JP6011661B2 - Pedal device for electronic percussion instruments - Google Patents

Description

  The present invention relates to a pedal device for an electronic percussion instrument.

  Conventionally, pedal devices for electronic percussion instruments are known. In the pedal device of the following Patent Document 1, a footboard is pivotally supported on a base, a weight is provided at the free end of the footboard, and a tension coil spring is provided at the free end of the footboard. And when the footboard is stepped on, it aims to realize a feeling of stepping down close to an acoustic drum by the inertial force due to the weight and the increase in the load due to the tension coil spring.

JP 2008-145464 A

  However, in the pedal device of Patent Document 1, since the weight is provided on the footboard, it is necessary to provide the weight so as not to hinder the operation of the footboard, and the size and shape are greatly limited. In addition, the amount of displacement of the weight depends on the amount of displacement of the portion attached to the footboard. Accordingly, the degree of freedom in adjusting the inertial force by the weight is small, and it is not easy to design so as to obtain a desired inertial force. Therefore, there is room for improvement in bringing the feeling of depression closer to a natural one.

  Moreover, in the pedal apparatus of the said patent document 1, when a footboard is stepped on, it will be in a contact state with respect to a base, and the stepping end position will be controlled. At that time, a downward impact is applied to the floor surface via the base, and vibration and impact sound are generated. In particular, in an electronic drum, these vibrations and impact sounds are easily felt in the way compared to an acoustic drum. Furthermore, there is room for improvement because the feel at the end of the step is different from that of the acoustic drum.

The present invention has been made to solve the above-described problems of the prior art, and an object of the present invention is to provide a pedal device for an electronic percussion instrument that can alleviate the impact on the floor and reduce the generated impact sound. There is to do.

In order to achieve the above object, a pedal device for an electronic percussion instrument according to claim 1 of the present invention includes a base (10) placed on a floor surface (26) and one end (20a) with respect to the base. Is supported by a footboard (20) that is rotatable by a stepping operation, and one end (21a) is pivoted on a pivoting fulcrum (23) provided near the other end (20b) of the footboard. The arm (21) that is supported and rotatable, has a mass part, and an engaging part that engages with the other end of the arm so as to be rotatable, and is rotated by a stepping operation of the footboard. anda mass moving mechanism unit for moving the parts by the displacement of the arms, the mass portion moving mechanism portion, the depression of the foot board, the engaging portion is, before Symbol footboard The one end of the footboard across the other end By moving mainly horizontally on opposite sides, characterized in that it is configured to move the parts by weight.

  In addition, the code | symbol in the said parenthesis is an illustration.

According to the first aspect of the present invention, it is possible to mitigate the impact on the floor surface and reduce the generated impact sound .

It is the top view and bottom view of the pedal apparatus for electronic percussion instruments which concern on one embodiment of this invention. It is sectional drawing which follows the AA line of Fig.1 (a). It is a schematic diagram of the system of the link mechanism of this Embodiment and a modification. It is sectional drawing which shows typically the structure of the stopper part of this Embodiment and a modification. It is a schematic diagram which shows the modification of the mechanism which controls the displacement track | orbit of a mass part. It is a figure which shows the modification of the arrangement | positioning aspect of the coil spring for maintaining the system of a link mechanism in an equilibrium state in a non-operation state.

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

  1A and 1B are a plan view and a bottom view, respectively, of a pedal device for an electronic percussion instrument according to an embodiment of the present invention. 2A and 2B are cross-sectional views taken along line AA in FIG.

  This pedal device is configured as a kick pedal used for an electronic bass drum as an electronic percussion instrument, for example. The pedal device is installed on the floor surface 26, and a performance operation is performed by stepping on the foot board 20. 2A and 2B respectively show a state in which the footboard 20 is in the stepping start position (non-operation state or initial state) and a state in which the footboard 20 is in the stepping end position (stepping end state).

  Hereinafter, the front and rear and up and down directions of the pedal device are based on the state of being placed on the horizontal floor 26, the right side of FIGS. 1 and 2 is the front side, and the upper side of FIGS. 2 (a) and 2 (b) is the upper side. To do. In addition, the left-right direction is referred to based on the direction seen from the player on the right side of FIG. 1A, and the upper side of FIG.

  As shown in FIG. 1 and FIG. 2, the pedal device has a base 10, and a link mechanism including a plate-like footboard 20 and two arms 21 (21 </ b> L and 21 </ b> R) on the base 10. Is disposed. In this link mechanism, the mass portion 22 is configured to slide in the front-rear direction, and a so-called slider crank mechanism is employed (details will be described later). The base 10, the foot board 20, and the arm 21 are all made of metal or the like.

  A support portion 12 is provided on the upper front portion of the bottom plate 11 of the base 10, and a stopper support portion 13 is provided on the rear upper portion of the bottom plate 11. Side plate portions 14 (14L, 14R) project upward from the left and right sides of the upper half of the bottom plate 11. A spring support portion 15 protrudes upward at a substantially middle portion in the front-rear direction of the bottom plate 11 and in a central portion in the left-right direction (FIG. 2). The support portion 12, the stopper support portion 13, the side plate portion 14, and the spring support portion 15 may be fixed to the bottom plate 11, and do not need to be integrally formed. A stopper portion 30 is disposed and fixed on the front surface of the stopper support portion 13.

  A leg portion 25 is provided on the lower surface of the bottom plate 11, and the leg portion 25 (FIG. 1) is grounded to the floor surface 26. The leg 25 is made of an elastic body such as rubber or a spring, and plays a role of blocking or suppressing vibration transmission between the base 10 and the floor surface 26. In order to make vibration isolation more effective, a viscoelastic material may be interposed in a portion corresponding to the leg portion 25, or an oil damper, an air damper, or the like may be provided to cause loss, thereby speeding up vibration attenuation. Good. At that time, it is preferable to design so that resonance does not occur.

  The support portion 12 is provided with a first rotation shaft 18 along the left-right direction, and the front end portion 20 a of the foot board 20 is pivotally supported on the first rotation shaft 18. As a result, the footboard 20 has a rear end 20b that is rotatable about the first rotation shaft 18 in the vertical direction (clockwise and counterclockwise in FIG. 2A).

  Further, a second rotating shaft 23 is provided along the left-right direction at the rear end 20b of the footboard 20. One arm 21 is provided in parallel on the left and right, and a front end portion 21 a of each arm 21 is pivotally supported on the second rotation shaft 23. Thus, the rear end portion 21b of each arm 21 is rotatable in the vertical direction (clockwise and counterclockwise in FIG. 2A) around the second rotation shaft 23.

  A rod-shaped sliding pin 24 is suspended between the rear end portion 21b of the arm 21L and the rear end portion 21b of the arm 21R. A mass part 22 is provided between the arms 21L and 21R. The mass portion 22 is preferably made of a material having a higher specific gravity than the footboard 20 or the arm 21 so that a large amount of mass of the system (operation system) including the footboard 20, the arm 21 and the mass portion 22 is concentrated on the mass portion 22. Become. A sliding pin 24 passes through the mass portion 22, and the sliding pin 24 is rotatable with respect to the mass portion 22. The mass portion 22 has a circular shape in a side view, but the shape is an example and the present invention is not limited to this.

  A concave guide groove 14 a is formed along the front-rear direction on the inner side surface in the left-right direction of each side plate portion 14 of the base 10. The sliding pin 24 is disposed along the left-right direction, and spans the left and right ends so as to engage with the guide groove 14a of the side plate portion 14L and the guide groove 14a of the side plate portion 14R. The vertical width of the guide groove 14a is slightly larger than the diameter of the slide pin 24, and the slide pin 24 is slidable in the front-rear direction in the guide groove 14a. Thereby, the mass part 22 can be displaced in the front-rear direction integrally with the sliding pin 24.

  A first coil spring 16 as an elastic material is interposed between the bottom surface of the foot board 20 and the bottom plate 11. The position where the first coil spring 16 is attached to the footboard 20 is preferably close to the rear end 20b, but is not essential. A second coil spring 17 as an elastic material is interposed between the mass portion 22 and the spring support portion 15. In the non-operating state of the footboard 20, both the first coil spring 16 and the second coil spring 17 are in a compressed state, and an equilibrium state of the link mechanism system including the footboard 20, the arm 21, and the mass portion 22 is maintained. . That is, the footboard 20 in the non-operating state is restricted to the stepping start position shown in FIG. Moreover, even if the footboard 20 is displaced in the forward direction (counterclockwise direction in FIG. 2 (a)) from the stepping start position or in the opposite direction, the foot spring 20 is moved by the elasticity of the coil springs 16 and 17. An urging force is applied to return the board 20 to the start position.

  The spring constants of the coil springs 16 and 17, the setting of the arrangement position, the amount of displacement, and the like can be arbitrarily set, and thereby the stepping torque can be set to the player's preference. Further, the stepping start position (initial angle) of the footboard 20 can be set to a desired position. By the way, in order to maintain the equilibrium state of the system of the link mechanism in the non-operation state, both the coil springs 16 and 17 may be in a tension state.

  When the footboard 20 is stepped on from the non-operating state (FIG. 2A), the footboard 20 rotates and the second rotation shaft 23 is displaced downward. Accordingly, the slide pin 24 slides backward in the guide groove 14a, and the mass portion 22 horizontally moves backward. The arm 21 has a posture corresponding to the positions of the second rotating shaft 23 and the sliding pin 24. Eventually, when the mass portion 22 comes into contact with the stopper portion 30, the stepping end position of the footboard 20 is regulated (FIG. 2B). Since the direction in which the impact force of the mass portion 22 directly acts is backward, the impact force on the floor surface 26 below is greatly reduced as compared with the conventional case. The configuration of the stopper portion 30 will be described later.

  FIG. 3A is a schematic diagram of a system of a link mechanism including the foot board 20, the arm 21, and the mass unit 22 in the present embodiment. The positions of the second rotating shaft 23 and the sliding pin 24 in the non-operating state are the starting points PfS and PaS, respectively, and the positions of the second rotating shaft 23 and the sliding pin 24 when the footboard 20 is in the stepping end position, respectively. The end points are PfE and PaE.

  In the stepping forward stroke, the linear distance from the starting point PaS to the end point PaE of the sliding pin 24 is longer than the linear distance from the starting point PfS to the end point PfE of the second rotating shaft 23. Since the amount of displacement of the mass portion 22 is increased when viewed from the second rotation shaft 23, the inertial mass of the mass portion 22 in the above system is larger than the configuration in which the mass portion 22 is directly fixed to the footboard 20. . Therefore, it is easy to design so that the influence of the inertial force due to the mass portion is greater than in the past. In addition, the shape of the mass portion 22 and the degree of freedom in setting the mass are also higher than when fixing to the footboard 20. In the present embodiment, the mass of the mass portion 22 and the amount of displacement are set so that the inertia mass is comparable to that of an acoustic kick pedal.

  4A and 4B are cross-sectional views schematically showing a detailed configuration of the stopper portion 30 in the present embodiment. Although the front view shape of the stopper part 30 is circular, a rectangular shape may be sufficient and a shape is not ask | required. 4A shows a non-contact state with the mass portion 22, FIG. 4B shows a contact state with the mass portion 22, and the deformation is exaggerated.

  As shown in FIG. 4A, the stopper portion 30 has a base plate 32 at the rearmost portion, and a cushioning material 33 such as a sponge is interposed between the base plate 32 and the sensor plate 34. A cushioning material 35 such as sponge is attached to the front surface of the sensor plate 34, and a rubber sheet 36 covers the front surface of the cushioning material 35. The front surface of the rubber sheet 36 is parallel to the vertical direction. A piezo sensor 31 is attached to a portion of the rear surface of the sensor plate 34 where the cushioning material 33 is not present.

  When the mass portion 22 comes into contact with the front surface of the rubber sheet 36, the buffer members 33 and 35 perform a buffer function, and the piezo sensor 31 detects a voltage change due to the impact, and outputs a signal. The output signal is sent as a batting performance trigger signal to a signal processing unit (not shown), and is converted into batting performance data or converted into sound in real time.

  Here, the hardness of the rubber sheet 36 is higher than that of the buffer materials 33 and 35. The rubber sheet 36 and the cushioning materials 33 and 35 are designed so that an appropriate repulsive force similar to the kick pedal of the acoustic drum is generated at the moment when the mass portion 22 contacts the rubber sheet 36. In terms of design, the repulsive force is mainly adjusted by the hardness of the buffer materials 33 and 35. By appropriate adjustment, a so-called double performance operation of hitting twice can be performed without a sense of incongruity. After the mass portion 22 bounces off at the stopper portion 30, the system returns to the stepping start position by the elasticity of the coil springs 16 and 17.

  According to the present embodiment, the footboard 20 and the arm 21 constitute a link mechanism, and the displacement track of the mass portion 22 is regulated in the front-rear direction by the guide groove 14a. Then, in the forward stroke of stepping on the footboard 20, the mass portion 22 slides backward and comes into contact with the stopper portion 30 from the front. Thereby, the impact with respect to the floor surface 26 can be relieved. In particular, since the contact surface of the stopper portion 30 is vertical, a repulsive force acts forward in the horizontal direction, and vibration transmitted to the floor surface 26 and generated impact sound can be reduced. Further, since the mass portion 22 is provided at the rear end portion 21b of the arm 21 linked to the foot board 20, and the displacement amount thereof is larger than that of the rear end portion 20b of the foot board 20, the inertia force of the mass portion 22 can be increased. , The degree of freedom for improving the feeling of stepping on can be increased. Therefore, it is possible to easily improve the depression feeling.

  In addition, the first coil spring 16 and the second coil spring 17 maintain the equilibrium state of the link mechanism system and impart the return habit to the initial position, thereby realizing an initial depression feeling similar to that of an acoustic pedal device. be able to.

  Moreover, since the buffer materials 33 and 35 of the stopper part 30 play a role as a reaction force generation part that generates a reaction force in the backward direction with respect to the footboard 20 when coming into contact with the mass part 22, good impact is achieved. Feeling can be realized and repeated hitting can be facilitated. Furthermore, since the reaction force generating portion and the piezo sensor 31 are built in the stopper portion 30, a good hitting feel and operation detection can be realized with a compact configuration.

  By the way, from the viewpoint of effectively mitigating the impact on the floor surface 26, the mass portion 22 may be configured to be displaced in a direction not including the lower component in the forward stroke. Hereinafter, modified examples will be described.

  FIGS. 3B to 3D are schematic views of a link mechanism of a modified example in which the displacement direction of the mass portion 22 is changed, and corresponds to FIG. For example, as shown in FIG. 3B, the mass portion 22 may be configured to slide forward as the footboard 20 is stepped on. Alternatively, an upper component may be included, and the mass part 22 may be configured to be displaced obliquely rearward and upward as shown in FIG. Further, it is not essential for the mass portion 22 to be linearly displaced, and a curved locus may be traced as shown in FIG.

  In addition, the displacement direction of the mass portion 22 may include a component in the left-right direction. However, from the viewpoint of buffering, the displacement component of the sliding pin 24 to the mass part 22 is larger in the horizontal component than the upper component in the relationship from the starting point PaS to the ending point PaE of the sliding pin 24. Is effective. Note that, in order to effectively act the inertial mass, the linear distance of displacement of the mass portion 22 (from the start point PaS to the end point PaE of the sliding pin 24) is larger than the linear distance of the second rotating shaft 23 that is displaced by the depression. It is preferable that the design is such that the (linear distance) is larger, as in the example of FIG. Further, regarding the direction of the repulsive force from the stopper portion 30, the surface of the stopper portion 30 with which the mass portion 22 abuts is preferably close to being parallel to the vertical direction.

  By the way, as a structure which incorporates a hit | damage detection mechanism and a reaction force generation | occurrence | production part in the stopper part 30, it is not restricted to the example of Fig.4 (a), (b). 4 (c) to 4 (f) show a modified stopper portion 30. FIG.

  For example, the stopper portion 30 shown in FIGS. 4C and 4D fixes the film portion 39 to the base plate 37 with a screw while maintaining the tension. A shock absorbing material 38 such as a sponge is provided on the rear surface of the film portion 39, and the piezo sensor 31 is disposed between the shock absorbing material 38 and the base plate 37. In this configuration, a repulsive force is generated mainly by the tension of the film part 39. When the mass portion 22 comes into contact, the buffer material 38 is deformed, and the piezo sensor 31 detects it as a hit.

  4 (e) and 4 (f), a spring 42 is interposed between the base plate 40 and the sheet metal 49, and a cushioning material 41 such as a sponge is provided on the rear surface of the base plate 40. A piezo sensor 31 is disposed between the base plate 40. A rubber sheet 36 covers the front surface of the sheet metal 49. In this configuration, a repulsive force is generated mainly by the elasticity of the spring 42. When the mass portion 22 comes into contact, the buffer material 41 is deformed, and the piezo sensor 31 detects it as an impact.

  In addition, the reaction force generation unit may be configured by an elastic body other than those exemplified, a member that generates tension, or a combination thereof. The type of sensor that detects the impact is not limited and is not limited to a piezo element. A capacitance type sensor, a pressure sensitive resistance type sensor, or the like may be employed.

  By the way, the mechanism for regulating the displacement trajectory of the mass portion 22 is not limited to the combination of the guide groove 14a and the sliding pin 24 illustrated in FIGS. FIGS. 5A and 5B are schematic views showing a modification of the mechanism that regulates the displacement trajectory of the mass section 22.

  For example, as shown in FIG. 5A, side plates 50 similar to the side plates 14 are provided on the left and right sides of the bottom plate 11 of the base 10, and concave guides are formed on the left and right side inner surfaces of both the left and right side plates 50. A groove 50a is formed. The mass part 22 is formed in a rectangular parallelepiped shape, and the mass part 22 and the arm 21 are connected by a rotation shaft 52. The mass portion 22 itself is configured to slide in the guide groove 50a in the front-rear direction.

  Alternatively, as shown in FIG. 5B, a block 51 is protruded from the bottom plate 11 of the base 10, and a circular guide hole 51 a in front view is formed in the block 51. The mass portion 22 is formed in a cylindrical shape, and the mass portion 22 and the arm 21 are connected by a rotation shaft 52. The mass portion 22 itself is configured to slide in the guide hole 51a in the front-rear direction.

  By the way, from the viewpoint of keeping the link mechanism system including the foot board 20, the arm 21 and the mass part 22 in an equilibrium state in the non-operating state, the arrangement is limited to the arrangement of the coil springs 16 and 17 shown in FIGS. Absent. FIGS. 6A to 6E are views showing modifications of the arrangement of coil springs for keeping the link mechanism system in an equilibrium state in a non-operating state. 6A to 6E, the spring locking portions 10a to 10e are portions fixed to the base 10, and may be the base 10 or members fixed to the base 10. .

  For example, as shown in FIG. 6A, coil springs 43 and 44 are interposed between the foot board 20 and the upper spring locking portion 10a and the lower spring locking portion 10b, respectively. Alternatively, as shown in FIG. 6B, a coil spring 43 is interposed between the foot board 20 and the spring locking portion 10a, and the mass portion 22 and the spring locking portion 10c behind the mass portion 22 are connected. A coil spring 45 is interposed therebetween. Alternatively, as shown in FIG. 6C, a coil spring 45 is interposed between the mass portion 22 and the spring locking portion 10c, and between the mass portion 22 and the spring locking portion 10d ahead of the mass portion 22. A coil spring 46 is interposed therebetween.

  In the case of the examples of FIGS. 6A to 6C, the two coil springs can be compressed together to keep the link mechanism system in an equilibrium state in the non-operating state. Alternatively, both can be kept in equilibrium even in tension.

  Moreover, as shown in FIG.6 (d), the coil spring 47 is interposed between the mass part 22 and the spring latching | locking part 10a above it. Then, in a non-operating state, the coil spring 47 is in a tension state, and the mass portion 22 is positioned just below the spring locking portion 10a. Alternatively, as shown in FIG. 6 (e), a coil spring 48 is interposed between the rear end portion 20b (or the second rotation shaft 23) of the foot board 20 and the spring engaging portion 10e obliquely above and behind the foot board 20. Disguise. In a non-operating state, the coil spring 48 is in a tension state, and the coil spring 48 is extended on the extension of the foot board 20.

  In the example of FIGS. 6D and 6E, there is one coil spring. The coil springs 47 and 48 are both arranged in a tensioned state so as to be the shortest when the footboard 20 is in the stepping start position. Even if the footboard 20 is displaced in the forward direction or the opposite direction from the stepping start position in the non-operating state, the coil springs 47 and 48 are pulled more, so the footboard 20 is returned to the stepping start position. The biasing force acts on the link mechanism system.

  In the above-described embodiment and each modification, in order to appropriately configure the link mechanism system, the position of the second rotation shaft 23 may be provided at a position near the rear end portion 20b of the footboard 20. . Further, the mass portion 22 may be provided at a position near the rear end portion 21 b of the arm 21. Further, the various coil springs such as the coil springs 16 and 17 may be any one that exhibits an elastic force, and may be other elastic materials such as rubber.

  Since the piezo sensor 31 only needs to be able to detect the operation of the footboard 20 directly or indirectly, the location of the piezo sensor 31 is not limited to the position where the piezo sensor 31 abuts on the mass portion 22, and the position where the operation of the footboard 20 itself can be detected, for example, the bottom plate 11 may be provided.

DESCRIPTION OF SYMBOLS 10 Base, 14a, 50a Guide groove (regulation means), 15 Spring support part, 16 1st coil spring (elastic material), 17 2nd coil spring (elastic material), 18 1st rotating shaft, 20 Foot board, 20a Front end Part (one end part), 20b rear end part (other end part), 21 arm, 21a front end part (one end part), 21b rear end part (other end part), 22 mass part, 23 second rotation shaft (rotation) Fulcrum), 26 floor, 30 stopper portion, 33, 35 cushioning material (reaction force generation portion), 39 membrane portion (reaction force generation portion), 42 spring (reaction force generation portion), 47, 48 coil spring (elastic material) 51a Guide hole (regulating means), PfS, PaS start point, PfE, PaE end point

Claims (3)

A base placed on the floor;
One end is pivotally supported with respect to the base, and a footboard that can be rotated by a stepping operation;
An arm that is pivotally supported at one end on a pivot point provided at a position near the other end of the footboard, and is pivotable;
A mass part movement having a mass part and an engaging part that engages with the other end of the arm so as to be rotatable, and moves the mass part by displacement of the arm that is rotated by a stepping operation of the footboard. And a mechanism part,
Moving the mass section moving mechanism portion, the depression of the foot board, the engaging portion is primarily horizontally on the opposite side of the one end of the foot board across the other end of the front Symbol footboard Thus, the pedal device for an electronic percussion instrument is configured to move the mass portion.   The pedal device for an electronic percussion instrument according to claim 1, further comprising a return mechanism that engages with the mass portion moving mechanism portion and returns the moved mass portion to a state before the movement.   The pedal device for an electronic percussion instrument according to claim 1 or 2, wherein the other end portion of the arm is positioned below the rotation fulcrum.