JP2009277327A - Disk conveying mechanism of disk device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a disk conveying mechanism wherein even when there is a difference in press-fitting force or friction force between an inserting/ejecting roller and a disk, no slippage occurs between the roller and the disk, and the surface of the disk is not damaged. <P>SOLUTION: In the disk conveying device 11 having two rollers arranged on a roller shaft with small-diameter parts set to face each other, the roller shaft is divided into two: a roller shaft 1R and a roller shaft 1L, a distant one and a near one from/to the ring gear 2 respectively, a roller 3R is attached to the roller shaft 1R, and a roller 3L is attached to the roller shaft 1L. The roller shaft 1R penetrates the roller shaft 1L to project to the outside the rear gear 2, and a differential gear unit 20 is attached between the roller shaft 1L and the roller shaft 1R. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a disk transport mechanism of a disk device, and more particularly to a disk transport mechanism that uses a roller for carrying a disk into and out of the disk device.

  Conventionally, in an optical disc apparatus that uses a disc medium such as a compact disc (CD), a digital versatile disc (DVD), a high-definition digital versatile disc (HDDVD), a Blu-ray disc (BD), etc., the disc medium In order to carry the disk into the apparatus or eject the disk medium from the apparatus, a disk transport mechanism using rollers is provided in the apparatus. Such a disk transport mechanism is disclosed in Patent Document 1, for example.

  In the disc transport mechanism disclosed in Patent Document 1, a disc feed roller shaft is rotatably supported by a roller lever that is rotatably supported by a main chassis, and a disc feed roller is attached to the roller shaft. The disk feed roller is composed of two frustoconical rollers, the two rollers are arranged with their top surfaces facing each other, and the roller shaft passes through the central axis. The roller is generally made of a flexible material such as rubber.

  The operation of such a conventional disk transport mechanism will be described with reference to FIG. FIG. 1A shows a configuration of a roller portion of a conventional disk transport mechanism 10. A conventional disk transport mechanism 10 includes a roller shaft 1, a ring gear 2 fixed to one end of the roller shaft 1, two insertion / discharge rollers 3L and 3R attached to the left and right of the roller shaft 1, and a ring gear 2, respectively. Is provided with a transmission gear 4 for transmitting power. The insertion / discharge rollers 3L and 3R are made of an elastic member such as rubber, and have a truncated cone shape whose diameter increases from the central portion of the roller shaft 1 toward the outside. In general, the insertion / discharge rollers 3L and 3R have a symmetrical shape, and the absolute value of the inclination of the tapered surface is the same. With this shape, centering is performed by the insertion / discharge rollers 3L, 3R to bring the disc edge toward the center of the insertion / discharge rollers 3L, 3R.

  In addition, an upper guide 5 as shown in (b) is provided above the two insertion / discharge rollers 3L and 3R of the conventional disk transport mechanism 10. The upper guide 5 guides a disk that is inserted into the disk device or is ejected from the disk device and passes through the disk transport mechanism 10. In order to easily guide the disk, a projection 5A for guiding the disk to the insertion / discharge rollers 3L, 3R may be provided on the surface of the upper guide 5 facing the insertion / discharge rollers 3L, 3R.

  When the disk 6 is inserted into the disk transport mechanism 10, the disk 6 is guided to the insertion / discharge rollers 3 </ b> L and 3 </ b> R by the protrusion 5 </ b> A of the upper guide 5. When the transmission gear 4 rotates and the rotational torque is transmitted to the ring gear 2, the roller shaft 1 that is integral with the ring gear 2 rotates. The insertion / discharge rollers 3L, 3R rotate together with the roller shaft 1, and the disk 6 is carried by the insertion / discharge rollers 3L, 3R. Since the upper guide 5 is fixed, in this state, as shown in (d) and (e), the disk 6 is pressed against the upper guide 5 by the pressing force F by the insertion / discharge rollers 3L and 3R.

  The rotational torque of the insertion / ejection rollers 3L and 3R is transmitted to the disk 6 by friction mainly at two locations near the edge of the disk 6. Further, between the disk 6 and the upper guide 5, a resistance R due to sliding contact acts in a direction opposite to the aforementioned rotational torque. As a result, the driving force T acts on the disk 6, and the disk 6 moves in the direction of the white arrow P and is inserted into a disk device (not shown).

  At this time, if there is no slip between the insertion / discharge rollers 3L, 3R and the disk 6, the rotation amount of the insertion / discharge rollers 3L, 3R (contact with the disk 6) as shown in FIG. Since the movement distances G and H at the point and the left and right movements M and N of the disk 6 are equal, the disk 6 is conveyed in the direction J perpendicular to the roller shaft 1.

JP 2001-338456 A (FIGS. 1, 4 and 6)

However, in the conventional disk transport mechanism 10, slip may occur between the insertion / discharge rollers 3 </ b> L, 3 </ b> R and the disk 6 due to a difference in transmission torque from the insertion / discharge rollers 3 </ b> L, 3 </ b> R. Here, for example, a case where a slip occurs between the insertion / discharge roller 3L and the disk 6 and no slip occurs between the insertion / discharge roller 3R and the disk 6 is considered. In this case, a relationship of G = H and M <N is established between the rotation amounts G and H of the insertion / discharge rollers 3L and 3R and the left and right movement amounts M and N of the disk 6. As a result, on the discharge roller 3L side, the amount of movement of the disk 6 is reduced with respect to the rotation of the discharge roller 3L, and the surface of the disk 6 is scratched. There was a problem that it was transported.
Therefore, the present invention does not cause slip between the insertion / ejection roller and the disk even if the pressure and friction between the insertion / ejection roller and the disk are not uniform, and the surface of the disk is damaged. It is an object of the present invention to provide a disc transport mechanism that can be avoided.

  A first aspect of the disk transport mechanism of the present invention that achieves the above object is a disk transport mechanism for carrying a disk medium in a disk device into or discharging a disk medium from the device. 1 roller, a first roller shaft to which the first roller is fixed, a second roller, and a second roller shaft to which the second roller is fixed. A differential gear unit is provided between the first roller shaft and the second roller shaft. The differential gear unit is driven by the driving force from the transmission gear. A ring gear for driving the unit is rotatably attached to the second roller shaft.

  A second aspect of the disk transport mechanism of the present invention that achieves the above object is a disk transport mechanism for carrying a disk medium in a disk apparatus into the apparatus or discharging a disk medium from the apparatus. A cylindrical first roller fixed to the distal end side of the first roller shaft, and a cylindrical first roller fixed to a second roller shaft through which the base side of the first roller shaft passes rotatably. 2 rollers, a differential gear unit provided between the first roller shaft and the second roller shaft, and a second roller shaft rotatably mounted on the second roller shaft. And a ring gear for driving the gear unit.

  According to the present invention, even when the pressure and friction between the insertion / discharge roller and the disk are not uniform, the drive shaft of the insertion / discharge roller is divided and the differential mechanism is provided between the two drive shafts. As a result, no slip occurs between the insertion / ejection roller and the disk, and the surface of the disk can be prevented from being damaged.

  Hereinafter, embodiments of the present invention will be described in detail based on specific examples with reference to the accompanying drawings. The members used in the conventional disk transport mechanism 10 described with reference to FIGS. 1 and 2 and the members that are continuously used in the disk transport mechanism 11 of the present invention are given the same reference numerals as in the past. explain.

  FIG. 3A shows the configuration of the roller portion of the disk transport mechanism 11 according to an embodiment of the present invention. The disk transport mechanism 11 of this embodiment includes a roller shaft 1, a ring gear 2 fixed to one end of the roller shaft 1, two insertion / discharge rollers 3L and 3R respectively attached to the left and right of the roller shaft 1, and a ring gear. 2 and a differential gear unit 20 provided on the side of the ring gear 2 opposite to the insertion / discharge roller 3L. The insertion / discharge rollers 3L and 3R are made of an elastic member such as rubber, as in the prior art, and have a truncated cone shape whose diameter increases from the center of the roller shaft 1 toward the outside. The insertion / discharge rollers 3L and 3R may have a symmetrical shape, and the absolute value of the inclination of the tapered surface is the same.

  In FIG. 3B, the disk 6 passes between the upper guide 5 and the insertion / discharge rollers 3L, 3R provided above the two insertion / discharge rollers 3L, 3R of the disk transport mechanism 11 of this embodiment. It shows the state. The structure of the upper guide 5 is the same as that of the prior art. In order to guide the disk 6 inserted into the disk device or ejected from the disk device and passing through the disk transport mechanism 11, in this embodiment, the upper guide 5 On the surface facing the insertion / discharge rollers 3L, 3R, a protrusion 5A for guiding the disk to the insertion / discharge rollers 3L, 3R is provided. There may be no protrusion 5A.

  Here, the overall configuration of the disk transport mechanism 11 of this embodiment will be described first with reference to FIG. 4A, and then the differential gear of this embodiment will be described with reference to FIGS. 3C to 3E. The configuration of the unit 20 will be described. 4A shows the entire cross section of the disk transport mechanism 11, FIG. 3C shows an enlarged view of the differential gear unit 20, and FIG. 4D shows the differential gear unit 20. (E) shows the differential gear unit 20 with the differential gear case 25 removed.

  As shown in FIG. 4A, in the disk transport mechanism 11 of this embodiment, the roller shaft 1 is divided into two parts, a roller shaft 1L closer to the ring gear 2 and a roller shaft 1R farther from the ring gear 2. The roller shaft 1L has a hollow structure and includes a through hole 1h. The roller shaft 1R has a portion having the same diameter as that of the roller shaft 1L and a small diameter portion 1r. The small diameter portion 1r passes through the through hole 1h of the roller shaft 1L so as to be rotatable, so that the roller shaft 1L It protrudes from the end on the ring gear 2 side. A roller 3R is fixed to the roller shaft 1R, and a roller 3L is fixed to the roller shaft 1L. A differential gear unit 20 is provided between the roller shaft 1L on the side of the ring gear 2 and the roller shaft 1r. 4 is a transmission gear.

  The differential gear unit 20 is composed of first to fourth four bevel gears 21 to 24 and a differential gear case 25, as shown in detail in FIGS. 3 (c) to 3 (e). . The differential gear case 25 is fixed to the ring gear 2 that is rotatably attached to the roller shaft 1L. In the differential gear case 25, the first bevel gear 21 is fixed to the first roller shaft 1r, and the second The bevel gear 2 is fixed to the second roller shaft 1L. Rotating shafts 26 and 27 protrude from opposing positions in the differential gear case 25, and the third and fourth bevel gears 23 and 24 are rotatably attached to the rotating shafts 26 and 27, respectively. The first and second bevel gears 21 and 22 are engaged with each other. The end portion of the first roller shaft 1r is rotatably supported by the differential gear case 25.

  Here, the operation of the differential gear unit 20 configured as described above will be described with reference to FIG. When the rotational torque from the transmission gear 4 is transmitted to the ring gear 2 as indicated by the black arrow, the differential gear case 25 fixed integrally with the ring gear 2 rotates relative to the roller shaft 1L and the roller shaft 1R. Due to the rotation of the differential gear case 25, the third bevel gear 23 and the fourth bevel gear 24 facing each other rotate (revolve) with respect to the roller shaft 1L and the roller shaft 1R.

  By the revolution of the third bevel gear 23 and the fourth bevel gear 24, the first bevel gear 21 and the second bevel gear 22 meshing with each other rotate, and the roller shaft 1L and the roller shaft 1R rotate. The flow of force transmitted from the third bevel gear 23 and the fourth bevel gear 24 to the roller shaft 1L is indicated by an arrow with a halftone dot, and the third bevel gear 23 and the fourth bevel gear 24 move to the roller shaft 1r (1R). The transmitted force flow is indicated by hatched arrows. As a result, the insertion / discharge rollers 3L, 3R fixed to the roller shaft 1L and the roller shaft 1R rotate, so that a driving force is applied to the disk 6 inserted between the upper guide 5 and the insertion / discharge rollers 3L, 3R. Communicated.

  If the crimping force and resistance between the two insertion / discharge rollers 3L, 3R and the disk 6 are the same and there is no slip, the insertion / discharge rollers 3L, 3R of the insertion / discharge rollers 3L, 3R, as shown in FIG. Since the rotation amounts (movement distances at the contact point with the disk 6) G and H and the left and right movement amounts M and N of the disk 6 are equal, the disk 6 is conveyed in the direction J perpendicular to the roller shaft 1. At this time, since the rotation amounts of the roller shaft 1L and the roller shaft 1R are the same, the third bevel gear 23 and the fourth bevel gear 24 only revolve and do not rotate.

  On the other hand, when the crimping force and resistance differ between the two insertion / discharge rollers 3L, 3R and the disk 6, for example, the driving force from the insertion / discharge roller 3R to the disk 6 is greater than the insertion / discharge roller 3L. When the driving force is larger than the driving force from the disk 6 to the disk 6, the rotation amounts of the insertion / discharge rollers 3L, 3R are not the same, and the insertion / discharge roller 3R tends to rotate more than the insertion / discharge roller 3L. No slip occurs between the insertion / discharge roller 3R and the disk 6, and the rotation amount of the insertion / discharge roller 3R and the movement amount of the disk 6 are equal.

  In the conventional structure, since the insertion / discharge roller 3L and the insertion / discharge roller 3R are integrated at this time, the rotation amount is equal, and as described with reference to FIG. A slip occurs between 6. However, in the structure of this embodiment, the differential gear unit 20 is installed between the insertion / discharge roller 3L and the insertion / discharge roller 3R, and the third bevel gear 23 and the fourth bevel gear 24 are revolved. Not only does it rotate, it can rotate. By this action, the insertion / discharge roller 3L can be rotated less than the insertion / discharge roller 3R. That is, the differential gear unit 20 can absorb the rotational difference between the insertion / discharge rollers 3L and 3R (rotational difference between the roller shafts 1L and 1R). This will be described with reference to FIGS.

  A slip may occur between the insertion / discharge rollers 3L, 3R and the disk 6 due to a difference in transmission torque from the insertion / discharge rollers 3L, 3R. Here, for example, a case where a slip occurs between the insertion / discharge roller 3L and the disk 6 and no slip occurs between the insertion / discharge roller 3R and the disk 6 is considered. In this case, a relationship of M <N is established between the left and right movement amounts M and N of the disk 6. In addition, the conventional relationship between M <G and N = H between the movement amounts M and N of the right and left of the disk 6 and the rotation amounts G and H of the insertion / ejection rollers 3L and 3R is as follows. In the example, due to the action of the differential gear unit 20, the relationship of M = G (<H) and N = H is established as shown in FIGS. 5 (a), (c), and (d).

  At this time, as shown in FIG. 5B, the bevel gear fixed to the roller shaft 1L of the insertion / discharge roller 3L is larger than the rotation amount X of the bevel gear 21 fixed to the roller shaft 1r of the insertion / discharge roller 3R. The rotation amount Y of 22 is small. In order to absorb this rotation difference, the third bevel gear 23 rotates in the arrow V direction, and the fourth bevel gear 24 rotates in the arrow W direction. As a result, no slip occurs between the insertion / discharge roller 3L and the disk 6, and the driving force from the insertion / discharge roller 3L to the disk 6 is transmitted without loss. In the disk 6, rotational motion may occur due to the difference in the amount of movement on the left and right sides of the disk.

  As described above, according to the disk transport mechanism 20 having the above-described configuration, even when the pressing force and friction between the insertion / discharge rollers 3L, 3R and the disk 6 are not uniform, the insertion / discharge rollers 3L, 3R and the disk are not uniform. No slip occurs between the disk 6 and the surface of the disk. For this reason, it is possible to make the shape of the insertion / discharge rollers 3L, 3R into a columnar shape instead of a truncated cone shape.

  FIGS. 6A and 6B show the configuration of the disk transport mechanism 12 according to another embodiment of the present invention. This embodiment differs from the disk transport mechanism 11 of the embodiment described with reference to FIGS. 3 to 5 only in the shape of the insertion / ejection rollers 3LA and 3RA. Therefore, the same components as those of the disk transport mechanism 11 of the embodiment described with reference to FIGS.

  In this embodiment, the insertion / discharge rollers 3LA, 3RA are cylindrical, and the insertion / discharge rollers 3LA, 3RA are not dots but lines instead of dots as shown in FIGS. 6 (d) and 6 (e). In contact. The urging force applied to the disk 6 from the insertion / discharge rollers 3LA, 3RA is the same at any part of the insertion / discharge rollers 3LA, 3RA as shown in FIG. 6 (c). Therefore, in the disk transport mechanism 12 of this embodiment, the transmission efficiency of the driving force of the disk 6 by the insertion / discharge rollers 3LA and 3RA is large.

  Further, as a modification of the disk transport mechanism 12 of another embodiment of the present invention shown in FIGS. 6A to 6E, grooves may be formed in the insertion / discharge rollers 3LA and 3RA. In this case, the grooves can be provided in the circumferential direction of the insertion / discharge rollers 3LA and 3RA. Furthermore, the insertion / discharge roller can be formed in a shape in which a plurality of tires are provided at predetermined intervals.

  Further, a known differential limiting mechanism can be provided in the differential gear unit 20 so that the disk does not rotate when the disk is inserted and ejected. As this differential limiting mechanism, for example, a coupling using viscosity, a differential limiting using a rotational difference in a subtle coupling, a differential limiting using a torque difference in Torsen differential, and the like can be considered.

  In the above-described embodiment, a bevel gear type using a bevel gear as a differential gear unit has been described. However, as a differential gear unit, a planetary gear type using a planetary gear or a worm gear can be used. There is a Torsen type used.

  When a planetary gear type differential gear unit is used, a sun gear is fixed to the end of the roller shaft 1L, and an internal gear facing the sun gear and a ring gear concentrically provided outside the internal gear are provided. A planetary gear that is fixed to the end of the roller shaft 1r (1R), a rotation shaft is provided on a carrier plate that is rotatably fitted to the roller shaft 1L, and meshes with the sun gear and the internal gear. Can be attached. The planetary gear can be provided at three locations on the carrier plate at equal intervals. Moreover, the planetary gear provided in three places can each be set as the structure which two gears mesh. In the planetary gear type differential gear unit, since the rotational force of the transmission gear is transmitted to the ring gear, the roller shaft 1r (1R) is directly driven to rotate by the transmission gear.

  When using a Torsen-type differential gear unit, the first and second helical gears are fixed to the ends of the roller shafts 1L and 1r (1R), respectively, and these are attached to a differential gear case provided with a ring gear. Contain inside. In the differential gear case, two worm wheels respectively meshing with the first and second helical gears are rotatably mounted in parallel at the positions on the sides of the triangle by a shaft supported by the differential gear case. In this case, the two worm wheels arranged in parallel are configured to mesh with each other with spur gears provided at both ends of the worm wheel. In the Torsen-type differential gear unit, when the rotational force of the transmission gear is transmitted to the ring gear, a set of three worm wheels revolves around the roller shafts 1L and 1r (1R) to transfer the rotational force to the roller shaft 1L. And tell 1r (1R).

  In a state where there is no resistance difference between the roller shaft 1L and the roller shaft 1r (1R), rotation of the worm wheel pair is transmitted to the first and second helical gears while revolving. When a resistance difference occurs, the worm wheel on the side with the larger resistance rotates, causing the worm wheel on the opposite side to rotate in the reverse direction via the spur gear. This rotation speeds up the helical gear on the opposite side. In this case, when the helical gear on the higher resistance side turns the worm wheel, tooth surface resistance is generated, and this resistance becomes the aforementioned differential limiting force. In addition to the worm gear type, the Torsen type differential gear unit includes a helical gear type.

(A) is a perspective view showing a configuration of a roller portion of a conventional disk transport mechanism, (b) is a perspective view showing a state where an upper guide is provided in the mechanism of (a), and (c) is shown in (b). FIG. 4D is a perspective view showing the operation of the disk transport mechanism, FIG. 4D is a front view showing the main part of FIG. 3C in an enlarged manner, and FIG. 3E is a side view showing the main part of FIG. (A) is a plan view showing a state in which there is no slip in the disk feeding operation of the conventional disk transport mechanism shown in FIG. 1, and (b) is a slip in the disk feeding operation of the conventional disk transport mechanism shown in FIG. It is a top view which shows a state when there exists. (A) is a perspective view showing the configuration of an embodiment of the roller portion of the disk transport mechanism of the present invention, (b) is a perspective view showing a state where an upper guide is provided in the mechanism of (a), and (c) is ( FIG. 4A is a partially enlarged perspective view showing an enlarged portion of a differential gear unit of the disc transport mechanism shown in FIG. 4A, FIG. 4D is a sectional view of the portion of the differential gear unit shown in FIG. FIG. 5 is a partially enlarged perspective view showing the differential gear unit shown in FIG. (A) is sectional drawing which shows the structure of the disc conveyance mechanism of this invention shown to Fig.3 (a), (b) is a partial expanded sectional view explaining operation | movement of the disc conveyance mechanism shown to (a). FIG. 3A is a plan view showing a state when there is a slip in the disk feeding operation of the disk transport mechanism of the present invention shown in FIGS. 3 and 4, and FIG. 4B is an operation of the differential gear unit in the state of FIG. (C) is explanatory drawing which shows the engagement state of the roller and disk in the C section of (a), (d) is the engagement state of the roller and disk in the D section of (a) It is explanatory drawing which shows. (A) is a perspective view showing the configuration of another embodiment of the roller portion of the disk transport mechanism of the present invention, (b) is a front view of the disk transport mechanism shown in (a) in which an upper guide is provided, (c) is a partially enlarged front view showing an enlarged portion in the vicinity of the differential gear unit of the disc transport mechanism shown in (b), and (d) is another embodiment of the roller portion of the disc transport mechanism of the present invention. The perspective view explaining the contact of a roller and a disk, (e) is a top view of (d).

Explanation of symbols

1, 1L, 1R, 1r Roller shaft 2 Ring gear 3L. 3R Insertion / ejection roller 4 Transmission gear 5 Upper guide 6 Disc 10 Conventional disc transport mechanism 11, 12 Disc transport mechanism of the present invention 20 Differential gear unit 21, 22, 23, 24 Bevel gear 25 Differential gear case 26, 27 Rotating shaft

Claims (9)

A disk transport mechanism for carrying a disk medium in the disk apparatus into the apparatus or discharging the disk medium from the apparatus,
A first roller;
A first roller shaft to which the first roller is fixed;
A second roller;
A second roller shaft to which the second roller is fixed,
The first roller shaft passes through the second roller shaft rotatably,
A differential gear unit is provided between the first roller shaft and the second roller shaft,
A disk transport mechanism, wherein a ring gear for driving the differential gear unit by a driving force from a transmission gear is rotatably attached to the second roller shaft. A disk transport mechanism for carrying a disk medium in the disk apparatus into the apparatus or discharging a disk medium from the apparatus,
A columnar first roller fixed to the tip side of the first roller shaft;
A cylindrical second roller fixed to a second roller shaft through which the base side of the first roller shaft rotatably penetrates;
A differential gear unit provided between the first roller shaft and the second roller shaft;
And a ring gear that is rotatably attached to the second roller shaft and that drives the differential gear unit by a driving force from a transmission gear.   3. The disk transport mechanism according to claim 1, wherein the first and second rollers are made of an elastic member. The differential gear unit is
A differential gear case fixed to the ring gear;
A first gear fixed to the first roller shaft in the differential gear case;
A second gear fixed to the second roller shaft in the differential gear case;
At least two gears rotatably mounted on a rotary shaft provided at a predetermined position in the differential gear case and revolving around the first and second roller shafts while meshing with the first and second gears. 4. The disk transport device according to claim 1, wherein the disk transport device is configured as follows. The differential gear unit is
A first gear fixed to the first roller shaft;
A second gear fixed to the second roller shaft, facing the first gear on the inner side, and forming the ring gear on the outer side;
A carrier plate rotatably attached to the first gear;
2. A planetary gear which is rotatably attached to a rotating shaft projecting from at least three locations of the carrier plate and meshes with the first gear and the internal gear. 5. The disk transport device according to any one of 4 above.   6. The disk transport apparatus according to claim 1, wherein a differential limiting mechanism is provided in the differential gear unit.   The disk transport apparatus according to claim 1, wherein an upper guide for defining a position of the disk medium is provided above the first and second rollers.   4. The disk transport apparatus according to claim 3, wherein grooves are formed in the first and second rollers.   9. The disk transport device according to claim 8, wherein the groove is formed in a circumferential direction of the first and second rollers.

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