JP3245543B2 - Disk unit - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a disk capable of preventing a nut portion of a rack engaged with a feed screw from coming out of a thread groove and preventing vibration of a head during a high-speed access operation, thereby enabling a high-speed and stable access operation. Related to the device.

[0002]

2. Description of the Related Art In recent years, with the increase in the scale of computer programs or data, larger-capacity optical disks have been widely used instead of conventional floppy disks as software recording media or supply media. In order to enhance the usability of the optical disk device, it is required to increase the speed of the operation for accessing data on the disk.
In order to speed up this access operation, it is necessary to move the head to the target position on the disk in a short time,
If the head is suddenly accelerated or decelerated, there arises a problem that the teeth of the rack are disengaged from the thread groove of the feed screw or the head vibrates. In order to increase the speed of the access operation, an access mechanism that can slide stably against sudden acceleration or deceleration of the head is essential.

[0003] First, a problem that occurs when the head is rapidly accelerated or decelerated in the conventional disk device will be described.

Hereinafter, an example of a conventional disk drive will be described with reference to the drawings. FIG. 12 is a perspective view showing a first example of a conventional disk device. In the figure, reference numeral 1 denotes a disk. Reference numeral 2 denotes a head for reading and writing signals from and to the disk 1. Reference numeral 3 denotes a head base on which the head 2 is mounted. Reference numeral 4 denotes a traverse motor that moves the head base 3 in the radial direction of the disk 1. Reference numeral 5 denotes a feed screw which is driven to rotate by the traverse motor 4, and 1
Reference numeral 5 denotes a thread groove formed on the outer periphery of the feed screw 5. Reference numeral 8 denotes a rack for engaging the head base 3 with the feed screw 5, reference numeral 6 denotes a fixing portion to which the head base 3 is fixed, and reference numeral 7 denotes a nut portion that engages with the screw groove 15. 2
Reference numeral 3 denotes a tooth with which the nut portion 7 engages with the thread groove 15. 2
Reference numeral 4 denotes a rack spring that urges the teeth 23 against the screw groove 15.

Reference numeral 11 denotes a guide mechanism for guiding the head base 3 so as to be slidable in the radial direction of the disk 1. 12
Is a guide hole provided in the head base 3, and 9 is a first guide shaft which is fitted in the guide hole 12 and guides the head base 3 slidably in the radial direction of the disk 1. Reference numeral 13 denotes a guide groove provided in the head base 3, and reference numeral 10 denotes a second guide shaft which engages with the guide groove 13 and restricts rotation of the head base 3 around the first guide shaft 9.

FIG. 13 is an enlarged plan view and a side view of the vicinity of the feed screw 5 and the rack 8 in FIG.

Reference numeral 14 denotes a fixed portion 6 and a nut portion 7 of the rack 8.
Are connected to each other. Usually, the thickness of the leaf spring 14 is
When the nut base 7 is made thinner and the movement of the head base 3 is prevented for some reason, the leaf spring 14 bends and the nut part 7 can be detached from the thread groove 15.

In the conventional disk drive having the above structure, when the traverse motor 4 is rotated to rapidly accelerate or decelerate the head base 3, the gap between the nut 7 of the rack 8 and the thread groove 15 of the feed screw 5 is increased. The first problem that the engagement is released occurs, and the force applied to the head base 3 fluctuates when the nut portion 7 is deformed by the force received from the thread groove 15 of the feed screw 5, and as a result, The second problem that the vibration of the head base 3 becomes large occurs.

First, the situation when the first problem occurs will be described with reference to FIG. Inertia acts on the head base 3 in response to rapid acceleration rotation or deceleration rotation of the feed screw 5, so that the movement of the head base 3 follows the change in the rotation of the feed screw 5 with a delay. At this time, from the inclination of the tooth surface of the tooth 23,
The directions of the force applied to the nut portion 7 from the surface of the screw groove 15 are three orthogonal directions: the rotation direction of the feed screw and the radial direction and the tangential direction of the feed screw at the point where the screw groove and the teeth of the rack are in contact. Has all the ingredients. In the conventional rack as shown in FIG. 13, the nut portion 7 is only supported by the leaf spring 14 having low rigidity, so that sufficient rigidity cannot be secured for the force components in these three directions. Therefore, the nut portion 7 is deformed so as to be twisted.

The nut moving position (P2 position) shown in FIG. 13 shows an example of a state in which the nut 7 is deformed, and is rapidly rotated in the R2 direction from the state where the feed screw 5 is stopped. This is the deformation movement position of the nut portion 7 when it is performed.

As described above, in the structure of the conventional rack 8 shown in FIGS. 12 and 13, the rigidity of the leaf spring 14 is insufficient with respect to the force applied from the thread groove 15 to the nut portion 7. However, the first problem that the nut portion 7 is largely twisted and the teeth 23 do not engage with the screw groove 15 when the feed screw is rotated at rapid acceleration or rapid deceleration, and finally the engagement is released.

The rack spring 24 divides the nut 7 into the thread groove 1.
When the force urging the nut 5 is increased to suppress the deformation of the nut portion 7, the friction between the teeth 23 and the screw groove 15 increases,
A new problem occurs in that the load torque of the driving motor increases.

The head base 3 is slidable in the radial direction of the disk 1 with a small force.
A clearance is provided between the motor and the guide mechanism 11. Since the direction of the force applied to the nut portion 7 from the head base 3 and the screw groove 15 has components in all three directions due to the inclination of the surface of the teeth 23 as described above, the head base is suddenly moved. If the head base 3 is slid by acceleration or rapid deceleration, a second problem occurs in that the head base 3 vibrates at the clearance of the guide mechanism 11.

As described above, the conventional first and second problems occur in the conventional general disk device at the time of high-speed access operation. Therefore, several measures for solving this problem have been disclosed. Next, typical ones will be described.

FIG. 14 is a perspective view showing a second example of a conventional disk device which solves the first problem (for example, Japanese Patent Application Laid-Open No. 5-314679). In this conventional example, the same components as those in the first example of the conventional disk device shown in FIGS. 12 and 13 are denoted by the same reference numerals, and description thereof will be omitted. Only different points will be described.

In FIG. 14, reference numeral 16 denotes annular grooves provided at both ends of the feed screw 5. The nut portion 7 is screwed to the feed screw 5 and has high rigidity so that the nut portion 7 is not deformed and unscrewed even when a force is applied from the screw groove 15. At both ends of the feed screw 5, an annular groove 16 is provided on the outer peripheral portion of the feed screw 5. When the nut 7 moves to this position, the nut 7 is easily unscrewed from the feed screw 5, Biting between the nut portion 7 and the thread groove 15 can be avoided. However, in such a structure, there is a possibility that a friction load between the nut portion 7 and the feed screw 5 becomes large due to a variation in processing accuracy or a temperature change, and in that case, a stable access operation cannot be performed. There is a problem.

FIG. 15 is a perspective view showing a third example of a conventional disk device which solves the first problem (for example, Japanese Patent Application Laid-Open No. Hei 5-325439). In this conventional example, the same components as those of the first example of the conventional disk device shown in FIGS. 12 to 14 are denoted by the same reference numerals, and description thereof will be omitted, and only different points will be described.

Reference numeral 17 in FIG. 15 denotes a stopper for limiting the amount of movement of the nut 7 in the direction in which the nut 7 is separated from the feed screw 5. By providing the stopper 17, even if the feed screw 5 rotates with rapid acceleration or rapid deceleration and the nut portion 7 is deformed in a direction to be separated from the screw groove 15, it is possible to prevent the nut portion 7 from being completely separated. It is effective for the above problem. However, the nut portion 7 is deformed in the movable range by the force received from the thread groove 15, so that the force applied to the head base 3 is changed by the deformation of the nut portion 7. Since the force applied to the head changes in this way, the head base 3 is vibrated, and no effect can be expected with respect to the second problem of vibration of the head base 3.

FIG. 16 is a perspective view showing a third example of a conventional disk device for solving the second problem (for example, Japanese Patent Application Laid-Open No. Hei 8-279257). In this conventional example, the same components as those of the example of the conventional disk drive shown in FIGS. 12 to 15 are denoted by the same reference numerals, and description thereof will be omitted. Only different points will be described.

In FIG. 16, reference numeral 18 denotes a guide bearing provided on the head base 3 and having a hole. The second guide shaft 10 is fitted into the hole of the guide bearing 18, and The rotation around the first guide shaft 9 is restricted. 19 is a bearing spring for urging the guide bearing 18 against the second guide shaft 10 in a direction parallel to the disk. The guide spring 18 is formed by the bearing spring 19.
The clearance between the head base 3 and the second guide shaft 10 is removed, and the vibration of the head base 3 during high-speed access can be reduced. However, the clearance can be reduced by the bearing spring 19 only in the direction parallel to the disk 1 and perpendicular to the moving direction of the head base 3, and the head base 3 has no effect on vibration perpendicular to the surface of the disk 1. small. In order to ensure the effect of suppressing the vibration of the head base by this configuration, the applied pressure of the bearing spring 19 must be increased, and the friction load between the second guide shaft 10 and the guide bearing 18 increases. In addition, there is a problem that the traverse motor 4 needs to be capable of generating a larger torque.

[0021]

In the above-described structure of the conventional disk drive, the nut portion of the rack is prevented from being detached from the thread groove of the feed screw, and further, when the head base is accelerated and decelerated. It is difficult to suppress the vibration of. Even if these problems can be prevented, the frictional load for sliding the head base on the guide mechanism increases, and it is difficult to perform stable and high-speed access.

The present invention has been made in view of such circumstances, and an object of the present invention is to increase the frictional load when the head berth slides without increasing the thread groove of the rack in the high-speed traverse operation. An object of the present invention is to provide a disk device capable of performing stable traversing operation at a high speed by suppressing detachment of the disk and vibration of a head base.

[0023]

According to the present invention, there is provided a disk drive comprising: a head for reading / writing signals from / to a disk; a head base on which the head is mounted; and a traverse motor for moving the head in a radial direction of the disk. When,
A feed screw rotatably driven by the traverse motor and having a screw groove on an outer periphery, a rack having a fixing portion fixed to the head base and a nut portion engaging with the screw groove; the a guide mechanism that movably guided in a radial direction of the disk, and the fixed part of the rack and the nut portion are connected with the feed displaceable cantilever parallel springs in the radial direction of the screw , Said na
Free end of the cantilever parallel spring provided with a slot
However, it is characterized in that it extends in the rotation axis direction of the feed screw .

Therefore, according to the present invention, even when the head is moved by rapid acceleration or rapid deceleration, the nut portion of the rack can be prevented from coming off from the feed screw, and a disk device capable of moving the head at high speed can be provided. Can be realized.

[0025]

Further, according to the present invention, the sliding direction of the head coincides with the buckling direction of the plate spring, since the leaf spring that has high stiffness in the buckling direction, rack sliding head High rigidity can be ensured in the moving direction, and a disk device capable of moving the head at high speed can be realized.

The disk device according to the present invention is characterized in that it has a stopper for limiting the amount of movement of the nut portion of the rack in the movable direction.

Therefore, according to the present invention, the nut can be reliably prevented from coming off the feed screw.

The disk device according to the present invention is characterized in that the cantilevered parallel spring provided on the rack is composed of at least two leaf springs, and the gap between the leaf springs is filled with a viscous material.

Therefore, according to the present invention, the nut portion can be prevented from vibrating, and the force applied from the feed screw to the nut portion can be vibrated to prevent the head from vibrating.

[0031]

[0032]

[0033]

The disk device according to the present invention is characterized in that the fixed portion of the rack, the nut portion, and the cantilevered parallel spring are integrally formed of resin.

Therefore, according to the present invention, the cost for manufacturing the rack can be kept small, and a disk device capable of moving the head at high speed can be realized at low cost.

[0036]

[0037]

A disk drive according to the present invention comprises a head for reading and writing signals from and to a disk, a head base on which the head is mounted, a traverse motor for moving the head in a radial direction of the disk, and a traverse motor. A feed screw that is driven to rotate and has a thread groove on the outer periphery, a fixed part fixed to the head base, a nut part engaged with the screw groove, and a cantilevered parallel spring connecting the fixed part and the nut part; A first rack that fits into a guide hole provided in the head base and guides the head base slidably in a radial direction of the disk;
And a second guide shaft which engages with a guide groove provided in the head base to regulate rotation of the head base around the first guide shaft, and one end of which is fixed to the head base. A direction in which the other end is pressed against the second guide shaft at a position separated from the guide groove by one in the axial direction of the second guide shaft, and the inner surface of the guide groove comes into contact with the second guide shaft. A shaft retainer for biasing the head base, wherein the cantilevered parallel spring is disposed in a radial direction of the feed screw.
And the nut portion is provided.
The free end of the cantilevered parallel spring moves in the direction of the rotation axis of the feed screw.
It is extended, and has a characteristic that the direction in which the cantilever parallel spring can be displaced and the direction in which the shaft retainer is pressed against the second guide shaft are orthogonal to each other.

Therefore, according to the present invention, the nut portion of the rack does not come off from the feed screw, and the force applied to the head base from the nut portion is suppressed in all directions by the cantilevered parallel spring and the shaft retainer of the rack. Therefore, even if the head base is moved at a rapid acceleration or a rapid deceleration, the vibration of the head base can be suppressed, and a disk device capable of moving the head at high speed can be realized.

[0040]

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

(Embodiment 1) In this embodiment,
The same components as those of the conventional disk device shown in FIGS. 12 to 16 are denoted by the same reference numerals, and description thereof will be omitted. Only differences from the conventional disk device will be described.

FIG. 1 is a perspective view of a disk device according to the first embodiment. Reference numeral 21 denotes a cantilevered parallel spring that connects the fixed portion 6 and the nut portion 7 of the rack 8. (Fig. 2)
It is the top view and side view which expanded the vicinity of the rack 8 and the feed screw 5 of (FIG. 1). As shown in the first embodiment, by connecting the fixed portion 6 of the rack 8 and the nut portion 7 with the cantilevered parallel spring 21, the nut portion 7 receives the force applied from the thread groove 15 to the nut portion 7. High rigidity is achieved in the tangential direction of the feed screw 5 at the point where the screw groove 15 and the teeth 23 come into contact, and in the direction of the rotation axis of the feed screw 5. Further, in the radial direction of the feed screw 5 at the point where the screw groove 15 and the teeth 23 come into contact, the nut portion 7 moves in parallel while being engaged with the feed screw 5 without being twisted. A position P1 in FIG. 2 indicates a position where the nut portion 7 has moved in parallel when the feed screw 5 is rapidly accelerated and rotated in the R1 direction from a stopped state.

As described above, since the nut portion of the first embodiment has high rigidity against torsion, the amount of deformation of the nut portion 7 is smaller than that of the rack 8 shown in the first example of the conventional disk device, and 23 is not easily detached from the screw groove 15. Nevertheless, when the movement of the head base 3 is prevented, the nut part is disengaged from the thread groove, and the teeth 23 are disengaged from the thread groove 15.
The teeth 23 can be prevented from being damaged by biting into the teeth. In addition, the nut 7 moves in parallel with the posture in which it engages with the feed screw 15, and the engagement between the screw groove 15 and the teeth 23 does not change suddenly. The size and direction of do not change abruptly. Therefore, the head base 3 does not vibrate significantly.

The rear of the nut 7 may be urged toward the feed screw 5 using an elastic material (not shown) such as a coil spring, and the nut 7 may be pressed against the feed screw 5. Even in this case, the engagement of the nut portion 7 can be ensured even if the urging force by the elastic body is weak, and a sufficient effect can be obtained with the weak urging force. Can be prevented from increasing.

(Embodiment 2) (FIG. 3) shows Embodiment 2
FIG. The free end of the cantilevered parallel spring 21 connecting the fixed portion and the nut portion of the rack 8 extends in the rotation axis direction of the feed screw 5. With such a configuration, the sliding direction of the head base 3 and the cantilever parallel spring 2
1 buckling directions are matched. Generally, the buckling direction of the plate is high in rigidity, so that the rigidity of the rack 8 in the sliding direction of the head base 3 can be increased. As a result, it is possible to further suppress the deformation of the nut portion 7 in response to sudden acceleration or sudden deceleration of the feed screw 15.

(Embodiment 3) (FIG. 4) shows Embodiment 3
FIG. A stopper 12 is provided for limiting the amount of movement of the nut 8 in the movable direction. As shown in the nut moving position (P1 position) in FIG. 2, the movement of the nut 7 at the time of rapid acceleration or rapid deceleration is limited to the direction perpendicular to the rotation axis of the feed screw. The detachment from the thread groove 15 can be easily prevented without suppressing the back of the nut portion 7.

(Embodiment 4) (FIG. 5) shows Embodiment 4.
FIG. Reference numeral 22 denotes a viscous material filled in the gap of the cantilevered parallel spring. With such a configuration, by providing the cantilevered parallel spring 21 with damping characteristics, it is possible to suppress the nut portion 7 from vibrating in the radial direction of the feed screw 15. As a result, the nut 7
And the feed screw 5 can be improved in adhesion, and vibration of the head base 3 can be prevented.

(Embodiment 5) (FIG. 6) shows Embodiment 5.
FIG.

According to the present invention, the entire structure is made of a resin material including the fixing portion 6, the nut portion 7, the cantilevered parallel spring 21 and the stopper 17 so that they can be integrally molded, thereby reducing the manufacturing cost. Things. In this case,
The shape of the hole of the gap of the cantilevered parallel spring 21 does not necessarily need to be rectangular, and the same effect can be obtained even if the shape of the square such as an ellipse is rounded.

(Embodiment 6) Embodiment 6 shown in FIG. 7 shows the dimensional relationship of each part in Embodiment 2 (FIG. 3). F indicates a force applied from the thread groove 15 in the movable direction of the cantilevered parallel spring 21. L1 is the length of the cantilevered parallel spring 21, L2 is the length of the cantilevered parallel spring 21
, The distance from the free end to the contact position between the nut portion 7 and the screw groove 15, D is the gap distance between the two leaf springs constituting the cantilevered parallel spring 21, and t is the plate constituting the cantilevered parallel spring 21 Spring thickness. b is the width of the leaf spring of the cantilevered parallel spring 21.

Strictly speaking, the deformation of the cantilever parallel spring 21 when a force is applied to the nut portion 7 includes both a component of "displacement due to parallel movement" and a component of "displacement due to bending". I have. The ratio of the component of “displacement due to bending” to the component of “displacement due to translation” is expressed by (Equation 2).

The derivation of this equation will be described. Appendix 8.7 of “Continuation / Actual Design Nikkan Kogyo Shimbun, edited by Yotaro Hatamura” describes the ratio of the “displacement due to bending” and “displacement due to translation” of the cantilevered parallel spring structure. As an expression to represent

[0053]

(Equation 3)

The following equation is shown. In this (Equation 3),
The component of “displacement due to bending” is

[0055]

(Equation 4)

And “displacement due to translation”.
The components of

[0057]

(Equation 5)

Is calculated as determined by In (Expression 3) and (Expression 4), F is the magnitude of the force applied to the nut portion 7 from the screw groove 15. E represents the longitudinal elastic modulus of the material of the cantilevered parallel spring 21. In (Equation 4), the thickness t of the leaf spring is treated as being extremely thin. However, in practice, as shown in the fifth embodiment, when molding the entire rack 8 with resin, the thickness t of the leaf spring must have a certain thickness in order to secure rigidity. It cannot be ignored. With this in mind,
Strictly, the component of "displacement due to bending" was calculated.

[0059]

(Equation 6)

(Equation 2) is equivalent to (Equation 5) and (Equation 6)
Is derived using. "Displacement due to translation"
If the ratio of the component of “displacement due to bending” to the component is large, the effect of providing the cantilevered parallel spring 21 decreases,
Only the same characteristics as those provided with the conventional leaf spring 14 can be obtained. More specifically, the teeth 23 easily come off from the thread groove 15, and in particular, in the configuration of the second embodiment, among the teeth of the nut portion 7 that engage with the feed groove 15, the teeth 23 are close to the cantilever parallel spring 21. Only the one rubs against the feed groove 15 and wears the teeth, shortening the life of the rack 8. In order to avoid such a problem, it is necessary that the magnitude of the component of “displacement due to bending” is at least smaller than “displacement due to translation”. This shows conditions under which the ratio of “displacement due to bending” becomes 1.0 or less. As a matter of course, the magnitude of the “displacement due to bending” should be smaller as compared to the “displacement due to parallel movement”. To 0.1 or less.

In this embodiment, the dimension of L2 is
The length from the free end of the cantilevered parallel spring to the position where the teeth of the nut 7 remote from the cantilevered spring contact the thread groove 15. As is clear from (Equation 2), the ratio of “displacement due to bending” increases as L2 increases. Therefore, the ratio is determined assuming the worst state of L2. Further, in the present embodiment, the dimensional relationship in the second embodiment is shown, but the same applies to other embodiments.

(Embodiment 7) (FIG. 8) shows Embodiment 7
FIG.

Reference numeral 20 denotes one end fixed to the head base 3 and the other end extending from the guide groove 13 to the second guide shaft 10.
The shaft presser presses against the second guide shaft 10 at a position separated from the second guide shaft 10 in one of the axial directions.

By providing such a shaft retainer 20, a force that twists around the guide groove 13 acts on the head base 3 to incline the head base 3 so that the guide hole 12 and the first guide shaft 9 are formed. Or the clearance between the guide groove 13 and the second guide shaft 10 can be eliminated.

As a result, vibrations generated in the head base 3 when the head base 3 moves with rapid acceleration or rapid deceleration can be suppressed.

When the shaft holder 20 is provided, the contact state between the head base 3 and the guide mechanism 11 depends on the positional relationship between the guide hole 12 and the guide groove 13, the hole diameter of the guide hole 12 and the first guide shaft 9 It varies depending on the relationship between the diameter, the gap between the guide grooves 13 and the shaft diameter of the guide shaft 10, or the relationship between the weight of the head 2 and the head base and the position of the center of gravity. (FIG. 9) and (FIG. 10)
An example of a contact state between the head base 3 and the guide mechanism 11 when the shaft retainer 20 is provided is shown. (FIG. 9) is a cross-sectional view of the head base 3 when the head base 3 is viewed from the direction of the guide groove 13. The first guide shaft 9 and the guide hole 12 are inclined and come into contact with each other, and the clearance is suppressed. I have. FIG. 10 is a side view of the head base 3 when the head base 3 is viewed from the direction of the guide groove 13, and shows the second guide shaft 10 and the guide groove 13.
Are inclined and contact with each other, and the clearance is suppressed.

The shaft presser does not incline the head base 13 only by the force of pressing the second guide shaft 10 but presses the position away from the head base 13 in one direction of the second guide shaft 10. The pressure contact generates a rotational moment around the guide groove 13, and the rotational moment tilts the head base 13. Therefore, the guide groove 13 and the shaft retainer 20
As the position where the second guide shaft 10 is pressed against the guide groove 13 is farther away, the head base 3 can be pressed against the guide mechanism 11 with a smaller pressing force. In the seventh embodiment (FIG. 8), the shaft retainer 20 is realized by a leaf spring, but the same effect can be obtained by using another elastic material such as a coil spring.

(Eighth Embodiment) (FIG. 11) is a perspective view showing an eighth embodiment. Cantilever parallel spring 2 of rack 8
1 is arranged so that the direction of movement thereof is horizontal to the disk 1 and in the direction of the radius of the feed screw 5, while the shaft retainer 20
Is the second guide shaft 1 in a direction perpendicular to the disc 1.
0 is pressed. In this manner, by making the movable direction of the cantilever parallel spring 21 of the rack 8 and the pressing direction of the shaft retainer 20 perpendicular, the clearance between the head base 3 and the guide mechanism 11 can be suppressed in all directions.
Even if the head base 3 is moved with rapid acceleration or rapid deceleration, the vibration generated in the head base 3 can be reduced, and a stable disk device can be realized. The direction of movement of the cantilevered parallel spring 21 of the rack 8 is perpendicular to the disk 1 and the radial direction of the feed screw 5 is different from that of the embodiment shown in FIG. Similar effects can be obtained even when the pressing direction of the presser 20 is set to a direction parallel to the disk 1 or the like.

[0069]

As described above, by adopting the structure of the present invention, even when the head base is rapidly accelerated or decelerated, the engagement between the nut portion of the rack and the feed screw does not come off, and the head base is not disengaged. Vibration can also be reduced. Further, since the increase in the sliding load between the nut portion and the feed screw and between the head base and the guide shaft is small, it is not necessary to increase the torque of the traverse motor.

According to the present invention, the head base can be moved at high speed without increasing the cost as described above.
Since a stable high-speed accessible disk device can be realized, it is extremely effective in industry.

[Brief description of the drawings]

FIG. 1 is a perspective view of a disk device according to a first embodiment of the present invention.

FIG. 2A is an enlarged side view of a feed screw and a rack part according to the first embodiment of the present invention. FIG. 2B is an enlarged plan view of a feed screw and a rack part of the first embodiment of the present invention.

FIG. 3 is a perspective view of a part of a feed screw and a rack according to a second embodiment of the present invention.

FIG. 4 is a perspective view of a part of a feed screw and a rack according to a third embodiment of the present invention.

FIG. 5 is a perspective view of a part of a feed screw and a rack according to a fourth embodiment of the present invention.

FIG. 6 is a perspective view of a part of a feed screw and a rack according to a fifth embodiment of the present invention.

FIG. 7 is a diagram showing a dimensional relationship between a cantilever parallel spring and a nut portion of a rack according to a sixth embodiment of the present invention.

FIG. 8 is a perspective view of a disk device according to a seventh embodiment of the present invention.

FIG. 9 is a sectional side view showing a contact state between a head base and a guide mechanism according to a seventh embodiment of the present invention.

FIG. 10 is a side view showing a contact state between a head base and a guide mechanism according to a seventh embodiment of the present invention.

FIG. 11 is a perspective view of a disk device according to an eighth embodiment of the present invention.

FIG. 12 is a perspective view of Example 1 of a conventional disk device.

13A is an enlarged side view of a portion of a feed screw and a rack of Example 1 of a conventional disk device. FIG. 13B is an enlarged plan view of a portion of a feed screw and a rack of Example 1 of a conventional disk device.

FIG. 14 is a perspective view of a second example of a conventional disk drive.

FIG. 15 is a perspective view of Example 3 of a conventional disk device.

FIG. 16 is a perspective view of Example 4 of a conventional disk device.

[Explanation of symbols]

 Reference Signs List 1 disc 2 head 3 head base 4 traverse motor 5 feed screw 6 fixing part 7 nut part 8 rack 9 first guide shaft 10 second guide shaft 11 guide mechanism 12 guide hole 13 guide groove 14 leaf spring 15 screw groove 16 annular Groove 17 Stopper 18 Guide bearing 19 Bearing spring 20 Shaft retainer 21 Cantilever parallel spring 22 Viscous material 23 Teeth 24 Rack spring R1 Rotation direction of feed screw R2 Rotation direction of feed screw P1 Nut moving position P2 Nut moving position

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Kiyoshi Masaki 1006 Kadoma Kadoma, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Inventor Masaharu Imura 1006 Kadoma, Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Inventor Tsutomu Kai 1006 Odaka, Kazuma, Kadoma, Osaka Pref. JP-A-8-249838 (JP, A) JP-A 63-62969 (JP, U) JP-A 1-81763 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) G11B 21/02

Claims (5)

(57) [Claims] 1. A head for reading and writing signals from / to a disk, a head base on which the head is mounted, a traverse motor for moving the head in a radial direction of the disk, and a traverse motor driven to rotate by the traverse motor. A rack having a feed screw having a screw groove, a fixing portion fixed to the head base, and a nut portion engaging with the screw groove, and a guide mechanism for guiding the head base so as to be movable in a radial direction of the disk. Wherein the fixed portion and the nut portion of the rack are connected by a cantilever parallel spring displaceable in a radial direction of the feed screw .
The cantilevered parallel spring provided with the nut portion
Of the feed screw extends in the direction of the rotation axis of the feed screw.
Disk and wherein the door. 2. The disk device according to claim 1, further comprising a stopper for limiting a movement amount of the nut portion in a movable direction. 3. The disk drive according to claim 1, wherein said cantilevered parallel spring comprises at least two leaf springs, and a gap between said leaf springs is filled with a viscous material. 4. The disk device according to claim 1, wherein the fixed portion, the nut portion, and the cantilevered parallel spring of the rack are integrally formed of resin. 5. A head for reading and writing signals to and from a disk, a head base on which the head is mounted, a traverse motor for moving the head in a radial direction of the disk, and a rotary drive by the traverse motor. Yes a feed screw having a screw groove, a nut portion engaged with the screw groove and the fixing portion fixed to the head base
And, the fixed portion and a rack having a cantilevered parallel springs for connecting the nut portion engaged with the guide hole formed in the head base, slidably the head base in the radial direction of said disk A first guide shaft for guiding the first base shaft and a guide groove provided in the head base;
A second guide shaft that restricts rotation of the head base around the first guide shaft, one end of which is fixed to the head base, and the other end of which extends from the guide groove in an axial direction of the second guide shaft; A shaft presser which presses the head base in a direction in which the inner surface of the guide groove comes into contact with the second guide shaft, the shaft press being pressed against the second guide shaft at a position separated from one side; Spring can be displaced in the radial direction of the lead screw
The cantilever flat provided with the nut portion
The free end of the row spring extends in the rotation axis direction of the feed screw.
Ri, a disk device, characterized in that the direction that presses the second guide shaft of the shaft retainer and displaceable direction of the cantilever parallel springs are orthogonal.