EP2488436A1

EP2488436A1 - Elevator system and suspension for such a system

Info

Publication number: EP2488436A1
Application number: EP10761015A
Authority: EP
Inventors: Danilo Peric; Oliver Berner; Ernst Ach
Original assignee: Inventio AG
Current assignee: Inventio AG
Priority date: 2009-10-14
Filing date: 2010-10-06
Publication date: 2012-08-22
Anticipated expiration: 2030-10-06
Also published as: CN102574665B; RU2012117956A; CN102574665A; AU2010305872A1; EP2488436B1; MY183948A; WO2011045215A1; CL2012000935A1; ES2567783T3; BR112012008407A2; HK1174320A1; MX2012004353A; ZA201202550B; KR20120083907A; US20120211310A1; CA2777541A1

Abstract

The invention relates to an elevator system having a suspension and a suspension for supporting and/or moving at least one elevator car (3) in an elevator system (1), wherein the suspension (12) can be guided and driven at least by means of a sheave (4), in particular a traction sheave (4.1) of a drive machine (2) of an elevator system (1), and the suspension (12) comprises a body (15) made of a polymer and at least one tie beam (22) extending in the longitudinal direction of the suspension (12) and embedded in the body (15) and made of wires (42) and is present as a cord or rope. A thickest wire (43) having the greatest wire diameter δ in the tie beam (22) comprises a bending stress σb in a range from σb = 350N/mm² to 900N/mm² when bending the tie beam (18) about a least bending radius r, and wherein the bending stress σb results as a function of the elastic modulus E and the diameter δ of the thickest wire (26), according to the following equation: σb = (δ*E)/2r, wherein the suspension (12) is run about a smallest pulley having a least pulley diameter D in the elevator system (1), the pulley diameter D thereof corresponding to no more than two times the least bending radius r: D ≤ 2r.

Description

Elevator installation and suspension for such a system

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 support means carry the

Elevator car and the counterweight and the drive means transmit the required driving forces on 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 support and / or

Drive means only referred to as a support 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 attempts at jacketed traction sheaves and jacketed suspension elements can be dated to the beginning of the 20th century (see US 1047330 of 1912), which was preferred at that time worked with leather as a jacket material. With the provision of suitable synthetic sheath material by the polymer industry, elevator builders began to deal with polymer-sheathed suspension in the 1970's (see US 1362514 of 1974), where from the beginning polyurethane as sheath material played an important role (ibid.). The behavior of the metallic tension members in the polymeric sheath is for the

Life of a suspension medium of central importance. That has to different

Proposed proposals for simple interpretation rules, according to which a suspension with metallic tension members and a polymeric sheath should be created. For example, EP1555234 discloses a V-ribbed belt as the suspension element of an elevator installation with tensioned stranded steel wires, wherein the total cross-sectional area of all tension members is to 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 EP1555234 is such a tension member with a two-ply

Central strand 1 + 6 + 12 and 8 outer strands 1 + 6 shown without specific information on the wire diameters of the individual wires or the traction sheave would be made. For the

Tensile beam as a whole is given a diameter of about 2mm or less.

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 elevator hoists made of steel, which prescribe a ratio of pulley diameter D to wire diameter d of D / d> 40, EP1640307A proposes a design 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 beam with strands whose central wires each have a larger diameter than the surrounding outer wires, also discloses US546185B in the context of elevators, conveyor belts 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 US 4947638B trying 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.

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 can be pulleys, guide discs,

Cabin 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 disc-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, usually by so-called

Guide rails determines the trajectory of the car and possibly counterweight, and in or on which today usually all the components of the drive are included (machine room 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, particularly high strength steel wires, and is in the form of a strand or rope, all of which can be the same thickness and 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 is a

Selected suspension means, in which the bending stress 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 system in a range between ab = 350N / mm ² to 900N / mm ² . If the bending stresses for the thickest wire are chosen in this stress range, the position of the thickest wire in the tension member is no longer so elementary

Meaning, as previously assumed. That is, with tensions in this

Area it is possible the thickest wire no longer as before only in the center of the

Zugträgers use, but it can also be selected wire configurations, in where a wire with the largest diameter, for example, in an outer wire or stranded layer is present.

The bending stress 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: ob = (5 * 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, which is induced in the wire of the tension member, which has the largest wire diameter, when running the suspension element through a disk with the smallest pulley diameter D, is increased in the range between 450N / mm ² to 750N / mm ² , the life increases of the train carrier. The best results in terms of lifetime and

Economy are achieved with suspension elements, the tension member when running the

Tragmittels over a disc with the smallest disc diameter D in their thickest

Wires bending stress whether in the range of ob = 490N / mm ² to 660N / mm ² experienced. 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 made of stainless steels with moduli of elasticity between 150kN / mm ² and 160kN / mm ² and of high strength, alloyed steels with moduli between 160kN / mm ² and 230kN / mm ² For steel wires with an average modulus of elasticity of approximately 190kN / mm ² to about

210 kN / mm ² for the wires with the largest wire diameter D in the tension member of a suspension element have given very good values for the service life with sufficient efficiency, if the ratio of the pulley diameter D of the smallest pulley in the elevator system to the wire diameter δ of the thickest wire in the tension member in 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 means the service life of the disk

Can reduce suspension. 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 Lighter motors are used in the elevator installation than in the case of use of suspension means of the same load carrying capacity, which have only one tension member or several tension members in different "layers" on top of each other, in this way space and costs can be saved.

If the support means on its side facing the traction sheave side provided with a plurality of longitudinally parallel to the support means ribs and at the same time the traction sheave in its periphery with circumferentially extending with the ribs of the support means corresponding grooves, the support means can be performed better 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 system, the grooves of the traction sheave are wedge-shaped, in particular a triangular or trapezoidal

Have cross-section. The wedge shape results in each groove by two side walls, also called groove flanks, which run in a flank angle ß 'each other. Particularly good guiding and traction properties result at 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 ß '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 advantageous the support means on one side of its traction opposite side be provided with a guide rib, which corresponds to a guide groove in a guide, support or deflection plate.

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 such that the bending stress 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 ob = 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 ob is given by the following equation: ob = (5 * 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 suspension element has a smallest bending angle

Bending radius r in the thickest wire of its at least one tension member with the largest wire diameter δ a bending stress (b, in the range of (b = 450N / mm ² to 750N / mm ² and preferably in the range of from = 490N / mm ² to 660N / mm ² lies.

In a further embodiment of the suspension means, the wire has the largest

Wire diameter δ a modulus of elasticity of about 210Ό0 N / mm ² For this embodiment, a particularly long service life of the suspension means with very good efficiency results if the ratio of the smallest bending radius r wire diameter δ of the thickest wire in the tensile carrier in the range of 2r / 5 = 200 bis 600, and even higher if in the range of 2r / 5 = 300 to 500 Hegt.

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 suspension means more than one in

In the longitudinal direction of the support means (12) extending tension members, 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 suspension 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 other embodiments, the support means comprises at least one tension member, the strand in a wire configuration with a core of 3 wires, each with a diameter a and two surrounding the soul wire layers with wire diameters b (1st wire layer) and

Wire diameters c (2nd wire layer) is formed. 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 a further embodiment, the at least one tensile member of the suspension element has a wire configuration (lf-6e-6d + 6c) W + n * (lb + 6a), where n is an integer between 5 and 10, and the smallest bending radius r is 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 for

Parts are the same and W stands for a Warrington configuration, as shown for example in DIN EN 12385-2: 2002 under 3.2.9 Figure 7. 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 at least one tensile carrier of the suspension element has 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 support means comprises at least one tension member having a wire configuration (le + 6d + 12c) + n * (lb + 6a) W, where n is an integer between 5 and 10, and at least the smallest bending radius r is> 35mm. 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 are exhibited by the abovementioned embodiments of the suspension element when the tension members SZS or ZSZ are struck (see DIN EN 1235-2: 2002 under "3.8 Stroke directions and types of impact"), that is, when the tension members 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 in a plane next to each other in the Embedded polymer shell

The number of ZSZ hit and the SZS beaten tension members should be the same over the entire suspension.

In a further embodiment, the suspension element has a plurality of the tension members described above, wherein preferably all tension members have 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 are adapted to the position in the suspension element (center or outside). 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 suspension element is the traction side with several in

Provided longitudinally of the support means parallel ribs, which have a wedge-shaped, in particular a triangular or trapezoidal cross-section with a flank angle ß in the range of 81 ° to 120 °, more preferably from 83 ° to 105 ° or 85 ° to 95 ° and most preferably 90 ° exhibit. The advantages correspond to those that have already been addressed in a traction sheave with analogously designed grooves.

Particularly evenly, the tension and the load on the tension members of a

Distribute suspension element, if each rib on the traction side of a suspension element two

Zugträger are assigned. 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 disclosed embodiment, the support means exactly two ribs on the

Traktions page on. 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.

The figures show by way of example and purely schematically:

1 shows a section parallel to an elevator car front through an elevator system according to the invention;

2a is 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;

2b is a cross-sectional view of the support means according to FIG. 2 with different

Examples of possible rib designs;

3a shows a perspective view of a second embodiment of a support means according to the invention in the form of a flat belt;

Fig.3b enlarges a section of the flat belt of Fig. 3a

4a shows a section parallel to the axis of rotation of a traction sheave of an elevator installation and through a further embodiment of a suspension element running over it;

4b is a section through yet another embodiment of a support means of

Elevator system perpendicular to its tension members;

5 shows a section analogous to that in Figure 4b through yet another embodiment of a support means of the elevator system.

6 shows a section analogous to that in Figure 4b through yet another embodiment of a support means of the elevator system.

FIG. 7 shows a section analogous to that in FIG. 4b through yet another exemplary embodiment of a suspension element of the elevator installation;

8 shows a cross section through a first embodiment of a steel wire tension member.

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

10 shows a cross section through a third embodiment of a steel wire tension member. 11 shows a cross section through a fourth embodiment of a steel wire tension member;

1 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 car guide rails 5 with cabin support disks 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 the 2: 1 suspension shown in Fig. 1 and elevator systems with 1: 1, 4: 1 or any other suspension conditions than inventive elevator systems can be designed. 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 be e.g. also 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 be arranged 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. In the exemplary embodiment of an elevator installation 9 according to the invention shown in FIG. 1, the suspension element 12 is fastened at one of its ends below the traction sheave 4. 1 to a first suspension 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 it wraps on each side of the elevator car 3 each mounted below the elevator car 3 cabin sheave 4.2 by approximately 90 °, and extends along the counterweight 8 remote cabin wall up to a second Tragmittelfixpunkt 11. To a better guidance of the support means 12 under the cabin floor 6 to ensure through, are between the two cabs washers 4.2 guide discs 4.4 provided. This is particularly useful for long distances between the cabin pulleys 4.2.

In the example of an elevator installation 9 according to the invention shown in FIG. 1, 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 system 9 according to the invention can be selected to be very small, which reduces the space required and the use of a lighter smaller

Machine allows. 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. Due to the small pulley diameter, it is possible to keep the gap between the cabin wall and the opposite shaft wall of the elevator shaft 1 very small. Due to the small size and low weight of

Drive unit 2, it is possible the drive unit 2 on one or more of the

Guide rails 5, 7 to install 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, shows in perspective a portion of a preferred embodiment of an inventive support means 12. 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 shown in FIG. 2b, it is possible to design the ribs 20, viewed in cross-section, instead of trapezoidal (FIG. 2a), also as 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. Pro rib 20 of the

Supporting means 12 are each a right-turn in its overall torque tension member 22, denoted by "R", and a left-turning in its overall torque tension member 22, denoted by "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 element according to the invention is shown in FIGS. 3a, 3b. This suspension is on both its traction te 18 and its back 17 designed 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

Lift suspension element 12. 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 (for example 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 one

Support layer 15a is advantageous with respect to a uniform force distribution in the support means 12 when running over 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 discs 4.2, 4.3, 4.4 of the elevator installation 9 under counterbending, a coating 61 which is, for example, polytetrafluoroethylene contains, reduces the friction during running of the support means 12 via these discs 4.2, 4.3, 4.4 under counter-bending, what the low-noise 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.

3000N / mm ² ). The stranding is designed so that at a bending of a provided with such a tension member 22 support means 12 by a smallest bending radius r a bending stress ob in the thickest wire with the largest wire diameter 5g in the tension member 22, which 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 so that when running the support means 12 with a tension member 22 over a smallest disc with a smallest disc diameter D in the elevator system 9, the bending stress ob for the thickest wire of the tension member 22 as a function of its modulus of elasticity E and its diameter δ according to the following equation: ob =

(5 * E) / Dk or ab = (5 * E) / 2r. Examples of tension members 22 according to the invention are shown in FIGS. 7 to 12. 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." is the calculated diameter d of the

Tensile carrier 22 indicated 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 disc diameter D, for example, the bending stress whether for the thickest wire 43 in

Tensile 22, the ratio of pulley diameter D to the diameter δ of the thickest wire 43 "D / δ" and the ratio of pulley diameter D to effective

Zugträgerdurchmesser "D / d eff specified. In Fig. 7 a tension member 22 is shown, according to the standard 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 results in a configuration (le + 6d + 12c) for the central strand 40. Furthermore, the tension member 22 comprises a first strand layer 50 with 8 outer strands 44, each of which has a central wire b and 6

Outer wires a, so overall has a configuration 8x (lb + 6a). This results in a tension member 22, also called "cord" in the associated table 7, with a simplified design

Nomenclature 19 + 8x7.

The configuration of the tension member 22 shown in Fig. 7 has its thickest wire 43 with the largest diameter 5 = e in the center as the central wire of the central strand 40. At a smallest bend radius of 36mm or a smallest pulley diameter in an elevator 9 of 72mm For this thickest wire 43, a bending stress of (b = 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 slightly larger radius r or disc diameter D of r = 44mm, D = 87mm we get:

ab = 459N / mm ² , D / δ = 458, D / d eff = 50.

In the embodiments shown in FIGS. 8a and 8b, the tension member 22 has a

Wire configuration (lf-6e-6d + 6c) W + n * (lb + 6a), where n is an integer between 5 and 10, and in which the smallest bending radius r at least r> 32mm. In Fig. 8a, a configuration is shown in which n = 9, the central strand 40 is a Warrington configuration

(lxf-6xe-6xd + 6xc) or written with the diameters of the individual wire types in mm (1x210-6x200-6x160 + 6x220) and the 9 outer strands 44 each have a central wire with wire diameter δ: b = 140mm and 6 outer wires with the same wire diameter δ: a = 140mm, giving a total of a cord 19 + 9x7 (see Table 8a.I).

The second embodiment for this configuration in Fig. 8b shows the same

Central strand 40 with the same Warrington construction (lxf-6xe-6xd + 6xd) and the same Wire diameters δ: f = 210mm, e = 200mm, d = 160mm, c = 220mm. Instead of the 9 outer caps 44 with seven individual wires 42 but 8 outer caps 44 of the configuration (lb + 6a) are provided in this embodiment. The wire diameters δ of the individual wires 42 are adapted accordingly here: b = 150 mm, a = 150 mm. As can be seen from the accompanying tables (8b.I and 8b.II), the bending stress is whether 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 or the bending radius r between the two embodiments 8a and 8b but change bending stress whether for the thickest wire c and the ratio of D / δ not. 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 tension member 22 with a basic wire configuration (3f + 3e + 3d) + n * (3c + 3b + 3a), where n is an integer between 5 and 10, and 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 from 72 mm to 150 mm (see Table 9. II), the bending stresses for the thickest wire 43 are in the range of ob = 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. 10 shows an embodiment of a tension member 22 according to the invention for a suspension element 12 according to the invention, which is in the form of a strand with a core 41 of 3 wires each having a diameter a and two wire layers 46, 48 with wire diameters b surrounding the core 46) and wire diameters c (second 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, for these thickest wires 43 with diameter δ = c, the bending stresses are given if, 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 "D / d ef" and "D / δ" are given, as shown in Table 10. II, the bending stress is at bending radii of r = 36mm or converted to a hoist at disc diameters D = 72mm at ob = 875N / mm ² , the ratio of D / δ = 240.

11 shows an embodiment of a tension member 22 with a central strand 40 according to (3e + 3d-15c) and 8 outer strands 44 according to (1b + 6a), the central strand 40 having a core 41 with 3 central wires with diameter e and three fillers with diameter d as well as 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. Additional values for this configuration are shown in Tables 11.1 and 11.11. Again in another embodiment of a tension member 22 with a principal

Wire configuration (3d + 7c) + n * (3b + 8a) and n equal to an integer between 5 and 10 is shown in FIG. 12. In this case, n is equal to 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 ob 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 12.11), the bending stresses whether for this thickest wire 43 in the range of ob = 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 12.11.

Particularly good torque characteristics and good cable stability are exhibited by the abovementioned embodiments of the tension member 22 when these SZS or ZSZ are beaten (see DIN EN 1235-2: 2002 under "3.8 Strike directions and types of impact"), that is to say when the tension members are left-handed. are beaten 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

Tragmittel very good values for the life with sufficient efficiency have been found if the ratio of the wheel diameter D of the smallest disc in the elevator system to 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, tension members, as illustrated and explained by way of example in FIGS. 7 to 12, are used according to the invention in suspension elements 12 of an elevator installation according to the invention. The bending stress ob in the thickest wire 43 with the largest wire diameter δ of the tension member 22 in the support means 12, then lies when bending a smallest bending radius r or a smallest disc with pulley diameter D in the elevator system in the range of ob = 300N / mm ² to 900N / mm ² better in the range of ob = 450N / mm ² to 750N / mm ² and even better in the range of ob = 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. 3a, 3b. 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 shown for example in Fig. 2a, 2b, will be explained in more detail below an elevator system 9 according to the invention, as shown in Fig. 1. The support means 12 will be te with its traction 18 via the traction sheave 4.1, the Gegengewichtstragscheibe 4.3 and the guide discs 4.4 out, these are provided accordingly at their periphery with grooves 35 which are complementary to the ribs 20 of the support means 20. Where the V-ribbed belt 12 one of

Belt pulleys 4.1, 4.3 and 4.4 wraps around its ribs 20 lie in corresponding grooves 35 of the pulley, whereby a perfect guidance of the support means 12 is ensured on these pulleys.

Via the car washers 4.2, the V-ribbed belt 12 is guided with a counterbending, i. the ribs 20 of the V-ribbed belt 12 are on the run 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. As can be seen from FIG. 1, the suspension element 12 between the cabin support disks 4.2 is guided with its rib side over the guide disks 4.4 provided with corresponding grooves. 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 is in

Contrary to a lateral guide by means of flanged wheels, no lateral wear on the support means 12 caused. Depending on the cabin dimension, selected suspension and interaction of the discs with the support means, it is also possible to work without 4.4 guide plates between the cab sheaves 4.2 or instead of the two guide discs shown 4.4 under the cab 3 only one or more than two guide discs 4.4 provided. 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 shown by way of example on FIG. 4 a, the traction sheave 4. 1 not only has grooves 35 in its periphery, but also has in its grooves 35 a groove bottom 36 which is lower than the trapezoidal flattened tips of the engaging ribs 20 of FIG 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 plates 4.4 advantageously have grooves 35 without deeper groove bottom 36 and elevations 38 are the same dimensions as the wells 26 of the support means 12 on its traction side 18. This reduces the risk that the suspension means in the disc 4.2, 4.3, 4.4 jammed and ensures good guidance with less traction.

In the elevator installation 9 according to the invention shown in FIG. 1, the diameters of all pulleys are the same. It is also conceivable that the pulleys have different size and the supporting and / or deflection pulleys 4.2, 4.3, 4.4 a larger

Have 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 a larger diameter, the other a smaller diameter than the traction sheave 4.1 have. 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 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 the thickest wire according to the following equation: ob =

(5 * E) / D. The best ratio of economy of the elevator installation and life of the support means 12 results in this case with a tension member 22 whose thickest wire with the largest diameter D has a bending stress ob in a range between ob = 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 examples shown in Figures 2a, 2b and 4a, each rib 20 is on the

Traction page 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, in the wrapping of a pulley 4.1 - 4.4 of the tension members 22 forces in the radial direction over the

Belt body 15 transmitted to 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 per rib 20 forces to be transmitted to a plurality of tension members and particularly favorable distributed to two tension members as shown in Fig. 2a, 2b and 4a.

As the embodiment in Fig. 4b shows, but it is also possible to provide more than two tension members 22 per rib 20. Shown in FIG. 4 b are three tension members 22 per rib 20, wherein the ribs 20, viewed in cross section, are trapezoidal in shape. 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 also conceivable, wherein cross-sectional shapes of the ribs are also conceivable, as shown in FIG. 2b. 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 corresponds to about 20% of the total thickness s of the support means 12.

In contrast to the examples in FIGS. 2 a, 2 b and 4 a, the support means 12 in FIG. 4 b is not provided with a coating on its flat side 17. For this, 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 in cooperation with the traction sheave 4.1 and / or another pulley 4.2, 4.3, 4.4 of the elevator installation 9 is set , Also, this coating 62 preferably comprises a fabric 61, in particular a nylon fabric.

FIG. 5 shows a further embodiment of a suspension element 12 according to the invention. As can be clearly seen in Fig. 5, in this example, the support means 12 on the

Traction page 18 per rib 20 only one tension member 22 on. 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 increased at the same

Strength of the wires, the load capacity of the tension members 22, the latter also simplifies the

Stranding and lowers the cost per tensile carrier 22. Preferably, the tension members 22 are each arranged centrally 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 of FIGS. 2a, 2b and 4b, the suspension element example 12 from FIG. 5 likewise has a coating on its flat rear side 17, which in this example contains tetrafluoroethylene in order to increase the coefficient of friction when interacting with deflecting disks 4.4 or support disks 4.2, 4.3 reduce. The layer may contain as diffusion layer polytetrafluoroethylene particles in the cladding material or be provided as a film-like polymer-based or tissue-based cladding with polytetrafluoroethylene particles. The tetrafluoroethylene particles preferably have a particle size of 10 to 30 micrometers.

Applies to all mentioned coatings that they can be applied over the entire length of the support means 12 or only one or more specific lengths of the support means 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 suspension element 12, which likewise has ribs 20 with two tension members 22 on its traction side 18. Especially on this support means 12 is that it is on his

Traction side 18 has exactly two ribs 20 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, which have a corresponding guide groove to the guide rib 19 to accommodate (not explicitly shown). The support means of 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 extending over the length of the support means 12 extending stabilizing elements (not shown) similar to the tension members 22. As shown in Fig. 4b and 5, the support means 12 have a flank angle ß 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 ß a decisive influence on the noise and the formation of

Has vibrations, and that for a lift-carrying means provided for V-ribbed belt flank angle ß of 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 °. Supporting means whose flank angle β in the ribs 20 is equal to the angles in the recesses 26 can be produced in a particularly simple manner. 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.

It can also be seen from FIGS. 4b and 5 that small dimensions and low weight of a ribbed suspension element 12 are achieved by making the distances X between the outer contours of the tension members 12 and the surfaces / flanks of the ribs 20 as small as possible. Optimal properties have resulted in tests for ribbed suspension elements 12, in which these distances X are at most 20% of the total thickness s of the

Be carrying means. 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 ob then results according to the following equation: ob = (5 * 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 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: ob = (5 * 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, which is induced during the running of the suspension element over a disc with the smallest pulley diameter D, in the wire of the tension member, is the largest

Wire diameter has been selected in the range between 300N / mm ² to 750N / mm ² , increases the life of the tension member. The best results in terms of service life and cost-effectiveness are achieved with support means, the tension member when running the

Tragmittels over a disc with the smallest disc diameter D in their thickest wires bending stress from in the range of ab = 350N / mm ² to 650N / mm ² experience.

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

claims

1 . Elevator installation with at least one pane (4), via which a suspension element (12) is guided, wherein at least one pane (4) is a traction sheave (4.1) of a drive machine (2) comprising the suspension element (12), which comprises at least one elevator cage ( 3) and / or carries, wherein the support means (12) comprises a made of a polymer body (15), in which at least one in the longitudinal direction of the support means (12) extending tensile carrier (22) is embedded, wherein the tension member (22) is made of wires and is present as a strand or rope and in the tension member (22) a thickest wire (43) with the largest wire diameter δ while running the tension member (22) over a smallest disc with a smallest disc diameter D in the elevator installation a bending stress whether in a range between ob = 350N / mm ² to 900N / mm ² .

2. Elevator installation according to claim 1, wherein the bending stress of the wire with the largest diameter δ in the tension member (22) when running over the disc with the smallest pulley diameter D in the range between 450N / mm ² to 750N / mm ² and preferably in the range from ab = 490N / mm ² to 660N / mm ² .

3. Elevator installation according to claim 1 or 2, wherein the bending stress ob in

Depending on the modulus of elasticity E and the diameter δ of the thickest wire (43) of the tension member (22) according to the following equation: ob = (5 * E) / D.

4. Elevator installation according to one of the preceding claims, in which the wire (26) with the largest wire diameter δ has a modulus of elasticity of approximately 210Ό00 N / mm ² and the ratio of the disk diameter D of the smallest disk to the wire diameter δ of the thickest wire (43) in the tension member (43) 22) of the guided over the disc support means (12) in the range of D / δ = 200 to 650, preferably in the range of D / δ = 230 to 500 Hegt.

5. Elevator installation according to one of the preceding claims, the traction sheave (4.1) is the disc (32) with the smallest disc diameter D.

6. Elevator installation according to one of the preceding claims, having a suspension element (12), at least one of the traction sheave (4.1) facing the traction side (18) in the longitudinal direction of the support means parallel extending ribs (20) and more than one in the longitudinal direction of the support means (12). extending tensile carrier (22), wherein the tension members (22), viewed in the width of the support means (12), in a plane adjacent to each other and preferably spaced from each other, and

with a traction sheave (4.1) which has grooves (35) which extend in the periphery in the circumferential direction and which correspond to the ribs (20) of the support means (12), the grooves (35) being provided with a lower groove bottom (36) that when wedges (35) interact with ribs (20), a wedging action results.

7. Elevator installation according to claim 5, in which the grooves (35) of the traction sheave (4.1) have a wedge-shaped, in particular a triangular or trapezoidal cross-section with a flank angle (β ') of 81 ° to 120 °, better still of 83 ° to 105 °, even better from 85 ° to 95 ° and most preferably 90 °.

8th . Supporting means for carrying and / or moving at least one elevator car (3) in an elevator installation, wherein the suspension means (12) can be guided and driven at least via a disk (4), in particular a traction sheave (4.1) of a drive machine (2) of an elevator installation (1) wherein the support means (12) comprises a body (15) made of a polymer and at least one tensile member (22) embedded in the body (15) extending in the longitudinal direction of the support means (12) and made of wires (42) and is present as a strand or rope, and

wherein in the tension member (22) a thickest wire (43) with the largest wire diameter δ when bending the tension member (22) by a smallest bending radius r a bending stress in a

Range between ab = 350N / mm ² to 900N / mm ² has.

9. Supporting means according to claim 8, wherein the bending stress of the wire with the largest diameter δ in the tension member (22) when bending by a smallest bending radius r in the range between (b = 450N / mm ² to 750N / mm ² and preferably in the range of (b =

490N / mm ² to 660N / mm ² , wherein the bending stress from preferably in

Depending on the modulus of elasticity E and the diameter δ of the thickest wire (43) and in particular according to the following equation: ob = (5 * E) / 2r.

10. Supporting means according to claim 8 or 9, wherein the wire with the largest wire diameter δ has a modulus of elasticity of about 210Ό00 N / mm ² 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). in the range of 2r / 5 = 200 to 650, preferably in the range of 2r / 5 = 240 to 500.

11. Supporting means according to one of claims 8 to 10, wherein the strands (28) or wires (42) of the tension member (18) in its outer wire or strand layer are spaced from each other and so on, the greater the viscosity of Polymer when embedding the tension member (18) in the body (15) of the support means (12), wherein the distance (60) is at least 0.03mm.

12. A suspension element according to any one of claims 8 to 11, wherein the tension member (22) has a wire configuration (lf-6e-6c + 6d) W + n * (lb + 6a), where n is an integer between 5 and 10 , and in which the smallest bending radius r is at least r> 30mm.

13. A suspension element according to any one of claims 8 to 11, wherein the tension member (22) has a wire configuration (3d + 7c) + n * (3b + 8a), where n is an integer between 5 and 10, and wherein the smallest bending radius r at least r> 32mm.

14. A support means according to any one of claims 8 to 11, wherein the tension member (22) has 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> 30mm.

15. A suspension element according to any one of claims 8 to 11, wherein the tension member (22) has a wire configuration (le + 6d + 12c) + n * (lb + 6a) W, where n is an integer between 5 and 10, and where the smallest bending radius r is at least r> 32mm.

16. Elevator installation according to one of claims 12 to 15, wherein the tension member (22) SZS or ZSZ is beaten.

17. Supporting means according to one of claims 8 to 11, wherein the tension member (22) as a strand in a seal configuration with a core (40) of three wires with a diameter a and with two wire layers (46), (48) surrounding the core (40) are formed with wire diameters b and c and in particular have a configuration (3a + 9b + 15c), and wherein the smallest bending radius r is at least r> 32mm.

18. The suspension element according to claim 8, wherein one side is designed as a traction side (18) which has a plurality of ribs (20) running parallel in the longitudinal direction of the suspension element and more than one tension member (22) extending in the longitudinal direction of the suspension element (12) ), wherein the tension members (22), viewed in the width of the support means, are arranged in a plane next to each other and preferably spaced from each other.

19. A support means according to claim 18, wherein the ribs (20) of the support means (12) have a wedge-shaped, in particular a triangular or trapezoidal cross-section with two mutually running flanks (24) which include a flank angle (ß), in the range of 81 ° to 120 °, better from 83 ° to 105 ° and even better from 85 ° to 95 ° and best with 90 ° ± 1 °.

20. Supporting means according to one of claims 18 or 19, wherein each rib (20) is associated with two tension members (22) which are each arranged in the region of the vertical projection (P) of an edge (24) of the rib (20).

21. Supporting means according to one of claims 18 or 19, wherein each rib (20) is associated with exactly one tension member (22), which is arranged centrally with respect to the two flanks (24) of the rib (20).

22. Suspension means according to one of claims 17 to 21, wherein the traction side (18) of the

Supporting means (12) and / or the traction side (18) opposite the rear side (17) of the support means (12) is / are coated, wherein with the aid of the coating (61) the desired coefficient of friction between the traction side (18) and traction sheave (4.1 ) and rear side (17) and deflection, guide, or support disks (4.2, 4.3, 4.4) is set and wherein the coating (61) in particular a fabric (62), preferably made of natural fibers or synthetic fibers, in particular of hemp , Cotton, nylon, polyester, PVC, PTFE, PAN, polyamide or a mixture of two or more of these types of fibers.

23. Supporting means according to one of Claims 17 to 21, in which the suspension element (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.