1 by the load par 6 and the load spring 7, and the disc 1 and the slider 3
It floats in a state where the air bearing force due to the air in between is balanced. Further, the guide arm 10 is connected to a servo motor (not shown) and is controlled to hold the magnetic head 2 on a magnetic recording track (not shown) recorded concentrically on the disk 1.

In such a conventional magnetic head support mechanism, the wind generated by the rotation of the disk 1 is blown onto the elastic support 8 in the direction B, so that the elastic support 8 vibrates. Therefore, disk 1
Since it is difficult to maintain a minute gap between the guide arm 1o and the slider 3 and to accurately position the magnetic head 2 on the magnetic recording track of the disk 1, the free end side of the guide arm 1o, that is, the elastic support 8 side. A windbreak arm 11 is integrally formed with the. The thickness t of this windbreak arm 11 is formed to be the same as the thickness y of the guide arm 10, and the cross-sectional shape of the windbreak arm 11 is as shown in FIG.
A 45° notch is provided on the side surface, and the top and bottom are symmetrically formed.

On the other hand, there is also one in which elastic supports 8 are provided on both sides of the guide arm 1o, but in such a case, elastic supports must also be provided on the side opposite to the side having the 45° notch.

When the wind flow around the windbreak arm 11 was visualized using the smoke wire method and the relationship between the various shapes and installation positions of the windbreak arm 11 and the elastic support 8 was investigated, the following matters were revealed. became.

(1) When the flow is visualized using the smoke wire method when two windbreak arms 11 and two elastic supports 8 are installed in a wide space as shown in Fig. 4, the width t@ of flows C and D is Even in a configuration in which the elastic support 8 is not hidden behind the windbreak arm 11 (see FIG. 2), a certain degree of vibration isolation effect can be expected.

(11) When the windbreak arm 11 has the shape shown in Fig. 4, the flow C on the side where the 45° notch is not provided is the windbreak arm 1.
After passing through 1, there is a risk that it will be blown towards the flow D on the side where the 45° notch is provided and collide with the elastic support 8. Therefore, the shape of the windbreak arm 11 that faces the wind is symmetrical,
For example, if it is formed into a rectangular shape, symmetry in the vibration damping effect can be expected.

However, when the thickness of the windbreak arm and the guide arm are the same as in the conventional example, there is a drawback that the vibration isolation effect is significantly reduced (2 to 3d13).

When the vibration-proofing effect of the 4iD windbreak arm 11 was compared with the case without a windbreak arm, it was found that the side with the 45° notch has a vibration effect of approximately (id13) against the vibration of the elastic support 8; The side where the elastic support 8 is not provided has almost no vibration damping effect against the vibrations of the elastic support 8.

On the other hand, when operating the magnetic disk device, the guide arm 1
0 moves toward the inner and outer circumference of the rotating disk 1, and the magnetic head 2
Desired information is written onto or read from the recording track on the disk 1 through the recording track. In this case, the disc 1 acts as a kind of blower because the friction on the disc surface causes air flow. , it changes depending on whether it is at the inner circumferential position. As the blower meteor-pressure characteristics change, the pressure within the disk device and the power for rotating the disk also change. Therefore, when the ratio of the width of the windbreak arm to the disc gap is large as in the conventional example, there is a drawback that the pressure fluctuation within the disc device and the power fluctuation for rotating the disc are large.

[Purpose of the invention]

In view of the above, the present invention reduces the vibration amplitude of the elastic support by blocking air flow in a direction perpendicular to the elastic support via a wind shield plate, thereby improving the vibration isolation effect, and improving the vibration isolation effect within the magnetic disk drive. The purpose of this is to reduce pressure fluctuations in the disk and power fluctuations in rotating the disc.

[Summary of the invention]

In order to achieve the above object, the present invention provides a slider that is disposed opposite to a rotatably provided disk and has a magnetic head, an elastic support that elastically supports the slider, and a side of the elastic support that is opposite to the slider and has a magnetic head. In a magnetic head support mechanism comprising a supporting guide arm or a windbreak arm provided upstream of an elastic support of this support mechanism, a windshield plate is provided close to the anti-sun plate side surface of the elastic support. It is characterized by:

[Embodiments of the invention]

Embodiments of the present invention will be described below with reference to the drawings.

In FIGS. 5 and 6, 1 is a disc mounted on a rotating main shaft (not shown) in a stacked manner, and 2 is a slider 3.
The slider 3 is attached to the free end 8a of the elastic support 8, and the base 8b of the elastic support 8 is attached to the guide arm 10 via a spacer 9. Such elastic supports 8 are attached to both sides of the guide arm 1o, and at two locations, front and rear. In other words, four elastic supports 8 are attached to one guide arm 10. Reference numeral 12 denotes a wind shielding plate made of thin plate material and having a size that sufficiently covers the elastic support 8.
is attached to the wind shield mounting portion 13 via screws 14. The wind shield mounting portion 13 is formed integrally with the guide arm 10, and since the thickness t' of the wind shield mounting portion 13 is smaller than the thicknesses t and t6 of the guide arm 10, the wind shield mounting portion 13 is formed integrally with the guide arm 10. Contact between the wind plate 12 and the elastic support 8 can be prevented.

As shown in FIG. 7, the wind shielding plate 12 is located close to a surface 8a of the elastic support 8 facing the disc 1, that is, a side surface (back surface) 8b opposite to the surface on which the slider 3 is attached. By providing the elastic support 8 so as to block the flow in the perpendicular direction F, the amplitude of the elastic support 8 can be significantly reduced.

On the other hand, the larger the area of the wind shield 12 that covers the elastic support 8, the greater the vibration isolation effect of the wind shield 12, and
When the distance to from the tip of the wind shield plate 12 to the side surface of the wind shield plate 12 is equal to the distance LE to the center of the elastic support 8, the vibration isolation effect is 3 to 4 dB, and the vibration isolation effect is 3 to 4 dB. When the distance is equal to ty, the vibration damping effect is 7 to 10 dB.

It is clear that the desired vibration isolation effect can be obtained by providing the wind shielding plate 12 of a size that covers the entire elastic support 8 in close proximity to the back surface 8b of the elastic support 8 as described above.

As shown in Figure 8, at the tip of the guide arm 1o,
If the wind shield plate 12 and the wind shield arm 11 are attached in combination, an even more remarkable vibration damping effect can be achieved. In this case, the thickness of the windbreak arm 11 needs to be larger than the thickness of the windshield plate 12. That is, if the distance from the surface of the windbreak arm 110 to the disk 1 is defined as t, and the distance from the surface of the windshield plate 12 to the disk 1 is t, it is necessary to satisfy the condition of the following equation (1).

L (1, . . . . . . . . . (1) According to this embodiment, the wind shield plate 12 can be attached after the elastic support 8 is attached to the guide arm 10. Therefore, the elastic support 8 can be easily and accurately attached to a predetermined position.Furthermore, since the thickness of the wind shield mounting portion 13 is thinner than the thickness of the guide arm 10, both sides of the guide arm 100 are parallel to each other. Not only can the degree and flatness be accurately finished, but the magnetic head can be assembled with an accurate mounting posture and mounting position.

A second embodiment of the invention shown in FIG.
This is a different system in that the ventilation plate support part 13 and the wind shielding plate 12 of the first embodiment shown in the figure are integrated to form a wind shielding plate 12A, and the wind shielding plate 12A is attached to the side surface of the guide arm 10 with screws 14. , and other configurations are the same as those of the first embodiment, so their explanation will be omitted. According to the second embodiment having such a configuration, the number of parts can be reduced and production costs can be reduced.

The third embodiment shown in FIGS. 10 and 11 is similar to the second embodiment described above.
A windbreak arm 11 is provided upstream of the elastic support 8 that supports the windshield plate 12A in the embodiment, and the thickness t'' of this windbreak arm 11 is also larger than the thickness t' of the windshield plate 12A. The structure differs from the second embodiment in that it is formed to satisfy the condition of equation (1), and the other structures are the same as the second embodiment, so their explanation will be omitted. Depending on the structure, the vibration isolation effect can be increased to 20 dB or more.

In the first to third embodiments described above, the guide arm 10 and the disc 1 are made of the same material, for example (11) aluminum alloy, and the wind shield plate 12 is made of the same material.
, 12A and the windbreak arm 11 are made of a material having a lower specific gravity than aluminum alloy, such as synthetic resin. With this configuration, there is an advantage that an increase in the mass of the servo-operated movable part due to the addition of the wind shield plate and the wind shield arm can be suppressed, and an increase in the load on the servo motor can be prevented.

FIG. 12 shows a cross section of a main part of a fourth embodiment of the present invention, in which the distance between the disk 1 and the windbreak arm 11 is L1.
The minimum and maximum distances between the cross section of the elastic support 8 closest to the disk 1 and the disk 1 are tl 1 z*, and the distance between the side surface of the guide arm 10 and the disk 1 is t3, respectively. It is composed of

FIG. 13 shows the results of measuring changes in the vibration amplitude of the elastic support 8 when the tension is changed.

From this figure, the amplitude of the elastic support decreases as L decreases. For example, when L=Lt, the amplitude is about -15 dB compared to when L=t2. Therefore, in order to obtain the currently desired vibration isolation effect (12) of -10 dB or more, at least one portion of the elastic support is hidden by the windbreak arm. That is, it is necessary to satisfy the condition shown in equation (2) below.

Therefore, in this embodiment, the shape of the windbreak arm 11 is defined to fall within a size range that satisfies the condition of equation (2) above.

In the fourth embodiment described above, it is important to set the magnetic head 2 parallel to the surface of the disk and with specified dimensional accuracy. Therefore, the guide arm 1 in contact with the spacer 9
The perpendicularity of the reference plane J at 0 and the parallelism to the reference plane when attaching the guide arm 10 to the servo motor (not shown) must be accurate. For this purpose, it is necessary to consider that productivity will be improved if the thickness of the guide arm 10 is made uniform.

The fifth embodiment shown in FIGS. 14 to 16 is similar to the conventional example (
Although the general structure is similar to that shown in Figures 1 and 2),
The differences are as follows.

(1) The windbreak arm 11 can be fitted by forming a stepped portion on the five surfaces of the guide arm 10 by making the thickness t'' on the tip side of the guide arm 10 smaller than the thickness t' of the guide arm 10. (11) The windbreak arm 11 is formed by bending an elastic plate material to form a fitting portion that is inserted into the fitting portion of the guide arm 10 as shown in FIG. In the fifth embodiment configured in this way, a wind shielding surface is formed that projects perpendicularly to the mating surface of the windshield, and the width t of this wind shielding surface is formed to a dimension that satisfies the above-mentioned formula (2). According to the above, since the windbreak arm height that satisfies the above formula (1) can be easily obtained, it is possible to achieve the desired vibration isolation effect of 10 dB or more.Furthermore, when the windbreak arm 10 of this embodiment is used, the guide arm 10
It is possible to make the processing precision required for this, that is, the perpendicularity of the five faces of the guide arm 10 and the parallelism of the five faces, accurate.

In the sixth embodiment shown in FIGS. 17 and 18, a wind shielding plate attachment part 13 is provided at the tip of the guide bar 10, which is thinner than the attachment part of the elastic support 8, and a wind shielding part 15, a windproof edge 16, and Attachment 7 The wind shield plate 12 is constructed of a thin plate having a flange portion 17, and the wind shield plate 12 is screwed to both sides of the wind shield mounting portion 13, and the wind shield plates 1 above and below these are screwed.
The difference from the third embodiment (Fig. 10.11) is that a ventilation passage (ventilation gap) that communicates the upstream side and the downstream side is provided between 2. omitted.

According to the sixth embodiment configured in this way, the above.

By providing a ventilation path communicating between the upstream side and the downstream side between the lower wind shield plates, the magnetic head support mechanism can obstruct the flow generated by the rotation of the disc. Therefore, pressure fluctuations within the magnetic disk device, rotational power of the disk, vibrations of the elastic support, etc. can be reduced.

〔Effect of the invention〕

As explained above, according to the present invention, by blocking the flow in the direction perpendicular to the elastic support via the wind shield plate, the amplitude caused by the vibration of the elastic support can be significantly reduced and the vibration isolation effect can be improved. At the same time, it is possible to reduce pressure fluctuations in the magnetic disc (15) and the rotational power of the disc.

[Brief explanation of the drawing]

1 and 2 are a plan view and a front view of a conventional magnetic head support mechanism, and FIG. 3 is a view taken along arrow A-A in FIG.
The figure is a visualization diagram using the smoke wire method of the flow around the conventional windbreak arm and elastic support, and Figures 5 and 6 are a plan view of the first embodiment of the magnetic head support mechanism of the present invention, and E in Figure 5. -E arrow view, Figures 7 and 8 are
9 and 10 are plan views of the second and third embodiments of the present invention, respectively. , FIG. 11 is a sectional view taken along the line G-G in FIG. 10, FIG. 12 is a sectional view of the main part of the fourth embodiment of the present invention, and FIG. 13 is the windbreak arm dimensions and the amplitude of the elastic support of the fourth embodiment. The diagrams 14 and 15 showing the relationship with changes are respectively the fifth embodiment of the present invention.
A plan view and a front view of Embodiment 1, FIG. 16 is a sectional view taken along the line H-H in FIG. 14, and FIGS. M-M in Figure 17
FIG. 1... Disc, 3... Slider, 8... Elastic support,
10... Guide arm, 11... Windbreak arm, 12
, 12A... Wind shield plate, 13... Wind shield mounting part. Agent Patent Attorney Akio Takahashi Y lo Scheme 11 Figure 1Z Figure y] 13 Figure'//3 % /4 (D >fJ15 Lo'4 /6 Mutual 77 Figure? [-and Bar 7

Claims (1)

[Scope of Claims] 1. A slider that is disposed opposite to a rotatably provided disc and has a magnetic head, an elastic support that elastically supports the slider, and a guide that rigidly supports the side opposite to the slider of the elastic support. In a magnetic head support mechanism consisting of an arm, or a magnetic head support mechanism comprising a windbreak arm provided upstream of an elastic support of this support mechanism, a windshield plate is provided close to the anti-sun plate side surface of the elastic support. A magnetic head support mechanism featuring: 2. The magnetic head support mechanism according to claim 1, wherein the wind shield plate is made of a thin plate material and attached to the guide arm. 3. The magnetic head support mechanism according to claim 1 or 2, wherein the mounting portion of the wind shield plate is thinner than the elastic support mounting portion. 4. The magnetic head support according to any one of claims 1 to 3, wherein the wind shield plate and the wind shield arm are made of a material having a smaller specific gravity than the guide arm. mechanism. 5. Write the distance L between the surface or edge of the windbreak arm closest to the disk and the disk and the minimum distance between the disk and the position closest to the disk on the cross section of the elastic support during continuous operation. The value and maximum value are respectively 1, . 1. Then, the magnetic head support mechanism according to claim 4, characterized in that the windbreak arm satisfies the condition L(tt+'(ts-t,). 6. The guide arm has its windbreak The magnetic head support mechanism according to claim 5, characterized in that the arm mounting portion is provided with a stepped portion having a thickness thinner than that of the elastic support mounting portion.7. The magnet according to any one of Claims 1 to 4, characterized in that the magnet is composed of a lower plate, and a ventilation passage communicating between the upstream side and the downstream side is provided between the two plates. Head support mechanism.