EP2488436B1 - Hoist unit and load-bearing medium for such a unit - Google Patents

Description

The invention relates to an elevator system and a support means for moving an elevator car in such an elevator system.

Elevator systems of the type according to the invention usually have an elevator car and usually a counterweight connected to the elevator car, which can be moved in an elevator shaft or along free-standing guide devices. To generate the movement, the elevator installation has at least one drive with at least one traction sheave each, which interacts with the elevator car and optionally with the counterweight via drive and / or suspension means. The suspension means carry the elevator car and the counterweight and the drive means transmit the required driving forces to them. Often, however, the drive means also takes over the supporting function at the same time. In the following, therefore, for the sake of simplicity, the carrying and / or drive means will only be referred to as suspension means.

Very early in the history of elevators, the quest for small, lightweight engines can be demonstrated and the knowledge that smaller rope diameters allow the use of smaller traction sheaves and thus smaller engines (see. DE 6338 of 1878 ). The use of flat ropes is already known at this time (ibid.). The inadequate traction of steel cables on cast iron or steel drive pulleys also became an issue early on, so that the first experiments with jacketed traction sheaves and jacketed suspension elements can be dated to the beginning of the 20th century (cf. US 1047330 of 1912 ), which was then preferably worked with leather as a shell material. With the provision of suitable synthetic sheath material by the polymer industry, elevator builders began to deal with polymer-sheathed suspension in the 1970s (cf. US 1362514 from 1974 ), from the beginning polyurethane as sheath material played an important role (ibid.).

The behavior of the metallic tension members in the polymeric sheath is of central importance for the lifetime of a suspension element. This has led to various proposals for simple design rules, according to which a suspension with metallic tension members and a polymeric sheath should be created.

For example disclosed EP1555234 a V-ribbed belt as the support means of an elevator installation with tension members made of stranded steel wires, wherein the total cross-sectional area of all tension members should account for 30% to 40% of the total cross-sectional area of the suspension element. The tension members should be made of at least 50 individual wires, each with the smallest possible diameter. In Fig. 5 of the EP1555234 Such a tension member is shown with a two-ply central strand 1 + 6 + 12 and 8 outer strands 1 + 6, without any specific information on the wire diameters of the individual wires or the traction sheave would be made. For the tension members as a whole, a diameter of about 2mm or less is specified.

Also EP1640307A discloses belt-like with an elastomer sheathed tensile carrier as the support means of an elevator, wherein the entire width of the belt-like support means cooperates with the traction sheave. As a result, a better distribution of the rope pressure to the individual tension members to be achieved. Based on the standards for steel hoisting ropes, which prescribe a ratio of pulley diameter D to wire diameter d of D / d ≥ 40, in EP1640307A proposed an interpretation of the suspension means according to the following formula: Pmax = (2F / Dw) with Pmax = maximum rope pressure; F = tensile force; D = diameter of the traction sheave; w = width of the belt. The tension members are each made of a single-layer central strand 1 + 6 and 6 single-layer outer strands 1 + 6, wherein the central wires of the strands each have a larger diameter than the surrounding outer wires.

Tensile beams with strands whose central wires each have a larger diameter than the surrounding outer wires, also reveals US546185B related to elevators, conveyors and heavy tires. Here, too, the tension members are to be embedded in a polymer, here in particular rubber. By choosing a diameter ratio of the central wire to the outer wires between 1.05 to 1.5, strands or ropes should result as a tensile carrier, which allow a good penetration through the elastomeric jacket material. The wires are indicated with diameters in the range of 0.15mm to 1.2mm, the diameter of the tension members in the range of 3 to 20mm.

Also in the US 4947638B Attempts to set up a formula for the design of tension members in elastomeric sheaths, which ensures a sufficient penetration of the tension member with elastomeric jacket material, but here also the modulus of elasticity of the wires and the ratio of the lay lengths of the outer strands to the central strand and the strands are taken into account.

EP 1273695 A1 discloses a rope for a lift system with a round cross-section, wherein several stranded strands are surrounded by a common jacket. The individual strands are spaced apart from each other, so that when using the rope on smaller discs high wear by friction of the strands against each other

As the above cited literature shows by way of example, in elevator construction and in particular in the area of interaction between traction sheave and suspension elements, topics such as good traction, small traction sheaves and thus small light engines, the distribution of the occurring forces on the tensile carriers of the suspension elements or the connection of metallic tension members with the cladding material always of interest. Likewise, there is a latent need for a simple method / formula that allows for interpretation of the tension members in jacketed suspension elements. The economy with lightweight, space-saving and easy to manufacture components is often in conflict with the life of important elevator components and in particular in contradiction with the requirements for a long life of the suspension element in the elevator system.

The present invention has for its object to provide an elevator system of the type described above, which takes into account at least some of these issues and shows a good economy with sufficient life of the support means.

According to the invention, this object is solved by the features of the independent patent claims.

The elevator system comprises at least one disc, over which a suspension element (12) is guided, which moves at least one elevator car. Advantageously, the support means also moves a counterweight. The at least one disc in the elevator system is a traction sheave, which belongs to a drive machine and is driven by this rotating. The guided over the traction sheave support means is moved by means of traction of the traction sheave and transmits this movement to the connected to the suspension means car and possibly the counterweight. Preferably, however, the suspension element not only transmits the movement to the cabin and possibly the counterweight, but at the same time carries it. The traction sheave is preferably arranged on a shaft of the drive motor and particularly advantageously formed integrally therewith.

Depending on the type of suspension 1: 1, 2: 1 or higher, the elevator system includes only the traction sheave (1: 1 suspension) or other various discs on the Carrying means is guided. These discs may be deflecting discs, guide discs, car washers, counterweight washers. For reasons of space, preference is given to disks with small diameters and, in relation to smaller, lighter engines, in particular also traction disks with small diameters. The number of discs and their diameters depend on the suspension and the composition of the individual components of an elevator in the elevator shaft. So it may happen that the discs have different diameters in an elevator system. The discs can be both larger and smaller than the traction sheave. When speaking of disks here, they may not only be disk-shaped, but they may also be formed in a cylindrical shape, similar to a shaft. Their function is independent of this design issue, a deflection, carrying or driving the suspension.

It should be noted here that under elevator shaft here is not necessarily meant a closed room, but quite generally the construction, which determines the trajectory of the cabin and possibly counterweight mostly by so-called guide rails, and in or on the nowadays usually all components of the drive are recorded (machine roomless elevator).

The support means guided around the disks comprises a body made of a polymer and at least one tension member embedded in the body and extending in the longitudinal direction of the support means. The tension member is made of wires, in particular steel wires with high strength and is in the form of a strand or rope, the wires can all be the same thickness and have the same diameter. But it is also possible to use wires of different thicknesses with different diameters. In order to obtain an elevator system with low costs for the maintenance of the suspension element, a suspension element is selected in which the bending stress σb of the wire with the largest wire diameter δ in the tension member when running over a disc with the smallest pulley diameter D in the planned elevator installation in a range between σb = 350N / mm ² to 900N / mm ² . If the bending stresses for the thickest wire in this range of stress are chosen, then the position of the thickest wire in the tension member is no longer of as elementary importance as previously assumed. This means that with strains in this range it is not possible to use the thickest wire as before only in the center of the tension member, but also wire configurations can be selected where a wire with the largest diameter, for example, in an outer wire or stranded layer is present.

The bending stress σb of the thickest wire in a tension member of an elevator support means results approximately as a function of the smallest pulley diameter D, over which the support means is guided, the modulus of elasticity E (also called modulus of elasticity) of the thickest wire and its wire diameter δ according to the following equation: σb = (δ * E) / D. Taking into account this relationship, the composition of the elevator with its possibly different pulley diameters and the suspension means with its at least one tension member and its casing can be coordinated.

If the bending stress σb, which is induced in the wire of the tension member, which has the largest wire diameter, when running the suspension element over a disk with the smallest pulley diameter D, is increased in the range between 450N / mm ² to 750N / mm ² , the service life is increased of the train carrier. The best results in terms of service life and cost-effectiveness are achieved with suspension elements whose tension members undergo bending stress σb in the range of σb = 490N / mm ² to 660N / mm ² when the suspension element runs over a disc with the smallest pulley diameter D in its thickest wires.

The above information applies in particular to the common types of steel wire whose moduli are between 140kN / mm ² and 230kN / mm ² ; and in particular for wires of stainless steels with moduli of elasticity between 150kN / mm ² and 160kN / mm ² and of high strength, alloyed steels with moduli of elasticity between 160kN / mm ² and 230kN / mm ²

For steel wires with an average modulus of elasticity of about 190 kN / mm ² to about 210 kN / mm ² for the wires with the largest wire diameter D in the tensile member of a suspension medium have very good values for the life with sufficient efficiency, if the ratio of the disc diameter D der smallest disc in the elevator system to the wire diameter δ of the thickest wire in the tensile carrier in the range of D / δ 200 to 600, preferably in the range of D / δ = 300 to 500.

Particularly economical can be a lift system described above, if the disc with the smallest disc diameter D is the traction sheave, because then a smaller light engine can be used. If all disks are the same size as the traction sheave, the space required for these disks is also small, which of course can reduce the service life of the suspension element.

If the suspension element comprises more than one tension member (18) extending in the longitudinal direction of the suspension element (12), and if these tension members, viewed in the width of the suspension element, are arranged next to one another and at a distance from one another in a plane, then pulleys with smaller pulley diameters and a smaller pulley can generally be used be used in the elevator system lighter than in the use of support means of equal capacity, which have only one tension member or more tension members in different "layers" on top of each other. In this way space and costs can be saved.

If the suspension element is provided on its traction sheave facing the traction side with a plurality of ribs running parallel in the longitudinal direction of the suspension element and at the same time the traction sheave in its periphery with circumferentially extending grooves corresponding to the ribs of the suspension element, the suspension element can be better guided in the traction sheave.

In addition, if the grooves of the traction sheave are provided with a deeper groove bottom, so that a wedge effect results when the grooves interact with the ribs, the traction is significantly increased and can be adjusted depending on the selected wedge angle of the ribs or grooves.

In a particular embodiment of the elevator installation, the grooves of the traction sheave are wedge-shaped, in particular having a triangular or trapezoidal cross section. The wedge shape results in each groove by two side walls, also called groove flanks, which run towards one another in a flank angle β '. Particularly good guiding and traction properties result from a flank angle β 'of 81 ° to 120 °, even better at a flank angle β' of 83 ° to 105 °, even better in the range of 85 ° to 95 ° and the best at a flank angle β 'of 90 °.

For a good guidance of the suspension element in the elevator installation, in addition to the traction sheave, other sheaves may also be provided with corresponding grooves which correspond to the ribs of the suspension element on the traction side thereof.

Also, in a guide of the support means with counterbending advantageously the support means may be provided on one of its traction side opposite rear with a guide rib, which corresponds to a guide groove in a guide, support or deflection.

In order to obtain a support means for moving and possibly carrying an elevator car, which has good traction properties and a high load capacity, a support means is provided which comprises a body made of a polymer and at least one embedded in the body, extending in the longitudinal direction of the support means traction , The tension member is made of wires and is available as a strand or rope. In order for the suspension element in the elevator installation to have a long service life, the tension member for the suspension element is constructed in such a way that the bending stress σb of the wire with the largest wire diameter δ in the tension member is bent by a smallest bending radius r in a range between σb = 350N / mm ² to 900N / mm ² . The bending stress results in dependence on the modulus of elasticity E and the diameter δ of the thickest wire and in dependence on the smallest intended bending radius r.

The mutual dependencies can be simplified mathematically represent. The bending stress σb is given by the following equation: σb = (δ * E) / 2r. The smallest intended bending radius r results in consultation with the elevator builder from the diameter D of the smallest disk provided in the elevator installation as: r = D / 2.

The body of the suspension element is made of a polymer, preferably an elastomer. Elastomers can be adjusted in their hardness and bring in addition to this necessary hardness at the same time a sufficiently high wear resistance and elasticity. The temperature and weathering resistance and other properties of the elastomers also increase the service life of the suspension element. If the elastomer is also a thermoplastic elastomer, the suspension element with its body and the embedded tension members can be produced in a particularly simple and cost-effective manner, for example by extrusion. Depending on the required friction factor between the traction side of the suspension element and the traction sheave or rear side of the suspension element and another disc, the suspension element may be constructed of a single elastomer or of different elastomers, eg in layers, with different properties.

Particularly suitable are polyurethane, in particular thermoplastic, ether-based polyurethane, polyamide, natural and synthetic rubber, in particular NBR, HNBR, EPM and EPDM as a material for the body of the suspension element. Also chloroprene can be used in the body especially as an adhesive.

For the consideration of special properties, it is also possible to provide the side with the traction side and / or the back of the support means with a coating. This coating can be applied, for example by flocking or extrusion, or even be sprayed, laminated or glued. It may also preferably be a woven fabric of natural fibers such as hemp or cotton or of synthetic fibers such as nylon, polyester, PVC, PTFE, PAN, polyamide or a blend of two or more of these types of fibers.

In a first embodiment, the support means has a bending stress σb when bending by a smallest bending radius r in the thickest wire of its at least one tension member with the largest wire diameter δ, which is in the range of σb = 450N / mm ² to 750N / mm ² and preferably in the range of σb = 490N / mm ² to 660N / mm ² .

In a further embodiment of the suspension means, the wire with the largest wire diameter δ has a modulus of elasticity of about 210'000 N / mm ^2. For this embodiment, a particularly long service life of the suspension element results in very good economy if the ratio of the smallest bending radius r to the wire diameter δ of the thickest wire in the tensile carrier 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 a further embodiment, the suspension element exhibits, in addition to at least one of the properties described above, a tension member in which the strands or wires are at least 0.03 mm apart from each other, at least in an outermost wire or strand layer. The distance is greater, the greater the viscosity of the polymer embedding the tension member when embedding the tension member.

In a further embodiment, the more strand layers and / or wire layers there are, the more strand layers or wire layers in this form are spaced apart from each other, as viewed from the outside inwards.

In a further embodiment, both apply. This means that in at least one strand layer both the strands and the outer wires in these outer strands are at least 0.03 mm apart.

This measure (s) ensures a good mechanical connection of the tension member with the material of the suspension element body, which further increases the service life of the suspension element. It should be noted here that the spacing can be provided in the circumferential direction and / or in the radial direction.

In a particular embodiment, the support means more than one in the longitudinal direction of the support means (12) extending tensile carriers, wherein the tension members, viewed in the width of the support means, are arranged in a plane next to each other and spaced from each other. In this way, the load that must be absorbed by the support means distributed to the plurality of smaller diameter tensile carriers, whereby the smallest bending radius r can be chosen smaller for this suspension means. Due to the distribution of the tension members in only one plane, the bending stress and the surface pressure can also be distributed relatively evenly over all tension members, which increases the service life and ensures a smoother running of the suspension element over the discs.

In further embodiments, the support means comprises at least one tension member which is in the form of a stranded wire with a core of 3 wires each having a diameter a and two wire layers surrounding the core with wire diameters b (1st wire layer) and wire diameters c (2nd wire layer ) is trained. A particularly advantageous configuration of this kind is (3a-9b-15c), where a, b, c are wire diameters which are all different, all the same or only partially the same, depending on the configuration. The numbers in front of the wire diameters indicate the number of wires with this diameter. The bracket indicates that it is a strand, with the number-letter combinations from left to right read the configuration of the wires from the middle of the wire to the outside. The bars between the digit-letter combinations separate the core / core of the strand from the next layer and this layer from the next. Number-letter combinations that are connected with a hyphen, but are in a common parenthesis, so belong to different layers of a strand.

In another embodiment, the support means comprises at least one tension member having a wire configuration (1f-6e-6d + 6c) W + n * (1b + 6a), where n is an integer between 5 and 10, and where the smallest bend radius r at least r ≥ 30mm. a, b, c, d, e, f are wire diameters which, depending on the configuration, are all different, all the same or only partially the same, and W stands for a Warrington configuration, as described, for example, in DIN EN 12385-2: 2002 under 3.2.9 picture 7 is shown. As can be seen from the wire configuration nomenclature, this is a Warrington core strand comprising a core wire of diameter f, a first wire layer of 6 wires of diameter e, and a second wire layer of 6 wires of diameter d and c (Number-letter combinations connected with "+"). This core strand is surrounded by a number of strands n, each comprising a core wire with a diameter b and a first wire layer with 6 wires of diameter a.

In another embodiment, the support means comprises at least one tension member having 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 ≥ 50mm , a, b, c, d, are wire diameters which, depending on the configuration, are all different, all the same or only partially the same.

Again, in another embodiment, the support means comprises at least one tension member having a wire configuration (3f + 3e + 6d) W + n * (3c + 3b + 6a) W, where n is an integer between 5 and 10, and wherein smallest bending radius r at least r ≥ 40mm. a, b, c, d, e, f are wire diameters that are all different, all the same or only partially the same, and W is a Warrington configuration.

In yet another embodiment, the at least one tensile member of the suspension means has a wire configuration (1e + 6d + 12c) + n * (1b + 6a) W, where n is an integer between and 10, and at least the smallest bend radius r r ≥ 32mm. a, b, c, d, e are Wire diameter, which are different depending on the configuration, all the same or only partially the same. W stands for a Warrington configuration.

Particularly good torque characteristics and good cable stability have the aforementioned embodiments of the support means when the tension members SZS or ZSZ are beaten (see DIN EN 1235-2: 2002 under "3.8 direction of impact and stroke types"), ie when the tension members are beaten left-right-left or right-left-right. The torque characteristics are even better when one, two or three SZS beaten tension members alternate with a respective same number ZSZ beaten tension members and all tension members should be embedded in a plane next to each other in the polymer shells. The number of ZSZ beaten and the SZS beaten tension members should be the same size over the entire suspension.

In a further embodiment, the suspension element has a plurality of the tension members described above, with preferably all tension members having the same wire configuration, so that the load-bearing strength, stress ratios and elongation properties of all tension members are the same.

In another embodiment, the support means comprises a plurality of tension members with different wire configurations, the configurations having their specific properties being adapted to the position in the suspension element (central or external). This can be advantageous if the stresses on the tension members despite the arrangement in a plane position-dependent large deviations.

In a particular embodiment, the suspension element is designed on one side as a traction side, which has a plurality of ribs running parallel in the longitudinal direction of the suspension element. In this case, it is advantageous if the support means also has more than one in the longitudinal direction of the support means extending tension members.

In a further embodiment, the support means the traction side is provided with a plurality of longitudinally extending in the longitudinal direction of the support means ribs having a wedge-shaped, in particular a triangular or trapezoidal cross-section with a flank angle β in the range of 81 ° to 120 °, more preferably from 83 ° to 105 ° or 85 ° to 95 ° and best 90 ° exhibit. The advantages correspond to those that have already been addressed in a traction sheave with analogously designed grooves.

Particularly uniformly, the tension and the load can be distributed to the tension members of a suspension element if each rib on the traction side of a suspension element is assigned two tension members. It is particularly advantageous in this case if the tension members are each arranged in the region of the vertical projection P of an edge of the rib. In particular, the tension members should be arranged centrally above the projection of the flank.

It is also very advantageous if each rib of the suspension element is assigned exactly one tension member which is arranged centrally with respect to the two flanks of the rib. Such an embodiment also allows a very even distribution of forces on all tensile carriers of the suspension element. With the same rib size, traction carriers with a larger diameter can also be used without negatively affecting the running properties.

In a further embodiment, the suspension element has exactly two ribs on the traction side. Such a suspension means offers in addition to the advantages of having a V-ribbed belt, the advantage that the number of suspension elements can be tuned very accurately to the load to be carried in the elevator. In a particular embodiment, this support means has a guide rib on its rear side opposite the traction side, in order to be guided against a correspondingly executed disc with guide groove in counterbending, without additional measures for a lateral guidance of the suspension means must be taken.

In a further special embodiment, such a support means may also be higher than wide, whereby upon bending higher internal stress in the support means body arise, which in turn reduces the risk of jamming of the support means in a grooved disc.

Further advantageous embodiments and modifications of the invention will become apparent from the other claims. As already apparent from the previous description, the features of the various embodiments can be combined with each other and are not limited to the examples in the context of which they are described. This will be apparent from the following explanations of the invention with reference to the accompanying diagrammatic drawings. The embodiments illustrated in the respective drawings each show certain features in combination with each other. However, this does not mean that they can be used meaningfully only in the combination shown. On the contrary, they can equally well be combined with features of other examples shown or described.

Fig. 1

einen zu einer Aufzugskabinenfront parallelen Schnitt durch eine erfndungsgemässe Aufzugsanlage;

Fig. 2a

eine perspektivische Ansicht einer Rippenseite eines ersten Ausführungsbeispiels eines Tragmittels gemäss Erfindung in Form eines Keilrippenriemens;

Fig. 2b

eine Querschnitts-Ansicht des Tragmittels gemäss Fig. 2 mit verschiedenen Beispielen für mögliche Rippenausgestaltungen;

Fig.3a

eine perspektivische Ansicht eines zweiten Ausführungsbeispiels eines Tragmittels gemäss Erfindung in Form eines flachen Riemens;

Fig.3b

vergrössert einen Ausschnitt des flachen Riemens aus Fig. 3a

Fig. 4a

einen Schnitt parallel zur Rotationsachse einer Treibscheibe einer Aufzugsanlage und durch ein darüber laufendes weiteres Ausführungsbeispiel eines Tragmittels;

Fig. 4b

einen Schnitt durch noch ein weiteres Ausführungsbeispiel eines Tragmittels der Aufzugsanlage senkrecht zu dessen Zugträgern;

Fig. 5

einen Schnitt analog zu dem in Fig. 4b durch noch ein anderes Ausführungsbeispiel eines Tragmittels der Aufzugsanlage;

Fig. 6

einen Schnitt analog zu dem in Fig. 4b durch noch ein anderes Ausführungsbeispiel eines Tragmittels der Aufzugsanlage;

Fig. 7

einen Schnitt analog zu dem in Fig. 4b durch noch ein weiteres Ausführungsbeispiel eines Tragmittels der Aufzugsanlage;

Fig. 8

einen Querschnitt durch ein erstes Ausführungsbeispiel eines Stahldraht-Zugträgers ;

Fig. 9

einen Querschnitt durch ein zweites Ausführungsbeispiel eines Stahldraht-Zugträgers;

Fig. 10

einen Querschnitt durch ein drittes Ausführungsbeispiel eines Stahldraht-Zugträgers;

Fig. 11

einen Querschnitt durch ein viertes Ausführungsbeispiel eines Stahldraht-Zugträgers;

The figures show by way of example and purely schematically:

Fig. 1

a section parallel to an elevator car front through a lift installation according to the invention;

Fig. 2a

a perspective view of a rib side of a first embodiment of a support means according to the invention in the form of a V-ribbed belt;

Fig. 2b

a cross-sectional view of the support means according to Fig. 2 with various examples of possible rib designs;

3a

a perspective view of a second embodiment of a support means according to the invention in the form of a flat belt;

3b

enlarges a section of the flat belt Fig. 3a

Fig. 4a

a section parallel to the axis of rotation of a traction sheave of an elevator installation and by a further running embodiment of a support means;

Fig. 4b

a section through yet another embodiment of a support means of the elevator system perpendicular to the tension members;

Fig. 5

a section analogous to that in Fig. 4b by still another embodiment of a suspension means of the elevator installation;

Fig. 6

a section analogous to that in Fig. 4b by still another embodiment of a suspension means of the elevator installation;

Fig. 7

a section analogous to that in Fig. 4b by still another embodiment of a suspension means of the elevator installation;

Fig. 8

a cross section through a first embodiment of a steel wire tension member;

Fig. 9

a cross section through a second embodiment of a steel wire tension member;

Fig. 10

a cross section through a third embodiment of a steel wire tension member;

Fig. 11

a cross-section through a fourth embodiment of a steel wire tension member;

Fig. 1 2 shows a section through an elevator system 9 according to the invention in an elevator shaft 1. Shown are essentially a drive unit 2 arranged at the top in the elevator shaft 1 with a traction sheave 4.1 and an elevator car 3 guided on cabin guide rails 5 with cabin sheaves 4.2 mounted below the cabin floor 6. In addition, a guided counterweight guide rails 7 counterweight 8 with a Gegengewichtstragscheibe 4.3 and a support means 12 which carries the elevator car 3 and the counterweight 8 and at the same time transmits the driving force of the traction sheave 4.1 of the drive unit 2 to the elevator car 3 and the counterweight 8.

The support means 12 has at least two elements, which are also referred to hereinafter simply as support means 12, although they exercise not only supporting but also driving function. Only one suspension element 12 is shown. However, it is clear to the elevator expert that, for safety reasons, at least two suspension elements 12 are generally present in an elevator installation. Depending on the cabin weight, suspension and carrying capacity of the support means 12, these can be used parallel to one another and running in the same direction or else in another configuration. Two or more parallel and running in the same direction support means 12 may be combined to form a suspension element strand, in which case either this one suspension element strand or even several suspension element strands may be provided in an elevator system. These can also be arranged parallel and in the same direction running or in any other configuration in the elevator system.

Contrary to in Fig. 1 1: 1, 4: 1 elevator systems or any other suspension conditions can be designed as elevator systems according to the invention. Also, the drive with the traction sheave 4.1 does not necessarily have to be arranged at the top of the elevator shaft but can also be arranged, for example, in the shaft bottom or in the shaft in a gap next to the trajectory of the cabin and an adjacent shaft wall and in particular also above a shaft door. The element referred to here as a suspension element 12 can also be used as a pure suspension means or pure drive means.

The suspension element 12 is in the in Fig. 1 shown embodiment of an inventive elevator system 9 at one of its ends below the traction sheave 4.1 attached to a first support means fixed point 10. From this it extends down to a counterweight 8 arranged on the counterweight pulley 4.3, wraps around this and extends from this to the traction sheave 4.1 It wraps around the traction sheave 4.1 in this case at about 180 ° and extends along the counterweight side cabin wall down. Then it undermines the car 3, wherein on each side of the elevator car 3 each below the elevator car 3 mounted Kabinentragsclieibe 4.2 wraps around each about 90 °, and extends along the counterweight 8 remote cabin wall up to a second Tragmittelfixpunkt 11. To a To ensure better guidance of the support means 12 under the cabin floor 6 through, 4.2 guide discs 4.4 are provided between the two car washers. This is particularly useful for long distances between the cabin pulleys 4.2.

In the in Fig. 1 As shown in an example of an elevator installation 9 according to the invention, a suspension element 12 according to the invention is used with tension members according to the invention and is guided over a traction sheave 4.1 tuned to the suspension element 12 according to the invention. As a result, the traction sheave 4.1 of the elevator installation 9 according to the invention can be selected to be very small, which reduces the space requirement and enables the use of a lighter, smaller machine. The plane of the traction sheave 4.1 is arranged at right angles to the counterweight-side cabin wall and its vertical projection is outside the vertical projection of the elevator car 3. The small pulley diameter makes it possible to keep the gap between the cabin wall and the hoistway wall of the hoistway 1 opposite it very small. Due to the small size and the low weight of the drive unit 2, it is possible to mount the drive unit 2 on one or more of the guide rails 5, 7 and support. In this way, it is possible to introduce the entire dynamic and static loads of the cabin and the engine as well as vibrations and noises of the running engine instead of in a shaft wall through the guide rails 5, 7 in the shaft bottom.

Fig. 2a , Perspective shows a portion of a preferred embodiment of a support means 12 according to the invention. In this embodiment, the support means 12 as a V-ribbed belt with a flat back 17 and one provided with ribs 20 Traction side 18 is formed. Evident are its belt body 15 with wedge-shaped ribs 20 and embedded in the body 15 according to the invention tensile carriers 22, which are arranged in a plane next to each other and spaced from each other. As in Fig. 2b illustrated, it is possible the ribs 20 viewed in cross section rather than trapezoidal ( 2a ) also triangular ( Fig. 2b left) or triangular with a rounded tip ( Fig. 2b right). Pro rib 20 of the designed as V-ribbed belt support means 12 two inventive tension members 22 are provided, which are each arranged centrally above a projection surface 70 of a flank 24 of the rib 20 of the support means. Per rib 20 of the support means 12 is ever one in its overall torque dextrorotatory tension member 22, designated "R", and in its overall torque left-turning tension member 22, designated "L", is provided. In this way, the torques of the individual tension members 22 should cancel each other and the support means 12 torque should be free.

Another example of a suspension means according to the invention is shown in FIGS Fig. 3a, 3b shown. This support means is configured both on its traction side 18 and its rear side 17 with a flat surface. Tensile carriers 22 according to the invention are arranged next to one another in a plane, as in the previous example. They are embedded at uniform intervals in the polymer of the body 15 of the support means 12 and selected in number and in their torques so that their torques over the entire support means 12 give up. The material of the body 15 is arranged between and around each tension member 12 around. In order to meet the specific requirements for the traction side 18 and the opposite rear side 17 (eg different hardness, wear resistance, friction coefficients), the illustrated suspension element 12 has a multilayer structure. On the traction side is located above the polymer of the base body 15, a harder base layer 15 a, which is provided with a coating of wear-resistant fabric 62. The hard support layer 15a is advantageous in terms of a uniform force distribution in the support means 12 when running on the traction sheave 4.1. The wear-resistant coating 61 with the fabric 62 protects against abrasion. On the rear side of the actual body 15 of the suspension element 12, a softer cover layer 15b is provided, at least in relation to the base layer 15a, which permits low-noise running over pulleys 4.2, 4.3, 4.4 of the elevator installation 9 under counterbending. a coating 61, which contains, for example, polytetrafluoroethylene, reduces the friction during running of the support means 12 via these discs 4.2, 4.3, 4.4 under counter-bending, which is the silent and low-wear sliding and rolling over this Slices further improved. The thickness of the individual layers is not shown to scale and should be selected according to the requirements.

The tension members 22 in the suspension elements 12 according to the invention are produced by stranding from steel wires of high strength (strength values in the range from 1770 N / mm ² to approx. 3000 N / mm ² ). The stranding is designed in such a way that bending of a suspension element 22 provided with such a tension member 22 by a smallest bending radius r has a bending stress σb in the thickest wire with the largest wire diameter δg in the tension member 22, which is in the range of 300N / mm ² and 900N / mm ² lies. According to the invention, for the use of this suspension element 12 in the elevator installation, the smallest bending radius r is equal to half the diameter of the smallest disk in the elevator installation, ie r = D / 2.

The design of the support means 12 and the tension member 22 in the support means 12 according to the invention is such that when running the support means 12 with a tension member 22 over a smallest disc with a smallest pulley diameter D in the elevator system 9, the bending stress σb for the thickest wire of the tension member 22 as a function of its modulus of elasticity E and its diameter δ in accordance with the following equation: σb = (δ * E) / or σb = (δ * E) / 2r.

Examples of inventive tension members 22 are in the Fig. 7 to 12 shown. In the accompanying tables "I" under "Cord" down with a, b, c, d, e, f are given by way of example possible wire diameter δ individual wire types in mm. The number N of wires of the individual wire types a, b, c, d, e, f present in the tension member 22 is shown to the right of the wire diameter in mm; including the sum Σ of all wires 42 in the tension member 22. Right next to the indication "d comput." the calculated diameter d of the tension member 22 is given in mm. Below, next to "d eff." is the diameter averaged from measurements d eff. of the tension member 22 in mm. Below, to the right of the indication "A (mm ² )" is the cross-sectional area of the tension member 22 in mm ² indicated. In the accompanying table II are under "examples" for different bending radii r and wheel diameter D exemplified bending stress σb for the thickest wire 43 in the tension member 22, the ratio of pulley diameter D to diameter δ of the thickest wire 43 "D / δ" and the ratio of pulley diameter D to effective pulley diameter "D / d eff".

In Fig. 7 a tension member 22 is shown, which according to the standardized nomenclature (see DIN EN 1235-2: 2002 (D)) a central strand 40 with a total of 19 individual wires 42 in seal configuration (1 + 6 + 12) with a central wire e a first, inner wire layer 46 to the central wire e with wires d and a second, outer wire layer 48 with wires c , This gives the central strand 40 a configuration (1e + 6d + 12c). Furthermore, the tension member 22 comprises a first strand layer 50 with 8 outer strands 44, each having a central wire b and 6 outer wires a, thus a total configuration 8x (1b + 6a). This results in a tension member 22, also referred to in the accompanying Table 7 "Cord", with a simplified nomenclature 19 + 8x7.

In the Fig. 7 shown configuration of the tension member 22 has its thickest wire 43 with the largest diameter δ = e in the middle as the central wire of the central strand 40. With a smallest bending radius of 36mm or a smallest disc diameter in a lift system 9 of 72mm results for this thickest wire 43 is a bending stress σb of σb = 554N / mm ² , the ratio of pulley diameter D to wire diameter δ of the thickest wire 43 D / δ = 379 and the ratio of pulley diameter D to the effective diameter d eff of the tension member 22 D / d eff = 41.5. For a somewhat larger radius r or disc diameter D of r = 44mm, D = 87mm, the result is: σb = 459N / mm ² , D / δ = 458, D / d eff = 50.

In the in Fig. 8a and 8b As shown, the tension member 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 bending radius r is at least r ≥ 32mm is. In Fig. 8a a configuration is shown in which n = 9, the central strand 40 has a Warrington configuration (1xf-6xe-6xd + 6xc) or written with the diameters of the individual wire types in μm (1x210-6x200-6x160 + 6x220) and the 9 outer strands 44 each show a central wire with wire diameter δ: b = 140 μm and 6 outer wires with the same wire diameter δ: a = 140 μm, resulting in a total cord 19 + 9x7 (see Table 8a.I).

The second embodiment of this configuration in Fig. 8b shows the same central strand 40 with the same Warrington construction (1xf-6xe-6xd + 6xd) and the same Wire diameters δ: f = 210μm, e = 200μm, d = 160μm, c = 220μm. Instead of the 9 outer strands 44 with seven individual wires 42, however, 8 outer strands 44 of the configuration (1b + 6a) are provided in this embodiment. The wire diameters δ of the individual wires 42 are adjusted accordingly here b = 150 μm, a = 150 μm. As can be seen from the attached tables (8b.1 and 8b.II), the bending stress σb in the thickest wires 43 of diameter δ = c and the ratios of D / δ and D / d eff. although depending on the pulley diameter D and the bending radius r between the two embodiments 8a and 8b but bending stress σb for the thickest wire c and the ratio of D / δ does not change. The situation is different for the calculated diameter d rechn and d eff, the cross-sectional area A and above all the load capacity FZM of the tension member 22 over the number of wires N. The tension member 22 from example 8a here has lower values everywhere than the tension member 22 from example 8b.

The embodiment in Fig. 9 shows a tensile member 22 having a basic wire configuration (3f + 3e + 3d) + n * (3c + 3b + 3a), where n is an integer between 5 and 10, and where the smallest bending radius r is at least r ≥ 30mm. Concretely represented is a configuration with n = 6; a = 0.17mm, b = 0.25mm, c = 0.22mm, d = 0.20mm, e = 0.30mm, f = 0.25mm. The thickest wire 43 with the largest wire diameter δ is the wire with diameter δ = e = 0.30mm. It belongs to the central strand 40. For bends around smallest bending radii r between 30 mm and 75 mm, which corresponds to disc diameters D of 72 mm to 150 mm (see Table 9.II), the bending stresses σb for the thickest wire 43 are in the range of σb = 875N / mm ² to 420N / mm ² . The total diameter d of the tension member 22 is about 2.5 mm, with a load capacity FZM over all wires N of about 7330N / mm ^{2 is} achieved.

In Fig. 10 an embodiments of a tension member 22 according to the invention for a support means 12 according to the invention is shown as a strand with a core 41 of 3 wires with a diameter a and two surrounding the soul wire layers 46, 48 with wire diameters b (1st wire layer 46) and wire diameters c (2nd wire layer 48) is formed, that is, a configuration (3a-9b-15c). For wire diameters δ of a = 0.27mm; b = 0.27 mm and c = 0.30 mm are the thickest wires 43 in the tensile member 22, the wires with the diameter δ = c, which form the soul 41 of this tension member 22. In Table 10. II the bending stresses σb are given for these thickest wires 43 with diameter δ = c, if a suspension element 12 are guided and bent with such a tensile carrier according to the invention 22 with different bending radii r and on different sized discs with disc diameters D. In addition, the ratios are "D / d eff". and "D / δ". As can be seen from the table 10. II, the bending stress σb at bending radii of r = 36 mm or converted to an elevator with disc diameters D = 72 mm at σb = 875N / mm ² ; the ratio of D / δ = 240.

Fig. 11 shows an embodiment of a tension member 22 with a central strand 40 according to (3e + 3d-15c) and 8 outer seats 44 according to (1b + 6a), the central strand 40 a core 41 with 3 central wires with diameter e and three fillers with diameter d and a Wire layer 46 has 15 wires with diameter c. The diameter d of the tension member is about 1.8 to 1.9 mm. Further values for this configuration can be found in Tables 11.I and 11.II.

Referring again to another embodiment of a tension member 22 having a basic wire configuration (3d + 7c) + n * (3b + 8a) and n equal to an integer between 5 and 10 Fig. 12 , In this case, n equals 6 (n = 6) and the smallest bending radius r ≥ 32mm. The diameter d of the tension member 22 is about 2.5mm, the bending stress σb for the thickest wire 43 with the largest wire diameter δ (wire diameter c = 0.27mm) is at bending radii r between 36mm and 75mm, which disc diameters D from 72mm to 150mm corresponds (see Table 12.II), the bending stresses σb for this thickest wire 43 in the range of σb = 788N / mm ² to 378N / mm ² . The overall diameter of the tension member 22 is about 2.5mm, with a load capacity FZM over all wires N of about 7450N / mm ^{2 is} achieved. Further values for this configuration can be found in Tables 12.1 and 12.II.

Particularly good torque properties and a good cable stability have the aforementioned embodiments of the tension member 22, when these SZS or ZSZ are beaten (see DIN EN 1235-2: 2002 under "3.8 direction of impact and stroke types"), ie when the tension members are beaten left-right-left or right-left-right. Even better are the torque characteristics when in a suspension element 12 each one, two or three SZS beaten tension members alternate with an equal number ZSZ beaten tension members and these are embedded in a plane next to each other in the support means body 15. The The total number of the ZSZ beaten and the SZS beaten train carrier should be the same.

For steel wires with an average modulus of elasticity of about 190 kN / mm ² to about 210 kN / mm ² for the wires with the largest wire diameter D in the tensile member of a suspension medium have very good values for the life with sufficient efficiency, if the ratio of the disc diameter D der smallest disc in the elevator system to the wire diameter δ of the thickest wire in the tensile carrier in the range of D / δ = 700 to 280, preferably in the range of D / δ = 600 to 320.

As already mentioned above, tensile members, as exemplified in the Fig. 7 to 12 illustrated and explained according to the invention are used in suspension means 12 of an elevator system according to the invention. The bending stress σb in the thickest wire 43 with the largest wire diameter δ of the tension member 22 in the suspension element 12 is then bent by a smallest bending radius r or by a smallest pulley with pulley diameter D in the elevator installation in the range of σb = 300N / mm ² to 900N / mm ² better in the range of σb = 450N / mm ² to 750N / mm ^2, and more preferably in the range of σb = 490N / mm ² to 660N / mm ² .

The above information applies in particular to the common types of steel wire whose moduli are between 140kN / mm ² and 230kN / mm ² ; and in particular for wires of stainless steels with moduli of elasticity between 150kN / mm ² and 160kN / mm ² and of high strength, alloyed steels with moduli of elasticity between 160kN / mm ² and 230kN / mm ²

Support means 12 with such tension members 22 may be designed as a flat belt, as shown in FIG Fig. 3a, 3b is shown. Such support means 12 are preferably used in elevators 9, which are equipped with flat and / or cambered discs 4.1,4.2, 4.3, 4.4, and show as needed also flanged wheels for better guidance.

But also rope-like support means with a circular cross-section and one or more encased tension members can be sensibly configured with these inventive tension members 22. Elevator systems 9, which are equipped with such support means 12, preferably have discs 4.1, 4.2, 4.3, 4.4 with semicircular to wedge-like grooves along its circumference.

Based on a designed as V-ribbed belt support means 12, as it is eg in Fig. 2a, 2b is shown below, an elevator system according to the invention 9, as shown in Fig. 1 is explained in more detail. The suspension element 12 is guided with its traction side 18 via the traction sheave 4.1, the counterweight sheave 4.3 and the guide sheaves 4.4, these are correspondingly provided at their periphery with grooves 35 which are formed complementary to the ribs 20 of the support means 20. Where the V-ribbed belt 12 wraps around one of the pulleys 4.1, 4.3 and 4.4, its ribs 20 lie in corresponding grooves 35 of the pulley, thus ensuring perfect guidance of the suspension element 12 on these pulleys.

About the Kabinentragscheiben 4.2, the V-ribbed belt 12 is guided with a reverse bend, ie the ribs 20 of the V-ribbed belt 12 are running on these discs on its side facing away from the Kabinentragscheiben 4.2 back 17 which is designed here as a flat side. For better lateral guidance of the V-ribbed belt 12, the car washers 4.2 can have lateral on-board discs. Another possibility to guide the support means laterally, is to arrange on the path of the support means 12 between the two car washers 4.2 two guide discs 4.4, as shown in this particular example. How out Fig. 1 it can be seen that the support means 12 is guided between the car washers 4.2 with its rib side over the provided with corresponding grooves guide discs 4.4. The grooves of the guide discs 4.4 cooperate with the ribs of the V-ribbed belt 12 as a side guide, so that the Kabinentragscheiben 4.2 require no on-board discs. This variant is advantageous because it causes no lateral wear on the support means 12 in contrast to a lateral guide means of flanged wheels. Depending on Kabinendiniension, selected suspension and interaction of the discs with the support means, it is also possible to work without 4.4 guide plates between the Kabinentragscheiben 4.2 or instead of the shown two guide discs 4.4 under the cab 3 only one or more than 4.4 guide plates. In general, it is also possible to carry the suspension means instead of under the cabin on the cabin on the other side of the cabin (not shown).

As an example of the Fig. 4a shown, the traction sheave 4.1 not only grooves 35 in its periphery, but also in their grooves 35 a groove bottom 36 which is lower than the trapezoidal flattened in this example tips of the engaging ribs 20 of the V-ribbed belt 12. In this way act on the traction sheave 4.1 only flanks 24 of the ribs 20 of the V-ribbed belt 12 with flanks 38 of the grooves 35 of the traction sheave 4.1 together, so that between the grooves 35 of the traction sheave 4.1 and the ribs 20 of the V-ribbed belt 12, a wedge effect that improves traction. Further, the wedge effect can be improved if the lying between the grooves 35 of the traction sheave 4.1 circumferentially extending ridges 37 of the traction sheave 4.1 are slightly less high than the recesses 26 between the ribs 20 of the support means 12 are deep. In this way, results in the meeting of the recesses 26 with the elevations 38, a cavity 28. As a result, forces are effective only on the flanks 24 of the ribs 20 and the flanks 38 of the grooves 35. The support disks 4.2, 4.3 and guide disks 4.4 advantageously have grooves 35 without underlying groove bottom 36 and elevations 38 which are the same dimensions as the recesses 26 of the support means 12 on its traction side 18. This reduces the risk that the suspension means in the disk 4.2, 4.3, 4.4 jams and ensures good guidance with less traction.

In the in Fig. 1 shown elevator system 9 according to the diameter of all pulleys are the same. It is also conceivable that the pulleys have different size and the support and / or pulleys 4.2, 4.3, 4.4 have a larger diameter than the traction sheave 4.1 or have a smaller diameter than the traction sheave 4.1, or that discs 4.2, 4.3 are provided, of which one discs 4.2, 4.3, 4.4 have a larger diameter, the other a smaller diameter than the traction sheave 4.1. According to the invention, the suspension element used in the elevator installation 12 is provided with tension members 22, which are made of wires and present as a strand or rope. The wires in the tension member 22 may all have the same diameter or be different in thickness. According to the invention, the tension member is designed such that a bending stress σb in the thickest wire with the largest wire diameter δ of the tension member 22, when running the tension member 22 over a smallest disc with a smallest pulley diameter D in the elevator system depending on the elastic modulus E and the diameter δ of thickest wire according to the following equation gives: σb = (δ * E) / D The best ratio of efficiency of the elevator installation and life of the support means 12 results with a tension member 22, the thickest wire with the largest diameter D a bending stress σb in a range between σb = 300N / mm ² to 900N / mm ² .

Fig. 4a shows a cross section through a V-ribbed belt 12 according to the present invention, which comprises a belt body 15 and a plurality of tension members 22 embedded therein. 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 Polyamide (PA), polyethylene (PE), polycarbonate (PC), polychloroprene (CR), polyurethane (PU) and, in particular, for easier processing and thermoplastic elastomers, such as ether or ester-based thermoplastic polyurethane (TPU).

On its flat side 17 of the belt body 15 is provided with a cover layer 62, which comprises an impregnated fabric here. However, non-impregnated fabrics 61 may also be applied or coatings may be provided by extrusion, gluing, laminating, flocking.

In the in the FIGS. 2a, 2b and 4a Examples shown are each rib 20 on the traction side 18, two tension members 22 assigned. For a favorable power transmission between the discs 4 in the elevator installation and the tension members 22 in the suspension element 12, the tension members 22 are each arranged centrically above the vertical projection 70 of a flank 24 of the rib 20 ( Fig. 2b ).

If each rib 20 of the support element 12 designed as a V-ribbed belt is assigned two tension members 22 and arranged centrally above a flank 24 of the rib 20, they can optimally transmit the belt loads occurring in the V-ribbed belt per rib. These belt loads are on the one hand the transmission of pure tensile forces in the belt longitudinal direction. On the other hand, when wrapping a. Pulley 4.1 - 4.4 transmitted from the tension members 22 forces in the radial direction over the belt body 15 on the pulley 4.1, 4.2, 4.3, 4.4. The cross sections of the tension members 22 are dimensioned such that these radial forces do not cut through the belt body 15. In the case of wrap around a pulley in the tension members 22 additionally bending stresses due to the curvature of resting on the pulley support means 12 on. To this bending stresses in the tension members 22 as low as possible hold the forces to be transmitted per rib 20 on several tension members and particularly favorable distributed to two tension members as in Fig. 2a, 2b and 4a shown.

Like the embodiment in Fig. 4b However, it is also possible to provide more than two tension members 22 per rib 20. Shown are in Fig. 4b three tension members 22 per rib 20, wherein the ribs 20 viewed in cross-section are designed trapezoidal. The respective middle tension member is arranged centrally in the rib 20 and the two tension members framing it in the rib are preferably arranged again centrically over an edge 24. The latter is not mandatory. In addition to the number of three tension members shown here, four or five tension members per rib are conceivable, wherein also cross-sectional shapes of the ribs are conceivable, as in Fig. 2b are shown. Preferably, the distance X between a tension member and the traction side surface of the suspension element, or in other words the traktionsseitige coverage X of the tension member with the polymer material of the body 15 about 20% of the total thickness s of the support means 12 corresponds.

In contrast to the examples in FIGS. 2a, 2b and 4a , the suspension element 12 is in Fig. 4b on its flat side 17 is not provided with a coating. For this purpose, however, it has on its traction side 18 a coating 62 indicated by a dashed line, by means of which the friction coefficient and / or wear is adjusted in cooperation with the traction sheave 4.1 and / or another pulley 4.2, 4.3, 4.4 of the elevator installation 9 , Also, this coating 62 preferably comprises a fabric 61, in particular a nylon fabric.

In Fig. 5 a further embodiment of a support means 12 according to the invention is shown. As in Fig. 5 Good to see, in this example, the support means 12 on the traction side 18 per rib 20 only one tension member 22. With the same dimensioning of the support means 12 and its ribs 20, the tension members 22 can be larger in diameter with only one tension member 22 per rib 20, instead of two tension members per rib 20, with a tension member 22 per rib 20. Larger diameters of the tension members 22 allow the use of more wires or thicker wires. Both increases the same strength of the wires, the load capacity of the tension members 22, the latter also simplifies the stranding and reduces the cost per tension member 22. Preferably, the tension members 22 are each centrally located in their rib 20, this leads to a very uniform distribution of Zugträgerbelastung via the two edges 24 of each rib 20. In addition, the total thickness of the support means can be kept slightly lower.

Like the examples Fig. 2a, 2b and 4b has the support means example 12 from Fig. 5 on its flat back 17 also has a coating which in this example contains tetrafluoroethylene in order to reduce the coefficient of friction when interacting with deflecting disks 4.4 or support disks 4.2, 4.3. The layer may contain as diffusion layer polytetrafluoroethylene particles in the cladding material or be provided as a film-like coating based on polymer or fabric with polytetrafluoroethylene particles. The tetrafluoroethylene particles preferably have a particle size of 10 to 30 micrometers.

It applies to all the coatings mentioned that they can be applied over the entire length of the carrier 12 or only one or more specific lengths of the carrier 12. In particular, those lengths of the support means 12 may be coated, which cooperate with a seating of the car 3 or the counterweight 8, for example on a buffer in the pit, with the traction sheave.

Fig. 6 shows a support means 12 that on its traction side 18 also has ribs 20, each with two tension members 22. Specially on this support means 12 is that it has exactly two ribs 20 on its traction side 18 and additionally on its rear side 17 a guide rib 19. The guide rib 19 cooperates with deflection, guide and support disks 4.2, 4.3, 4.4, the have a corresponding guide groove to receive the guide rib 19 (not explicitly shown). The suspension means off Fig. 6 is higher than wide or at most the same height as wide. In a further embodiment, this support means can also be equipped with only one tension member 22 per rib or more than two tension members per rib, in particular 3, 4 or 5 tension members per rib. Like the other embodiments, it may be provided on the traction side and / or the back with a coating. Conversely, the other embodiments of the suspension element 12 shown here can also be provided with one or more guide ribs 19 on the rear side 17. These can be equal to or greater than the ribs 20 on the traction side 18 and can be made of a different material for better stability of the support means 12 or over the length of the support means 12 extending stabilizing elements (not shown) similar to the tension members 22 included.

As in Fig. 4b and 5 shown, the support means 12 have a flank angle β of about 90 °. The flank angle β is the angle enclosed by its two flanks 24 of a rib 20 of the suspension element 12. Experiments have shown that the flank angle β has a decisive influence on the development of noise and the formation of vibrations, and that for a designed as elevator support means V-ribbed belt edge angle β from 81 ° to 120 ° and better from 83 ° to 105 ° and even better from 85 ° to 95 ° are applicable. The best properties in this respect and also with regard to guidance are achieved with rib angles β of 90 °

Particularly simple suspension elements can be produced whose flank angle β in the ribs 20 is equal to the angles in the recesses 26. The same also applies to the production of grooved pulleys, which are fitted with grooves 35 or elevations 37 matching the intended suspension means, the flanks 38 of which each include a flank angle β 'in the groove 35 and the elevation 37.

From the Fig. 4b and 5 is also seen that small dimensions and low weight of a ribbed support means 12 are achieved in that the distances X between the outer contours of the tension members 12 and the surfaces / edges of the ribs 20 are made as small as possible. Optimal properties have resulted in tests for ribbed suspension elements 12, in which these distances X amount to at most 20% of the total thickness s of the suspension element. The total thickness s is to be understood as meaning the entire thickness of the belt body 15 including the ribs 20.

The mutual dependencies can be simplified mathematically represent. The bending stress σb then results according to the following equation: σb = (δ * E) / 2r. The smallest intended bending radius r results in consultation with the elevator builder from the diameter D of the smallest disk provided in the elevator installation as: r = D / 2

The bending stress σb of the thickest wire in a tension member of an elevator support means results approximately as a function of the smallest pulley diameter D, over which the support means is guided, the modulus of elasticity E (also called modulus of elasticity) of the thickest wire and its wire diameter δ according to the following equation: σb = (σ * E) / D. Taking into account this connection, the composition of the elevator can with their possibly different pulley diameters and the suspension means with its at least one tension member and its sheathing to be coordinated.

If the bending stress σb, which is induced in the wire of the tension member, which has the largest wire diameter, when running the suspension element through a disc with the smallest pulley diameter D, is increased in the range between 300 N / mm ² to 750 N / mm ² , the service life is increased of the train carrier. The best results in terms of service life and cost-effectiveness are achieved with suspension elements whose tension members undergo bending stress σb in the range of σb = 350N / mm ² to 650N / mm ² when the suspension element runs over a disc with the smallest pulley diameter D in its thickest wires.

As already mentioned above, in order to obtain an elevator installation with low maintenance costs, it is important, inter alia, to use a suspension element with a long service life in the installation. In addition, the cost can be reduced if a small lightweight motor with a small traction sheave can be used. The space required for an elevator installation can be further reduced if, in addition to the small traction sheave, additional disks with small diameters are used. Also advantageous for an elevator system is a well adapted to the defined requirements of this system traction between traction sheave and suspension element.

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.

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