JP3006014U - Gear assembly for disk transfer device - Google Patents

Abstract

(57) [Abstract] [Purpose] The object of the present invention is to configure a driving gear and a driven gear, and to transmit a power by a buffering force at the time of power transmission between these gears to make a fine correction like an instrument. The purpose is to provide a gear assembly that protects the gear with and can operate accurately. An annular coupling groove and a locking portion are formed on the lower surface of the upper gear, and a cutoff portion corresponding to the locking portion and an annular coupling protrusion corresponding to the annular coupling groove are formed on the upper surface of the lower gear. There is. Corresponding to a panel spring or a locking portion on both sides of the locking portion, the panel spring or the locking portion is provided between the locking portion and the side wall of the annular protrusion to reduce the impact during power transmission between the upper gear and the lower gear. A semi-circular end protruding elastic portion having holes inside both ends of the combined annular protruding portion is formed. The gears can be protected and precise operation can be performed by finely compensating for the instrument during operation of the gear assembly between both cross sections of the annular coupling protrusion and both side surfaces of the locking portion.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gear assembly for a disc transfer device, and more particularly, to a gear assembly for driving a mini disc tray which is a draw type data memory device (Draw Type Data Memory device).

[0002]

[Prior art]

 Recently, in computers, audio equipment, and video equipment, many pits are formed on the surface of a disc to store information, and the disc player drives the disc to rotate the disc at a high speed. After the laser beam is projected onto the surface of the disk to detect the light reflected from the disk, it is converted into an electrical signal to read the image and / or acoustic information or other information. In such a disc player, after mounting the disc on the disc tray, the disc tray is moved to be positioned below the head of the disc drive device. An example of such a disc transfer device is disclosed in U.S. Pat. No. 4,839,881.

The disc tray is supported at the bottom by a cylindrical bearing, so that it moves smoothly along the guide rails. The side surface of the disc is provided with a rack having a plurality of slots for transmitting power so that the disc tray can move in the vertical direction. Such a disc tray operates so as to reciprocate in a certain section.

Generally, in a disc drive system, a motor is driven to transmit power to the disc tray so that the disc tray can reciprocate. More specifically, first, the rotational force of the motor is firstly transmitted to a moving rack (also referred to as an operation control member) capable of reciprocating a short distance from the motor to form the moving rack. Move in a certain direction in a certain area A large number of gears mesh with each other between the moving rack and the disc tray rack to transmit the power of the motor to the disc tray. In the case of moving racks, the above gears are configured so that the disk tray racks can move a predetermined distance longer due to the short moving distance of the moving racks. In this case, in order to amplify and transmit the moving distance of the moving rack, a pair of gears which are generally coaxial (this is called “double gear”) is used to make a reciprocating motion between the moving rack and the disc tray. Is adjusting the distance. An example of such a double gear is disclosed in U.S. Pat. No. 4,442,516. FIG. 1 is a view showing the double gear of the above-mentioned US patent.

As shown in the figure, the double gear meshes with the rack (not shown) of the disc tray, and the first gear 26 and the second gear 25 are coaxial with each other by the support pin (not shown). It is mounted on a guide rail (not shown) so that it can rotate coaxially and is supported by a support pin (not shown). The first gear 26 is formed at its center with an axial through hole 31 through which a support pin can pass and an arc-shaped confronting arc-shaped engagement hole 32. The second gear 25 has a shaft through hole 30 through which a support pin passes in the center thereof, and a pair of opposing pins 27 corresponding to the above holes 32 is formed in the upper portion thereof. The ratio of the diameter D2 of the first gear 26 to the diameter D1 of the second gear 25 is about 2: 1. That is, the ratio of the number of gear teeth is 2: 1.

A moving rack (not shown) reciprocates according to the rotational force of the motor and transmits the reciprocating motion to the meshed second gear 25 to rotate the second gear 25. The rotational force of the second gear 25 is transmitted to the first gear 26 by the two pins 27 and the fitting holes 32, and the first gear 26 drives another gear (not shown) directly meshed with it or the tray rack. Then, the disc tray is reciprocated so that it can move. Either keep the minidisk under the head of the disk drive in this way, or remove it. When the above-mentioned conventional double gear is used, the pin 27 of the second gear 25 frequently collides with the side wall of the fitting hole 32 of the first gear when the disc tray reciprocates. Therefore, the pin 27 is easily damaged by the impact generated during the reciprocating motion, and it is necessary to replace the pin 27 with a new double gear frequently. Further, since the power of the second gear 25 is transmitted to the first gear 26, the drive motor is overloaded, which is not desirable.

[0007]

[Means for solving the problem]

 Therefore, the object of the present invention is to consist of a driving gear and a driven gear, and when transmitting power between these gears, the power is transmitted by a buffering force to protect the gear by making a fine correction like an instrument, The present invention provides a gear assembly that can be operated accurately. Another object of the present invention is to provide a gear assembly that is easy to manufacture and easy to assemble. In order to achieve the above and other objects of the present invention, the gear assembly of the present invention has an annular coupling protrusion formed on an upper surface of a first gear and an engagement portion formed on a lower surface of a second gear. A coupling groove is formed, and shock absorbing means is included between the locking portion and the annular protruding portion. That is, according to the present invention, an annular coupling groove and an engaging portion are formed on the lower surface, and a first gear having a first diameter; an upper surface corresponding to the disconnecting portion corresponding to the engaging portion and the annular engaging groove. A second gear having a diameter smaller than the first diameter and positioned coaxially with the first gear at a lower part of the first gear; For transmitting the rotational force from the drive gear to the driven gear, the drive gear includes shock absorbing means for absorbing a shock at the time of power transmission between the first gear and the second gear with the side wall of the annular coupling protrusion. It provides a gear assembly.

According to one embodiment of the present invention, the shock absorbing means is also a panel spring including a pair of opposed panels and a spring provided between the panels. According to another embodiment of the present invention, the shock absorbing means is a buffer part formed on both upper side walls of the annular coupling protrusion corresponding to the locking part. The upper cushioning portion may be formed, for example, by extending from the upper side surface of the annular coupling protrusion corresponding to the locking portion and protruding in a semicircular shape. The buffer portion has a hole therein which is smaller than the diameter of the semi-annular distal elastic protrusion. The buffer portion is preferably formed by using the same material as that of the annular coupling protrusion. The present invention also provides a first circular convex portion formed in a first circular concave portion formed on the bottom surface and having a diameter smaller than the diameter of the first circular concave portion; the first circular convex portion on the first circular convex portion. A first gear having a diameter smaller than the diameter of the protrusion and having a first diameter having a second circular protrusion having an annular coupling groove having a locking portion formed thereon; Smaller than the diameter of the second circular convex portion and larger than the diameter of the second circular convex portion and formed on the third circular convex portion and the third circular convex portion, corresponding to the cutout portion corresponding to the locking portion and the annular coupling groove. Which has a diameter smaller than the diameter of the first annular recess and is about ½ of the first diameter, and is coaxial with the first gear at a lower portion of the first gear. A second gear that is positioned with; and the locking portion and the annular protrusion on both sides of the locking portion. Drive gear composed of a pair of panels and a spring provided between the two panels in order to mitigate impact during power transmission between the first gear and the second gear between the two side walls of the vehicle. To provide a gear assembly for transmitting rotational force from the driven gear to the driven gear. Further, the present invention is formed on the first circular concave portion formed on the bottom surface, the first circular convex portion having a diameter smaller than the diameter of the first circular concave portion, and the first circular convex portion formed on the first circular convex portion. A first gear having a diameter smaller than that of the first circular protrusion and having a first diameter having a second circular protrusion having a shape coupling groove having a locking portion formed thereon; A third circular convex portion that is smaller than the diameter of the circular convex portion and is larger than the diameter of the second circular convex portion and a cutoff portion that is formed on the third circular convex portion and that corresponds to the locking portion, and the annular shape. The first gear has a diameter smaller than that of the first circular recess and is smaller than about 1/2 of the first diameter, and includes an annular coupling protrusion corresponding to the coupling groove. A second gear that is coaxially positioned with the locking portion, and the locking portion on both sides of the locking portion. In order to mitigate the shock during power transmission between the first gear and the second gear between the side walls of the annular coupling protrusion, both ends of the coupling annular protrusion facing the locking portion are provided. Provided is a gear assembly for transmitting a rotational force from a driving gear to a driven gear, and a pair of semi-circular end projecting elastic portions projecting from an upper side wall and having a hole of a smaller diameter in the center thereof. The double gear of the present invention can also be used to drive a mini disc tray. Provide a shock absorbing device between both cross-sections of the annular coupling protrusion and both sides of the locking portion, and give a slight margin when a stop or rotation command is received with the double gear and the adjacent gear meshing. . Therefore, the shock is buffered and the overload of the motor can be prevented.

[0009]

【Example】

 Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings. FIG. 2 is a schematic view showing a double gear according to an embodiment of the present invention. In the figure, 100 is an upper gear, 102 is a first circular recess formed in the lower portion of the upper gear 100, that is, a bottom surface, and 104 is a first circular projection formed in the first circular recess 102. Reference numeral 106 denotes a second circular convex portion formed on the first annular protrusion 104, 108 denotes an annular coupling groove, and 110 denotes a lock formed by connecting the outer peripheral surface and the inner peripheral surface of the annular coupling groove 108. Numeral 112 denotes a central through hole through which the supporting shaft passes through the center of the first gear 100, 115 denotes a panel spring, 120 denotes a lower gear, and 122 denotes an upper surface of the lower gear 120. The third circular projection 124, which is formed on the third circular projection 122 (corresponding to the annular coupling groove), is an annular coupling projection, 125 is the central shaft passage hole of the lower gear 120, and 126 is the above. Locking A cutout of the annular coupling protrusion 124 corresponding to the portion 110 is shown.

In the double gear shown in FIG. 2, an annular coupling groove 108 and a locking portion 110 are formed in a lower portion of an upper gear 100 which is a first gear (driven gear), and the diameter of the upper gear 100 is about 1 mm. An annular coupling protrusion 124 and a cut-off portion 126 of the annular coupling protrusion 124 are formed on the upper surface of the lower gear 120 that is the second gear (driving gear) having a diameter of / 2. The upper cut-off portion 126 is formed to have a width slightly larger than the width of the locking portion 110 corresponding to the locking portion 110 of the first gear 100. Here, the size of the width of the locking portion 110 is defined by the angle of the line between the side surfaces of the locking portion 110 and the center line of the gear assembly, and the size of the cut-off portion 126 is an annular coupling. It is defined by the angle of the line connecting both side walls of the protrusion 124 and the center line of the gear assembly. The upper gear 100 is mounted on the lower gear 120 so that the annular coupling protrusion 124 is inserted into the annular coupling groove 108 and meshed with each other. More specifically, a first circular recess 102 having a diameter larger than that of the lower gear 120 is formed on the bottom surface of the upper gear 100, and the first circular recess 102 has a diameter substantially the same as the diameter of the lower gear 120. The first circular convex portion 104 having the is formed. A second circular convex portion 106 having a diameter smaller than that of the first circular convex portion 104 and having an annular coupling groove 108 having a locking portion 110 is formed on the first circular convex portion 104. There is. The annular coupling protrusion 124 of the lower gear 120 is formed on the upper surface of the lower gear 120, and is formed on the third circular protrusion 122 having a diameter smaller than the diameter of the lower gear 120, and the annular coupling groove 108. It has almost the same height and width as the depth of. The first, second and third circular protrusions 104, 106 and 122 improve the joint between the annular coupling groove 108 and the annular coupling protrusion 124. Also, the first circular recess 102 reduces the gap between the upper and lower gears. The rotational force of the lower gear 120 is transmitted to the upper gear 100 due to the existence of the engaging portion 110 formed on the upper gear 100 and the annular coupling protrusion 124 of the lower gear 120. It is well known to those skilled in the art that the upper gear 100 and the lower gear 120 are usually made of engineering plastic.

In this embodiment, a pair of cylinder type panel springs 115 are provided between both side surfaces of the annular coupling protrusion 124 and both side surfaces of the locking portion 110. FIG. 3 is a schematic view showing an example of the panel spring 115 used in this embodiment. As shown in the figure, the panel spring 115 is provided with disk-shaped panels 115a and 115b having the same diameter on both sides, and has the same diameter as the panel 115a and 115b between the two panels 115a and 115b. A spring 115c having a diameter of The diameter of the panel spring 115, which is defined by the diameter of the panels 115a and 115b or the diameter of the spring 115c, is the side surface of the locking portion 110 having a square shape or an annular coupling protrusion in consideration of handling and assembly of the double gear. It is preferable to determine the size so as to inscribe the quadrangle on the side surface of the portion 124. As shown in FIG. 2, when assembling the double gear, the pair of panel springs 115 is attached to the side wall of the locking portion 110 or the side wall of the annular protrusion 124 using an adhesive, and then the upper gear 100 is attached. The annular coupling protrusion 124 is mounted on the lower gear 120 so as to mesh with the annular coupling groove 108.

FIG. 4 is a cross-sectional view showing an example of a disc tray driving device using the double gear of the present invention. In the figure, reference numeral 10 is a moving rack, 11 is a first screw, 12 is a second screw, 50 is a transmission gear, 55 is a gear meshing portion of the transmission gear 50 and the upper gear 100, 60 is a tray, and 70 is a tray. A rack, 80 is a moving gear and a gear meshing portion of the second gear 120, and 90 is a support base. FIG. 5 is an enlarged view of portion A of FIG. Referring to FIG. 4, the moving rack 10 is driven by a motor to reciprocate a short distance. The upper gear 100 and the lower gear 120 are fixed to the support base 90 by the first screw 11 on the same axis so that the annular coupling groove 108 of the upper gear 100 meshes with the annular coupling protrusion 124. The reciprocating motion of the moving rack 10 is transmitted to the lower gear 120 through the gear connecting portion 80, and the lower gear 120 rotates. The rotational movement of the lower gear 120 is transmitted to the upper gear 100 through the annular coupling protrusion 120 of the lower gear 120 and the locking portion 110 of the upper gear 100. The rotational movement of the upper gear 100 is reciprocated in the tray 60 by transmitting the reciprocating movement to the trailer 70 through the transmission gear 50 which is fixed to the other part of the support 90 by the second screw 12 so as to rotate. Exercise. In the double gear, which is an example of the present invention, the panel springs 115 are provided on both cross sections of the annular coupling protrusion 124. When the stop command is received when the double gear is rotated, or when the stop command is received when the double gear is stopped, the panel spring 115 provides the double gear (that is, the gear assembly) with a fine margin. The panel spring 115 buffers these forces and protects the gear from impacts on them. This buffering action prevents the motor that drives the moving rack from being overloaded and extends the life of the motor. In addition, when manufacturing the double gear, the tolerance for the precision of the stopper is widened, which not only simplifies the assembly but also eliminates the gap generated from the gear connecting part and corrects it to a steady coupling state. This is to compensate for minute movements so that the gear can operate steadily.

FIG. 6 shows a lower gear 120a of a double gear according to a second embodiment of the present invention. In this embodiment, the same upper gear as that of the first embodiment is used. The lower gear 120a according to the present embodiment is different from the panel spring 115 used in the first embodiment in that the buffer portion 130 is formed on the upper side wall of the annular coupling protrusion 124 of the lower gear 120a. This is the same as the lower gear 120 of the first embodiment. That is, in the first embodiment, the panel spring 115 is used for the purpose of buffer relaxation of the double gear, but in this embodiment, the buffer portions 130 are formed on the upper side walls of both ends of the annular coupling protrusion 124. FIG. 7 is an enlarged view of the B portion including the buffer portion 130 of FIG. As shown in the figure, the buffer part 130 is formed in a semicircular shape extending toward the locking part 110 and protruding from the upper side surface of the annular coupling projecting part 124 corresponding to the locking part 110. A hole having a diameter slightly smaller than the diameter of the semicircle at the end of the buffer portion 130 is formed in the central portion. The buffer portion 130 is preferably made of the same material as that of the coupling annular protrusion 124. When the lower gear 120a is formed by using plastic, it can be easily formed by using a mold for manufacturing the above-described shape. Alternatively, first, after manufacturing the same lower gear 120 as in the first embodiment, a buffer part 130 is separately manufactured, and the additional buffer part 130 is attached to the upper sidewall of the annular coupling protrusion 124 of the lower gear 120. It can also be attached using an adhesive. Here, the buffer unit 130 may be manufactured using an elastic material such as natural or synthetic rubber. Since plastic has elasticity, if a hole is formed inside the hemispherical protrusion as shown in the figure, the hemispherical protrusion can be used for shock absorption. Although it is possible to form one large hole, it is also possible to form and use a large number of holes. The operation of the double gear of this embodiment is the same as that of the first embodiment described above, and the description thereof is omitted. In the first embodiment described above, it was difficult to manufacture and handle the panel spring, but in this embodiment, since the buffer portion is directly attached to the lower gear, the buffer portion and the lower gear can be manufactured at the same time in the molding process. .

As described above, according to the present invention, a shock absorbing device is provided between both cross-sections of the annular coupling protrusion 124 and both sides of the locking portion 110 so that the upper gear meshes with another gear or tray rack. When a stop or rotation command is received in a state, it gives a minute allowance and acts as a buffer. Therefore, it protects the gears and prevents the motor that drives the moving rack from being overloaded. In addition, the tolerance for the precision of the stopper is expanded, the assembly is simple, and the gap generated from the gear connection part is removed to correct the normal connection state, compensating for minute movements and gears. Be able to operate normally. Although the present invention has been specifically described based on the above-described embodiments, the present invention is not limited to this, and modifications and improvements can be made within the scope of ordinary knowledge of those skilled in the art. For example, in the embodiment of the present invention, the double gear is used only for driving the disc tray, but it goes without saying that the double gear of the present invention can be used in other mechanical fields.

[Brief description of drawings]

FIG. 1 is a view showing an example of a conventional double gear.

FIG. 2 is a schematic view showing a double gear according to an embodiment of the present invention.

FIG. 3 is a schematic view showing an example of a panel spring used in the double gear of FIG.

FIG. 4 is a sectional view showing an example of a disc tray driving device using a double gear of the present invention.

5 is an enlarged view of a portion A of FIG.

FIG. 6 is a view showing a lower gear of a double gear according to a second embodiment of the present invention.

FIG. 7 is an enlarged view of portion B in FIG.

[Explanation of symbols]

 10 Moving Rack 11 1st Screw 12 2nd Screw 50 Transmission Gear 60 Tray 70 Tray Rack 80 Gear Fitting Part 90 Supporting Base 100 Upper Gear 102 First Circular Recess 104 104 First Circular Convex 106 106 Second Circular Convex 108 Ring Connection Groove 110 Locking portion 112 Central through hole 115 Panel spring 120 Lower gear 122 Third circular convex portion 124 Annular coupling protruding portion 126 Cutoff portion 130 Buffer portion

Claims (9)

[Scope of utility model registration request] 1. A first gear having an annular coupling groove and a locking portion formed on a lower surface and having a first diameter; a cutting portion corresponding to the locking portion and an annular protrusion corresponding to the annular coupling groove on an upper surface. A second gear having a diameter smaller than the first diameter and located coaxially with the first gear at a lower portion of the first gear; and the engaging portions on both sides of the locking portion. Rotational force is transmitted from the drive gear to the driven gear, including a shock absorbing means for absorbing a shock during power transmission between the first gear and the second gear between the side wall of the stopper and the side wall of the annular protrusion. Gear assembly for disk transfer device. 2. The gear assembly for a disk transfer device according to claim 1, wherein the shock absorbing means is a panel spring composed of a pair of panels and a spring provided between the panels. 3. The gear assembly for a disk transfer device according to claim 1, wherein the shock absorbing means is a buffer portion formed at both ends of the annular protrusion corresponding to the locking portion. 4. The semi-annular end elastic member, wherein the buffer portion is formed in a semi-circular shape and protrudes from the upper side surface of the annular coupling protrusion corresponding to the locking portion to the locking portion, and has a hole having a smaller diameter therein. The gear assembly for a disk transfer device according to claim 3, wherein the gear assembly is a protrusion. 5. The gear assembly for a disk transfer device according to claim 3, wherein the buffer portion is made of the same material as the annular coupling protrusion portion. 6. The gear assembly of claim 1, wherein the diameter of the first gear is about twice the diameter of the second gear. 7. The first gear has a first circular recess that is larger than the diameter of the second gear in the bottom surface of the first gear, and the first circular recess has a diameter substantially equal to the diameter of the second gear. The first circular convex portion having a diameter of the same size, the first circular convex portion having a diameter smaller than the diameter of the first circular convex portion, and the locking portion. 2. The gear assembly for a disk transfer device according to claim 1, further comprising a second annular protrusion having an annular coupling groove formed therein. 8. The annular protrusion is formed on the upper surface of the first gear, and is formed on a third circular protrusion having a diameter smaller than that of the second gear. The gear assembly for a disk transfer device according to 1. 9. The gear assembly for a disc transfer device according to claim 1, wherein the gear assembly is used for driving a mini disc tray.