JP2011158757A - Action unit of grand piano - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an action unit of a grand piano capable of easily and accurately adjusting a static load of a key of the grand piano, and a mass of a hammer head, which is easily installed in a limited space in the grand piano. <P>SOLUTION: In the action unit 1 of the grand piano, including a wippen 20, a repetition lever 23 and a hammer 32, a first spring 46 is mounted between a first member 40, and a second member 41, wherein the repetition lever 23 being the first member 40, a hammer shank 33 of the hammer 32 being the second member 41. The first member 40 is pressed to a direction of the key 10 by the first spring 46, and the second member 41 is pressed to a direction of a string 80. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an action of a grand piano.

The action of a typical conventional grand piano will be described (see Non-Patent Document 1). In the following explanation, unless otherwise noted, the front side is called “front”, the back side is “back”, the left side is “left”, and the right side is “right”. I will do it.
The action of the grand piano has a key, a whippen, a repetition lever, a hammer, and a hammer stop rail. Some grand piano actions have hammer rests instead of hammer stop rails. Wippen has a repetition lever frenzy, a repetition lever and a jack. The hammer has a hammer shank, a hammer head, and a hammer shank roller.

When the action of the grand piano is not activated and the key is in the rest position, the rear end of the key is in the lowest position and the hammer is stationary.
When the performer presses the key in the stationary position, the rear end of the key rises, the whippen moves up, the repetition lever pushes up the hammer roller, the jack pushes up the hammer roller, and the hammer rotates. The hammer head hits the string. Thereafter, the hammer descends while rotating in reverse. When the performer releases the key, the key returns to the rest position.

When the performer presses a key at a stationary position, the load of the hammer, wippen, jack, repetition lever, hammer, etc. is transmitted to the performer's finger as a so-called static load of the key. The performer plays the grand piano by pressing the key with a force that exceeds the static load of the key.
The static load of the key is an important parameter that affects the touch feeling of the grand piano, and greatly affects the quality of the grand piano. Therefore, the adjustment of the static load of the key is very important in the grand piano. At present, the static load of a general key is adjusted to about 47 to 55 g. In order to adjust the static load of the key, many grand pianos have a lead weight embedded in the front end portion of the key.

In addition, although the unit of the static load of the key was described as “g” according to the convention, if this is described in the SI unit, the static load of 47 to 55 g is 0.46 to 0.54 N. In order to change the unit of the static load of the key from “g” to “N”, a value of 9.80665 × 10 ⁻³ may be multiplied.
At one time, the static load on the keys of a grand piano manufactured in Japan was approximately 62-67 g. Current performers feel that the static load of such keys is too heavy. Therefore, it is necessary to lightly adjust the static load of the key. Further, since the static load of the key fluctuates due to secular change, it is necessary to adjust the static load of the key. When adjusting the static load of the key, the mass of the weight buried in the key may be changed. However, when changing the mass of the weight buried in the key, it is necessary to replace the weight one by one, and the work is complicated.

  Therefore, in order to adjust the static load of the key, a technique described below has been proposed (hereinafter, this technique is referred to as “prior art 1”) (see Patent Document 1). Prior art 1 has a tension spring above the hammer shank and an attachment for suspending the tension spring. The tip of the tension spring is fixed to the upper surface of the hammer shank. The tension spring applies an upward force to the hammer shank, and torque acts in the rotating direction of the hammer shank.

  Another form of technology has been proposed (hereinafter, this technology is referred to as “prior art 2”) (see Patent Document 1). Prior art 2 has a mounting rod and weight above the hammer shank. The weight is screwed into the front end portion of the mounting rod, and the rear end portion of the mounting rod is fixed to the upper surface of the hammer shank. The front end of the mounting bar extends farther forward than the hammer shank flange. And a torque acts on the rotation direction of a hammer shank with a weight. When the position of the weight moves on the mounting rod, the static load of the key changes.

JP 2002-41028 A

Nishiharu Yasuharu, Taro Mori, “The Piano Structure I Want to Know More”, 1st Edition, Ongaku no Tomosha, April 30, 2005, p. 48-49, 58-70

In Prior Art 1, the fixture must be installed above the hammer shank. When installing such a fixture, there is a problem that the space inside the grand piano is limited. Moreover, when installing a fixture on an existing grand piano, a large-scale modification is required.
In Prior Art 2, the mounting rod extends greatly forward from the hammer shank flange. Similar to the prior art 1, when the mounting rod is installed, there is a problem that the space inside the grand piano is limited. Further, since the rear end portion of the mounting rod is fixed to the upper surface of the hammer shank, the load of the mounting rod and the weight acts on the hammer shank. As a result, the load of the mounting bar and the weight is transmitted to the key through the wippen, and the static load of the key becomes heavy.

Further, if the hammer head is made heavy, the contact between the hammer head and the strings can be strengthened, and if the hammer head is lightened, the contact between the hammer head and the strings can be softened. Therefore, it may be required to change the mass of the hammerhead. However, the weight of the hammerhead is transmitted to the key as it is and affects the static load of the key. Also, from the viewpoint of preventing the balance of touch feeling from being lost, the mass of the hammerhead cannot be changed to darkness.
The present invention solves the above-mentioned problems, and an object of the present invention is to easily and accurately adjust a static load of a key of a grand piano and a mass of a hammer head, and a limited space in the grand piano. It is to provide a grand piano action that can be installed easily and comfortably.

  The present invention adopts the following configuration in order to solve the problem. The action of the grand piano according to the first aspect of the invention is such that the whippen pivotally supported by the whippen frenzy fixed to the whippen rail and the repetition lever frenzy formed on the whippen can be turned. It is equipped with a pivoted repetition lever, a hammer pivotally supported by a hammer shank flange fixed to the hammer shank rail, and a hammer stop rail formed below the hammer shank of the hammer. The action of a grand piano in which the hammer rotates toward the string when the performer presses the key, the whippen rail, the whippen frenzy, the whippen, the repetition lever frenzy, and the A repetition lever, the hammer shank rail, Any one of the hammer shank flange and the hammer stop rail constitutes a first member, the hammer shank constitutes a second member, and the first spring constitutes the first member. And the second member, and is supported between the first member and the second member, and is mounted between the first member and the second member, and the key is in a stationary position. Sometimes, the first spring is sandwiched and bent between the first member and the second member, and presses the first member in the direction in which the key is located, and the second member Is pressed in the direction of the string.

  The action of the grand piano according to the invention of claim 2 is such that the whippen pivotally supported by the whippen flange fixed to the whippen rail and the repetition lever flange formed on the whippen can be rotated. It is equipped with a pivoted repetition lever, a hammer rest formed on the whippen, and a hammer pivotally supported by a hammer shank flange fixed to the hammer shank rail. When pressed, it is an action of a grand piano in which the hammer rotates toward the string, and the whippen rail, the whippen frenzy, the whippen, the repetition lever frenzy, the repetition lever, and the hammer A rest, the hammer shank rail, and the hand -Any one of the shank frenzy forms the first member, the hammer shank of the hammer forms the second member, and the first spring includes the first member and the second member. Is mounted between the first member and the second member, supported by either or both of the members, and when the key is in a stationary position, the first One spring is sandwiched and bent between the first member and the second member, presses the first member in the direction in which the key is located, and the second member is the string Press in the direction.

The action of the grand piano according to the invention of claim 3 is the action of the grand piano according to claim 1 or 2, wherein the player returns to the rest position after pressing the key in the rest position. In the meantime, the first spring strikes the first member and the second member without leaving.
The action of the grand piano according to the invention of claim 4 is the action of the grand piano according to any one of claims 1 to 3, wherein the second spring is the hammer shank flange. It is supported by any one of the hammer shank rail and the hammer shank, and when the hammer hits the string, the second spring is the hammer shank flange or the hammer shank rail, The hammer shank is bent between the hammer shank and the hammer shank is pressed in the direction of the key.

  The action of the grand piano according to the invention of claim 5 is the action of the grand piano according to claim 4, wherein the second spring is based on any one of the hammer shank flange and the hammer shank rail. When supported, only when the hammer strikes the string, the second spring strikes the hammer shank and deflects, and the deflected second spring presses the hammer shank in the direction of the key. However, when the second spring is supported by the hammer shank, the second spring is deflected by hitting the hammer shank flange or the hammer shank rail only when the hammer strikes the string. The second spring holds the hammer shank in the key It is pressed in a certain direction.

The inventor of the present application, after trial and error, mounts the first spring between the first member and the second member, and the first member is locked by the first spring in the direction in which the key is located (ie, the downward direction). It was found that the static load of the key changes if the second member is pressed in the direction in which the string is present (ie, upward) with the first spring.
When the first member is one of the wippen, the repetition lever frenzy, the repetition lever, and the hammer rest, the force by which the first spring presses the first member in the direction in which the key is located is via the wippen. To the key. This force with which the first spring presses the first member affects the static load of the key and the rotational moment of the whippen.

  When the first member is one of the Wippen rail, the Wippen frenzy, the hammer shank rail, the hammer shank frenzy, and the hammer stop rail, the first spring moves the first member in the direction of the key. The pressing force is transmitted to the bracket that fixes the first member, but not to the key. This force with which the first spring presses the first member does not affect the static load of the key and the rotational moment of the whippen.

The force with which the first spring presses the second member in the direction of the string affects the rotational moment of the hammer.
When the position where the first spring presses the second member moves from the front side to the rear side, the static load of the key becomes lighter. Further, when the first member is any one of the wippen, the repetition lever frenzy, the repetition lever, and the hammer rest, the position where the first spring presses the first member moves from the front side to the rear side. The static load on the key will be lighter.

The magnitude and position where the first spring presses the first member, the magnitude and position where the first spring presses the second member, and the mass of the first spring The mass of the hammer head and the static load of the key influence each other. The static load of the key and the mass of the hammer head can be adjusted by adjusting the elastic coefficient, shape, and mounting position of the first spring.
Based on the above knowledge, the present inventor has determined the magnitude and position of the force that the first spring presses the first member, and the magnitude and pressure of the force that the first spring presses the second member. A relational expression is obtained that is established between the position of the first spring, the mass of the first spring, the mass of the hammer head, and the static load of the key. If this relational expression is used, the details (namely, the elastic coefficient, the shape, and the mounting position) of the first spring necessary for obtaining the desired static load of the key and the mass of the hammer head are determined.

  Examples of the first spring include a leaf spring and a torsion coil spring. The first spring may be supported by any one of the first member and the second member, or may be supported by both. However, the first spring must hit both the first member and the second member at least when the key is in the rest position. When the first spring is supported on a certain member, the first spring is in contact with the member at the supported position.

  When the first spring hits or leaves the first member or the second member, the place where the first spring hits or leaves can be covered with a flexible material. Such covering prevents noise from being generated when the first spring hits or leaves the first member or the second member. Examples of the flexible material include various cloths such as felt, resin, and rubber.

A configuration is possible in which the first spring is always in contact with the first member and the second member from when the performer presses the key at the rest position until the key returns to the rest position. . With this configuration, the first spring does not hit or separate from the first member or the second member, and generation of noise is prevented.
Interference between the first spring and another member can be avoided by adjusting the shape of the first spring. Further, by adjusting the shape of the first spring, the magnitude of the force with which the first spring presses the first member and the second member and the pressing position are adjusted.

  Since the static load of the key can be adjusted using the first spring, it is not necessary to bury a lead weight in the front end side portion of the key, and the mass of the front end side portion of the key is lighter than that of a conventional grand piano. When a player who has depressed a key releases his / her finger from the key, the rear end portion of the key is lowered by the force received from the wippen or the like, the front end portion of the key is raised, and the key returns to the rest position. If the mass of the front end portion of the key is reduced, the key reacts sharply by the force applied from the wippen or the like, and the time required for the key depressed by the performer to return to the rest position is shortened. Therefore, the performer can press the same key more times within a certain time to sound the same string, and the repeatability of the same key on the grand piano is improved.

When the hammer strikes the string, if the second spring presses the hammer shank in the direction of the key, the return speed of the hammer that strikes the string and returns to the rest position is accelerated. Further, the first spring presses the hammer shank in the direction of the string, and the second spring prevents the return of the hammer to the rest position due to this pressing.
When the hammer strikes the string, the amount of deflection of the second spring is maximized, and the amount of deflection of the second spring decreases as the hammer moves away from the string. With this configuration, it is possible to reduce or prevent an increase in the static load of the key due to the force acting from the second spring.

It can be configured that the second spring presses the hammer shank only when the hammer strikes the string. In such a configuration, the second spring does not press the hammer shank when the key is in the rest position. The force acting from the second spring prevents the static load of the key from becoming heavy.
Examples of the second spring include a leaf spring and a torsion coil spring.
Interference between the second spring and another member can be avoided by adjusting the second spring shape. Further, by adjusting the shape of the second spring, the magnitude of the force with which the second spring presses the hammer shank and the position to press it are adjusted.

When the second spring is supported by the hammer shank, the mass of the second spring affects the static load of the key. In this case, the static load of the key and the mass of the hammer head can be adjusted by adjusting the mass of the second spring.
When the second spring hits or leaves any one of the hammer shank, hammer shank frenzy and hammer shank rail, the position where the second spring hits or leaves can be covered with a flexible material It is. Such covering can prevent noise from being generated when the second spring hits or leaves.

  Because it is an action of the grand piano as described above, the static load of the key of the grand piano and the mass of the hammer head can be adjusted easily and accurately, and it can be easily installed in a limited space inside the grand piano. Is possible.

It is a block diagram of the action which concerns on Example 1 seen from the left side when a key exists in a rest position. It is a side view of the 1st spring and the 2nd spring. It is a block diagram of the action which concerns on Example 1 seen from the left side in the moment when a hammer head strikes a string. It is a block diagram of the action which concerns on the comparative example when a key exists in a rest position. It is a block diagram of the action which concerns on Example 3 when a key exists in a rest position. It is a block diagram of the action which concerns on Example 6 when a key exists in a rest position. It is a block diagram of the action which concerns on Example 8 when a key exists in a rest position. It is a block diagram of the action which concerns on Example 13 when a key exists in a stationary position.

Example 1 which is an embodiment of the present invention will be described with reference to FIGS.
The action 1 of the grand piano according to the first embodiment has the same configuration as that of the conventional one except that it includes a first spring 46 and a second spring 54 described later.
The action 1 includes a key 10, a whippen 20, a repetition lever 23, and a hammer 32.
A large number of keys 10 (only one is shown) are arranged on the ridge 11 in the left-right direction. A hole 13 for receiving a balance pin 12 is formed in the center of the key 10. The key 10 is supported so as to be swingable with the balance pin 12 as a fulcrum. A cap stan screw 14 is formed between the center portion and the rear end portion of the key 10. A back check 15 is formed at the rear end of the key 10. Note that the longitudinal axis of the key 10 is referred to as an axis X1.

A heel 21 at the lower end of the wippen 20 hits the cap stun screw 14. The rear end portion of the wippen 20 is pivotally fixed to the wippen flange 63 by a pin 72 so as to be rotatable. The wippen frenches 63 are fixed to the wippen rails 64. The wippen rail 64 is bridged and fixed between the left and right brackets 62 (only one is shown).
A strut is formed on the upper side surface of the central portion of the wippen 20 as a repetition lever flange 22. An intermediate portion of the repetition lever 23 is pivotally fixed to an upper end portion of the repetition lever flange 22 by a pin 73 so as to be rotatable.

An L-shaped jack 24 is pivotally fixed to a front end portion of the wippen 20 by a pin 74 so as to be rotatable. The jack 24 has a push-up portion 25 and a jack tail 26. The leading end of the push-up portion 25 is inserted into a hole (not shown) penetrating vertically formed in the front end portion of the repetition lever 23.
The wippen 20, the repetition lever flange 22, the repetition lever 23, and the jack 24 form a part that rotates integrally with the wippen flange 63 as a center.

  The hammer 32 includes a hammer shank 33, a hammer head 34, and a hammer shank roller 35. The front end portion of the hammer shank 33 is pivotally fixed to the hammer shank flange 65 by a pin 75. The hammer shank flange 65 is fixed to the hammer shank rail 66. The hammer shank rail 66 is bridged between the left and right brackets 62 and fixed. A hammer head 34 is attached to the rear end of the hammer shank 33, and a hammer shank roller 35 is attached to the lower surface near the front end of the hammer shank 33. The longitudinal axis of the hammer shank 33 is referred to as an axis X2.

The hammer shank 33, the hammer head 34, and the hammer shank roller 35 form a part that rotates integrally around the hammer shank flange 65.
The repetition lever 23 is positioned below the hammer shank 33. When the key 10 is in the rest position, the hammer shank roller 35 is in contact with the repetition lever 23. The position P3 where the hammer shank roller 35 hits the repetition lever 23 is a position where the hole at the front end of the repetition lever 23 is present.

A hammer stop rail 67 is formed below the rear end portion of the hammer shank 33 and above the rear end portion of the wippen 20. The hammer stop rail 67 is bridged between the left and right brackets 62 and fixed.
A string 80 is stretched above the hammer head 34.
The repetition lever 23 forms the first member 40, and the hammer shank 33 forms the second member 41.

A first spring 46 is mounted between the first member 40 and the second member 41. As shown in FIG. 2, the first spring 46 is a torsion coil spring, and has a coil portion 47 and two legs 48 and 49. The foot 48 extends from one end of the coil portion 47, and the foot 49 extends from the other end of the coil portion 47. A foot 48 is implanted on the upper side surface of the first member 40. The position where the foot 48 is implanted is a position P <b> 1 where the first spring 46 hits the first member 40.
The position P1 is behind the position P3 and the pin 73. The foot 49 extends forward and obliquely upward. When the key 10 is in the stationary position, the tip of the foot 49 is in contact with the second member 41 from below at the position P2. The position P2 is closer to the hammer head 34 than the hammer shank roller 35.

  The first spring 46 has a shape in which the amount of bending of the first spring 46 is maximized when the hammer 32 is at the lowest position. Further, when the hammer head 34 strikes the string 80, the first spring 46 has the deflection amount of the first spring 46 zero, and the tip of the foot 49 hits the second member 41 from below. Has a shape. That is, the first spring 46 has a shape in which the first spring 46 is always in contact with the first member 40 and the second member 41. In order to create such a shape, the lengths and bending of the legs 48 and 49 may be selected as appropriate.

  A second spring 54 is mounted between the hammer shank flange 65 and the hammer shank 33. As shown in FIG. 2, the second spring 54 is a torsion coil spring, and has a coil portion 55 and two legs 56 and 57. The foot 56 extends from one end of the coil portion 55, and the foot 57 extends from the other end of the coil portion 55. The feet 56 are implanted on the upper side of the hammer shank flange 65. The position where the foot 56 is implanted is in front of the pin 75. The foot 57 extends rearward, and the tip of the foot 57 is positioned above the hammer shank 33. The second spring 54 is curved in a mountain shape, and has a shape in which the tip of the foot 57 hits the hammer shank 33 from above only when the hammer head 34 strikes the string 80. In order to make such a shape, the length of the legs 56 and 57 and the degree of bending may be appropriately selected.

Next, the operation will be described. In the following description, the static load of the key 10 is simply referred to as “static load”.
First, a case where the key 10 is in a stationary position will be described (see FIG. 1).
The rear end of the key 10, the whippen 20, and the rear end of the repetition lever 23 are at their lowest positions. A hammer shank roller 35 hits the hole of the repetition lever 23 at the position P3.

  The first spring 46 is sandwiched and bent between the first member 40 and the second member 41. The force generated from the bent first spring 46 presses the first member 40 in the direction in which the key 10 is located at the position P1. The force generated from the bent first spring 46 presses the second member 41 in the direction in which the string 80 is located at the position P2. The foot 57 of the second spring 54 is away from the hammer shank 33, and no force is applied from the second spring 54 to the hammer shank 33. Therefore, the second spring 54 does not affect the static load and does not prevent the hammer 32 from rising.

  The heel 21 presses the cap stun screw 14 downward. A static load is obtained by multiplying the downward force by a predetermined proportional constant k. The proportionality constant k is a value obtained by dividing “the distance in the axis X1 direction between the center of the hole 13 and the cap stun screw 14” by “the distance in the axis X1 direction between the front end of the key 10 and the center of the hole 13”. is there. In a typical size white key, k = 0.50, and in a typical size black key, k = 13/21.

Next, a case where the performer presses the key 10 at the stationary position will be described.
When the performer presses the key 10 in the stationary position with a force exceeding the static load, the cap stan screw 14 pushes up the heel 21 from below. The whippen 20 rises while rotating about the whippen frenzy 63. The repetition lever flange 22, the repetition lever 23, and the jack 24 rise together with the wippen 20 while rotating around the wippen flange 63.
The repetition lever 23 pushes up the hammer shank roller 35, and the push-up portion 25 of the jack 24 pushes up the hammer shank roller 35. By this push-up, the hammer 32 rises while rotating around the hammer shank flange 65. When the performer continues to press the key 10, the push-up portion 25 rotates forward and comes off from under the hammer shank roller 35.

After that, the hammer 32 is inertia and rotates toward the upper string 80, the hammer shank roller 35 is separated from the repetition lever 23, and the movement of the hammer 32 is separated from the movement of the key 10. Then, the hammer head 34 strikes the string 80 (see FIG. 3).
After the hammer head 34 strikes the string 80, the hammer 32 immediately reverses and descends while rotating. The hammer shank roller 35 hits the repetition lever 23 and the hammer shank roller 35 pushes down the repetition lever 23. Thereafter, the hammer head 34 is held by the back check 15 and stopped.

  As shown in FIG. 3, when the hammer head 34 strikes the string 80, the tip of the foot 57 of the second spring 54 hits the hammer shank 33 from above, and the second spring 54 bends. The bent second spring 54 presses the hammer shank 33 in the direction in which the key 10 is located. The lowering speed of the hammer 32 is accelerated by the pressing from the second spring 54, and the contact time between the hammer head 34 and the string 80 is shortened. By reducing the contact time between the hammer head 34 and the string 80, the sound emitted by the string 80 becomes clearer.

When the hammer 32 is lowered, the foot 57 of the second spring 54 is immediately separated from the hammer shank 33. Therefore, the second spring 54 presses the hammer shank 33 only when the hammer 32 strikes the string 80.
When the performer removes his / her finger from the key 10, loads such as the whippen 20, the repetition lever 23, and the hammer 32 act on the cap stun screw 14 from the heel 21, and the rear end portion of the key 10 is lowered. The back check 15 is lowered together with the rear end portion of the key 10, the hammer head 34 is separated from the back check 15, and the hammer 32 is further lowered. Then, after the hammer shank 33 momentarily hits the hammer stop rail 67, the hammer 32 rises several mm and stops, and the key 10 returns to the stationary position. When the hammer shank 33 momentarily hits the hammer stop rail 67, the hammer 32 is in the lowest position.

Next, the action of the first spring 46 on the static load will be described.
First, the action 8 which does not have the 1st spring 46 and the 2nd spring 54 is demonstrated as a comparative example (refer FIG. 4). Action 8 has the same configuration as a typical typical grand piano action.
In FIG. 4, the same components as those of the action 1 are denoted by the same reference numerals, and the force acting on the whippen 20 and the hammer 32 is displayed as a vector. These vectors represent only the direction of the force, and the length of the vector does not represent the actual force magnitude. This also applies to FIG. 1 and FIGS. 5 to 8 referred later.
In action 8 in which the key 10 is at a stationary position, equations (A1) and (A2) are established when the rotational moments of the wippen 20 and the hammer 32 are considered, and equations (A3) and (A4) are established when considering the balance of forces. To do.

The symbols used in the formulas (A1) to (A4) are as follows.
m ₁ is the total mass of the parts that rotate integrally around the hammer shank flange 65, and is the total mass of the hammer shank 33, hammer head 34, and hammer shank roller 35. m ₂ is the total mass of the parts that rotate integrally around the Wippen Frenzy 63.
f _1R is a force by which the repetition lever 23 pushes up the hammer shank roller 35 at the position P3. f _2R is a force by which the hammer shank roller 35 pushes down the repetition lever 23 at the position P3. The forces f _1R and f _2R are both forces in the direction orthogonal to the axis X2. f _K is a vertical component of the force by which the cap stan screw 14 pushes up the heel 21.

d _1W is the distance in the direction of the axis X 2 between the center of gravity of the part that rotates integrally around the hammer shank flange 65 and the pin 75. d _1R is the distance in the axis X2 direction between the position P3 and the pin 75. d _2W is the horizontal distance between the center of gravity of the component that rotates integrally around the Wippen Frenzy 63 and the pin 72. d _K is a horizontal distance between the tip of the capstan screw 14 and the pin 72. d _2R is a horizontal distance between the position P 3 and the pin 72.
k is the above-described proportionality constant. θ is an angle formed by the axis X2 with respect to the horizontal direction when the key 10 is at a stationary position, and 0 ° <θ <90 °. F is a static load and g is a gravitational acceleration.
When the equations (A1) to (A4) are coupled and deformed, the equation (A5) is obtained.

When playing the grand piano having action 8, the performer presses the key 10 with a force exceeding the static load F. As a result, a force exceeding the force f _K acts on the heel 21 from the cap stun screw 14 and the action 8 is activated.
Next, the static load of action 1 will be described with reference to FIG.
The mass of the action 1 hammerhead 34 is heavier than the mass of the action 8 hammerhead 34 by Δm ₁ .
In action 1 in which the key 10 is in the stationary position, equations (B1) and (B2) are established when the rotational moments of the wippen 20 and the hammer 32 are considered, and equations (B3) to (B5) are established when considering the balance of forces. To do.

In the formulas (B1) to (B5), the same symbols are used for the same formulas (A1) to (A5). The symbols newly used in the formulas (B1) to (B5) are as follows.
Δm ₁ is a change in the mass of the hammer head 34 with respect to the action 8. m _S1 is the mass of the first spring 46.
f _1R ′ is a force by which the repetition lever 23 pushes up the hammer shank roller 35 at the position P3. f _2R ′ is a force by which the hammer shank roller 35 pushes down the repetition lever 23 at the position P3. f _1S is a force by which the first spring 46 presses the second member 41 in the direction of the string 80 at the position P2. f _2S is a force by which the first spring 46 presses the first member 40 in the direction in which the key 10 is located at the position P1. The forces f _1R ′, f _2R ′, f _1S , and f _2S are all forces in the direction orthogonal to the axis X2. Δf _K is a change in force f _K with respect to action 8. When the force with which the cap stan screw 14 pushes up the heel 21 is small with respect to the action 8, Δf _K is negative, and when the force with which the cap stan screw 14 pushes up the heel 21 is large, Δf _K becomes positive.

Δd _1W is a change in the distance d _1W with respect to the action 8. When the center of gravity of a part that rotates integrally around the hammer shank flange 56 moves to the hammer head 34 side with respect to the action 8, the distance Δd _1W becomes positive, and the center of gravity moves toward the hammer shank flange 65 side. The distance Δd _1W is negative. Δd _2W is a change in the distance d _2W with respect to the action 8. When the center of gravity of a component that rotates integrally with the Wippen Frenzy 63 moves forward with respect to the action 8, the distance Δd _2W is positive, and when the center of gravity moves backward, the distance Δd _2W is negative. Become.

d _1S is a distance in the direction of the axis X2 between the position P2 and the pin 75. d _2S is a horizontal distance between the position P 1 and the pin 72. When the position P1 is ahead of the pin 72 when the action 1 is viewed from above, the distance d _2S is positive, and when the position P1 is behind the pin 72, the distance d _2S is negative.
ΔF is a change in the load F with respect to the action 8. When the static load is heavy with respect to the action 8, ΔF is positive, and when the static load is light, ΔF is negative.
When equations (A5) and (B1) to (B5) are coupled and deformed, equations (B6) to (B9) are obtained.

When playing the grand piano having action 1, the performer presses the key 10 with a force exceeding the static load F + ΔF. As a result, a force exceeding the force f _K + Δf _K acts on the heel 21 from the cap stun screw 14 and the action 1 is activated.
Α ₁ (f _1S , d _1S , d _2S ) in the expressions (B6) and (B7) is a function of the force f _1S , the distances d _1S , d _2S , and the strength and mounting position of the first spring 46 with respect to the static load. Represents the contribution. Β ₁ (Δm ₁ , Δd _1W ) in the formulas (B6) and (B8) is a function of the mass Δm ₁ and the distance Δd _1W and represents the contribution of the change in the mass of the hammer head 34 to the static load. In the expressions (B6) and (B9), γ ₁ (m _S1 , Δd _2W ) is a function of the mass m _S1 and the distance Δd _2W and represents the contribution of the mass of the first spring 46 to the static load.

The following can be understood from the equations (B6) to (B9).
When the mass m _S1 is approximated to zero, the distance Δd _2W is approximated to zero, and the function γ ₁ (m _S1 , Δd _2W ) is also approximated to zero. When the mass Δm ₁ is approximated to zero, the distance Δd _1W is approximated to zero, and the function β ₁ (Δm ₁ , Δd _1W ) is also approximated to zero. If the mass Δm ₁ is zero, the distance Δd _1W is zero, and the function β ₁ (Δm ₁ , Δd _1W ) is also zero.
When the position P2 moves from the hammer shank flange 65 side to the hammer head 34 side, the distance d _1S increases and the function α ₁ (f _1S , d _1S , d _2S ) decreases. When the position P1 moves from the front to the rear, the distance d _2S decreases and the function α ₁ (f _1S , d _1S , d _2S ) also decreases. If (d _2S / d _2R ) − (d _{! S} / d _{! R} ) becomes negative, the function α ₁ (f _1S , d _1S , d _2S ) also becomes negative.

Expressions (B6) to (B9) represent a relationship established between the presence or absence of the first spring 46, the change in the mass of the hammer head 34, and the change in the static load. If the equations (B6) to (B9) are used, the elastic coefficient, shape, mass, and mounting position of the first spring 46 necessary for obtaining the desired static load and the mass of the hammer head 34 in the action 1 are determined.
The elastic coefficient and shape of the first spring 46 are such that the amount of bending of the first spring 46 is maximized when the hammer 32 is at the lowest position, and the first spring 46 strikes the string 80. The amount of bending of the spring 46 becomes zero and is determined from the fact that the first spring 46 is in contact with the second member 41, the magnitude of the force f _1S , and the positions P1 and P2. Further, the mounting position of the first spring 46 is determined from the positions P1 and P2.

As can be seen from the equations (B6) to (B9), if at least one of force f _1S , distance d _1S , d _2S , Δd _1W , Δd _2W , mass Δm ₁ , m _S1 changes, load ΔF changes. To do. By changing at least one of the force f _1S , the distances d _1S , d _2S , Δd _1W , Δd _2W , mass Δm ₁ , m _S1 , the static load of the action 1 and the mass of the hammer head 34 can be adjusted.
The case where the action 1 is formed by attaching the first spring 46 and the second spring 54 to the action 8 will be described. For example, consider a case where the static load of action 1 is made lighter by ΔF than the static load of action 8 and the mass of hammer head 34 of action 1 is made heavier by Δm ₁ than the mass of hammer head 34 of action 8.

First, values of desired load ΔF and mass Δm ₁ are substituted into formulas (B6) to (B9), and force f _1S , distance d _1S , d _2S , Δd _1W , Δd _2W , mass m satisfying these formulas are substituted. Determine the value of _S1 in any order. If the values of force f _1S , distances d _1S , d _2S , and mass m _S1 are determined, the elastic coefficient and shape of the first spring 46 are determined.
According to the determined distances d _1S and d _2S , the foot 48 of the first spring 46 is implanted in the first member 40 and the tip of the foot 49 is applied to the second member 41. After mounting the first spring 46, the bending and bending of the first spring 46 are adjusted, and the static load F + ΔF is adjusted to a predetermined value. In addition, interference between the first spring 46 and other parts is reduced. To prevent.

The shape of the first spring 46 is such that when the hammer head 34 strikes the string 80, the amount of deflection becomes zero. As a result, when the hammer head 34 strikes the string 80, the force acting on the hammer shank from the first spring 46 becomes zero, and the action 1 quickly returns to the stationary position.
When the first spring 46 is attached, the foot 56 of the second spring 54 is implanted in the hammer shank flange 65. Then, the degree of bending or bending of the second spring 54 is adjusted, and only when the hammer head 34 strikes the string 80, the tip of the foot 57 is applied to the upper side of the hammer shank 33, together with the second spring. 54 to prevent interference with other parts.

Next, the case where the static action and the mass of the hammer head 34 are adjusted in the existing action 1 will be described.
First, assuming the action 8 in which the first spring 46 and the second spring 54 are removed from the action ₁ , the mass m ₁ and the distance d _1W in the action 8 are calculated. After that, it is assumed that action 1 is newly formed from action 8, and the above-described procedure is performed.

As the second embodiment, in the action 1, the first member 40 may be the whippen 20 or the repetition lever flange 22, and the first spring 46 may be implanted only in the first member 40. Further, the second spring 54 may be implanted in the hammer shank rail 66. Also in this case, the expressions (B6) to (B9) are established as described above.
FIG. 5 shows action 2 according to the third embodiment. In action 2, the first member 40 is the repetition lever 23. A leg 48 of the first spring 46 is implanted on the lower surface of the second member 41. A position where the foot 48 is implanted is a position P <b> 2 where the first spring 46 hits the second member 41. When the key 10 is in the stationary position, the tip of the foot 49 of the first spring 46 is in contact with the first member 40 from the upper side at the position P1.

  The shape of the first spring 46 is such that the amount of deflection of the first spring 46 is maximized when the hammer 32 is at the lowest position, and the first spring 46 strikes the string 80 when the hammer head 34 strikes the string 80. The amount of bending of 46 is zero and the foot 49 is in contact with the first member 40. Since the foot 49 is bent largely in the middle, the foot 48 can be implanted at the position P2, and the foot 49 can be applied to the position P1.

A foot 56 of the second spring 54 is implanted on the upper side of the hammer shank 33. The foot 57 of the second spring 54 extends forward, and the tip of the foot 57 is located above the hammer shank flange 65. The shape of the second spring 54 is curved in a mountain shape, and the foot 57 hits the hammer shank flange 65 from above only when the hammer head 34 strikes the string 80.
The other configuration of the action 2 is the same as the configuration of the action 1 of the first embodiment.
When the key 10 of the action 2 is in the stationary position, equations (C1) and (C2) are established when considering the rotational moments of the wippen 20 and the hammer 32, and equations (C3) to (C5) are obtained when considering the balance of forces. To establish.

In the formulas (C1) to (C5), the same symbols are used for the same formulas (B1) to (B5). The symbol m _S2 newly used in the expressions (C1) to (C5) is the mass of the second spring 54. When equations (A5) and (C1) to (C5) are coupled and deformed, equations (C6) to (C9) are obtained.

Α ₂ (f _1S , d _1S , d _2S ) in the expressions (C6) and (C7) is a function of the force f _1S , the distances d _1S , d _2S , and the strength and mounting position of the first spring 46 with respect to the static load. Represents the contribution. Β ₂ (Δm ₁ , Δd _1W ) in the expressions (C6) and (C8) is a function of the mass Δm ₁ and the distance Δd _1W and represents the contribution of the change in the mass of the hammer head 34 to the static load. In equations (C6) and (C9), γ ₂ (m _S1 , m _S2 , Δd _1W ) is a function of the mass m _S1 , m _S2 , and the distance Δd _1W , and the change in the mass of the hammer head 34 with respect to the static load and the first Represents the contribution of the mass of the spring 46 and the mass of the second spring 54.

The following can be understood from the equations (C6) to (C9).
When the masses m _S1 and m _S2 are both approximated to zero, the function γ ₂ (m _S1 , m _S2 , Δd _1W ) is also approximated to zero. Expressions (C6) to (C9) at this time have the same form as Expressions (B6) to (B9) when the mass m _{S1 is set} to zero in action 1.
When the sum of the mass m _S1 and the mass m _S2 is approximated to zero, the distance Δd _1W is also approximated to zero, and the function β ₂ (Δm ₁ , Δd _1W ) and the function γ ₂ (m _S1 , m _S2 , Δd _1W ) Is also approximated to zero. Expressions (C6) to (C9) at this time are the same forms as Expressions (B6) to (B9) when the masses Δm ₁ and m _S1 , the distances d _1W and d _2W are set to zero in action 1.

When the position P2 moves from the hammer shank flange 65 side to the hammer head 34 side, the distance d _1S increases and the function α ₂ (f _1S , d _1S , d _2S ) decreases. When the position P1 moves from the front to the rear, the distance d _2S decreases and the function α ₂ (f _1S , d _1S , d _2S ) decreases. If (d _2S / d _2R ) − (d _{! S} / d _{! R} ) is negative, the function α ₂ (f _1S , d _1S , d _2S ) is also negative.
Expressions (C6) to (C9) represent the relationship established between the presence or absence of the first spring 46, the presence or absence of the second spring 54, the change in the mass of the hammer head 34, and the change in the static load. . Using the equations (C6) to (C9), the elastic coefficient, shape, mass, mounting position of the first spring 46 necessary for obtaining the desired static load and the mass of the hammer head 34 in the action 2, and the second The mass of the spring 54 is determined.

The elastic coefficient and shape of the first spring 46 are such that the amount of bending of the first spring 46 is maximized when the hammer 32 is at the lowest position, and the first spring 46 strikes the string 80. The amount of bending of the spring 46 becomes zero, and the first spring 46 is in contact with the first member 40, the magnitude of the force f _1S , and the positions P1 and P2. The mounting position of the first spring 46 is determined from the positions P1 and P2.

As can be seen from the equations (C6) to (C9), if at least one of force f _1S , distance d _1S , d _2S , Δd _1W , mass Δm ₁ , m _S1 , m _S2 changes, load ΔF Changes. By changing at least one of the values of force f _1S , distances d _1S , d _2S , Δd _1W , mass Δm ₁ , m _S1 , m _S2 , the static load of action 2 and the mass of hammerhead 34 can be adjusted.
A case where the action 2 is formed by attaching the first spring 46 and the second spring 54 to the action 8 will be described. For example, consider a case where the static load of action 2 is made lighter by ΔF than the static load of action 8 and the mass of the hammer head 34 of action 2 is made heavier by Δm ₁ than the mass of the hammer head 34 of action 8.

First, values of desired load ΔF and mass Δm ₁ are substituted into equations (C6) to (C9), and force f _1S , distances d _1S , d _2S , Δd _1W , mass m _S1 , m satisfying these equations are satisfied. Select the value of _S2 in any order. If the values of force f _1S , distances d _1S , d _2S , and mass m _S1 are determined, the elastic coefficient and shape of the first spring 46 are determined.
The first spring 46 and the second spring 54 are attached to the action 8 according to the determined value. Then, the degree of bending or bending of the first spring 46 and the second spring 54 is adjusted, and the static load F + ΔF is adjusted to a predetermined value so that the first spring 46 and the second spring 54 interfere with other parts. To prevent.

A case where the static load and the mass of the hammer head 34 are adjusted in the existing action 2 will be described.
First, an action 8 in which the first spring 46 and the second spring 54 are removed from the action 2 is assumed, and the mass m ₁ and the distance d _1W in the action 8 are calculated. After that, it is assumed that action 2 is newly formed from action 8, and the procedure described above is performed.

As the fourth embodiment, in the action 2, the first member 40 may be the whippen 20 or the repetition lever flange 22, and the tip of the foot 57 of the second spring 54 may hit the hammer shank rail 66. Similar to the above, the expressions (C6) to (C9) are established.
As a fifth embodiment, in the action 2, the second spring 54 may be implanted in the hammer shank flange 65 or the hammer shank rail 66. In this case, the mass m _S2 does not affect the static load. Formulas (C6) to (C9) are established with the mass m _S2 being zero.

FIG. 6 shows action 3 according to the sixth embodiment. The configuration of action 3 is the same as the configuration of action 1 of the first embodiment except that the foot 56 of the second spring 54 is implanted in the second member 41. The configuration of the second spring 54 is the same as the configuration of the second spring 54 in action 2 of the third embodiment.
When the key 10 of the action 3 is in the stationary position, equations (D1) and (D2) are established when the rotational moments of the wippen 20 and the hammer 32 are considered, and equations (D3) to (D5) are obtained when considering the balance of forces. To establish.

  In the formulas (D1) to (D5), the same symbols are used for the same formulas (B1) to (B5) and (C1) to (C5). When equations (A5) and (D1) to (D5) are coupled and deformed, equations (D6) to (D9) are obtained.

Α ₃ (f _1S , d _1S , d _2S ) in the equations (D6) and (D7) is a function of the force f _1S , the distances d _1S , d _2S , and the strength and mounting position of the first spring 46 with respect to the static load. Represents the contribution. Β ₃ (Δm ₁ , m _S2 , Δd _1W ) in the equations (D6) and (D8) is a function of the mass Δm ₁ , m _S2 , and the distance Δd _1W . Represents the contribution of the mass of the spring 54. In equations (D6) and (D9), γ ₃ (m _S1 , Δd _2W ) is a function of the mass m _S1 and the distance Δd _2W and represents the contribution of the mass of the first spring 46 to the static load.

The following can be understood from the equations (D6) to (D9).
When the mass m _S1 is approximated to zero, the distance Δd _2W is approximated to zero, and the function γ ₃ (m _S1 , Δd _2W ) is also approximated to zero. When the sum of mass Δm ₁ and mass m _S2 is approximated to zero, distance Δd _1W is approximated to zero, and β ₃ (Δm ₁ , m _S2 , Δd _1W ) is also approximated to zero.
When the position P2 moves from the hammer shank flange 65 side to the hammer head 34 side, the distance d _1S increases and the function α ₃ (f _1S , d _1S , d _2S ) decreases. When the position P1 moves from the front to the rear, the distance d _2S decreases and the function α ₃ (f _1S , d _1S , d _2S ) also decreases. If (d _2S / d _2R ) − (d _{! S} / d _{! R} ) becomes negative, the function α ₃ (f _1S , d _1S , d _2S ) also becomes negative.

  Expressions (D6) to (D9) represent the relationship established between the presence or absence of the first spring 46, the presence or absence of the second spring 54, the change in the mass of the hammer head 34, and the change in the static load. . Using the equations (D6) to (D9), the elastic coefficient, shape, mass, mounting position, second position of the first spring 46 necessary for obtaining the desired static load and the mass of the hammer head 34 in the action 3 The mass of the spring 54 is determined.

The elastic coefficient and shape of the first spring 46 are such that the amount of bending of the first spring 46 is maximized when the hammer 32 is at the lowest position, and the first spring 46 strikes the string 80. The amount of bending of the spring 46 becomes zero and is determined from the fact that the first spring 46 is in contact with the second member 41, the magnitude of the force f _1S , and the positions P1 and P2. The mounting position of the first spring 46 is determined from the positions P1 and P2.

As can be seen from the equations (D6) to (D9), if at least one of the force f _1S , distance d _1S , d _2S , Δd _1W , Δd _2W , mass Δm ₁ , m _S1 , m _S2 changes. The load ΔF changes. By changing at least one of the values of force f _1S , distance d _1S , d _2S , Δd _1W , Δd _2W , mass Δm ₁ , m _S1 , m _S2 , the static load of action 3 and the mass of hammerhead 34 are adjusted. it can.

The case where the action 3 is formed by attaching the first spring 46 and the second spring 54 to the action 8 will be described. For example, consider a case where the static load of action 3 is made lighter by ΔF than the static load of action 8 and the mass of the hammer head 34 of action 3 is made heavier by Δm ₁ than the mass of the hammer head 34 of action 8.
First, values of desired load ΔF and mass Δm ₁ are substituted into equations (D6) to (D9), and force f _1S , distances d _1S , d _2S , Δd _1W , Δd _2W , mass m satisfying these equations are substituted. Select the values of _S1 and m _S2 in any order. If the values of force f _1S , distances d _1S , d _2S , and mass m _S1 are determined, the elastic coefficient and shape of the first spring 46 are determined.

The first spring 46 and the second spring 54 are attached to the action 8 according to the determined value. Then, the degree of bending or bending of the first spring 46 and the second spring 54 is adjusted, and the static load F + ΔF is adjusted to a predetermined value so that the first spring 46 and the second spring 54 interfere with other parts. To prevent.
A case where the static load and the mass of the hammer head 34 are adjusted in the existing action 3 will be described.

First, assuming the action 8 in which the first spring 46 and the second spring 54 are removed from the action 3, the mass m ₁ and the distance d _1W in the action 8 are calculated. After that, it is assumed that action 3 is newly formed from action 8, and the procedure described above is performed.
As the seventh embodiment, in the action 3, the first member 40 may be the whippen 20 or the repetition lever flange 22, and the tip of the foot 57 of the second spring 54 may hit the hammer shank rail 66. Similar to the above, the equations (D6) to (D9) are established.

FIG. 7 shows action 4 according to the eighth embodiment. In action 4, the first member 40 is a whippen rail 64. A leg 48 of the first spring 46 is implanted in the first member 40. A position where the foot 48 is implanted is a position P <b> 1 where the first spring 46 hits the first member 40. The leg 49 of the first spring 46 is bent or bent, and interference between the first spring 46 and other parts is prevented. When the key 10 is in the stationary position, the tip of the foot 49 is in contact with the second member from below at the position P2. Other configurations of the action 4 are the same as the configuration of the action 1 of the first embodiment.
When the key 10 of the action 4 is in the stationary position, equations (E1) and (E2) are established when considering the rotational moments of the wippen 20 and the hammer 32, and equations (E3) and (E4) are considered when considering the balance of forces. To establish.

  In the formulas (E1) to (E4), the same symbols are used for the same formulas (B1) to (B5). When equations (A5) and (E1) to (E4) are coupled and deformed, equations (E5) to (E7) are obtained.

Α ₄ (f _1S , d _1S ) in the equations (E5) and (E6) is a function of the force f _1S and the distance d _1S and represents the contribution of the strength of the first spring 46 and the mounting position to the static load. Β ₄ (Δm ₁ , Δd _1W ) in the equations (E5) and (E7) is a function of the mass Δm ₁ and the distance Δd _1W and represents the contribution of the change in the mass of the hammer head 34 to the static load.
The following can be seen from the equations (E5) to (E7).
The forms of equations (B6) to (B9) when the distances d _2S , Δd _2W and mass m _S1 are zero are the same as the equations (E5) to (E7).

If the mass Δm ₁ is zero, the distance Δd _1W is zero, and the function β ₄ (Δm ₁ , Δd _1W ) is also zero. At this time, the expressions (E5) to (E7) are the same as the expressions (B6) to (B9) when the distances d _2S , Δd _1W , Δd _2W , mass Δm ₁ , and m _S1 are all zero.
The function α ₄ (f _1S , d _1S ) is always negative. When the position P2 moves from the hammer shank 65 side to the hammer head 34 side, the distance d _1S increases and the absolute value of the function α ₄ (f _1S , d _1S ) decreases.

Expressions (E5) to (E7) represent the relationship established between the presence or absence of the first spring 46, the change in the mass of the hammer head 34, and the change in the static load. If the equations (E5) to (E7) are used, the elastic coefficient, shape, and mounting position of the first spring 46 necessary for obtaining the desired static load and the mass of the hammer head 34 in the action 4 are determined. In action 4, the mass m _S1 and the distance d _2S do not affect the static load.

The elastic coefficient and shape of the first spring 46 are such that the amount of bending of the first spring 46 is maximized when the hammer 32 is at the lowest position, and the first spring 46 strikes the string 80. The amount of bending of the spring 46 becomes zero, and the first spring 46 is in contact with the second member 41, the magnitude of the force f _1S , and the positions P1 and P2. Further, the mounting position of the first spring 46 is determined from the positions P1 and P2.

As can be seen from the equations (E5) to (E7), if at least one of the force f _1S , the distance d _1S , Δd _1W , and the mass Δm ₁ changes, the load ΔF changes. By changing at least one of the force f _1S , the distance d _1S , Δd _1W , and the mass Δm ₁ , the static load of the action 4 and the mass of the hammer head 34 can be adjusted.
The case where the action 4 is formed by attaching the first spring 46 and the second spring 54 to the action 8 will be described. For example, consider a case where the static load of action 4 is made lighter by ΔF than the static load of action 8 and the mass of hammer head 34 of action 4 is made heavier by Δm ₁ than the mass of hammer head 34 of action 8.

First, the values of desired load ΔF and mass Δm ₁ are substituted into equations (E5) to (E7), and the values of force f _1S and distance d _1S satisfying these equations are selected. If one of the distance Δd _1W and the mass Δm ₁ is determined, the other is also determined. If the values of the force f _1S and the distance d _1S are determined, the elastic coefficient and shape of the first spring 46 are determined.
The first spring 46 and the second spring 54 are attached to the action 8 according to the determined value. Then, the degree of bending or bending of the first spring 46 and the second spring 54 is adjusted, and the static load F + ΔF is adjusted to a predetermined value so that the first spring 46 and the second spring 54 interfere with other parts. To prevent.

The case where the static load of the existing action 4 and the mass of the hammer head 34 are adjusted will be described.
First, assuming the action 8 in which the first spring 46 and the second spring 54 are removed from the action 4, the mass m ₁ and the distance d _1W in the action 8 are calculated. Thereafter, it is assumed that the action 4 is newly formed from the action 8, and the procedure described above is performed.
As the ninth embodiment, in the action 4, the first member 40 may be the Whippen flange 63, the hammer shank rail 66, or the hammer shank flange 65, and the second spring 54 is implanted in the hammer shank rail 66. May be. Similar to the above, equations (E5) to (E7) are established.

As the tenth embodiment, in the action 4, the first member 40 is the whippen rail 64, the whippen flange 63, the hammer shank rail 66 or the hammer shank flange 65, and the first spring 46 is implanted in the second member 41. The second spring 54 may be implanted in the hammer shank flange 65 or the hammer shank rail 66. In this case, the mass m _S1 affects the static load, and the mass m _S2 does not affect the static load. Expressions (C6) to (C9) are established with the distance d _2S and the mass m _S2 being zero.

As Example 11, in the action 4, the first member 40 is the Wippen rail 64, the Wippen flange 63, the hammer shank rail 66, or the hammer shank flange 65, and the second member 41 is implanted in the second member 41. The spring 54 may hit the hammer shank rail 66 or the hammer shank flange 65. In this case, the mass m _S2 affects the static load, and the mass m _S1 does not affect the static load. Expressions (C6) to (C9) are established with the distance d _2S and the mass m _S1 being zero.

As Example 12, in Action 4, the first member 40 is the Whippen rail 64, the Whippen flange 63, the hammer shank rail 66 or the hammer shank flange 65, and the first spring 46 and the second spring 54 are the first. The second spring 54 may be in contact with the hammer shank flange 65 or the hammer shank rail 66. In this case, the masses m _S1 and m _S2 affect the static load. Expressions (C6) to (C9) are established with the distance d _2S being zero.
In each of Examples 2, 4, 5, 7, and 9-12, each action can be formed from action 8 using the relational expressions established in each case, and the static load of each existing action and the mass of hammer head 34 are adjusted. it can.

  FIG. 8 shows action 5 according to the thirteenth embodiment. Action 5 has a hammer rest 27 instead of the hammer stop rail. The hammer rest 27 is formed at the rear end of the wippen 20, and forms a part of a part that is integrated with the wippen 20 and rotates around the wippen frenzy 63. The hammer rest 27 is located behind the pin 72. Action 5 has the same configuration as a conventional action having a hammer rest, except that it has a first spring 46 and a second spring 54.

The hammer rest 27 forms the first member 40. A leg 48 of the first spring 46 is implanted in the first member 40. A position where the foot 48 is implanted is a position P <b> 1 where the first spring 46 hits the first member 40. The other configuration of the action 5 is the same as the configuration of the action 1 of the first embodiment.
In action 5, equations (B6) to (B9) are established. Similar to action 1, action 5 can be formed from a conventional action with a hammer rest using equations (B6) to (B9), and the static load of existing action 5 and the mass of hammer head 34 can be adjusted.

  As Example 14, in Action 5, the first member 40, the first spring 46, and the second spring 54 may be configured in the same manner as in Examples 1-12. However, in this case, the first member 40 does not become a hammer stop rail. Depending on the configuration of the first member 40, the first spring 46, and the second spring 54, the same equations as in Examples 1 to 12 are established. In each case, using the relational expressions established, the action 5 can be formed from a conventional action with a hammer rest, and the static load of the existing action 5 and the mass of the hammer head 34 can be adjusted.

In each action of Examples 1 to 14, the first spring 46 is implanted only in one of the first member 40 and the second member 41. Instead, in each of these actions, one of the legs 48 and 49 of the first spring 46 may be implanted in the first member 40 and the other may be implanted in the second member 41. .
In the above description, the fact that the first spring 46 or the second spring 54 is implanted in a member means that the first spring 46 or the second spring 54 is supported by the member. It is that you are hit with.

1, 2, 3, 4, 5, 8 Grand Piano Action 10 Key 20 Whippen 22 Repetition Lever Frenzy 23 Repetition Lever 27 Hammer Rest 32 Hammer 33 Hammer Shank 34 Hammer Head 40 First Member 41 Second Member 46 First Spring 54 second spring 63 wippen frenches 64 wippen rails 65 hammer shank frenches 66 hammer shank rails 67 hammer stop rails 80 strings

Claims (5)

A whippen pivotally fixed to a whippen flange fixed to the whippen rail, a repetition lever pivotally fixed to the repetition lever flange formed on the whippen, and fixed to the hammer shank rail And a hammer stop rail formed below the hammer shank of the hammer, and when the player presses a key, the hammer is chorded. An action of a grand piano that rotates toward
One of the whippen rail, the whippen frenzy, the whippen, the repetition lever frenzy, the repetition lever, the hammer shank rail, the hammer shank frenzy, and the hammer stop rail. One is the first member,
The hammer shank forms a second member;
A first spring is supported by one or both of the first member and the second member, and is mounted between the first member and the second member. Has been
When the key is in a stationary position, the first spring is sandwiched between the first member and the second member and bends, and presses the first member in the direction in which the key is located. Then, the action of the grand piano, wherein the second member is pressed in the direction of the string. A whippen pivotally fixed to the whippen flange fixed to the whippen rail, a repetition lever formed pivotally on the whippen, and a repetition lever pivotally fixed to the whippen formed on the whippen. A hammer rest, and a hammer pivotally fixed to a hammer shank flange fixed to the hammer shank rail, and when the player presses the key, the hammer rotates toward the string. Grand piano action,
One of the whippen rail, the whippen frenzy, the whippen, the repetition lever frenzy, the repetition lever, the hammer rest, the hammer shank rail, and the hammer shank frenzy Is the first member,
The hammer shank of the hammer forms a second member;
A first spring is supported by one or both of the first member and the second member, and is mounted between the first member and the second member. Has been
When the key is in a stationary position, the first spring is sandwiched between the first member and the second member and bends, and presses the first member in the direction in which the key is located. Then, the action of the grand piano, wherein the second member is pressed in the direction of the string.   The first spring always hits the first member and the second member without being separated from when the performer presses the key at the rest position until the key returns to the rest position. The action of the grand piano according to claim 1, wherein the action is a grand piano. A second spring is supported by any one of the hammer shank flange, the hammer shank rail, and the hammer shank;
When the hammer strikes the string, the second spring bends between the hammer shank flange or the hammer shank rail and the hammer shank and presses the hammer shank in the direction of the key. The action of the grand piano according to any one of claims 1 to 3, wherein the action is a grand piano. When the second spring is supported by one of the hammer shank flange and the hammer shank rail, the second spring hits the hammer shank only when the hammer strikes the string. The bent second spring presses the hammer shank in the direction of the key,
When the second spring is supported by the hammer shank, only when the hammer strikes the string, the second spring is deflected against the hammer shank flange or the hammer shank rail, and this deflection 5. The grand piano action according to claim 4, wherein the second spring presses the hammer shank in a direction in which the key is present.

Images