JP2014191328A - Music box - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a music box for suitably suppressing the occurrence of an off performance tempo.SOLUTION: The music box controls the output torque of a motor when a pawl part 36 plays a vibration valve 18 in accordance with the type of the sound issued by playing of at least one vibration valve 18 by the pawl part 36 of a star wheel 14. Therefore, the music box previously predicts a load of a motor when the pawl part 36 plays the vibration valve 18 in consideration of respective characteristics of a plurality of vibration valves 18, and controls the output torque of the motor. Thus, the rotational speed of the motor can be kept constant regardless of the vibration valve 18 played by the pawl part 36.

Description

  The present invention relates to a music box, and more particularly, to an improvement for suppressing a deviation in performance tempo.

  Music boxes that play music are known. The music box includes, for example, a plurality of claw portions that are directed outward in the radial direction, and a plurality of star wheels that are rotatably provided around the first axis. Corresponding to each of the plurality of star wheels, a plurality of vibration valves are provided with a diaphragm provided along the first axis. For example, the plurality of star wheels are driven to rotate by a motor. Further, the rotation of the star wheel is controlled by driving a solenoid provided corresponding to each star wheel. And a nail | claw part is made to contact a vibration valve selectively with a predetermined timing, and it plays, and a music is played. There has been proposed a technique for controlling the output of a motor when a claw part flips a vibration valve. For example, this is the performance device described in Patent Document 1.

JP 2004-12852 A

  In the music box, for example, at the moment when the vibration valve is bounced, the rotation speed is reduced by applying a load to the motor that drives the star wheel. As a result, there has been a problem that the performance tempo becomes unstable due to a decrease in the rotation speed of the motor. The conventional technique performs control after detecting that the rotational speed of the motor has changed. Therefore, it is not always possible to sufficiently suppress the change in the rotation speed of the motor. That is, there is a possibility that the music box performance tempo may be shifted. Such a problem has been newly found in the course of continuous research by the present inventor with the intention of improving the performance of the music box.

  The present invention has been made against the background of the above circumstances, and an object of the present invention is to provide a music box that suitably suppresses a shift in performance tempo.

  In order to achieve such an object, the gist of the invention according to claim 1 of the present application is that a diaphragm including a plurality of vibration valves each having different characteristics corresponding to different scales, and the vibration A claw portion that is arranged corresponding to each of the valves and that plays the vibration valve corresponding to the sound to be played by driving the motor according to the music data for which the timing to play the sound is determined, and a control unit that controls the driving of the motor The control unit is configured to generate a sound that is played when the vibration valve is played when the claw unit plays at least one of the vibration valves at a timing of sounding the sound defined in the music data. The music box is characterized in that the output torque of the motor is controlled according to the type.

  According to the first aspect of the present invention, the load of the motor when the claw portion flips the vibration valve is predicted in advance in consideration of the characteristics of each of the plurality of vibration valves, and the output torque of the motor is determined. By controlling, the rotational speed of the motor can be kept constant regardless of the vibration valve that the claw part repels. That is, it is possible to provide a music box that suitably suppresses the occurrence of a deviation in the performance tempo.

  The gist of the invention according to claim 2 of the present application subordinate to the invention according to claim 1 is that the control unit plays the vibration valve at the timing of making the sound defined in the music data. According to the number of sounds to be played with the timing set at the same time, the greater the number of the vibration valves that the claw parts play simultaneously, the more the output of the motor when the claw parts play the vibration valve The torque is increased.

  The gist of the invention according to claim 3 of the present application subordinate to the invention according to claim 1 or 2 is that the control unit plays the vibration valve at the timing of making the sound according to the music data. According to the scale of the sound to be played, the higher the scale of the vibration valve that the claw part plays, the greater the output torque of the motor when the claw part plays the vibration valve.

  The gist of the invention according to claim 4 of the present application dependent on the invention according to any one of claims 1 to 3 is that the volume of the music box is changed by changing a relative distance between the vibration valve and the claw portion. The control unit is adjusted by the volume adjustment mechanism according to the volume of the sound to be played when the vibration valve is played at the timing of sounding the sound according to the music data. The greater the volume of the music box, the greater the output torque of the motor when the claw portion flips the vibration valve.

  The gist of the invention according to claim 5 of the present application that is dependent on the invention according to claim 1 is that the number of the vibration valves that the claw parts play simultaneously, the scale corresponding to the vibration valve that the claw parts play, And a table that stores a relationship between at least one of the music box volumes adjusted by the volume control mechanism and an output torque of the motor, and the control unit is configured to store the claw from the relationship stored in the table. Based on at least one of the number of the vibration valves that the part simultaneously plays, the scale corresponding to the vibration valve that the claw part plays, and the volume of the music box that is adjusted by the volume adjustment mechanism, The output torque of the motor when the vibration valve is flipped is controlled.

It is a perspective view which illustrates the structure of the performance mechanism part in the music box which is one Example of this invention. It is the figure which looked at the performance mechanism part of FIG. 1 in the axial direction of the 1st axis | shaft. It is a top view explaining the structure of the diaphragm with which the music box of FIG. 1 was equipped. It is a figure which shows an example of a torque required in order that the nail | claw part with which the star wheel in the music box of FIG. It is a figure explaining the action | operation which the nail | claw part in a star wheel plays the sound by playing the vibration valve of a diaphragm in the music box of FIG. It is a functional block diagram explaining the principal part of the control function with which ECU in the music box of FIG. 1 was equipped. It is the cross-sectional schematic diagram along the extending | stretching direction (longitudinal direction) of a vibration valve of the performance mechanism part in the music box of FIG. It is a figure explaining the amount of lap | wraps of the nail | claw part with respect to each vibration valve in the music box shown in FIG. It is a figure which shows an example of the table used for the motor output control of a present Example. It is a figure explaining an example of the gradual increase control of the output torque of the motor of a present Example. It is a flowchart explaining the principal part of an example of the motor output torque control by ECU of the music box of FIG.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a perspective view illustrating a state in which a configuration of a performance mechanism unit 100 in a music box 10 according to an embodiment of the present invention is viewed obliquely from above. In the present embodiment, the upper side of the music box 10 means the upper side (substantially vertically upward) when the music box 10 is installed on an installation plane (not shown). As shown in FIG. 1, the music box 10 of this embodiment includes a plurality of (for example, 40) star wheels 14 that are rotatably provided around a first shaft 12 (see FIG. 2 and the like). . A diaphragm 16 provided along the first axis 12 is provided. A second shaft 20 is provided along with the first shaft 12. A second shaft 20 is preferably provided in parallel with the first shaft 12. A plurality of locking members 22 corresponding to the plurality of star wheels 14 are provided so as to be rotatable about the second shaft 20. A plurality of electromagnets 24 respectively corresponding to the plurality of locking members 22 are provided. A plurality of sun wheels 28 are provided which are provided in a relatively non-rotatable manner with respect to a third shaft 26 provided in parallel with the first shaft 12 and are rotated integrally with the third shaft 26. The plurality of sun wheels 28 correspond to the plurality of star wheels 14, respectively. Preferably, a plurality of sun wheels 28 assembled to the third shaft 26 so as not to rotate relative to the third shaft 26 so as to be movable in the axial direction sandwich one star wheel 14 between two adjacent sun wheels 28. By being fixed at both ends of the third shaft 26, the third shaft 26 is fixed so as not to be rotatable relative to the axial direction. Alternatively, it is fixed in advance to the third shaft 26 so that it cannot be rotated relative to the third shaft 26 and cannot move in the axial direction.

  The music box 10 includes a pedestal 29 on which the diaphragm 16 and the like are assembled. A frame 30b is provided that supports the first shaft 12 and the third shaft 26 so that the first shaft 12 and the third shaft 26 can rotate about their respective axes, and the second shaft 20 cannot rotate, and a plurality of electromagnets 24 and the like are assembled. The pedestal 29 and the frame 30b are configured to be relatively moved as will be described later. A motor 32 is provided that generates a driving force for rotationally driving the first shaft 12 and the third shaft 26 in synchronization with the respective shaft centers. The motor 32 is preferably a well-known DC motor (direct current motor) whose output torque changes according to the supplied current (drive current).

  FIG. 3 is a plan view for explaining the configuration of the diaphragm 16 provided in the music box 10. As shown in FIG. 3, the diaphragm 16 is provided with a plurality of (for example, 40) vibration valves 18. The plurality of vibration valves 18 respectively correspond to the plurality of star wheels 14. That the vibration valve 18 corresponds to the star wheel 14 means that the claw portion 36 provided in the star wheel 14 is in a positional relationship for flipping the vibration valve 18. By assembling the diaphragm 16 to the pedestal 29, a plurality of vibration valves 18 are provided along the first shaft 12. The plurality of vibration valves 18 respectively correspond to a plurality of predetermined scales. As will be described later, the sound of the corresponding scale is played by being played by the claw portion 36 of the star wheel 14. That is, the vibration valve 18 corresponds to the sounding body in the music box 10. In other words, the plurality of vibration valves 18 generate sounds having different frequencies by being played by the claw portions 36 of the star wheel 14. For this reason, the plurality of vibration valves 18 have different characteristics. For example, characteristics such as a dimension (length) in the longitudinal direction, a dimension (thickness) in the width direction, and a dimension (thickness) in the thickness direction of each vibration valve 18 are different among the plurality of vibration valves 18. The dimension in the thickness direction may be common to all the vibration valves 18. For example, the higher the scale corresponding to the vibration valve 18, the shorter the longitudinal dimension.

  FIG. 4 is a diagram illustrating an example of torque necessary for the claw portions 36 provided in the star wheel 14 to play the plurality of vibration valves 18 respectively. Since the characteristics of the plurality of vibration valves 18 are different from each other, as shown in FIG. 4, the torque required for the claw portions 36 provided in the star wheel 14 to repel the plurality of vibration valves 18 is different. For example, the higher the scale corresponding to the vibration valve 18, the greater the torque required to play each vibration valve 18. That is, the higher the scale corresponding to the vibration valve 18, the greater the load on the motor 32 for playing the vibration valve 18. This is because the higher the scale corresponding to the vibration valve 18, the shorter the dimension in the longitudinal direction. Further, regarding the characteristics of the vibration valve 18, as the dimension in the width direction is larger (thicker), the torque required to play the vibration valve 18 is increased. As the dimension in the thickness direction is larger (thicker), the torque required to play each vibration valve 18 increases.

  In the music box 10, it is conceivable that the claw portions 36 provided on the star wheel 14 play the plurality of vibration valves 18 simultaneously. The maximum value of the number of vibration valves 18 that the claw portions 36 play simultaneously is, for example, six. That is, the music box 10 can preferably be played with a maximum of six scales as chords. The phrase “the claw portions 36 play the plurality of vibration valves 18 at the same time” means that the claw portions 36 corresponding to the vibration valves 18 come into contact with the vibration valves 18 at the same time. When the claw portion 36 plays the plurality of vibration valves 18 at the same time, the torque required for the claw portions 36 provided on the star wheel 14 to play the vibration valve 18 varies depending on the number of vibration valves 18 that are simultaneously played. That is, as the number of vibration valves 18 that the claw portions 36 provided in the star wheel 14 simultaneously play increases, the load on the motor 32 for playing the vibration valves 18 increases. Further, regarding the plurality of vibration valves 18 that the claw portions 36 provided on the star wheel 14 simultaneously play, the higher the scale corresponding to the plurality of vibration valves 18, the greater the load on the motor 32 for flipping the vibration valves 18. .

  As will be described later with reference to FIG. 7, the music box 10 includes a volume adjustment mechanism that adjusts the volume of the music box 10 by changing the relative distance between the vibration valve 18 and the claw portion 36. Depending on the relative distance between the vibration valve 18 and the claw portion 36, the torque required for the claw portion 36 provided on the star wheel 14 to repel the vibration valve 18 differs. That is, the motor 32 for repelling the vibration valve 18 is increased as the lap amount La (see FIG. 8) of the claw part 36 with respect to each vibration valve 18 described later corresponding to the relative distance between the vibration valve 18 and the claw part 36 increases. The load of increases. Further, regarding the plurality of vibration valves 18 that the claw portions 36 provided on the star wheel 14 simultaneously play, the higher the scale corresponding to the plurality of vibration valves 18, the greater the load on the motor 32 for flipping the vibration valves 18. . Furthermore, the load of the motor 32 for flipping the vibration valve 18 increases as the number of the vibration valves 18 simultaneously repelled by the claw portions 36 provided in the star wheel 14 increases.

  The performance mechanism unit 100 in the music box 10 of this embodiment shown in FIG. 1 is accommodated in a rectangular parallelepiped housing (not shown). The music box 10 includes a first shaft 12, a plurality of star wheels 14, a diaphragm 16, a second shaft 20, a plurality of locking members 22, a plurality of electromagnets 24, a third shaft 26, a plurality of sun wheels 28, and the like. Housed in a housing. That is, a base 29 on which the diaphragm 16 configured as shown in FIG. 1 is assembled, the first shaft 12, the plurality of star wheels 14, the diaphragm 16, the second shaft 20, the plurality of locking members 22, and the plurality of members. A frame 30b on which the electromagnet 24, the third shaft 26, the plurality of sun wheels 28, and the like are assembled is assembled to a lower frame (not shown) and accommodated inside the housing. Preferably, the center of the second shaft 20 and at least a part of the plurality of electromagnets 24 are arranged on the same plane along the bottom surface of the housing. Note that all the electromagnets 24 need not be arranged on the same plane along the bottom surface of the housing. A viewing window for visually recognizing the inside of the casing is provided on the upper plane portion of the casing. The observation window is provided with a lid (not shown) made of a transparent material such as a glass plate. The music box 10 includes an ECU (Electric Control Unit) 60 (see FIG. 6) as a control unit that controls excitation or non-excitation of each of the plurality of electromagnets 24.

  FIG. 2 is a diagram of the configuration of the star wheel 14, the locking member 22, the sun wheel 28, and the like in the performance mechanism unit 100 of the music box 10 as viewed in the axial direction of the first shaft 12. It is. In FIG. 2, the illustration of the frame 30b is omitted. In FIG. 2, the star wheel 14, the locking member 22 corresponding to the star wheel 14, the electromagnet 24, and the like are illustrated among the plurality of star wheels 14 of the performance mechanism unit 100. The correspondence between the star wheel 14 and the locking member 22 means that the rotation of the star wheel 14 is locked in the locked state in which the locking member 22 is positioned as shown in FIG. The correspondence between the star wheel 14 and the sun wheel 28 means that the gear portion 38 of the star wheel 14 and the outer peripheral teeth 40 of the sun wheel 28 mesh with each other. The adjacent sun wheel 28 refers to the sun wheel 28 that is arranged along the third axis 26 around the axis.

  As shown in FIG. 2, the star wheel 14 includes a plurality of claw portions 36. The claw portions 36 are protrusions that are radially formed toward the radially outer side of the star wheel 14. Preferably, four claw portions 36 are provided in the circumferential direction of the star wheel 14 in the same phase. That is, the claw portion 36 is provided every 90 ° in the circumferential direction of the star wheel 14. The star wheel 14 includes a plurality of gear portions 38 on the inner peripheral side (radially inner side) than the claw portion 36. Preferably, a gear portion 38 is provided as a protruding portion with two teeth at a position corresponding to each claw portion 36. The gear portion 38 is disposed while the plurality of star wheels 14 are disposed along the first shaft 12. That is, the gear portion 38 is disposed at a position different from the claw portion 36 with respect to the axial direction of the first shaft 12. Specifically, it is arrange | positioned between the nail | claw parts 36 mutually adjacent | abutted regarding the axial direction. The sun wheel 28 is configured to include a plurality of outer peripheral teeth 40 toward the radially outer side. The plurality of star wheels 14 are sandwiched between two adjacent sun wheels 28. That is, the outer peripheral teeth 40 of the sun wheel 28 on both sides enter the radially inner peripheral side from the outer peripheral surface 72 of the star wheel 14 (see the enlarged portion surrounded by a broken line in FIG. 2). Thereby, the plurality of star wheels 14 are positioned in the axial direction of the first shaft 12.

  As shown in FIG. 2, in the state where the star wheel 14 is assembled to the first shaft 12, the claw portion 36 has at least one of the vibration valves 18 corresponding to the rotation locus centered on the axis of the first shaft 12. It is provided in the position which contacts a part. The nail | claw part 36 is provided in the position latched by the latching member 22 in the latching state of the corresponding latching member 22. FIG. This locked position is a position that prevents the star wheel 14 from rotating following the rotation of the first shaft 12 in a state where the claw portion 36 is in contact with the locking member 22. That is, the claw portion 36 functions as a stopper that prevents the follow-up rotation accompanying the rotation of the first shaft 12 of the star wheel 14 by repelling the vibration valve 18 in the diaphragm 16 and contacting the locking member 22. The gear portion 38 is provided at a position where the rotation locus centering on the axis of the first shaft 12 is meshed with the outer peripheral teeth 40 of the corresponding sun wheel 28.

  In a state where the star wheel 14 is assembled to the first shaft 12, a predetermined frictional force is applied between the inner peripheral surface of the star wheel 14 and the outer peripheral surface (contact surface) of the first shaft 12. . This frictional force is set to be stronger than the force for rotating the star wheel 14 and weaker than the force for removing the locking member 22 by the rotation of the star wheel 14. With such a configuration, the star wheel 14 is provided to be rotatable around the first shaft 12 in a state where the star wheel 14 is assembled to the first shaft 12. When the locking member 22 is in a non-locking state to be described later, the locking member 22 is rotated following the first shaft 12 by the frictional force at the contact portion with the first shaft 12. If the generated frictional force is weaker than the force for rotating the star wheel 14, the star wheel 14 may idle even in a state where the locking of the locking member 22 is released. If the force of removing the locking member 22 by the rotation of the star wheel 14 is stronger, the plate member 50 of the locking member 22 moves in the left direction in FIG. There is a risk of being released.

  As shown in FIG. 2, the locking member 22 preferably has at least one claw in the star wheel 14 as the locking member 22 is rotated toward the star wheel 14 about the second shaft 20. A plate member 50 that is brought into contact with the portion 36 is provided. The electromagnet 24 is provided with a magnetic member 52 that generates an action of rotating the locking member 22 in the first rotation direction, that is, the direction away from the star wheel 14 by the magnetic force of the electromagnet 24 in the excited state. The magnetic member 52 is a metal whose main component is an iron group element such as iron, cobalt, or nickel. The magnetic member 52 is preferably a particularly unmagnetized iron plate, but may be a magnetized so-called permanent magnet. In the locking member 22, the magnetic member 52 is embedded in the synthetic resin member 54.

  The electromagnet 24 preferably includes a cylindrical coil around an iron core that is a magnetic material such as iron. When an electric current is passed through the coil, the coil is excited and generates a magnetic force (magnetic field). On the other hand, it is a well-known general electromagnet that is brought into a non-excited state when no current is passed through the coil.

  As shown in FIG. 2, the electromagnet 24 is provided corresponding to each locking member 22. The locking member 22 is provided in the vicinity of the synthetic resin member 54 in which the magnetic member 52 is embedded. The locking member 22 is configured such that a predetermined gap is provided between the magnetic member 52 and the electromagnet 24 in any of the locked state shown in FIG. 2 and the non-locked state shown in FIG. It is. This interval is preferably within a range in which the magnetic force of the electromagnet 24 can be exerted on the magnetic member 52 in the excited state of the electromagnet 24. For example, even when the electromagnet 24 and the locking member 22 are most separated from each other, the interval is designed so that the magnetic member 52 is attracted by the magnetic force of the electromagnet 24 when the electromagnet 24 is excited. That is, the interval is designed so that an attractive force that rotates the locking member 22 in the direction of separating the locking member 22 from the star wheel 14 is generated. The axis of the electromagnet 24 (the central axis of the iron core) is in a positional relationship that intersects the rotation center of the locking member 22, that is, the axis of the second shaft 20.

  As shown in FIG. 2, the locking member 22 preferably includes a snap spring (torsion coil spring) 56. The snap spring 56 biases the locking member 22 in a direction to rotate it toward the star wheel 14. The locking member 22 and the plate member 50 are preferably rotated toward the star wheel 14 by being biased by the snap spring 56 when the electromagnet 24 is in a non-excited state. The plate member 50 is in a locked state in which at least one of the plurality of claw portions 36 provided on the star wheel 14 is locked. On the other hand, in the excited state of the electromagnet 24, the locking member 22 and the plate member 50 are moved in the first rotation direction around the second shaft 20, that is, the star, against the biasing force of the snap spring 56 by the magnetic force of the electromagnet 24. It is rotated in a direction away from the wheel 14. Then, the locking member 22 is stopped at a position where the force (attraction force) for attracting the magnetic member 52 according to the magnetic force by the electromagnet 24 and the urging force of the snap spring 56 are balanced. In other words, the claw portion 36 is unlocked by the plate member 50 and unlocked.

  As shown in FIG. 2, the plurality of electromagnets 24 and the locking members 22 corresponding to the electromagnets 24 are preferably a plurality of electromagnets 24 and the locking members 22 belonging to the first group, and the plurality of electromagnets 24 belonging to the second group. The electromagnet 24 and the locking member 22 are disposed with a phase difference of 90 ° in the circumferential direction around the axis of the first shaft 12 (that is, at a position that forms an angle of 90 ° with each other). Preferably, when a numerical value from 1 to n (corresponding to the electromagnet 24 at the other end) is attached from the electromagnet 24 provided at the end to the other end side among the plurality of electromagnets 24, an odd number is assigned. A plurality of electromagnets 24 belong to the first group, and a plurality of electromagnets 24 with even numbers belong to the second group. That is, in the music box 10 of the present embodiment, preferably, the electromagnets 24 respectively corresponding to the star wheels 14 adjacent to each other are alternately arranged with a phase difference of 90 ° in the circumferential direction around the axis of the first shaft 12. It is arranged. By adopting such a configuration, the arrangement space of the performance mechanism unit 100 (particularly, the plurality of electromagnets 24) in the music box 10 can be made as small as possible, and the apparatus can be miniaturized.

  FIG. 5 is a diagram illustrating a specific operation of the performance mechanism unit 100 in the music box 10 configured as described above. During performance by the music box 10, the first shaft 12 and the third shaft 26 are always rotated around the respective axis centers synchronously by driving the motor 32, as indicated by arrows in FIG. 2. The first shaft 12 and the third shaft 26 are driven to rotate in the opposite directions. Preferably, the first shaft 12 has a claw portion 36 provided on the star wheel 14 and the vibration valve 18 of the diaphragm 16. It is rotated in the direction of flipping from below to above. The third shaft 26 is rotated in the direction in which the star wheel 14 is rotationally driven, that is, in the direction indicated by the arrow in FIG. 2, in a state where the outer peripheral teeth 40 of the sun wheel 28 and the gear portion 38 of the star wheel 14 are engaged with each other. . Since the plurality of sun wheels 28 are provided so as not to rotate relative to the third shaft 26, during the performance by the music box 10, each of the sun shafts 28 always rotates around the respective axis as the third shaft 26 rotates around the axis. Has been rotated.

  FIG. 2 illustrates the operation when the locking member 22 is in the locked state. As shown in FIG. 2, when the corresponding electromagnet 24 is not energized and the electromagnet 24 is in a non-excited state, the plate member 50 of the locking member 22 is biased by the snap spring 56. . Thereby, the locking member 22 is turned to the star wheel 14 side, and is brought into a locked state in which at least one of the plurality of claw portions 36 provided on the star wheel 14 is locked. That is, the tip end portion of the plate member 50 is brought into contact with the rotation direction side (the rotation progress side) of the first shaft 12 in at least one of the plurality of claw portions 36. As described above, the star wheel 14 is configured to be rotated following the first shaft 12 by the frictional force at the contact portion with the first shaft 12. In the state shown in FIG. 2, the locking member 22 is in the locked state, so that the follow-up rotation of the star wheel 14 with respect to the first shaft 12 is prevented against the frictional force at the contact portion. In other words, the contact surface between the star wheel 14 and the first shaft 12 is light while the phase of the star wheel 14 around the axis of the first shaft 12 (the positional relationship with respect to the vibration valve 18 and the like) is fixed. They are in a state where they are relatively rotated while sliding with a load. In such a state, the gear portion 38 of the star wheel 14 is in a position where it does not mesh with the outer peripheral teeth 40 of the sun wheel 28, and the rotation of the sun wheel 28 does not affect the rotation of the star wheel 14.

  FIG. 5 illustrates the operation when the locking member 22 is switched from the locked state to the non-locked state. When the electromagnet 24 is energized from the state shown in FIG. 2, the energized electromagnet 24 is in an excited state. Then, the plate member 50 of the locking member 22 rotates in a direction (first rotation direction) away from the star wheel 14 about the second shaft 20 against the biasing force of the snap spring 56 by the magnetic force of the electromagnet 24. Be made. Thereby, it is set as the non-locking state from which the latching of the nail | claw part 36 by the plate member 50 is cancelled | released. That is, the star wheel 14 is brought into a state in which the star wheel 14 is rotated following the first shaft 12 by the frictional force at the contact portion with the first shaft 12.

  FIG. 5 illustrates an operation in which the claw portion 36 of the star wheel 14 plays the sound by playing the vibration valve 18 of the diaphragm 16. As shown in FIG. 5, when the locking member 22 is positioned, the locking member 22 is in a non-locking state, and the locking of the claw portion 36 by the plate member 50 is released. Thereafter, the star wheel 14 is rotated following the first shaft 12 by the frictional force at the contact portion with the first shaft 12. Then, as shown in FIG. 5, in the vicinity of the phase where one claw portion 36 of the plurality of claw portions 36 is brought into contact with the vibration valve 18 of the diaphragm 16, the rotation direction side adjacent to the claw portion 36 (that is, the rotation direction). The gear portion 38 corresponding to the claw portion 36 (provided with a phase difference of 90 °) is meshed with the outer peripheral teeth 40 of the sun wheel 28. In this state, the rotation of the sun wheel 28 drives the star wheel 14 in the direction indicated by the arrow A in FIG. 5, that is, the direction in which the claw portion 36 flips the vibration valve 18 of the diaphragm 16 upward from below. By such an operation, the vibration valve 18 is repelled by the claw portion 36, and the sound of the scale corresponding to the vibration valve 18 is played. After the vibration valve 18 is bounced in this way, the star wheel 14 is further rotated following the first shaft 12 so that the gear portion 38 and the outer peripheral teeth 40 of the sun wheel 28 are not engaged again. In the transition process from the state shown in FIG. 5 to the state where the gear portion 38 and the outer peripheral teeth 40 do not mesh, the energization of the electromagnet 24 is stopped and the electromagnet 24 is brought into a non-excited state. As a result, the locking member 22 is rotated toward the star wheel 14 by the urging of the snap spring 56, and returned to the state shown in FIG.

  The music box 10 according to the present embodiment moves the frame 30b in the extending direction (longitudinal direction) of the vibration valve 18 with respect to the casing, so that the distance between each vibration valve 18 and the corresponding star wheel 14 in the vibration plate 16 is increased. A moving device 80 to be changed is provided. FIG. 7 is a schematic cross-sectional view along the extending direction (longitudinal direction) of the vibration valve 18 for the performance mechanism unit 100 of the music box 10 including the moving device 80. In the music box 10, a pedestal 29 to which the diaphragm 16 is attached is fixed to a lower frame fixed to a housing (not shown). That is, the diaphragm 16 is provided in a fixed position with respect to the lower frame and is indirectly fixed to the housing. The frame 30b that holds the first shaft 12 and the third shaft 26 in a rotatable manner is provided so as to be movable in the extending direction of the vibration valve 18 with respect to the housing by the moving device 80.

  As shown in FIG. 7, the moving device 80 preferably includes a spring 82 as an urging member that urges the frame 30 b toward the diaphragm 16 with respect to the lower frame (that is, the housing). Yes. For example, as shown in FIG. 7, the frame 30 b is provided so as to be slidable (translatable) in the extending direction of the vibration valve 18 with respect to the frame 30 c provided to be fixed to the lower frame. A spring 82 is provided between the frame 30b and the frame 30c. The moving device 80 preferably includes a cam mechanism 84 that pushes back the frame 30b in the direction away from the diaphragm 16 against the urging force of the spring 82. An adjustment shaft 88 that is integrally rotated about the same axis as the adjustment knob 86 is provided. The cam mechanism 84 is attached to the adjustment shaft 88 so as to be rotated integrally with the rotation of the adjustment shaft 88. The adjustment shaft 88 is held in parallel with the first shaft 12 so as to be rotatable about the shaft center with respect to the lower frame. When the adjustment knob 86 is turned, the adjustment shaft 88 is rotated about the axis. As the adjustment shaft 88 rotates, the cam mechanism 84 is integrally rotated.

  The moving device 80 preferably includes a plurality of springs 82 and a cam mechanism 84. Each spring 82 and cam mechanism 84 are disposed at corresponding positions in the axial direction of the adjustment shaft 88, that is, in the axial direction of the first shaft 12. In other words, a pair of springs 82 and cam mechanisms 84 are disposed at substantially equal positions in the axial direction of the adjustment shaft 88. Preferably, springs 82 and cam mechanisms 84 are provided at both ends of the first shaft 12 in the axial direction.

  FIG. 7 is a diagram illustrating a state in which the frame 30b is moved in the extending direction of the vibration valve 18 by the moving device 80 with respect to the lower frame (housing). In FIG. 7, a part of the vicinity of the cam mechanism 84 (a part surrounded by a broken line) is shown in an enlarged manner. The cam mechanism 84 is a well-known mechanism that has a peripheral shape whose distance from the rotation axis is not constant, and gives movement to other members in the peripheral shape by rotation. That is, in FIG. 7, the distance between the contact portion 90 provided integrally with the frame 30b and the axis of the adjustment shaft 88 is indicated by D. From the state shown in FIG. When it is rotated 90 ° clockwise, the distance D between the contact portion 90 and the axis of the adjustment shaft 88 is shortened. That is, the frame 30b is pushed out of the casing by the biasing force of the spring 82, and is moved in the extending direction of the vibration valve 18 (approaching the vibration valve 18). Further, when the adjustment shaft 88 is rotated 90 ° clockwise toward the paper surface, the distance D between the contact portion 90 and the axis of the adjustment shaft 88 is further shortened. That is, the frame 30b is pushed out further with respect to the housing by the biasing force of the spring 82, and is further moved in the extending direction of the vibration valve 18 (further closer to the vibration valve 18).

  As described above, the diaphragm 16 is fixed to the lower frame (housing). Therefore, the position of the plurality of vibration valves 18 is fixed with respect to the lower frame. When the frame 30b is moved in the extending direction of the vibration valve 18 with respect to the lower frame by the moving device 80, the distance between each vibration valve 18 and the corresponding star wheel 14 is changed. In particular, the distance between each vibration valve 18 and the claw portion 36 in the corresponding star wheel 14 is changed. Thereby, the lap amount La of the claw part 36 with respect to each vibration valve 18 changes. The lap amount La corresponds to the size of the portion of the vibration valve 18 that is inside the rotation outer diameter when the rotation outer diameter of the claw portion 36 (indicated by a one-dot chain line in FIG. 8) is assumed. When the lap amount La of the claw portion 36 with respect to each vibration valve 18 changes, the sound volume when the vibration valve 18 is bounced by the claw portion 36 changes. In other words, the volume increases as the lap amount La increases. In other words, the closer the distance between each vibration valve 18 and the corresponding claw portion 36 is, the higher the volume when the vibration valve 18 is bounced. That is, in this embodiment, the moving device 80, the spring 82, and the cam mechanism 84 correspond to a volume adjusting mechanism that adjusts the volume of the music box 10 by changing the relative distance between the vibration valve 18 and the claw portion 36. . The moving amount of the frame 30b relative to the lower frame by the moving device 80, that is, the moving distance of the vibrating valve 18 in the extending direction is preferably about 0.1 to 1.0 mm. The music box 10 preferably includes a distance sensor 66 (see FIG. 6) that detects a relative distance between the vibration valve 18 and the claw portion 36 when the vibration valve 18 is in contact with the music valve 10. The distance sensor 66 may detect the amount of movement of the frame 30b relative to the lower frame by the moving device 80. The amount of rotation of the cam mechanism 84 may be detected. In other words, the distance sensor 66 is a volume sensor that detects the volume of the music box 10 according to the relative distance between the vibration valve 18 and the claw portion 36.

  In the music box 10, preferably, as shown in FIG. 8, the contact position between the vibration valve 18 and the claw portion 36 is a straight line connecting the contact position and the rotation center C <b> 1 of the first shaft 12. The position is an angle φ with respect to 12 horizontal directions (direction parallel to the bottom surface of the housing). This angle φ is preferably in the range of 45 ° ± 10 °. When the angle φ is smaller than such a range, the volume change according to the change in the lap amount La becomes large, and there is a possibility that appropriate adjustment becomes difficult. On the other hand, when the angle φ is larger than the above range, the volume change corresponding to the change in the lap amount La becomes small, and the volume may not be adjusted.

  FIG. 6 is a functional block diagram for explaining a main part of a control function provided in the ECU 60 for controlling excitation or non-excitation of each of the plurality of electromagnets 24 of the music box 10. The score database 62 shown in FIG. 6 stores a plurality of score data respectively corresponding to songs to be played by the music box 10. The musical score database 62 may be stored in a storage medium such as a well-known SD card (Secure Digital Card), and the ECU 60 may be able to read data recorded in the storage medium. The musical score data is, for example, data in MIDI (Musical Instrument Digital Interface) format, and for each of a plurality of predetermined types of musical instruments, a plurality of tracks (for example, a sound output timing and a scale corresponding to the musical instrument are defined). Channel). The music box 10 of the present embodiment performs performance control described in detail below based on, for example, the output timing and scale of a track (channel) corresponding to a guide melody in MIDI data, that is, a main melody.

  The lock release timing determination unit 42 determines the timing for releasing the lock of the claw 36 in the star wheel 14 by each of the plurality of lock members 22. In other words, the timing for switching the excitation or non-excitation of the electromagnet 24 corresponding to each of the plurality of locking members 22 (the timing for executing or stopping the energization of the electromagnet 24) is determined. For example, in the performance of a song corresponding to predetermined score data among a plurality of score data stored in the score database 62, the determination is performed based on the sound output timing and scale determined in the score data. Specifically, in order to play the plurality of vibration valves 18 corresponding to each scale at the output timing determined in the musical score data, the timing for releasing the locking of the claw portion 36 in the star wheel 14 by the locking member 22 is determined. To do. When the rotation speed of each of the first shaft 12 and the third shaft 26 is set to a constant value, the locking by the locking member 22 corresponding to each star wheel 14 is released and the claw portion 36 of the star wheel 14 responds. The time lag until the vibrating valve 18 is bounced is obtained in advance. The lock release timing determination unit 42 performs the determination based on the musical score data to be played. In the score data, the output timing of the scale corresponding to each vibration valve 18 is determined. The determination is made so that the locking of the claw portion 36 in the star wheel 14 by the locking member 22 corresponding to the vibration valve 18 is released before the time corresponding to the time lag before the output timing. In other words, the lock release timing determination unit 42 determines to switch the electromagnet 24 from the excited state to the non-excited state after a predetermined time after the electromagnet 24 is switched from the non-excited state to the excited state.

  The electromagnet excitation / non-excitation control unit 44 switches between excitation and non-excitation of each of the plurality of electromagnets 24 based on the determination result by the lock release timing determination unit 42. That is, based on the determination result by the locking release timing determination unit 42, control is performed to execute or stop the energization of each of the plurality of electromagnets 24. Specifically, when the timing for releasing the locking of the claw 36 in the star wheel 14 by the locking member 22 is determined by the locking release timing determination unit 42, the corresponding electromagnet 24 is moved from the non-excited state at that timing. Switch to the excited state. That is, energization of the electromagnet 24 is started at such timing. The electromagnet excitation / de-excitation control unit 44 preferably switches the electromagnet 24 from the excited state to the non-excited state after a predetermined time has elapsed after switching the electromagnet 24 from the non-excited state to the excited state. That is, energization of the electromagnet 24 is stopped at such timing.

  The motor output calculation unit 46 calculates the output torque (motor torque, output shaft torque) of the motor 32 when the music box 10 is played. Preferably, the current (drive current) supplied to the motor 32 is calculated. Basically, the output torque of the motor 32 is calculated based on the tempo determined in the musical score data in the performance of a song corresponding to the predetermined musical score data among the plurality of musical score data stored in the musical score database 62. That is, the current supplied to the motor 32 is calculated based on the tempo defined in the score data so that the output shaft of the motor 32 is always rotated at a constant speed. Preferably, the music box 10 includes a rotation sensor 65 that detects the output rotation speed of the motor 32. The rotation sensor 65 is preferably a well-known rotary encoder. The rotation sensor 65 may detect the rotation speed of the first shaft 12 or the rotation speed of the third shaft 26. The motor output calculation unit 46 preferably feedback-controls the rotational speed of the motor 32 based on the formula (1) described later. In such feedback control, control described in detail below is performed so that the output shaft of the motor 32 is always rotated at a constant speed.

  The motor output calculation unit 46 calculates the output torque of the motor 32 when the claw portion 36 provided in the star wheel 14 flips the vibration valve 18. Preferably, the current (drive current) supplied to the motor 32 when the claw portion 36 flips the vibration valve 18 is calculated. In other words, at least the claw portion 36 provided on the star wheel 14 comes into contact with the vibration valve 18 (contacts the lower side of the vibration valve 18), and then the vibration valve 18 is flipped away (not contacted). ) To calculate the current supplied to the motor 32. Preferably, the current supplied to the motor 32 when the claw portion 36 flips the vibration valve 18 is set to a value larger than a steady value based on the tempo of the musical score data. Preferably, it is a value obtained by adding an addition amount corresponding to the type of sound played when the claw portion 36 plays at least one vibration valve 18 to a steady value based on the tempo of the musical score data.

The motor output calculation unit 46 preferably has a motor 32 based on the tempo of the musical score data according to the type of sound played by the pawl unit 36 playing the at least one vibration valve 18 from a predetermined relationship. The amount of addition to the output torque is calculated. Preferably, with respect to the current supplied to the motor 32, an amount of current addition (added current value) I _FF with respect to a steady value based on the tempo of the score data is calculated. In other words, the addition amount I _FF for the amount of current supplied to the motor 32 while the claw portion 36 provided in the star wheel 14 does not flip the vibration valve 18 is calculated. The type of sound that is played when the claw portion 36 plays at least one vibration valve 18 is determined by the number of vibration valves 18 that are simultaneously played, the scale corresponding to each vibration valve 18 that is played, the volume of the music box 10, and the like. . That is, the motor output calculation unit 46 preferably has a predetermined relationship, such as the number of vibration valves 18 that are simultaneously played by the claw portions 36, the scale corresponding to each vibration valve 18 that is played, the volume of the music box 10, and the like. Based on the above, the addition amount I _{FF of the} current supplied to the motor 32 is calculated. Preferably, the relationship is determined such that the amount of addition I _FF increases as the number of vibration valves 18 that the claws 36 simultaneously play increases. It is determined that the addition amount I _FF increases as the scale corresponding to the oscillating valve 18 to be played is higher. It is determined that the addition amount I _FF increases as the volume of the music box 10 adjusted by the volume adjustment mechanism increases. That is, it is determined that the addition amount I _FF increases as the relative distance between the vibration valve 18 and the claw portion 36 detected by the distance sensor 66 _decreases .

The music box 10 preferably has at least one of the number of vibration valves 18 that the claw portions 36 play simultaneously, the scale corresponding to the vibration valve 18 that the claw portions 36 play, and the volume of the music box 10 that is adjusted by the volume adjustment mechanism. A table 64 is provided for storing the relationship with the amount of addition of current supplied to the motor 32. FIG. 9 shows an example of the table 64. In the table 64 shown in FIG. 9, for each vibration valve 18 (respective scale), for example, the values A to U corresponding to the case where the volume of the music box 10 is large, the case where the music box 10 is medium, and the case where the volume is small, respectively. It has been established. The values A to U preferably correspond to an addition amount (addition current value) I _FF when the claw portion 36 flips each vibration valve 18. For example, when the volume of the music box 10 is high, the addition amount I _FF when playing the vibrating valve 18 corresponding to the scale of B is B. When the claw portion 36 plays a plurality of vibration valves 18 at the same time, preferably, the sum of the values determined in the table 64 of FIG. 9 corresponding to each vibration valve 18 is calculated as the addition amount I _FF . For example, the addition amount I _FF when simultaneously playing the vibration valves 18 corresponding to the scales of de, les, mi, and fa in a state where the volume of the music box 10 is high is A + B + C + D.

The motor output control unit 48 controls the output of the motor 32 when the music box 10 is played. That is, the output of the motor 32 is controlled based on the output torque of the motor 32 calculated by the motor output calculator 46. Preferably, the drive current supplied to the motor 32 is controlled. For example, the duty ratio of the drive current supplied to the motor 32 is controlled. Specifically, the current calculated by the motor output calculation unit 46 is supplied to the motor 32. Preferably, feedback control is performed on the current (drive current) I _M supplied to the motor 32 based on the following equation (1). I _M ⁻¹ shown in the equation (1) is a current (drive current) supplied to the motor 32 in the previous control cycle. I _FF is an addition value calculated by the motor output calculation unit 46 as described above. C _P is a constant of the proportional term. e is a deviation of the rotational speed of the motor 32. That is, the difference between the target rotation speed N ^* of the motor 32 and the actual rotation speed N _M detected by the rotation sensor 65. C _I is an integral term constant. The target rotational speed N ^* of the motor 32 corresponds to, for example, a steady value based on the tempo of the musical score data to be played.

I _M = I _M ⁻¹ + I _FF + C _P · e + C _I · ∫edt (1)

The addition amount I _{FF in the} equation (1) is set to 0 while the claw portion 36 does not play the vibration valve 18. When the claw portion 36 plays the vibration valve 18, the motor output calculation portion 46 calculates as described above prior to that. That is, in this embodiment, (1) by the feedback control based on the expression, while the claw portions 36 do not play a vibrating valve 18 constant value based on the tempo of the musical score data speed N _M of the motor 32 is playing object It is controlled to become. When the claw portion 36 plays the vibration valve 18, the addition amount I _FF calculated according to the type of sound played by the claw portion 36 playing the at least one vibration valve 18 corresponds to the steady value. Added to the current. That is, based on the addition amount I _FF calculated by the motor output calculation unit 46, feedforward control of the output torque of the motor 32 (electric power supplied to the motor 32) is performed. Therefore, when the claw part 36 plays the vibration valve 18, it is possible to suitably suppress the torque being insufficient and the rotation delay of the motor 32 from occurring. That is, when the claw portion 36 plays the vibration valve 18, the rotation speed of the motor 32 can be maintained at a constant value (a value approximately equal to a steady value based on the tempo of the musical score data to be played).

The motor output control unit 48 preferably performs control to gradually increase the output torque of the motor 32 (current supplied to the motor 32) based on the addition amount I _FF calculated by the motor output calculation unit 46. FIG. 10 is a diagram illustrating an example of the gradual increase control of the output torque of the motor 32. In the example shown in FIG. 10, the control when the vibration valve 18 corresponding to the scale of the musical instrument 10 is played in the state where the volume of the music box 10 is high in the example shown in FIG. 9 is shown. The time point t _{0 corresponds} to the time point when the claw portion 36 contacts the vibration valve 18, and the time point t _A corresponds to the time point when the vibration valve 18 has finished being played. The time point t ₀ is determined by a time lag from when the locking by the locking member 22 is released to when the corresponding vibration valve 18 is bounced by the claw portion 36 of the star wheel 14. The time from the time point t ₀ to the time point t _A is, for example, a value obtained experimentally in advance. As shown in FIG. 10, for example, when the claw portion 36 plays the vibration valve 18, the motor output control unit 48 finishes playing the vibration valve 18 from the time t ₀ when the claw portion 36 contacts the vibration valve 18. During the period up to t _A , the addition amount I _FF for the current supplied to the motor 32 is gradually increased from 0 to the value A calculated by the motor output calculation unit 46. Alternatively, the addition amount I _FF for the current supplied to the motor 32 may be gradually increased from 0 to a value calculated by the motor output calculation unit 46 in a quadratic or exponential manner. In such control, the addition amount I _FF for the current supplied to the motor 32 is represented by a function a (t) of time t, where 0 is the lower limit value and the value A calculated by the motor output calculation unit 46 is the upper limit value. (2) is expressed as follows.

I _FF = a (t) (2)

The motor output control unit 48 preferably outputs the output torque of the motor 32 (supplied to the motor 32) based on the addition amount I _FF calculated by the motor output calculation unit 46 corresponding to each vibration valve 18 that is simultaneously played. Current) is gradually increased or decreased. For example, as shown in FIG. 10, when the corresponding claw portions 36 simultaneously play the vibration valves 18 corresponding to the scales of “do”, “fa”, and “si”, the amount of addition I _FF with respect to the current supplied to the motor 32 is calculated for each vibration. Corresponding to the valve 18, the motor output calculation unit 46 gradually increases proportionally up to the sum of the values A, D, and G. Alternatively, it may be gradually increased or decreased in a quadratic or exponential manner. In such control, the addition amount I _{FF with} respect to the current supplied to the motor 32 has an upper limit value A calculated by the motor output calculation unit 46 and a lower limit value 0 for the vibration valve 18 corresponding to the scale of the sound. A function a (t) of time t, and a function d (t) of time t with the value D calculated by the motor output calculation unit 46 for the vibration valve 18 corresponding to the scale of fa as the upper limit value and 0 as the lower limit value , The function G (t) of time t with the value G calculated by the motor output calculation unit 46 for the vibration valve 18 corresponding to the scale of the shim as the upper limit value and 0 as the lower limit value, It is expressed as follows.

I _FF = a (t) + d (t) + g (t) (3)

  FIG. 11 is a flowchart for explaining a main part of an example of motor output torque control by the ECU 60 of the music box 10 and is repeatedly executed at a predetermined cycle.

First, in step (hereinafter, step is omitted) S1, the star wheel 14 by the locking member 22 corresponding to a predetermined vibration valve 18 based on the sound output timing and scale determined in the musical score data to be played. It is determined whether or not the timing for releasing the locking of the claw portion 36 is determined. If the determination in S1 is negative, in S7, the drive current supplied to the motor 32 is set to a steady value based on the tempo of the musical score data to be played, and then the processing from S6 is executed. However, if the determination in S1 is affirmative, in S2, the electromagnet 24 corresponding to the locking member 22 determined to be unlocked in S1 is energized, and the claw portion 36 of the locking member 22 is energized. The lock is released. When the timing for releasing the locking of the plurality of locking members 22 is determined in S1, the locking of the claw portions 36 by the plurality of locking members 22 is simultaneously released in S2. Next, in S3, the scale corresponding to the vibration valve 18 that the claw portion 36 corresponding to the unlocked locking member 22 repels, the number of vibration valves 18 that the claw portion 36 simultaneously repels, and the detection result of the distance sensor 66. Information such as the volume of the music box 10 corresponding to is acquired. Next, in S4, from the table 64 as shown in FIG. 9, the scale corresponding to the vibration valve 18 that the claw portion 36 repels acquired in S3, the number of vibration valves 18 that the claw portion 36 repels simultaneously, and the music box 10 A value corresponding to information such as the volume of the sound is acquired. Next, in S5, based on the value acquired from the table 64 in S4, an addition amount I _FF for the drive current supplied to the motor 32 when the claw portion 36 flips the vibration valve 18 is determined. Next, in S6, after the drive current supplied to the motor 32 is controlled based on the addition amount I _FF determined in S5 and the steady value based on the tempo of the musical score data to be played, this routine is performed. Is terminated. In the above control, S1 is the operation of the unlocking timing determination unit 42, S2 is the operation of the electromagnet excitation / non-excitation control unit 44, S3 to S5 are the operation of the motor output calculation unit 46, S6 and S7 corresponds to the operation of the motor output control unit 48, respectively.

  According to this embodiment, the ECU 60 controls the motor when the claw portion 36 plays the vibration valve 18 according to the type of sound played by the claw portion 36 of the star wheel 14 playing the at least one vibration valve 18. Since the output torque of the motor 32 is controlled, the load of the motor 32 when the claw portion 36 flips the vibration valve 18 is predicted in advance in consideration of the characteristics of each of the plurality of vibration valves 18, and the output torque of the motor 32 is estimated. By controlling this, the rotational speed of the motor 32 can be kept constant regardless of the vibration valve 18 that the claw portion 36 repels. That is, it is possible to provide the music box 10 that suitably suppresses the occurrence of a deviation in the performance tempo.

  The preferred embodiments of the present invention have been described in detail with reference to the drawings. However, the present invention is not limited to these embodiments, and may be implemented in other modes.

  For example, in the above-described embodiment, as shown in FIG. 9, the scale corresponding to the vibration valve 18 that the claw portion 36 repels, the number of vibration valves 18 that the claw portion 36 repels simultaneously, and the music box that is adjusted by the volume control mechanism. The aspect of controlling the output torque of the motor 32 when the claw portion 36 flips the vibration valve 18 using the table 64 that stores the relationship between at least one of the ten sound volumes and the output torque of the motor 32 has been described. Further, simpler control may be performed. For example, a table 64 that stores the relationship between the number of vibration valves 18 that the claw portions 36 simultaneously play and the output torque of the motor 32 is used, and the claw portions 36 are exclusively based on the number of vibration valves 18 that the claw portions 36 simultaneously play. May control the output torque of the motor 32 when flipping the vibration valve 18.

  The music box 10 may be provided with a cam mechanism of a form different from the cam mechanism 84 illustrated in FIG. For example, a cam mechanism having a polygonal shape (for example, a hexagonal shape) having different distances from the axis of the adjustment shaft 88 when viewed in the axial direction may be provided. Further, an oval cam mechanism may be provided when viewed in the axial direction. In the cam mechanism 84 illustrated in FIG. 7, the distance between each vibration valve 18 and the corresponding star wheel 14 can be continuously changed. The cam mechanism 84 includes a cam mechanism that changes the distance stepwise. There may be. In order to switch the volume of the music box between two levels, large and small, a cam mechanism that changes the distance between each vibration valve 18 and the corresponding star wheel 14 in two levels may be provided. A motor that drives the cam mechanism 84 may be provided, and a mechanism that automatically changes the relative distance between the vibration valve 18 and the claw portion 36 by driving the cam mechanism 84 by the motor may be provided. The relative distance between the vibration valve 18 and the claw portion 36 may be automatically changed based on MIDI data or the like which is musical score data.

  The moving device 80 vibrates the frame 30b with respect to the lower frame against a biasing force of the spring 82 and a spring 82 that urges the frame 30b toward the diaphragm 16 with respect to the lower frame (housing). Although the cam mechanism 84 that pushes back in the direction away from the plate 16 is provided, a configuration in which the spring 82 and the cam mechanism 84 are replaced is also conceivable. That is, a spring 82 that biases the frame 30b away from the diaphragm 16 with respect to the lower frame, and a direction in which the frame 30b approaches the diaphragm 16 relative to the lower frame against the biasing force of the spring 82. A cam mechanism 84 for pushing back may be provided.

  The locking member 22 may include a permanent magnet as a magnetic member that generates an action of rotating the locking member 22 in the first rotation direction by the magnetic force of the electromagnet 24 when the electromagnet 24 is excited. The permanent magnet is preferably provided integrally with the plate member 50 at a position where a repulsive force (repulsive force between the same kind of magnetic poles) is generated with the electromagnet 24 when the electromagnet 24 is in an excited state. The synthetic resin member 54 may be insert-molded. The plate member 50 of the locking member 22 opposes the bias by the snap spring 56 due to the magnetic force of the electromagnet 24, that is, the repulsive force between the electromagnet 24 and the permanent magnet. Thereby, the locking member 22 is rotated in a direction (first rotation direction) away from the star wheel 14 about the second shaft 20, and the locking of the claw portion 36 by the plate member 50 is released. The non-locking state.

  The number of claw portions 36 provided on the star wheel 14 is not limited to four, and may not be provided every 90 ° in the circumferential direction. The gear portion 38 in the star wheel 14 does not necessarily have to be provided at a position corresponding to the claw portion 36, and may be provided at a position having a different phase in the circumferential direction. The plurality of electromagnets 24 and the locking member 22 belonging to the first group and the plurality of electromagnets 24 and the locking member 22 belonging to the second group are 90 ° in the circumferential direction around the axis of the first shaft 12. For example, all the electromagnets 24 may be arranged in a line on the same plane. Conversely, in the case where five or more claw portions 36 are provided in the circumferential direction of the star wheel 14, the plurality of electromagnets 24 and the locking members 22 according to the number of claw portions 36 provided on the star wheel 14. However, it may be arranged at a position corresponding to three or more phases with a predetermined phase difference in the circumferential direction around the axis of the first shaft 12. As a configuration for locking the star wheel 14, two or more locking members 22 may be provided corresponding to each star wheel 14. The ECU 60 may be connected to a communication line such as the Internet, and the score data may be downloaded via the communication line and stored in the score database 62. In addition, the shape of the star wheel 14, the configuration of the locking member 22 (the shape of the plate member 50), the relative position of each configuration, and the like are appropriately changed according to the design of the music box. For example, the gear portion 38 does not necessarily have to be provided with two teeth, and it is sufficient that the claw portion 36 is driven from the sun wheel 28 by a sufficient distance and time for flipping the corresponding vibration valve 18. Alternatively, a gear portion having three or more teeth may be provided.

  In addition, although not illustrated one by one, the present invention is implemented with various modifications within a range not departing from the gist thereof.

  10: music box, 16: diaphragm, 18: vibration valve, 32: motor, 36: claw part, 60: ECU, 64: table, 80: moving device, 82: spring, 84: cam mechanism

Claims (5)

A diaphragm having a plurality of vibration valves formed with different characteristics corresponding to different scales,
According to the music data that is arranged corresponding to each of the vibration valves and the timing for sounding is determined, the claw portion that flips the vibration valve corresponding to the sound to be sounded by driving a motor,
A control unit for controlling the driving of the motor,
The control unit, when the claw unit plays at least one of the vibration valve at the timing of sounding the sound defined in the music data, according to the type of sound played by the vibration valve is played, A music box that controls output torque of the motor. When the control unit is configured to play the vibration valve at the timing of sounding the sound determined in the music data, the claw unit is simultaneously operated according to the number of sounds to be played with the timing set at the same time. 2. The music box according to claim 1, wherein the number of the vibration valves to be flipped increases the output torque of the motor when the claw portion flips the vibration valves. The control unit, when playing the vibration valve at the timing of sounding the sound according to the music data, according to the scale of the sound to be played, the higher the scale of the vibration valve that the nail part plays, the higher the nail The music box according to claim 1, wherein the portion increases an output torque of the motor when the vibration valve is flipped. A volume adjustment mechanism for adjusting the volume of the music box by changing the relative distance between the vibration valve and the claw portion;
When the control unit plays the vibration valve at the timing of sounding the sound according to the music data, the volume of the music box adjusted by the volume adjustment mechanism is increased according to the volume of the played sound. The music box according to any one of claims 1 to 3, wherein the pawl portion increases an output torque of the motor when the vibration valve is flipped. At least one of the number of the vibration valves that the claw part simultaneously repels, the scale corresponding to the vibration valve that the claw part repels, and the volume of the music box that is adjusted by the volume adjustment mechanism, and the output torque of the motor With a table that stores the relationship between
The control unit, based on the relationship stored in the table, the number of the vibration valves that the claw part simultaneously plays, the scale corresponding to the vibration valve that the claw part plays, and the music box that is adjusted by the volume control mechanism 2. The music box according to claim 1, wherein the output torque of the motor when the claw part flips the vibration valve is controlled based on at least one of the sound volumes.

Images