JPH09329188A - Antirattler - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an antirattler which has the enough vibration proof characteristic and the shock resistant characteristic, can be made compact and thin, and sufficiently control the movable displacement of the rubber vibration isolator. SOLUTION: The shape of a rubber cushion main body 31 is a doughnut-type rotator obtained by rotating an almost H-shaped section body on the center axis, the innermost peripheral part 33 has a thin cylindrical shape, an intermediate neck part 34 has the thick disc shape extending to the outer periphery from the center part of the innermost peripheral part 33, the outermost peripheral part 35 has the thick cylindrical shape swelled from the intermediate neck part 34, and the outer peripheral face of the outermost peripheral part 35 is formed by chamfering a ridge line, and has a concave part 36 to be engaged with a pick-up plate chassis. Further the rubber cushion main body 31 is loaded on an optical pick-up module in a condition that a boss integrated with tray, is inserted into a cylinder of the innermost peripheral part 33, both ends of the cylinder of the innermost peripheral part 33 are kept into contact with a box member, and the both ends of the cylinder of the outermost peripheral part 35 are not kept into contact with the box member.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration proof device such as a vibration proof rubber used in an optical disc device, and it is an object of the present invention to provide a new vibration proof device for an optical disc device having improved vibration resistance and impact resistance. To do.

[0002]

2. Description of the Related Art FIG. 9 is a diagram showing the structure of a conventional optical disk device. As shown in FIG.
An optical pickup module 13 is attached to the drive body 12 by a pickup sheet metal chassis 14 and configured. A direction D indicated by an arrow in the figure indicates a tracking direction of the optical pickup module 13. Also,
Anti-vibration structures 16, 17 are provided at three locations between the shaft 15 on the drive body 12 side and the pickup sheet metal chassis 14.
18 are provided.

FIG. 10 is a sectional view of a main part of a vibration-proof structure. In the figure, the vibration isolation structures 16 to 18 are composed of the following components. That is, the anti-vibration rubber body 21 has openings 1 at the top and bottom.
9 and the inside thereof is of a so-called lantern type having upper and lower air chambers 22a and 22b. Furthermore, coil springs 23a and 23b are provided in the air chambers 22a and 22b, respectively.
Is stored.

Further, the pickup sheet metal chassis 14 is provided with a circular opening 14a, and the outer wall recess 21a near the center of the lantern-shaped vibration proof rubber main body 21 is fitted into the circular opening 14a. Has been done. The pickup sheet metal chassis 14 fitted with the vibration proof rubber body 21 is inserted into the shaft 15 to form a vibration proof structure.

With the above structure, the vibration-proof rubber main body 21 is provided before external vibrations and shock waves are transmitted to the pickup sheet metal chassis 14 through the shaft 15 of the drive main body 12.
And the coil springs 23a and 23b absorb and attenuate the energy of vibration and impact. It has been known that the damping characteristics in this case are more effective as the hardness of the vibration-proof rubber main body 21 is lower, that is, the softer the vibration-proof rubber main body 21 is. Therefore, conventionally, the weight supported by the pickup sheet metal chassis 14 is reduced by the coil springs 23a, 2
The vibration damping rubber main body 21 is formed to have a low hardness by being handled by 3b.

[0006]

However, assuming that the conventional vibration-proof structure is used to rotate the optical disk at 4 × speed, the vibration in the tracking direction (D direction in the figure) generated by the rotation of the spindle motor 24 is generated. The acceleration is 0.25 G in the frequency characteristic of the conventional anti-vibration structure (for example, f0 = 70 Hz in FIG. 2),
It was known that this was almost equal to the limit for the skip condition.

Further, the conventional vibration-proof structure technology has the following problems. 1) Depending on the shape of the anti-vibration rubber, the vibration resistance or impact resistance for the drive of the optical disk device may be impaired.

2) Since oil is enclosed in the anti-vibration rubber and a coil spring is incorporated, there is a limit to the size or thickness reduction of the optical disk device due to its structure.

3) In the frequency characteristics, when an optical disc having a deviated center of gravity is rotated at a high speed of 6 times or more, the transmissibility (Q
In some cases, the internal vibration is amplified by the value), and the vibration resistance characteristics may be impaired.

4) When a larger impact is applied to the optical disk device, the vibration-proof rubber attached to the pickup sheet metal chassis mainly shakes up and down, so that the optical disk device is relatively moved between the housing and the optical pickup module. Fluctuations may occur and data reading errors may occur during operation, or the optical pickup module itself may interfere with the housing of the optical disk device during non-operation, and the optical disk clamped by the spindle motor or the pickup sheet metal chassis, etc. Could be damaged.

Therefore, the above problems have been solved, sufficient vibration resistance and impact resistance have been achieved, downsizing and thinning are possible, and an internal disturbance suppressing effect and external disturbance as an optical disk device have occurred. An object of the present invention is to provide a vibration damping device that sufficiently regulates the movable displacement of the vibration damping rubber at the time.

[0012]

According to the vibration isolator of the present invention, the shape of the anti-vibration rubber body is the shape of a donut-shaped rotating body obtained by rotating a substantially H-shaped cross-section around the central axis. The innermost peripheral portion has a thin-walled cylindrical shape, the middle neck portion has a thick disk shape extending further from the center portion of the innermost peripheral portion to the outer periphery, and the outermost peripheral portion has a thick-walled cylindrical shape that bulges from the middle neck portion. The outer peripheral surface of the outermost peripheral portion is chamfered at the ridgeline and formed to have a fitting recess for fitting with the pickup sheet metal chassis.

Further, when mounting the above-mentioned anti-vibration rubber main body to the optical pickup module, the boss is inserted into the cylinder of the innermost peripheral portion so that both ends of the cylinder of the innermost peripheral portion are brought into contact with the housing, and Both ends of the cylinder in the outer peripheral portion are configured so as not to touch the housing.

In the above structure, the natural frequency associated with the shape of the intermediate neck is adjusted to the frequency characteristic in the tracking direction. Accordingly, the vibration acceleration and the shock acceleration are alleviated by the vertical motion and the lateral motion of the anti-vibration rubber in the middle neck portion, and the vibration resistance and the shock resistance in the tracking direction are improved.

Further, when a larger impact is applied,
Since the middle neck portion swings up and down and the ridge line is chamfered, it is possible to swing the region surrounded by the housing and regulate the movable amount.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION The invention described in claims 1 and 2 of the present invention is formed by rotating a rotating body having a substantially H-shaped cross section around a central axis, and has a generally donut shape as a whole. A vibration isolator having a shape, the innermost peripheral portion of the shape is a thin-walled cylindrical shape, the middle neck portion is a thick disk shape extending further from the central portion of the innermost peripheral portion to the outer periphery, the outermost peripheral portion is It is formed in a thick-walled cylindrical shape that bulges out from the intermediate neck portion, and the outer peripheral surface of the outermost peripheral portion is chamfered with a ridge line, and the outer peripheral cylindrical surface of the outermost peripheral portion is for fitting with a supporting member of the supported means. It is formed into a shape having a fitting recess, and vibration acceleration and shock acceleration are alleviated by the movement of the middle neck portion, and it is possible to improve the vibration resistance and shock resistance of the optical disk drive device. Is to have.

According to a third aspect of the present invention, the hollow cylindrical portion of the innermost peripheral portion is inserted into the boss provided upright on the first casing, and the first casing is provided at one end of the innermost peripheral portion. Abutting the second housing facing the first housing to the other end of the innermost peripheral portion,
Further, the third casing is fitted into the fitting recess provided in the outermost peripheral portion, and the third casing is supported without abutting against the first casing or the second casing. Item 1
It is a vibration isolation device described in, and when a larger impact is applied, the middle neck part shakes up and down greatly,
In addition, since the ridge line is chamfered, the swing range has an action that the movable amount (swing range) can be regulated by swinging the region surrounded by the housing.

Embodiments of the present invention will be described below with reference to the drawings. (Embodiment 1) FIG. 1 is a sectional view of a vibration isolator 30 according to an embodiment of the present invention. The vibration isolator 30 of the optical disc device of the present invention has a vibration-proof rubber main body 31 having a thin-walled cylindrical shape having an opening 32 at an innermost peripheral portion 33 for attaching to the optical disc device, and an intermediate neck portion 34 of the innermost peripheral portion 33. A thick disk shape extending further from the central portion to the outer periphery is formed, and the outermost peripheral portion 35 is formed into a thick cylindrical shape bulging from the intermediate neck portion 34, and the outer peripheral surface of the outermost peripheral portion 35 is chamfered with a ridge line (35a).
And has a fitting recess 36 for fitting with the pickup sheet metal chassis 14.

The ratio of the anti-vibration rubber body 31 in both the shearing and compression directions, for example, the resonance frequency in the shearing direction of the anti-vibration rubber body 31, which is also the in-plane direction of the optical disk device, is 1
The resonance frequency in the compression direction of the anti-vibration rubber body 31 which is 90 Hz and is also the direction perpendicular to the optical disk surface is 100
By setting the frequency to Hz, the vibration resistance and the shock resistance can be improved while damping and insulating the vibration and the shock from the inside and the outside of the optical disk device.

Further, as shown in FIG. 1, the vibration-proof rubber main body 3
In No. 1, a tray-integrated boss 41 is inserted inside the cylinder of the innermost peripheral portion 33, and is fixed to the optical disk device by a mounting screw 42. Further, the pickup sheet metal chassis 14 is provided with a circular opening 14a.
The fitting recess 36 on the outer peripheral surface of the outermost peripheral portion of the vibration-proof rubber main body 31 is fitted to the 4a.

By surrounding the vibration-proof rubber main body 31 with the tray 37 constituting the upper surface of the mounting surface of the optical disk device and the tray cover 38 constituting the lower surface, the vibration-proof rubber main body 31 is impacted while restricting its movable amount. It can be used as a stopper for, and the amount of movable displacement of the anti-vibration rubber main body 31 when an internal disturbance suppressing action of the optical disk device or an external disturbance occurs can be sufficiently regulated.

Further, when a larger impact is applied to the optical disk device, in the vibration isolator 30 of the present invention, the antivibration rubber main body 31 attached to the pickup sheet metal chassis 14 moves up and down mainly in the middle neck portion 34. A large fluctuation causes relative fluctuation between the optical disk device and the optical pickup module. However, the chamfer 35 is attached to the outermost peripheral portion 35 fitted with the pickup sheet metal chassis 14.
By performing a, the vibration-proof rubber main body 31 moves in the area surrounded by the tray 37 and the tray cover 38, and also serves as an impact stopper while limiting the movement amount to ± 0.5 mm. Further, by maintaining the allowable range of relative displacement between the optical disc and the lens 43 of the optical pickup module, it is possible to prevent a phenomenon that a data reading error occurs during the operation of the optical disc device. Further, when the optical disk device is not in operation, the optical disk, the optical pickup module and the like are not likely to be damaged by impact.

The optical pickup module, which is the heart of the optical disk device, is a spindle motor 24.
The actuator 44, the pickup sheet metal chassis 14, and the pick cover 45 are provided.

The anti-vibration rubber body 31 of the present invention is shown in FIG.
It is attached as shown in FIGS. Further, when the optical disk device is attached to the main body of the personal computer, the optical disc device is fixed at attachment positions 46, 47, 48 and 49.

The effect of improving the miniaturization and thinning of the structure described above will be described below. For example, the conventional anti-vibration rubber body 21 shown in FIG. 10 had a height of 8.5 mm, but the anti-vibration rubber body 31 in the embodiment of the present invention could have a height of slightly 4.5 mm. .

FIG. 2 is a diagram showing a frequency characteristic curve of the anti-vibration rubber body 31 according to the embodiment of the present invention. In this characteristic curve diagram, the horizontal axis represents frequency (Hz) and the vertical axis represents vibration transmission. The frequency characteristic of the vibration-proof rubber main body 21 when the ratio (Q value) is taken and the total mass of the optical pickup module including the optical disc in the D (tracking) direction is shown.
As shown in the figure, in the conventional anti-vibration rubber body 31, f0 was 70 Hz and the Q value was 9 dB, whereas in the anti-vibration rubber body 31 of the present invention, f0 was 190 Hz and the Q value was 5 dB. I know there is. The setting point of f0 of the present invention is that the first condition is to suppress the internal vibration generated when an optical disk having a decentered center of gravity in the apparatus is rotated at a high speed by the spindle motor 24, for example, at a high speed of 6 times or more. Further, it is for improving the vibration resistance and the shock resistance characteristics of the vibration damping against the disturbance.

FIG. 3 is a diagram showing a characteristic curve of vibration acceleration in tracking control according to the embodiment of the present invention. In this characteristic curve diagram, the horizontal axis represents the frequency (Hz) and the vertical axis represents the relative acceleration (G) between the optical pickup module and the lens 43, and the anti-vibration rubber when the input disturbance is 0.2 G It shows the difference in relative acceleration with f0 of the main body 31 as a parameter.

When the total weight of the optical pickup module including the optical disk is the total mass, the f0 in the D (tracking) direction of the frequency characteristic of the antivibration rubber body 31 is 190 Hz and the frequency characteristic of the conventional antivibration rubber body 31 is D ( It can be seen that a significant level difference occurs when f0 in the (tracking) direction is 70 Hz. The reason why the level is large when f0 is 70 Hz is that the Q value of the frequency characteristic result shown in FIG. 2 is 9 dB, which is a factor of amplifying the disturbance about twice as much as that of the present invention type. Therefore, the conventional anti-vibration rubber body 21 is unsuitable for high-speed rotation of 6 times or more.

FIG. 4 is a frequency characteristic curve diagram of relative acceleration of the vibration-proof rubber body 31 in the embodiment of the present invention. In the figure, it is a figure which shows the characteristic curve of the relative acceleration with respect to the change of the transmissibility (Q value, FIG. 2) when f0 in the D (tracking) direction of the anti-vibration rubber main body 31 is 190 Hz. This frequency characteristic curve diagram shows the frequency (Hz) on the horizontal axis.
Is the relative acceleration (G) on the vertical axis, and the input disturbance is 0.2
When G is given, it represents the relative acceleration (G) with the total mass of the optical pickup module including the optical disc. According to the example shown in this figure, the relative acceleration is lower as the transmissibility (Q value) of f0 in the D (tracking) direction of the anti-vibration rubber body 31 at 190 Hz is as close as possible to 0 dB. . The Q value of the vibration damping structure 30 of the present invention is 5 dB as shown in FIG. Further, as shown in FIG. 4, when f0 is 190 Hz, the relative acceleration is 0.36 G, which means that the transmissibility is about 1.8 times. On the other hand, since the Q value of the conventional vibration damping structures 16 to 18 is also 9 dB, the relative acceleration thereof is 0.47 G, and thus the transmissibility is 2.35 times.

FIG. 5 is a characteristic curve diagram showing vibration resistance characteristics in the tracking direction of the vibration isolator according to the embodiment of the present invention. This characteristic curve diagram shows the frequency (Hz) on the horizontal axis,
In addition, the vertical axis indicates the limit vibration acceleration (G), and the sound skip evaluation result of the sound data read by the optical pickup in the D (tracking) direction is shown. As shown in the figure, in the conventional anti-vibration structure, the limit was 0.27 G, while
In the present invention, it can be seen that the level is improved to the level of 0.6G. It can be seen that the point at which the sound skip level is the worst is due to the difference between the f0 and Q values of the respective vibration isolation structures 16 to 18 and 30 shown in FIG.

FIG. 6 is a characteristic curve diagram showing vibration resistance characteristics in the focus direction of the vibration isolator according to the embodiment of the present invention. In this characteristic curve diagram, the horizontal axis represents frequency (Hz) and the vertical axis represents limit vibration acceleration (G), and Fo (focus)
The sound skip evaluation result of the sound data read by the optical pickup in the direction is shown. As shown in the figure, in the conventional vibration-proof structure, the limit was 0.5 G, whereas in the present invention, it was improved to the level of 0.8 G.
With respect to the standard value of 0.25 G, the vibration resistance level of both anti-vibration structures is better than the sound skip evaluation result in the tracking direction shown in FIG. This is the vibration-proof rubber body 3 of the present invention.
It can be seen that the effect is a slight vertical movement in the direction of compression of the intermediate neck portion 34 of No. 1.

FIG. 7 is a characteristic curve diagram showing impact resistance characteristics in the tracking direction of the vibration isolator according to the embodiment of the present invention. This characteristic curve diagram shows the impact application time (ms
ec), and the vertical axis represents the limit impact acceleration (G), D
The sound skip evaluation result of the sound data read by the optical pickup in the (tracking) direction is shown. As shown in the figure, the limit impact acceleration at the application time of 11 ms in the standard for evaluation of CD-ROM is 0.7 G in the past, whereas the vibration isolator of the present invention is Standard 1G
It can be seen that it has improved to 1.21G.

Further, particularly in the case of an optical disk drive device built in a notebook personal computer, it is necessary to consider the influence of the impact of typing on the keyboard.
Therefore, for reference evaluation, the limit impact acceleration at an application time of 6 ms is also shown in FIG. As shown in FIG.
While the limit was 9 G, the vibration damping device of the present invention has been improved to 1.74 G.

FIG. 8 is a characteristic curve diagram showing impact resistance characteristics in the focus direction of the vibration isolator according to the embodiment of the present invention. This characteristic curve diagram shows the impact application time (mse
c), and the vertical axis represents the limit impact acceleration (G).
The sound skip evaluation result of the sound data read by the optical pickup in the (focus) direction is shown. As shown in the figure, the critical impact acceleration at the standard application time of 11 ms is
It can be seen that, while the limit was 3.2 G in the past, the vibration damping device of the present invention cleared the standard of 1.5 G and improved to 5.9 G.

As in the case of FIG. 7, it is necessary to consider the influence of typing impact of the notebook type personal computer. Therefore, for reference evaluation, the limit impact acceleration at an application time of 6 ms is also shown in FIG. As shown in FIG. 8, the conventional value is 3.5.
While G is the limit, the vibration damping device of the present invention has a limit of 6.
It has improved to 5G.

[0036]

As described above, according to the vibration isolator for the optical disk device in the first embodiment of the present invention, the resonance frequency in the tracking direction of the optical disk is 19
The resonance frequency is 0 Hz and the resonance frequency in the focusing direction of the optical disc is 100 Hz. As a result, it is possible to reduce vibration acceleration and shock acceleration due to internal vibration acceleration or disturbance generated from the spindle motor of the optical disk device. Therefore, the vibration resistance and impact resistance of the optical disk drive can be improved.

Further, since the coil spring in the air chamber, which is conventionally provided, can be omitted, the overall thickness of the optical disk drive device can be made thin, and it can be easily mounted on a notebook computer or the like. have.

Further, according to the vibration isolator of the optical disk device in the second embodiment of the present invention, the outermost circumference of the vibration isolating rubber main body fitted to the pickup sheet metal chassis when a large impact is applied to the optical disk device. Since the part is wrapped with the tray that constitutes the upper surface of the optical disc device and the tray cover that constitutes the lower surface, it serves as an impact stopper while regulating the movable amount of the vibration-proof rubber body.

In this way, the relative positional relationship between the housing of the optical disk device and the optical pickup module can be maintained, and a data reading error during operation can be prevented. Further, when the optical disk device is not in operation, the optical disk, the optical pickup module and the like are not likely to be damaged by the impact.

As described above, according to the present invention, downsizing and thinning are realized, and sufficient vibration resistance and impact resistance are provided,
It is possible to provide a vibration isolation device that further improves the reliability of the optical disc device.

[Brief description of drawings]

FIG. 1 is a sectional view of a vibration damping device according to an embodiment of the present invention.

FIG. 2 is a diagram showing a frequency characteristic curve of the anti-vibration rubber body according to the embodiment of the present invention.

FIG. 3 is a diagram showing a characteristic curve of vibration acceleration in tracking control according to the embodiment of the present invention.

FIG. 4 is a frequency characteristic curve diagram of relative acceleration of the anti-vibration rubber body according to the embodiment of the present invention.

FIG. 5 is a characteristic curve diagram showing anti-vibration characteristics in the tracking direction of the image stabilization device according to the embodiment of the present invention.

FIG. 6 is a characteristic curve diagram showing vibration resistance characteristics in the focus direction of the image stabilization device according to the embodiment of the present invention.

FIG. 7 is a characteristic curve diagram showing impact resistance characteristics in the tracking direction of the vibration isolator according to the embodiment of the present invention.

FIG. 8 is a characteristic curve diagram showing impact resistance characteristics in the focus direction of the vibration isolator according to the embodiment of the present invention.

FIG. 9 is a diagram showing a configuration of a conventional optical disc device.

FIG. 10 is a cross-sectional view of the main part of the vibration-proof structure.

[Explanation of symbols]

 11 Optical Disk Device 12 Drive Body 13 Optical Pickup Module 14 Pickup Sheet Metal Chassis 14a, 14b Circular Opening 15 Shafts 16, 17, 18, 30 Vibration Isolating Structure 19 Opening 21, 31 Vibration Isolating Rubber Main Body 21a Outer Wall Recesses 22a, 22b Air Chamber 23a , 23b Coil spring 24 Spindle motor 32 Opening 33 Innermost peripheral portion 34 Middle neck portion 35 Outermost peripheral portion 35a Chamfering 36 Fitting concave portion 37 Tray 38 Tray cover 41 Tray integrated boss 42 Mounting screw 43 Lens 44 Actuator 45 Pick cover 46, 47, 48 , 49 Mounting position

Claims (3)

[Claims] 1. An anti-vibration device, which is formed by rotating a rotating body having a substantially H-shaped cross section around a central axis and has a generally donut-shaped shape as a whole, wherein an innermost peripheral portion of the shape is It has a thin-walled cylindrical shape, the middle neck portion has a thick disk shape that extends further from the central portion of the innermost peripheral portion to the outer periphery, and the outermost peripheral portion has a thick cylindrical shape that bulges from the middle neck portion. Further, the outer peripheral surface of the outer peripheral portion is chamfered with ridge lines, and the outer peripheral cylindrical surface of the outermost peripheral portion is formed to have a fitting recess for fitting with a supporting member of the supported means. Anti-vibration device. 2. The anti-vibration device is formed of an anti-vibration elastic member,
2. The resonance frequency of the middle neck portion and the outermost peripheral portion with respect to the innermost peripheral portion is set to 100 Hz in the direction of the central axis and 190 Hz in the direction perpendicular to the central axis, respectively. Anti-vibration device described. 3. A hollow cylindrical portion of the innermost peripheral portion is inserted into a boss provided upright on the first casing, and the first casing is brought into contact with one end of the innermost peripheral portion, the first casing A second casing facing the other casing of the innermost peripheral portion, and the third casing is fitted into a fitting recess provided in the outermost peripheral portion. The anti-vibration device according to claim 1, which supports the anti-vibration device.