JP4442360B2 - Keyboard device - Google Patents

Description

  The present invention relates to a keyboard device in which an inertial force is applied to a key when the key is depressed by moving an arm driven by the key.

2. Description of the Related Art Conventionally, there has been known a keyboard device that can change a touch feeling (hereinafter referred to as “key press feeling”). For example, in the keyboard device disclosed in Patent Document 1 below, one end of the arm is engaged with the key, a weight is provided at the other end of the arm, and the arm is driven via the one end in conjunction with the key depression to be supported. It is comprised so that it can rotate by using a member as a fulcrum. In addition, the other end of the arm is configured to be adjustable from the ascending limit position to the descending limit position. When the other end is set at the lower limit position, the arm rotates around the support member along with the key depression, but when the other end is set at the upper limit position, the arm does not contact the support member. Therefore, the rotation with the supporting member as a fulcrum does not occur. Thereby, the weight of the key pressing feeling can be changed according to the setting position of the other end of the arm.
JP-B-1-47798

  However, in Patent Document 1, one end of the arm is always engaged with the key, and the arm also has a mass in a portion other than the weight. Therefore, even when the other end of the arm is in the ascending limit position and the arm does not contact the support member, the arm moves with the key, so that the inertial force due to the movement of the arm is always applied to the key. It will be. Therefore, there is a certain limit to setting the key pressing feeling lightly, and there is room for further improvement in making it possible to change the key pressing feeling more clearly and widely.

The present invention has been made to solve the above-described problems of the prior art, and its purpose is to make it possible to adjust the inertial force imparted to the key and to change the key-press feeling clearly and widely. An object of the present invention is to provide a keyboard device that can be used.

In order to achieve the above object, a keyboard apparatus according to claim 1 of the present invention has a support member (1) and a drive unit (12), is rotatably supported by the support member, and is released from a key release state. A key (10) that is operated to be pressed and released within a rotation range until the key is pressed, and a key return means (11) that operates to always return the key in the direction of the key release state within the key rotation range. And a rotation member that is rotatably supported by the support member at a first rotation fulcrum (34), and a second rotation fulcrum provided on the rotation member that is different from the first rotation fulcrum. Is pivotally supported and has a driven part (22), and the driven part is driven by the driving part of the key to rotate about the second rotation fulcrum (35). an arm (20) for imparting inertia to the key when depressed while, at least part of the forward stroke of key depression operation, before A first state in which the driven part of the arm is driven by the driving part of the key; and a second state in which the driven part of the arm is not driven by the driving part of the key in the entire key pressing process; the a switching means (AM1) for switching, possess an adjustment means (40, 38) for adjusting the degree of engagement with the driven part and the driving part in the first state, the arm, the first The rotation member is configured to be displaceable in a predetermined direction different from the key pressing direction by the rotation of the rotation member about the rotation fulcrum, and the switching means displaces the arm in the predetermined direction, thereby 1. Switch between the first and second states .

Preferably, before Kikagi and the arm is provided with a plurality to correspond to each other, said switching means, is displaced in the predetermined direction together a plurality of arms (claim 2).

Preferably, the arm is configured to be displaceable in a predetermined direction including a component perpendicular to a rotation direction of the arm, and the driven unit and the driving unit in the first state by the adjusting unit The degree of engagement with is adjusted by displacing the arm in the predetermined direction (Claim 3). Preferably the is found, the key and the arms, with provided a plurality to correspond to each other, said adjusting means (38) is provided for each arm, each adjustment means, for each corresponding arm, the driven It is possible to adjust the degree of engagement between the part and the corresponding key drive part (claim 4).
In order to achieve the above object, a keyboard device according to a fifth aspect of the present invention includes a support member and a drive unit, and is rotatably supported by the support member to rotate from a key release state to a key press state. A key that is pressed and released within a moving range, a key return means that operates to always return the key in the key-released direction within the rotation range of the key, and a driven part, and the driven An arm that is rotated by the drive unit of the key and applies an inertial force to the key when the key is depressed; the driven unit of the arm; and the drive unit of the key; Adjusting means for adjusting the degree of engagement of the key, and at least part of the forward stroke of the key pressing operation, the driven portion of the arm is driven by the driving portion of the key, and the key pressing operation Configured so that the driving relationship between the driving unit and the driven unit is terminated in the course of The adjusting means adjusts the degree of engagement between the driven portion and the driving portion collectively for a plurality of keys, thereby driving the driving portion and the driven portion in the forward stroke of the key pressing operation. The relationship end timing is changed.
Preferably the is found, urged together to regulate the key depression end position of the key and contact with the key during the key depression, when the key and in contact, the key in the direction of the release key state having a return biasing means (4) to (claim 6).

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

According to the present invention, to allow adjustment of the inertial force applied to the key, it is possible to clearly and widely arbitrarily change the key-touch.

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

(First embodiment)
FIG. 1 is a side view of a keyboard apparatus according to the first embodiment of the present invention. The keyboard device according to the present embodiment has a key body 10 (a white key is illustrated in the figure) that is operated to press and release the chassis 1, and a hammer for giving appropriate inertia to the key body 10 during a key pressing operation. The body 20 and the like are supported so as to be swingable in the vertical direction. Hereinafter, the free end side (right side of the figure) of the key body 10 is referred to as “front”.

  The key body 10 is rotatable in the vertical direction around the key rotation shaft 2 at the rear end. A weight 11 is provided at the rearmost part of the key body 10 from the key rotation shaft 2 and at the rearmost end thereof. The weight body 10 is moved counterclockwise (opposite to the key pressing direction) by the weight of the weight 11. Is always energized in the direction of A stopper abutting portion 13 is suspended from the front lower portion of the key body 10. A hammer drive unit 12 for driving the hammer body 20 is provided to hang down from the lower part of the front side of the key body 10 and slightly behind the stopper contact part 13. The lower end portion of the hammer drive unit 12 is formed in a side view arc shape.

  An upper limit stopper 3 and a key pressing switch 4 made of an elastic member are provided at a position of the chassis 1 corresponding to the stopper contact portion 13 of the key body 10. The key pressing switch 4 may be an optical switch that detects light. In the non-key-pressed state (key-released state), the stopper abutting portion 13 abuts on the upper limit stopper 3 due to the weight of the weight 11, and as shown in FIG. Key stroke initial position) is regulated. On the other hand, when the key is depressed, the stopper abutment portion 13 abuts on the key depression switch 4 by fully pushing the key body 10, and the key stroke end position of the key body 10 is regulated. At that time, the key pressing operation is detected by the key pressing switch 4. A lower limit stopper for preventing the key pressing switch 4 from being crushed may be provided in the chassis 1.

  The hammer body 20 is provided corresponding to each key body 10 and is supported so as to be rotatable in the vertical direction around an upper rotation fulcrum 35 of a rotation arm 33 described later. A weight 21 is provided at the tail end of the hammer body 20, and most of the mass of the hammer body 20 is concentrated on the weight 21. Due to the weight of the weight 21, the hammer body 20 is always urged counterclockwise (the direction opposite to the key pressing direction) in the figure. A flat slope portion 22 facing forward and upward is formed in the foremost portion of the hammer body 20, and the slope portion 22 is driven by the hammer drive portion 12 of the key body 10 as will be described later. Function as.

  A hammer lower limit stopper 5 is provided at a position of the chassis 1 substantially corresponding to the weight 21 of the hammer body 20. In a predetermined state to be described later including when the key is not pressed, the free end of the hammer body 20 abuts against the lower limit stopper 5 for the hammer due to the weight of the weight 21, and the hammer body 20 is The initial position of the rotation stroke is restricted.

  Although details will be described later, due to the engagement between the hammer drive unit 12 of the key body 10 and the inclined surface portion 22 of the hammer body 20, the hammer body 20 performs a key pressing direction (see FIG. 1 clockwise). By the initial position adjusting mechanism AM1 described later, the engagement relationship between the hammer drive unit 12 and the inclined surface part 22 can be made variable, and thus the key pressing feel can be made variable.

  FIG. 2 is a partial plan view of the keyboard device. FIG. 3 is a side view of the initial position adjusting mechanism AM1. FIG. 2 shows a configuration of a keyboard device for a predetermined octave (in this embodiment, two octaves).

  As shown in FIGS. 1 and 2, a lower rotation fulcrum 34 is fixedly provided on the chassis 1, and the clockwise and counterclockwise directions of FIG. 1 are centered on the lower rotation fulcrum 34. A rotating arm 33 that rotates is provided. On the chassis 1, a spring locking portion 31 is provided in front of the rotating arm 33, and the front portion of the rotating arm 33 and the spring locking portion 31 are connected by a spring 32. The rotating arm 33 and the spring 32 are provided corresponding to each key body 10. The spring 32 always urges the corresponding rotating arm 33 in the clockwise direction in FIG. One spring locking portion 31 is provided in common for the key body 10 for two octaves, but may be provided individually.

  In addition, on the chassis 1, an initial position adjusting mechanism AM <b> 1 is disposed behind the rotating arm 33. A thread material 36 with low elasticity is attached to the rear part of the rotating arm 33, and this thread material 36 is connected to a part (described later) of the initial position adjusting mechanism AM1. The initial position adjusting mechanism AM1 is provided in common for the key body 10 for two octaves. The thread material 36 is provided corresponding to each key body 10.

  The initial position adjusting mechanism AM1 and the spring locking portion 31 are not limited to be provided corresponding to the two octaves of the key body 10, and may be provided for each of the three or more key bodies 10, You may provide in common with all the key bodies 10. FIG.

  The initial position adjusting mechanism AM1 includes a slide base 37 (37L, 37R), an individual adjusting unit 38, a connecting member 39 (39L, 39R), and a collective adjusting unit 40 (40L, 40R). As shown in FIG. 2, the slide bases 37L and 37R, the connecting members 39L and 39R, and the collective adjustment portions 40L and 40R are respectively arranged on the left and right sides of the key body 10 for two octaves, and are similarly configured symmetrically. The Hereinafter, when it is not necessary to distinguish between the slide base 37, the connecting member 39, and the collective adjustment unit 40, the reference numerals are not denoted with “L” and “R”.

  4A is a front view of the collective adjustment unit 40L, and FIG. 4B is a front view of the individual adjustment unit 38. Since the initial position adjusting mechanism AM1 is configured symmetrically, the configuration on the left side will be mainly described below.

  As shown in FIGS. 3 and 4A, the collective adjustment portion 40L is configured such that a collective adjustment slide member 45L is slidably movable in the front-rear direction with respect to the L-shaped fixing member 46L. Is done. An adjustment screw 48 is provided at the rear end of the fixing member 46, and the position in the front-rear direction of the collective adjustment slide member 45 with respect to the fixing member 46 can be adjusted by inserting and removing the adjustment screw 48. The collective adjustment slide member 45 can be fixed to the fixing member 46 with a fixing screw 47. A C-channel guide member 82 is embedded in the fixing member 46. The guide member 82 includes a nut 81, and the nut 81 is screwed to the lower end portion of the fixing screw 47.

  On the other hand, as shown in FIG. 3 and FIG. 4B, the individual adjustment portion 38 includes a common slide member 42 and an individual slide member 41 that are L-shaped in a side view, and the common slide member 42 corresponds to two octaves. However, the individual slide member 41 is provided corresponding to each key body 10.

  The common slide member 42 is provided so as to be bridged to the slide bases 37L and 37R. The slide bases 37L and 37R are formed with dovetail grooves 37La and 37Ra each having a substantially C-shaped cross section, and the portions of the common slide member 42 corresponding to the dovetail grooves 37La and 37Ra are formed in a fitting shape. Has been. Therefore, the common slide member 42 is slidable in the front-rear direction with respect to the slide bases 37L and 37R along the dovetail grooves 37La and 37Ra. In addition, the individual slide members 41 can slide in the front-rear direction with respect to the common slide member 42.

  Further, an adjustment screw 44 is provided at the rear end portion of the common slide member 42, and the position of the individual slide member 41 in the front-rear direction with respect to the common slide member 42 can be individually adjusted by inserting and removing the adjustment screw 44. It is. Further, each individual slide member 41 can be fixed to the common slide member 42 by a corresponding fixing screw 43. A C-channel guide member 84 is embedded in the common slide member 42. The guide member 84 is internally provided with a nut 83, and the nut 83 is screwed to the lower end portion of the fixing screw 43.

  2 and 3, the front end portions of the collective adjustment slide members 45L and 45R and the corresponding rear end portions of the common slide member 42 are connected by the connecting members 39L and 39R. . The connecting member 39 is formed of a member such as metal or resin that is not so much elastically deformed as rubber or the like. Therefore, at the time of adjusting the key pressing feeling, the collective adjustment slide member 45 and the common slide member 42 are integrally slid in the front-rear direction via the connecting member 39. The thread material 36 is connected to the front end portion of the corresponding individual slide member 41.

  As described above, the rotating arm 33 is always urged clockwise in FIG. 1 by the corresponding spring 32. Therefore, in a non-key-pressed state, the thread material 36 is in a tensioned state (pulled with a pin). The posture of the rotating arm 33 is maintained. Therefore, if it is limited to the non-key-pressed state, the position of the rotation arm 33 in the rotation direction is determined by the position of the individual slide member 41, and at the same time, the position of the hammer body 20 in the front-rear direction is also determined. Each position of the rotating arm 33 and the hammer body 20 in the non-key-pressed state is also simply referred to as “initial position”.

  In such a configuration, the initial position of the hammer body 20 is performed by “collective adjustment” and / or “individual adjustment” by the initial position adjustment mechanism AM1.

  With reference to FIG. 3, the batch adjustment will be described first. By loosening the fixing screw 47 and adjusting the position of the adjusting screw 48 in a state where the collective adjusting slide member 45 is in contact with the tip of the adjusting screw 48, the collective adjusting slide member 45 on the fixing member 46 is adjusted. Slide. As the collective adjustment slide member 45 slides, the connecting member 39 and the individual adjustment unit 38 slide. When the collective adjustment slide member 45 comes to a desired position, the fixing screw 47 is screwed to fix the collective adjustment slide member 45 to the fixing member 46. Thereby, the initial position of the hammer body 20 can be collectively adjusted for the key body 10 for two octaves.

  Individual adjustment is performed as follows. Similarly to the relationship between the fixing member 46 and the collective adjustment slide member 45, the fixing screw 43 corresponding to the hammer body 20 to be adjusted is loosened and the individual slide member 41 is in contact with the tip of the adjustment screw 44. The individual slide member 41 is slid on the common slide member 42 by adjusting the position of the adjustment screw 44. When the individual slide member 41 comes to a desired position, the fixing screw 43 is screwed to fix the individual slide member 41 to the common slide member 42. Thereby, the initial position of the hammer body 20 corresponding to each key body 10 can be individually adjusted.

  Next, the mode of operation of the key body 10 and the hammer body 20 during the key pressing operation will be described. These operation modes differ not only depending on the key pressing mode, that is, the key pressing speed or key pressing strength, but also depending on the setting of the initial position of the hammer body 20.

  The setting of the position of the hammer body 20 in the front-rear direction is roughly divided into at least a part of the forward stroke of the key depression, for example, in a non-key depression state, as shown in FIG. A setting (hereinafter referred to as “live piano setting”) in which the 12 is engaged with the inclined surface portion 22 of the hammer body 20 (hereinafter referred to as “live piano setting”), as will be described later with reference to FIG. There is a setting (hereinafter referred to as “organ setting”) in which the hammer body 20 is always separated and not engaged at all in the entire stroke of the key depression (second state). In “raw piano setting”, the initial position of the hammer body 20 can be adjusted steplessly. As will be described later, an intermediate state between the organ setting and the live piano setting can also be set with respect to the engagement state between the hammer driving unit 12 and the slope portion 22.

  FIGS. 5A to 5D are side views of the keyboard device when the key is slowly depressed (hereinafter referred to as “weakly depressed key”) in the “raw piano setting”, and the key body 10 and the hammer body 20 are illustrated. The transition of the operation is shown. FIG. 6 is a schematic diagram showing the interrelationships of the key pressing force, the normal drag force, and the frictional force when “raw piano setting” is set and the key is weakly pressed. FIGS. 7A to 7D are side views of the keyboard device when the key is quickly pressed (hereinafter referred to as “strongly pressed key”) in the “raw piano setting”, and the key body 10 and the hammer body 20 are illustrated. The transition of the operation is shown.

  Here, “weak key press” refers to a key press mode ranging from an extremely weak key press strength such as whether a hammer strikes a string to a relatively weak key press strength in an acoustic piano. The “strong key press” is a key press mode that is sufficiently stronger than the weak key press and corresponds to a key press strength range from a normal pronunciation to a strong pronunciation.

  First, in the case of a weak key press, in the non-key press state shown in FIG. 5A, the hammer drive unit 12 of the key body 10 is in contact with the inclined surface portion 22 of the hammer body 20, and the key is slowly pressed. The hammer body 20 rotates in conjunction with the key body 10 when the hammer driving section 12 presses the slope portion 22. Then, until the weight 21 of the hammer body 20 approaches the lower surface of the key body 10 as shown in FIG. 5B, the hammer drive section 12 and the slope section 22 maintain the contact state at the contact point P. . Therefore, during this time, both are engaged in a static friction state, hardly slide, and the rotating arm 33 hardly rotates.

  That is, the rotation center of the key body 10 is the key rotation shaft 2, but the rotation center of the hammer body 20 is the upper rotation fulcrum 35. If the rotation arm 33 does not rotate at all, Since the position of the moving fulcrum 35 also does not change, the position corresponding to the contact point P at the time of non-key-pressing of both (hammer driving portion 12 and slope portion 22) does not follow the same locus. That is, the respective rotation trajectories centering on the key rotation shaft 2 and the rotation fulcrum 35 at both positions corresponding to the contact point P when the key is not pressed are gradually separated from each other with the rotation. However, as long as the hammer drive section 12 and the slope section 22 are engaged in a static friction state, the rotation fulcrum 35 is moved back and forth by the amount of absorption of the deviation of the rotation locus in order to maintain the same contact point P. Move in the direction. The rotating arm 33 is rotated so as to cause this movement. However, the amount is small.

  In a normal key pressing mode including a weak key press and a strong key press, the forward rotation of the hammer body 20 ends in the middle, so that the weight 21 of the hammer body 20 contacts the lower surface of the key body 10. There is no. Therefore, in the present embodiment, an upper limit stopper that contacts the hammer body 20 is not provided. Thereby, the configuration is simple and the thickness of the entire keyboard device can be reduced.

  Although the detailed operation will be described later, the engagement relationship between the hammer drive portion 12 and the slope portion 22 then shifts to the kinetic friction state, and the rotating arm 33 moves counterclockwise as shown in FIG. If it rotates a lot, the upper rotation fulcrum 35 provided on the upper part of the rotation arm 33 is displaced rearward, and accordingly, the hammer body 20 is also displaced rearward (predetermined direction). As a result, the hammer driving unit 12 is detached from the inclined surface part 22, so that a static let-off feeling like an acoustic piano is obtained. In addition, the stopper abutting portion 13 abuts on the key depression switch 4 to detect the key depression operation, and the key depression forward stroke with respect to the key body 10 is completed.

  After the hammer drive unit 12 is detached from the sloped part 22, the front end of the hammer body 20 (corresponding to the lower edge of the sloped part 22) is in sliding contact with the rear wall of the hammer drive unit 12, while the hammer body 20 is counterclockwise. It quickly rotates in the direction, and the weight 21 comes into contact with the lower limit stopper 5 for hammer. At this point, the hammer body 20 stops at a position displaced slightly rearward from the true initial position. At this time, since the mass of the hammer body 20 is not applied to the key body 10, even if the key body 10 is kept pressed, only the static load of the key body 10 is applied, and the finger does not get tired.

  Thereafter, when the key pressing force is released, the key body 10 returns to the initial position as shown in FIG. At that time, the key body 10 receives not only the weight of the weight 11 but also the initial reaction force from the key press switch 4, so that the key body 10 can be quickly returned, which leads to improvement in the repeatability. When the hammer drive unit 12 returns to a position where it can engage with the inclined surface portion 22 by the return of the key body 10, the rotating arm 33 is rotated clockwise by the urging force of the spring 32, and the hammer body 20 is also in the initial position. Return.

  Next, with reference to FIG. 6, the operation between the hammer drive section 12 and the slope section 22 at the time of weak key pressing will be described. In the figure, the key pressing force is represented by F, the normal force is represented by N, and the friction force is represented by f. FIGS. 9A, 9D, 9G, and 10M show the transition of the action between the key body 10 and the hammer body 20. FIG. (B), (e), (h), and (k) in the same figure correspond to (a), (d), (g), and (j) in FIG. The relationship between the normal force N and the frictional force f generated in FIG. (C), (f), (i), (l) corresponds to (a), (d), (g), (j), and corresponds to the normal force N and the frictional force f. The relationship between the horizontal component force and the vertical component force applied to the slope portion 22 is shown. In the drawing, for easy understanding, the angle of the slope portion 22, the shape of the hammer drive portion 12, the magnitude of the force, and the like are exaggerated.

  In the figure, the horizontal component force and the vertical component force applied to the inclined surface portion 22 corresponding to the vertical drag N are represented by Nx and Ny, respectively, and the horizontal component force and the vertical component force applied to the inclined surface portion 22 corresponding to the frictional force f. Are represented by fx and fy, respectively. The same figure (a)-(c) has shown the mutually same state. Also, (d) to (f), (g) to (i), and (j) to (l) in FIG. Hereinafter, the key pressing force F, the vertical drag N ′ and its reaction force N, the friction force f ′ and its reaction force f, the horizontal component force Nx, the horizontal component force fx, the vertical component force Ny, and the vertical component force fy are shown in FIG. When the force in each state shown in (a) to (c), (d) to (f), (g) to (i), (j) to (l) is distinguished and indicated, “1” in parentheses. To “4” and expressed as, for example, key pressing force F (1), frictional force f (1), and the like.

  Hereafter, “friction” in considering the action refers to “sliding friction”. However, the tip of the hammer drive unit 12 is arcuate, and strictly speaking, it rolls with the inclined surface portion 22, so that some rolling friction is caused by this, but there is no significant effect on the key pressing. Ignore the rolling friction above.

  When the frictional state between the hammer drive section 12 and the inclined surface section 22 is compared between the same figure (a), (d), (g), (j), (m), the same figure (a), (d). In the static friction state, (g) and (j) in the figure, the dynamic friction state is present, and between the figures (d) and (g), there is a boundary state between the static friction state and the dynamic friction state. 6 (a) and 6 (d) correspond to the states shown in FIGS. 5 (a) and 5 (b). FIG. 6 (m) corresponds to the state shown in FIG. 5 (c).

  First, in the initial stage of key depression, as shown in FIG. 2A, the downward key depression force F (1) is applied to the slope from the hammer drive section 12 at the contact point P between the hammer drive section 12 and the slope section 22. Given to part 22. Here, the inclined surface portion 22 is configured to generate appropriate sliding friction, and the static friction state is maintained in the state shown in FIG. Accordingly, due to the key pressing force F (1), the normal force N ′ (1) perpendicular to the inclined surface portion 22 and the frictional force f parallel to the inclined surface portion 22 at the contact point P with respect to the hammer driving portion 12. '(1) is given ((b) in the figure).

  As shown in FIG. 5C, at the contact point P, the force N (1) applied to the inclined surface portion 22 corresponding to the vertical reaction force N ′ (1) (as a reaction force) is the horizontal component force Nx (1). , Distributed to the vertical component force Ny (1) and applied to the inclined surface portion 22. In addition, the force f (1) applied to the inclined surface portion 22 corresponding to the frictional force f ′ (1) (as a reaction force) is distributed to the horizontal component force fx (1) and the vertical component force fy (1). Part 22 is applied. At this point of time, since it is in the static friction state, the horizontal component force Nx (1) and the horizontal component force fx (1) cancel each other and the force in the front-rear direction hardly acts on the hammer body 20, so the hammer The body 20 hardly moves in the front-rear direction. On the other hand, in the vertical direction, the sum of the vertical component force Ny (1) and the vertical component force fy (1) (here, equal to the key pressing force F (1)) is applied to the inclined surface portion 22, and the hammer body 20 is thereby It turns.

  The static friction state continues until the state of (d), (e), and (f) in the figure, and the action relationship of force is the same as the state of (a), (b), and (c) in the figure. With a weak key press, the player presses the key body 10 so that the key body 10 rotates slowly at a substantially constant speed, so that the key pressing force F is maintained while the static friction state continues. It is substantially constant (that is, F (1) = F (2)). However, since the inclination angle of the inclined surface portion 22 gradually increases, the frictional force f gradually increases (f (1) <f (2)). Since the state shown in FIG. 4D is a limit state where the static friction state can be maintained, the frictional force f (2) is equal to the maximum frictional force determined by the static friction coefficient.

  If the key is slightly advanced from the state shown in FIG. 4D, the frictional force f cannot exceed the maximum frictional force, and the sliding friction state between the hammer driving portion 12 and the slope portion 22 is a static friction state. Abruptly transitions to a dynamic friction state ((g) in the figure). That is, slipping occurs. Actually, even if slippage occurs, it may be repeated in small steps between a static friction state and a dynamic friction state at the beginning. Since the dynamic friction coefficient is smaller than the static friction coefficient, the frictional force f decreases rapidly (that is, f (3) <f (2)) ((h) in the figure). As a result, the horizontal component force fx (3) becomes smaller than the horizontal component force Nx (3) ((i) in the figure), so that the hammer body 20 receives a rearward biasing force after shifting to the dynamic friction state. Therefore, the turning arm 33 turns counterclockwise, and the hammer body 20 is displaced backward.

  Further, after the hammer body 20 starts moving backward, the frictional force f is small, so that it is perpendicular to the horizontal component force Nx regardless of the magnitude of the key pressing force F as compared with the static friction state. Since the component force fy relatively decreases, the backward movement has priority over the rotational movement in the key pressing direction. When the weight of the weight 21 is won, the hammer body 20 stops rotating in the forward direction, and conversely rotates in the backward direction (FIGS. (J) to (l)). Then, when the hammer drive unit 12 is detached from the slope part 22, the frictional state generated in the slope part 22 disappears, and the drive relationship between both ends via friction, and as shown in FIG. The same key depression end state as in (c) is entered.

  In this way, with a weak key press, the driving relationship between the key body 10 and the hammer body 20 continues until near the end of the key pressing process, and the load of the hammer body 20 is sufficiently applied to the key body 10, resulting in a heavy touch, Performance expression such as “for” becomes easy.

  Next, with reference to FIG. 7, the operation in “raw piano setting” and strong key pressing will be described. First, when the key is pressed quickly from the non-key-pressed state shown in FIG. 7A (same as FIG. 5A), the hammer drive unit 12 and the sloped portion 22 are initially subjected to a static friction state without any substantial friction. It becomes a dynamic friction state. Therefore, from the beginning of the rotation of the key body 10, a state similar to that shown in FIGS. Therefore, the hammer body 20 hardly rotates in the key pressing direction, the rotation arm 33 rotates counterclockwise, and the hammer body 20 quickly moves backward.

  Then, as shown in FIG. 7B, at a stage sufficiently before the end of the key press, the hammer drive unit 12 is detached from the inclined surface portion 22, and the drive relationship between the two via friction ends. As shown in FIG. 7 (c), the key pressing end state of the key body 10 is the same as in FIG. 5 (c). Accordingly, the load of the hammer body 20 is hardly applied to the key body 10 in the key pressing forward process, and the touch is light. The mode of transition from FIG. 7 (c) to FIG. 7 (d) after releasing the key pressing force is exactly the same as the mode of transition from FIG. 5 (c) to FIG. 7 (d).

  In this way, with a strong key press, the driving relationship between the key body 10 and the hammer body 20 is terminated at the very beginning of the key pressing process, so that the touch is felt lighter than with a weak key press, thereby allowing the player to play quickly. And the ability to express repeatedly improves. In addition, in common with weak keys and strong keys, the key body 10 is not subjected to the load of the hammer body 20 while the key is being pressed. Fingers are less likely to get tired because the force required to continue the condition is weak.

  Here, during the transition from FIG. 7A to FIG. 7B, the amount of rotation of the hammer body 20 in the clockwise direction or the clockwise rotation force applied to the hammer body 20 is the key pressing strength. Depending on the situation, the free end of the hammer body 20 may not be separated from the lower limit stopper 5 for the hammer, and the hammer body 20 may not rotate at all. That is, when the key pressing speed is high, the amount of rotation of the hammer body 20 in the clockwise direction (key pressing direction) tends to be smaller than when the key pressing speed is low. Further, depending on the initial position of the hammer body 20, it is possible to prevent the hammer body 20 from rotating clockwise at all beyond a predetermined key pressing speed.

  Further, in the “raw piano setting”, the key body is set at the same key pressing speed by setting the initial position of the hammer body 20 by the initial position adjusting mechanism AM1 in both the weak key press and the strong key press. 10 and the end timing of the driving relationship between the hammer body 20 can be made different. Accordingly, the operation of the hammer body 20 is different even at the same key pressing speed, and as a result, the key pressing feeling can be arbitrarily changed according to the music, the user's preference, the tone color, and the like.

  When changing the key-pressing feeling, the above-mentioned “batch adjustment” is usually performed in units of two octaves, and the initial position of the hammer body 20 is commonly adjusted with respect to all pitches. You can easily set the key press feel. Furthermore, by the “individual adjustment”, it is possible to further optimize the key pressing feeling of the individual key bodies 10.

  Next, the operation in the case of “organ setting” will be described with reference to FIG. FIG. 8 is a side view of the keyboard apparatus in “organ setting”, and shows the transition of the operation of the key body 10 and the hammer body 20. In “organ setting”, the mode of transition is the same for both weak and strong key presses, although the speed of operation is different.

  “Organ setting” is set by displacing the initial position of the hammer body 20 backward to a position where the key body 10 is not in contact with or engaged with the hammer body 20 in the entire key pressing process by the above-described “batch adjustment”. The As for the position of the collective adjustment slide member 45, a standard position corresponding to “live piano setting” and a position corresponding to “organ setting” are set as preset positions, and a mark, a pin, or the like is provided on the fixing member 46. You may comprise so that it can switch easily in two steps.

  First, as shown in FIG. 8A, the hammer driving portion 12 of the key body 10 and the tip of the hammer body 20 are separated in the front-rear direction in a non-key-pressed state. Therefore, even if the key is depressed, as shown in FIGS. 2B and 2C, the hammer driving portion 12 and the slope portion 22 do not engage with each other. Rotate alone without receiving any. When the key pressing force is released, the key body 10 returns to the non-key pressing position ((d) in the figure).

  Thus, the “organ setting” makes the touch of the key body 10 extremely light, and is suitable for playing organ music. Therefore, it is possible to easily realize the optimum key pressing feeling when playing the organ while allowing the hammer body 20 to provide inertia.

  Each material of the hammer drive section 12 and the slope section 22 is made of, for example, resin, and the surface state of these is selected or finished so that the friction state between them is desired. Alternatively, a predetermined sheet may be attached, for example, a non-woven fabric formed by applying pressure may be attached. Further, since the frictional state is related to the angle of the inclined surface portion 22 and the tip shape of the hammer driving portion 12, it is desirable to realize an optimum combination by comprehensively considering or experimenting with these.

  Up to this point, the description has been made by paying attention to the key body 10 that is a white key, but the black key is also not shown, but has the same configuration as the spring locking portion 31, the spring 32, the rotating arm 33, and the thread material 36. In the same manner as the hammer body 20, the initial position of the corresponding hammer body is adjusted. A mechanism similar to the initial position adjusting mechanism AM1, the spring locking portion 31, the spring 32, the rotating arm 33, and the thread material 36 may be separately provided for the black key.

  According to the present embodiment, in the “real piano setting”, the engagement state (friction state) between the key body 10 and the hammer body 20 changes suddenly at a predetermined key pressing speed, thereby causing a predetermined pressing operation. When the key is depressed slower than the key speed, the hammer drive unit 12 and the inclined surface portion 22 are engaged in a static friction state in a wide stroke range excluding the second half of the key pressing stroke, while the strong key is pressed faster than the predetermined key pressing speed. At the time of keying, the engagement in the static friction state is completed from the very beginning of the key pressing process. In the dynamic friction state, the movement of the hammer body 20 in the rearward direction has priority over the movement of the hammer body 20 in the key-pressing direction, and the hammer body 20 hardly moves in the key-pressing direction. 20 moves mainly in the key pressing direction. Accordingly, when the key is pressed hard, the load of the hammer body 20 is not applied to the key body 10 as compared to when the key is pressed weakly. Further, the hammer body 20 is driven by the key body 10 through sliding friction generated between the hammer drive unit 12 and the inclined surface part 22 to give an inertial force to the key body 10. The frictional state between the inclined surface portion 22 is rapidly shifted from the static frictional state to the dynamic frictional state when the frictional force is increased, so that the frictional force is released, and thus the hammer body 20 according to the key depression strength is released. Such an operation is realized. Thereby, the touch feeling at the time of strong key press can be set lighter than at the time of weak key press. That is, the inertial force applied to the key body 10 by the hammer body 20 acts lightly when the key is pressed hard and heavier when the key is pressed weakly. A feeling can be realized. In this respect, the key press feeling of this keyboard device does not match the key press feeling of a general acoustic piano, but if the player gets used to the touch that becomes light only when pressing strongly, the touch will be better than the acoustic piano. May be evaluated.

  Further, in the “raw piano setting”, the driving relationship between the hammer drive unit 12 of the key body 10 and the inclined surface portion 22 of the hammer body 20 is terminated during the key pressing process, so Even when the hammer body 20 is not loaded and the key pressing state is continued, the fatigue of the fingers can be reduced. Further, when the key is depressed weakly, a light touch feeling is transferred as in the operation after the state shown in FIG. This can give a let-off feeling that occurs in both the strong touch and the weak touch realized in a live piano, particularly a grand piano.

  Further, the hammer body 20 rotates about the upper rotation fulcrum 35 of the rotation arm 33, and the movement of the hammer body 20 in the front-rear direction is performed by the rotation arm 33 about the lower rotation fulcrum 34. Since it is realized by turning, the durability of the turning and moving mechanism of the hammer body 20 is high.

  Moreover, since the attitude | position of the rotation arm 33 is stabilized by the forward urging | biasing by the spring 32 and the tension | tensile_strength of the thread material 36, the initial position of the rotation arm 33 is maintained stably.

  According to the present embodiment, the initial position adjustment mechanism AM1 can adjust the initial position of the hammer body 20 in the front-rear direction, and can be roughly switched between “raw piano setting” and “organ setting”. By switching between applying / not applying inertial force to the key body 10 by the hammer body 20, it is possible to easily realize a key press feeling of a completely different keyboard device such as a live piano and an organ with a single keyboard device. it can. In addition, in the “raw piano setting”, the degree of engagement between the hammer drive unit 12 and the sloped portion 22 can be adjusted steplessly by the initial position adjustment mechanism unit AM1, thereby the hammer drive unit in the key pressing forward stroke. Since the end timing of the drive relationship between the head 12 and the inclined surface portion 22 can be arbitrarily changed, the manner in which the inertial force is applied to the key body 10 can be made variable, and the key pressing feeling can be changed clearly and widely.

  Further, since the initial position adjusting mechanism AM1 can collectively adjust the hammer body 20 for two octaves, it is possible to change the key pressing feeling of a plurality of keys at once, thereby facilitating the key pressing feeling changing operation. . Furthermore, the provision of the individual adjustment unit 38 makes it possible to individually adjust the key press feeling of each key, which is convenient for fine adjustment.

  As described above, the initial position adjusting mechanism AM1 is not limited to being provided in units of two octaves, but by providing for each predetermined sound range, the key press feeling can be collectively adjusted for each predetermined sound range, and the initial position adjusting mechanism unit AM1 can be pressed according to the sound range. It is also possible to vary the key feel greatly. For example, as one application, it is possible to make the key press feeling completely different depending on the sound range in one keyboard device, such as a grand piano in the low sound range, an upright piano in the high sound range, or an organ. Further, it is possible to easily realize a key press feeling in an intermediate state between the piano and the organ, which is not included in the conventional keyboard device.

  In addition, in this Embodiment, although the predetermined direction which can move separately from the rotation direction of the hammer body 20 was back, it is not restricted to this. In other words, from the viewpoint of releasing the frictional force between the hammer drive unit 12 and the slope portion 22, the direction may be different from the key pressing direction. Further, from the viewpoint of making the engagement relationship between the hammer drive unit 12 and the inclined surface portion 22 variable, the direction may include any component that is perpendicular to the rotation direction of the hammer body 20.

  In the initial position adjustment mechanism AM1, the “live piano setting” and the “organ setting” are normally set by the collective adjustment unit 40. However, instead of the collective adjustment unit 40, both settings are performed in two stages. And a mechanism for changing in a stepless manner. Alternatively, the individual adjustment unit 38 may be used as a mechanism for changing in a stepless manner, and a mechanism for switching in two steps separately from the individual adjustment unit 38 may be provided instead of the collective adjustment unit 40.

  In the present embodiment, the collective adjustment unit 40 is disposed rearward with respect to the individual adjustment unit 38, but may be disposed forward with respect to the individual adjustment unit 38 from the viewpoint of workability. Note that a configuration other than the spring 32 may be adopted as long as the rotating arm 33 is urged forward.

  Next, various modifications of the first embodiment will be described with reference to FIGS.

  [Modification 1] FIG. 9 is a schematic diagram illustrating configurations of a drive unit and a driven unit according to Modification 1 of the first embodiment. In the first embodiment (keyboard device in FIG. 1), the lower end portion of the hammer drive unit 12 that is a drive unit is formed in a side view arc shape, and the inclined surface portion 22 of the hammer body 20 that is a driven unit is a flat surface. Met. In the first modification, the relationship between the two is reversed, the drive unit 51 is formed on a slope, and the driven unit 52 is formed in a side view arc shape.

  Also in this configuration, the action at the time of engagement between the drive unit 51 and the driven unit 52 is the same as that in the first embodiment. That is, in the states shown in FIGS. 6A and 6B, both are in a static friction state, and are in the same state as shown in FIGS. 6A and 6D. In the state shown in FIG. 9C, the dynamic friction state is entered as in FIG. 6J, and then, as shown in FIG. 9D, the drive unit 51 is driven 52 as in FIG. Deviate from. Therefore, the same effects as those of the first embodiment can be obtained.

  [Modification 2] FIGS. 10A to 10D are schematic diagrams illustrating configurations of a drive unit and a driven unit according to Modification 2 of the first embodiment. In the second modification, a cylindrical roller 55 as a driven portion is rotatably held by the roller holding portion 54a of the hammer body 54. The lower end part of the drive part 53 is formed in side view arc shape.

  First, as shown in FIG. 6A, in the initial stage of key depression, a moment MA (1) in the clockwise direction of FIG. On the other hand, in the hammer body 54, the roller 55 is in a static friction state with respect to the roller holding portion 54a of the hammer body 54, and a counterclockwise moment MB (1) in FIG. Works. At this time, the moment MA (1) and the moment MB (1) are balanced, and the roller 55 does not rotate, and the hammer body 54 itself rotates as in the state of FIG. 6A.

  Next, after the rotation angle of the hammer body 54 changes and the moment MA (2) reaches the limit (FIG. 10B) that balances the moment MB (2) (FIG. 10B), the rollers 55 and the rollers of the hammer body 54 The sliding friction state with the holding portion 54a rapidly changes from the static friction state to the dynamic friction state, and the moment MA (3) wins over the moment MB (3) as in the state of FIG. 6 (j). Then, the roller 55 rotates in the clockwise direction (FIG. 10C). The hammer body 54 moves backward. Thereafter, as shown in FIG. 10D, the drive unit 53 is detached from the roller 55 as in FIG.

  [Modification 3] FIGS. 10E to 10H are schematic diagrams illustrating configurations of a drive unit and a driven unit according to Modification 3 of the first embodiment. In the third modification, the hammer body 58 is formed with a driven portion 59 having a slope similar to the slope portion 22 in the keyboard device of the first embodiment, and the roller holding portion 56a of the drive portion 56 includes A cylindrical roller 57 is rotatably held.

  First, as shown in FIG. 5E, in the initial stage of key depression, a moment MD (1) in the clockwise direction from the driven portion 59 acts on the roller 57. On the other hand, in the driving unit 56, the roller 57 is in a static friction state with respect to the roller holding unit 56a of the driving unit 56, and the roller 57 has a counterclockwise moment based on the frictional force from the roller holding unit 56a. MC (1) acts. At this time, the moment MD (1) and the moment MC (1) are balanced, the roller 57 does not rotate, and the hammer body 58 itself rotates as in the state of FIG.

  Next, after the rotation angle of the hammer body 58 is changed and the moment MD (2) reaches the limit (FIG. 10 (f)) that balances the moment MC (2), the roller 57 and the roller holding portion 56a The sliding friction state during the transition from the static friction state to the dynamic friction state suddenly changes, and as in the state of FIG. 10C, the moment MD (3) exceeds the moment MC (3) and the roller 57 It rotates clockwise (FIG. 10 (g)). The hammer body 58 moves backward. Thereafter, as shown in FIG. 10 (h), the drive unit 56 is detached from the driven unit 59 as in FIG. 10 (d).

  As in these modified examples 2 and 3, friction is not directly generated between the key body and the hammer body, but is generated through friction generated between the roller holding portion of either the hammer body or the key body and the roller. Even in the configuration in which the hammer body is driven, the transition of the action of the frictional force can be considered basically the same as in the first embodiment. Therefore, the same effects as those of the first embodiment can be obtained by the second and third modifications.

  In addition, even if it is the structure which provided the roller in both the hammer body and the key body, it is possible to implement | achieve the same function and effect | action.

  [Modification 4] FIGS. 11A to 11C are schematic diagrams illustrating configurations of a drive unit and a driven unit according to Modification 4 of the first embodiment. In the fourth modification, the drive unit is configured to be bendable. That is, the drive unit 60 corresponding to the hammer drive unit 12 has a base 61 and an arm 62, and the arm 62 is bent only at the fulcrum 63 downward with respect to the base 61. Further, a biasing member (not shown) for returning the arm portion 62 to the state shown in FIG. Further, the hammer body 64 is formed with a driven portion 65 that is an inclined surface similar to the inclined surface portion 22 in the keyboard device of the first embodiment.

  In such a configuration, the action in the forward stroke in which the drive unit 60 drives the hammer body 64 is the same as that in the first embodiment. From the initial state shown in FIG. After the sliding with the driving unit 65, the rotation of the hammer body 64, the rearward movement, and the like, the key pressing end state shown in FIG.

  In the first embodiment, the keying end state is reached when the front end of the hammer body 20 is in contact with the rear wall of the hammer drive unit 12. However, in the fourth modification, the drive unit 60 is the hammer body 64. This is different from the first embodiment in that the hammer body 64 does not need to contact the drive unit 60 and is returned to the initial position.

  On the other hand, when the key is released, as shown in FIG. 11C, when the drive unit 60 is about to return, the arm unit 62 is once bent at the fulcrum 63 so that the drive unit 60 is located above the hammer body 64. It can move and easily return to the initial position. Even if the configuration as in Modification 4 is adopted, the effect of the first embodiment is maintained.

  As shown in FIG. 11 (d), a pin 78 is suspended from the hammer body 77 in place of the driven portion 65 that is a slope, and the pin 78 is driven by the drive portion 60. Also good. Such a configuration using the driven part as a pin can also be applied to the first embodiment and the first and third modifications. Moreover, the structure of the drive part which can be bent as illustrated in Modification 4 can be applied to the drive part of the first embodiment or Modifications 1 to 3.

  Next, another modified example of the mechanism for moving the hammer body in the front-rear direction will be described in Modification 5 below. In the first embodiment, the movement of the hammer body 20 in the front-rear direction is realized by the rotation of the rotation arm 33 around the lower rotation fulcrum 34. Various mechanisms are conceivable.

  [Modification 5] FIG. 12A is a perspective view showing a main part of a mechanism for moving the hammer body in the front-rear direction according to Modification 5 of the first embodiment.

  First, a support member 69 is fixed to the chassis 1 instead of the rotating arm 33. A hanging piece 67 is formed to hang down from the lower part of the hammer body 60, and cylindrical pins 68 project from left and right sides of the hanging piece 67. The lower edge of the hanging piece 67 is formed in a side view arc shape. The support member 69 is configured in the same manner as the sliding member shown in FIG. 3 of Japanese Patent No. 3324384. That is, a concave main guide groove 70 for guiding the drooping piece 67 is formed in the support member 69 along the front-rear direction, and the left and right inner surfaces of the main guide groove 70 are used for guiding the pins 68. Pin guide grooves 71 and 72 are formed along the front-rear direction.

  The hanging piece 67 of the hammer body 60 is inserted into the main guide groove 70 of the support member 69, and the pin 68 is inserted into the pin guide grooves 71 and 72, respectively. When the hammer body 60 receives a force in the key pressing direction, the arcuate hanging piece 67 rolls in the main guide groove 70. On the other hand, when the hammer body 60 receives a rearward force, the drooping piece 67 slides backward on the main guide groove 70 to move backward. At that time, the pin 68 also slides in the pin guide grooves 71 and 72, so that the hammer body 60 can smoothly move in the front-rear direction regardless of the rotational position of the hammer body 60. In addition, since the pin 68 is inserted into the pin guide grooves 71 and 72, the hammer body 60 does not fall off from the support member 69 even for shocking key depression.

  Also in this modified example 5, the durability of the turning and moving mechanism of the hammer body is high, and the same effects as in the first embodiment can be obtained.

  From the viewpoint of simplifying the configuration of the hammer body moving mechanism in the front-rear direction, a configuration in which the hammer body 73 is placed on the columnar rotation fulcrum 74 as shown in FIG. It is.

  In the first embodiment and the first, third, and fourth modifications, the drive unit or the driven unit is formed on a flat slope. However, the shape of the slope is not limited to this, and for example, FIG. The concave slope 75 shown in c) or the convex slope 76 shown in FIG. As a result, the change modes of the horizontal component force and the vertical component force applied to the driven part in the key pressing process are not linear, and an arbitrary change mode can be realized by setting the curved surface, so that the key pressing feeling is further desired. It becomes easy to approach.

(Second Embodiment)
FIG. 13 is a side view of a keyboard apparatus according to the second embodiment of the present invention. In the keyboard device of the present embodiment, a key body 110 (a white key is illustrated in the figure) that is operated to press a key on the chassis 112, and a hammer body that gives appropriate inertia to the key body 110 during a key pressing operation. 120 and the like are supported so as to be swingable in the vertical direction. Hereinafter, the free end side (right side of the figure) of the key 110 is referred to as “front”.

  The key body 110 is rotatable at the rear end portion in the vertical direction about the key rotation axis P1. A return spring 113 is suspended over the rear portion of the key body 110 from a substantially central portion in the front-rear direction of the chassis 112. A hammer driving unit 111 for driving the hammer body 120 is provided to hang down from the lower front part of the key body 110. A key pressing switch 114 is provided on the upper portion of the chassis 112, and a key guide 126 is provided on the front portion. Further, an upper limit restricting stopper 125 is provided on the upper rear portion of the chassis 112.

  A lower pivot fulcrum 134 is fixedly provided on the chassis 112, and a pivot arm 133 that pivots clockwise and counterclockwise in FIG. 13 is provided around the lower pivot fulcrum 134. . The hammer body 120 is provided corresponding to each key body 110 and is supported so as to be pivotable in the vertical direction around the upper pivot fulcrum 135 of the pivot arm 133. A driven part 121 described later is provided in the foremost part of the hammer body 120.

  The front part of the rotating arm 133 and the front part of the chassis 112 are connected by a spring 132. On the chassis 112, an initial position adjusting mechanism AM2 is disposed behind the rotating arm 133. A thread material 136 is attached to the upper rear portion of the rotating arm 133, and this thread material 136 is connected to a part (described later) of the initial position adjusting mechanism AM1. The spring 132, the rotation arm 133, and the thread material 136 are provided corresponding to each key body 10, and the spring 32, the rotation arm 33, and the thread material 36 in the first embodiment are arranged and shaped in mutual relationship. Although different, the function is similar.

  FIG. 14A is a side view showing a detailed configuration of the initial position adjusting mechanism AM2 in the keyboard device according to the present embodiment. FIG. 4B is a perspective view of the driven part 121, and FIG. 4C is a schematic view of the driven part 121 and the hammer driving part 111 as viewed from the side.

  The initial position adjusting mechanism AM2 includes a slide base 137, a common slide member 138, an operation arm 140, and the like. The slide base 137 is formed with dovetail grooves 137a similar to the dovetail grooves 37La and 37Ra (see FIG. 3), and the corresponding lower portion of the common slide member 138 has a shape fitting to the dovetail groove 137a. Is formed. The dovetail 137a is along a direction (substantially the same as the longitudinal direction of the thread material 136) substantially parallel to a line connecting the initial position adjusting mechanism AM2 and the upper part of the rotating arm 133, and this direction is a common slide member. 138 is the movable direction.

  The operation arm 140 is rotatable in a clockwise direction and a counterclockwise direction in FIG. 14A by a rotation fulcrum 142 provided on the slide base 137. In addition, an elongated hole 139 is formed in the operation arm 140. A pin 141 protrudes from the common slide member 138, and the pin 141 is inserted into the elongated hole 139 of the operation arm 140. The thread material 136 is connected to the common slide member 138.

  The slide base 137 is disposed on both the left and right sides of the key body 110 for a predetermined octave and is similarly configured symmetrically. The operation arm 140 is provided so as to be bridged to the slide bases 137 on both sides. At least one operation arm 140 is provided with respect to the key body 110 for a predetermined octave, for example, one side or both left and right sides.

  With this configuration, when the user rotates the operation arm 140, the common slide member 138 moves in the movable direction with respect to the slide base 137 via the long hole 139 and the pin 141. As a result, as in the first embodiment, the rotational position of the rotational arm 133 is restricted, so that the initial position of the hammer body 120 can be adjusted collectively for the key body 110 for a predetermined octave. it can.

  As shown in FIG. 14B, a cylindrical roller 123 is provided at the tip of the driven part 121 so as to be rotatable around a rotation fulcrum 124. Unlike the rollers 55 and 57 shown in FIG. 10, the roller 123 is configured such that sliding friction during rotation is minimized. Further, as shown in FIG. 14C, the driven portion 121 is formed with a slope portion 122 similar to the slope portion 22 of the hammer body 20 in the first embodiment. The roller 123 is disposed so as to protrude slightly from the slope portion 122 in the direction perpendicular to the slope portion 122.

  In such a configuration, when the driven part 121 is driven with a weak key by the hammer driving part 111, the operation of the hammer driving part 111 and the slope part 122 is halfway (until the hammer driving part 111 abuts on the roller 123. ) Is the same as the operation of the hammer drive section 12 and the slope section 22 in the first embodiment (see FIGS. 6A to 6L).

  However, when the hammer driving unit 111 comes into contact with the roller 123, the roller 123 protrudes, so that the key pressing reaction force is temporarily increased or the degree of decrease is temporarily reduced. Thereby, the let-off feeling in an acoustic piano appears more clearly.

  In the first embodiment, the upper limit stopper for the hammer body 20 is not provided. However, in the second embodiment, unlike the first embodiment, as described above, the upper limit restriction stopper. 125 is provided. That is, in the normal key pressing mode, the rear end portion 120a of the hammer body 120 does not come into contact with the upper limit regulating stopper 125, but the hammer body 120 is changed due to secular change (change in frictional state, etc.), extremely key pressing, or the like. Even if the rotation end position is unexpected, the impact received by the finger from the key body 110 is mitigated by the presence of the upper limit regulating stopper 125.

  According to the present embodiment, except for the individual adjustment of the initial position of the hammer body, the same effect as in the first embodiment is obtained, and the operation arm 140 collectively adjusts the initial position of the hammer body 120. Is easier to do. Moreover, since the roller 123 is provided in the driven part 121, a specific let-off feeling is realized in a clearer form when the live piano is weakly pressed. On the other hand, when the key is strongly pressed, the driving force by the hammer driving unit 111 is not transmitted to the roller 123, but is transmitted to the hammer body 120 in the initial stage of the key pressing. A feeling of let-off at the time of key can be realized.

  Also in the second embodiment, it is desirable to provide the same configuration as the initial position adjusting mechanism AM1 in the first embodiment so that the initial position of the hammer body 120 can be individually adjusted. For example, a weight having a function for returning the key body 110 corresponding to the weight 11 in the first embodiment may be provided at the front portion of the key body 110.

  In the first embodiment, the operation mechanism using the operation arm 140 in the second embodiment may be adopted as the moving mechanism of the collective adjustment slide member 45 with respect to the fixing member 46. Further, in the first embodiment, the roller 123 in the second embodiment may be employed.

  In the first and second embodiments, the mechanism for adjusting the initial position of the hammer body is not limited to that illustrated. The operation method for adjustment is not limited to manual operation, and an electric or electromagnetic movement mechanism may be used. Further, as the initial position adjusting mechanism portions AM1 and AM2, as a mechanism for pulling the thread material, a mechanism for winding the thread material may be adopted so that the initial position of the hammer body can be adjusted by the winding amount. .

(Third embodiment)
FIG. 15 is a side view of a keyboard apparatus according to the third embodiment of the present invention. The third embodiment is mainly different from the first embodiment in that the hammer body 220 corresponding to the hammer body 20 is configured such that the operation direction associated with key pressing is not the rear but the front. Different. Accordingly, in addition to the hammer body 220, a spring 232, which is a compression spring, is used instead of the spring 32, which is a tension spring, and an initial position adjusting mechanism AM3 is used instead of the initial position adjusting mechanism AM1, respectively. It differs from the first embodiment in that a tension spring 245 is provided at the rear end portion of the key body 10 instead of the weight 11 as having a function for returning the key body 10.

  A flat slope portion 222 facing rearward and upward is formed at the frontmost portion of the hammer body 220, and this slope portion 222 functions as a driven portion that is driven by the hammer drive portion 12 of the key body 10. The front portion of the rotating arm 33 and the spring locking portion 31 are connected by a spring 232.

  Further, the initial position adjustment mechanism AM3 is configured such that the gear 243 is fixed to the gear base 242 fixed to the chassis 1 and the worm 244 is engaged with the gear 243. The worm 244 is rotated by the motor 241 and meshed with the gear 243, so that the worm 244 moves substantially in the front-rear direction along with the rotation. The stop position of the motor 241 is defined by a position sensor (not shown) that detects the back-and-forth movement of the worm 244.

  The upper half of the rotating arm 33 is urged rearward by the spring 232 around the lower rotating fulcrum 134, and the front end of the worm 244 contacts the rear wall of the rotating arm 33. It resists the urging force of the spring 232. Thus, the initial position of the rotary arm 33 can be adjusted at the position of the worm 244, and when the hammer body 120 receives a force to move forward, the spring 232 contracts and the rotary arm 33 is retracted. Can be rotated forward.

  The operation at the time of key pressing is the same as that of the first embodiment except that the moving direction of the hammer body 220 changes from the rear to the front. As for the initial position adjusting mechanism AM3, the organ setting and the live piano setting can be set by adjusting the position of the worm 244 in the same manner as the initial position adjusting mechanism AM1.

  According to the present embodiment, the same effects as those of the first embodiment can be obtained except for the individual adjustment of the initial position of the hammer body.

1 is a side view of a keyboard device according to a first embodiment of the present invention. It is a partial top view of this keyboard apparatus. It is a side view of an initial position adjustment mechanism part. It is a front view (figure (a)) of a collective adjustment part, and a front view (figure (b)) of an individual adjustment part. FIG. 5 is a side view of the keyboard device when a weak key is pressed in “Raw Piano Setting”. It is a schematic diagram showing the interrelationships of key pressing force, vertical drag force, and frictional force at the time of “raw piano setting” and weak key pressing. FIG. 5 is a side view of the keyboard device when a key is strongly pressed in “Raw Piano Setting”. It is a side view of the keyboard device in “organ setting”. It is a schematic diagram which shows the structure of the drive part and driven part which concern on the modification 1 of 1st Embodiment. It is a schematic diagram which shows the structure of the drive part and driven part which concern on the modification 2 of 1st Embodiment. It is a schematic diagram which shows the structure of the drive part and to-be-driven part which concern on the modification 4 of 1st Embodiment. The perspective view (figure (a)) which shows the principal part of the movement mechanism to the front-back direction of the hammer body which concerns on the modification 5 of 1st Embodiment, The movement mechanism to the front-back direction of the hammer body which concerns on another example FIG. 6 is a schematic diagram showing a main part (FIG. (B)) and a side view (examples (c) and (d)) showing an example of a driven part according to another example. It is a side view of the keyboard apparatus which concerns on the 2nd Embodiment of this invention. The side view (Drawing (a)) which shows the detailed composition of the initial position adjustment mechanism part in the keyboard device of a 2nd embodiment, the perspective view (Drawing (b)) of a driven part, a driven part, and a hammer drive It is a schematic diagram (figure (c)) by the side view of a part. It is a side view of the keyboard apparatus which concerns on the 3rd Embodiment of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Chassis (support member), 4 Key press switch (returning bias means), 10 Key body (key), 11 Weight (key return means), 12 Hammer drive part (drive part), 20 Hammer body (arm), 22 Slope (driven part), 32 Spring, 33 Rotating arm (Rotating member), 34 Lower rotating fulcrum (part), 35 Upper rotating fulcrum (Rotating fulcrum), 36 Yarn material, 38 Individual adjustment Part (adjustment means), 40 collective adjustment part (adjustment means), AM1 initial position adjustment mechanism part (switching means)

Claims (6)

A support member;
A key that has a drive unit, is rotatably supported by the support member, and is operated to be pressed and released in a rotation range from a key release state to a key press state;
A key return means that operates to always return the key in the direction of the key release state within the rotation range of the key;
A rotation member supported by the support member so as to be rotatable at a first rotation fulcrum;
Wherein provided on the rotating member, wherein the first pivot point pivotally supported by the different second pivot point, has a driven portion, by the driven portion is the driven portion of the key An arm that rotates around the second pivot point and applies an inertial force to the key when the key is depressed;
In at least some forward stroke of key depression operation, a first state in which the driven portion of the arm is driven to the driving portion of the key, the key depression entire stroke, the driven portion of said arm the Switching means for switching between a second state that is not driven at all by the drive part of the key;
It possesses an adjustment means for adjusting the degree of engagement with the driven part and the driving part in the first state,
The arm is configured to be displaceable in a predetermined direction different from the key pressing direction by the rotation of the rotation member around the first rotation fulcrum,
The keyboard device according to claim 1, wherein the switching means switches the first and second states by displacing the arm in the predetermined direction . Said key and said arm is provided with a plurality to correspond to each other, said switching unit, a keyboard apparatus according to claim 1, wherein the displacing in the predetermined direction together multiple arms. Adjusting the degree of engagement between the driving portion and the driven portion in the first state by previous SL adjustment means according to claim 1 characterized in that it is made by displacing the arm in the predetermined direction or 2. The keyboard device according to 2 . A plurality of the keys and the arms are provided corresponding to each other, and the adjusting means is provided for each arm, and each adjusting means is provided with a key driving unit corresponding to the driven part for each corresponding arm. keyboard apparatus according to claim 1, characterized in that the degree of engagement is adjustable to. A support member;
A key that has a drive unit, is rotatably supported by the support member, and is operated to be pressed and released in a rotation range from a key release state to a key press state;
A key return means that operates to always return the key in the direction of the key release state within the rotation range of the key;
An arm that has a driven portion, and that is driven by the driving portion of the key so as to rotate and apply an inertial force to the key when the key is depressed;
Adjusting means for adjusting the degree of engagement between the driven part of the arm and the driving part of the key;
In at least some forward stroke of key depression operation, the driven portion of the arm is driven in the driving portion of the key, and, the forward stroke as the way the driver of the key depression operation of the driven part The drive relationship is configured to end,
The adjusting means adjusts the degree of engagement between the driven portion and the driving portion collectively for a plurality of keys, thereby driving the driving portion and the driven portion in the forward stroke of the key pressing operation. A keyboard device characterized by changing the end timing of the relationship . A return urging means for restricting a key pressing end position of the key in contact with the key in the key pressing state and for urging the key in the direction of the key releasing state when in contact with the key; The keyboard device according to claim 1 , wherein the keyboard device is provided.

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