JP2000057758A - Disk apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a disk apparatus in which a vibration from a board in which a drive unit or the like is built is not transmitted surely to an enclosure. SOLUTION: A disk apparatus is constituted in such a way that an auxiliary support member to which a vibration is hard to transmit and which shoulders the weight of a unit mechanism chassis 6 is installed between the unit mechanism chassis 6 and a unit holder 9, that the deformation of vibration isolating legs 8 due to the weight of the unit mechanism chassis 6 is suppressed, and that a drop in a vibration isolating effect is prevented. As an example of the execution shape of the auxiliary support member which shoulders the weight of the unit mechanism chassis 6, magnets 16a, 16b are used. They support the weight of the unit mechanism chassis 6 by using the repulsive force or the attractive force of the magnets 16a, 16b.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disk drive, and more particularly to a disk drive, which is suitable for rotating a disc-shaped exchangeable recording medium at a high speed and recording and / or reproducing information.
The present invention relates to a disk device such as a ROM, a DVD-ROM, a DVD-RAM, an MO, and a removable HDD.

[0002]

2. Description of the Related Art As a disk device using a disk-shaped recording medium, there is an optical disk device such as a CD-ROM, a DVD, and an MO. In these apparatuses, recording or reproduction is performed by rotating the disk at a high speed, so that a vibration is generated in the disk drive unit due to imbalance of the rotation system or the like. In order to prevent this vibration from propagating to the housing, a unit mechanical chassis incorporating a disk drive mechanism and the housing are connected by vibration-proof legs made of an elastic body. Japanese Patent Application Laid-Open No. H08-106773 discloses an anti-vibration support structure in which the vibration of the drive mechanism of the magnetic disk is not transmitted to the housing as described above.

[0003]

In the conventional vibration-proof supporting structure using only the elastic body as described above, as a practical problem, the transmission of vibration from the drive unit to the housing is reliably prevented. I couldn't. An object of the present invention is to provide a disk device in which vibration from a substrate in which a drive device and the like are incorporated is not reliably transmitted to a housing.

[0004]

In order to solve the above-mentioned problems, according to the present invention, a unit mechanical housing and a housing are provided.
An auxiliary support member for supporting the weight of the unit mechanical chassis is provided to suppress the deformation of the anti-vibration legs due to the weight of the unit mechanical chassis, and to maintain the anti-vibration effect of the anti-vibration legs. As an example of an auxiliary support member that receives the weight of the unit mechanical chassis in a non-contact manner, it supports the weight of the unit mechanical chassis by using a repulsive force or an attractive force of a magnet.

[0005] Some solutions are described below. That is, a mechanism unit incorporating a drive mechanism for rotating a disk-shaped recording medium and a head for recording or reproducing at least information on the recording medium, and a mechanism unit holder for housing the mechanism unit, wherein the mechanism unit In the disk device supporting the mechanism unit holder with an elastic member, an auxiliary support member for correcting a support imbalance is provided between the mechanism unit and the mechanism unit holder.

Further, the auxiliary support member is preferably a member that mainly transmits a static load among static loads and vibrations, and is a member that transmits a force in a non-contact manner. Further, a magnet can be used as the auxiliary support member. Further, the magnet is provided with a surface material having at least lower electric resistance than the magnet on surfaces facing each other.

[0007]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is an external view of an optical disk (CD-ROM) device using one embodiment of the present invention. In the operation of the optical disk device, the disk tray 3 on which the disk 1 is placed is mounted on the front panel 14 of the device by a disk loading mechanism (not shown) in order to send the disk 1 into or out of the device. Protrude from the hole. Disk 1 in this state
Is placed on the protruding disc tray 3. afterwards,
The disc tray 3 sends the disc 1 into the apparatus by the loading mechanism.

The disk 1 is fixed on a turntable 2 of a spindle motor by a magnetic attraction force by a disk clamper 4 attached to a clamper holder 5. The disk 1 starts rotating at a predetermined number of revolutions by a spindle motor, and information is written on the disk 1 by an optical head (not shown) provided in a unit mechanical chassis 6 (mechanical unit) arranged below the disk 1. Write and read. The optical head has an objective lens driving device mounted thereon.

The unit mechanical chassis 6 is provided with a spindle motor, an optical head and a drive mechanism therefor. Further, the unit mechanical chassis 6 includes a unit holder 9 (not shown) and anti-vibration legs 8a made of an elastic member.
8b, 8c and 8d (the details of the anti-vibration legs 8 will be described later). The unit holder 9 and the mechanical base 7 constituting the mechanism unit holder are directly connected to each other by fitting the components.

Regarding the auxiliary support member in the present invention,
This will be described in detail with reference to FIG. Note that the housing is the mechanical base 7, the bottom cover 12, the top cover 13, and the unit holder 9 in FIG. 1, and is divided into three parts in this apparatus, but the bottom cover 12, the top cover 13, and the mechanical base 7 The bottom cover 12 or the mechanical base 7 and the top cover 13 may be integrally formed to be divided into two parts, or may be composed of finer divided parts.

FIG. 2 is a more detailed external view of the unit mechanical chassis 6 and the unit holder 9. The unit mechanical chassis 6 is elastically supported by anti-vibration legs 8 in a box-shaped unit holder 9 without an upper lid, and prevents the vibration generated by the unit mechanical chassis 6 from propagating to the housing. The optical pickup 11 moves in the longitudinal direction of the unit mechanical chassis 6 according to the guide rail 20 attached in parallel with the moving direction of the disc tray 3, and writes and reads information on the disc 1. The read information is transmitted to the processing device via the flexible print circuit 10. The fitting pin 21 is for fitting and fastening the unit holder 9 and the mechanical base 7 as described above.

FIG. 3 shows the structure of the anti-vibration leg 8. Anti-vibration legs 8
Is mounted on a support 17 fixed to the unit holder 9 by a retaining ring 19, and supports the unit mechanical chassis 6. The anti-vibration leg 8 is made of an elastic member. The mechanical properties of the constituent material include a property that the elastic coefficient increases as the amount of deformation increases. Such characteristics are generally found in rubber materials and the like. Therefore, the rigidity of the anti-vibration leg 8 increases as the deformation amount increases, and the anti-vibration effect decreases.

When the disk device is installed in a horizontal position in which the disk is in a horizontal plane (hereinafter referred to as a horizontal position), gravity acts in the longitudinal direction of the column 17, so that the anti-vibration leg 8 is moved by the weight of the unit mechanical chassis. 17 are deformed in the longitudinal direction and are in an equilibrium state. Since there is no deformation in the direction within the horizontal plane, a predetermined vibration damping effect is exhibited in the direction within the disk plane where the unbalanced vibration is large.

However, when the apparatus is tilted, or when the direction of gravity changes as in a vertically placed state in which the disk surface is perpendicular to the horizontal plane (hereinafter referred to as "vertically placed"), the column 1
A load component in a direction orthogonal to the direction 7 is generated, and the anti-vibration leg 8 is deformed in a direction orthogonal to the column by the weight of the unit mechanical chassis 6 to be in a balanced state.

Since the rigidity of the anti-vibration legs 8 is small, the deformation amount of the anti-vibration legs 8 in the direction orthogonal to the columns is increased in the conventional configuration at this time, and as described above, the elastic coefficient is increased, or The direct contact between the side surface and the anti-vibration leg 8 sometimes reduced the anti-vibration effect. To solve this problem, if a normal spring or the like is added to support the weight of the unit mechanical chassis 6 to suppress the deformation of the anti-vibration legs 8, the spring itself becomes a new vibration transmission path. It was not possible to reduce the transmission of vibrations to the vehicle.

FIG. 4 shows an embodiment of the present invention.
The unit holder 9 is viewed from above. The y direction in the figure is the moving direction of the optical pickup 11 described with reference to FIG. 2, and is hereinafter simply referred to as the y direction or the unit mechanical chassis longitudinal direction. The x direction is a direction perpendicular to the y direction, and is hereinafter simply referred to as the x direction or the unit mechanical chassis vertical direction. Also, when the device is in a horizontal position, gravity acts in a direction perpendicular to the xy plane.

In the present invention, magnets 16a and 16b are provided on the side surfaces of the unit mechanical chassis 6 and the unit holder 9 to receive the weight of the unit mechanical chassis 6 by magnetic force and reduce the amount of deformation of the anti-vibration legs 8, thereby preventing the vibration. The vibration effect was prevented from lowering, and the vibration of the housing was reduced. As an example of a specific configuration, as shown in FIG. 4B, a pair of magnets in which the S and S poles or the N and N poles of the magnet are opposed to each other is combined with the unit mechanical chassis 6 and the unit holder 8. , One of the pair to the unit mechanical chassis 6 and the other to the unit holder 8
Fix to.

In FIG. 4A, a pair of magnets 16a and 16b is arranged on both sides of the unit mechanical chassis 6, but if the installation posture of the apparatus is determined, only one side is sufficient. This configuration supports the unit mechanical chassis 6 using the repulsive force of the magnet. When the magnets 16a and 16b approach each other due to the deformation of the anti-vibration leg 8, a repulsive force is generated between the magnets, and the unit mechanical chassis 6 is supported. Since the magnetic force has a large vibration damping effect as compared with a metal spring or the like, it is possible to support only the weight of the unit mechanical chassis 6 without forming a new vibration transmission path.

In FIG. 4, the magnets 16a and 16b are provided on the center line of the unit mechanical chassis 6. However, as described later, in order to support the static weight of the unit mechanical chassis 6, the magnets 16a and 16b are installed at the center of gravity. Doing so is more stable. Further, in order to increase the vibration isolation effect in consideration of the balance of the moment load, it is necessary to install the motor at a position where the force including the moment is balanced as described with reference to FIG. However, FIG. 4 is superior in manufacturability since the position can be easily specified. Therefore, when the manufacturability is prioritized, the one shown in FIG. 4 is more appropriate, and a sufficient anti-vibration effect can be obtained even with this configuration.

Here, with reference to FIGS. 7 and 8, a description will be given of the point that a magnetic spring using a magnet is superior to a normal elastic spring. The whole system is simply modeled as shown in FIG. The mechanical vibration considered in this model is a vibration in the direction parallel to the disk perpendicular to the column 17 shown in FIG. Regarding the longitudinal direction of the column 17,
This is not a problem because the vibration is smaller than in the direction parallel to the disk.

As shown in FIG. 7A, the unit mechanical chassis is supported by vibration-proof legs made of an elastic member, and is additionally supported by a magnetic spring. FIG. 7B shows the spring characteristics of the anti-vibration legs and the characteristics of the magnetic spring. In this figure, the horizontal axis represents displacement from the equilibrium equilibrium position, and the vertical axis represents reaction force of each spring, and is schematically plotted.

The anti-vibration legs are generally made of a rubber material. By reducing the rigidity, the natural frequency of the unit mechanical chassis support system is kept away from the frequency of the drive unit to reduce the vibration transmission rate. In addition, the vibration insulation of the housing is achieved by utilizing the vibration damping effect of the rubber material itself. The rubber material generally has low rigidity (represented by the slope of the tangent of the curve) when the displacement is small, as shown in the spring characteristic of the anti-vibration leg in FIG. 7B, but increases the displacement from the equilibrium position. When the deformation amount increases, the rigidity increases. In a normal installation state (horizontal installation), the unit mechanical chassis weight is not loaded in the direction parallel to the disk. Supporting.

However, when the disk drive is placed vertically or the disk device is tilted, a load due to the weight of the unit mechanical chassis is generated in a direction parallel to the disk surface. . Since the rigidity of the anti-vibration legs is designed to be low for the purpose of vibration isolation as described above, in order to generate a force that balances with the weight W, the leg must be deformed to a region where the rigidity sharply increases. for that reason,
The equilibrium position in the vertically placed state moves to the point A in FIG. The rigidity of the anti-vibration legs near point A is very large as compared with the vicinity of point O. As a result, the natural frequency of the unit mechanical chassis support system increases and approaches the frequency of the driving unit. Ascends and the damping effect decreases.

In order to improve the deterioration of the vibration-proof effect due to the large deformation of the vibration-proof legs, it is considered to suppress the deformation of the vibration-proof legs by using an auxiliary support member. First, consider the case where an elastic body such as a normal metal spring is used. In this case, in order to support the unit mechanical chassis weight W without greatly deforming the anti-vibration legs, a member having considerably higher rigidity than the anti-vibration legs must be used. That is, a member having the characteristics shown in the elastic body spring characteristics of FIG. 7B is provided between the unit mechanical chassis and the housing. The support system as a whole has the anti-vibration leg + elastic body spring characteristics shown in the figure, but since the elastic body spring has high rigidity, the rigidity of the entire support system is almost determined by the characteristics of the elastic body spring. .

As a result, the equilibrium position when the unit mechanical chassis weight W is loaded is point C, and the amount of deformation of the anti-vibration legs can be kept small. However, the rigidity of the support system is increased due to the newly provided elastic member, and the vibration isolation effect is reduced by increasing the natural frequency of the support system as described above. This means that the elastic member becomes a new vibration transmission path, and the vibration is transmitted to the housing.

As a solution to this problem, a configuration in which a magnetic spring made of a magnet is provided between the housing and the unit mechanical chassis as shown in FIG. FIG. 7A shows a configuration in which an upward magnetic force always acts. When the unit mechanical chassis is displaced downward, the distance between the magnets is reduced, so that the reaction force due to the magnetic force increases, and when the unit mechanism chassis is displaced upward, the reaction force decreases. Since this magnetic force is inversely proportional to the square of the distance, if the distance between the magnets is increased to some extent, the reaction force against the displacement of the magnetic spring is much larger than that of a normal elastic spring, as shown in FIG. Shows a moderate response. Also,
An upward reaction force is always generated.

Therefore, the combined rigidity of the anti-vibration leg and the magnetic spring exhibits a gentle spring characteristic while retaining the spring characteristic of the anti-vibration leg, as shown in FIG. As a result, in the vertical position, the equilibrium position when the unit mechanical chassis weight W is loaded is point B, without deforming the anti-vibration legs to the region where the rigidity sharply increases, and supporting the elastic body spring as much as described above. The unit mechanical chassis weight W can be supported without increasing the rigidity of the system. Unit mechanical chassis weight W
When no load is applied, an equilibrium state is established at point D in FIG. 7B, but also in this state, the rigidity of the support system does not increase as much as the elastic body spring.

In order to realize such a gradual spring characteristic by using a normal elastic body spring, it is necessary to give a large initial deformation to a spring having a long natural length before use.
There are many problems in terms of manufacturability, weight reduction, material cost, and the like.
In addition to the above advantages, the magnetic spring is desirable as a vibration insulating member because it has a kinetic energy dissipation due to eddy current heat generation, which will be described later, that is, a vibration damping effect.

FIG. 8 shows a configuration in which the rigidity of the vibration isolating leg is further reduced from the initial value by using a magnetic spring. In the configuration of FIG. 8A, the unit mechanical chassis is lifted by a pair of magnets that generate an attractive force. FIG.
As shown in (b), the magnetic force always acts upward, but when the unit mechanical chassis is displaced downward, the magnetic force decreases because the distance between the magnets increases, and when the unit mechanical chassis is displaced upward, the magnetic force increases. I do.

Therefore, if the magnitude and the interval of the magnets are appropriately set, the spring characteristics obtained by combining the anti-vibration legs and the magnetic spring have a flat portion as shown in FIG. 8B. If the spring reaction force of this flat portion is designed to be balanced with the unit mechanical chassis weight W, the rigidity of the support system becomes very small, which is effective in reducing the vibration transmission rate. However, if the unit mechanical chassis weight W is larger than the flat portion, or if the unit mechanical chassis weight W
If no load is applied, an equilibrium state is established at points B and D, which have high rigidity. As described above, the magnetic spring using the magnet is superior to the ordinary elastic body spring as an auxiliary support member.

FIG. 4B is an enlarged view of the magnets 16a and 16b. A part of the magnet supporting the weight of the unit mechanical chassis 6 includes a magnet cover 18a made of a material having a lower electric resistance than the magnet itself. The embodiment provided with 18b is shown. This utilizes the magnetic viscous effect.

The principle of vibration damping due to magnetic viscosity is as follows. When the magnet moves due to mechanical vibration, the density of the magnetic flux passing through the surrounding conductor including the magnet itself changes, and an eddy current is induced in the conductor. The magnetic field interacts, and the magnetic force acts in a direction that hinders the movement of the magnet, thereby suppressing vibration.

At the same time, the kinetic energy is dissipated due to the heat generated by the electric resistance, and the vibration is attenuated. When there is no conductor around, or when the magnet itself and the surrounding conductor have high electric resistance and do not generate a sufficient eddy current, the magneto-rheological effect cannot be obtained. Therefore, in order to obtain a large magneto-rheological effect, an eddy current may be actively generated to increase the interaction with the magnet.

FIG. 4B is a block diagram of a magnet according to an embodiment for realizing this. Covers 18a and 18b made of a low electric resistance material such as aluminum are attached to the surfaces of the magnets 16a and 16b. The role of the magnet covers 18a, 18b is to allow a larger eddy current to flow, and it is required that the magnet covers 18a, 18b be smaller than at least the electric resistance of the magnets 16a, 16b.

The magnet covers 18a and 18b are preferably thin so as not to reduce the magnetic force. Further, as shown in the figure, the magnet covers 18a and 18b
a, 16b, the magnets 16a, 16b
It is also possible to provide on the side of b. However, in the figure,
When the unit mechanical chassis vibrates in the vertical direction, the time change of the magnetic flux density is considered to be the largest on the magnet facing surface. Therefore, providing the magnet covers 18a and 18b on the facing surfaces provides a higher magnetic viscous effect. Can be

Specifically, when the unit mechanical chassis 6 vibrates in the x direction in FIG. 4, the distance between the opposing magnets 16a and 16b fluctuates. Hereinafter, the magnet 16a
Assume that it is stationary. The density of the magnetic flux exiting the magnet 16b and passing through the magnet cover 18a increases as the magnet 16b approaches the magnet 16a and decreases as the magnet 16b moves away. The eddy current flows in a direction to cancel the change in the magnetic flux density penetrating the magnet cover 18 to generate a magnetic field. Therefore, apparently, when the magnet 16b approaches, the magnetism of the magnet 16a increases, and when the magnet 16b separates, the magnetism decreases. That is, the magnetic force changes so as to suppress the displacement of the magnet 16b.

Therefore, a magnetic force is generated for a static load as in the case where the magnet cover 18 is not provided, and a magnetic force acts to suppress a displacement for a dynamic load. And at the same time, the kinetic energy is dissipated by the heat generated by the eddy current, so that it functions as a vibration damping mechanism.

As another embodiment of FIG.
A plurality of pairs 6a and 16b may be provided and installed on the unit mechanical chassis 6 at intervals. For example, a pair of four magnets 16a and 16b is
Are provided at the corners in the longitudinal direction of the unit mechanical chassis or on the corners in the vertical direction of the unit mechanical chassis. By doing so, the moment load from the drive system can be supported, as compared with the case where the magnet is supported by two sets of magnets as shown in FIG. 4, so that the stability is improved.

In the above embodiment, the magnets are provided on a plane parallel to the y direction. However, similar effects can be obtained by providing them on a plane parallel to the x direction. Furthermore, it is also possible to install on all surfaces parallel to the x and y directions.

Although the above-described embodiment uses the repulsive force of the magnet, an embodiment using the attractive force of the magnet will be described below with reference to FIG. In this configuration, the magnet 1
6a and 16b are mounted so that the S pole and the N pole face each other on a plane parallel to the x direction, and the unit mechanical chassis 6 is pulled up by the attraction of the magnet to reduce the amount of deformation of the vibration isolating legs 8. .

Also in this case, as described with reference to FIG. 4, the weight of the unit mechanical chassis 6 is supported by the magnetic force.
Is suppressed, and the deterioration of the vibration control function when the posture of the device is changed can be prevented. In FIG. 5, the magnets are provided on a plane parallel to the x direction. However, similar effects can be obtained by providing them on a plane parallel to the y direction. Furthermore, it is also possible to install on both surfaces parallel to the x and y directions. Further, in FIGS. 4 and 5, repulsive and attractive magnet pairs may be combined and provided on any or both surfaces parallel to the x and y directions.

A comparison will be made between the configuration using the repulsive force and the configuration using the suction force. For example, when two magnet pairs are provided at the position shown in FIG. 4A, in the attraction type magnet, the attraction force of the magnet on the approaching side is further increased. There is. In this case,
This is undesirable because the anti-vibration legs 8 are deformed and come to rest. On the other hand, in the case of a repulsion type magnet, a magnetic force that always tries to push back acts, so the above is not the case,
Considering this, the repulsion type is more advantageous.

FIG. 6 shows a configuration in which a dynamic effect is considered. Anti-vibration legs 8 due to static weight of unit mechanical chassis 6
In order to suppress the deformation of the magnet 16a, the magnet 16a is positioned on a line passing through the center of gravity G of the unit mechanical chassis 6 and extending in the direction of gravity.
16b may be provided to support the weight. However, when the spindle motor 15 is driven, a moment opposite to the motor rotation direction acts on the unit mechanical chassis 6. In order to suppress the deformation of the anti-vibration leg 8 due to this moment, a pair of the magnets 16a and 16b is placed at a distance L
It may be provided at a position only apart. The value of L is the moment generated by the spindle motor as M, the magnets 16a, 1
Assuming that the magnetic force of 6b is F, it is given by the following equation from a mechanical moment balance equation.

L = M / F If a pair of magnets 16a and 16b is provided at the position of L obtained from the above equation, in addition to the deformation of the vibration isolating leg 8 due to the weight of the unit mechanical chassis 6, the rotation of the spindle motor 15 Deformation due to a moment can also be reduced, and the performance of the anti-vibration legs 8 can be sufficiently brought out.

In FIG. 6, the magnets 16a and 16b are provided on a plane parallel to the y direction. However, the magnets 16a and 16b can be provided on a plane parallel to the x direction or on both surfaces. As the type of the magnet, either a repulsion type or a suction type can be used.

[0046]

According to the present invention, by providing the auxiliary support member, the vibration of the housing can be reduced irrespective of the posture of the apparatus such as vertical installation and horizontal installation.

[Brief description of the drawings]

FIG. 1 is an optical disc (CD-R) for explaining the present invention.
It is an external view of an OM) apparatus.

FIG. 2 is an external view of a CD-ROM unit mechanism for explaining the present invention.

FIG. 3 is a structural diagram of a vibration isolating leg according to the present invention.

FIG. 4 is a top view of a CD-ROM unit showing one embodiment of the present invention.

FIG. 5 is a top view of a CD-ROM unit showing another embodiment of the present invention.

FIG. 6 is a top view of a CD-ROM unit showing another embodiment of the present invention.

FIG. 7 is a diagram illustrating the effect of the magnetic spring in the present invention.

FIG. 8 is a diagram illustrating the effect of reducing the rigidity of the support system by the magnetic spring according to the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Recording medium (disk) 2 Turntable 3 Disk tray 4 Disk clamper 5 Clamper holder 6 Unit mechanical chassis 7 Mechanical base 8a, 8b, 8c, 8d Elastic member (anti-vibration leg) 9 Unit holder 10 Flexible print circuit 11 Optical pickup 12 Bottom Cover 13 Top cover 14 Front panel 15 Spindle motor 16a, 16b Magnet 17 Support 18a, 18b Magnet cover 19 Retaining ring 20 Guide rail 21 Mating pin

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hisahiro Miki 4-6-6 Kanda Surugadai, Chiyoda-ku, Tokyo Inside the Visual Information Media Division of Hitachi, Ltd. (72) Inventor Shigeki Mori 4-6-1 Kanda Surugadai, Chiyoda-ku, Tokyo Hitachi, Ltd.Video Information Media Division (72) Inventor Shinobu Yoshida 502, Kandachicho, Tsuchiura-shi, Ibaraki Pref.

Claims (5)

[Claims] A mechanism unit incorporating a drive mechanism for rotating a disk-shaped recording medium, a head for recording or reproducing at least information on the recording medium, and a mechanism unit holder for accommodating the mechanism unit; A disk device for supporting a mechanism unit and the mechanism unit holder by an elastic member, wherein an auxiliary support member for correcting a support imbalance is provided between the mechanism unit and the mechanism unit holder. . 2. The disk device according to claim 1, wherein the auxiliary support member includes a static load and a vibration.
A disk device characterized by being a member mainly transmitting a static load. 3. The disk device according to claim 1, wherein the auxiliary support member is a member that transmits a force in a non-contact manner. 4. The disk device according to claim 1, wherein a magnet is used as said auxiliary support member. 5. The disk device according to claim 4, wherein said magnets are provided with surface materials having at least lower electric resistance than said magnets on surfaces facing each other.