EP2435351B1 - Load bearing medium attachment in a lift assembly - Google Patents

Description

The present invention relates to an elevator installation, in which at least one elevator car and at least one counterweight are moved in opposite directions in an elevator shaft, wherein the at least one elevator car and the at least one counterweight are guided on guide rails and carried by means of suspension. The present invention relates in particular to the stationary fastening of suspension element ends, a so-called suspension element attachment.

A support means attachment is typically arranged on a fixed structure (building part or guide rails supported console or the like) by a Tragmittelendverbindung is held by a pull rod or a tie rod which is supported on the fixed structure. As a support, a compression spring may be provided which serves as a length compensation for the support means.

The suspension element end connection is, for example, a connection acting on the wedge principle and may be part of a stationary support means attachment or be part of a arranged on the elevator car suspension means attachment and / or be part of a arranged on the counterweight suspension means attachment. The former is usually the case with a 2: 1 cable guide, the latter for example with a 1: 1 cable guide.

Depending on the dimensioning of the elevator installation or arrangement of guide rails, traction sheave, elevator car or counterweight, the suspension element can occur when describing the maximum travel, both in 2: 1 and in 1: 1 cable guides or in principle further cable guide types the elevator car or the counterweight is deflected from the lowest shaft position to the highest shaft position of the vertical or the perpendicular. It can also be realized from the outset inclined guide of the support means, for example, because you want to exploit the horizontal force component of the oblique support means guide as a the elevator car or the counterweight to the guide rails approaching force in a so-called backpack suspension.

The deflection of the support means from the vertical away, or from the vertical, which occurs basically in all types of suspension in which the Tragmittelbefestigungen, the outer diameter of the idlers and the outer diameter of the traction sheave are not aligned vertically to each other, has the consequence that the support means be bent more or less at the Tragmittelendverbindung and the pull rod during operation of the elevator system depending on the height position of the elevator car or the counterweight.

This buckling stress in turn can permanently represent an undesirable load or material fatigue for the suspension element, which leads to an early replacement of the suspension element, but at least to a control and maintenance requirement or even to a breakage of the suspension element.

In general, to avoid horizontally occurring forces manifesting as bending or shearing forces in a pull rod, pairs of washers are known in which a convex shaped side of one washer is fitted into a corresponding concave shaped side of the other washer. However, a disadvantage of such solutions that the pivotability is limited only to low deflection angle and subject to high frictional forces.

In fact, in such solutions, the unwanted horizontally occurring forces are no longer absorbed solely by the material of the tie rod or its bending strength, but by the frictional forces only compensated. The overall situation of the forces occurring in relation to one another is thus not satisfactorily resolved. Lateral, ie horizontally acting force components still occur. A possible free pivoting or a possible free adaptation to the deflection angle - while full transmission of the vertical holding force - is thus not achieved.

Due to the high frictional forces it can be observed in these solutions that only a dynamic adaptation takes place, i.e., when the elevator car or the counterweight moves during operation or the deflection angle is just changing, then the convex concave washers adapt to the deflection. Static, on the other hand, i.e., when the elevator car or the counterweight stand, no adaptation takes place because of the high friction between the convex and the concave surfaces of the washers.

As a result, friction is minimized at this point by treating lubricants and / or the surfaces or by using special low-friction and self-lubricating plastics. This, in turn, makes the solutions costly and time-consuming, although in the end they are always only a compromise on the mechanical basis.

The patent US B1-6,341,669 discloses to avoid the buckling load and to generate constant deflection angle of the suspension means on the two sides of the elevator car, a stationary, but pivotable Tragmittelbefestigung that is identical in mechanical principle. A hemisphere or a shaft in the form of a longitudinally halved cylinder is arranged in a correspondingly concavely shaped seat. This seat is to keep the friction as low as possible, preferably from a technical plastic, an acetal plastic from Dupont made by Delrin®.

The object of the present invention is to propose a pivotable suspension means fastening, which is optimized with regard to the friction forces occurring, but also with respect to the pivot angle. In addition, it should be distinguished by technical simplicity, low maintenance and cost efficiency.

The solution to the problem consists initially in the arrangement of a rolling body on a flat bearing surface of a holding plate.

The term rolling body is to be understood in the following a full cylinder or even a tube having at least one bore through which the pull rod is guided, which is fixed in extension of Tragmittelendverbindung. As with conventional Tragmittelbefestigungen also, a compression spring between the end of the tie rod and the holding plate is tensioned.

According to the present invention, however, the compression spring is preferably located on a fixing sleeve on the top of the rolling body and this latter is not arranged in a concave seat, but can roll freely on the flat support surface of the support plate.

As a result, the friction forces that occur in solutions according to the prior art between a convex footprint and a corresponding concave receiving virtually eliminated, there remains only a negligible contact friction of the rolling body on the support surface - hereinafter rolling surface - the holding plate. This negligible contact friction is no longer in the way of a preferably gentle and progressively growing or progressively falling adjustment of the deflection angle. Also an adjustment in static operation is thus possible.

The contact friction is preferably low due to hard surfaces of the rolling body and the rolling surface, so that advantageously additionally only a negligible material wear occurs.

In the context of the disclosure of the present invention, however, is also an embodiment variant in which to avoid lateral sliding movements of the rolling body on the rolling surface (and consequently a contact of the drawbar with the inner edges of the bore in the holding plate) straight surfaces are provided with desired high contact friction. Such surfaces can be realized for example with rubber-like materials or a corrugation or even a toothing. A corresponding rubber-like layer, be it on the rolling body or on the rolling surface or on both offers in addition to the avoidance of lateral sliding movements also the further advantage that a sound bridge is interrupted by the support means on the suspension means fixing and on the stationary arranged holding plate to the building.

Furthermore, according to the invention, the distance or the overall height of the bore for the drawbar is reduced by eliminating the concave seat to the overall height of the retaining plate itself. This advantageously allows a hole in the holding plate, which releases larger adjustment angle of the pull rod than conventional pivotable Tragmittelbefestigungen.

The bore in the retaining plate is preferably formed conical in that the bore on the rolling surface of the retaining plate has a diameter which is slightly larger than the outer diameter of the tie rod. At the bottom of the holding plate, so the rolling surface opposite, the diameter of the bore is larger. As a result, adjustment angles are achieved, which are significantly larger than in known solutions and, for example, in an angular range of ± 0-30 degrees lie, but preferably be ± 6 degrees. In principle, higher adjustment angles are advantageous for elevator systems with large delivery heights, but also for machine room-less elevator systems in which the elevator cage or the counterweight can be moved as close as possible to the stationary suspension element fastenings or as close as possible to the traction sheave.

The fact that the hole at the top of the holding plate, i. on the rolling surface for the rolling body is only slightly larger than the outer diameter of the drawbar, gives an advantage in the mounting of the suspension element attachment. Namely, it is not necessary, as in conventional Tragmittelbefestigungen to seek a central adjustment position and to align the convex footprint in the concave receiving center, because the inventive support means attachment is quasi self-centering.

A preferred higher stability of the flanks of the bore on the rolling surface of the holding plate can be achieved by the bore has at least two stepwise concentrically growing individual holes.

A further preferred embodiment variant of a support means fastening provides in the holding plate instead of a round hole before an oblong hole, which is arranged with its longitudinal direction in the deflection direction of the support means. As a result, an unhindered pivoting movement of the drawbar is ensured and almost any pivoting angle can be realized. The height of the retaining plate is irrelevant in this embodiment variant to achieve a wide adjustment angle. It can rather be high in favor of the stability of the retaining plate.

A still further embodiment variant according to the invention provides that the rolling surface of the rolling body in cross-section no round sectional contour, but having a flattened around the central location around cutting contour. This flattened cut contour preferably has the shape of a parabola, which is compressed by its power and / or by a fractional quotient. In terms of triviality, according to this design variant, the suspension element fastening according to the invention, like a standing block, develops a force which forces it back into the central position, which becomes greater the more the deflection angle increases. In this way, an adjustment possibility of Tragmittelbefestigung is realized by means of which small adjustments take place around the central location around unhindered, but as soon as the deflection angle threatens to assume a maximum, which claims the pull rod with shear forces, the rounding of the rolling body acts contrary to the opposite.

The described rounding of the rolling body thus also counteracts a lateral slipping or lateral tilting away of the pivotable suspension element attachment. The same can continue according to the invention - in combination with the flattened rounding or in combination with the previously disclosed concentric rounding - can be achieved with stops that are formed on demand on the flanks of the rounding.

A further embodiment variant of a suspension element attachment according to the invention is based on the assumption that a compression spring in the form of a helical spring naturally does not build up optimal lateral holding forces. The compression spring must also on the one hand include the drawbar with play, so that they can still compress or relax freely. On the other hand, the deflection movement is initiated due to the leverage laws by the longest lever, ie by the upper end of the pull rod. This upper end of the pull rod exerts a pressure on one side of the compression spring at a deflection of the support means and this side of the compression spring in turn initiates the rolling movement of the rolling body. This pressure transmission is the one force that causes the Mitschwenken the Tragmittelbefestigung according to the deflection and may take place only after the middle turns of the compression spring have been applied to the pull rod. This pressure transmission has in any case due to a more or less compressed state of the compression spring and due to the compelling storage of the compression spring with play around the tie rod, as well as the inherent poor lateral stability of springs inaccuracies.

By contrast, a significantly higher lateral stability than compression springs in the form of helical springs have gas springs or gas springs. Modern gas springs - such as those of the company Bansbach easylift GmbH from Lorch, Germany or for example those of the company Stabilus from Koblenz, Germany - are in addition to the high lateral stability continue to advantageously for high loads (up to 10500 N) with shorter spring travel - despite identical Spring rates - and thus usable at lower heights.

The gas spring can, in a manner similar to the previously disclosed embodiment variant with a helical compression spring, be arranged in a hollow pull rod. However, a preferred embodiment of a pivotable support means attachment with a gas spring provides that the support means with its Tragmittelendverbindung is fastened directly to the piston rod of the gas spring, preferably rotatably in a joint eye. The cylinder of the gas spring is supported directly on the top of the rolling body, which can optionally also be flattened. In this way, a pivotable Tragmittelbefestigung is realized, which is characterized by only three components and a direct and play-free transmission of the deflection movement of the support means to the pivotal movement of the suspension element attachment.

Another advantage of this embodiment variant of a pivotable suspension element attachment with a gas spring is that the force application point of the suspension element attachment for the support means is lower than in coil compression springs, in which the entire length of the coil compression spring must be taken for example with a mother and thus the force application point is located on this nut at the end of the pull rod. The lower force application point of a gas spring manifests itself advantageously in a lower height, which accommodates the design and construction of machine room-less elevator systems, and in smaller adjustment angles and lower tilt and buckling loads.

This last-described embodiment variant can optionally be further optimized by directly forming the cylinder of the gas spring, the rolling surface according to the invention and thus a separate rolling body is no longer required. This embodiment variant of a pivotable support means attachment with a gas spring thus consists only of the gas spring, which is supported on the plate, so only two components.

In the context of the disclosure of the present application, however, there is also a particularly simple and correspondingly cost-effective and furthermore inventive embodiment variant which dispenses with a force storage element at all. The pull rod is guided by a rigid or flexible support sleeve, which rests on the rolling body. The pull rod can form a head which, in turn, rests directly on the rolling body on the support sleeve or, according to a further simplified variant of the invention, and further according to the embodiment variant. Basically, the head of the drawbar can integrate the rolling body by the bottom of the tie rod head directly forms the rolling body rolling surfaces.

As already mentioned above, the described embodiments of inventive pivotable Tragmittelbefestigungen both for fixed Tragmittelbefestigungen, as well as fortifications of a Tragmittelendverbindung to the elevator car and / or on the counterweight suitable. From this, combinations are possible, for example in an elevator installation, in which a 2: 1 cable guide is provided for the counterweight and a 1: 1 cable guide for the elevator car. Such an elevator installation would then disclose both at least one pivotable suspension element attachment according to the invention at at least one fixed attachment point, and at least one pivotable suspension element attachment according to the invention at at least one attachment point of the elevator cage.

The inventive pivotable Tragmittelbefestigungen can be implemented individually, but also - with individual holding plates and individual rolling elements or even with one-piece holding plates and one-piece rolling elements - be provided for a plurality of support means, which are for example performed in parallel.

Further or advantageous embodiments of an inventive pivotable support means attachment form the subject of the dependent claims.

The invention will be explained symbolically and by way of example with reference to figures. The figures are described coherently and comprehensively. The same reference symbols denote the same components, reference symbols with different indices indicate functionally identical or similar components.

• Fig. 1 eine schematische Darstellung einer Aufzugsanlage gemäss Stand der Technik mit einer 2:1-Seilführung für eine Aufzugskabine und ein Gegengewicht;
• Fig. 2 eine schematische Detaildarstellung einer schwenkbaren Tragmittelbefestigung gemäss Stand der Technik;
• Fig. 3a eine schematische Detaildarstellung einer erfindungsgemässen schwenkbaren Tragmittelbefestigung für drei parallel geführte Tragmittel;
• Fig. 3b eine schematische und geschnittene Detaildarstellung einer geringfügig andersartigen, aber prinzipiell identischen Ausgestaltungsvariante einer erfindungsgemässen schwenkbaren Tragmittelbefestigung;
• Fig. 4a eine schematische Darstellung eines erfindungsgemässen Rollkörpers;
• Fig. 4b eine schematische Darstellung einer Ausgestaltungsvariante des erfindungsgemässen Rollkörpers mit einer Verzahnung;
• Fig. 4c eine schematische Darstellung einer weiteren Ausgestaltungsvariante des erfindungsgemässen Rollkörpers;
• Fig. 5 eine schematische Darstellung einer weiteren Ausgestaltungsvariante einer erfindungsgemässen schwenkbaren Tragmittelbefestigung mit einer Gasdruckfeder und
• Fig. 6 eine schematische Darstellung einer weiteren Ausgestaltungsvariante einer erfindungsgemässen schwenkbaren Tragmittelbefestigung mit einer Stützhülse statt einem Kraftspeicherelement.

It show here

• Fig. 1 a schematic representation of an elevator system according to the prior art with a 2: 1 cable guide for an elevator car and a counterweight;
• Fig. 2 a schematic detail of a pivotable support means attachment according to the prior art;
• Fig. 3a a schematic detail of an inventive pivotable support means attachment for three parallel guided support means;
• Fig. 3b a schematic and sectional detail of a slightly different, but in principle identical embodiment variant of an inventive pivotable support means attachment;
• Fig. 4a a schematic representation of a rolling body according to the invention;
• Fig. 4b a schematic representation of an embodiment variant of the inventive rolling body with a toothing;
• Fig. 4c a schematic representation of a further embodiment variant of the inventive rolling body;
• Fig. 5 a schematic representation of another embodiment variant of an inventive pivotable support means attachment with a gas spring and
• Fig. 6 a schematic representation of another embodiment variant of an inventive pivotable support means attachment with a support sleeve instead of a force storage element.

Fig. 1 shows an elevator installation 100, as known from the prior art. In an elevator shaft 1, an elevator car 2 is movably arranged, which is connected via a support means 3 with a movable counterweight 4. The support means 3 is driven in the operation of the elevator system 100 with a traction sheave 5 of a drive unit 6, which are arranged in the uppermost region of the elevator shaft 1 in a machine room 12. The elevator car 2 and the counterweight 4 are guided by extending over the shaft height guide rails 7a and 7b and 7c.

The elevator car 2 can serve at a delivery height h a top floor 8, further floors 9 and 10 and a bottom floor 11. The elevator shaft 1 is formed by shaft side walls 15a and 15b, a shaft ceiling 13 and a shaft bottom 14 on which a shaft bottom buffer 22a for the counterweight 4 and two shaft bottom buffers 22b and 22 c are arranged for the elevator car 2.

The support means 3 is fixedly attached to the shaft ceiling 13 or fixed to the shaft side wall 15a and guided parallel to the shaft side wall 15a to a support roller 17a for the counterweight 4. From here again, the support means 3 is guided back over the traction sheave 5, further to a support roller 17b for the elevator car 2 and to a second fixed attachment to the shaft ceiling 13 or to the shaft side wall 15b.

In the stationary fasteners, the suspension element 3 is fastened in each case with a suspension element end connection 19a or 19b to a pull rod 18a or 18b. The tie rods 18a and 18b are, reinforced with a respective compression spring 21a and 21b, supported on a respective stationary holding plate 20a and 20b. The holding plates 20a and 20b are arranged, for example, on the shaft side walls 15a and 15b, on the shaft ceiling 13, on at least one guide rail 7 or on a drive console, not shown.

The counterweight 4 is shown by a solid line in a lowest shaft position PG _t and accordingly the elevator car 2 in a highest shaft position PK _h . Dashed lines show the counterweight 4 in a highest shaft position PG _h and the elevator car 2 in a lowest shaft position PK _t . Particularly in the case of the stationary fastening of the cabin-side section of the suspension element 3, the deepest shaft position PK _{t of} the elevator car 2 and the highest shaft position PK _{h of} the elevator car 2 illustrate that the suspension element 3 forms a maximum deflection angle AW _max .

The Fig. 2 schematically shows a known from the prior art pivotable support means attachment 33. An unillustrated Tragmittelendverbindung is connected to a pull rod 18c, which through a bore 24 in a Holding plate 20c, further guided by a further bore 24a in a hemisphere 23 and through the turns of a helical compression spring 21c. The helical compression spring 21c is fixed with washers 26, a nut 27, a lock nut 28 and a locking pin 29 against a bearing surface 30 of the hemisphere 23. The hemisphere 23 is seated in a concavely shaped seat 25. Pivoting the Tragmittelbefestigung 33 corresponding to a deflection angle AW ₁ between a vertical S and an axis A of the tie rod 18c on the one hand high frictional forces between the surface of the hemisphere 23 and the concave surface of the seat 25 and on the other hand is limited by contact of the tie rod 18c on the flanks of the bore 24.

In Fig. 3a is an inventive pivotable suspension means attachment 33a for three parallel guided support means 3a-3c shown in perspective. The three support means 3a-3c are each secured to a support means end connection 19c-19e to a respective drawbar 18d-18f, which are guided through bores 24b-24d in a stationarily arranged holding plate 20d and corresponding bores (not shown) in a rolling body 31a.

Deflection movements of the support means 3a-3c and the Tragmittelendverbindungen 19c-19e lead to a pivoting movement of the tie rods 18d-18f and this pivoting movement in turn leads to a rolling of the rolling body 31a on a flat rolling surface 34 of the holding plate 20d.

The rolling body 31a further comprises a support surface 30a for lower fixing sleeves 32a-32c for each screw compression spring 21d-21f, which in turn by means of an upper fixing sleeve 35a-35c, a nut 27a-27c, a lock nut 28a-28c and a Splint 29a-29c is mounted under preload.

The Fig. 3b shows a schematic and sectioned detail of a novel pivotable support means attachment 33b, which is pivoted about the deflection angle AW ₁ , which is formed between the vertical S and the axis A of a pull rod 18g. The pull rod 18g is guided through a bore 24e in a holding plate 20e and through a further bore 24f in a rolling body 31b.

The hole 24e in the holding plate 20e consists of two individual holes with different diameters, so that the pull rod 18g can describe larger adjustment without abutting the flanks of the bore 24e.

The rolling body 31b, in contrast to the rolling body 31a of the Fig. 3a no support surface for a lower fixing sleeve 32d or for a helical compression spring 21g. However, the rolling body 31b has a rolling body rolling surface 36, which rolls on a rolling surface 34a of the holding plate 20e during pivoting movements of the carrying means attachment 33b.

The lower fixing sleeve 32d may optionally also be designed such that its lowest diameter below the collar comprises the pull rod 18g along the entire length of the bore 24f, preferably by means of a clearance fit which allows the pull rod 18g to move along its axis A, but as little as possible lateral movements transversely to the axis A releases.

The Fig. 4a shows schematically and in a partially sectioned detailed representation of the operation of a suspension device according to the invention 33c and a rolling body 31c according to the invention with a concentric rolling body rolling surface 36a when rolling on a flat rolling surface 34b of a holding plate 20f. The rolling body 31c is shown in full line in a vertical position in which the vertical S and the axis A coincide. The rolling body 31c is thus in one Contact point 37. As soon as a pivoting movement takes place in accordance with a deflection angle AW ₂ of preferably 6 degrees, the rolling body 31c assumes a position which is shown with a dotted line. In this new position of the rolling body 31c, the rolling body 31c is in a new contact point 37 ', which is shifted to the left. It can be seen that a tilted axis A 'has hardly shifted its intersection with the line representing the rolling surface 34b of the holding plate 20f. This is an indication that a transfer of the holding force for the support means along the axis A 'is ensured even in this position and any reset torque remains negligible.

In the Fig. 4b is a schematic and sectional detail of an embodiment variant of a pivotable support means fixing 33d shown in favor of a pivoting of significantly more than 6 degrees lateral stabilizing interlocking teeth on a rolling body rolling surface 36b of a rolling body 31d and at the same time on a rolling surface 34c of a holding plate 20g having.

The Fig. 4c shows schematically and in a sectional detail representation of a further embodiment variant of an inventive pivotable support means attachment 33e. This embodiment variant is characterized by the fact that on a as before in the FIGS. 3a . 3b and 4a Planing surface 34d of a holding plate 20h, a rolling body 31e is supported, the rolling body rolling surface 36c is not concentric round, but centrally, ie, on both sides about an axis A1, the rolling body rolling surface 36c is flattened. In other words, the rolling member rolling surface 36c forms a central portion 38b having a radius R _B that is larger than the radii R _a and R _c of two sections 38a and 38c. The latter portions 38a and 38c flank the central portion 38b on both sides and merge seamlessly into the curvature of the central portion 38b. The two lateral sections 38a and 38c represent quasi two shoulders, which - as shown by dashed lines - upon reaching a deflection angle AW ₃ , toward an axis A1 ', with a progressively increasing restoring moment RM in the direction of original orientation of the support means attachment 33e act.

An exemplary mathematical function that represents the sectional contour of the rolling body rolling surface 36c according to the invention is a parabola that is compressed by its power and / or a fractional quotient. Such a mathematical function is, for example, f _(x) = ax ⁿ , where 0 <a <1 and n is an even number. For example, f _(x) = 0.1 x ² or f _(x) = 0.5 x ⁴ .

The Fig. 5 shows schematically and in a partially sectioned detailed representation of a further inventive embodiment variant of a pivotable support means attachment 33f with a gas spring 40, which comprises a cylinder 41 and a piston rod 42. The piston rod 42 preferably has at its lower end a hinge eye 43a in which the suspension element end connection is preferably pivotally mounted. Optionally, the cylinder 41 also has a joint eye 43b at its upper end, which can prove useful during initial assembly or disassembly if replaced, but can be retrofitted in favor of a low structural height of the suspension element attachment 33f.

The gas pressure spring 40 and the suspension element attachment 33f has a force application point KAP, which is significantly lower than the point of force application of the design variants with helical compression spring. In the case of the latter, it lies in the nut that grips the helical compression spring at the upper end of the drawbar. (See nuts 27a-27c on tie rods 18d-18f in FIG Fig. 3a .)

The cylinder 41 is supported on a bearing surface 30b, at or around a bore 24h of a rolling body 31f supported. The rolling body 31f may optionally also be formed directly in one piece with the cylinder 41 and has a rolling body rolling surface 36d, which can be unrolled in the manner disclosed so far on a flat rolling surface 34e of a holding plate 20i.

The holding plate 20i preferably has a bore 24g, which consists of a plurality of stepwise and concentrically arranged individual bores. This type of bore allows wide pivoting of the piston rod 42 with optimum material strength of the retaining plate 20i in the area around the bore 24g. As already mentioned, the bore 24 g can also be configured as a slot that coincides in its longitudinal direction with the deflection direction of the piston rod 42.

Furthermore, this embodiment variant has two stops 39a and 39b on the rolling body 31f, which block a deflection of the support means attachment 33f beyond certain angles. These stops 39a and 39b can also be combined with all previously shown design variants of rolling bodies 31.

In the Fig. 6 is shown schematically and in a partially sectioned detail representation of a further embodiment variant of an inventive pivotable support means attachment 33g. A pull rod 18h is guided through a bore 24i in a holding plate 20j, wherein the bore 24i is configured here in the form of a slot whose longitudinal direction coincides with the deflection of the pull rod 18h, which in turn corresponds to the drawing plane in the illustrated figure. In contrast to the previously shown centric bores, the slot 24i results on the one hand in increased pivoting angles, but on the other hand, another advantage: there are no more edges of a (round, centric) bore, which interlock with the edges of a bore 24j in the rolling body 31g could, because the slot 24i forms two webs, of which in the one shown Sectional view only a rear web 46 is visible, which intersects an axis A "of the drawbar 18h.

The drawbar 18h can, as in Fig. 3a shown fastened with nuts on a thread of the pull rod. Like in this one Fig. 6 However, the drawbar may also form a tie-rod head 45, with which it grips a support sleeve 44, which in turn is supported on a support surface 30c of a rolling body 31g. The support sleeve 44 may be made of rigid material, or else be made of a defined and preferably only slightly flexible material.

As already mentioned, however, a further embodiment variant according to the invention is also conceivable in which the tie rod head 45 is supported directly on the support surface 30c of the rolling body 31g or even a further embodiment variant in which the tie rod head 45 directly supports roller body rolling surfaces 36e and 36f formed.

Claims (15)

1. Suspension means attachment (33) for suspension means (3, 3a-3c) in an elevator installation (100), wherein the suspension means (3, 3a, 3b, 3c) are connected to suspension means end connections (19, 19a-19e) which are connected to pull rods (18a-18h), wherein each pull rod (18a-18h) is supported on a common rolling body (31a-31g) carried by a retaining plate (20a-20j) and is adaptable to deflections of the suspension means (3, 3a-3c) corresponding to a deflection angle (AW), wherein the rolling body (31a-31g) is able to roll on the retaining plate (20d-20j) depending on the deflection angle (AW).
2. Suspension means attachment (33) according to Claim 1, characterized in that an energy store element (21d-21g, 40) is arranged on the pull rod (18d-18h, 42).
3. Suspension means attachment (33) according to either of the preceding claims, characterized in that the retaining plate (20d-20j) has a planar rolled-on surface (34, 34a-34e) on which the rolling body (31a-31g) is able to roll by way of a rolling body rolling surface (36, 36a-36f).
4. Suspension means attachment (33) according to one of the preceding claims, characterized in that, for each pull rod (18d-18h), the retaining plate (20d-20j) has a conical bore (24b-24e, 24g) through which the pull rod (18d-18h, 42) is guided.
5. Suspension means attachment (33) according to one of the preceding Claims 1-3, characterized in that, for each pull rod (18d-18h), the retaining plate (20d-20j) has a bore (24b-24e, 24g) which consists of at least two individual bores, arranged in a stepped and concentric manner, having different diameters, and in that the pull rod (18d-18h, 42) is guided through the bore (24b-24e, 24g).
6. Suspension means attachment (33) according to one of the preceding Claims 1-3, characterized in that, for each pull rod (18d-18h), the retaining plate (20d-20j) has a bore (24b-24e, 24g) in the form of a slot, through which the pull rod (18d-18h, 42) is guided.
7. Suspension means attachment (33) according to one of the preceding Claims 3-6, characterized in that the rolling body rolling surface (36, 36a-36f) has a first non-slip and damping layer and/or the rolled-on surface (34, 34a-34e) has a second non-slip and damping layer.
8. Suspension means attachment (33) according to one of the preceding Claims 3-7, characterized in that the rolling body rolling surface (36, 36a-36f) has a first toothing which engages in a second toothing on the rolled-on surface (34, 34a:-34e).
9. Suspension means attachment (33) according to one of the preceding Claims 3-8, characterized in that the rolling body rolling surface (36, 36a-36f) has a sectional contour which corresponds to a parabola with a fraction quotient (a) and/or with an even power (n).
10. Suspension means attachment (33) according to one of the preceding Claims 3-9, characterized in that the rolling body rolling surface (36, 36a-36f) has a sectional contour which has, in a central portion (38b), a radius (R_b) which is greater than the radii (R_a, R_c) of two portions (38a, 38c) flanking the central portion (38b).
11. Suspension means attachment (33) according to one of the preceding Claims 3-10, characterized in that the rolling body rolling surface (36, 36a-36f) has at least two stops (39a, 39b).
12. Suspension means attachment (33) according to one of the preceding Claims 2-11, characterized in that the energy store element (21d-21g) is a gas compression spring (40) having a cylinder (41) and a piston rod (42) which is connected as pull rod (18d-18h) to the suspension means end connection (19c-19e).
13. Suspension means attachment (33) according to Claim 12, characterized in that the suspension means end connection (19c-19e) is arranged in a pivotable manner in a joint eye (43a) on the piston rod (42).
14. Suspension means attachment (33) according to either of the preceding Claims 12 and 13, characterized in that the rolling body (31a-31g) is integrated into the cylinder (41).
15. Suspension means attachment (33) according to one of the preceding claims, characterized in that the suspension means attachment (33) is arrangeable optionally at a stationary attachment point or on the elevator car (2) or/and on the counterweight (4).

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