EP2488436B1 - Aufzugsanlage und tragmittel für eine solche anlage - Google Patents

Aufzugsanlage und tragmittel für eine solche anlage Download PDF

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Publication number
EP2488436B1
EP2488436B1 EP10761015.6A EP10761015A EP2488436B1 EP 2488436 B1 EP2488436 B1 EP 2488436B1 EP 10761015 A EP10761015 A EP 10761015A EP 2488436 B1 EP2488436 B1 EP 2488436B1
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EP
European Patent Office
Prior art keywords
wire
load bearing
bearing member
tension member
diameter
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Application number
EP10761015.6A
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German (de)
English (en)
French (fr)
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EP2488436A1 (de
Inventor
Danilo Peric
Oliver Berner
Ernst Ach
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Inventio AG
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Inventio AG
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Priority to EP10761015.6A priority Critical patent/EP2488436B1/de
Publication of EP2488436A1 publication Critical patent/EP2488436A1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B11/00—Main component parts of lifts in, or associated with, buildings or other structures
    • B66B11/04—Driving gear ; Details thereof, e.g. seals
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B7/00—Other common features of elevators
    • B66B7/06—Arrangements of ropes or cables
    • B66B7/062—Belts
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B1/00—Constructional features of ropes or cables
    • D07B1/06—Ropes or cables built-up from metal wires, e.g. of section wires around a hemp core
    • D07B1/0673—Ropes or cables built-up from metal wires, e.g. of section wires around a hemp core having a rope configuration
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B1/00—Constructional features of ropes or cables
    • D07B1/16—Ropes or cables with an enveloping sheathing or inlays of rubber or plastics
    • D07B1/162—Ropes or cables with an enveloping sheathing or inlays of rubber or plastics characterised by a plastic or rubber enveloping sheathing
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B1/00—Constructional features of ropes or cables
    • D07B1/22—Flat or flat-sided ropes; Sets of ropes consisting of a series of parallel ropes
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B2201/00—Ropes or cables
    • D07B2201/20—Rope or cable components
    • D07B2201/2015—Strands
    • D07B2201/2036—Strands characterised by the use of different wires or filaments
    • D07B2201/2037—Strands characterised by the use of different wires or filaments regarding the dimension of the wires or filaments
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B2401/00—Aspects related to the problem to be solved or advantage
    • D07B2401/20—Aspects related to the problem to be solved or advantage related to ropes or cables
    • D07B2401/206—Improving radial flexibility
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B2501/00—Application field
    • D07B2501/20—Application field related to ropes or cables
    • D07B2501/2007—Elevators

Definitions

  • 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.
  • 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.
  • 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.
  • 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.
  • a diameter of about 2mm or less is specified.
  • 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.
  • 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.
  • the tension members are to be embedded in a polymer, here in particular rubber.
  • 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.
  • 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
  • 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.
  • the elevator system comprises at least one disc, over which a suspension element (12) is guided, which moves at least one elevator car.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the traction sheave is 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.
  • 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 ⁇ '.
  • Particularly good guiding and traction properties result from a flank angle ⁇ 'of 81 ° to 120 °, even better at a flank angle ⁇ ' of 83 ° to 105 °, even better in the range of 85 ° to 95 ° and the best at a flank angle ⁇ 'of 90 °.
  • other sheaves may also be provided with corresponding grooves which correspond to the ribs of the suspension element on the traction side thereof.
  • 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.
  • a support means 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.
  • the bending stress results in dependence on the modulus of elasticity E and the diameter ⁇ of the thickest wire and in dependence on the smallest intended bending radius r.
  • the mutual dependencies can be simplified mathematically represent.
  • 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.
  • the suspension element may be constructed of a single elastomer or of different elastomers, eg in layers, with different properties.
  • 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.
  • chloroprene can be used in the body especially as an adhesive.
  • 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.
  • the wire with the largest wire diameter ⁇ has a modulus of elasticity of about 210'000 N / mm 2.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the support means also has more than one in the longitudinal direction of the support means extending tension members.
  • 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 ⁇ 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.
  • 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.
  • 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.
  • the suspension element has exactly two ribs on the traction side.
  • 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.
  • 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.
  • 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.
  • a guided counterweight guide rails 7 counterweight 8 with a Jacobisstragin 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.
  • elevator systems or any other suspension conditions can be designed as elevator systems according to the invention.
  • 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 Tragstofffixddling 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.
  • 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.
  • 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.
  • the drive unit 2 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.
  • 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.
  • the 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.
  • tensile carriers 22 which are arranged in a plane next to each other and spaced from each other.
  • 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.
  • FIGS Fig. 3a, 3b 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.
  • the illustrated suspension element 12 has a multilayer structure.
  • a harder base layer 15 a 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.
  • 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 ⁇ b in the thickest wire with the largest wire diameter ⁇ g in the tension member 22, which is in the range of 300N / mm 2 and 900N / mm 2 lies.
  • inventive tension members 22 are in the Fig. 7 to 12 shown.
  • inventive tension members 22 are in the Fig. 7 to 12 shown.
  • the accompanying tables "I" under “Cord” down with a, b, c, d, e, f are given by way of example possible wire diameter ⁇ 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 ⁇ of all wires 42 in the tension member 22.
  • the calculated diameter d of the tension member 22 is given in mm.
  • d eff is the diameter averaged from measurements d eff. of the tension member 22 in mm.
  • 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.
  • 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.
  • n is an integer between 5 and 10
  • r is at least r ⁇ 32mm is.
  • n 9
  • f 210 ⁇ m
  • e 200 ⁇ m
  • d 160 ⁇ m
  • c 220 ⁇ m.
  • 8 outer strands 44 of the configuration (1b + 6a) are provided in this embodiment.
  • the bending stress ⁇ b in the thickest wires 43 of diameter ⁇ c and the ratios of D / ⁇ 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 ⁇ b for the thickest wire c and the ratio of D / ⁇ 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.
  • 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.
  • 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.
  • 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).
  • Table 10 In Table 10.
  • the ratios are "D / d eff". and "D / ⁇ ".
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 Kabinentragusionn 4.2 back 17 which is designed here as a flat side.
  • 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 Kabinentragusionn 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.
  • selected suspension and interaction of the discs with the support means it is also possible to work without 4.4 guide plates between the Kabinentragusionn 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.
  • 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.
  • the traction sheave 4.1 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.
  • 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.
  • 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.
  • ⁇ b ( ⁇ * E) / D
  • 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.
  • EPM ethylene-propylene rubber
  • EPDM ethylene-propylene-diene rubber
  • PA Polyamide
  • PE polyethylene
  • PC polycarbonate
  • CR polychloroprene
  • PU polyurethane
  • TPU thermoplastic elastomers
  • cover layer 62 On its flat side 17 of the belt body 15 is provided with a cover layer 62, which comprises an impregnated fabric here.
  • cover layer 62 which comprises an impregnated fabric here.
  • non-impregnated fabrics 61 may also be applied or coatings may be provided by extrusion, gluing, laminating, flocking.
  • the tension members 22 are each arranged centrically above the vertical projection 70 of a flank 24 of the rib 20 ( Fig. 2b ).
  • 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.
  • Fig. 4b 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.
  • the distance X between a tension member and the traction side surface of the suspension element, or in other words the Graions mille 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.
  • the suspension element 12 is in Fig. 4b on its flat side 17 is not provided with a coating.
  • the suspension element 12 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 ,
  • this coating 62 preferably comprises a fabric 61, in particular a nylon fabric.
  • a further embodiment of a support means 12 according to the invention is shown.
  • the support means 12 on the traction side 18 per rib 20 only one tension member 22.
  • 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.
  • the tension members 22 are each centrally located in their rib 20, this leads to a very uniform distribution of Switzerlandtownbelastung via the two edges 24 of each rib 20.
  • the total thickness of the support means can be kept slightly lower.
  • 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.
  • 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.
  • this support means 12 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.
  • 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.
  • 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.
  • the support means 12 have a flank angle ⁇ of about 90 °.
  • the flank angle ⁇ is the angle enclosed by its two flanks 24 of a rib 20 of the suspension element 12.
  • the flank angle ⁇ 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 ⁇ 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 ⁇ of 90 °
  • a ribbed support means 12 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 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
EP10761015.6A 2009-10-14 2010-10-06 Aufzugsanlage und tragmittel für eine solche anlage Active EP2488436B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10761015.6A EP2488436B1 (de) 2009-10-14 2010-10-06 Aufzugsanlage und tragmittel für eine solche anlage

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Application Number Priority Date Filing Date Title
EP09173069 2009-10-14
PCT/EP2010/064902 WO2011045215A1 (de) 2009-10-14 2010-10-06 Aufzugsanlage und tragmittel für eine solche anlage
EP10761015.6A EP2488436B1 (de) 2009-10-14 2010-10-06 Aufzugsanlage und tragmittel für eine solche anlage

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EP2488436B1 true EP2488436B1 (de) 2016-01-13

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US (1) US20120211310A1 (zh)
EP (1) EP2488436B1 (zh)
KR (1) KR20120083907A (zh)
CN (1) CN102574665B (zh)
AU (1) AU2010305872A1 (zh)
BR (1) BR112012008407A2 (zh)
CA (1) CA2777541A1 (zh)
CL (1) CL2012000935A1 (zh)
ES (1) ES2567783T3 (zh)
HK (1) HK1174320A1 (zh)
MX (1) MX2012004353A (zh)
MY (1) MY183948A (zh)
RU (1) RU2012117956A (zh)
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ZA (1) ZA201202550B (zh)

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Also Published As

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CL2012000935A1 (es) 2012-08-03
BR112012008407A2 (pt) 2016-03-29
AU2010305872A1 (en) 2012-05-03
HK1174320A1 (zh) 2013-06-07
CA2777541A1 (en) 2011-04-21
EP2488436A1 (de) 2012-08-22
CN102574665A (zh) 2012-07-11
RU2012117956A (ru) 2013-11-20
MY183948A (en) 2021-03-17
CN102574665B (zh) 2015-11-25
MX2012004353A (es) 2012-09-07
ES2567783T3 (es) 2016-04-26
WO2011045215A1 (de) 2011-04-21
KR20120083907A (ko) 2012-07-26
US20120211310A1 (en) 2012-08-23
ZA201202550B (en) 2013-06-26

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