DE3226184A1 - Tuning key - Google Patents

Abstract

Tuning key having a motor-controlled, automatically adjusting key-receiving bush (STCKS), having an antitwisting means which is braced at wrest pins, is preferably easy to brace and has a small spring excursion, as well as preferably devices for bracing the antitwisting means, having just one point of impact which has an adjustable distance ( DELTA x in Fig 1) with respect to the axis of the key-receiving bush and takes the form of a connecting piece (VSB) braced between two wrest pins (SWIB in Fig 1), the underside of the circumferential surface of one wrest pin blocking the upper side of the connecting piece (OV) and the upper side of the circumferential surface of the other wrest pin blocking the underside of the connecting piece (UV), preferably at the string spool of the wrest pin (WCK), and having preferably devices which ensure that, for each angular position of a wrest pin, the key-receiving bush only has to be fitted once (within a guaranteed adjusting range) and, when fitting and adjusting the antitwisting means, the motor spindle only has to overcome a small displacement for the longitudinal advancement of the tuning fork shank, preferably brought about by a joint (GL in Fig 1) which is arranged between mounting of the longitudinal drive (for example mounting of the motor spindle) and antitwisting means of the tuning key in such a way that, while maintaining the bracing of the antitwisting means, the longitudinal drive is swivelled automatically under its own control (without external control) into the angular position predetermined by the tuning key shank position. The preferred configuration of the invention is such that, in spite of the high torque at the axis of the key-receiving bush, a relatively small and consequently lightweight gear mechanism can be used and, due to the short control displacements, also a motor of small output can be used. <IMAGE>

Description

Socket wrench

The invention relates to an additional application to P 32 00 288.2 or G 82 00 230.4, an application with the same name.

In this An arrangement is disclosed which makes it possible to automatically tune stringed instruments, in particular pianos. Assuming that for what is probably the most common application of the invention, tuning pianos, more than 200 strings are to be tuned, then this means a total of three to four minutes for every second of time / string.

If, for example, 5 seconds / string can be saved, then there is one Time savings of 15-20 minutes. Because of this, the inventor has the technical Task set to build a self-balancing tuning key that has a minimum guaranteed in terms of set-up time, adjustment time and an optimal adjustment range in which it is ensured that for every angular position of a tuning peg, the socket wrench socket only has to be put on once and when putting on and adjusting. the anti-twist device the motor spindle for the longitudinal advance of the shaft of a standard Tuning key only has to overcome a short distance (or when using a longer spindle, can overcome this path very quickly). To reduce the set-up time of the To shorten the tuning key even more, the inventor has the technical task set, a static one to prevent rotation of the motorized arrangement firmly clamped, having only a small spring deflection, directly on the String wrap of the tuning pegs acting, the motor arrangement against both rotation as well as against pulling forces from the sound post wall to create a tensioning stop, where for the bracing of the torsional only one assurance adjusting stop should be necessary whose vertebral tension at the same time Only radial bracing has a bracing that acts against pull-off forces target.

The technical problem posed was achieved in that the anti-rotation device the motor arrangement (GM in Fig. 1) by a between two tuning pegs (SWIB) braced connector (VSB) is made, the loose in which by the distance the tuning pegs given space can be inserted and its axis (ax) is aligned perpendicular to the axis of the tuning pegs (aß) that the connector a shaft (ST) fixed perpendicular to its longitudinal axis (ax), which between the tuning pegs parallel to their axis (aB) and that the shaft is a Torsional moment (SM), which is caused by the tension between the tuning pegs Connector is blocked and the surface of the connector to the Contact points with the outer surface of the tuning peg, preferably on the string wrap (WCK), a compressive force on both tuning pegs that inhibits the torsional moment of the shaft exercises, with the underside of the lateral surface of a tuning peg the top of the Connection piece (OV) as well as the top of the lateral surface of the other tuning peg the underside of the connector (UV) blocked.

The technical problem posed for every angular position of a tuning peg having to put on the socket wrench socket only once and when putting on and adjusting the anti-rotation device, the motor spindle for the longitudinal advance of the shaft (controlled by end contacts when the drive continues to run, see P 32 00 288.2) of a standard tuning key only a short distance (i.e. short run time for fast Adjust) was overcome solved a; By means of a joint (GL in Fig. 1, Fig. 12) between the holding of the longitudinal Drive (e.g.

Storage of the motor spindle) and anti-twist protection of the tuning key is arranged so that a pivoting of the tangential to the direction of rotation of the tuning key on its shaft arranged driver (WA in Fig. 1, Fig. 12, Fig. 15b) longitudinally its tangential, the pivoting movement of the tuning key shaft (SFTH) corresponding Steering radius or

Tuning key rotation angle (VTOT in Fig. 1 and Fig. 15b) allows is, whereby the swiveling of the tuning key shaft (SFTH) optionally by means of a driver feed the motor spindle (SP, WA) or by bending the joint (GL), b) through several locking positions of the joint, in which the bending of the joint can either be fixed or adjusted again from a fixed position, wherein these latching positions can be locked and unlocked, and c) by a method with the following process steps: I) Attaching the socket wrench socket (STCKS) on the tuning pegs to be adjusted as well as adjusting the anti-twist device (JBL, Fig. 1) by bending the joint with the joint locked position unlocked and Locking the anti-twist device on the tuning pegs, II) controlling the joint (GL) to the next joint locking position through the acting on the tuning key shaft Driver (WA) with unlocked joint locking position, with the tuning key shaft due to the torsional resistance of the in the socket wrench socket (STCKS) stuck tuning pegs kept in rest position and the tangential at the Voice key shaft attacking driver (WA) along his at the point of application of the Tuning key shaft (SFTH) acting, the pivoting movement of the tuning key shaft (with unlocked joint articulation) corresponding control radius (TOT, Fig. 1) is swiveled against the next C-joint locking position via the joint pivot point (by pivoting the spindle SP by PGL in Fig. 1 III) when the controlled Joint locking position lock the joint in this position, IV) control the motor Drive when the socket wrench socket is rotated by driver-controlled Pivoting the tuning key shaft in the direction of rotation that reduces the control deviation, V) on reaching the end stop (EAN in Fig. 13c or EAN in Fig. 12) of the longitudinal Participant drive, unlock the joint locking position and reverse control of the longitudinaliOn driver drive, with the tuning key shaft through the Resistance to twisting of the one inserted in the socket wrench socket (STCKS) The tuning peg is held in the rest position and the one engaging tangentially on the tuning key shaft Driver WA) along its acting at the point of application of the tuning key shaft (SFTH), the pivoting movement of the tuning key shaft (when the joint bend is unlocked) corresponding control radius (VTgT Fig. 1) over the joint pivot point of the next is swiveled in the opposite direction (by swiveling the spindle SP to PGL in Fig. 1), VI) when the controlled joint locking position is reached, lock of the joint in this position, VII) control of the motor drive in the event of rotation the socket wrench socket through the driver controlled pivoting of the tuning key shaft in the direction of rotation that reduces the control deviation and continuing process steps IV to VII until the system deviation the pitch of the string to be adjusted is zero.

Description of the figurative representations: Regarding Fig. 1: i Fig. 1 is an overall representation of the most important inventive components is given. On the bearing bracket GELA the socket wrench socket STCKS is arranged with a 3-way joint (taL), with both the BMB engine block mounting and the adjustment block mounting (Torsional shear) BVS, can be swiveled at any angle to the bearing bracket GELA can. The joint consists of three cylinders which can be rotated into one another, one of which the middle arn bearing bracket GELA and of the two outer one at B and one are attached to BVS. The cylinder walls of the joint have locking positions, of which the rotation angle of the BMB engine block mounting is electromagnetically switched on or off. can be freaked out; the BVS rotation angle can be locked mechanically. Through this arrangement according to the invention with the control method according to the invention described an optimal contact area for the socket wrench socket with as short a length as possible Length of the longitudinal spindle drive SP achieved. Every time the feed of the Driver WA, because of the low spindle height, for the required angle adjustment the socket wrench socket STCKS is not sufficient (driver WA on the upper or the lower stop of the spindle SP), the electromagnetic disengagement takes place of the joint cylinder GLMB attached to the engine mount with the following, opposite to the actual direction of rotation, reverse control of the driver WA in the not blocked direction. As the socket wrench socket has a much greater resistance to twisting at the inserted tuning peg, as the (electromagnetically disengaged) bearing point of the angle of rotation between BMB Unä GELA, the driver WA will return the gearbox GM to its longitudinal Drag the control area until the next latching point of the joint sets the angle of rotation blocked between BMB and GELA. The angle of rotation between BMB and GELA between two successive locking points of the articulated cylinder must be smaller than that through longitudinal spindle control of driver WA resulting angle of rotation (ocva Ccve in Fig. 15b) with each reverse control (with disengaged joint) of the driver the next locking point of the joint can be reached with certainty.

In addition to the controllable angle of rotation between BMB and GELA (with electromagnetic Engagement / disengagement) is a rotation angle change between the adjustment block fastening BVS and GELA for the purpose of expanding the adjustment range of the adjustment block JB, which is attached to the BVS. For engaging or disengaging a mechanically operated lock is sufficient for this angle of rotation.

Instead of a 3-way swivel joint, you can also use two standard swivel joints can be used. An example of this is shown in FIG an electromagnetic Ein / Ausrastmöglivhkeit for the fixation of the between BMB and GELA adjustable rotation angle. For changing the angle of rotation between BVS and GELA, another joint of the same type can be used, the release locking takes place by pressing a button.

After placing the socket wrench socket on the ah to be matched Tuning pegs must be guaranteed de3 their motorized rotation in each given Angular position of the tuning peg square can be done in both directions of rotation. For example, the socket wrench socket would be at an angle that is in the limit area their motoric rotation possibility is placed on the tuning pegs, then under certain circumstances this can no longer be compensated because the Socket wrench receptacle beyond its motorized rotation option would have to be controlled. In order to be able to do so when the socket wrench socket is put on to ensure a predetermined minimum adjustment angle of a tuning peg the inventive measure taken, the angle of rotation of the touchdown area (N VTOT -2 XTE in Fig. 1) by the angle of rotation of the specified minimum adjustment angle (b§TE) smaller, which means that the touchdown area around goSTE differs from the actual adjustment area reduced. This contact area must be at least equal to the angular division of the corner wrench socket (for standard socket wrench socket 45 °).

By reducing the angle (i.e. increasing the number of milled Square) of the division of the piece wrench socket (standard = two square edges offset by 450), the play of the touchdown area can be further expanded will. The contact area is preferably reduced by 2αTE by contact control as described in the explanation of FIG.

So the automatically controlled tuning key for all types of piano Can be used universally, it should have the following properties: a) the entire The arrangement of older pianos may be horizontal under the tuning pegs leave fende delimitation plane g BL (Fig. 1) do not protrude, b) The entire arrangement may be replaced by the existing grand pianos and newer pianos The bridges of the tuning material are not hindered, i.e. those formed by the bridges Do not project beyond the boundary plane g PG, c) the entire arrangement must be symmetrical be usable, whereby the work and touchdown areas shown in Fig. 1 I (with E PG as limitation) and II (with SPG SYM. As limitation). Both touch areas is as a horizontal delimitation plane - (based on a vertical sound post) g BL together, d) as quick as possible tensioning of the anti-twist protection of the motorized Arrangement (adjustment block JBL, Fig. 1), changing the angle as quickly as possible between the GELA bearing bracket and the BMB engine block mounting as well as the shortest possible spindle stroke for after-running, the shaft sleeve SFTH is required.

This requirement is met by the ore in deric measures described achieved. The motor control for the after-running of the shaft sleeve SFTH during the Adjustment (placing of STCKS and tensioning of BVS) takes place with limit switches, which are operated by SFTH and are arranged on the engine block, see also P 32 00 288.2 or G 82 00 230.4.

Putting on STCKS and bracing BVS is preferably done in the following sequence: Attachment of STCKS in the available attachment area (I or II, Fig. 1), swivel the BVS into the required adjustment position with the disengaged Joint (BMB / GELA) and simultaneous after-running of the motor spindle, triggered by End contacts via shaft sleeve SFTH (ct shaft sleeve / BVS is used in addition to the spindle swivel by joint still changed by longitudinal spindle feed), Adjustment of ST between tuning pegs SWIB via adjustment block JBL and bracing from JBL on the tuning pegs.

The actual bracing of the adjustment block is made by a connecting piece VSB made, which is preferably designed as a steel pin with rubber coating and through the shaft ST into the space between two tuning pegs, preferably two adjacent ones Tuning pegs (SWIB), pushed in and by turning the shaft (clamping torque SM) preferably on the string wraps of the tuning pegs (rubber pad presses on the string wrap WCK), with which the sound post is clamped. Directly by issuing VSB direct on the string coils their shear torque is kept so low that the tension from JBL has no influence on strings that have already been tuned.

Since the adjustment of ST (shaft of the connecting piece VSB) within of the JBL adjustment block, it could happen that a If there is a bridge (e.g. in the case of a grand piano), the adjustment is hindered by the housing from JBL (on the side) butts against the wall of the bridge. To avoid this, the adjustment block is attached BVS, as shown in detail A, Fig. 1, adjustable by adjusting the slot (XL) and can be fixed with a locking screw. In the one shown in FIG In the exemplary embodiment, the locking screw is integrated into the adjusting block (LVS carried out up to the BVS bracket that can be moved in the direction of XL).

All reference designations not referred to are explained in the following descriptions of the figurative representations.

Regarding Fig. 2: In Fig. 2 there is an exemplary embodiment for the storage and bracing of the connecting piece (VSB, Fig. 1) for the transmission of a torsional moment attached shaft (ST) shown. The shaft is preferably braced by a cam (HU, Fig. 2), which is fixed to the shaft or via a radial driver is arranged.

The torsional moment is generated by the action of force (F in Fig. 2) on the lateral surfaces of the cam, caused by clamping two rails arranged one above the other and forming a cavity (H, see Fig. 6), in which the cam can be displaced with its end face parallel to the soundpost wall on their outer surfaces on the rail inner walls (El. E2, Fig. 2) slides, whereby an adjustable distance (E x in Fig. 1) of the shaft of the connector to the axis the motor-driven rotatable socket wrench socket is made.

On the shaft ST is a clutch cylinder KK with an inclined conical bore (Brass bush with rough surface = dome surface K) pressed in.

The cam itself (hay) is sliding around on the shaft (rod-ST) this rotatable, but has a cone-shaped extension (KW) that goes into the conical bore (K) of the clutch cylinder is fitted. By axial displacement of the cam (HU) Optional coupling and decoupling of the cam and shaft (through Pressing or sliding of the conical coupling surfaces K) can be made. This axial displacement is generated by the handle G, which is at the free end of the The shaft ST is screwed on and its end face DA receiving the shaft end with the face of the cam adjoining this surface (flange from HU = FL) a friction surface forms whose frictional resistance (rB) through Tighten and relax the face of the handle (DA) against the one flanged to the cam HU Front face (FL) optionally reinforced (screwing in the shaft) or weakened (screwing out the shaft), whereby a tensioning of the handle face against the front face of the flange FL of the sleeve HU the pressing of the coupling surfaces K, and relaxation the grip face (DA) the sliding of the coupling surfaces K of the coupling cylinder causes.

When inserting the connector into the space between two tuning pegs the grip face DA is relaxed, a.h. the connector can be with the shaft ST can be rotated to any position within o max without the shaft is blocked by the guide rails of the cam (Ela, E2a, see Fig. 6). at When the handle is turned in the clamping direction, the coupling surface K also turns the cam HU. However, before the dome surface K begins to act, the Thread friction between shaft ST and handle G (see also RF in Fig. 4) the connecting piece rotated so far that the underside of the lateral surface of a tuning peg is the top of the connecting piece (OV in Fig. 1) and the top of the lateral surface of the other Tuning peg blocks the underside of the connector (UV). Only then does it begin the coupling surface K of the coupling cylinder to act by tightening shaft ST, it is automatically ensured that when the cam is rotated, the connecting piece is already blocked by the tuning pegs (tensioned position, see also explanation to Fig. 6).

All reference designations not referred to are explained in the following descriptions of the figurative representations.

To Fig. 3: In Fig. 3 is an embodiment for the storage the cam according to the invention (HU with ST in Fig. 2). The cam is here not firmly connected to their Ruppelwelle (cf. KW in Fig. 2), but on a camshaft (NW) as a radial driver axially slidably guided, the Camshaft on the connecting piece (VSB, see Fig. 1) to generate a Torsion torque attached shaft (ST), is arranged rotatable against this and the coupling surface (K) of the coupling cylinder (see HK in Fig. 2).

Rail surfaces are at the level of the end faces of the cam sleeve (NH) provided that prevent axial displacement of the cam sleeve. These rail surfaces (V in Fig.

3) can be part of the profile of the rails that make up the sliding guide form the cam (E1, E22 and Ela, E2a in Fig. 6) or side surfaces of the rail bell housing (see also Fig. 9).

The shaft ST becomes when inserting and removing the connecting piece axially shifted in / out of the space between two tuning pegs, then the shift prevented from NH by the rail surfaces (V); this is a narrower design of the rails for the sliding of the cam allows, resulting in a considerable Reducing the weight of the arrangement helps, as these rails provide a significant To withstand the bending moment.

Lj is the adjustment length that is required for inserting and removing the connector in / out of the (the) space between two tuning pegs is required (cf. Lj-LVYL in Fig. 2).

The caused by pressing the slide or guide rails El, EL Bracing of the cam or the angle of rotation of the shaft ST in which this bracing is still possible, is limited by the diameter of the camshaft, as on the one hand the rail area V cannot go beyond the limit of NW, on the other hand ST may no longer be rotated than the rail surface V is still present, so that NH is not shifted axially (slides out of the rail fiche). a max + oCr represents the theoretically max.

Twist angle of ST; Obx is the angle by which the possibility of rotation is the cam is reduced because of the conditions described, the one for the rail play hvo remaining angle of rotation bSvO must still be taken into account. hvo and hx are the projected perpendiculars associated with OAvo and ° 5x.

Fig. 4 shows one way of reducing the tension range COv (see Fig. 3) to expand. For this purpose, the maximum outside diameter of the camshaft is (Di-max of NW) less than or at most equal to the minimum effective (= be screwed-in cam effective) outer diameter of the cam sleeve (Da- min from NH in Fig. 4), reduced by the height (-hx = s) of the effective area (including sliding play) for the rails (V) arranged on the end faces of the cam sleeve (NH). By this measure, the adjustment angle Ot max of the shaft ST is significantly increased, which can be easily seen by comparing FIGS. 3 and 4.

In Fig. 4, another measure is also shown, the Properties of the anti-rotation device according to the invention improved. Like in the Description of Fig. 2 has already been explained, causes the thread friction between shaft ST and handle G the automatic assurance that when rotated Cam the connector already blocked by the tuning pegs is, whereby it is ensured that for the tensioning of the cam is still sufficient Spring travel that acts directly on the connector is available. This travel is generated by a clamping device that clamps the inner surfaces of the rails together allows the sliding guide for the cam, whereby by clamping the rail inner surfaces the torsional moment of the shaft (ST) of the connecting piece (VSB) via the cam rotation (N max) is generated (see also explanation of FIG. 6).

Fig. 5 shows an embodiment for the sliding guide in Fig. 2 to 4 explained anti-rotation device (compare square VK in Fig. 2) within one of the axis (a) of the motorized rotatable piece wrench socket (STCKS) measured adjustable distance (aA = A X in Fig. 1). To that end is a rail wheel (RH) is provided, which is located in the cavity (HO) of two stacked, parallel to the soundpost wall or parallel to the front surface of the cavity for the Cam (HU in Fig. 2 or NH in Fig. 4) forming rails (H in Fig. 6) or parallel rails (SC) aligned with the front surface of the rail housing (SG in Fig. 5) slides in the profile (sliding guide in Fig. 5), the shaft in the rail wheel is guided displaceably in the axial direction. To avoid tilting the cam, the rail wheel is preferably within reach (G) of the free end of the shaft (ST) arranged and is coupled to the cam via radial drivers (camshaft NW), whereby A twisting of the cam is possible via knurling of the rail wheel, depending on Tension of the handle G (in Fig. 4) rotates when the rail wheel is rotated the shaft (ST) attached to the connecting piece with (G clamped) or not with (G loose, i.e.

relaxed). Preferably handle G and rail wheel are RH so to arrange that both can be operated with one hand at the same time, e.g. can handle G are encircled with a fist and RH with thumb and forefinger moved or rotated.

Fig. 6 shows an embodiment of a clamping device that allows the inner surfaces of the rails (E1, E2 in Fig. 2 to Fig. 4) to be clamped together, whereby the clamping of the inner rail surfaces (Ei, E2 in Fig.

6) the torsional moment of the shaft (ST) of the connecting piece (VSB in Fig. 1) on the rotation (maximum torsional margin in Fig. 4) of the cam (NHa in Fig. 1 and Fig. 6).

As has already been explained in Fig. 5, a handle (G in Fig. 4) angular position already set once by the rail wheel RH within of the torsional clearance dmax (Fig. 4) of the cam can be adjusted. Fixate and The cam is tensioned with the tensioning device provided, with tensioning and Relaxation of the handle G as long as it is not necessary, as long as the torsion clearance of the connector is sufficient. Is cOmax the cam NHa for the required Rotation of the connecting piece (VSB) too small, then by releasing the Handle G a decoupling of the cam and ST of the connecting piece can be made, whereby the rotation clearance Omax of the connecting piece of the new position of the Connector can be adapted.

This is in a range of rotation of X - 3600 for the connector VSB possible.

In order to avoid that, as already mentioned in the explanation of FIG has been, the cam (EW) or, Nockenwe7.3e and cam sleeve (MM and NW in Fig. 4) when turning the handle G in Spc nrichtung by bearing friction on the Connector arranged shaft ST rotates, a further cam is preferably provided, which is statically connected axially to the first cam (MMa) and at an angle to it (ß in Fig. 6) is offset that the second cam (NHb), o like the first cam (NHa), also provided in one of collapsible rails (SE1a, Se2a for NHa) second pair of rails 5E1b 'SE2b for NHb) is available that the angle between first cam and second cam (ß) is chosen so that when clamping the for the second cam (NHb) provided pair of rails (sEllb 'SE2b) the camshaft is rotated in the opposite direction, as when tightening the for the first cam (NHa) provided pair of rails (SE1a, SE2a) and that the clamping of the pair of rails for the first cam is made alternately for clamping together of the pair of rails for the second cam and vice versa (NHa in clamping position and NHb relieved or NHb in the clamped adjustment position and MMa relieved, see see Fig. 6).

To ensure that the friction between handle G (Fig. 4) and Shaft (ST) screwed into the handle when the cam MMa is blocked by the cam MMb is large enough for the shaft ST to rotate in the direction of rotation of the handle the frictional force of the thread between the handle thread bushing (GH in Fig. 4) and the shaft ST by a slip clutch acting between shaft ST and handle G (RB / RM in Fig. 4) reinforced. This slip clutch is preferably designed so that one on the Shaft (ST) centric to its axis arranged cylinder surface (RM) together with the cylindrical surface of a hole provided in the handle (G) centric to its axis Via a between the cylindrical surface of the shaft (KM) and the cylindrical surface of the handle: Üi'-bore pressed-in elastic material (e.g. foam RB) the friction surface (RF) the slip clutch bll- the. In addition, it must be taken into account in the arrangement: that the direction of rotation of the thread (GH in Fig. 4) of the at the free end of the shaft (ST, which transmits the torsional moment of the connecting piece) screwed-on handle (G) when tightening the connecting piece between the cam or camshaft and shaft (ST) arranged coupling surfaces (K of HU and KK in Fig. 2) the same direction of rotation has, like the cam (NHa in the clamping position in Fig. 6), which the torsional moment for the connector inserted between two tuning pegs.

As shown in Fig. 6 (see also Fig. 8), the clamping device, which enables the inner surfaces of the rails (E1a, E2a or Eib, E2b) to be clamped together, produced in that the pair of rails (SE1a, SE2a or

SE1b, SE2b) have an articulated hinge (S in FIG. 6) at their one end and a collet (KS with K1a, K2a or Kib, K2b) at their other end. This collet is preferably made in that the collet through inclined surface (s) (wedge surfaces K1a, K2a or Kib, K2b) arranged on the top surfaces of the rails and on the Inclined surface (s) pushing slide (KS) is designed as a stop that can be rotated radially against the incline of the inclined surface in its plane (KS rotatable in axis DP in Fig. 7) 7) is adapted to the rotational path of the contact surface (GUA) of the stop (KSVK) so that there is a self-locking tension of the contact surface and inclined surface (FKn) of the rail for every angle of rotation of the stop contact surface (GUA). This adaptation of the inclined surface to the radial path of rotation of the contact surface can be done, for example, by purely static shaping of the inclined surface, as shown in FIG.

Compensating for the swiveling of the rails around their articulated hinges S (Fig. 6) takes place here by elastic support of the contact surface (rubber support GUA in Fig.

7). An automatic adjustment of the inclined surface to the radial rotation path the contact surface is preferably achieved by the arrangement shown in FIG (see explanation of Fig. 8). The slide for the collet preferably has that Feature that its axis (aDP) between the pair of rails for the first cam (MMa) and pair of rails for the second cam (NHb) perpendicular (or approximately perpendicular) to the contact surfaces of the inner rail walls (ein, E2a or yellow, E2b in Fig. 6) is arranged that the pair of rails for the first cam and that for the second Cams are preferably arranged parallel to each other and at the same height and that the inclined surfaces arranged on the top surfaces of the rails are mirror images of one another, from the inside to the outside increasing slope (% ST in Fig. 8), the radial rotatable stop has three positions: - one in which its contact surface (GUA in Fig. 8) presses the pair of rails for the first cam (NHa, Fig. 6) together and the pair of rails for the second cam (NHb) is relaxed because the contact surface is rotated away from its inclined surface, - one in which its contact surface is the pair of rails for the second cam (NHb) and the pair of rails for the first cam (NHa) is relaxed because the contact surface is turned away from its inclined surface, - and one in which its contact surface in the middle position parallel to the pairs of rails is aligned at the lowest point of the inclined surfaces, creating both pairs of rails are relaxed in this position of the contact surface (middle position of the slide KS see Fig. 6, clamping position of SE1b, SE2b see Fig. 8, where SE,; a, SE2a relaxed).

As has already been explained in FIG. 1, the arrangement should both can be used in the I. and II. quadrants of the adjustment range. For this purpose, the anti-twist device should also be used turned by 1800 can, in which case the entire arrangement shown in FIG. 1 is rotated by 1800 is and a measure is provided with which the motor spindle SP of the spindle feed WA is always directed upwards, even if the arrangement is used in mirror image is. This measure is shown below in Fig.g using an exemplary embodiment explained (see also Fig. 11 and its explanation).

In order to be able to use the anti-twist device twisted by 1800, the measure has been taken that the axis (aDP in Fig. 6 and Fig. 8) of the on an inclined surface (K1a, K2a, Kalb, K2b) against the slope of the inclined surface in their plane radially rotatable stop (KS in Fig. 6 and KSVK in Fig. 8) Top surface and bottom surface of the pairs of rails (SE1a SE2a; SE1b 'C SE2b) led out is that the free end of the radially rotatable stop is designed as a handle end (gene) and that between the handle and the radially rotatable stop a KuDpelstück (KS-BU) is provided, this coupling piece between handle and stop (thread KS-BU in Fig. 6) or between the stop and the axis of rotation of the stop (thread KS-BU in Fig. 8) is preferably provided.

Fig. 7 shows an embodiment in which the adaptation of the radial Incline of the inclined surface (FKn) on the rotational path of the contact surface (GUA) through pure static shaping of the inclined surface is made. While axis aGKN rotates, every point on radius R must have the same height difference H or h, minus the difference created by rotating the rails around their hinge joint arises, exhibit. The exact adjustment is made by means of a GUA rubber pad.

Fig. 8 shows an embodiment for the preferred design the arrangement in which the adaptation of the radial rise of the inclined surface FKn on the rotational path of the contact surface (GUA) in every angular position of the rail bers KS takes place automatically. This preferred design of the arrangement was made by that the inclined surface (K1a, K1b in Fig. 8) rotatably mounted about its longitudinal axis (a) is, the stop which can be rotated radially against the inclined surface when it is rotated the pivot axis (longitudinal axis a, Fig. 8) intersects the inclined surface and through the Contact pressure of the stop the inclined surface is pivoted into one position, in which they the maximum self-locking tension of the contact surface (GUA) and inclined surface (K1a, Klb in Fig. 8). In order to increase the tensioning effect, the contact surface is an elastic, also s an axis of rotation (aSL) pivotable surface.

Regarding Fig. 9 In Fig. 9 is the anti-rotation device mounted on the bracket BVS in Fig. 1 (also referred to as JBL adjustment block) again shown in detail. The one with it The reference designations selected correspond to those selected in FIGS. 1 to 8. Because the rails are braced with KS around the pivot point at their end S are swiveled, of course that between the rail inner walls (E1, E2) Remove adjustment play (JS) in direction of rotation axis a from STCKS. By the in Fig. 2 to Fig. 8 explained inventive measures is ensured that when turning of the handle G from the relaxed position to its cocked position, the connecting piece VSB always rests on the SWIB tuning pegs before through the dome surface K the cam is clamped in its clamping position with the shaft ST in a torsion-proof manner is. In addition, it should be pointed out that it is expedient to use the one shown in FIG Corrugated dome surface to provide a more resistant anti-twist protection between shaft ST and cam. The fact that the connector when turning the handle automatically into the correct angular position (when the cam is stationary, locked by NHb), the tension margin is independent of the angular position of the connector.

As shown in Fig. 9, the pair of rails for bracing the cam, which provides the torsional moment for the torsional tension of the connecting piece (SM from VSB in Fig. 1), an angled clamping surface on (preferably T-shaped clamping surface), consisting of a parallel to the soundpost wall Longitudinal piece (preferably across the T-shaped clamping surface), which is the actual a hinge (S) at one end and a collet at the other end (KS) having, clampable rail and consists of a right-angled, flat piece aligned with the sound post (preferably the center piece of the T-shaped Clamping surface), with the cam (NHa) generating the torsional moment as close as possible the free end of the clamping surface aligned against the soundpost wall in that of the gap formed on the opposite surface slides. In front of this pair of rails is at the same height the pair of rails for the cam NHb, the one with the pair of rails for the cam NHa to be braced alternately via GK, respectively.

Tensioning and relaxing is done with the following steps: a) Relaxation of G by turning it into the tightening torque SM (of the connecting piece) opposite direction of rotation. GK can assume the positions sp, m or j.

b) Adjustment of or A A by shifting axis aST with RH, where GK in position j.

c) Insertion of VSB in the space between the tuning pegs SWIB and tensioning from G by turning in the direction corresponding to the clamping torque SM. Afterward GK in position sp.

The steps described under a, b, c know how to do it quickly that for a standard piano this work only takes (1 - 1.5 sec.) 240 strings = 4 to 6 minutes must be used.

On the one hand, through the bars of a stick, the adjustment process of A x not to hinder (see Fig. 1), on the other hand, the cam (NHa), which the Torsional moment for the torsional tension of the connecting piece (VSB) is generated, Bring as close as possible to the soundpost wall in order to reduce the bending moment of the shaft ST The measure was to keep the connection piece and cam as small as possible seized that the longitudinal pieces (SE1 2aL) of the clamping surfaces (E1a, E2a) of the rail pair, that is the torsional moment for the torsional stress (SM) of the connecting piece generated, not over the boundary line given by the free ends of the web walls (Web wall boundary line SL in Fig. 1) protrudes that the set at right angles, Pieces that are aligned with the soundpost wall and form the cam guide (SE1 2art) the clamping surfaces of the same pair of rails (SE1a, SE2å) as close as possible to the The end faces of the tuning pegs protrude, with the Cam (s free The end of these clamping surfaces is performed. The cam must be close to the outer one Edge of the pair of rails can be adjusted that also directly on a web edge the VSB connector is still adjustable.

The arrangement shown in Fig. 9 has in addition to the adjusting screw already explained in Fig. 1 LVS (length Adjustment from AA, see explanation in 55, another adjusting screw EVS for setting the immersion depth of SE1aRW and SE2aRW> especially from U to, because on the one hand the length EL of ST should be as short as possible, on the other hand different pianos can have different bridge lengths STEGL.

In order to find the right one for different distances between adjacent tuning pegs To be able to change the lengths of the connecting pieces (VSB) quickly (in general Rest steps of 1-3 octaves, i.e. 6-2 changes, sufficient), is at the free, between the tuning pegs inserted, shaft end a hole perpendicular to the shaft axis made, in which the connecting piece is interchangeably pinned, preferably by a clamping nut tightened against the side surface of the connector (AV with knurling). In order to get through the play between the hole and the connecting piece Change of direction of rotation of the shaft ST to avoid loosening of the clamping nut, it is advisable to place the side surface between the clamping nut and the side surface pressed by the clamping nut attach a spring washer (FS) to the connecting piece and tighten the clamping nut to secure a counter nut (also with knurling) (AVK).

In Fig. 9 there is also a suggestion for the preferred embodiment the coupling between the shaft of the connecting piece (shaft ST) and the torsional moment generating cam (NHa), which has the purpose of determining the length EL (at the end of the Connecting piece) of the shaft ST as short as possible to keep. For this purpose, the Kunpelfläche is arranged between the first cam and the second cam and preferably centrally to its axis, one statically connected to the cams (Cylindrical) housing is provided in which the shaft of the connecting piece is axially and is mounted radially displaceable (see detail Gt in Fig. 9) and the shaft of the Connector provided in the cavity of the housing with a pressure surface that together with the inner surface of the on the handle side of the housing Housing front wall forms the coupling surface (K).

104, 11, 12 show exemplary embodiments for the design of the arranged between the holder of the longitudinal drive and the anti-twist device Joint (see explanation of Fig. 1).

In the joint shown in FIG. 10 there is a three-point mounting of the locking pin (= extension of the push rod SST). To this end, assigns the inner sleeve HMV corresponding bores, matching the grid bores of the inner cylinder GLMB on. In Fig. 11 an embodiment is shown in which the motor drive (GSN = worm gear with motor M) used as a mirror image of the symmetry axis SYM The spindle SP with its spindle guide SPV is optional for this purpose Can be attached to each base plate side of the worm gear (bracket MB) (SBZ can be inserted in SBX and lockable with GFL in NUT (NT) from SBH (spindle drive attachment area I and touchdown area II see Fig. 1).

In order to ensure a firm hold of the PLC in the SBH, between the insertion holes of SBH and the support surfaces of SPV (= SBS) rubber washers intended.

The SBZ is unlocked by pressing the GFL together whose axis aL against the spring force of FZ.

Fig. 12 shows a preferred arrangement of the geared motor combination GSM and M, with the longitudinal axis of the motor (aGSM) parallel to the longitudinal axis of the socket wrench shaft (aSFTH) is aligned. This has considerable advantages for the use of space. That Joint GL consists of two joint cylinders that pass through one between the cylinders axially pressed-in ball bearings are rotatably supported against each other. The inner one The cylinder has a grid of holes on its outer surface, each with the same grid spacing in the radial direction. The outer cylinder, however, only has one matching hole to the hole pattern of the inner cylinder. A locking pin can be inserted into this hole intervene (eVS), which occurs when the inner and outer cylinders rotate at the same angle of the joint engage in both holes and thus the rotation of the two cylinders can block against each other or again when the locking pin is pushed out can share. The sliding movement of the locking pin is preferably electromagnetic controlled.

Reference designations that are not referred to are in the following Description of the figurative representations explained.

13a and 13b, FIGS. 13a and 13b show an exemplary embodiment for the proposal according to the invention, the angle of rotation of the touchdown area (dTOT- 2 O'TE in Fig. 1) by the angle of rotation of a specified minimum adjustment angle (2xTE) keep smaller. As shown in Fig. 13a, are for this purpose on the joint GL (see also Fig. 12) Contacts k TE (t TE1 ...

hTEl +), which are arranged so that when rotating 3MB (around the joint axis) for each direction of rotation (L, R) at least one contact (iTE2 for R or ßTE1 for L in touchdown area I and kTE4 for R or bTE3 for L in touchdown area II) activated before the penultimate joint stop point is exceeded is. k TE1 to k TE4 are decoding contacts that are used for each direction of rotation and in each touchdown area is assigned a rotation angle beyond which at least one locking step of the joint is possible. When activating kTE1 to kTE4, the joint is locked automatically by pressing the locking pin (eVS, see Fig. 12 immediately before reaching the penultimate resting point on the Inner cylinder is pressed (caused by electromagnetic release) as long as until it engages when this locking point is reached. It then remains locked in place until it is unlocked again either by pressing a button or by a control signal. The actual contact activation takes place by closing a contact on BVS (see Fig. 12) arranged contact spring (A-TE according to the scheme corresponding to Fig. 13) and one the contact spring pressing, arranged on GLMB stop (kAN in Fig. 12), whereby the potential pending at the GLMB over km is switched through to the corresponding ATE contact (expediently, in Fig. 12 the locking pin is in the contact stop stored). 13b shows a simple suggested circuit for the control of the locking pin (eVS). With the TA button, by pressing the (o OV) button L2 are energized, provided that kTE1 to kTE4 are open (= touchdown area the arrangement). If 1 of 4 TE1 to hTE4 is closed (= OV via R to km), then the OR function causes the excitation of L1, regardless of the key status TA. With the TR key or a control signal, km can be set back to VCC, which means L1, L2 are again directly dependent on the identification status of the TA key. The key TR and button TA are to be arranged in such a way that a simultaneous pressing of button TA and button TR is possible.

In addition to tTE1 to TOTE4, in the last joint locking positions further contacts can be arranged in both contact areas, which means that that in this position the joint can only be opened by simultaneously pressing The TR and TA buttons can be turned back to alert the operator to make sure that the joint is in the stop position. As shown in FIG it is useful for the electrical magnetic control of the locking pin eVS to use a bipolar switching element. In the proposal according to FIG. 13 there is this switching element consists of a solenoid with two connected in series Field coils in which the switching rod eVS (see. Fig. 12) than in the transition zone the coils located in its central position core is guided, as well as permanent magnetic Holding disks (MAG), which are attached to both sides of the end faces of the solenoid, in one Distance which allows the required switching path of the shift rod, are arranged and off for each switch position of the switch rod touching the adhesive disks and these attracting magnetizable surfaces (MF) on the switching rod are arranged. KOl and K02 are contacts that form the circuit of the coils L1 and Interrupt L2 in series after the shift rod is held by the adhesive washers will. With this design you can switch the switching rod eVS with pulses, whereby the coils L1 and L2 can be made very small. The contacts KOl and K02 are in each case connected to the circuit of that coil that is actuating it cause. When designing the switching cycle of KOl and K02, it must be ensured that that in the middle position of the core (eVS in the position shown in FIG. 13) both Contacts are still closed. The contacts should only be made shortly before blocking the switching rod eVS (by MF / MAG surfaces) must be switched off. To this condition will meet suggested instead of normally closed contacts for the power cut-off of the coils, working contacts to use, these working contacts are designed so that each contact surface of a pair of contact surfaces through an ordered contact plane between the magnetically adhering surfaces ar, and his other contact surface through one of the magnetically adhering surfaces (preferably through the one arranged on the shift rod (MF), the one with the shift rod a conductive one Has connection) is formed. Fig. 14a shows an embodiment for a such arrangement.

13c shows an exemplary embodiment for a preferred configuration of the sleeve driver. Pushing up (MNO) and pushing down (MNU) drivers are angled so that when the upper spindle stop is reached the shaft sleeve SFTH does not protrude beyond the upper limit of the spindle bearing LGR. As shown in Fig.

11 and 12 as can be seen, a worm gear motor is preferably used (GSN) is used, but its axial load on the axis is limited. That's why is in all structural proposals for the embodiment of the invention the axial thrust bearing LGR arranged at the upper end of the spindle SP is provided, whereby the coupling between the spindle and the gear shaft (GW in Fig.

15a) is carried out by a radial driver that does not have any axial load (GW / asp see Fig. 15a, Fig. 11, 12 and Fig. 14b). As for the follow-up control contacts required when fitting the socket wrench socket directly shaft sleeve (SFTH) and driver arms are used for this purpose are isolated from each other.

14a see explanation of FIGS. 13a and 13b.

Fix7. 14b shows an embodiment of a dome arrangement for electronically controlled coupling / decoupling of the coupling between the spindle drive shaft SP and engine or Gear shaft of worm gear MW, with the disengaged State of the spindle drive shaft independently of the drive of the gear shaft MW by means of Auxiliary smo tor is set to a much higher idle speed to control the follow-up control of the spindle driver when putting on the socket wrench socket can be done more quickly (see also P 32 00 288.2 and G 82 00 230.4 and explanation of FIG. 1 and control contact connections in FIG. 13c).

Motor M3 generates the idling speed of SP with the gear shaft disengaged MW. The speed difference between M3 and M2 controls the coupling and decoupling process between SP and MW in the following way: Engaging: When engaging the HKT lower from the spindle SP; the differential speed acting between SP and HKT must therefore have a direction of rotation that corresponds to the pitch of the thread.

Disengaging: When disengaging, the HKT sleeve must come off the spindle Raise SP; the differential speed acting between SP and HKT must therefore be one of the Have the thread pitch corresponding direction of rotation.

The coupling itself is formed by a screw slot (EKTM), into which a screwdriver (SETS) engages. EKTS is used here by spring force FKT inEKTM pressed in. This spring force is acted on by the stop for the uncoupling process limited. KT is a square guide, gTR the coupling interface. The shutdown of the motors takes place by limiting the motor current.

In FIGS. 15a and 15b, a preferred embodiment of the motor-gearbox block fastening is shown suggested by which an optimal expansion of the tuning key rotation angle with the shortest spindle stroke v is given. The engine block attachment is for this purpose not as shown in Fig. 11 symmetrically to the top and bottom of the arrangement (see symmetry axis SYM in Fig.

11), but asymmetrically (see center line mi of the motor-gearbox block in Fig. 15a) made by a, a U-shape having bracket (UFB), on its open side (of the U-shape) shaft sleeve and driver arms through the spindle drive can be swiveled in and out.

As already explained in FIG. 1, the arrangement should also be a mirror image (upside down) can be used. For this purpose there are two dovetail guides intended. One on the joint bracket suspension (SW2 on BVS) and one on the transmission suspension (ski), i.e. on the two side parts of the U-shaped bracket.

The direction of insertion of the dovetail mount located on the BVS (SW2) takes place in the longitudinal direction of the BVS from the outside to the inside to the axis (a) of the socket wrench socket (STCKS). The V-shaped bracket pushed into the dovetail receiver arranged part can, however, be turned upside down symmetrically from both sides (for dovetail guide is mi = SYM) must be inserted into BVS.

In SWI the gear housing must be in the axial direction of the spindle drive SP can be inserted into the dovetail mount to the end of the coupling the spindle. Spindle (SP) and spindle guide bracket (sps) are over the thrust bearing LGR (cf. Fig. 11 and Fig. 1k) through the U-piece over the two dovetails guided tours connected.

If the working range of the tuning key is to be changed, then the handle on the shaft sleeve is first of all (GSFTH in Fig. 15b) unscrew from the shaft sleeve, whereupon after unlocking a fuse the V-shaped bracket piece complete with gear motor, thrust bearing and spindle guide bracket Pulled off the dovetail guide of the hinge bracket suspension (SW2) and upside down can be plugged in again. Before plugging in, however, the gearbox is on his Also insert the suspension upside down, so that the same arrangement is reversed (see touchdown area I and touchdown area II) is available.

FIG. 15b gives an overview of the in the arrangement according to FIG. 15a effective lifting and pivot points.

They mean: ... max spindle stroke of the driver arms MNU MNO O6va ... the control (twisting) angle caused by the spindle stroke: GLVS .. anotherX by hand) joint GSFTH .. a handle that is attached to the driver shaft of the tuning key is screwed on, whereby for the exchange or the upside down assembly of bracket GSFTH 16 shows a preferred circuit proposal for the control loop.

Is only a simple device for the target / actual value comparison, without a spectrum filter used (principle of the illustrated blocks of a standard device according to Fig. 16), then the display result is at the output of the integrated setpoint / actual value comparator be subject to the following sources of interference: a) Possibly not good The muted strings of a choir can be temporary due to beating phenomena Cause a decrease or increase in the output voltage at comparator output A, b) the noise from the motor and gearbox of the drive can also have a disruptive effect.

For this reason, the inventive measure is taken that the the actual value / target value deviation output by the actual value / target value comparison circuit indicating, comparison signal (at output A in Fig. 16) of a differentiating circuit (Diff.) With downstream minimum detector (min.) For the evaluation of the respective minimal signal rise or fall is introduced (Diff.), as well as an instantaneous value memory (Momentsp., Fig. 16), the output of which counteracts the control deviation, is supplied, the value of the stored in the instantaneous value memory comparison signal delivered by the actual value / setpoint value comparison circuit during the duration of a minimum signal rise or fall is renewed. It is also suggested that the motorized rotation of the socket wrench socket to be carried out in a time-division multiplex process, with actual target value evaluation and motor-driven Alternating rotation of the socket wrench socket and the Motor control time is preferably regulated as a function of the measurement result (s. VCO input of the time division multiplex oscillator in Fig. 16).

17 shows a proposal for a light marker generator for identification the strings of a choir to be blocked in each case if the accessibility of the Strings The inventive feature relates to the fact that the light source has one has an adapter (e.g. socket) to be attached to a tuning peg, whereby at plugged-in adapter, the light line along the piano strings is aligned and can be adjusted parallel to the marking string by means of a swivel joint and that the incidence of light from a diaphragm of the Licktcuelle that generates the light line as close as possible to the strings (Long LAL).

Blank page

Claims (41)

Claims 1. Tuning key, its to be matched in each case Socket wrench receptacle that takes up the tuning pegs can be rotated by motor around its axis is, the motor rotation by a control loop to which the audio frequency the string belonging to the tuning peg to be adjusted as the actual value and a preselected one Reference frequency is supplied as a setpoint, counteracting the control deviation is controlled and the motorized arrangement for rotating the each to be adjusted Tuning pegs receiving socket wrench socket through on one or more other tuning pegs adjoining stop (s) is secured against rotation, d a d u r c h e k e n n n z e i c h n e t that the anti-twist protection of the motorized Arrangement (GEw by a clamped between two tuning pegs (SWIB in Fig. 1) Connection piece (VSB) is made, the idose led in through the gap the tuning peg is inserted and its axis (longitudinal axis ax) is oriented perpendicular to the axis of the tuning pegs (i3? that the connector a shaft (ST) fixed perpendicular to its Lelgsachse (ax), which between the tuning pegs are inserted parallel to their axis (aß) and that the shaft is a Torsional moment (SM), which is caused by the tension between the tuning pegs Connector is blocked and the surface of the connector to the Points of contact with the outer surface of the tuning pegs, preferably on the string wrap (WcK), a compressive force on both tuning pegs that inhibits the torsional moment of the shaft exercises, with the underside of the lateral surface of a tuning peg the top of the Connection piece (OV) and the top of the jacket surface of the other tuning peg the underside of the connector (UV) blocked. 2. Connector (VSB) according to claim 1, d a -d u r c h g e k e n n z e i c h n e t that the connecting piece as a pin that connects to the shaft (ST) a T-shape, is executed, the pin preferably so in the through the distance inserted into the space given for the tuning pegs used for bracing is that the shaft (ST) approximately the same distances to those used for Verspannzg Has tuning pegs. 3. Connector (VSB) according to claim 1 or 2, d a -d u r c h g e k e n n n n e i c h n e t that the jacket surface of the connecting piece at the contact points with the outer surfaces of the tuning pegs or string wraps an elastic covering (e.g. rubber). 4. Anti-rotation device with connector according to one of the claims 1 to 3, g e k e n n z e i c h n e t a) by a cam (HU, Fig. 2) which is attached to the shaft attached to the connecting piece (VSB, for the transmission of a torsional moment) (ST), fixed or via a radial driver (coupling surface K in Fig. 2 and / or Camshaft NW with cam NH in Fig. 3) is arranged, D) by two one above the other arranged, a cavity (H, Fig. 6) forming rails (SE1a, SE2a), in their Cavity, the cam can be displaced with its end face parallel to the soundpost wall on their outer surfaces on the inner rail walls (El, E2 in Fig. 2 to Fig. 4) slides, creating an adjustable distance between the shaft of the connector and the axis the motorized rotatable socket wrench socket (STCKS in Fig. 1) is made with adjustable spacing (E X) X), and c) by a clamping device that clamps the inner surfaces of the rail (E1a, E2a in Fig. 6), whereby the clamping of the rail interior surfaces the torsional moment of the shaft (ST) of the connecting piece (VSB) via the cam rotation (max) is generated (see also rail planes El, E2 in Fig. 2 to Fig. 4). 5. anti-rotation device according to one of claims 1 to 4, d a d u r c h g e k e nn n z e i c h n e t, daP, at the free end of the on the connector (VSB, for the transmission of a torsional moment) attached shaft (ST) a handle (G in Fig. 2) is screwed, whose end face (DA) receiving the shaft end with a pressure surface aligned parallel to the wave guide or sound post wall (FL, Fig. 2), preferably the cam face or the face of one with the cam radially coupled sleeve (NW, Fig. 4), a friction surface (DA, Fig. 4) forms whose frictional resistance (rB) by tensing and relaxing the grip face (DA) the contact surface (FL) used against the cls friction surface is optionally reinforced or can be weakened, whereby for the insertion of the connector into the Between two tuning pegs, preferably a relaxation and fixation the angular position of the connecting piece a tension of the grip face against the contact surface (FL) is to be made. 6. anti-rotation device according to one of claims 4 or 5, d a d u r c h g e k e n n n z e i c h n e t that the generation of a torsional moment on the shaft (ST) attached cam (HU in Fig. 2) rotatable on the shaft against this (Rod ST sliding in sleeve HU) is arranged that on the connector (VSB) to generate a torsional moment attached shaft (ST) a coupling surface (K in Fig. 2), which allows an optional coupling and uncoupling of the cam and shaft, is arranged, with this dome surface preferably as between sccien The connecting piece and the cam are fixedly arranged on the shaft, the radial end face (the E.g. it can also be inclined, as in Fig. 2 surface K) of the handle (G) screwed on the free end of the shaft to the face (K) of the Cam or a sleeve (KW) firmly connected to the cam is pressed on as well when the grip is released from this (K) again. 7. anti-rotation device according to one of claims 4 to 6, d a d u r c h g e k e n n z e 1 c h n e t that the generation of a torsional moment on the shaft attached cam as a cam sleeve (NH in Fig. 3), which on a as further sleeve designed camshaft (NW) as a radial driver axially sliding is guided, is formed, wherein the camshaft (NW) on the on the connector (VSB) to generate a torsional moment attached shaft (ST) can be rotated against it is arranged and said coupling surface (K), via which an optional input as well as Decoupling of the radial driver rotation of the cam sleeve (NH via camshaft NW) is made possible with the shaft (ST) attached to the connector and that rails (V, Fig. 4) prevent axial displacement of the cam sleeve. 8. anti-rotation device according to claim 7, d a d u r c h g e k e n n shows that the maximum outside diameter of the camshaft (Di-max of NW in Fig. 4) less than or at most equal to the minimally effective (= when screwed in Effective cam) outer diameter of the cam sleeve (Da-min of NH in Fig. 4), reduced by the height (-hx = s) of the effective area (including sliding play) for the the end faces of the cam sleeve (NH) arranged rails (V), is dimensioned. 9. anti-rotation device according to one of claims 5 to 8, d a d u r c h g e k e n n z e 1 c h n e t that the one at the free end of the shaft (ST, which the Torsional moment of the connecting piece transfers) screwed handle (G in Fig. 4) with the shaft via a friction surface (RF) acting as a slip clutch (RB / RM) is coupled. 10. Slip clutch mg for anti-rotation device according to claim 9, d a d u r c h e k e n n n z e i c h n e t that one on the shaft (ST) is centric to its Axis arranged cylinder surface (RM in Fig. 4) together with the cylinder surface a hole provided in the handle (G) centrically to its axis via a between Cylindrical surface of the shaft (RM) and cylindrical surface of the handle bore pressed-in elastic Material (e.g. foam R3 in Fig. 4) is the friction surface (RF) of the slip clutch form. 11. Anti-rotation device according to one of claims 1 to 10, d a d u r c h e k e n n z e 1 c h n e t that the, for the transmission of a torsional moment on the connecting piece (VSB), provided shaft (ST in Fig. 5) a rail wheel (RH) has, in the cavity (HO) two superposed, parallel to Soundpost wall or parallel to the front surface of the cavity for the cam (HU in Fig. 2 and NH in Fig. 4) forming rails (H in Fig. 6) or parallel to Front surface of the rail housing (SG in Fig. 5) aligned rails (SC) in whose profile slides (sliding guide in Fig. 5), the shaft in the rail wheel in is guided displaceably in the axial direction. 12. anti-rotation device according to claim 11, d a d u r ch g e k e n n z e i c h n e t that the rail wheel (RH in Fig. 5) with the one for the transmission of a torsional moment tes ar connector provided shaft (ST) via a radial driver (e.g. camshaft NW, Fig. 4 and Fig. 5 in connection with clutch HK and K, Fig. 2) is coupled that the rail wheel is preferably in Close to the grip (G) of the free end of the shaft (ST) or this itself forms that the rail wheel preferably has a knurl. 13. Clamping device that clamps the inner surfaces of the rails together (E1a, E2a in Fig. 6) allows for anti-twist protection according to claim 4, d a d u r c h g e -k e n n n z e i c h n e t that the pair of rails (SE1a, SE2a) on their at one end a hinge (S in Fig. 6) and has a collet (KS) at its other end. 14. Collet for clamping device according to claim 13, d a d u r c h e k e n n n z e i n e t that the collet through on the top surfaces of the Rails arranged inclined surface (s) (wedge surfaces Kla, K2a in Fig. 6) and on the Inclined surface (s) pressing (n) slide (KS) is formed. 15. Slider for collet according to claim 14, d a -d u r c h g e k It is noted that the pressure on the inclined surface (Kla, K2a in Fig. 6) Slide (KS) than can be rotated radially against the rise of the inclined surface in its plane Stop (KS rotatable about axis DP in Fig. 7) is executed, the inclined surface has a radial rise, the radial rise of which (H in Fig. 7) the rotational path of the contact surface (GUA) of the stop (KSVK) is adapted so that a self-locking bracing for every angle of rotation of the stop contact surface (GUA) of contact surface and inclined surface (FKn) de :: rail results. 16. Inclined surface arranged on the top surfaces of the rails (Kla, K2a, Fig. 6) according to claim 15, d a -d u r c h g e k e n n n z e i c h n e t that the inclined surface (via, K1b in Fig. 8) is rotatably mounted about its longitudinal axis (a), wherein the stop, which can be rotated radially against the inclined surface, is rotated the pivot axis (longitudinal axis a, Fig. 8) intersects the inclined surface and through the Contact pressure of the stop the inclined surface is pivoted into one position, in which they the maximum self-locking tension of the contact surface (GUA) and inclined surface (K1a, Klb in Fig. 8). 17. Radially rotatable stop according to claim 15 or 16, d a d u r c h g e k e n n z e 1 c h n e t that the stop as rotatable, against the Inclined surface pressing rod is carried out. 18. Radially rotatable stop according to claim 15 or 16, d a d u r c h g e k e n n z e 1 c h n e t that the stop surface is around its longitudinal axis (aSL, Fig. 8) is rotatably mounted, the longitudinal axis of the inclined surface being the longitudinal axis intersects the stop surface when the stop is rotated radially. 19. On the inclined surface (K1a, Kalb, Fig. 8) pressing surface of a in the plane of the inclined surface against its rise radially rotatable stop after one of claims 15 to 18, d u r c h g e n n n -z e i c h n e t that the pressing surface has a support made of elastic material (e.g. rubber). 20. Inclined surface (K1a, calf, Fig. 8) according to one of claims 15 to 19, it is indicated that the inclined surface is a support made of elastic material (e.g. rubber). 21. Anti-rotation device according to one of claims 4 to 20, d a d u r c h g e k e n n n z e i c h n'e t that in addition to generating a Torsional moment on the shaft (ST) attached cam (NHa in Fig. 6) another Cam (NHb in Fig. 6) is provided which is axially static with the first cam (NHa) connected and offset to this at an angle (R in Fig. 6) that the second Cam (NHb), like the first cam (NHa), also in one of the clamps Rails (SElb 'SE2b) formed cavity (H) slides braced, wherein for the second cam one in addition to the pair of rails for the first cam (SE1a, SE2a for NHa) provided second pair of rails (SE1b, SE2b for IxEb) is available that the angle between the first cam and the second cam (ß in Fig. E) is chosen so, that when clamping the pair of rails provided for the second cam (NHb) (SE1b, SE2b> the camshaft is rotated in the opposite direction as when clamping the pair of rails (SEla ') provided for the first cam (NHa) SE2a) and that the clamping of the pair of rails for the first cam alternates is made to clamp the pair of rails for the second cam and vice versa (NHa in clamped position and NHb relieved or NHb in clamped adjustment position and MMa relieved, see Fig. 6). 22. Anti-rotation device according to one of claims 5 to 21, d a d u r c h e k e n n n n n z e i c h n e t that the direction of rotation of the thread (GH in Fig. 4) of the at the free end of the shaft (ST, which is the torsional moment of the connecting piece transfers) screwed-on handle (G) when tightening the between the cam or camshaft and shaft (ST) of the connecting piece arranged coupling surfaces (K of HV and KK in Fig. 2) has the same direction of rotation as the cam (NHa in the clamping position in Fig. 6), which is the torsion device for the between two tuning pegs introduced connector generated. 23. Slider for collet according to one of claims 45 to 20 for Anti-twist device according to claim 21 or 22, d u r c h g e k e n n z e i c h n e t that the axis (aDP in Fig. 8) of the on an inclined surface (K7a, Klb in Fig. 8) against the rise of the inclined surface in its plane radially rotatable stop (KS-BU with KSVK and GUA) between the pair of rails for the first cam (NHa) and the pair of rails for the second cam (IGHb) perpendicular (or almost perpendicular) to the contact surfaces the inner rail walls (Ela, E2a or E7b, E2b in Fig. 6) is arranged that the Pair of rails for the first cam and that for the second cam, preferably to one another are arranged parallel and at the same height and that the on the top surfaces of the Rails arranged inclined surfaces mirror images of one another from the inside to the outside rising slope (s ST in Fig. 8) hook, the radially rotatable stop has three positions: One in which its contact surface (GUA in Fig. 8) the pair of rails for the first cam (NHa, Fig. 6) and the pair of rails for the second The cam (mob) is relaxed because the contact surface is rotated away from its inclined surface is, one in which its contact surface is the pair of rails for the second cam (NHb) compresses and the pair of rails for the first cam (NHa) is relaxed because the pressing surface is rotated away from its inclined surface, and one in which its pressing surface in the middle position parallel to the pairs of rails at the lowest point of the inclined surfaces is aligned, whereby both pairs of rails in this position of the pressure surface are relaxed (middle position of slide KS see Fig. 6, clamping position of SElb SE2b see FIG. 8, where SE1e, SE2a relaxed). 24. Anti-rotation device according to one of claims 15 to 23, characterized in that the axis (aDP in Fig. 6 and Fig. 8) of the on an inclined surface (K1a, K2a, K1b, K2b) can be rotated radially against the rise of the inclined surface in the plane thereof Stop (KS in Fig. 6 and KSVK in Fig. 8) on the top surface and bottom surface of the rail pairs (SE1a ' SE2b shows that the free end of the radially rotatable stop is designed as a handle end (GK) and that a coupling piece (KS-BU) is provided between the handle and the radially rotatable stop, this coupling piece between the handle and the stop (thread KS-BU in Fig. 6) or between the stop and the axis of rotation of the stop (thread KS-BU in Fig. 8) is preferably provided. 25. Anti-rotation device according to one of claims 4 to 24, d a d u r 0 h e k e n n z e 1 c h n e t that the pair of rails for bracing the cam, which is the torsional moment for the torsional tension of the connecting piece (SM generated by VSB by NHa in Fig. 1 and Fig. 9), opposite, angled Has clamping surfaces (preferably T-shaped clamping surface), each consisting of a longitudinal piece aligned parallel to the soundpost wall (preferably a transverse line the T-shaped clamping surface), which is the actual one, at one end a joint hinge (S) and at its other end a collet (KS) which can be clamped together Rail (SElaL 'SE2aL) forms and consists of a right-angled attached to the soundpost wall aligned, the cam guide (U in Fig. 9) forming piece (SEl'2aRW), wherein the cam guide protrudes as close as possible to the end faces of the tuning pegs and longitudinal pieces of the pair of rails which have the articulated hinge (S) and collet not through the free ends of the web walls de given The boundary line (SL in Fig. 1) protrude (see also Fig. 9). 26. Anti-rotation device according to one of claims 21 to 25 with between Shaft (ST) of the connecting piece and torsional moment (SM) generating cam arranged Dome surface (K in Fig. 2) according to claim 6, d u r c h g e k e n n n z e i c h n e t that the coupling surface between the first cam (NHa in Fig. 9) and the second cam (mob) is arranged (HK). 27. Anti-rotation device according to claim 26, d a d u r ch g e k e n N z e i h n e t that along the axis between the first cam and the second cam a preferably cylindrical housing statically connected to the cams is provided is, in which the shaft (ST in Fig. 9) of the connecting piece axially and radially displaceable or rotatably mounted (see detail ß in Fig. 9) and that the shaft of the connecting piece in the Hohlrez of the housing has a pressure surface which, together with the on the On the handle side of the housing, the inner surface of the housing end wall is the dome surface (K) forms. 28. Tuning key, whose tuning pegs to be matched receiving socket wrench receiving socket is rotatable about its axis by a motor, wherein the motor rotation through a control circuit to which the audio frequency of the to be adjusted Tuning pegs associated string as an actual value and a preselected reference frequency is supplied as a setpoint, the control deviation is counteracted and the motorized arrangement for rotating the tuning pegs to be adjusted in each case receiving socket wrench receiving socket through to one or more other Is secured against rotation with a standard or similar to a standard tuning key Tuning key whose socket wrench socket is driven by a longitudinal motor Drive is rotated by a motor, one on the shaft of the tuning key, tangentially to its direction of rotation guided driver the longitudinal control of the drive in a the socket wrench receiving socket rotating pivoting movement of the tuning key shaft implemented, g e k e n nz e 1 c h n e t a) by a joint (GL, Fig. 1, Fig. 12), that between the holder of the longitudinal drive (e.g. mounting of the motor spindle) and anti-rotation of the tuning key is arranged so that a pivot the tangential to the direction of rotation of the tuning key arranged on its shaft Driver (WA in Fig. 1, Fig. 12, Fig. 15b) along its tangential, the pivoting movement of the tuning key shaft (SFTH) corresponding control radius or tuning key rotation angle (ccvTOT in Fig. 1 and Fig. 15b) is enabled, whereby the pivoting of the tuning key shaft (SFTH) either through the drive feed of the motor spindle (SP, WA) or through angling of the joint (GL) is made, bi through several locking positions of the joint, in which the angling of the joint either fixed or from a fixed position can be adjusted again, these latching positions being lockable and unlockable are, and c) by a process with the following process steps: I) Put on the socket wrench socket (STCKS) on the tuning peg to be adjusted and Adjust the anti-twist device (JBL, Fig. 1) by bending the joint at unlocked joint locking position and locking the anti-twist device on the tuning pegs, II) Control of the joint (GL) to the next joint locking position using the tuning key shaft attacking driver (WA) with unlocked.r joint locking position, whereby the tuning key schzwt due to the torsional resistance of the in the socket wrench socket (STCKS) stuck tuning pegs held in rest position and tangential to the tuning key shaft attacking driver (WA) along his at the point of application of the tuning key shaft (SFTH) acting, the pivoting movement of the tuning key shaft (with unlocked Joint deflection) corresponding control radius (VTCT, Fig. 1) over the joint pivot point is swiveled towards the next joint locking position (by swiveling the Spindle SP to PGL in Fig. 1), III) when the controlled joint locking position is reached " Locking the joint in this position, IV) Controlling the motor drive when the socket wrench socket is rotated by means of driver-controlled pivoting of the tuning key shaft in the direction of rotation that reduces the control deviation, V) on reaching the end stop (EAN in Fig. 13c or EAN in Fig. 12) of the longitudinal Driver drive, unlock the joint locking position and reverse control of the longitudinal driver drive, the tuning key shaft through the Resistance to twisting of the one inserted in the socket wrench socket (STCKS) The tuning peg is held in the rest position and the one engaging tangentially on the tuning key shaft Driver (WA) along its at the point of application of the tuning key shaft (SFTH) acting, the pivoting movement of the tuning key shaft (with unlocked steering deflection) corresponding steering radius (OSTOTS Fig. 1) over the pivot point of the next Joint locking position is swiveled in the opposite direction (by swiveling the spindle SP by PGL in Fig. 1), VI) when the controlled joint detent position is reached, lock the Joint in this position, VII) Controlling the motorized drive in the event of rotation the socket wrench socket by means of the driver-controlled pivoting of the tuning key shaft in the direction of rotation reducing the control deviation and continuing the process steps IV to VII until the deviation of the pitch of the string to be adjusted Is zero. 29. Tuning key according to claim 28, d a d u r c h g e k e n n z e i c h n e t that the feed spindle of the driver drive (SP in Fig. 45a) for Motor-gear shaft has a plug-in coupling, the feed screw can be plugged onto the motor gearbox shaft from two opposite axes. 30. Tuning key according to claim 28 or 29, d a -d u r c h g e k It is noted that the two motor-gearbox shafts are mirror images (to a center line perpendicular through the shaft) opposite coupling parts has, each of which can optionally accommodate the feed screw that at the end of the spindle opposite the coupling part of the feed spindle Bearing for absorbing the axial load on the spindle is provided, the coupling part the feed spindle is not axially loaded and preferably screw slot and screwdrivers are provided as a radial driver for the motor gearbox shaft. 31. Tuning key according to one of claims 28 tns 30, d a d u r c h e k e n n n e i c h n e t that between the joint (GL in Fig. 15a) and the motor or transmission suspension (BI3) a U-shaped bracket (UFB), n whose open side (the U-shape) shaft sleeve (SFTH) and driver arms (MNU, MNO) through the spindle feed of the driver can be pivoted in and out, is arranged that between Joint (GL) and side wall of the U-shaped bracket a 3-rail (preferably = a Dovetail guide SWGL in Fig. 15a) in which the U-shaped bracket (UFB) is optional can also be inserted upside down, reversed, lockable is, and that between the engine or transmission suspension (BMB) and the side wall of the U-shaped Bracket a rail (preferably a dovetail guide SWMBM in Fig. 15a with direction of insertion along the spindle axis aSP), ie the motor or gearbox suspension (BMB) can optionally also be inserted upside down, reversed, lockable can, is arranged. 32. Tuning key according to claim 30 or 31, d a -d u r c h g e k It is noted that the Mitnellmerarme are attached to the spindle nut (SPM, Fig. 15a) have attached extension piece (WAV in Fig. 11), which the rotation lock the driver threads (! NU, MNO, Fig.15a), whereby the extension piece (WAV) in a sheet metal slot (BSZ, Fig. 11) and that the end of the spindle forming bearings (LGR, Fig. 12) with sheet metal slot (BSZ) and U-shaped bracket (UFB, Fig.15a) with rail parts (SW1 and SW2 in Fig. 15a) form a structural unit (see Fig. 15a). 33. Swivel joint (GL, Fig. 12) with lockable detent positions for Tuning key according to one of Claims 28 bie 32, g e k e n n marked by a cylinder wall with a segment-like distribution (e.g. division t in Fig. 10) on a radial line lying locking holes, through a concentric Fixed point (FI) mounted to the cylinder wall with congruent to the locking holes (preferably another cylinder wall according to Fig. 12, both cylinder walls clamped together by ball bearings KL) and by a guide hole (FI) of the Fixed point and locking hole of the cylinder wall engaging shift rod (eS), which as far it can be moved so that it can be positioned either in the fixing hole of the fixed point or in the locking hole the cylinder position or only in the guide hole of the fixed point when the locking hole is released the cylinder wall is guided, whereby an optional locking and unlocking of the angle of rotation (oSt in Fig. 10) between the fixed point and the cylinder wall provided with a perforated grid Is. 34. Egg-polar switching element for controlling the displacement of the switching rod (eVS) for optional locking and unlocking of the joint rotation angle for the swivel joint (GL in Fig. 12), according to claim 33, d u r c h g e k e n n -z e i c h n e t, that the switching rod is in a solenoid, consisting of a field coil (or two in a row switched field coils L1, L2 in Fig. 13b), as a bipolar - magnetizable core (BMK, Fig. 1Db) is performed that two the switching cycle (SAS) limiting the switching rod, arranged as fixed points, in cooperation with others, on the shift rod Magnetically arranged at a distance that allows the shifting path of the shift rod attractive surfaces (MAG and MF), are provided, being for each of the bipolar Switching states of the rod (eS) which alternatively limit the switching path of the rod Fixed point the shift rod is fixed by permanent magnetic attraction and that the bipolar switching states of the switching rod decoding contacts intended are the ones that trigger the switching state when a respective switching state is reached Switch off the excitation of the field coil. 35. Bipolar switching element according to claim 3 @, d a -d u r c h g e k It is indicated that the reaching of a respective switching state of the Switching rod decoding contacts are designed as working contacts zld that a pair of working contact surfaces each by means of an attracting, a permanent magnetic force field having surfaces arranged contact plane and magnetisable ones that press on this contact plane through the permanent magnetic force field and an electrically conductive surface is made (e.g. in FiC. 13b contact level ks and MF made of soft iron, with ML4G permanent magnet). 36. Swivel joint (GL, Fig. 12) with lockable detent positions for * tuning key, according to one of claims 28 to 35, characterized in that the joint (GL in Fig. 12 and Fig. 13a and b) contacts (kTE or kTE1 ... kTE4) are provided and arranged in such a way that when the longitudinal drive is rotated (pivoting of the feed spindle of the shaft sleeve driver) around the joint axis for each direction of rotation of the joint bend (L, R, Fig. 13a) at least one contact (kTE2 for R or kTE1 for L in touchdown area I and kTE4 for R or kTE3 for L in touchdown area II) is activated in its characteristic state before the penultimate joint locking point is exceeded, with the penultimate joint locking point being activated at least one rest step of the gel 37. Tuning key according to one of claims 1 to 36, d u r c h g e k e n n notices that for driving the socket wrench socket (STCKS) a Corner gear, whose gear shaft (aSP in Fig. 11, Fig. 12) is perpendicular to the motor shaft is arranged, is used, wherein the motor shaft (aGSM) is radial to the socket wrench socket (Fig. 10, Fig. 11, Fig. 12) is aligned. 38. Drive for tuning key according to claim 37, d a -d u r c h g It is not shown that the motor shaft (aGSM) is parallel to the axis of the tuning key shaft (aSFTH) (Fig. 12). 39. Actual target value evaluators for tuning keys, whose to be matched Socket wrench receiving socket that accepts tuning pegs, rotatable around its axis by motor is, the motor rotation by a control loop to which the audio frequency the string belonging to the tuning peg to be adjusted as the actual value and a preselected one Reference frequency is supplied as a setpoint, counteracting the control deviation is controlled, with an integrated actual setpoint comparator, d u r c h g e -k e n n n z e i c h n e t that the actual value / Solla value comparison circuit output comparison signal of a Differentiating circuit with downstream minimum detector (Min.) for the evaluation of the minimum signal increase or decrease is (Diff. Fig. 16v as well as an instantaneous value memory (Momentsp., Fig. 16), whose Output controls the system deviation counteracting, is supplied, the im Instantaneous value storage: ner each saved value of the actual value / target value comparison circuit supplied comparison signal during the duration of a respective minimal signal rise respectively. -waste is renewed. 40. Control loop control method for voting keys, whose each To be adjusted tuning pegs receiving socket wrench socket around its axis is rotatable by motor, the motorized rotation by a Wegelkreis, the the sound frequency of the string associated with the tuning peg to be adjusted as the actual value and a preselected reference frequency is supplied as a setpoint value, d a -d u r c it is noted that the motorized rotation of the socket wrench removal socket takes place in a time division multiplex process, with actual target value evaluation and motor Alternating rotation of the socket wrench socket. 41. Light marker generator for marking piano strings with one Light source that creates a line of light, that the light source has an adapter to be plugged onto a tuning peg (e.g. socket), the light line along the Piano strings aligned and parallel to the marked by a swivel joint String is adjustable and that the incidence of light from a generating the light line The aperture of the light source is made as close as possible to the strings (preferably parallel) is.