DE19703422A1 - Hammer mechanism for piano - Google Patents

Abstract

The spring appliance (251,254) is pre-tensioned. The spring arrangement leads away firstly from the connection between the spring arrangement to the hammer appliance. The spring arrangement leads away firstly from the pivot point of the hammer arrangement and secondly from the pivot point of the hammer-control. In its second part of its course, the spring arrangement runs towards the lifting element (250) and is joined to the hammer-control.

Description

Hammer instruments have a keyboard with side by side lying keys, each of which has a mechanism in the called the following hammer mechanism, operated a hammer. The keys are made of spruce wood, the mechanical links Hornbeam wood. In a frame are side by side lying strings retracted, which in graded pitches are voted. At these strings there are dampers, which prevent possible string vibration. These dampers are about another mechanism, below Called damper mechanism, connected to the buttons. Becomes a button is pressed, the associated damper is removed from the Lifted the string so that the string can swing freely. Furthermore, the associated hammer against the string moves and produces a sound when it hits the string. When the button is released, the damper puts on again the string on and stops it vibrating.

The invention relates to the improvement of Mechanisms that depress and release the Transfer keys to the hammers, for instruments, whose strings are on at least one level, which Which instruments run perpendicular to the keyboard "Pianos" are called.

Fig. 1 and Fig. 2 show the arrangement of the keys of the keyboard in a detail, Fig. 1 in plan view, Fig. 2 in side view. In a certain order, wide, flat keys 1 alternate with narrow, high keys 2 between them, which are shown in longitudinal hatching. The latter end further inside, they do not extend, like the wide, flat keys, to the outer edge of the keyboard, which runs down in Fig. 1, on the right in Fig. 2. Fig. 3 shows a link of a mechanism for pianos, as it is used almost exclusively today, reduced in side view. In the following it will be called "standard piano mechanics". The balance beam 4 , which carries the pin 5 , is fastened on the keyboard frame 3 . The frame also carries the felt pad 6 , the key guide pin 7 and the felt disk 8 . In pins 5 and 7 , key 1 , which is designed as a two-armed lever, is tiltably supported on balance beam 4 at support point A. It is rotated counterclockwise by the lead weight 8 A around the support point A and pressed onto the felt support 6 . The key covering 9 is glued onto one lever arm of the key 1 , and the adjusting screw 10 is screwed in on the other. Key 1 is usually depressed at point P ₁ , but can also be depressed at point P ₁ 'and at all points between P ₁ and P ₁ '.

When button 1 is one of the flat keys 1 from Fig. 1 and Fig. 2. Similarly, in Fig., The arrangement for the high keys 2 shown in these figures. 3 The key 2 is typically depressed at the point P ₂ or in the range between P ₂ and P ₂ '. The point P ₂ is closer to the set screw 10 than the point P ₁ , so that, in order to guarantee the same reduction ratio, the tilting bearing A 'of the key 2 is shifted relative to the tilting bearing A of the key 1 towards the adjusting screw 10 .

The felt 11 , which is glued onto the lifting member 12, rests on the adjusting screw 10 . The lifting member 12 is rotatably mounted in the capsule 13 . The capsule joint bears the designation B. The joint B of the lifting member 12 , the point of contact of the felt 11 on the adjusting screw 10 and the tipping point A of the key 1 lie on a straight line, one end of which is shown at the tipping point A. This line forms the angle alpha with the lower edge of key 1 . The side of the set screw 10 facing the felt 11 is designed as a spherical cap. The adjusting screw 10 has two intersecting bores in its head, which can accommodate an adjusting iron.

The capsule 13 is screwed onto the mechanical bar 14 , which appears in cross section in the plane of the drawing. The capsule 13 is provided on the side which rests on the mechanical bar 14 with a notch running perpendicular to the plane of the drawing, as is the mechanical bar 14 . The notch wire 15 runs in this notch and aligns the capsule 13 in the vertical position when it is screwed tight. The beam rail 16 is screwed onto the mechanical beam 14 and secures it against torsion. It is attached to keyboard jaws, not shown, which rest on the keyboard frame 3 .

The further structure is explained with reference to FIG. 4, which shows a section of FIG. 3 in a slight reduction compared to the original size. First the damper mechanism: an extension, the damper spoon 19 , is attached to the lifting member 12 . The damper spoon 19 consists of a wire which is crimped into a spoon shape at its upper end. The damper spoon 19 holds in the idle state of the arrangement with its convex side a small distance from the damper felt cloth 20 which is glued to the damper arm 21 . The damper arm 21 is rotatably mounted in the capsule 22 . The joint bears the designation C. The damper spring 23 is fastened in the capsule 22 by being wound around an axis parallel to the joint axis. The spring base point thus formed bears the designation D. The upper end of the damper spring 23 is rounded and lies in a graphitized groove (not shown), the damper barrel, on the damper arm 21 . The damper spring 23 causes a torque counterclockwise on the damper arm 21 around the joint C.

The wire 24 is fastened to the upper end of the damper arm 21 . The damper 25 , which is covered with the felt 27 on its side facing the string 26, is screwed onto it. The felt 27 is pressed against the string 26 by the action of the damper spring 23 . The fixed damper baffle 28 is covered with the felt 29 on the side facing the damper wire 24 .

In a hammer instrument there should be the possibility that all dampers are lifted off their strings regardless of the key position. For this purpose, the damper rod 30 , which runs perpendicular to the plane of the drawing, is located in an indentation of the mechanical beam 14 , shown in detail in FIG. 4a. This rod carries the extensions 30 a and 30 b outside the plane of the drawing. The extension 30 b is rotatably mounted on the mechanical beam 14 at point E. Under the extension 30 a is the rod 31 , which can move up and down in the bearing 32 . This rod 31 is actuated by a pedal, not shown. The adjusting screw 33 is still screwed into the damper arm 21 .

So much for the description of the damper mechanism. Now for the hammer mechanism. The jack capsule 34 is seated in the lifting member 12 . The jack 35 is rotatably mounted in it. The joint bears the designation F. The jack 35 represents a two-armed lever with a large transmission ratio, the two lever arms of which are perpendicular to one another. The free end of the upstanding lever arm of the jack engages the butt 44 over the butt leather 46 . The jack 35 is rotated counterclockwise in the joint F by the helical compression spring 36 , which acts on the lifting member and on the short lever arm of the jack, and is applied to the butt pad 43 . The function of the spring 36 , if it has rotated clockwise in the joint F, to put the jack back under the butt, to return it to its point of attack on the butt, is also fulfilled by many other known spring constructions. The lever arm of the jack 35, in which the helical spring 36 engages, is convexly rounded on the side facing away from the lifting member 12 and graphitized there. Opposite the curvature of the short lever arm of the jack, the nose of the jack, sits the release manikin 37 , which represents a stop for the convex end of the jack 35 underneath. The release manikin 37 is covered with manikin felt 38 on the side which faces the convex tongue end. The set screw 39 is screwed into the release manikin bar 40 , which appears in cross section in the drawing plane, so that the screwed-in end protrudes. The trigger manikin 37 is screwed into this. The trip bar 40 is fastened to the mechanical beam 14 with screws (not shown). If the lifting link in joint B moves counterclockwise, the nose of the jack is pressed against the jack manikin and the jack rotates joint F clockwise. The tip of the tongue leaves its point of attack on the butt. This process is called triggering. There are other types of jacks with different trigger designs.

The long lever arm of the jack 35 protrudes upwards parallel to the mechanical beam 14 , pointing away from the button 1 . In addition to the long, upstanding lever arm of the jack 35 there is, opposite the mechanical beam 14 , the jack baffle bar 41 , which is covered with the felt 42 on the side pointing to the jack 35 . The shock impact bar 41 is fastened to the mechanical beam 14 with screws (not shown) in such a way that the distance between the two is adjustable. The tiltable lifting link, the tilting jack with its device, which it can return to its point of attack on the butt, and the parts that are firmly connected to the lifting link are referred to in this application as hammer actuation devices.

The end face of the long lever arm of the jack 35 engages in the butt 44 . The rotation of the jack 35 caused by the helical spring 36 is limited by the butt pad 43 , the helical spring 36 thus presses the free end of the upstanding arm of the jack 35 against the butt pad 43 . In the past, other types of suspension with the same effect were used. The butt pad 43 is attached to the butt 44 , which is rotatably mounted in the butt capsule 45 , which is screwed onto the mechanical beam 14 . The camp has the designation G. The butt 44 is covered at the point where the jack 35 engages with the felt 45 A, which is covered with the butt leather 46 , on which the end face of the long lever arm of the jack 35 then engages. Opposite this point a little protruding recessed and pierced nose 44 a is formed on the butt 44 . A glue-coated cord, the hammer butt cord, is pulled through the hole and is wound around the hammer return spring 47 , which has a helical shape at this point. The coil of the hammer return spring 37 is located in the not shown recess of the nose 44 a. One end of this spring presses against the butt, the other jumps out bent and is suspended in the capsule string 48 , which is attached to the butt capsule 45 . The capsule string 48 consists of a loop, which arises from the fact that a string is glued into a groove on the end faces of both forks of the hammer nut capsule 45 . Fig. 4b shows in perspective the butt flange 45 with the Kapselschnürchen 48 and the Hammerrückholfeder 47th The function of this arrangement is to return the hammer to its rest position. This function is also performed by other designs of the hammer return spring that were previously common.

Back to FIG. 4. The arrangement of the hammer return spring 47 and the capsule string 48 causes the butt 44 in the joint G to rotate clockwise. The counter-catcher 49 is glued into the hammer-nut capsule via the counter-catcher style 49 a. The counter-catcher style represents a distance element to the butt for the counter-catcher. The counter-catcher is covered with the counter-catcher leather 50 at its outer end. Furthermore, he wears the ribbon 51 , which is covered with leather at the other end and is attached to the ribbon wire 52 .

The ribbon sags slightly in the idle state. It has the task of limiting the opposite rotation of the butt and the lifting link. The ribbon wire 52 is fastened in the lifting member 12 . The catcher wire 53 is also fastened in the lifting member 12 and carries the catcher 54 at the other end. This is covered on the side facing the counter-catcher 49 with the catcher felt 55 .

In the butt 44 the hammer style 56 is fastened, which carries the hammer head 57 , over which the hammer felt 58 is drawn. Hammer butt, counter catcher and hammer and all parts that are rigidly connected to it are referred to as hammer devices in this application. The hammer style 56 rests on the folding strip fabric 59 which is glued onto the folding strip 60 , which is rotatably mounted in the folding strip capsule 61 . The hinge bears the designation H. An angle (not shown) is fastened to the folding bar 60 , which can be moved upwards via a vertical rod (not shown) located underneath. Rod and bracket function like the pedal rod and its extensions from Fig. 4a. Due to the action of the rod, the folding bar in joint H can be rotated counterclockwise via a second pedal, not shown.

The felts in Fig. 3 and Fig. 4 serve to dampen noise, the leather covers provide a soft, yet tough surface.

.. The standard piano mechanism according to Figures 3 and 4 operates as follows. When the key 1 in Figure 3 is depressed at the point P _1, it tilts about the support point A in the clockwise direction and the adjusting screw 10 increases. As a result, the lifting member 12 rotates counterclockwise around the joint B. Because the pivot point B of the lifting member 12 , the contact point of the felt 11 on the adjusting screw 10 and the tipping point A of the button 1 lie on a straight line and by a suitable radius of the spherical cap, which forms the surface of the set screw 10 , the felt 11 rolls off the set screw 10 and the friction of the transition is minimized.

Continue to Fig. 4: The damper spoon 19 of the Dämpferarms 21 is pressed against the felt 20, the latter rotates clockwise around the hinge C, which is lifted off the cushion 25 of the string 26 and these are free to vibrate. So that the damper 25 does not lift too far from the string 26 due to its swing during rapid movement, its course is restricted by the felted damper impact bar 28 . So much for the damper mechanism during the striking process.

The jack 35 is pushed upward by the rotation of the lifting member 12 about the joint B counterclockwise. Since this is rotatably mounted in the joint F, it remains stuck to the butt pad 43 during this process due to the action of the helical spring 36 . The rising jack 35 causes the butt 44 to rotate counterclockwise around the joint G and moves the hammer head 57 to the string 26 against the restoring force of the hammer return spring 47 . The force of the jack 35 driving the hammer head 57 is interrupted when the round end of the short lever arm of the jack 35 , which is located above the coil spring 36 , touches the felt 38 of the release man 37 . The further rotation of the lifting member 12 in the joint B counterclockwise causes a rapid rotation of the jack 35 about the joint F clockwise, whereby the tip of the long lever arm of the jack 35 moves away from the butt 44 . The hammer head 57 is no longer driven to the string 26 , but moves against the string 26 with its own swing, strikes it and falls back due to the rebound and the restoring force of the hammer return spring 47 . The process of interrupting the power transmission of the jack 35 to the butt 44 is called "triggering". The hammer butt 44 turns clockwise after the hammer head bounces off the string 26 in the joint G until the counter-catcher 49 falls into the catcher 54 , which has now been accommodated, whereby the movement of the hammer head 57 comes to rest. When the hammer head 57 falls back, the butt 44 falls with the butt leather 46 onto the end face of the jack 35 and rotates it further in the joint F in a clockwise direction until it rests on the felt 42 of the jack impact bar 41 .

When the button is released, the following happens: The adjusting screw 10 sinks, the lifting member 12 rotates clockwise by its own weight about the joint B. As a result, the damper spoon 19 releases the damper arm 21 , which rotates counterclockwise through the action of the damper spring 23 around the joint C and the damper 25 rests on the string 26 with the felt 27 . Furthermore, the catcher 54 moves away from the counter-catcher 49 , the jack 35 sinks and the butt 44 rotates clockwise around the joint G. The action of the return spring 23 causes the hammer head 57 to fall back until the hammer style 56 rests on the flap strip fabric 59 . The jack 35 lowers further and is driven under the butt 44 again by the action of the spring 36 . The starting position is reached again. The return process of the hammer 56 , 57 is reinforced by the tightening of the ribbon 51 by the lifting member 12 rotating clockwise around the joint B. The band 51 limits the maximum distance between the end face of the jack 35 and its point of attack on the butt leather 46 . This distance is called tongue air.

FIG. 4a: If the extension of a pedal rod 30 is not drawn by kicking a 30 ranged the pedal by the rod 31 moves according to above, the projection 30 rotates b them the pedal bar in the hinge D in the clockwise direction. The pedal rod is brought to the felt 20 of the damper arm 21 at the point opposite the damper adjusting screw 33 . The continuation of this movement rotates all damper arms clockwise around the joint C, the dampers 25 lift off the strings 26 . This causes all struck tones to continue to sound even when their keys are not pressed. This allows the sound strength to be increased and the sound to be blurred. When the aforementioned pedal is released, the process is reversed and the dampers rest on the strings again.

If the folding bar 60 is moved counterclockwise around the hinge H by pushing a second pedal, not shown, of the left pedal, the folding bar material 59 pushes the hammer styles 56 against the string 26 until this second pedal comes to a stop at a stop. The hammer styles 56 are placed halfway to string 26 compared to the starting position shown. If the key 1 is now struck, the hammer 57 gets less momentum. This should allow a particularly quiet game.

In order for this mechanism to work exactly, it must be adjusted. The necessary adjustments are made as follows: The lead weight 8 is chosen so large that the force P ₁ , or P ₂ , which is necessary to depress the key 1 or 2 , the so-called "game severity", 50 to 60 pond is. With the adjusting screw 10 , which is located in the button 1 , the height of the lifting member 12 is adjusted in the idle state. If it is too deep, there is a gap between the butt leather 46 and the upper end of the jack 35 , which is called "jack air". If the lifting member 12 is too high, if the entire arrangement falls back after the button 1 has been released, the jack 35 cannot slide completely under the butt.

The lifting point of the damper 25 from the string 26 , which is to take place at half the key stroke, is adjusted by bending the damper spoon 19 .

Triggering: If the key 1 is pressed hard, the hammer head 58 flies to the string 26 . When the button 1 is depressed slowly, the hammer head is only moved to the point at which the triggering, the interruption of the power transmission of the jack 35 to the butt 44 , takes place and reverses at this point. The distance of the apex of the hammer head 58 from the string 26 at said reversal point is also called "triggering". The release is adjusted by turning the trigger screw 39 . It is 2 mm.

After triggering, the hammer head 57 falls off the string until the counter-catcher 49 has fallen into the catcher 54 . Then the hammer should be about half the distance from the string compared to the distance at rest. This distance is set by bending the catcher wire 53 . The ribbon wire 52 is bent in such a way that the ribbon 51 sags slightly when the arrangement is at rest.

Fig. 4c shows a variant of the limitation of the maximum air between the jack and its point of attack on the butt, which does not require a ribbon. It was built by Bechstein around the turn of the century. The butt 100 has a projection 100 a below the jack cushion 101 . The jack 102 is angled at its free end, so that the angled portion 102 a is between the butt leather 103 and the projection 100 a of the butt. The projection 100 a is padded with the felt 104 on the side facing the jack projection. Now, when the jack 102 is stationary, the butt 100 rotates counterclockwise, this rotation is limited when the projection 100 a meets the underside of the angled end 102 a of the jack. The jack air is limited.

The most important constructions and patent applications for Improvement in piano mechanics by 1944 are in Walter Pfeiffer's standard work "Vom Hammer", Frankfurt am Main 1979.

The following problems of the mechanics shown are to be overcome or reduced in the present application:

• 1a) Prevention of hammer relapse when the button is released until the jack is under the butt again: let it After the key has been released, the button slowly releases, so the Hammer back and the jack is only under again the hammer butt when the hammer is at rest. If you hit the key again before it enters your Has returned to its original position, the jack bumps into the void. This problem is raised by many patent applications more or less solved. Some keep the hammer on Position where he was caught so that the sliding of the Jack is done earlier, so z. B. at Pfeiffer on p. 58 Mechanics shown by Schaaf.
• 1b) Perfect solutions require that the hammer, the counter-catcher 49 is released again by the catcher 54 towards the string. This is the case with grand piano mechanics, and it must also be the case with perfect piano mechanics. Here, a simple and easy to adjust solution in the spring force is to be found.
• 2) If there is such a movement, it turns out Problem swinging the hammer towards the string just before reaching it reduce this string so far that this movement does not the hammer strikes the string. This Loss of swing may not gradually take place on the path of Hammer to the string, but must be just before reaching insert the string, so that the Button a restart is possible. This loss of momentum should be done in a simple way and a moderate, not too have high repercussions on the key, otherwise, as with the heavy bass hammers of wings are known to be an inhibition arises that complicates the pianissimo.
• 3) Points 1 and 2 make up the general repetition ability of the mechanics. However, there is an unfavorable exceptional case in which the hammer device falls back beyond the point at which it is usually intercepted by the catcher and sticks in the catcher when the key is struck again. Perfect repetitiveness, as is known for "heart mechanics" for wings, requires a rebound device when the hammer falls back, which is adjusted to about half the fall. Since the catcher usually catches the hammer by a third of its way back via the counter-catcher, this rebound device usually does not work. In exceptional cases, however, it prevents falling further than half the way. Such a rebound device should be found for piano mechanics.
• 4) The hammer return spring 47 can not be designed so strong in the mechanics shown in Fig. 4 that their reaction to the key effect would produce the game heavy. The repetition behavior would suffer and a lead weight would have to be attached to the front end of the key. It is desirable to create the difficulty of playing with the hammer return spring in order to feel that you have the hammer under control while playing. This is the case with grand pianos because the hammer lies horizontally and its weight creates this effect on the key. This effect should be created on piano mechanics.
• 4a) Return of the game severity when the key is released: If the player presses the key 1 , the force of the hammer return spring 44 acts on the finger 35 via the jack 35 , the lifting member 12 and the key 1 and generates part of the game severity. However, if he releases the button, this reaction is missing or it is very diminished. As a result, the finger largely does not get back the energy that it has given to the key. This problem grows with the strength of the hammer return spring. The invention is intended to provide the possibility that the hammer return spring exerts as much force on the key when the key is released as when the key is depressed.
• 5) When the key movement is transmitted to the hammer, especially when the hammer return spring 47 is reinforced, friction occurs at the transition from the jack 35 to the butt 44 . This friction is given in the piano, the quiet game, by the contact pressure of both parts, which the hammer return spring 47 produces. This friction with quiet play should be reduced or eliminated.
• 6) Dancing the butt on the jack: The maximum space between the butt and jack, called "ribbon air", ie the play of the butt 44 to the jack 35 is limited by the strap 51 . If the ribbon wire 52 is bent so that this jack air becomes minimal in the idle state, the ribbon will sag due to the geometry of the arrangement during the striking process, so that the butt 44 on the jack 35 begins to dance when the same tone is repeated. As a result, the player loses the feeling of having the hammer under control. This problem is to be solved by the present application.
• 7) If the left pedal is depressed and the stroke of the hammer felt 58 down to the string 26 is reduced, a considerable jack air is created. The first part of the keyboard path has no effect. This is extremely uncomfortable, so that the left pedal is hardly used on the piano. The tongue air when the left pedal is depressed is to be prevented by lowering the keys when the pedal is depressed, so that the key stroke is reduced, as is the case with a few modern wing designs. Only this reduced key stroke with a reduced hammer stroke results in a new timbre when playing the pianissimo.
• 8) In Fig. 3, the key 1 is pressed at the point P ₁ . If it is pressed at point P ₁ ', the lever arm is lower up to the tipping point of key 1 . In order to achieve the same torque, button 1 must be pressed more strongly at position P than at position P ₁ '. This difference is significant and should be reduced.
• 9) Rolling behavior of the pilot 10 on the lifting link felt 11 . In Fig. 4 the lifting link felt 11 is flat. There are also constructions in which it is slightly convex in shape with respect to the Pilote 10 . In both cases there is friction. The aim is to find the form in which the pilot and the lifting link felt really roll on each other, and no friction occurs.

The problems presented are partly caused by the Patent applications P 44 14 109, P 44 14 139 and P 44 14 145 solved, but with a significant change in design, what at high conversion costs and increased production costs leads, sometimes with complex designs, what the Production costs continue to rise.

U.S. Patent Application 4,119,008 solves problem # 1a, but has a complicated design and is when the Mechanics built into the piano cannot be adjusted. she does not solve problem # 2 and thereby improves the Repetition properties only moderate.

French patent application 89 12 409 solves problem no. 1 with a spring between the butt and the tip of the tongue, which is attached laterally, and solves problem 2 by cushioning the hammer action on its last section, ie directly in front of the string. During hammer action, the spring rubs against its point of attack at the tip of the jack. The hammer return spring is missing and there is no possibility to solve problem 4. The necessary pressure on the button is generated by a spring on the lifting link ( Fig. 1, part no. 67 of this French application) and lead weights in the lifting link. If a hammer return spring were installed to solve problem 4, the spring between the butt and the tip of the jack would have to be strengthened and the release of the jack, in which this spring is tensioned with a high ratio, would require too much force.

European patent application 0 229 746 A2, which is a second Jack used to repetition the piano mechanics bring, does not lead to a safe repetition, has the Disadvantage of a complex design and solves problem No. 3a Not. If the hammer return spring were to be reinforced, the second Jack tongue to be armed and required then a too high release force.

Problem 3 is not addressed by any of these applications composed so that a perfect repetition does not take place can. The problems of the above problem list with a higher one Numbers as three are also not resolved, so with these registrations do not have any mechanics which are the wing mechanics achieved or even surpassed, can be built.

The object of the invention is an excellent in quality, easy to build mechanics for pianos, and to gradually solve all of the problems No. 1 to 9 shown. The standard components should be used or only a little modified and these designs by simple Additional parts are added. The basic idea of the invention is formulated in the main claims.

The main advantage of the invention is that an expressive mechanism with a pleasant touch to provide low additional costs, with safe and pleasant piano and pianissimo playing with safe or absolutely safe repetition behavior.

Show it:

Fig. 1, the keyboard of a hammer tool from above,

Fig. 2, this keyboard in side view,

Fig. 3 shows the mechanism of the standard piano action in an overall view,

Fig. 4 shows the central section of this mechanism,

Fig. 4a-c, details of this central cutout,

Fig. 4d is a detailed version of the standard piano action,

Fig. 5 shows a first embodiment of a piano mechanism according to the invention,

Fig. 6 shows the bending shape of the Repetitionsfeder used therein,

FIG. 6a, the bending shape of the Repetitionsfeder used therein,

Fig. 7 is a Unhingeable Schnürchenbefestigung Repetitionsfeder of the lifting member,

Fig. 7a another aushängebare Schürchenbefestigung Repetitionsfeder of the lifting member,

Fig. 8 is a Unhingeable Schnürchenbefestigung the Repetitionsfeder the catcher style,

Fig. 9 is a Unhingeable Schnürchenbefestigung Repetitionsfeder of the lifting member with a slot guide of the Repetitionsfeder the whippen,

Fig. 10 is a movable fastening of Repetitionsfeder to the jack,

Fig. 11 is a rigid fastening of the Repetitionsfeder on the lifting member,

Fig. 12 is an immovable attachment of the Repetitionsfeder to the butt,

Fig. 13 is an embodiment of the hammer swing reduction for the hammer,

Fig. 14 for attachment of the hammer swing reduction for the hammer,

Fig. 15 individually adjustable Hammer swing reduction for the hammer,

Fig. 16 is another individually adjustable Hammer swing reduction for the hammer,

Fig. 17 is another view of the individually adjustable Hammer swing reduction for the hammer of FIG. 16,

FIG. 18 is a still others individually adjustable hammer swing reduction for the hammer,

Fig. 19 shows an alternative form of the damper wire,

FIG. 20 is a still others individually adjustable hammer swing reduction for the hammer,

FIG. 21 is again another way of individually adjustable hammer swing reduction for the hammer,

FIG. 22 is again another way of individually adjustable hammer swing reduction for the hammer,

Fig. 23 is a leaf spring for individually adjustable Hammer swing reduction for the hammer,

Fig. 24, the finished leaf spring device for Hammer swing reduction,

Fig. 25 an alternative design of this leaf spring device,

Fig. 26 is a jack scavenger and an alternative mounting for the ribbon,

Fig. 27 a notched catcher and the catcher matching,

Fig. 28 is a bounce bounce device with a wire,

FIG rotated. 28a to bounce wire 90 degrees,

Fig. 28b a special design of the bumper wire

Fig. 29 is a bounce bounce device having a plate,

Fig. 30 is a device having a bounce bounce doll

Fig. 31 is a Repetiervorrichtung with a repetition lever,

Fig. 32 is a Repetiervorrichtung 2 Repetierschenkeln,

Fig. 33 is a Repetiervorrichtung with acting on the hammer style adjustable by a screw Repetitionsfeder,

Fig. 34 is a Repetiervorrichtung with acting on the hammer style is not adjustable Repetitionsfeder,

Fig. 35 shows a section through Fig. 33,

Fig. 36 is an attachment of the bridle wire Repetitionsfeder,

Fig. 37 is a known rocker switch,

Fig. 38 is a rocker switch according to the invention.

Fig. 5 shows a hammer mechanism according to the invention in a first embodiment. This differs from that of the mechanics in FIG. 4 in the following points:

• - In the lifting member 250 , which is rotatably mounted in the joint AB, there is a bore AC parallel to the bore of the joint AB towards its free end. A resilient wire, the repetition spring 251 , is rotatably mounted in this bore, the end of which is bent over for this purpose. Optionally, the lifting member 250 is recessed around this bore at least on one side, ie provided with a depression, as indicated by the arc around the point AC. This repeater spring leads in an arc around the catcher 54 a and the counter catch 49 b to a bore AD in the butt 252 , which is rotatably mounted in the joint AE. This hole runs parallel to the axis of the joint AE. The repeater spring 251 is also bent at this end, which is rotatably mounted in the bore of the butt 252 , and bent again after passing through this bore, so that the repeater spring 251 does not fall out of the butt 252 . The bending angles are to be selected so that the spring parts protruding from the butt do not rub against the butt. The repeater spring 251 is biased, the tension being so directed that the repeater spring 251 tends to move the counter-catcher away from the lifting member.
  The course of the repetition spring 251 can also be described so that it is rotatably mounted in the butt and first, ie in a first area, leads away from the joint of the butt AE and from the joint of the lifting member AB and then, in a second area, on the Lifting member runs in which it is rotatably mounted. There is a transition between the two areas of the repetition spring, so that there is preferably an ear-shaped course of the repetition spring 251 .
  The repeater spring 251 is either stored directly in a hole in the butt, the diameter of which allows a backlash-free or backlash-free turning, or, better, to prevent rattling noises on the one hand and no jamming due to swelling of the wood on the other hand, in bushings that fit into a corresponding hole the butt are inserted. As bushing material, as is customary in piano mechanics for axle mounting, material is suitable, in particular Kasimir, which, however, is preferably taken thinner and narrower because of the smaller diameter of the wire to be stored. Plastic bushings can also be used. The inner diameter of the bushings is adapted to the diameter of the spring wire, so that the bearing can be rotated. The plastic material is preferably nylon, polyethylene or PVC. It can be drawn in as a tube and then cut off. Or, secondly, the repetition spring 251 is covered with a fine tube at least at the section on which it is mounted, for example in the arrangement in which insulated jumper wires are surrounded with soft material in electrical engineering, and in a suitable bore of the butt used. The hose can be chosen with a larger outside diameter in order to generate a defined friction. The hose can also be longer than the thickness of the butt so that it projects beyond the material in which the repeater spring 251 is mounted in a bore. The entire wire can also be covered with soft material. The bore in which the coated wire is rotatably supported is expediently graphitized. Or, thirdly, the bushing bore is filled with a cord that is provided with a bore. Natural and / or plastic fibers, in particular nylon fibers, are suitable as the material for the cord. In order not to damage soft bearing material, the respective end of repeater spring 251 is preferably pointed before it is inserted into the bushing.
  The point of application of the repetition spring on the butt is preferably placed in such a way that the line connecting this point of attack to the joint AE of the butt is perpendicular or approximately vertical, as perpendicular as possible on the line connecting this point of attack to the point of action of the repetition spring on the lifting member. This also applies to the following embodiments. The lever arm AD-AE, with the Repetitionsfeder 251 acts on the butt is made so great that the torque which the Hammerrückholfeder 254 generated via the Repetitionsfeder on the lifting member 250 is equal to the torque that the Hammerrückholfeder 254 via the jack 35 at off-hook Repeater spring generated on the lifting link. This equality of the torques generated on the lifting link is brought about by selecting points for the point of application of the repetition spring on the butt and the point of application of this spring on the lifting link, the distance from which remains the same when the hammer moves to the string. This principle is to be called the "principle of equidistant points of attack" in this application. This is the ideal case, the best solution to the problem 4 a mentioned above, which is also the yardstick for the following embodiments.
• - On the side facing the hammer style 56 of the damper strip 28 , soft, elastic material 253 , preferably elastic foam, is applied, preferably not a single piece of foam for each hammer, but a continuous strip that extends over several or many mechanical links. The hammer style 56 hits the soft material 253 when the hammer moves to the string 26 just before the hammer hits the string, that is to say on the last section of its way to the string, and can only reach the string by compressing this soft material. If the hammer has little swing, it sticks to the material 253 , if it has more swing it overcomes this hammer swing reduction and reaches the string. In this different effect, the hammer swing reduction according to the invention differs from the prevention of the hammer action of the patent specification DE 44 08 505, which uses a stop bar which, regardless of the force of the hammer, prevents the hammer from moving to the string before reaching the string.
  Foam, also known as "foam rubber", has the advantage over other soft materials, such as felt, that it has a certain basic tension, so that the pressure does not increase continuously from zero when compressed, but, like a prestressed spring, on a certain one Basic level begins. Open-pore foam made of polyether is particularly suitable as the material, but other materials from which foams are manufactured industrially, such as polyurethane or ethylene vinyl chloride, are also suitable. Foamed synthetic rubber materials such as z. B. are commercially available under the name "Neoprene" or "ATP". A protective skin is preferably formed on the open-pore material or a protective skin is applied.
  Function: The repetition spring 251 turns the butt 252 back when it is released after the stop when the button 54 is released, ie it leads the hammer 58 to the string 26 . Is adjusted the power of Repetitionsfeder 251 by ejecting them from the joint AC and bending the wire. The setting is optimal when the hammer is, the catcher 49 b from the catcher 54 a when releasing the button is released, quickly jump up rapidly immigrates on the string 26 without. The progression of the spring wire is chosen so that it can be easily adjusted. If it is too small, you have to bend too much, if it is too big, every little bend is too much.
• - The hammer return spring 254 , which is inserted into the nose 252 a of the butt 252 , is reinforced to such an extent that it produces a pleasant hammer weight, as occurs for the striking finger in the wing mechanism, preferably 50 to 60 pond play, at the key. In order to avoid friction of the capsule string 48 on the butt 252 , a double hook is formed at the free end of the spring, which pulls the capsule string 48 to a certain width in front of the butt 252 . Such a spring is known from application P 44 14 139, part no. 533. However, the double hook of the hammer return spring 254 is preferably not made as wide as the hammer nut capsule 45 , but only so wide that the hammer nut 252 certainly does not rub against the capsule cord 48 when the hammer is moved to the string, ie preferably half as wide as the hammer nut capsule . The position of the hammer return spring 254 in the middle of the capsule cord 48 is thereby better secured. The hammer return spring 254 and the capsule cord 48 are shown in perspective. So that the hammer return spring does not scratch the nose, in the recess of which it is seated, during movement, the cross section of the recess is preferably designed to be trapezoidal. It widens outwards and the hammer return spring 254 does not scratch the edge of the recess in the nose of the hammer nut capsule.
• - The ribbon wire 259 is shorter than usual and more inclined to the normal to the course of the lifting member. The ribbon 51 a is thus longer than the ribbon 51 from FIG. 4. The distance between the two fastening points of the ribbon 51 is shortened in most mechanics during the stop process until it is triggered. As a result, in the course of the striking process, the maximum jack air limited by the band 51 , which is called "band air", increases the play between the jack 35 and the butt 44 when the butt dancing on the jack during the movement process. Even if this ribbon air is set just barely in the idle state of the arrangement (by appropriately bending the ribbon wire 52 ), when the button is repeated, the hammer butt on the jack tongue dances in the other positions. By shortening and increasing the inclination of the ribbon wire 259 , as shown in FIG. 5, and correspondingly extending the ribbon, a case can be found in which the ribbon air remains approximately constant during the stop. It is set as close as possible in the idle state (approx. 1/2 mm). This solves problem # 6 above.
• - The counter catch 49 b differs from the counter catch 49 of Fig. 4 in that its side pointing away from the butt is not perpendicular to the counter catcher style 49 a. The normal on this side at the level of the counter-catcher part 49 a cuts the butt between the extension of the counter-catcher part 49 a and the pivot point AE of the hammer butt. Accordingly, the scavenger is 54 a steeper than the catcher 54 in Fig. 4. This can be achieved in the counterclockwise direction by a different angle of the bore for the catcher wire 53 or by bending the upper end of the catcher wire. These measures make catching the hammer in the catcher 54 a after it rebounded from the string 26 safer.
• The lead weight 255 , which weighs down the end of the key 256 , at which the force of the stop is transmitted to the lifting member 250 , can be omitted. The tilt point AF of the key 256 on the balance beam 257 is, compared to FIG. 4 further, preferably moved away by 2-4 cm from the end of the key on the stop side. Accordingly, the point of attack of the pilot 10 on the lifting member 250 is moved closer to the joint AB in order to keep the overall translation of the keyway to the lifting member constant. Furthermore, the lifting link felt 250 a is made thinner than the lifting link felt 11 from FIG. 3, preferably 2 mm thick, in order not to increase the flexibility of the mechanics and to allow a direct feeling of play. Instead of a felt, leather is also suitable, which can withstand the higher loads for longer. Due to the displacement of the balance beam tipping point, the stop-side end of the key 256 is sufficiently overweight to prevent the lifting member 250 from dancing on the pilot 10 . A thin felt does not increase the noise. This excess weight also enables the lead weight 255 to be eliminated. If a reduction ratio of 1: 2 is selected for the key, the key and lifting element are approximately in balance and the difficulty of play is determined solely by the hammer return spring 254 . An ideal condition. Any necessary corrections to the game severity can be made by a small lead weight in the button or, for environmental reasons, an iron or brass weight. The hammer return spring 254 and the repetition spring 251 can both be amplified beyond the specified value, and the increased game difficulty can be reduced again by a key weight in the front key area or a further increase in the reduction ratio (e.g. 1: 2.5) of the key.

The measure to shift the tipping point AF in the manner indicated means that the ratio of the forces P ₁ to P ₁ 'from FIG. 3 becomes smaller, a considerable gain for the feeling of playing. On a piano with a height of 116 cm, a value can be achieved that is otherwise usual on grand pianos with a length of 220 cm. Problem number 8 has been solved.

If one presses the left pedal of a button designed in this way, which is overweight on the stop side and a ribbon without or with very little ribbon air, then in Fig. 4 the hammer bar 60 is turned counter-clockwise by point H, the keys become lowered. The smaller key stroke enables a nuanced pianissimo play. This solves problem # 7.

The measures which are listed in the discussion of FIG. 5 in the points designated by a dash are not all to be implemented in the same construction.

For example, the soft material 253 can be omitted. The movement of the hammer caused by the repetition spring is braked by the soft material 253 , which reduces the hammer swing when the hammer style 56 touches this material and compresses it as it progresses. If the repeater spring 251 is put under less tension, so that it only carries the hammer in position after the solution of the counter catch 49 b from the catcher 54 a, but does not drive it back to the string, one speaks of a suspension spring instead of a repeater spring. If the repeater spring 251 is designed as a suspension spring, the soft material 253 can be omitted. The repetition behavior of such a construction is better than that of the standard mechanics, but worse than that of a mechanics with a repetition spring and hammer swing reduction.

The distance of the bore AD in the butt 252 to the swivel joint AE of the butt is preferably selected so that the torque which is transmitted from the return spring 254 by the repeater spring 251 to the lifting member 250 about the joint AB is the same, approximately the same or only the torque which is transferred by this hammer return spring via the jack 35 and the jack joint FA to the lifting member 250 about the joint AB is less small. This relieves the jack and the friction of the jack against the butt 254 in the piano is very low, which creates a differentiated feel. Secondly, the force which the hammer butt transmits to the lifting link in the specified ways will remain constant when the butt dancing on the jack is minimized but not completely avoided, as can occur in repetitions, apart from acceleration effects.

FIG. 6 shows the course of the repetition spring 251 in a view rotated by 90 degrees compared to FIG. 5, as it is built into the butt but not inserted into the lifting member 250 . The butt is not shown. The end of the repeater spring 251 , which rotates in the joint AD, is bent again after passing through the butt, but not the end which is inserted into the joint AC of the lifting member. This allows this end to be removed from the lifting link for removal or adjustment. So that the repetition spring 251 in the AC joint has a secure fit in the lifting member, both ends of the repetition spring 251 are offset from one another. If the end of the repetition spring 251 , which is rotatably mounted in the lifting member, is removed from the latter and in this state the bending points of the ends of the repetition spring 251 , at which the regions of the repetition spring 251 , which are inserted in bores of the mechanical parts, bend, with one connected straight line, which is shown in dashed lines, and the points at which the ends of this wire leave the holes of the mechanical parts, also connected with a straight line, which is also shown in dashed lines, these connecting lines together with the areas of the wire, which in the holes of the mechanical parts are intended to run, a non-rectangular parallelogram ( Fig. 6 is not a perspective view). It is thereby achieved that the repetition spring 251 presses into the joint AC with a certain force P in the inserted state, so that it does not require any additional security and can be easily removed in order to adjust it by bending or to take apart the mechanics.

The articulated, resilient wire connection of the butt and the lifting member by means of the repetition spring 251 can also attack at other points which are connected to the butt or the lifting member. On the one hand, the resilient wire, which fulfills the function of a repeater spring, can be rigid in FIG. 4 in a bore of the counter catch 49 , the counter catcher style between the butt 44 and the counter catch 49 , and the hammer style 56 or otherwise. attack firmly connected parts. On the other hand, the spring can engage in bores of parts firmly connected to the lifting member 12 , such as the catcher 54, or of movably connected parts, such as the jack 35 . These points of attack reduce the effect of the repeater spring, but not to zero. Any other part can also be attached to the butt and / or the lifting link and serve as a bearing for the resilient wire connection.

FIG. 6a shows a possible bending shape of the hammer return spring 254 , namely from the string 26 in FIG. 5, in an enlarged view. The spring is inserted with the butt cord 252 b in the nose 252 a of the butt 252 . Her long arm leaves the spiral shape with which she is wrapped around the butt cord 252 b by running away from the inside of the recess of the nose 252 a, crosses the middle of the face of the butt, and then at an acute angle in the double hook on her free Run in end. This prevents scratching noises when moving. There is no need for a trapezoidal recess in the bearing of the hammer return spring.

Fig. 7 shows an alternative attachment of the repeater spring to the lifting member. At the free end of the lifting member 250 b, the string 252 is fastened, preferably by gluing into sawn-in slots on both sides of the lifting member. The string 251 b forms a loop in which the repeater spring 251 a, on the free end of which a hook is formed, is suspended. This connection is secure, frictionless and noiseless when moving and easy to release, e.g. B. to remove the hammer or to adjust the spring. The loop 251 b can instead of the lifting link also on a part firmly connected to the lifting link, for. B. an extension of the lifting link. Fig. 7a shows a free end of the lifting member 250 'used in an inclined bore loop 251 b', in which the hook-shaped end of the Repetitionsfeder 251 is mounted a '. As is known, the loop 251 a 'is glued with a pointed stick 251 a''. The advantage of this position of the string is that it extends less deeply and thus does not hinder the adjustment of the pilot 10 .

Fig. 8 shows the reverse case. The repeater spring 251 c is rotatably mounted in the lifting member 250 , as described with reference to FIG. 5, but as in FIG. 5 in the butt with a bent wire end which secures the repeater spring against falling out. Instead, the repetitive spring can also be rotatably supported by forming a capsule at the free end of the lifting member 250 into which an axis is inserted. The end of the repeater spring 251 c to be stored is in this case designed as a helix through which the fabric garment known in piano construction is drawn. Back to Fig. 8. On the catcher style 49 a, which is attached to the butt 252 ', the string 251 d, which forms a loop, is attached. This is done either by gluing into a counter-catcher style hole or, as shown, by inserting a known clamp 251 e onto the counter-catcher style 49 a, to which the string 251 d, which forms a loop, is attached. The point at which the clamp is seated can be identified by a notch on the counter-catcher style or in a known manner or the clamp rests on the butt. On the repeater spring 251 c a hook is formed at its free end with which it is hung in the loop of the string 251 d. This variant enables a particularly simple hammer removal.

The shape of the wire path of the repeater spring 251 c is drawn in an ear shape. However, if the loop 251d is made longer, this spring can also be shaped with two essentially straight sections which are at an angle to one another, for example in the form of an inverted "L", or a short loop and the spring wire can be used designed as an acute angled reverse "L".

The butt 252 ', as shown, is preferably beveled directly above the counter-catcher style so that the clamp 251 e can be pushed up to the butt and the string and hook of the repeater spring 251 c cannot touch the butt. With the usual mechanical dimensions, the lever arm of the point of application of the repeater spring up to the joint of the butt AE is most favorable when the spring is mounted in the butt as in FIG. 5. The point of application of the repetition spring 251 c on the catcher style extends this lever arm, so that for optimal transmission conditions for the principle of equidistant points of attack, the lifting link had to be extended so that the lever arm with which the repetition spring 251 c carries the lifting link is also enlarged. To avoid this, the string 251 d must be fastened as close as possible to the butt so that the transmission ratios deteriorate only insignificantly. For this, said chamfering of the butt is necessary. An equidistance error of 20% does not yet play a significant role. If you want to further minimize the equidistance error, you have to extend the lifting link in the construction according to FIG. 8, ie increase the distance of the lower point of application of the repetition spring 251 c from the lifting link AB.

Instead of the loop 251 b or 251 d, an eyelet or a hook can also be used.

It is also possible according to the invention to provide the repeater spring with hooks at both ends and to hang it in loops on the lifting link as well as on the butt or an extension thereof, i.e. at one end as in FIG. 7 and at the other end as in FIG. 8. Then the repeater spring has one degree of freedom too much and can tip over the connecting line of its end points. To prevent this, an additional guide must be installed. Fig. 9 shows such a guide on the lifting link. The lifting member 253 rotatably mounted in the capsule 13 in the joint AB is extended at its free end and provided with a slot in the tilting plane of the lifting member. This slot is padded in Fig. 9 with the felt 253 a to avoid noise. The repeater spring 254 is suspended in the loop 251 b, then runs parallel to the lifting link, bends vertically and passes through the slot of the lifting link. Instead of the Filzpolsterung Repetitionsfeder 254 may be coated with a hose to the point at which it passes through the lifting member 253. So that it does not slide upwards, the repetition spring is preferably provided with a bend after the hose. Instead, the hose can cover the entire repeater spring up to its hook.

Instead of the lifting link, a slot guide can be used Repeater spring also on the catcher or on the counter catcher be attached.

Fig. 10 shows a further variant of attaching the repeater spring. The repeater spring 255 is on the one hand rotatably mounted in the butt 256 or, according to FIG. 8, accesses the counter-catcher style via a loop, on the other hand in the short lever arm of the jack 257 , which in turn is in the jack capsule 34 , which is firmly connected to the lifting member 250 , is rotatably mounted. The jack spring 258 is reinforced with respect to the jack spring 36 from FIG. 4 by the force of the repetition spring 255 . Instead, the point of application of the repetition spring 255 on the jack 257 can also lie above the swivel joint F of the jack or to the left thereof if a corresponding nose is formed on the jack. In the latter case, the point of application can be chosen so that the jack spring 258 is omitted, in other cases the jack spring does not have to be reinforced.

Generally speaking, the repeater is on the Hammer actuation device on the lifting link or in the nearer Attached around the pivot point F. she was in the previous embodiments with the hammer device and the hammer actuator is movably connected.

In principle, the flexible connection of the repeater spring to the lifting link and the butt is the best solution. However, tests have shown that the repeater spring can also be connected to the lifting member in such a way that the repeater spring cannot move relative to the lifting member during the striking process, so that it is rigidly attached to the lifting member, e.g. Example, as shown in FIG. 11, the repetition spring 261 is inserted into a bore in the lifting member 260 , which runs parallel to the catcher wire 53 , and is preferably glued there. However, in order to simulate the mobility of the connection, the repetition spring is preferably provided with one or more turns 261 'in the vicinity of its attachment point on the lifting member and there is particularly elastic for movements which would result in rotary movements in the case of a rotatable mounting.

Using this method to form a coil before the end of the repeater spring, which coil is to be called the elastic coil, the attachment of the repeater spring to the butt can also be rigid. At least one of the two fastenings of the repeater spring must be detachable for expansion or adjustment purposes, but neither of the two fastenings has to be movable. Fig. 12 shows such an embodiment. The repeater spring 262 is fastened in the lifting member 260 as in FIG. 11. Then follows the coil 262 'on the repeater spring, which corresponds to the coil 261 ' of FIG. 11. At the other end of the repetition spring 262 , the coil 262 ″ is formed on it with at least one turn, but better 3 to 4 turns. The end of the repeater spring is then attached to a plug eyelet, as used in electronics, be it by soldering, welding or as a clamp connection. This eyelet is placed on a pin, the base of which, preferably having a square cross section, is pressed into a bore in the butt 265 .

The Repetitionsfedern of Fig. 5 to 12 are bent so that they rotate the catcher and the catcher. This is the most favorable case since the spring then does not have a large progression and there is no risk that the spring could rub against the catcher or counter-catcher. Instead of an arch, an L-shape is possible, the spring then runs straight away from the lifting link, bends over the catcher by 90 degrees and runs at a sufficient distance above the counter catcher to the hook with which it is shown in Fig. 8 the loop is hung, or with a further bend for its storage in the butt according to FIG. 5. Intermediate shapes are also possible, other shapes if only their ends are rotatably connected to the hammer device and the hammer actuating device, or provided with elastic coils and are firmly connected, the point of application of the repetition spring on the hammer device has a greater distance from the pivot point of the hammer device than the point of application of the jack and the repetition spring at least partially runs outside an imaginary connecting line of the fastening points of their ends. Outside here means a greater distance from the joints of the hammer device and the hammer actuating device than this connecting line. If the repeater spring does not run around the catcher, it must run between the links of the mechanics. If it runs around the catcher, its course is free in front of or behind or in the drawing plane. Instead of this spring according to the invention, known spring constructions could also be used if they press the lifting member and the butt away from each other. The basic idea of the invention is not in the spring course or the attachment of the spring, but in the combination of a suspension, which has the function of pushing the butt and lifting link away from each other, the tendency to turn in opposite directions, in combination with a swing reduction of the hammer on the last section of it Movement towards the string.

In order that the compression of the soft material 253 by a hammer style does not affect the position of the material opposite the neighboring hammer styles of the mechanics, the soft material 270 can be cut or left out between the hammer styles, as shown in FIG. 13. However, no case was found in the model tests in which this was necessary. Incisions, recesses of triangular cross section and such rectangular cross section are shown.

A disadvantage of the mechanism shown in FIG. 5 and the other figures is that an individual adjustability for reducing the hammer swing of the hammer is still missing. A rough adjustment of the hammer swing reduction takes place by changing the distance of the damper strip 28 from the hammer styles. This is done with the usual measures in piano construction, either by inserting or removing cardboard disks or other thin material between the damper strip 28 and its fastening points on the mechanical jaws, or by fastening the damper strip with screws, the halves of which have opposite threads, preferably on the hammer strip 63 from Fig. 4.

Fig. 14 shows a variant of the fastening of the soft material 271 on the damper bar 28, which is recommended if between the damper bar 28 and the hammer 56 is styles little space. On the side of the damper strip 28 facing away from the hammer style 56 , flat material 271 , which preferably consists of plywood or sheet metal, is attached, which projects under the damper strip in the direction of the mechanical beam 14 . The soft material 272, preferably 8-10 mm thick, which reduces the hammer swing of the hammer styles, is applied to this material. Generally speaking, the soft material is preferably applied to the damper bar or material attached to it.

Fig. 15 - Fig. 22 show individual hammer swing reduction adjustments for the individual hammers.

Fig. 15: the hammer butt 275 is provided on the side in which the hammer style is inserted with a bore which runs approximately parallel to the bore for the hammer style 56 . The flexible stop wire 276 , which runs past the hammer style 56 and is provided at the end with a preferably convex counter-bend, is inserted into this bore. It serves as a stop on the soft, elastic material 253 , 272 instead of the hammer style 56 . The stop wire 276 can be adjusted at its base point, as is customary in piano construction, with a crook. Since the stop wire 276 is not made as strong as the hammer styles, it does not disturb the conditions on the neighboring hammers, even if no cuts are made in the soft material 270 ( FIG. 13). The thickness of the stop wire 276 is preferably 1.5 mm. The soft material 253 , 272 is preferably made less wide for the mechanical units of the lighter hammers of the treble, ie that its vertical extension in FIG. 15 is smaller than that of the heavier hammers of the bass registers. Instead of the hammer butt, the stop wire can also be attached to the hammer head 57 and would then point downward.

Fig. 16 and Fig. 17 show an alternative of an adjustable stop wire. The wire 280 is bent in a U-shape at the point opposite the soft material 272 , runs parallel to the hammer style 56 , is bent by 90 degrees on both legs at the base of the hammer style, takes the hammer style in the middle with both legs, then runs parallel to it Top of the butt and is also U-shaped at the other end and pulled up a bit. "End" here refers to the representation in the drawing. The beginning and end of the real wire are around the 90-degree bend at the base of the hammer style. The wire 280 can be used at this point and is fastened to the butt with the screw 282 and the washer 283 . The adjustment is made by moving the wire structure 280 . The thickness of the wire 280 is preferably 0.5 mm if it is made of steel.

In Fig. 18, the cross section of the damper bar 290 is trapezoidal in shape, so that one edge of the damper bar 290 is located closer to the hammer style 56, than the other. A clamp 291 is preferably clamped at the base of the hammer style and continues in the sheet 292 , which is bent at its free end toward the hammer style 56 . The soft material 293 is applied to this free end. The clamp 291 and the sheet 292 can be made from one piece or can be composed of two pieces.

The clamp 291 is shown in FIG. 18 as a clamp, but a screw clamp can also be used.

Function: If the clamp 291 is pushed away from the butt, the distance of the soft material 293 from the damper strip 290 is reduced. The soft material 293 is preferably felted or leather-coated on its side facing the damper strip 290 .

Instead of applying the soft material to a continuation on the clamp 291 , it can be applied according to the invention to the damper strip 290 as described above.

Fig. 19 shows another form of the damper wire. If there is not enough space between the damper bar and hammer style, the damper bar must be moved further away from the hammer styles. To do this, the damper wire 24 of FIG. 4 must be laid. In Fig. 19, the damper wire 300 extends a little parallel to the damper arm 21 from its end to which the damper 25 is screwed, then bends away from the damper bar to make room and then runs parallel to the damper bar. At the other end, the damper wire 300 bends back and then bends to secure it in the damper arm 21 . In this way, approx. 5 mm can be obtained.

In Fig. 20, a flexible wire 310 is attached to the damper bar 28 and brought up in the direction of the hammer head 57 . A piece of soft material 311 is attached to its free end, which the hammer style encounters during the course of the hammering. This arrangement is adjusted by bending the wire 310 . According to the invention, the flexible wire, on the free end of which soft material is applied, can also be guided in the direction of the butt from the damper track to which it is attached, so that the lower end of the hammer style 56 abuts it.

Fig. 21 shows an alternative adjustable Hammer swing reduction, which acts against the hammer style 56th In the damper strip 28 a, the screw 312 is screwed, the head of which is covered with the soft material 313 . This arrangement is adjusted by selecting a screw in the hexagonal head and a hexagon socket wrench for adjustment.

Fig. 22 shows another adjustable hammer swing reduction, in which a clamp 314 is attached to the hammer style 56 , which has a projection 314 a, in which the screw 315 is screwed. The screw 315 runs next to the hammer style and parallel to the hammer 57 . The free end of this screw strikes the resilient hammer swing reduction 253 on the hammer bar 28 .

Fig. 23 shows a resilient sheet as an alternative to foam. From a rectangular, rust-free, resilient sheet, as z. B. is used for beverage cans, recesses are punched out, so that a base 320 a with a series of tongues 320 b with gaps between these tongues remains. Then, as shown in FIG. 24 for a tongue, the base 320 a is preferably attached to the damper strip by gluing, each tongue 320 b is bent into a U-shape on the base 320 a, one on the side facing the hammer style 56 of each tongue Bulge is formed, the convex side facing the hammer style 56 . An adjustment screw 321 , preferably a plate screw, is screwed into the damper strip 28 for each tongue, and the free end of each tongue is inserted under its head. The tongues are so biased that their tension presses their free end against the head of the plate screw. The side of each tongue 320 b facing the hammer style 56 is covered with the felt 320 c up to its free end.

If the hammer style 56 now strikes the tooth 320 b of the resilient plate 320 , it bumps against a prestressed hammer swing reduction. The advantage of the resilient sheet over foam is the longer service life. The disadvantage 25111 00070 552 001000280000000200012000285912500000040 0002019703422 00004 24992 is that the vibration is undamped. Optionally, the free space of the U-shape can be filled with low-strength foam, the spring force of which is insignificant, but which dampens the vibration. The distance of the tooth 320 b from the hammer style is adjusted with the screw 321 , the spring force by removing the tooth from the stop on the screw 321 and bending.

Instead of the screw 321 , a fixed stop can also be used and the adjustment can be carried out with the wire 276 from FIG. 15 or the screw 315 from FIG. 22. In this case, the projection on the tongue, which is convex to the hammer style, can be omitted. Fig. 25 shows the suitable shape of the spring plate. The spring plate 325 is bent around the damper strip 28 , then bent again. The tongue of the spring plate 325 is inserted under this bend, it being covered with the soft material 325 on this side. In this material the adjusting elements take from FIG. 15 and FIG. 22.

Instead of a double right-angled bend at the lower edge in FIGS. 24 and 25, a round bend can take place there. The vibration damping of the tongue can be done by applying vibration damping material to the tongue, e.g. B. done by gluing an epoxy resin laminate. The tongues for the mechanical units with lighter hammers can be made less pretensioned by a narrower design or a larger bend.

Instead of the hammer swing reductions described in FIGS. 5 and 13-24, the hammer swing reductions of French patent application 89 12 409 can also be used. However, these offer no advantage because they have more complex designs. In addition, unlike the foam construction, they have no vibration damping.

Fig. 26 shows another arrangement of the ribbon. The ribbon 335 is attached to the hammer style 56 about 10-20 mm from the base of the hammer style. The ribbon wire 336 is longer than the ribbon wire 52 in FIG. 4, so that the ribbon runs flat. The dimensions are chosen so that the distance between the position of the hammer style 56 at which the ribbon 335 is attached and the location where it is attached to the ribbon wire 336 remains constant during the striking process, that is, operate according to the equidistance principle formulated above. In this way, the jack air can be reduced further during the hammering action than with the ribbon construction according to FIG. 5. This creates an extremely handy feel.

Fig. 26 further shows a jack tongue construction known per se. If the proposed repeater spring is used, the hold of the counter-catcher 49 in the catcher 54 ( FIG. 4) is uncertain. The hammer usually jumps out of the catcher 54 after the stop and moves forward to reduce its hammer swing. This is beneficial for the safety of the repetition, but not for the uniformity when trilling. Around 1900, the Bechstein company built piano mechanics with jack catchers, which are used here with minor modifications.

The jack 330 is thickened at the upper end and extends beyond the end reaching into the butt 331 ( 330 a). A hard, flexible wire, preferably 2 mm in diameter, is attached to the butt, to which the counter-catcher 333 is attached. This is covered with leather on the side facing the jack 330 . The location of the jack tongue 330 , which points towards the counter-catcher 333 , is covered with the jack tongue felt 334 . What is new is to leave out a window 330 b on the thickening of the jack 330 in order to reduce the inertia. The outline of this window preferably follows the outline of the jack. Second, the tongue catcher felt 334 is preferably designed to be stronger than in the Bechstein original.

If the jack 330 in the joint BA rotates clockwise, as is the case towards the end of the hammering step towards the string, the butt 331 with the counter-catcher 333 falls on the jack catcher felt 334 of the jack 330 . If the jack sinks, as is the case when the button is released, the hammer is released again.

This arrangement has the further advantage that the catcher 54 and the catcher wire 53 from FIG. 4 are omitted. This creates space for the repetition spring 251 and the hoisted ribbon wire 336 .

The disadvantage of the tongue catcher is that the stop of the key 1 is intercepted hard. It is no longer felt 8 that brakes the keystroke, but jack felt 334 . This cannot be designed as soft as the felt 8 , otherwise the release of the hammer will be delayed. In addition, the translation of the jack movement provides additional hardness of the reaction to key 1 when intercepted. It is not the noise that is the problem, but the feel of the game. To reduce this hardness, the 334 jack tongue felt is 5 mm thick, while 3 mm thick felts are applied to Bechstein. However, compared to the standard piano mechanics, there remains a greater hardness, which is not uncomfortable for the applicant's fingers, but conveys a feeling of precision.

FIG. 27 is another possibility shows the safety of the capture process to increase the per se known notched catcher construction. The viewing direction is based on FIG. 5 from above. In principle, it is a form of catcher and countercatcher, as Jakob Schaf stated and as described in Pfeiffer p. 58. The catcher 350 has on its side facing the catcher 351 side has a concave shape, preferably a V-shape, the catcher 351 is correspondingly on its side facing the catcher 350 side convex, preferably roof-shaped. As usual, the counter-catcher is covered with leather ( 351 a), the catcher 350 with thin felt ( 350 a). This construction has proven itself in the mechanics in Fig. 5, it holds the counter-catcher better in the catcher, so that the repeater spring 251 can not solve the connection of the two so easily. An amount of 60-70 degrees has proven to be suitable as the notch angle beta, while sheep used 90 degrees. The inclination of the catcher and counter-catcher is chosen as in FIG. 4.

Another possibility of improving the catching process is to use foamed neoprene for the catcher felt 55 in FIG. 4, possibly also to produce the counter-catcher leather 50 also from foamed neoprene.

Fig. 28 shows an adjustable bouncing device which allows the hammer butt to bounce back from the front of the jack 35 after it has been released, ie when the button is pressed. In order to make repetition quite safe, the hammer, if it crosses the point at which the catcher catches it when it rebounds from string 26 , must meet resistance which, in unfavorable cases, prevents it from falling back too far and in Catcher stuck. The situation is unfavorable if the key is released from the string during the rebound of the hammer and is then quickly pressed again. In this case it must be prevented that the hammer falls into the catcher.

For this purpose, the butt 360 , preferably at the point at which the center of the circular arc is located, which forms the outside of the butt leather 46 ( FIG. 4), is provided with a bore into which the buff wire 361 , on which an angled fluted foot is located is formed, is pressed. The bump wire runs along the butt along the butt leather 46 , is angled a few mm under the counter catcher style 49 a, i.e. on the side of the counter catcher style facing away from the hammer catcher 56 , then runs under the counter catcher style over the width of the butt with a small distance ( approx. 1-2 mm) from the hammer butt leather, is then angled in the opposite direction to an extension that runs approximately parallel to the opposing style 49 a or runs slightly away from it. The portion of the bump wire 361 running across the width of the butt is covered with a suitable hose 362 , preferably made of silicone.

FIG. 28a shows the course of the rotated 90 degrees bounce wire 361st One recognizes the angled, pointed and scalloped foot, then the course that leads along the butt in Fig. 28, then the renewed bend, so that the foot, course and renewed bend run in a wide U-shape, then the bend of the Extension, so that the course, renewed bending and extension run in a right-angled Z-shape. The hose 362 is pulled over the "renewed bend".

On the extension of the bumper wire 361 is for adjusting a rod of solid material, such. B. brass, which is provided with a suitable hole, and this rod moved up and down with a hammer. The bump wire 361 rotates around its base in the butt 360 . The diameter of the bounce wire is preferably 1.5 mm. The baffle wire can be flattened slightly in the area between its base in the butt and the first bend from above and below (in the drawing of FIG. 28) in order to reduce the bending stiffness during adjustment and thus to facilitate the adjustment process. The buffer wire is adjusted so that the hammer would be prevented from falling back by the buffer wire 5 to 8 mm after the catch point. To do this, the catcher is first bent away from the counter-catcher and readjusted after adjusting the bounce wire. If the distance of the hammer felt 58 from the string 26 in the caught state is 16 mm, this distance is 24 mm when the bounce wire is seated on the jack.

FIG. 28b shows a safeguard against a possible sliding out of the hose 362 from the section of the bumping wire running transversely to the butt. At the point where the extension 361 a is angled, an additional bend with a small radius is applied, which runs in the plane of the butt.

The disadvantage of the baffle wire construction is that the adjustment of the baffle wire 361 by bending is uncomfortable. Fig. 29 shows a construction in which the bouncing device is adjusted with a screw. Hammer butt 370 a, counter catcher style 370 b and counter catcher 370 c are made from one piece 370 , so that the counter catcher style has a rectangular or square cross section. Instead, a counter-catcher style of such cross section can also be glued into the butt, preferably with tongue and groove. On the side of the counter-catcher style 370 b, which faces the jack 35 , a piece of flat, elastic material, preferably stainless steel sheet, is attached to the baffle plate 371 at the end of the counter-catcher style facing the counter-catcher 370 c, preferably with a screw 372 . To prevent the piece 371 from rotating around the screw 372, a tapered end of the baffle plate 371 is inserted in the counter-catcher 373 c. This tapered end is bent in the drawing, but can also run straight. The baffle plate 371 has the width of the counter-catcher style 370 b and presses resiliently against it. It is kept at a distance by the screw 373 turned towards the baffle plate by the counter-catcher style. It is covered with felts 374 and 375 on both sides for noise reduction. The string 376 is glued into the counter-catcher style 370 b and forms a loop in which the repeater spring 251 c is suspended. Both ends of the string 376 can be fastened in one bore or in two bores which are located one behind the other in the drawing. Such a sling with a wide base facilitates hanging and unhooking the repeater spring 251 c. As a special feature, the butt 370 a has a smaller expansion in the direction of the counter-catcher style and a sharper curve 370 aa at the attack of the jack 35 than usual. The narrower design allows the point of repetition spring to move closer to joint G of the butt. The sharper curve ensures a clear trigger point, a win for the feel of the game.

To adjust the distance of the baffle plate 371 from the counter-catcher style 370 b, the screw 373 , which is preferably designed as a grub screw, is rotated. The baffle 371 can also be made of elastic plastic material, e.g. B. nylon or thin plywood.

Fig. 30 shows a third solution of an adjustable bounce device. The counter-catcher style 49 rotates an adjusting screw 381 which is common in piano construction and onto which a doll 380 padded with the soft material, preferably leather, is screwed. The doll is on the side facing to the jack 35 side of the catcher and near the butt skin 46th The set screw 381 preferably runs parallel to the course of the butt leather at the level of the doll 380 . The manikin is preferably made less tall than usual in piano construction and preferably bevelled on its upper side, as shown. These measures ensure that the manikin is at a sufficient distance from the tip of the jack. The bounce point can be specified by making the doll convex on its side facing the jack.

Generally speaking, it is in the constructions of Fig. 28, Fig. 29 and Fig. 30 is a mounted on the hammer butt or an extension of the butt adjustable bounce device that limits the dropout of the hammer butt, by the end face of the jack at the relapse of the hammer , if this exceeds a certain distance, bumps against a padded resistor, the fallback distance being adjustable. In the designs of Figs. 29 and FIG. 30, the cushioning between the jack and bounce device may also be attached to the jack by a the front side of the jack superior leather is glued on the facing away from the butt side of the jack.

Fig. 31 finally shows an alternative design for the Repetitionsfedereinrichtung. The repeater arm 391 is rotatably mounted at the free end of the lifting member 390 , which is preferably extended for this purpose. A capsule bearing is shown, but a connection with flexible material such as sheet metal or parchment is also possible. The repetition leg is less extended perpendicular to the plane of the drawing than the lifting link. At the free end of the repetition leg 391 , the repetition spring 392 is mounted, the free end of which is movably and detachably connected to the butt 252 or 44 , here via a loop attached to the catcher style 49 a. At the free end of the repeater leg, a screw 393 is attached, on which an extension of the repeater spring presses. This method of spring adjustment is known in piano construction with standard grand piano mechanics. The advantage of this device is that the repeater spring can be adjusted with a screw.

Fig. 32 shows a variant with 2 Repetitionsschenkeln and 400, wherein the repetition lever 401 is rotatably mounted at the free end of the repetition lever 400 401. At the free end of the repetition leg 401 , a hook 402 is attached, which is movably and detachably connected to the butt 44 . The repeater spring 403 is accommodated in the leg 400 and presses against the leg 401 .

Fig. 33 shows a Repetition Setup wherein the Repetitionsfeder 404 in a window that is to located in the lifting member 405 to its free end, stored, there being the adjustment screw 406 presses against the bent end of the Repetitionsfeder 404. The spring is guided in the form of an inverted "L" or ear-shaped to the hammer style 407 , preferably bent there in a z-shape and hung in a hook 408 which is rotatably mounted in a hole in the hammer style 407 . Fig. 35 shows this checkmark rotated 90 degrees in the section of the hammer style. After passing through the bore, the wire from which the hook is formed is preferably bent toward the butt 44 . The entire wire from which the hook is formed is expediently covered with a fine, not shown plastic tube in order to avoid noise. The repetition spring 404 is pre-bent so that it exerts a torque on the hammer in order to drive it against the string (not shown).

The repeater spring bends to the point at which it is hooked into the hook 408 , so that it points essentially perpendicularly away from the lifting member 405 and extends up to, preferably above, the damper strip 28 . On the damper strip 28 , the leather 409 is glued or other soft material is applied to the side thereof which faces the hammer style 407 . The repeater spring 404 is convexly curved at its end, at the point opposite the leather 409 . The leather 409 can be omitted if the Repetitionsfeder 404 is coated at least on the point at which it faces the damper bar 28 having a suitable hose.

Function: With its towering arm, the repeater spring generates the force necessary for the repeater function. Its free end hits the damper bar during hammer action, and therefore no longer transmits its force to the hammer, so that the hammer swing reduction is generated. The position of the hammer gear at which the hammer swing reduction begins can be adjusted by bending the free end of the repeater spring, ie by bending close to the point at which it is hooked into the hook 408 . This is done with pliers after the repeater spring has been unhooked from the hook 408 .

Fig. 34 shows an alternative fastening of the Repetitionsfeder 404 'at the free end of the lifting member 405'. In the lifting member 405 'a slot is sawn in its swivel plane, perpendicular to the swivel plane there is a hole through which round material 410 is inserted and glued. The end of the repetition spring 404 'is wound into a coil through which the round material 410 is inserted. After the bobbin, the repetition spring 404 'continues in an extension pointing to the lifting member, which is inserted into a bore made in the lifting member. This type of attachment is suitable for upgrading pianos. The force of the repetition spring 404 'is adjusted by bending.

Fig. 36 shows an alternative compound of Repetitionsfeder the hammer actuator. On the ribbon wire 259 ', which is fastened in the lifting member 12 , a coil is formed, in which the loop 251 f is hung. The repeater spring 251 e, at the end of which a checkmark is formed, is hung in this loop. This arrangement of the loop has the advantage over the arrangement in FIG. 7 that the loop does not hang so low that the pilot 10 (see FIG. 3) is freely accessible for adjustment purposes.

Fig. 37 shows a transmission of the key 411 to the lifting member 412 does not have a Pilote, but via a rocker key 413th Such rocker switches, which represent a two-armed lever, were previously used, but are difficult to adjust because 2 screws have to be adjusted. The screw 414 adjusts the height of the key rocker, the screw 415 ensures its firmness on the key. The advantage of key rockers is that the transfer to the lifting link takes place with a roller shape and not a spherical shape as with the Pilote. The dome digs into the lifting link felt 416 more than the roller, and the rolling conditions at the edge of the dome are different than in the middle, while they remain the same with a roller shape. In order to reduce friction, the roller shape of the key rocker 413 is graphitized.

Fig. 38 now shows a rocker switch according to the invention, the adjustment takes place via a single screw, whereby the necessary pressure is produced via a spring. The rocker 421 is tiltably seated on the button 420 , the connection being secured against slipping by the pin 422 . The key rocker 421 forms a two-armed lever around the tipping point on the pin 422 , one arm of which engages with a graphitized surface of a suitable radius 421 a on the lifting element (not shown), and the other arm of which is pushed away from the key 420 by a preferably helical or funnel-shaped spring 423 is against the head of a screw 424 , which passes between the spring 423 and the tipping point on the pin 422 through a hole, but preferably an elongated hole, of the key rocker 421 and is screwed into the key 420 . The spring 423 , which engages on the other lever arm of the key rocker 421 , presses the key rocker against the head of the screw 424 on the one hand, and the key rocker at its contact point on the key 420 against this key on the other hand. According to the invention, the same function is performed by a tension spring which acts on a lever arm, the lever arm of the key rocker, which transmits the movement of the key to the lifting member and engages the key 420 . A hexagon shape or the head with cross hole known in piano construction is suitable as the head of the screw 424 . The portion of the key rocker 421 which presses against the head of the screw 424 is preferably convex. An optional washer between the screw head and the rocker switch makes the construction more durable.

The axis of the roller shape with which the key rocker preferably engages the lifting link, preferably runs perpendicular to the lifting link, i.e. parallel to the axis in which the lifting link turns. The longitudinal course of the button rocker is adapted to the length of the key.

In addition to the mentioned advantage of adjustment with just one screw, this key rocker has the advantage, in particular in the mechanical constructions of the designs according to FIG. 7 or FIG. 9, that the adjustment iron can access an exposed adjustment element.

Claims (25)

1. Hammer mechanism unit for pianos, with

• a) a hammer device consisting of
  • - a pivoted hammer butt ( 44 , 100 , 252 , 252 ', 256 , 265 , 275 , 331 , 360 , 370 a),
  • a hammer attached to it for striking a string ( 26 ), which consists of a hammer style ( 56 , 407 ) and a hammer head ( 57 , 58 ),
  • - a counter-catcher device, consisting of a spacer element ( 49 a, 332 , 370 b) and a counter-catcher ( 49 b, 333 , 370 c) firmly connected to the butt,
  • - a return spring device ( 47 , 48 ; 254 , 48 ) which exerts a force on the hammer device for returning to its rest position,
• b) with a hammer actuating device for moving the hammer device
  • - a pivoted lifting link ( 12 , 250 , 250 b, 253 , 260 , 405 , 405 ', 412 ),
  • - A pivotable on the lifting link jack ( 35 , 102 , 330 ), which has an arm which acts depending on the position of the lifting link on the butt, to put on the butt, move it to a string ( 26 ) and then can release,
  • a catcher device ( 53 , 54 , 55 ; 53 , 54 a, 55 ; 330 , 334 ; 350 , 350 a), which holds the hammer device on its counter-catcher device when the hammer device falls back in the direction of its starting position,
• c) a gear limiting device ( 51 , 52 ; 100 a, 102 a; 51 a, 259 ; 335 , 336 ) which limits the jack air, ie the distance between the jack and its point of attack on the butt,
• d) a spring device ( 251 ; 251 a, 251 b; 251 c, 251 d; 251 b, 254 ; 261 ; 262 ; 251 c, 376 ; 391-393 ; 400-403 ; 404 , 408 ) with the hammer device and is connected to the hammer actuation device, the tension of which exerts opposing torques on the hammer device and hammer actuation device, in the sense that the counter-catcher device moves away from the lifting member,

characterized in that the spring device ( 251 ; 251 a, 251 b; 251 c, 251 d; 251 b, 254 ; 261 ; 262 ; 251 c, 376 ; 391-393 ; 400-403 ; 404 , 408 ) is biased, from its connection with the hammer device from the pivot point of the hammer device and from the pivot point of the hammer actuating device initially, that is to say in a first region of the course of said spring device, and then after a transition area, that is to say in a second area of the course of this spring device, runs towards the lifting member and is connected to the hammer actuator. 2. Hammer mechanism unit according to claim 1, characterized in that the spring device ( 251 ; 251 a, 251 b; 251 c, 251 d; 251 b, 254 ; 261 ; 262 ; 251 c, 376 ; 391-393 ; 400-403 ; 404 , 408 ) transmits a force due to its preload to other parts of the mechanics only at 2 points. 3. Hammer mechanism unit according to claim 1 or 2, characterized in that the spring device with one of the two parts ( 49 a, 252 ) which connects them, or with both ( 250 , 252 ; 252 , 250 b; 250 , 49 a; 49 a, 253 ; 256 , 257 ) is movably connected. 4. Hammer mechanism according to claim 3, characterized in that the spring device ( 251 ; 251 a, 251 b; 251 c, 251 d; 251 b, 254 ; 261 ; 262 ; 251 c, 376 ; 391-393 ; 400-403 ; 404 , 408 ) from a resilient wire ( 251 ; 251 a, 251 b; 251 c, 251 d; 251 b, 254 ; 261 ; 262 ; 251 c, 376 ; 404 , 408 ). 5. hammer mechanism unit according to claim 4, characterized in that
the resilient wire ( 251 , 251 a, 251 c, 254 , 255 ) at one of its ends in one of the two parts ( 252 , 250 , 256 , 331 ), which it connects, rotatably supported and secured against falling out by bending its end , and
either the resilient wire ( 251 a, 251 c) at the other end with a hook formed there in a loop attached to the other of the two parts ( 250 b, 49 a, 370 b) ( 251 b, 251 d, 376 ) or eyelet or a correspondingly curved hook is attached,
or that the resilient wire ( 251 , 255 ) is also rotatably mounted in the other of the two parts ( 250 , 257 ), this wire being pretensioned so that the pretension pushes it into the bearing,
or that on both of the parts connected by the resilient wire ( 254 ) ( 49 a, 253 ) a loop ( 251 d, 251 b), a hook or an eyelet is formed, in which the wire is suspended, whereby on Lifting member ( 253 ) is preferably a capsule-shaped recess through which the wire ( 254 ) passes. 6. Hammer mechanism unit according to claim 3, characterized in that the spring device

• a) consists of a leg ( 391 ) which is rotatably mounted on the hammer actuating device at the free end of the lifting member ( 390 ) and a resilient wire ( 392 ) attached to the leg at the free end, which is connected to the hammer device, whereby against the free End of the leg is preferably attached to an adjusting screw ( 393 ) for adjusting the spring force of the wire, or
• b) from a leg ( 400 ) which is rotatably mounted on the free end of the lifting member ( 390 ), wherein at the free end of this leg a further leg ( 401 ) is rotatably mounted, which is connected to the hammer device, one of the two Leg is a spiral spring ( 403 ) is attached, the force can preferably be adjusted by an adjusting screw and this acts on the other leg so that it increases the smaller angle of the two legs to each other.

7. hammer mechanism unit according to claim 5 or 6, characterized in that the loop ( 251 d, 376 , 402 ) on the spacer element ( 49 a, 370 b) of the counter-catcher device and / or at the free end of the lifting member ( 250 b, 253 ) is attached . 8. hammer mechanism unit according to claim 1, characterized in that the spring device consists of a resilient wire ( 261 , 262 ) which is rigidly attached to at least one of its ends, with this end to this wire to a coil ( 261 ', 262 ' , 262 ''). 9. hammer mechanism unit according to claim 4, characterized in that the resilient wire ( 404 ) is attached to the free end of the lifting member ( 405 , 405 ') and movably engages the hammer style ( 407 ), preferably by having a z-shaped bend in a hook ( 408 ) is rotatably mounted in this. 10. Hammer mechanism unit according to claim 1, characterized in that a damper strip ( 28 ) is present which extends over a plurality of hammer mechanism units, to which damper strip the hammer style runs when the hammer mechanism unit is actuated, flat, solid material ( 271 ) optionally being attached to the damper strip is. 11. Hammer mechanism unit according to claim 9 and 10, characterized in that the resilient wire ( 404 ) from its mounting on the hammer style ( 407 ) from the lifting member ( 405 ) pointing away and preferably opposite with a convex bend of the damper bar ( 28 ). 12. Hammer mechanism unit according to claim 1 and 10, characterized in that on the hammer device or on the damper strip ( 28 ) or an attached part ( 271 ) elastic material ( 253 , 272 , 313 , 293 , 311 ), preferably foam, preferably open-pore Foam is attached, which is compressed by the movement of the hammer device when the piano strikes against the end of the gait of the hammer (), so that the hammer swing is reduced without being prevented, this foam preferably made of polyether, ethyl vinyl chloride, PU foam or foamed synthetic rubber, preferably neoprene or ATP. 13. Hammer mechanism unit according to claim 1 and 10, characterized in that on the damper strip ( 28 ) at least one resilient plate ( 320 , 325 ) is attached to the U-shaped pretensioned tongues ( 320 b) are formed, each for one Hammer device, wherein the side of the tongue facing the hammer device is preferably convex and this side of the tongue is preferably covered with soft material ( 320 c, 326 ), preferably felt, the hammer device or a part attached to it towards the end of the gear of the hammer against the tongue beats and the hammer swing is reduced without being prevented. 14. Hammer mechanism unit according to claim 1 and 10 and 12 or 13, characterized in that on the hammer device, preferably on the butt, a wire element ( 276 , 280 ) is attached, which is guided past the hammer style ( 56 ) and that when the hammer is in motion on the elastic material fastened according to claim 12 or on the tongue according to claim 13. 15. Hammer mechanism unit according to claim 1 and 10, and 12 or 13, characterized in that on the style ( 56 ) of the hammer, a clamp ( 314 ), preferably a clamp is attached, through which a screw ( 315 ) is rotated, the end of which The hammer meets the elastic material ( 253 ) on the damper bar ( 28 ) or the tongue ( 320 b). 16. Hammer mechanism unit according to claim 1, characterized in that the hammer device has an adjustable, preferably padded extension ( 361 ; 371 ; 380 , 381 ) which is preferably attached to the butt ( 360 ) and which, when it falls back on the portion of the jack ( 35 ) that touches the hammer device, preferably on the front of the jack. 17. Hammer mechanism unit according to claim 16, characterized in that
an initially U-shaped bump wire ( 361 ) is attached to the butt, a section of which runs perpendicular to a butt leather attached to the butt in a known manner, this section being covered with a hose ( 362 ), preferably made of silicone is which bounce wire has an extension pointing away from the butt, or that
flat elastic material ( 371 ), preferably sheet metal, is attached to the spacer element ( 370 b) of the counter-catcher device on the side pointing towards the jack ( 35 ) at its end opening into the counter catcher ( 370 c), and an adjusting screw () through the spacer element of the counter catcher ( 373 ) that hits the flat elastic material, or that
through the spacer element ( 49 a) of the counter-catcher, an adjusting screw ( 381 ) is rotated, which carries a doll ( 380 ), which is preferably covered with soft material, on the side of the spacer element pointing towards the jack ( 35 ), the adjusting screw preferably being inclined into the spacer element of the Counter bolt is screwed, preferably parallel to the shape of the butt between the attack area of the jack and the attachment point of the spacer element of the counter catch, the side of the manikin ( 380 ) facing the jack being preferably convex. 18. Hammer mechanism unit according to claim 1, characterized in that the gear limiting device of the jack air in a known manner from a ribbon wire attached to the lifting member ( 52 , 259 , 336 , 259 ') and a ribbon ( 51 , extending between the hammer device and the free end of the ribbon wire) 51 a, 335 ). 19. Hammer mechanism unit according to claim 4 and 18, characterized in that a coil is formed on the ribbon wire ( 259 '), in which a loop ( 251 f) is hung, and the resilient wire with a hook formed at its end in this Noose is hung. 20. Hammer mechanism unit according to claim 18, characterized in that the ribbon is attached to the hammer style ( 56 ) and the ribbon wire ( 336 ) is so long that the attachment point of the ribbon on the hammer style and the attachment point of the ribbon on the ribbon wire during the striking process of the piano cover the same distances. 21. Hammer mechanism unit according to claim 1, characterized in that the catcher ( 350 ) and its counter-catcher ( 351 ) are designed in a known manner so that the catcher on the side facing the counter-catcher has a padded V-shaped incision and the counter-catcher on the Catcher side is roof-shaped, the angle of the incision or the roof angle is 70 degrees or below. 22. Hammer mechanism unit according to claim 1, characterized in that the spacer element ( 332 ) of the counter-catcher device is designed in a known manner as a wire to which a counter-catcher ( 333 ) is fastened and as a catcher the jack ( 330 ), the free of which is also known The end is widened, which widening extends beyond the point of application of the jack on the butt ( 331 ) and is covered with felt ( 334 ) at the end facing away from the butt, the jack being provided with a window ( 330 b) at its widening that preferably follows the outline of the jack. 23. Hammer mechanism unit according to claim 1, characterized in that a tiltable bearing button ( 411 , 420 ) is present, the actuation of which via a button rocker ( 413 , 421 ) moves the lifting member ( 412 ). 24. Hammer mechanism unit according to claim 1 and 21, characterized in that a lever arm of the key rocker ( 421 ) is pressed by a spring ( 423 ) against the head of an adjusting screw ( 424 ) screwed into the key ( 420 ). 25. Hammer mechanism unit according to one of the preceding claims, characterized in that a plurality of hammer mechanism units is arranged in parallel on a mechanical beam ( 14 ).