EP1630119A1 - Cable end carrier for elevator - Google Patents

Abstract

The cable fixing point (12,13) for the fastening of at least one elevator cable (7) has a rotational bearing (40) for the fastening of a cable end (7',7"), whereby each rotational bearing enables a rotation of the cable end fastening around a prescribed axis (L) which is orientated by a traction force (F) acting on the cable and/or in the longitudinal direction of a cable section (7.1,7.5) adjacent to the cable fixing point. The rotational bearing includes an axial bearing (41,43,44) with a rotatable section (43) to which is connected the cable end fastening. An independent claim is included for an elevator equipped with the aforesaid cable fixing point.

Description

The invention relates to a rope fixation point for attaching at least one rope according to the preamble of claim 1 and an elevator for conveying at least one load carrier by means of at least one movable in its longitudinal direction rope with a rope fixation point for a rope end of the respective rope.

In an elevator ropes, which are provided for carrying and carrying load carriers (for example, a car or a counterweight), usually held at the cable ends in rope fixing points and between the rope fixing points at least in sections in their longitudinal direction along tracks which by means of a suitable Guide device for the ropes are controlled, movable. The respective cable fixing points can be arranged or fastened, for example, to the ceiling or the floor of an elevator shaft or to a load carrier of the elevator. The guide device usually comprises one or more rollers around which the cables must move during a movement in their longitudinal direction, in particular a drive roller with which traction forces can be transmitted to the cables, and optionally deflection rollers.

If the ropes are moved in their longitudinal direction during operation of the elevator, then they may at the same time make a rotational movement about their longitudinal direction on the guide device. Rotation of a rope about its longitudinal direction may be caused, for example, on the guide device when the cable on the guide device is under an "oblique" tension (biasing pull) and moved under boundary conditions allowing rotation of the cable about its longitudinal direction. This is the case when the rope is under a tension in its longitudinal direction and thereby guided on a guide surface (for example on the surface of a roller) in a direction which is not parallel but oblique to the longitudinal direction of the rope. In the case of a rope which is under a train acting in its longitudinal direction and guided in a groove on the surface of a roller, diagonal tension is realized, for example, when the groove is disposed within a plane perpendicular to the axis of rotation of the roller and the cable is not parallel led to this level. Under these circumstances, the rope can not be guided exclusively at the bottom of the groove when the roller is about its axis of rotation rotated and the rope is thereby moved in its longitudinal direction. Rather, the rope runs partially over the flanks of the groove and thus transversely to the groove and can thereby perform a rolling movement on the surface of the roller in the direction of the axis of rotation of the roller. The rolling movement of the rope is in each case accompanied by a rotation of the rope about its longitudinal direction.

In elevators, diagonal pull may unintentionally occur, for example, when the guide device for the ropes and the rope fixing points during assembly are not aligned so precisely that each cable is guided on the guide device in each case parallel to the pulling direction. In other cases, diagonal pull is unavoidable - and therefore intended - due to the design of the cable guide. The latter is the case, for example, when a plurality of ropes are each guided side by side over a first roller and subsequently over a second roller, but the axes of rotation of the rollers are not arranged exactly parallel to one another. In this case, if appropriate, one of the ropes can be guided so that it is not under diagonal pull. The remaining ropes are inevitably on at least one of the rollers under a diagonal pull.

Rotational movements which are introduced into a cable can in turn lead to torsions of the respective cable or individual longitudinal sections of the respective cable around the respective longitudinal direction. This is the case when the rope is not rotated uniformly over its entire length by the same angle during a rotational movement about its longitudinal direction. In general, twists of the cables are associated with torsional moments, which exerts the respective rope on the guide device or the rope fixing points.

In the following, a longitudinal section of a rope is to be referred to as a "rope section".

If a rope is twisted, then the structure of the rope - under certain circumstances irreversible - can be changed. A rope usually consists of several tension members, which are "stranded" together. In general, a plurality of tension members - such as strands, which are made of metallic wires and / or synthetic fibers and / or natural fibers - beaten in a (Zugträger-) layer or several (Zugträger-) layers around a centrally arranged tension members each spirally. In this way, the tension members of a tension carrier layer form a periodic arrangement which repeats in the same direction in the longitudinal direction of the rope in each case after a characteristic distance (the "lay length"). With a rotation of the rope about its longitudinal direction can Under certain circumstances, the relative arrangement of the tension members may be irreversibly changed and the cable may be damaged. In a twisting of a rope in particular the lay length of the tension members is shortened or extended within a Zugträgerlage.

The effect of a rotation of a cable section is for the arrangement of the tension members in the region of the cable section depending on the direction of rotation with which the ends of the cable section are rotated relative to each other. A rotation of a cable section should be considered here as "turning" when the rotation is associated with a shortening of the lay length of a Zugträgerlage in this rope section. Correspondingly, a torsional moment which, when introduced into the rope or into a section of the rope, causes a shortening of the lay length, should be referred to as a "twisting" torsional moment. Similarly, a rotation of a cable section is referred to here as "revolving" when the rotation is associated with an extension of the lay length of a Zugträgerlage in this cable section. Accordingly, a torsional moment, which - initiated in the rope or in a section of the rope - causes an extension of the lay length, be referred to as a "twisting" torsional.

Ropes can be damaged by over-tightening or over-tightening of a tension carrier layer. Many rope constructions are particularly sensitive to untwisting a Zugträgerlage, in particular with respect to a loosening of the outermost Zugträgerlage. For example, if ropes, which are under the action of a tensile load, turned up, then the various tension members are loaded to varying degrees by the tensile load. The most heavily loaded tension members can increasingly degrade and, if necessary, be destroyed. This effect can significantly shorten the life of a rope.

Therefore, in an elevator, rotational movements of the cables should be controlled in such a way that torsions or moments of torsion, which may be introduced into the cables, do not exceed a certain tolerable level.

EP1026115 A1 discloses a cable fixation point for fastening at least one cable, which has in each case a cable end attachment for a cable end of the respective cable and a respective rotary mounting for the respective cable end attachment, wherein each rotary mounting comprises a thrust bearing which rotates the respective cable end attachment about a rigid, vertical axis allows. Such rope fixing points are in one Elevator used to fasten the ends of the ropes with which load carriers of the elevator are carried. The thrust bearings ensure that the ropes can freely rotate around the longitudinal direction of the rope-fixing points. In this case, the ropes in the rope fixing points are each held so that no torsional moment is introduced into the respective rope at the rope set points. The latter is intended to cause rotations and / or twists and / or torsional moments, which may under certain circumstances be introduced into one of the cables between the respective cable fixing points - for example when rotating around a traction sheave or pulleys - in the axial bearings of the cable fixing points. In this way, in particular, it should be achieved that the extent of such twists, which may be introduced into a cable section of a cable adjoining a cable tie point, is rapidly reduced again due to a corresponding rotation of the cable ends. In this way, in particular the adjacent to the fixed points cable sections should be spared.

The elevator known from EP1026115 A1 has a number of disadvantages when a rope of the elevator fastened to the cable fixation point is guided such that the cable section immediately adjacent to the cable fix point does not run exactly vertically but at a certain angle of inclination with respect to the vertical. In this case, the tensile force acting on the rope and thus directed parallel to the longitudinal direction of the rope is introduced at the rope end attachment of the rope in a direction in the rope fixation point inclined by said inclination angle with respect to the vertical. The size of the inclination angle depends under these conditions usually from the current position of the respective load carrier of the elevator and is thus changed in a carriage of the load carrier. These effects lead to several technical problems. On the one hand, the thrust bearing, which is connected to the Seilendbefestigung the rope, loaded radially to the axis of rotation of the thrust bearing. The thrust bearing can wear out quickly under the action of radial forces, unless elaborate countermeasures are taken. Furthermore, the rope is bent at the end of the rope attachment to the side and possibly greatly curved or kinked. The tension members of the rope and possibly other components of the rope (eg an outer rope sheath or an intermediate layer arranged between different tension carrier layers) are therefore loaded unevenly by the tensile force. A part of the tension members is therefore burdened above average and can therefore degrade faster. Due to the fact that the rope is constantly rotated about the vertical axis of rotation of the thrust bearing during transport of the load carrier about its longitudinal direction and thus at the cable fix point, this becomes Rope on the rope end attachment at each reversal of the direction of travel of the load carrier loaded by a bending change. These bending changes also promote the degradation of the rope. For example, the arrangement of the tension members in the region of the cable end attachment can be irreversibly changed by bending change and the cable can thus be damaged. Another problem should be noted if the rope is not designed to be absolutely torsion free. In this case, a Zugträgerlage the rope can be turned on under the action of the tensile load, since the thrust bearing allows free rotation of the rope at the cable fix point and can not apply a torsional moment, which could counteract the unraveling of the Zugträgerlage. This effect can occur even if the load carriers of the elevator are not carried.

The invention has for its object to avoid the disadvantages mentioned and to provide a rope fixation point for attaching at least one rope and a lift for conveying at least one load carrier by means of at least one movable in its longitudinal direction rope with at least one rope fixation point for a rope end, so that rotational movements of the respective Rope are controlled in a gentle way for the rope, even if the rope link point is loaded by a force acting on the rope pulling force whose direction deviates from the vertical and / or whose direction can be arbitrarily specified at least within an angular range.

This object is achieved by a cable hinge point with the features of claim 1 and an elevator with the features of claim 10.

The rope fixation point comprises a Seilendbefestigung for a rope end of the respective rope and each a pivot bearing for the respective Seilendbefestigung, each pivot bearing allows rotation of the respective Seilendbefestigung about a (rotary) axis. According to the invention, the pivot bearing is constructed so that the axis is alignable by a tensile force acting on the rope. The axis is therefore not rigidly arranged. It automatically changes its direction or orientation when the direction of the pulling force acting on the respective cable is changed. The axis can align under the action of the tensile force such that the component of the tensile force acting radially to the axis becomes minimal. The pivot bearing must therefore be highly resilient only in the direction of the respective tensile force. Thus, the condition is created that the pivot bearing can be realized with relatively simple means. Furthermore, the respective rope, if it is offset at the cable link point in a rotation about its longitudinal direction, only minimally stressed by bending change.

In one embodiment of the rope fixation point, the axis can be aligned in the direction of a tensile force acting on the rope and / or in the longitudinal direction of a rope section adjoining the rope tie point. This has the advantage that the pivot bearing is not claimed by any forces acting radially to the axis and therefore can be realized with particularly simple means. Furthermore, the respective rope, if it is offset at the cable link point in a rotation about its longitudinal direction, claimed at the cable link point not at all by bending or bending change.

The pivot bearing can be realized in various ways within the scope of the invention. The pivot bearing may comprise a thrust bearing having a part rotatable about the axis, the rope end mounting being connected to the rotatable part.

The pivot bearing may comprise a pivoting mechanism for the thrust bearing for aligning the axis within an angular range. In this case, since the pivoting mechanism allows pivoting of the thrust bearing in its entirety, the thrust bearing can have an axis of rotation that is immovable (i.e., oriented in a given direction) with respect to the thrust bearing. Such thrust bearings are particularly simple to implement with standard components, for example as Axialwälzlager or Axialgleitlager. For example, the pivot mechanism may include a hinge for pivoting the thrust bearing about a point or hinge for pivoting the thrust bearing about a pivot axis or hinge for pivoting the thrust bearing about a first pivot axis and about a second pivot axis not disposed parallel to the first pivot axis. Such hinges allow the axis to be aligned by pivoting in one dimension through an angle within a predetermined angular range or aligning the axis in two dimensions within a predetermined solid angle range. A joint that allows pivoting in two dimensions in this context has the advantage that the cable link point does not have to be precisely aligned during assembly, since the axis of the pivot bearing self-aligns with respect to the direction of the tensile force within a solid angle range.

Alternatively, the thrust bearing can be designed as Axialpendellager, the rotatable part is mounted pendulum. In this case, the axis of rotation of the thrust bearing is not rigidly aligned relative to parts of the thrust bearing, but within a predetermined angular range or solid angle range aligned. An additional one Swing mechanism for pivoting the thrust bearing in its entirety is therefore not required in this embodiment.

Another embodiment of the rope fixation point comprises means for controlling a torsional moment acting on the rope at the end of the rope. In this case, the rope is held rotatably on the rope fixation point, but not kept freely rotatable. Rotations of the rope can be controlled with the means mentioned so that the rope initiates a torsional moment in the pivot bearing whose size is within predetermined limits. The means may for this purpose comprise, for example, a braking device for braking a rotational movement of the cable and / or a drive for transmitting a torsional moment to the rotatable part and / or to the cable end attachment and / or to the cable. Preferably, the rotational movements of the rope at the rope fixation point are controlled so that the rope is held at the rope fixation point under a twisting torsional moment. In this way it can be achieved that the rope - should it not be rotation-free - does not turn up under the tensile load. Furthermore, it is ensured that the torsional moment acting on the cable at the cable fix point does not exceed a predetermined limit. In this way, ropes can be kept gentle, which are not rotation-free.

The rope fixation point according to the invention can be used in an elevator for conveying at least one load carrier by means of at least one rope movable in its longitudinal direction, wherein the rope fixation point serves for fastening a rope end of the respective rope and the respective rope is under tensile force at the rope end whose direction is dependent is changeable from a position of the load carrier. The construction of the cable hinge point ensures that the axis of the rotary bearing is aligned by the tensile force, for example in the respective direction of the tensile force and / or in the longitudinal direction of a cable section adjacent to the cable hinge point. Regardless of the current position of the load carrier to be transported, the axis of the pivot bearing is automatically aligned so that rotational movements of the rope are controlled in a manner as gentle as possible for the rope. The rope fixing point does not have to be arranged very precisely during assembly, since the axis of the pivot bearing optimally aligns under the effect of the tensile force anyway.

• die eine geringe Steifigkeit gegenüber Torsionen aufweisen und/oder
• die derart geschlagen sind, dass sie unter einer Zuglast nicht drehungsfrei sind und/oder
• die zwischen den Seilfixpunkten an einer Führungsvorrichtung unter einem Schrägzug stehen und in die aufgrund des Schrägzugs besonders grosse Torsionsmomente zwischen den Seilfixpunkten eingeleitet werden können.

The invention allows a gentle guide any ropes. In particular, it allows a gentle guidance of ropes,

• which have a low rigidity against torsions and / or
• which are beaten so that they are not free of rotation under a tensile load and / or
• which stand between the rope-fixing points on a guide device under a diagonal pull and can be introduced into the due to the oblique pull particularly large torsional moments between the rope fixing points.

Fig. 1:

Einen Aufzug zum Befördern einer Aufzugskabine und eines Gegengewichts mittels eines bewegbaren Seils, mit einer Treibrolle und mehreren Umlenkrollen für das Seil und zwei Seilfixpunkten zur Befestigung der Seilenden des Seils gemäss der Erfindung,

Fig. 2:

die Treibrolle gemäss Fig. 1, in einer Ansicht in Richtung des Pfeils II in Fig. 1, wobei das Seil schräg über die Treibrolle läuft,

Fig. 3:

die Treibrolle gemäss Fig. 2, aus einer anderen Perspektive gesehen (gemäss Pfeil III in Fig. 2),

Fig. 4:

ein erstes Ausführungsbeispiel für einen Seilfixpunkt gemäss der Erfindung,

Fig. 5:

ein zweites Ausführungsbeispiel für einen Seilfixpunkt gemäss der Erfindung,

Fig. 6:

der Seilfixpunkt gemäss Fig. 5, in einem Schnitt VI-VI gemäss Fig. 5, und

Fig. 7:

ein drittes Ausführungsbeispiel für einen Seilfixpunkt gemäss der Erfindung.

In the following, further details of the invention and in particular advantageous embodiments of the invention will be explained with reference to schematic drawings. Show it:

Fig. 1:

An elevator for conveying an elevator car and a counterweight by means of a movable cable, with a drive roller and a plurality of deflection rollers for the cable and two cable fixing points for fastening the cable ends of the cable according to the invention,

Fig. 2:

1, in a view in the direction of the arrow II in Fig. 1, wherein the cable runs obliquely over the drive roller,

3:

the drive roller according to FIG. 2, viewed from a different perspective (according to arrow III in FIG. 2),

4:

a first embodiment of a rope fixation point according to the invention,

Fig. 5:

A second embodiment of a rope fixation point according to the invention,

Fig. 6:

the rope set point according to FIG. 5, in a section VI-VI according to FIG. 5, and

Fig. 7:

a third embodiment of a rope fixation point according to the invention.

Fig. 1 shows a lift 1 for conveying at least one load carrier with at least one movable cable connected to the respective load carrier. FIGS. 2-7 illustrate various details of the elevator 1.

In the present case, the elevator 1 comprises two load carriers which can be transported by a cable 7: an elevator car 3, which is guided on guide rails 4 in the vertical direction, and a counterweight 5, which is guided on guide rails 6 in the vertical direction. The cable 7 has two cable ends 7 ', 7 ", which in each case at a cable fix point 12 or 13 are arranged rotatably about an axis L ₁₂ and L ₁₃ . The rope 7 can be rotated at the rope fixing points 12 and 13 about the axes L ₁₂ and L ₁₃ in any direction of rotation, as indicated in Fig. 1 by the double arrow 12 'and 13'. The rope fixing points 12 and 13 are fixed to a supporting structure 2 and arranged such that the respective directions of the axes L ₁₂ and L ₁₃ deviate from the direction of a vertical V. According to FIG. 1, it is assumed that the axis L ₁₂ is inclined relative to the vertical V by an inclination angle α ₁₂ and the axis L ₁₃ is inclined relative to the vertical V by an inclination angle α ₁₃ . Constructive details of the rope fixing points 12 and 13 are not shown in Fig. 1; These will be explained below in connection with FIGS. 4-7.

The cable 7 is guided over a rotatably mounted drive roller 20 which is arranged on the support structure 2 together with a drive (not shown) for the drive roller 20. The cable 7 is in addition to two pulleys 11.1 and 11.2, which are both attached to the cab 3, guided in the region of the cable section which extends between the drive roller 20 and the cable fix point 12. As a result, a 2: 1 suspension for the car 3 is realized. The cable 7 is in addition to a pulley 11.3, which is attached to the counterweight 5, guided in the region of the cable section which extends between the drive roller 20 and the cable link point 13. As a result, a 2: 1 suspension for the counterweight 5 is realized. When the drive roller 20 is set in rotation about its axis of rotation, traction forces are transmitted to the cable 7 and the cable 7 is moved in its longitudinal direction. This causes the cable 7 to run around the pulleys 11.1, 11.2, 11.3 and at the same time the elevator car 3 and the counterweight 7 in opposite directions - depending on the direction of rotation of the drive roller 20 - are moved up or down, as in Fig. 1 by a respective Double arrow on the cab 3 and the counterweight 5 is indicated.

During a drive of the cabin 3, the drive roller 20 and the guide rollers 11.1, 11.2, 11.3 influence the path which follows the cable 7 during its movement in its longitudinal direction. The drive roller 20 and the guide rollers 11.1, 11.2, 11.3 thus form a guide device for the cable 7: serve as guide surfaces, the areas of the surfaces of the rollers 11.1, 11.2, 11.3 and 20, with the cable 7 when driving the car 3 in Contact advised.

In the following, a distinction is made between different cable sections 7.1, 7.2, 7.3, 7.4 and 7.5 of the cable 7: The cable section 7.1 extends between the cable end 7 'at the cable tie point 12 and the guide roller 11.1, the cable section 7.2 extends between the guide rollers 11.1 and 11.2, the cable section 7.3 extends between the guide roller 11.2 and the drive roller 20, the cable section 7.4 extends between the drive roller 20 and the guide roller 11.3 and the cable section 7.5 extends between the guide roller 11.3 and the cable end 7 "at the cable junction 13th

In order to keep the car 3 and the counterweight 5 in their respective position, a tensile force F _{12 is introduced} into the cable fixation point 12 via the cable section 7.1 and a tensile force F ₁₃ into the cable fixation point 13 via the cable section 7.5. The tensile force F ₁₂ is along the longitudinal direction of the cable section 7.1 and the tensile force F ₁₃ is directed along the longitudinal direction of the cable section 7.5. When driving the car 3, the lengths of the cable sections 7.1, 7.3, 7.4 and 7.5 - the current position of the car 3 and the counterweight 5 are changed accordingly - each. The rope fixing points 12 and 13 are arranged such that the longitudinal direction of the cable section 7.1 and the longitudinal direction of the cable section 7.5 are inclined relative to the vertical V and the respective angle between the longitudinal direction of the cable section 7.1 and the longitudinal direction of the cable section 7.5 relative to the vertical V at a Drive the cab 3 also be changed. As a result, the tractive forces F ₁₂ and F ₁₃ change direction as the car 3 travels.

According to the invention, it is provided that the axis L ₁₂ can be aligned by the tensile force F ₁₂ acting on the cable 7 and the axis L ₁₃ by the tensile force F ₁₃ acting on the cable 7. Correspondingly, the inclination angles α ₁₂ and α ₁₃ also change when the car 3 is driven. In the example according to FIG. 1, it is assumed that the axis L ₁₂ is oriented in the direction of the tensile force F ₁₂ or in the longitudinal direction of the cable section 7.1 is. Accordingly, the axis L ₁₃ is aligned in each case in the direction of the tensile force F ₁₃ and in the longitudinal direction of the cable section 7.5.

According to FIGS. 2 and 3, the cable 7 is guided in such a way that it is not only moved in its longitudinal direction when the car 3 is moving, but is also caused to rotate about its longitudinal direction.

In Fig. 2 and 3, the course of the rope 7 in the vicinity of the drive roller 20 is shown in more detail. Fig. 2 shows a view in the direction of the arrow II in Fig. 1, ie in the horizontal direction, Fig. 3, however, shows a view in the direction of the arrows III in Fig. 2, ie in the vertical direction from bottom to top. It is assumed that the rope 7 has a round cross-section and in a groove 21 on the surface of the drive roller 20 is guided. The groove is arranged symmetrically to a plane 27, which is oriented perpendicular to the axis of rotation 25 of the drive roller 20. The position of the bottom of the groove 21 is defined by the intersection between the plane 27 and the driving roller 20.

Figures 2 and 3 illustrate the drive roller in a state of rotation about the axis 25. In the present example, it is assumed that the respective surface of the drive roller 20 facing the viewer is currently being moved in the direction of the arrows 26. Due to the rotation of the drive roller 20, the cable 7 is moved in its longitudinal direction, i. moved in the direction of the arrows 31 and guided along the surface of the drive roller 20 through the groove 21. Furthermore, it is assumed that the cable 7 - due to the relative arrangement of the drive roller 20 and the groove 21 with respect to the guide rollers 11.1, 11.2, 11.3 on the elevator car 3 and the counterweight 5 - is not performed exactly parallel to the plane 27. Under this condition, the rope 7 is - influenced by the tensile forces acting on the cable 7 - in contact with the driving roller 20 along a curve which extends obliquely with respect to the plane 27. In other words, in the present configuration, the rope 7 is under diagonal pull. In the situation shown in Figs. 2 and 3, the rope 7 runs at the top of its path at the bottom of the groove 21, i. in the middle between the adjacent flanks of the groove 21, and there crosses the plane 27 (see Fig. 2). 2 and 3, the (in the region of the cable section 7.4) strikes upward in the direction of the support structure 2 running part (ie, on the roll 20 or entering the groove 21) of the rope 7 at a Edge 21 'of the groove 21 on the surface of the drive roller 20 and the plane 27 approaches on an edge of the groove 21, as indicated by the arrow 34. The (in the region of the cable section 7.3) down from the support structure 2 away running (ie running off the roller 20 or expiring from the groove 21) part of the rope 7 moves away from the plane 27 and approaches on the other flank of the groove 21 to the edge 21 "of the groove 21, as indicated by the arrow 35.

In the example according to FIGS. 2 and 3, it is assumed that the coefficient of friction for a contact between the cable 7 and the drive roller 20 is so great that the cable 7 does not move without resistance in the direction of the axis of rotation 25 or in the direction of the arrows 34 and 35 can slide. This assumption is compatible with the requirement that with the drive roller 20 - according to its function in the elevator 1 - large traction forces are to be transmitted to the cable 7. In the present case, the movement of the cable 7 along the arrows 34 and 35 - depending on the size of the coefficient of friction for contact between the cable 7 and the drive roller 20 - with a rolling motion or a superimposition of a Rolling motion and a sliding motion connected. The rolling movement is favored in the present case by the round shape of the cross section of the rope 7. Furthermore, the rolling motion is facilitated by the fact that the rope 7 is not guided in a form-fitting manner at the bottom of the groove 21. Due to the rolling movement, the rope 7 is rotated about its longitudinal direction. The direction of rotation is indicated by an arrow 32 in FIG.

In the case of the situation illustrated in FIGS. 2 and 3, the rotation of the cable 7 in the direction of the arrow 32 is due to the fact that a torsional moment T is introduced into the cable 7 on the drive roller 20. The instantaneous direction of the torsional moment T is indicated in each case by arrows in FIG. 1-3. The direction of the torsional moment T can be reversed with respect to the indicated arrows when the drive roller 20 rotates counter to the direction of the arrows 26 about the axis of rotation 25.

In the case of FIGS. 2 and 3, the effect of a diagonal pull on the cable 7 is shown by way of example with reference to the drive roller 20. It should be noted that the technical relationships shown can be transferred analogously to the movement of the cable 7 on the guide rollers 11.1, 11.2 and 11.3, if a diagonal train should also be realized on one of these rollers. It should also be noted that for the occurrence of the rotation 32, the presence of the groove 21 is not a necessary requirement. A sufficient condition for the occurrence of a rotation of the rope 7 is the presence of diagonal pull. In general, the cable 7 is under diagonal pull when the cable 7 is guided such that it at least in sections in the direction of one of the axes of rotation of the rollers 11.1, 11.2 when moving in its longitudinal direction in contact with the rollers 11.1, 11.2, 11.3 and 20 respectively , 11.3 or 20 (ie not exclusively in a plane perpendicular to the axis of rotation of the respective roller) is moved.

When the cable 7 is rotated about its longitudinal direction during a rotation of the drive roller 20 on the drive roller 20, this rotation usually does not affect uniformly over the entire length of the cable 7. The rope 7 is namely not freely rotatable over the entire length, especially as a rotation of the rope 7 is limited to its longitudinal direction at several points, for example, to the pulleys 11.1, 11.2, 11.3 due to friction between the cable 7 and the pulleys 11.1, 11.2 , 11.3 and under certain circumstances - as will be explained below - also at the rope fixing points 12 and 13. Furthermore, further torsional moments can be introduced into the rope on the pulleys 11.1, 11.2 and 11.3, depending on whether the rope 7 also these roles is under a diagonal pull or not. Consequently, the cable sections 7.1, 7.2, 7.3, 7.4 or 7.5 can be rotated during a drive of the car.

The latter is true even if the rope 7 is not under diagonal pull on the steering rollers 11.1, 11.2 and 11.3. If the cable 7 is exclusively on the drive roller 20 under diagonal pull and the drive roller 20 is set in a rotation of the car 3 in a rotation, then at the drive roller 20 first twists can be introduced directly into the cable sections adjacent to the drive roller 20, ie in the cable sections 7.3 and 7.4. These introduced at the drive roller 20 twists can lead indirectly to a rotation of the car 3 to rotations in other cable sections between the two cable hinge points, as in a rotation of the rope 7 to the pulleys 11.1, 11.2 and 11.3 and twists on the rollers 11.2 and 11.3 can be transported out, ie in the cable sections 7.1, 7.2 and 7.5. This is especially true when the car 3 is repeatedly caused to travel up and down. The extent of the rotations of the individual cable sections can each be different. In addition, the extent of the rotation of the respective cable section can be changed during a travel of the car 3 as a function of the current length of the cable section.

• a) von den jeweiligen Reibwerten für die Kontakte des Seils 7 mit den Rollen 11.1, 11.2, 11.3 und 20,
• b) von der Torsionssteifigkeit des Seils 7,
• c) von dem "Ausmass" des Schrägzuges an jeder einzelnen Rolle, beispielsweise charakterisiert durch den Winkel zwischen der Drehachse der jeweiligen Rolle und dem jeweiligen Verlauf der Längsrichtung des Seils 7 längs der Oberfläche der jeweiligen Rolle (ist dieser Winkel an allen Stellen, an denen das Seil 7 mit der Rolle in Kontakt gebracht ist, gleich 90°, dann liegt kein Schrägzug vor, d.h. das Seil 7 bewegt sich an der Oberfläche der Rolle innerhalb einer Ebene senkrecht zur Drehachse der Rolle; je mehr dieser Winkel in einem ausgewählten Längsabschnitt des Seils 7 an der Oberfläche der Rolle von 90° abweicht, desto stärker ist der Schrägzug in diesem Längsabschnitt ausgeprägt).

In general, the extent of twists which can be introduced into the cable 7 due to the interaction of the cable 7 with the rollers 11.1, 11.2, 11.3 and 20 depends on several factors a) -c):

• a) of the respective coefficients of friction for the contacts of the cable 7 with the rollers 11.1, 11.2, 11.3 and 20,
• b) the torsional rigidity of the rope 7,
• c) of the "extent" of the diagonal pull on each individual roller, for example characterized by the angle between the axis of rotation of the respective roller and the respective course of the longitudinal direction of the cable 7 along the surface of the respective roller (this angle is at all points where the cable 7 is brought into contact with the roller, equal to 90 °, then there is no skew, ie the cable 7 moves on the surface of the roller within a plane perpendicular to the axis of rotation of the roller, the more this angle in a selected longitudinal section of the roller Rope 7 deviates at the surface of the roll of 90 °, the stronger the skew is pronounced in this longitudinal section).

As the cross-sections of the cable 7 shown in Fig. 3 indicate, the cable 7 comprises a plurality of tension members 8, which are stranded together, and a cable sheath 10, which encloses the tension members 8 and the surface of the cable 7 forms. The tensile members may comprise, for example, synthetic fibers (e.g., aramid) and / or metallic wires (e.g., steel wires) and / or natural fibers. The fibers and / or wires can each be processed into strands. The cable sheath 10 may be made of an elastomer, such as polyurethane or rubber.

• Das Seil 7 besitzt eine geringe Torsionssteifigkeit, wenn die Zugträger beispielsweise aus Kunstfasern wie Aramid gefertigt sind.
• Elastomere wie Polyurethan oder Gummi als Material für den Seilmantel 10 sorgen jeweils für eine hohe Reibung zwischen dem Seilmantel 10 und der Treibrolle 20 bzw. den Umlenkrollen 11.1, 11.2 und 11.3. Dies führt einerseits zu einer hohen Traktion zwischen der Treibrolle 20 und dem Seil 7. Andererseits können an den Rollen 20, 11.1, 11.2 und 11.3 extrem grosse Torsionsmomente in das Seil 7 eingeleitet werden, wenn das Seil unter einem Schrägzug steht.

The rope 7 can - with the above characteristics - are particularly easy to twist:

• The rope 7 has a low torsional stiffness when the tensile carriers are made of synthetic fibers such as aramid, for example.
• Elastomers such as polyurethane or rubber as the material for the cable sheath 10 each ensure high friction between the cable sheath 10 and the drive roller 20 and the guide rollers 11.1, 11.2 and 11.3. On the one hand, this results in a high degree of traction between the drive roller 20 and the cable 7. On the other hand, extremely large torsional moments can be introduced into the cable 7 on the rollers 20, 11.1, 11.2 and 11.3 when the cable is under an oblique pull.

The invention makes it possible to protect the cable 7 in that the extent of rotation of the cable section 7.1 and / or the extent of rotation of the cable section 7.5 is kept within limits by a suitable construction of the cable fixing points 12 and 13.

FIGS. 4-7 illustrate three different embodiments of the fixed points 12 and 13, respectively. The embodiments each comprise a cable end attachment 50 for the cable end 7 'or 7 "of the cable 7 and a respective rotary mounting 40 or 60 or 100 for the cable Rope end fitting 50.

By means of the cable end attachment 50, the cable 7 is held in a conventional manner at the cable end 7 'or 7 "For this purpose, a longitudinal section (drawn in dashed lines in FIGS. 4, 5 and 7) of the cable 7 in the vicinity of the cable end 7 'or 7 "between a housing part 51 and a wedge 52 of the cable end connection 50 is clamped. The pivot supports 40, 60 and 100 allow - in different ways in each case - a rotation of the respective Seilendbefestigung 50 about an axis L, which is pivotable and each assumes a direction that of the Direction of a force acting on the rope 7 traction F depends. The symbol "L" is here used to represent the axis L ₁₂ or the axis L ₁₃ . The axis L is shown in FIGS. 4, 5 and 7 as a dashed line. The symbol "F" is here used as representative of the introduced via the cable section 7.1 in the rope fixation point 12 traction F ₁₂ or for the introduced via the rope section 7.5 in the cable fix point 13 tensile force F ₁₃ . The rotary bearings 40, 60 and 100 are each constructed so that the respective axis L can align with the respective direction of the tensile force F. The instantaneous direction of the tensile force F is indicated in FIGS. 4, 5 and 7 by an angle α with respect to the vertical V, which is shown as a double-dashed line. The symbol "α" is representative of the inclination angle α ₁₂ or the inclination angle α ₁₃ .

• ein Axiallager in Form eines Axialpendellagers mit einer Basis 41, welche auf der Tragstruktur 2 abgestützt werden kann, und mit einem um die Achse L drehbaren Teil 43, welches über mehrere Wälzkörper 44 auf einer Oberfläche 41.1 der Basis 41 abgestützt ist, und
• eine Befestigung 45 zur Befestigung der Seilendbefestigung 50 am drehbaren Teil 43.

The embodiment of the cable fixation point 12 or 13 according to FIG. 4 comprises the cable end attachment 50 for the cable end 7 'or 7 "and the rotary support 40, wherein the rotary support 40 comprises:

• a thrust bearing in the form of a Axialpendellagers with a base 41 which can be supported on the support structure 2, and with a rotatable about the axis L part 43, which is supported by a plurality of rolling elements 44 on a surface 41.1 of the base 41, and
• a fastener 45 for attachment of the Seilendbefestigung 50 on the rotatable part 43rd

The surface 41.1 has the shape of a spherical surface segment. In Fig. 4, the point P indicates the center of a circle of curvature 42 adapted to the surface 41.1. Each of the rolling elements 44 has the form of a pendulum roller whose lateral surface adjoining the surface 41.1 has the same curvature within a longitudinal section along the respective central axis (not shown in FIG. 4) as the surface 41.1. The center axes of the various rolling elements 44 are directed in a star shape on the axis L.

The attachment 45 is rod-shaped in the present case and arranged such that in the longitudinal direction of the cable section 7.1 and 7.5 acting tensile force F along the axis L can be introduced into the rotatable member 43. For this purpose, the attachment 45 - as shown in Fig. 4 - through a through hole 2.1 in the support structure 2, a aligned with the passage opening 2.1 central through hole 41.2 in the base 41 and formed between the rolling elements 44 and the rotatable member 43 space guided.

The rotatable member 43 is mounted on the rolling elements 44 and the surface 41.1 - with respect to the point P - pendulum. Thanks to the spherical shape of the surface 42.1 and the above-mentioned shape and arrangement of the rolling elements 44, the rotatable member 43 can be rotated on the one hand about the axis L when a rotary motion is transmitted to the Seilendbefestigung 50 via the cable 7, as in Fig. 4 by the double arrow 46 is indicated. On the other hand, the rotatable part 43 and thus the axis L can be pivoted about the point P, provided that the friction between the rolling elements 44 and the surface 41.1 is so small that the rolling elements 44 can slide sufficiently well radially to the axis L. The friction between the rolling elements 44 and the surface 41.1 can be chosen so low in the rule that the rotatable member 43 under the action of the tensile force F assumes a position which is characterized in that the tensile force F along a straight line through the point P is directed. In this position, the rotatable member 34 is solely along the axis L, i. axial, loaded. Since in this position no force acting in the radial direction with respect to the axis L, the axis L is under this condition in a stable equilibrium position. If the direction of the tensile force F changes, the rotatable part 43 swings around the point P until the axis L again assumes an equilibrium position in which no force acts radially to the axis L. In this way, it is ensured that the axis L is aligned in each case in the direction of the tensile force F and in the longitudinal direction of the cable section 7.1 or of the cable section 7.5.

The embodiment of the rope fixation point 12 or 13 according to FIGS. 5 and 6 comprises the cable end attachment 50 for the cable end 7 'or 7 ", the rotary mounting 60 for the cable end attachment 50 and a brake device 70.

The brake device 60 is used - as will be explained below - to control a rotational movement of the cable 7 or to control a force acting on the cable 7 at the cable anchorage point 12 or at the cable tie point 13 Torsionsmoments.

• eine Basis 61,
• einen an der Tragstruktur 2 befestigten Schwenkmechanismus 65, an der die Basis 61 befestigt ist, um ein Schwenken der Basis 61 gegenüber der Vertikalen V zu ermöglichen,
• ein um die Achse L drehbares Teil 62, welches über ein Axiallager 63 auf die Basis 61 derart gestützt ist, dass die Achse L bezüglich der Basis 61 starr angeordnet ist.

The pivot bearing 60 includes:

• a base 61,
• a pivoting mechanism 65 fixed to the support structure 2, to which the base 61 is fixed to allow pivoting of the base 61 with respect to the vertical V,
• a rotatable about the axis L part 62 which is supported on the base 61 via a thrust bearing 63 such that the axis L is rigidly arranged with respect to the base 61.

The Seilendbefestigung 50 is fixed to the rotatable member 62 and thus can also be rotated about the axis L when a rotary motion is transmitted to the Seilendbefestigung 50 via the cable 7, as indicated in Fig. 5 by the double arrow 46.

The thrust bearing 63 is shown in FIG. 5 as a rolling bearing. A corresponding function can of course be achieved with other types of thrust bearings, such as plain bearings.

• einen Träger 65.1 für eine um die Achse 65.4 drehbare erste Welle 65.3,
• eine Befestigung 65.2 zur Befestigung des Trägers 65.1 an der Tragstruktur 2,
• eine auf der Welle 65.3 sitzende, um die Achse 65.4 drehbare zweite Welle 65.5, welche entlang der Achse 65.6 angeordnet ist und
• einen auf der zweiten Welle 65.5 drehbar angeordneten Träger 65.7 für die Basis 61.

The pivoting mechanism 65 is formed as shown in FIGS. 5 and 6 as a universal joint and allows pivoting of the base 61 and thus the axis L about two intersecting axes 65.4 and 65.6. The pivot mechanism 65 includes:

• a carrier 65.1 for a first shaft 65.3 rotatable about the axis 65.4,
• a fastening 65.2 for fastening the carrier 65.1 to the supporting structure 2,
• a seated on the shaft 65.3, rotatable about the axis 65.4 second shaft 65.5, which is disposed along the axis 65.6 and
• a support 65.7 rotatably mounted on the second shaft 65.5 for the base 61st

The base 61 is fixed to the carrier 65.7 such that the axis L extends both about the axis 65.4 and about the axis 65.6, i. pivoted in two dimensions (as indicated by double arrows on the axes 65.4 and 65.6 in Figure 5. The axis L is arranged such that the axes L, 65.4 and 65.6 intersect at a common point of intersection (as in Figure 5) and axis 6 can thus oscillate about the point of intersection of the axes 65.4 and 65.6.

The Seilendbefestigung 50 is attached to the rotatable portion 62 of the pivot bearing 60 such that the pivot bearing 60 assumes a stable equilibrium position when the tensile force F along the axis L - that is axially - is introduced into the pivot bearing 60. If the direction of the tensile force F or the angle α is changed, then the axis 6 is pivoted about the axes 65.4 and 65.3 or the intersection of the axes 65.4 and 65.3 until the axis L again assumes a new equilibrium position, that is, the axis L is aligned with the direction of the tensile force F. The pivot bearing 60 can always take the respective equilibrium position, provided that the friction between the carrier 65.1 and the shaft 65.3 and / or the friction between the shaft 65.5 and the carrier 65.7 is sufficiently small. In general, the friction between said components of the pivot mechanism 65 can be selected so that the axis L is aligned in the direction of the tensile force F or in the longitudinal direction of the cable section 7.1 or the longitudinal direction of the cable section 7.5.

• eine Bremstrommel 71, welche starr mit dem drehbaren Teil 62 verbunden und derart angeordnet ist, dass sich die Bremstrommel 71 jeweils um ihre Mittelachse dreht, wenn das drehbare Teils 62 um die Achse L gedreht wird;
• einen Bremsklotz 72, der mit der Aussenseite der Bremstrommel 71 in Kontakt gebracht werden kann, um die Bremstrommel 71 mit einer vorgegebenen Bremskraft F_B zu beaufschlagen und gegebenenfalls eine Drehbewegung des drehbaren Teils 62 zu bremsen; und
• eine Kontrollvorrichtung 75 zur Kontrolle der Bremskraft F_B.

With the braking device 70 is a rotational movement rope 7 braked at the rope fixation point 12 and the cable fix point 13. The brake device 70 includes:

• a brake drum 71 which is rigidly connected to the rotatable member 62 and arranged such that the brake drum 71 rotates about its center axis each time the rotatable member 62 is rotated about the axis L;
• a brake pad 72 that can be brought into contact with the outside of the brake drum 71 to apply a predetermined braking force F _B to the brake drum 71 and, if necessary, to brake a rotational movement of the rotatable part 62; and
• a control device 75 for controlling the braking force F _B.

• eine Stellschraube 75.1,
• einen Halter 75.2 für die Stellschraube 75.1, wobei der Halter 75.2 an der Basis 61 der Drehlagerung 60 fixiert ist und die Stellschraube 75.1 in ihrer Längsrichtung in einer im Halter 75.2 bereitgestellten Gewindebohrung geführt ist,
• eine Feder 75.3, die mit dem Bremsklotz 72 und einem dem Bremsklotz 72 zugewandten Ende der Stellschraube 75.1 in Kontakt steht.

The control device 75 comprises:

• a set screw 75.1,
• a holder 75.2 for the adjusting screw 75.1, wherein the holder 75.2 is fixed to the base 61 of the rotary bearing 60 and the adjusting screw 75.1 is guided in its longitudinal direction in a threaded hole provided in the holder 75.2,
• a spring 75.3, which is in contact with the brake pad 72 and a brake block 72 facing the end of the screw 75.1.

The brake drum 71, the brake pad 72, the adjusting screw 75.1 and the spring 75.3 act together as follows. The adjusting screw 75.1 serves both to guide the brake pad 72 and to control the braking force F _B acting on the brake drum 71. In order to ensure a guidance of the brake pad 72, the brake pad 72 is provided on the side facing away from the brake drum 71 with a bore 72.1, which is arranged so that a longitudinal portion of the screw 75.1 protrudes into the bore 72.1, and their diameter so to the dimensions the adjusting screw 75.1 is adapted, that the brake pad 72 is guided in the longitudinal direction of the adjusting screw 75.1 with some play. The spring 75.3 is arranged in the bore 72.1 so that the longitudinal extent of the spring 75.3 can be changed by adjusting the screw 75.1 to tension the spring 75.3 and to produce a force acting in the longitudinal direction of the spring 75.3 spring force. With this spring force is the brake pad 72 is pressed against the brake drum 71. By adjusting the adjusting screw 75.1 in its longitudinal direction, therefore, the braking force F _B acting on the brake drum 71 can be varied and thus controlled.

• Ist die Stellschraube 75.1 so eingestellt, dass die Feder 75.3 nicht gespannt und die Bremstrommel 71 folglich nicht gebremst ist, so kann der drehbare Teil 62 jeder Drehbewegung des Seilabschnitts 7.1 bzw. des Seilabschnitts 7.5 um die Achse L frei folgen. Auf das drehbare Teil 62 wirkt in diesem Fall kein Torsionsmoment.
• Ist die Stellschraube 75.1 so eingestellt, dass die Bremstrommel 71 mit einer Bremskraft F_B beaufschlagt ist, so legt die Bremskraft F_B eine Obergrenze T_max(F_B) für ein Torsionsmoment fest, das auf das drehbare Teil 62.1 bezüglich der Achse L wirken kann, ohne dass das drehbare Teil 62 gegenüber der Basis 61 gedreht wird. T_max ist umso grösser, je grösser die Bremskraft F_B ist. Falls auf das drehbare Teil 62 ein Torsionsmoment wirkt, dessen Wert T_max überschreitet, kann die Bremskraft überwunden und das drehbare Teil 62 gegenüber der Basis 61 gedreht werden. Durch Beaufschlagung der Bremstrommel 71 mit einer vorgegebenen Bremskraft F_B kann der Seilabschnitt 7.1 bzw. der Seilabschnitt 7.5 unter einem vorgegebenen Torsionsmoment T_max gehalten werden.
• Die Bremsvorrichtung 75 kann verwendet werden, das auf den Seilabschnitt 7.1 am Seilfixpunkt 12 wirkende Torsionsmoment bzw. das auf den Seilabschnitt 7.5 am Seilfixpunkt 13 wirkende Torsionsmoment wie folgt zu kontrollierten. Wenn das Seil 7 drehungsfrei ist, dann ist es vorteilhaft, wenn die Bremstrommel 71 nicht mittels der Bremsvorrichtung 75 mit einer Bremskraft beaufschlagt wird (F_B =0). Da das Seil voraussetzungsgemäss drehungsfrei ist, kann es allein unter der Wirkung einer Zugkraft nicht verdreht werden. Verdrehungen bzw. Torsionsmomente, die bei einer Beförderung der Lastträger des Aufzugs zwischen den Seilfixpunkten 12 und 13 in das Seil eingeleitet werden können, belasten das Seil nicht übermässig, da das Seil 7 an den Seilfixpunkten 12 bzw. 13 frei drehbar gehalten ist. Falls aber das Seil 7 nicht drehungsfrei ist und an den Seilfixpunkten 12 bzw. 13 frei drehbar gehalten ist, dann wird das Seil unter der Wirkung der auf das Seil wirkenden Zugkraft F aufgedreht, selbst wenn Lastträger des Aufzugs nicht befördert werden und deshalb keine Verdrehungen bzw. Torsionsmomente zwischen den Seilfixpunkten 12 und 13 in das Seil 7 eingeleitet werden. Falls das Seil 7 nicht drehungsfrei ist, dann kann mittels der Bremsvorrichtung 7 ein Aufdrehen des Seils 7 verhindert werden, indem die Bremstrommel 71 mit einer Bremskraft (F_B > 0) beaufschlagt und der Seilabschnitt 7.1 bzw. 7.5 unter einem vorgegebenen Torsionsmoment gehalten wird. Das Torsionsmoment kann so gewählt werden, dass ein Aufdrehen des Seils verhindert wird. Bevorzugt wird die Bremskraft so gewählt, dass der Seilabschnitt 7.1 am Seilfixpunkt 12 bzw. der Seilabschnitt 7.5 am Seilfixpunkt 13 unter einem zudrehenden Torsionsmoment gehalten wird. Das Torsionsmoment kann so limitiert werden, dass das Seil 7 nicht übermässig belastet wird. Auf diese Weise kann das Seil 7 selbst dann schonend gehalten werden, wenn es aufgrund seiner Konstruktion nicht drehungsfrei ist.

The brake device 70 can be operated as follows:

• If the set screw 75.1 is set such that the spring 75.3 is not tensioned and the brake drum 71 is consequently not braked, then the rotatable part 62 can freely follow any rotational movement of the cable section 7.1 or of the cable section 7.5 about the axis L. In this case, no torsional moment acts on the rotatable part 62.
• If the adjusting screw 75.1 is set so that the brake drum 71 is acted upon by a braking force F _B , the braking force F _B defines an upper limit T _max (F _B ) for a torsional moment which can act on the rotatable part 62.1 with respect to the axis L. without rotating the rotatable member 62 with respect to the base 61. T _max is greater, the greater the braking force F _B. If a torsional moment whose value exceeds T _max acts on the rotatable member 62, the braking force can be overcome and the rotatable member 62 rotated relative to the base 61. By loading the brake drum 71 with a predetermined braking force F _B , the cable section 7.1 or the cable section 7.5 can be held below a predetermined torsional moment T _max .
• The brake device 75 can be used to control the torsion moment acting on the cable section 7.1 at the cable tie point 12 or the torsional moment acting on the cable section 7.5 at the cable tie point 13 as follows. If the cable 7 is free of rotation, then it is advantageous if the brake drum 71 is not acted upon by the braking device 75 with a braking force (F _B = 0). Since the rope is according to the assumption rotation-free, it can not be twisted alone under the effect of a tensile force. Twists or torsional moments that can be introduced into the rope during carriage of the load carrier of the elevator between the cable fixing points 12 and 13, do not overload the rope excessively, since the rope 7 is held freely rotatably on the cable fixing points 12 and 13 respectively. But if the rope 7 is not free of rotation and is freely rotatably held at the rope fixing points 12 and 13, then the rope is turned up under the action of the force acting on the rope tension F, even if load carriers of the elevator are not promoted and therefore no twists or Torsional moments between the cable fixing points 12 and 13 in the Rope 7 are initiated. If the cable 7 is not free of rotation, then the cable 7 can be prevented from being turned up by applying a braking force (F _B > 0) to the brake drum 71 and holding the cable section 7.1 or 7.5 under a predetermined torsional moment. The torsional moment can be chosen so that untwisting of the rope is prevented. Preferably, the braking force is selected so that the cable section 7.1 is held at the cable fix point 12 or the cable section 7.5 at the cable fix point 13 under a twisting torsional moment. The torsional moment can be limited so that the rope 7 is not overloaded excessively. In this way, the rope 7 can be kept gentle even if it is not rotation-free due to its construction.

The braking device 75 according to FIG. 5 can be variously modified within the scope of the invention. For example, the size of the braking force F _B could be changed and / or controlled by electronic means. Alternatively, other parts that are moved during a rotational movement of the cable 7, the braking force F _B could be applied, for example, the cable section 7.1 or the cable section 7.5 and / or the Seilendbefestigung 50th

7 comprises the cable end fastening 50 for the cable end 7 'or 7 ", the rotary bearing 100 for the cable end fastening 50 and a drive 80. The drive 80 and parts of the rotary bearing 100 are shown in FIG. 7 presented in three different perspectives.

The drive 80 is used - as will be explained below - to control a rotational movement of the rope 7 or to control a force acting on the rope 7 at the rope fixing point 12 or at the rope fixing point 13 torsional moment.

• eine Basis 61,
• einen an der Tragstruktur 2 befestigten Schwenkmechanismus 90, an der die Basis 61 befestigt ist, um ein Schwenken der Basis 61 gegenüber der Vertikalen V zu ermöglichen,
• ein um die Achse L drehbares Teil 62, welches über ein Axiallager 63 auf die Basis 61 derart gestützt ist, dass die Achse L gegenüber der Basis 61 starr angeordnet ist.
  Die Seilendbefestigung 50 ist an dem drehbaren Teil 62 befestigt und kann somit ebenfalls um die Achse L gedreht werden, wenn über das Seil 7 eine Drehbewegung auf die Seilendbefestigung 50 übertragen wird, wie in Fig. 7 durch den Doppelpfeil 46 angedeutet ist.

The pivot bearing 100 includes:

• a base 61,
• a pivoting mechanism 90 fixed to the support structure 2, to which the base 61 is attached to allow pivoting of the base 61 with respect to the vertical V,
• a rotatable about the axis L part 62, which is supported via a thrust bearing 63 on the base 61 such that the axis L is rigidly arranged relative to the base 61.
  The Seilendbefestigung 50 is attached to the rotatable member 62 and thus can also be rotated about the axis L when a rotary motion is transmitted to the Seilendbefestigung 50 via the cable 7, as indicated in Fig. 7 by the double arrow 46.

The thrust bearing 63 is shown in FIG. 7 as a rolling bearing. A corresponding function could of course also be achieved with other types of thrust bearings, for example with plain bearings.

• Eine Kugelpfanne 91 mit einer sphärischen Auflagefläche 91.1,
• ein auf der Auflagefläche 91.1 drehbar gelagertes Kugelteil 92 und
• eine Befestigung 64 zur Befestigung der Basis 61 an dem Kugelteil 92.

The swivel mechanism 90 is designed according to FIG. 7 as a ball joint and makes it possible to pivot the base 61 and thus the axis L. The swivel mechanism 90 comprises:

• A ball socket 91 with a spherical bearing surface 91.1,
• a rotatably mounted on the support surface 91.1 ball part 92 and
• an attachment 64 for fixing the base 61 to the ball part 92.

The ball socket 91 is arranged on the support structure 2 such that the ball socket 91 is supported on the periphery of a through hole 2.1 formed in the support structure 2. The attachment 64 is rod-shaped and attached to the ball member 92 such that the attachment 64 is disposed along the axis L and protrudes through an opening 91.2 at the bottom of the ball socket 91 and the through hole 2.1. Due to the shape of the ball socket 91, the axis L is pivotable about the center of curvature of the support surface 91.1 in two dimensions.

The Seilendbefestigung 50 is attached to the rotatable portion 62 of the pivot bearing 100 such that the ball member 92 and thus the base 61 each assume a stable equilibrium position when the tensile force F along the axis L - that is axially - is introduced into the pivot bearing 100. If the direction of the tensile force F or the angle α is changed, then the axis L is pivoted about the center of curvature of the support surface 91.1 until the axis L assumes a new equilibrium position, such that the axis L is aligned with the direction of the tensile force F. The pivot bearing 100 can always take the respective equilibrium position, provided that the friction between the ball member 92 and the ball socket 91 is sufficiently small. In general, the friction between the ball member 92 and the ball socket 91 can be selected so that the axis L in the direction of the tensile force F and / or in the longitudinal direction of the cable section 7.1 or the longitudinal direction of the cable section 7.5 is aligned.

The drive 80 is secured by a bracket 85 to the attachment 64. It is designed as a belt drive and serves for the transmission of a torsional moment on the rotatable part 62 of the rotary bearing 100. The drive 80 comprises a motor 81 (which can be driven by electrical means, for example), a (driving) belt pulley 82 seated on a drive shaft of the motor 81 (driven) pulley 83 fixed to the rotatable member 62, a belt 84 spanning the pulleys 82 and 83 and (not shown in Fig. 7) a control device for controlling the torque transmittable to the pulley 82 with the motor 81.

By a suitable control of the motor 81 can be achieved that the rotatable part 62 of the pivot bearing 100 relative to the base 61 rotates. In this way, the extent of a rotation of the cable section 7.1 or the cable section 7.5 can be actively controlled by a suitable control of the motor 81. In operation, the drive 80 is controlled by means of the control device so that the cable section 7.1 at the rope fixation point 12 or the rope section 7.5 at the rope fixation point 13 is under a torsional moment, which is directed so that it on the cable section 7.1 or on the cable section 7.5 zudrehend acts, and its size is limited so that the rope 7 is not damaged. In this way, the cable section 7.1 or the cable section 7.5 can be kept under a twisting torsional moment. The drive 80 can be regulated, for example, so that the torsional moment acting on the cable section 7.1 or the torsional moment acting on the cable section 7.5 during operation of the elevator 1 is constant. In this way, the aufdrehend acting rotations, which may be initiated due to the Schrägzugs on the drive roller 20 and the guide rollers 11.1, 11.2 and 11.3 in the cable section 7.1 or in the cable section 7.5, by corresponding opposite rotations, by means of the Drive 80 can be initiated at the rope fixation point 12 in the rope section 7.1 or at the rope fixation point 13 in the rope section 7.5 compensated.

The drive 80 can be modified in various ways within the scope of the invention. He does not necessarily have to be designed as a belt drive. The described functions of the drive 80 can also be realized with other principles known from drive technology. According to a further variant, the drive 80 can be arranged so that the rotatable part 62 and / or the cable section 7.1 or 7.5 and / or the respective cable end connection 50 can be acted upon by a torsional moment in order to keep the cable section 7.1 or the cable section 7.5 under a torsional moment that acts to turn.

It is also possible to replace the drive 80 according to FIG. 7 by a space-saving variant. For example, it is possible to properly integrate a motor into the pivot bearing 100. For this purpose, the base 61 and the rotatable part 62 of the pivot bearing 100 can be designed so that between the base 61 and the rotatable member 62 enough space for receiving a motor (with or without gear), with a torsional moment on the rotatable Part 62 is transferable, and where appropriate, sufficient space for a suitable control for the engine results.

The elevator car 3 and the counterweight 5 can also be suspended on a plurality of cables 7, which can be guided, for example, via the drive roller 20 and the deflection rollers 11. In this case, the rope fixing points 12 and 13 can be modified accordingly: The rope ends of the additional ropes can - like the rope 7 - each have a cable end connection 50 and a rotary bearing 40 or 60 or 100 attached to the support structure 2 and if necessary, such as shown in Fig. 5 and 7, be equipped with a braking device 70 and 80 with a drive. The various ropes can be influenced to varying degrees by diagonal pull on the drive roller 20 and the guide rollers 11. It may therefore be expedient to hold the different ropes at the respective ends of the rope under different torsional torques - according to the circumstances of each individual case. Furthermore, the cable end connections 50 can be arranged in the respective pivot bearings so that they are movably mounted along the respective axis L against the restoring force of a spring.

The pivot bearings 40, 60 and 100 may also be modified within the scope of the invention. Instead of the pivoting mechanisms 65 and 90, any pivoting mechanism may be used which allows automatic alignment of the axis L in a direction dependent on the direction of the pulling force introduced into the respective pivot bearing.

Claims (11)

Cable tie point (12, 13) for fastening at least one cable (7), each having a cable end attachment (50) for a cable end (7 ', 7 ") of the respective cable (7) and each having a rotary bearing (40, 60, 100) for the respective cable end attachment (50), wherein each pivot bearing (40, 60, 100) permits a rotation (12 ', 13', 46) of the respective cable end attachment (50) about an axis (L ₁₂ , L ₁₃ , L),
characterized in that
the axis (L ₁₂ , L ₁₃ , L) by a force acting on the rope (7) tensile force (F ₁₂ , F ₁₃ , F) is alignable. A rope fixation point according to claim 1, characterized in that the axis (L ₁₂ , L ₁₃ , L) in the direction of a tensile force acting on the rope (F ₁₂ , F ₁₃ , F) and / or in the longitudinal direction of a section adjacent to the rope fixation point (7.1, 7.5) of the rope (7) is alignable. Rope fix point according to one of claims 1 or 2, characterized in that
the pivot bearing (40, 60, 100) comprises a thrust bearing (41, 43, 44, 63) having a part (43, 62) rotatable about the axis, the end fitting (50) being connected to the rotatable part (43, 62) is. Rope fix point according to claim 3, characterized in that
the rotary bearing (60, 100) a pivot mechanism (65, 90) for the axial bearing (63) for orientation of the axis (L _12, L _13, L) within an angular range. Rope fixation point according to claim 3, characterized in that the thrust bearing is an axial pendulum bearing (41, 43, 44), wherein the rotatable part (43) is mounted oscillatingly. A rope fixation point according to claim 4, characterized in that the pivoting mechanism (65, 90) comprises: a hinge (65, 90) for pivoting the thrust bearing about a point or a joint (65) for pivoting the thrust bearing (63) about a pivot axis (65.4, 65.6) or a hinge (65) for pivoting the thrust bearing about a first pivot axis (65.4) and a second, not parallel to the first pivot axis (65.4) arranged second pivot axis (65.6). A rope fixation point according to claim 6, characterized in that the joint is a universal joint (65) or a ball joint (90). Cable fix point according to one of claims 1-7, characterized
in that means (70, 80) are provided for checking a torsional moment acting on the cable at the cable end. A rope fixation point according to claim 8, characterized
in that the means comprise a brake device (70) for braking a rotational movement of the cable
and / or that the means comprise a drive (80) for transmitting a torsional moment to the rotatable part (43, 62) and / or the cable end attachment (50) and / or the cable (7, 7.1, 7.5). Elevator (1) for conveying at least one load carrier (3, 5) by means of at least one rope (7) movable in its longitudinal direction, with a cable fixing point (12, 13) for a cable end (7 ', 7 ") of the respective cable (7) according to any one of claims 1-9, wherein the respective cable (7) at the cable end (7 ', 7 ") is under a tensile force (F ₁₂ , F ₁₃ , F) whose direction depends on a position of the load carrier (3 , 5) is variable, and the axis (L ₁₂ , L ₁₃ , L) by the tensile force (F ₁₂ , F ₁₃ , F) is alignable. Elevator according to claim 10, wherein the axis (L ₁₂ , L ₁₃ , L) in the direction of the tensile force (F ₁₂ , F ₁₃ , F) and / or in the longitudinal direction of a section adjacent to the cable hinge point (12, 13) (7.1 , 7.5) of the rope (7) is alignable.

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