HK1174320B - Hoist unit and load-bearing medium for such a unit - Google Patents

Description

The invention relates to a lifting system and a support for moving a lifting cabin in such a lifting system.

Lifts of the type described in the present invention usually have a lifting cab and usually a counterweight connected to the lifting cab, which can be moved in a lift shaft or along free-standing guides. To generate the movement, the lifting system has at least one drive with at least one drive wheel each, which interact with the lifting cab and, where appropriate, with the counterweight via drive and/or load equipment. The load equipment supports the lifting cab and the load equipment and the load equipment transfer the necessary load forces to this load equipment. Often, however, the drive equipment also performs the load-bearing function. Therefore, the following are referred to as the following because of the simplicity of the drive and/or load equipment.

The use of flat ropes was already known at this time (ibid.). The inadequate traction of steel ropes on cast or steel drives was also an early issue, so that the first attempts at coated drives and coated loaders can be dated to the beginning of the 20th century (cf. US 1047330 of 1912), with leather being preferred as the load-bearing material.

The behaviour of the metallic load carriers in the polymer casing is of central importance for the life of a load carrier, which has led to various proposals for simple rules for the construction of a load carrier with metallic load carriers and a polymer casing.

For example, EP1555234 shows a wedge belt as a support for a lift system with tractor beams made of welded steel wires, whereby the total cross-sectional area of all the tractor beams should be 30% to 40% of the total cross-sectional area of the support. The tractor beams should be made of at least 50 individual wires, each with the smallest possible diameter. In Fig. 5 of EP1555234 such a tractor is shown with a two-layer central slit 1+6+12 and 8 outlets 1+6, without specific information being given on the wire diameters of the individual wire or the drive shaft. For the tractor as a whole, a diameter of about 2 mm or less is given.

EP1640307A also reveals a belt-like supporting structure coated with an elastomer as a lifting medium, whereby the entire width of the belt-like supporting structure interacts with the drive disk. This is to achieve a better distribution of the rope pressure on the individual supporting structures. Based on the standards for steel lifting ropes, which require a ratio of drive diameter D to wire rope diameter d of D/d ≥ 40, EP1640307A proposes an interpretation of the average load bearing capacity according to the following formula: Pmax = (2F/Dw) with Pmax = maximum rope load; whereby = drag force; D = diameter of the drive disk; w = width of the train. Each of them has a center diameter of 1+6+6 and a center diameter of 6+6 litres, each of which has a maximum output of 6 litres, and each of them has a maximum output of 6 litres, each of which has a maximum output of 6 litres.

The US546185B also reveals that the tractor beams are to be embedded in a polymer, specifically rubber, by choosing a diameter ratio of the central wire to the outer wires between 1.05 and 1.5, to produce tractor beams or ropes that allow good penetration through the elastomeric coating material. The wires are specified with diameters in the range of 0.15 mm to 1.2 mm, the diameter of the tractor beams in the range of 3 to 20 mm.

US 4947638B also attempts to formulate a design for traction supports in more elastic enclosures which ensures sufficient penetration of the traction supports by the elastomeric coating material, taking into account the E-module of the wires and the ratio of the outer slit lengths to the central slits and the strands themselves.

EP 1273695 A1is a rope for a lifting system with a round cross-section, where several secured ropes are surrounded by a common coat, the individual ropes being spaced apart, so that when the rope is twisted into smaller discs, there is a high wear due to friction between the ropes.

As the above literature shows, in elevator design and in particular in the field of the interaction of drive and load bearing components, topics such as good traction, small drives and thus small light engines, the distribution of forces on the load bearing elements or the connection of metallic load bearing elements to the housing material are of constant interest. There is also a latent need for a simple method/formula that allows the design of the load bearing elements in housing elements. The cost-effectiveness of lightweight, space-saving and easily manufactured components is often at odds with the service life of important lifting components and in particular with the requirements for a long service life of the lifting system.

The present invention is based on the task of creating a lifting system of the type described above which takes into account at least some of these issues and which demonstrates good economic efficiency with sufficient service life of the support.

The invention is designed to solve this problem by the characteristics of independent patent claims.

The lift system consists of at least one disc through which a supporting device (12) moves at least one lifting cabin. The supporting device also moves a counterweight at the same time. The supporting device at least one disc in the lift system is a drive unit which belongs to a drive machine and is driven by it rotating. The supporting device carried through the drive unit is moved by the drive unit by traction and transmits this movement to the cabin connected to the supporting device and, if necessary, the counterweight. Preferably, however, the supporting device not only transmits the movement to the cabins and all of them but also transmits the counterweight at the same time. The drive unit is preferably arranged on one side of the drive unit and, if necessary, particularly preferably with this in mind.

The number of discs and their diameters depend on the suspension and composition of the individual components of a lift in the shaft. It may be that the discs in a lift may have different size diameter. The discs may be both large and small. If these discs are used, they can be of a similar shape or shape, but not only independently of the shape of the lift.

It should be noted that the term "elevator shaft" does not necessarily refer to an enclosed space, but rather to the design, which usually determines the movement path of the cabin and, where necessary, counterweight by means of so-called guide rails, and which nowadays usually includes all the components of the drive (elevator without engine room).

The supporting material around the discs consists of a body made of polymer and at least one pulling supporting material embedded in the body, extending along the length of the supporting material. The pulling support is made of wires, especially steel wires of higher strength, and is available as a sheet or rope, whereby the wires can all be of the same thickness and have the same diameter. However, it is also possible to use wires of different thicknesses with different diameters.If the bending stresses are chosen for the thickest wire in this tension range, the position of the thickest wire in the drawbar is no longer as elementary as previously assumed, i.e. at stresses in this range it is no longer possible to use the thickest wire as before only in the centre of the drawbar, but also wire configurations can be chosen in which a wire with the largest diameter is present, for example in an external wire or seat position.

The bending stress σb of the thickest wire in a drawbar in a lifting medium is approximately related to the smallest diameter of the disc D through which the lifting medium is passed, the modulus of elasticity E (also called E-module for short) of the thickest wire and its wire diameter δ according to the following equation: σb = (δ*E)/D. Taking this into account, the composition of the lift with its possibly different disc diameters and the lift with at least one drawbar and its casing can be coordinated.

If the bending stress σb, induced by running the load carrier over a disc of small diameter D, in which the wire of the towing carrier with the largest wire diameter is induced, is chosen in the range from 450N/mm2 to 750N/mm2, the service life of the towing carrier increases.

The above information applies in particular to common steel wire types with E-modules between 140kN/mm2 and 230kN/mm2; and in particular to stainless steel wire with E-modules between 150kN/mm2 and 160kN/mm2 and to high strength alloy steel wire with E-modules between 160kN/mm2 and 230kN/mm2.

For steel wires with a mean modulus of elasticity of about 190 kN/mm2 to about 210 kN/mm2 for the wires with the largest wire diameter D in the support of a support, very good values for service life have been obtained with sufficient cost-effectiveness, when the ratio of the disc diameter D of the smallest disc in the lifting system to the wire diameter δ of the thickest wire in the support is in the range of D/δ 200 to 600, preferably in the range of D/δ = 300 to 500.

The above-mentioned lifting system is particularly economical if the drive shaft is the one with the smallest diameter of the disc D, since a small, lighter motor can be used.

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If the load bearing material is fitted with several ribs parallel to the load bearing material on its traction side facing the drive shaft and at the same time the drive shaft has grooves corresponding to the ribs of the load bearing material on its periphery, the load bearing material can be better guided in the drive shaft.

In addition, if the grooves of the drive shaft are fitted with a lower groove base, so that the grooves interact with the ribs to produce a wedge effect, the traction is also significantly increased and can be adjusted depending on the chosen wedge angle of the ribs or grooves.

In a special design of the lifting system, the grooves of the drive shaft are wedge-shaped, in particular having a triangular or trapezoidal cross-section. The wedge shape results in two side walls, also called groove flanks, running in a side angle β' on each groove.

For good guidance of the support in the lifting system, other discs may be fitted with corresponding grooves in addition to the drive shaft, corresponding to the ribs of the support on its traction side.

In the case of a guide of the load-bearing medium with counter-bend, it may also be advantageous to have a guide strip on the back of the load-bearing medium on one of its traction sides, which corresponds to a guide nut in a guide, support or steering disc.

In order to obtain a support for moving and possibly carrying a lifting cabin, which has good traction properties and a high load capacity, a support is provided which comprises a body made of a polymer and at least one drawbar bearing embedded in the body, extending in the longitudinal direction of the lift. The drawbar bearing is made of wires and is available as a slide or rope. To ensure that the support in the lift has a long service life, the drawbar bearing for the support is designed so that the bending stress σb of the wire with the largest wire diameter δ δ in the drawbar when bending by a small bending radius in a range from σb = 350 mm/N2 to 900 mm/N2 is greater than the bending stress δ. This is dependent on the intended bending speed and the elasticity of the drawbar.

The reciprocal dependencies can be represented mathematically in a simplified way. The bending voltage σb is given by the following equation: σb = (δ*E)/2r. The smallest predicted bending radius r is given by the manufacturer in agreement with the lift manufacturer from the diameter D of the smallest disc predicted in the lift system as: r = D/2.

The body of the carrier is made of a polymer, preferably an elastomer. Elastomers can be adjusted in their hardness and, in addition to this necessary hardness, at the same time provide a sufficiently high wear resistance and elasticity. Also, the temperature and weather resistance and other properties of the elastomers increase the life of the carrier.

Polyurethane, especially thermoplastic ether-based polyurethane, polyamide, natural and artificial rubber, such as NBR, HNBR, EPM and EPDM, are particularly suitable as material for the body of the carrier.

In order to take account of special characteristics, it is also possible to coat the side with the traction side and/or the back of the support material with a coating, which may be applied by means of, for example, flocculation or extrusion, or may also be injected, laminated or glued, preferably a fabric made of natural fibres such as hemp or cotton, or of synthetic fibres such as nylon, polyester, PVC, PTFE, PAN, polyamide or a mixture of two or more of these fibres.

In a first embodiment, the support material, when bent by a minimum bend radius r in the thickest wire of at least one of its drawbars with the largest wire diameter δ, has a bend stress σb in the range of σb = 450N/mm2 to 750N/mm2 and preferably in the range of σb = 490N/mm2 to 660N/mm2.

In another embodiment of the supporting medium, the wire with the largest wire diameter δ has a modulus of elasticity of about 210'00 N/mm2. For this embodiment, a particularly high service life of the supporting medium is obtained at very good cost-effectiveness if the ratio of the smallest bending radius r to the wire diameter δ of the thickest wire in the supporting medium is in the range of 2r/δ = 200 to 600, and even higher if it is in the range of 2r/δ = 300 to 500.

In another embodiment, the supporting material has at least one of the characteristics described above and a drawbar where the strands or wires are at least 0.03 mm apart at the outermost wire or drawbar position, the greater the viscosity of the polymer embedding the drawbar at the time of the drawbar's insertion.

In another embodiment, the more bed layers or wire layers in this embodiment are spaced apart, the more bed layers and wire layers there are in total.

In another embodiment, both are true, i.e. at least in one position, both the ribs and the outer wires in these outer ribs are at least 0.03 mm apart.

This measure (s) ensures a good mechanical connection of the drawbar with the material of the load bearing body, which further increases the service life of the load bearing.

In a particular embodiment, the load carrier has more than one drawbar stretcher (12) extending along the length of the load carrier, the drawbars being placed in a plane adjacent to and spaced apart from each other, in view of the width of the load carrier. In this way, the load to be taken up by the load carrier is distributed among several smaller diameter drawbars, which allows the smallest bending radius r to be chosen for this smaller load carrier.

In other embodiments, the support comprises at least one drawbar, which is a slit in seal configuration with a core of 3 wires of diameter a each and two layers of wire surrounding the core with wire diameters b (1 wire position) and wire diameters c (2 wire position). A particularly advantageous configuration of this type is (3a-9b-15c), where a, b, c are wire diameters, which are all different, all equal or only partially equal depending on the configuration. The digits in front of the wire give the number of wires with this diameter.

Err1:Expecting ',' delimiter: line 1 column 883 (char 882)

In another embodiment, the support comprises at least one drawbar with a wire configuration (3d+7c) +n*(3b+8a), where n is an integer between 5 and 10, and where the smallest bend radius r is at least r ≥ 50 mm. a, b, c, d are wire diameters that are all different, all equal or only partially equal depending on the configuration.

In another embodiment, the support comprises at least one drawbar bearing with a wire configuration (3f+3e+6d)W+n*(3c+3b+6a)W, where n is an integer between 5 and 10, and where the smallest bend radius r is at least r ≥ 40 mm. a, b, c, d, e, f are wire diameters that are all different, all equal or only partially equal, and W is a Warrington configuration.

In yet another embodiment, the drawbar of the load-bearing medium has at least one wire configuration (1e+6d+12c) +n*(1b+6a)W, where n is an integer between and 10, and where the smallest bend radius r is at least r ≥ 32 mm. a, b, c, d, e are wire diameters, which are all different, all equal or only partly equal depending on the configuration.

Err1:Expecting ',' delimiter: line 1 column 253 (char 252)

In another embodiment, the supporting medium has several of the load carriers described above, preferably all load carriers having the same wire configuration, so that the load-bearing strength, stress ratio and tensile characteristics of all load carriers are the same.

In another embodiment, the support comprises several drawbars with different wire configurations, the configurations being adapted with their specific characteristics to the position in the support (center or outer).

In a particular embodiment, the support is designed as a traction side on one side, with several ribs running parallel to the support.

In another embodiment, the load carrier has a traction side with several ribs running parallel to the load carrier, which have a wedge-shaped cross-section, in particular a triangular or trapezoidal cross-section with a side angle β in the range of 81° to 120°, preferably 83° to 105° or 85° to 95° and preferably 90°.

The tension and load on the drawbar bearings of a load-bearing medium can be distributed evenly if two drawbars are attached to each rib on the drawbar side of the load-bearing medium.

It is also very advantageous if each rib of the support is assigned exactly one drawbar, which is centrally arranged in relation to the two sides of the rib.

In another embodiment, the support has exactly two ribs on the traction side. In addition to the advantages of a wedge-ribbon belt, such a support has the advantage that the number of support can be adjusted very precisely to the load to be carried in the lift. In a special embodiment, this support has a guide rib on its rear side opposite the traction side, so that when bending it can be guided through a correspondingly designed slide with a guide groove without additional measures having to be taken for a lateral guidance of the support.

In another particular embodiment, such a support may also be higher than wide, which, when bent, creates a higher internal tension in the support body, which in turn reduces the risk of the support being trapped in a disc with grooves.

Further advantages and refinements of the invention are shown by the further claims. As already shown in the previous description, the features of the various embodiments can be combined with each other and are not limited to the examples in which they are described. This is also clearly shown in the following explanations of the invention by means of the accompanying schematic drawings. The examples of embodiments presented in the respective drawings each show certain features in combination with each other. This does not mean, however, that they can only be used meaningfully in the combination shown. On the contrary, they can be equally well combined with other features shown or described in other examples.

The figures show, for example and purely schematically: Fig. 1a perspective view of a second example of a supporting structure made to order in the form of a flat cross-section;Fig. 2a perspective view of a rib side of a first example of a steel supporting structure according to the invention in the form of a wedge-ribbon belt;Fig. 2a cross-sectional view of the supporting structure according to Fig. 2 with various examples of possible supporting structures;Fig.3a perspective view of a second example of a supporting structure made to order in the form of a flat cross-sectional section;Fig.3b perspective view of a rib side of a steel supporting structure according to the invention in the form of a wedge-ribbon belt;Fig. 4a perspective view of a rib side of a steel supporting structure according to the invention in the form of a wedge-ribbon belt;Fig. 2a perspective view of the cross-sectional view of the supporting structure according to Fig. 2a perspective view of the supporting structure according to Fig. 2a perspective view of the cross-sectional view of the supporting structure according to Fig. 2a perspective view of the various examples of possible supporting structures;Fig.3b perspective view of a second example of a supporting structure according to the invention in the form of a flat cross-sectional section;Fig.3b perspective view of a second example of a supporting structure according to the invention in the form of a steel supporting structure according to the invention;Fig. 3a perspective of a second example of a supporting structure according to Fig. 4a perspective of a steel supporting structure similar to the invention;Fig. 4a perspective of a second example of a supporting structure similar to Fig. 4a second example of a steel supporting structure;Fig. 4a example of a supporting structure similar to the same type;Fig. 4a example of a supporting structure;Fig. 4a example of a similar structure;Fig. 4a example of a steel supporting structure similar to the second example of the same type;Fig. 4a example of the second example of the second example;Fig. 4a example of the second example of the second example of the second example;Fig. 4a example of the second example

Fig. 1 shows a section through an inventive lifting system 9 in a lift shaft 1. It essentially shows a drive unit 2 mounted on top of the lift shaft 1 with a drive unit 4.1 and a lifting unit 3 guided by cabin guide rails 5 with cabin support discs 6 mounted below the cabin floor 4.2 In addition, a counterbalance 8 guided by counterbalance rails 7 with a counterbalance load disc 4.3 and a load medium 12 supporting the lifting unit 3 and the counterbalance 8 and transferring the driving force from the drive unit 2's drive unit 4.1 to the lifting unit 3 and the counterbalance 8 at the same time.

The supporting material 12 has at least two elements, which are also referred to as supporting materials 12 although they are not only supporting but also propelling. Only one supporting material 12 is shown, but it is clear to the elevator operator that for safety reasons there are usually at least two supporting materials 12 in a lifting system. Depending on the cabin weight, suspension and load capacity of the supporting materials 12, these can be used parallel to each other and running in the same direction or in another configuration. Two or more supporting materials 12 running in the same direction can be combined into a supporting material 12 in parallel, with either one or more supporting materials being provided in a lifting system. These can also be placed in the same direction or in another configuration and be placed in a lifting system.

In contrast to the 2:1 suspension shown in Fig. 1, elevator systems can also be designed with 1:1, 4:1 or any other suspension ratio as elevator systems according to the invention. The drive unit with the drive unit 4.1 must also not necessarily be located at the top of the lift shaft but can, for example, be located in the shaft floor or in the shaft in a gap next to the cabin's motion path and an adjacent shaft and in particular also above a shaft door.

In the example of a lifting system 9 according to the invention shown in Fig. 1, the supporting device 12 is attached at one end below the drive unit 4.1 to a first supporting centre point 10. From this point it extends downwards to a counterbalance supporting device 4.3 located at counterweight 8 and encircles it and extends from this to the drive unit 4.1 It encircles the drive unit 4.1 in this case by about 180° and runs downwards along the counterbalance cabin supporting wall. Then the cabin 3 is encircles, with a point on each side of the load-bearing cabin 3 located below the lifting device 4 at a distance of approximately 90° from the counterweight 8 to the counterweight 4.2 and a better conversion is ensured between the two cabin supporting devices 4.2 and 4.2 on the second side of the cabin, with a better conversion of the load-bearing cabin 6 to the load-bearing cabin 6 at a distance of approximately 90° from the centre of the load-bearing cabin.

In the example of a lifting system 9 according to the invention shown in Fig. 1, a lifting system 12 according to the invention is fitted with drawbars according to the invention and is guided by a drive unit 4.1 according to the invention. This allows the drive unit 4.1 of the lifting system 9 according to the invention to be selected very small, reducing the space required and allowing the use of a lighter, smaller machine. The plane of the drive unit 4.1 is aligned vertically to the cabinet rather than to the weight-side cabinet and its vertical projection is located behind the cabinet's vertical projection.

Err1:Expecting ',' delimiter: line 1 column 1118 (char 1117)

Another example of a load bearing device is shown in Fig. 3a, 3b. This load bearing device is designed with a flat surface on both its traction side 18 and its back side 17. The load bearing devices 22 are arranged in a plane next to each other as in the previous example. They are inserted at equal distances from each other into the polymer of the body 15 of the load bearing device 12 and are weighed in their number and in their torque in such a way that their torques are given over the entire medium 12. The material of the body 15 is arranged between and around each load bearing device 12.The hard load coating 15a is advantageous in terms of an even force distribution in the load coating 12 when running over the drives 4.1. The wear resistant coating 61 with the fabric protects 62 from abrasion. On the back of the actual body 15 of the load coating 12 there is a softer load coating 15a, at least in relation to the load coating 15a, of deck 15b, which provides a smooth sheath of sheets over 4.A coating 61, containing, for example, polytetrafluoroethylene, reduces friction when the carrier 12 passes over these panes 4.2, 4.3, 4.4 under counter-bending, which further improves the noise and wear-free sliding and rolling over these panes.

The drawbars 22 in the load carriers 12 of the invention are made by means of high-strength steel wire strands (strength values in the range of 1770 N/mm2 to about 3000 N/mm2). The drawbar is designed so that, when a drawbar 12 equipped with such a drawbar 22 is bent by a minimum bending radius r, there is a bending stress σb in the thickest wire with the largest wire diameter δg in the drawbar 22 which is in the range of 300 N/mm2 and 900 N/mm2.

The design of the support 12 or the drawbar 22 in the support 12 is as follows: when the support 12 is run with a drawbar 22 over a smallest disc with a diameter of the smallest disc D in the lifting system 9, the bending stress σb for the thickest wire of the support 22 is given by the following equation: σb = (δ*E) / or σb = (δ*E) / 2r.

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The configuration of the drawbar 22 shown in Fig. 7 has its thickest wire 43 with the largest diameter δ=e in the middle as the central wire of the central slits 40. At a minimum bend radius of 36 mm or a minimum disc diameter in a lifting system 9 of 72 mm, for this thickest wire 43 a bending stress σb of σb = 554N/mm2, the ratio of disc diameter D to wire diameter δ of the thickest wire 43 D/δ = 379 and the ratio of effective diameter D to effective diameter d of the drawbar = 22 D/d = 41.5.

In the embodiments shown in Fig. 8a and 8b, the drawbar 22 has a wire configuration (1f-6e-6d+6c) W+n*(1b+6a) where n is an integer between 5 and 10 and the smallest bend radius r is at least r ≥ 32 mm. Fig. 8a shows a configuration where n=9, the central slit 40 has a Warrington configuration (1xf-6xe-6xd+6xc) or written with the diameters of the individual wire types in μm (1x210-6xe200-6x160+6x2x20) and the 9 outlets 44 have a central wire with a wire diameter of at least: δm = 140 μm and 6 μm = 6 μm, giving a total length of 8 μm, giving a wire diameter of 19 μm (I,a,b,c,d,d,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e,e

The second embodiment of this configuration in Fig. 8b shows the same central loops 40 with the same Warrington structure (1xf-6xe-6xd+6xd) and the same wire diameters δ: f=210μm, e=200μm, d=160μm, c=220μm. Instead of the 9 outlets 44 with seven individual wires 42 are provided in this embodiment but 8 outlets 44 of the configuration (1b+6a). The wire diameter of the single wires 42 are shown here accordingly b=150μm, a=150μm. As can be seen from the corresponding tables (8b and 8b.1) the number of bins in the thicknesses of the two loops differs from the ratio of the thicknesses of the two loops 8a and 8a. The ratio of the two loops is not different from the one for the most common example of 8a and 8a. The ratio of the two loops is not changed, and the tractive efficiency of the two loops is not affected by the difference in the thickness of the loops 8a and 8a.

The embodiment in Fig. 9 shows a drawbar 22 with a basic wire configuration (3f+3e+3d) +n*(3c+3b+3a), where n is an integer between 5 and 10, and where the smallest bend radius r is at least r ≥ 30 mm. In concrete terms, a configuration with n=6; a=0.17mm, b=0.25mm, c=0.22mm, d=0.20mm, e=0.30mm, f=0.25mm is shown. The thickest wire 43 with the largest wire diameter δ is the wire with diameter δ = e=0.30mm.

Err1:Expecting ',' delimiter: line 1 column 961 (char 960)

Fig. 11 shows an embodiment of a drawbar 22 with a central slit 40 measured (3e+3d-15c) and 8 external slits 44 measured (1b+6a), where the central slits 40 have a core 41 with 3 central wires of diameter e and three fillers of diameter d and a wire frame 46 with 15 wires of diameter c. The diameter d of the drawbar is approximately 1.8 to 1.9 mm. Further values for this configuration are given in Tables 11.I and 11.II.

Figure 12 shows that n is specifically equal to 6 (n=6) and the smallest bend radius r ≥ 32 mm. The diameter d of the pulling support 22 is approximately 2.5 mm, the bending tension σb for the thickest wire 43 with the largest wire diameter δ (wire with diameter c=0.27 mm) is approximately 2.5 mm for bending radii r between 36 mm and 75 mm, which corresponds to disc diameters D of 72 mm to 150 mm (see Table 12.II), where the bending stresses are σb for this thickest range of 43 mm = 788 mm/N. The bending tension is approximately 7.8 mm/N. The overall load capacity for this pulling support is approximately 12.1 mm/N. A drawing capacity of approximately 2.5 mm/N is achieved for all the weights of the pulling support 12.1 mm/N.

Err1:Expecting ',' delimiter: line 1 column 247 (char 246)

For steel wires with a mean modulus of elasticity of about 190 kN/mm2 to about 210 kN/mm2 for the wires with the largest wire diameter D in the support of a support, very good values for service life have been obtained with sufficient cost-effectiveness, if the ratio of the disc diameter D of the smallest disc in the lifting system to the wire diameter δ of the thickest wire in the support is in the range of D/δ = 700 to 280, preferably in the range of D/δ = 600 to 320.

As already mentioned, the drawbars, as illustrated and explained in Figures 7 to 12, are used in the load carriers 12 of a lifting system according to the invention. The bending stress σb in the thickest wire 43 with the largest wire diameter δ of the drawbar 22 in the load carriers 12 is then in the range of σb = 300N/mm2 to 900N/mm2 and even better in the range of σb = 490N/mm2 to 750N/mm2 and even better in the range of σb = 490N/mm2 to 660N/mm2 when bending by a smallest bending radius r or by a smallest disc with a disc diameter D in the lifting system.

The above information applies in particular to common steel wire types with E-modules between 140kN/mm2 and 230kN/mm2; and in particular to stainless steel wire with E-modules between 150kN/mm2 and 160kN/mm2 and to high strength alloy steel wire with E-modules between 160kN/mm2 and 230kN/mm2.

The load carriers 12 with such load carriers 22 may be designed as flat belts as shown in Fig. 3a, 3b. Such load carriers 12 are preferably used in lifting equipment 9 equipped with flat and/or bombed discs 4.1, 4.2, 4.3, 4.4 and having, as appropriate, side discs for better guidance.

However, the use of these drainage rails 22 may also be used to make a useful configuration of a circular-sectioned support with one or more overlapping support rails.

The following is a description of a lifting device 9 as described in Figure 1 using a support device 12 shaped as a wedge belt, as shown in Figure 2a, 2b. The support device 12 is guided with its traction side 18 through the drive shaft 4.1, the counterbalance bearing shaft 4.3 and the guide discs 4.4, which are fitted with grooves 35 at their periphery, which are complementary to the ribs 20 of the support device 20. Where the wedge belt 12 encircles one of the ribs 4.1, 4.3 and 4.4, its body 20 is located in the corresponding carrying side of the 35 ribs, thus ensuring perfect guidance of the support device 12 on these ribs.

The cabin strap 12 is carried over the 4.2 cabin discs with a counter-curve, i.e. the ribs 20 of the 12 cabin strap are on its back side 17 when running over these discs, which is turned away from the 4.2 cabin strap discs and is formed here as a flat side. To improve the lateral guidance of the 12 cabin strap, the cabin strap discs 4.2 may have lateral edge discs. Another way of driving the vehicle sideways is to place two guide bars 4.4 on the running path of the 12 vehicle between the two cabin strap discs 4.2 as shown in this particular example.The grooves of the guide discs 4.4 work together with the ribs of the wedge belt 12 as a side guide, so that the cabin support discs 4.2 do not require side discs. This variant is advantageous because, unlike a side guide by means of board discs, it does not cause side wear on the support 12 Depending on the cabin dimension, the chosen suspension and the interaction of the discs with the support, it is also possible to work without any guide discs between the cabin support discs 4.2 or 4.4 instead of the two guide discs shown 4.4 under the cabin 3 only one or more than two guide discs 4.In general, it is also possible to move the load carrier over the cabin to the other side of the cabin (not shown) instead of under the cabin.

As illustrated in Fig. 4a, the drive 4.1 not only has grooves 35 in its periphery, but also in its grooves 35 a groove base 36 which is deeper than the trapezoid-flattened tips of the insertive ribs 20 of the wedge belt in this example 12. In this way, on the drive 4.1 only flanks 24 of the ribs 20 of the wedge belt 12 act together with flanks 38 of the grooves 35 of the drive 4.1 so that between the grooves 35 of the drive 4.1 and the ribs 20 of the wedge belt 12 a wedge is formed which improves traction.If the peripheral elevations 37 of the 4.1 drive are slightly less high than the elevations 26 between the 20 ribs of the 12 support, the result is a cavity 28 at the junction of the 26 ribs with the 38 elevations.This reduces the risk of the load-bearing medium becoming stuck in the disc 4.2, 4.3, 4.4 and provides good guidance with less traction.

In the lifting system 9 according to the invention shown in Fig. 1, the diameters of all the belt discs are the same. However, it is also conceivable that the belt discs may be of different sizes and that the support and/or override discs 4.2, 4.3, 4.4 may be larger in diameter than the drive unit 4.1 or smaller in diameter than the drive unit 4.1, or that discs 4.2, 4.3 may be provided, one of which is larger in diameter than the other.The wires in the drawbar 22 may all have the same diameter or be of different thickness. According to the invention, the drawbar is designed so that a bending stress σb in the thickest wire with the largest wire diameter δ of the drawbar 22 results, when the drawbar 22 is running over a smallest disc with the smallest disc diameter D in the lifting system, depending on the modulus of elasticity E and the diameter δ of the thickest wire, according to the following equation: σb = (δ*E) /D The best ratio of lifting system efficiency to the service life of the drawbar 12 is obtained with a drawbar 22 whose thickest wire with the largest diameter has a bending stress in a range from σ2 to 900 mm/N2 = 300 μN.

Fig. 4a shows a cross-section of a wedge belt 12 according to the present invention, comprising a belt body 15 and several drawbars 22 embedded in it. The belt body 15 is made of an elastic material such as natural rubber or synthetic rubber such as NBR, HNBR, ethylene-propylene rubber (EPM), ethylene-propylene-diene rubber (EPDM), etc. Also a variety of synthetic elastomers such as polyamide (PA), polyethylene (PE), polycarbonate (PC), polychloroprene (CR), polyurethane (PU), and especially because of a simpler processing also thermoplastic, ethylene-based or ester-based, such as thermoplastic polyurethane (TPU).

On the flat side 17, the body of the belt 15 is covered with a cover layer 62 which contains impregnated fabric, but may also be covered with non-impregnated fabric 61 or may be covered by extrusion, bonding, lamination or flocculation.

In the examples shown in Figures 2a, 2b and 4a, each rib 20 is located on the traction side 18, two drawbars 22 are located there, and for a favourable transfer of force between the discs 4 in the lift system and the drawbars 22 in the support 12 the drawbars 22 are each located centrally above the vertical projection 70 of a flank 24 of the rib 20.

If two load carriers 22 are attached to each rib 20 of the load carrier 12 and centrally placed on a flank 24 of the rib 20, they can together optimally transmit the strap loads occurring in the belt per rib. These strap loads are, on the one hand, the transmission of pure traction forces in the belt longitudinal direction. On the other hand, when one is circled, the strap discs 4.1 - 4.4 are distributed by the load carriers 22 in a radial direction through the belt body 15 to the belt carriers 4.1, 4.2, 4.3, 4.4. The cross sections of the load carriers 22 are radiated so that these forces do not intersect the belt by a 15th dimension. In the case of a 20a transmission, these forces are transmitted in the direction of the 20a. In addition, the load carriers 22 are placed on the two traction bearers 22 and placed on the strap as low as possible, especially in the case of a 20a.

As shown in Fig. 4b, it is also possible to provide more than two 22 per rib, but in Fig. 4b three 22 per rib, where the ribs 20 are trapezoidal in cross-section, the middle one is centrally placed in rib 20 and the two framing them in rib are preferably centrally placed on a flank 24. The latter is not mandatory.

Unlike the examples in Figures 2a, 2b and 4a, the load carrier 12 in Figure 4b is not coated on its flat side 17 but has a coating 62 on its traction side 18 indicated by a dashed line, which adjusts the coefficient of friction and/or wear in conjunction with the drive unit 4.1 and/or another belt disc 4.2, 4.3, 4.4 of the lifting device 9. This coating 62 also preferably covers a fabric 61, in particular a nylon fabric.

Figure 5 shows another embodiment of a support 12 according to the invention. As can be seen in Figure 5, in this example the support 12 has only one drawbar 22 on the traction side 18 per rib 20. With the same dimensions of the support 12 and its ribs 20, with only one drawbar 22 per rib 20, instead of two drawbars per rib 20, with one drawbar 22 per rib 20, the drawbar 22 can be larger in diameter.

Like the examples in Figures 2a, 2b and 4b, the carrier sample 12 of Figure 5 also has a coating on its flat back 17 which contains tetrafluoroethylene in this example to reduce the coefficient of friction when interacting with shift discs 4.4 or carrier discs 4.2, 4.3.

All the above coatings may be applied over the entire length of the support 12 or only one or more specified lengths of the support 12 and in particular those lengths of the support 12 which interact with the drive shaft when the cabin 3 or counterweight 8 is mounted, for example on a buffer in the shaft pit.

Fig. 6 shows a support 12 that also has ribs 20 on its traction side 18 with two tractor beams 22 on each. Specifically, this support 12 has exactly two ribs 20 on its traction side 18 and additionally a guide strip 19 on its back side 17. The guide strip 19 works in conjunction with the diversion, guide and support discs 4.2, 4.3, 4.4 when counter-curving, which have a corresponding guide nut to accommodate the guide strip 19 (not explicitly shown). The support in Fig. 6 is higher than or maximum equal to the width.In particular, it may be equipped with 3, 4 or 5 drawbars per rib; like the other embodiments, it may be coated on the traction side and/or the rear; conversely, the other embodiments of the bearing 12 shown here may be equipped with one or more guide ribs 19 on the rear 17; these may be of the same size or larger than the ribs 20 on the traction side 18 and may be made of a different material to improve the stability of the bearing 12 or contain stabilizing elements (not shown) similar to the drawbars 22 extending over the length of the bearing 12.

As shown in Figures 4b and 5, the supporting material 12 has a lateral angle β of about 90°. The lateral angle β is the angle 24 of a rib 20 of the supporting material 12 enclosed by its two flanks. Experiments have shown that the lateral angle β has a decisive influence on the development of noise and the generation of vibrations and that for a wedge belt intended as a lifting supporting material, lateral angles β of 81° to 120° and better from 83° to 105° and even better from 85° to 95° are applicable. The best characteristics in this respect and also in terms of guidance are achieved with rib angles β of 90°.

It is particularly easy to produce loaders whose side angle β in ribs 20 is equal to the angles in the grooves 26 and the same applies to the production of rimmed belt discs fitted with grooves 35 or 37 in accordance with the intended loaders, the sides of which 38 contain a side angle β' in the groove 35 and the height 37.

It is also apparent from Figures 4b and 5 that the small dimensions and light weight of a striped support 12 are achieved by keeping the X-spaces between the outer contours of the drawbars 12 and the surfaces/flanks of the ribs 20 as small as possible. Optimal characteristics have been obtained by tests on striped support 12 where these X-spaces are not more than 20% of the total thickness s of the support.

The reciprocal dependencies can be represented mathematically in a simplified way. The bending voltage σb is then given by the following equation: σb = (δ*E)/2r. The smallest predicted bending radius r is given by the manufacturer in agreement with the lift manufacturer from the diameter D of the smallest disc provided for in the lift system as: r = D/2

The bending stress σb of the thickest wire in a drawbar in a lifting medium is approximately related to the smallest diameter of the disc D through which the lifting medium is passed, the modulus of elasticity E (also called E-module for short) of the thickest wire and its wire diameter δ according to the following equation: σb = (σ*E)/D. Taking this into account, the composition of the lift with its possibly different disc diameters and the lift with at least one drawbar and its casing can be coordinated.

If the bending stress σb, induced by running the load carrier over a disc of small diameter D, in which the wire of the towing carrier with the largest wire diameter is induced, is chosen in the range from 300N/mm2 to 750N/mm2, the service life of the towing carrier increases.

As already noted above, in order to obtain a lift system with low maintenance costs, it is important, among other things, to use a load carrier with a long service life in the system. In addition, the costs can be reduced if a small lightweight motor with a small drive can be used. The space required for a lift system can be further reduced if other small-diameter discs are used in addition to the small drive.

Claims (11)

1. Load bearing member for supporting and/or moving at least one elevator cabin (3) in an elevator system, wherein load bearing member (12) can be guided and driven, at least by way of a pulley (4), particularly a drive pulley (4.1) of an engine (2), wherein the load bearing member (12) comprises a body (15) which is made from a polymer and at least one tension member (22) which is embedded in the body and extends in the longitudinal direction of the load bearing member (12), the tension member (22) being made from wires and being in the form of a cord or rope, and wherein, in the tension member (22), a thickest wire (43) with the largest wire diameter δ has a bending stress σb in a range of between σb = 350 N/mm² and 900 N/mm² when the tension member (22) is bent through a smallest bending radius r, characterised in that the tension member (22) has a wire configuration (1e+6d+12c)+n*(1b+6a)W, n being a whole number between 5 and 10, wherein a, b, c, de, e are wire diameters which are all different, all the same or only partly the same depending on the respective configuration, wherein W is a Warrington configuration and in which the smallest bending radius r is at least r ≥ 32 mm.
2. Load bearing member according to claim 1, in which the bending stress σb of the wire with the largest diameter δ in the tension member (22) when the latter is bent through a smallest bending radius r lies in the range of between σb = 450 N/mm2 and 750 N/mm2 and preferably in the range of σb = 490 N/mm2 to 660 N/mm2, the bending stress σb preferably being obtained as a function of the modulus of elasticity E and of the diameter δ of the thickest wire (43) and particularly according to the following equation: σb = (δ*E)/D.
3. Load bearing member according to claim 1 or 2, in which the wire with the largest wire diameter δ has a modulus of elasticity of about 210,000 N/mm2 and the ratio of the smallest bending radius r to the largest wire diameter δ of the thickest wire (43) in the tension member (22) lies in the range of 2r/δ = 200 to 650, preferably in the range of 2r/δ = 230 to 500.
4. Load bearing member according to any one of claims 1 to 3, in which the cords (28) or wires (42) of the tension member (18) in its outer wire or cord ply are spaced apart from one another and in particular the further apart they are the higher the viscosity of the polymer when the tension member (18) is embedded in the body (15) of the load bearing member (12), the spacing (60) amounting to at least 0.03 mm.
5. Load bearing member according to any one of claims 1 to 4, in which the tension member (22) is SZS-laid or ZSZ-laid.
6. Load bearing member according to any one of claims 1 to 5, one side of which is configured as a traction side (18) which has a plurality of ribs (20) running parallel in the longitudinal direction of the load bearing member and more than one tension member (22) extending in the longitudinal direction of the load bearing member (12), the tension members (22) being arranged in one plane next to one another, preferably spaced from one another, as seen in the width of the load bearing member.
7. Load bearing member according to claim 6, in which the ribs (20) of the load bearing member (12) have a wedge-shaped, in particular triangular or trapezium-shaped, cross-section with two flanks (24) which run toward one another and include a flank angle (β) which is in the range of 81° to 120°, better 83° to 105°, even better of 85° to 95° and best 90° ± 1°.
8. Load bearing member according to one of claims 6 and 7, in which each rib (20) is assigned two tension members (22) which are arranged in each case in the region of the vertical projection (P) of a flank (24) of the rib (20).
9. Load bearing member according to one of claims 6 and 7, in which each rib (20) is assigned exactly one tension member (22) which is arranged centrally with respect to the two flanks (24) of the rib (20).
10. Load bearing member according to any one of claims 6 to 9, in which the traction side (18) of the load bearing member (12) and/or the rear side (17), lying opposite the traction side (18), of the load bearing member (12) is or are coated, the desired coefficient of friction between the traction side (18) and the drive pulley (4.1) or rear side (17) and deflecting, guiding or supporting pulleys (4.2, 4.3, 4.4) being set with the aid of the coating (61), and the coating (61) being, in particular, a woven fabric (62), preferably composed of natural fibres or of synthetic fibres, in particular of hemp, cotton, nylon, polyester, PVC, PTFE, PAN, polyamide or a mixture of two or more of these fibre types.
11. Load bearing member according to any one of claims 6 to 9, in which the load bearing member (12) has two ribs (20) on the traction side (18) and preferably a guide rib (27) on the rear side (17) opposite the running surface.