EP3541737A1

EP3541737A1 - Cable drive having a sheathed traction element

Info

Publication number: EP3541737A1
Application number: EP17794994.8A
Authority: EP
Inventors: Daniel Schoepke; Christoph Reimers
Original assignee: "brugg" Drahtseil AG; Brugg Drahtseil AG
Current assignee: BRUGG LIFTING AG
Priority date: 2016-11-16
Filing date: 2017-11-14
Publication date: 2019-09-25
Also published as: EP3323769A1; WO2018091470A1

Abstract

The invention relates to a cable drive which, in particular, is suitable for cranes or mass-produced hoists and which comprises a drum (1) and a traction element (2a; 2; 2a), which runs on the drum (1). The traction element (2a; 2; 2a) comprises at least one load-bearing element (21; 22; 21a-21d) and is at least partly surrounded by a sheath (22), which preferably consists of a polymer, in particular preferably of a thermoplastic and/or elastomer. At least part of the sheath (22) constitutes the contact surface of the traction element (2a; 2; 2a).

Description

Rope drive with sheathed traction element

Technical area

The invention relates to a cable drive, in particular for cranes and / or standard hoists. The cable drive comprises a drum and a pulling member which runs on the drum and which comprises at least one support element. Furthermore, the invention relates to a lifting drive comprising a cable drive and a drive, which acts on the drum and thus can cause a movement of the tension member comprises. Furthermore, the invention relates to a hoist comprising a lifting drive and a holder. The bracket receives at least a portion of the forces acting on at least a portion of the lift drive. Furthermore, the invention relates to manufacturing methods of a cable drive, a lifting drive and a hoist. State of the art

The DIN 15 020, sheet 1, from February 1974 describes the principles for standardized rope drives of cranes and series hoists. Cable drives with traction sheave drive are also excluded, as are wire ropes that do not run on drums and / or pulleys. The wire ropes described therein consist of steel wires with nominal strengths of 1570, 1770, 1960, 21 60 and 2450 N / mm ² . With plastic coated or coated wire ropes are, according to sheet 2 of DIN 15 020 from April 1974, not allowed. For monitoring purposes, the number of wire breaks should be counted and this is not possible with coated or sheathed wire ropes. To protect against mechanical damage, extreme external wear or corrosion attack, the use of thick outer wires is recommended. The use of lubricants reduces the friction between grooves of pulleys or drums. The absence of lubrication causes a shorter lay time of the rope.

JP 2008 308 265 A describes the use of a sheathed wire rope loop as a tension member in a storage and retrieval unit for clean rooms. The aim of J P 2008 308 265 A is to keep the abrasion of the cable and the deflecting pulleys as small as possible in order to minimize the contamination of the cleanroom atmosphere. The wire rope loop is driven by a traction sheave drive.

JP 09-02 1084 describes a jacketed round rope and a jacketed belt for use in a weaving machine for transferring motive power in various machines and for lifting goods. How the cable drives are realized in these applications, whether there are traction sheave drives or drums, JP 09-021084 does not disclose. For the transmission of drive forces usually rope loops are used. Rope loops and traction sheave drives are often used in load lifts for lifting goods. As described in the standard DIN 15 020, the resting time of a rope without lubrication between drum, rope pulleys and rope, clearly reduced. This reduces the cost-effectiveness of such a cable drive. Systems with closed cable loops, which are driven by traction sheaves, are quite expensive to maintain since the rope is on site the exact correct length must be brought and must be closed to a rope loop. Drives without a closed cable loop with traction sheave usually use a counterweight on the one hand always enough to load the traction sheave and so to maintain the necessary friction and on the other hand to keep the applied force small. However, counterweights can only be used to advantage if the load is essentially always the same.

Presentation of the invention

The object of the invention is to provide a the technical field mentioned in the beginning rope drive, which is characterized by low system costs. In contrast to passenger lifts and other systems without drums, rope drives according to the invention should preferably be suitable for intensive use with a large but fluctuating load.

The solution of the problem is defined by the features of claim 1: According to the invention comprises a cable drive, in particular a cable drive for cranes or Serienhebezeugen, a drum and a pulling member. The tension member runs on the drum and comprises at least one support element. The support element is at least partially surrounded by a jacket comprising a polymer. At least a part of the jacket represents the support surface of the tension member. Preferably, at least one support element is completely surrounded by a jacket along its length.

In one embodiment, the sheath consists essentially entirely of the polymer. The polymer is in particular a thermoplastic and / or an elastomer.

The use of a sheathed tension member protects the support element, the drum and any other components of a cable drive, which come into contact with the tension member during operation. In addition, the jacket can protect the support member from environmental influences such as moisture. The materials and construction of the support element can be optimized to the requirements of the work to be done, such as the number of bending changes within a period of time and / or on the loads to be moved. The materials and the structure of the shell can in the inventive cable drive on an optimal interaction between the drum and tension member and between the tension member and be optimized for other components. This optimization extends the life of the tension member and / or drum and / or other components. It has surprisingly been found that the use of a sheathed traction element in cable drives increases the life of the traction element up to 10 times compared with a non-sheathed traction element of comparable design.

The jacket and the combination of several support elements in a pulling element allow in particular small bending radii of the tension member and thus the use of small dimensioned components such as pulleys, drums and drives. This also reduces the costs of the system and also saves space. It has also been found that the necessary maintenance work can also be carried out on jacketed tension members with sufficient reliability. Surprisingly, it has been found that the number of bending changes experienced by a pulling member with a jacket in a rope drive is a reliable indicator of the wear of the tension member , Therefore, by counting the bending change can be determined when the tension member must be stored. A visual inspection is only needed to detect mechanical damage to the coat in good time. On a visual inspection of the support elements can be omitted.

Definition:

A rope drive in the sense of the application comprises a drum on which the tension member is wound up and unwound during operation. The winding and unwinding can be done in particular by an active rotation of the drum (hereinafter "drum drive") and / or by the action of traction sheaves on the tension member (hereinafter "traction sheave drive"). The name of the drive should preferably designate which drive applies the majority of the force for moving a payload mounted on the tension member. If traction sheaves are used for the controlled movement of the traction element, then the drum is preferably slightly pretensioned, so that when the traction is released on the traction element, it rotates in such a way that the traction element is wound onto it. Such a bias is generated in one embodiment by a spring. In one embodiment of a rope drive with traction sheave drive generates a drive, such as a motor, the drum movement for rolling up the tension member upon release of the train. A pulling member in the sense of the application comprises a support element and a jacket. In the terms "pulley", "rope traction", "rope drive" and "rope attachment", the word component "rope" should preferably be synonymous with "traction".

A support element is preferably made of twisted or stranded elements. Such a preferred support element is not itself stranded with other elements. A stranded or twisted element, which forms, stranded with other elements, a support member is called in the following strand. For example, a strand can be stranded together with other strands to form a support element. A strand can also be stranded with single wires or single fibers or strands of metal or fibers and form a support element in this way. A strand may be made of metal wires or of fibers (for example of aramid, polyamide, carbon or polyethylene) or of a mixture of materials.

A support member may also consist of individual members, which pass the tensile force to each other when loaded, such as a chain. A support element may also consist of a strand or bundle of individual wires or a wire mesh. A support member may also consist of a strand or bundle of fibers or a fiber braid.

As support elements of a tension member those components of the tension member are preferred, which have a significantly higher tensile strength than the jacket material. A significantly higher tensile strength is a tensile strength which is preferably greater than twice the lower tensile strength, more preferably greater than five times the lower tensile strength. In the present case, in particular, the jacket material has the lower tensile strength.

The jacket material is in particular that material which forms the bearing surface of the tension member, preferably it is that material which makes up the major part of the volume between the support element and the bearing surface of the tension member. In this case, the jacket material is in particular a different material than that of the support element. In one embodiment, the jacket material is a polymer, in particular an elastomer and / or a thermoplastic, such as TPU, or another polyurethane or EDPM. In addition to the polymer, the coat can also contain reinforcing additives such as fibers, fabrics or particles. The jacket can be coated.

The contact surface of the tension member is preferably that part of the surface of the tension member which in use contacts the drum at any time or, if the cable drive comprises rope pulleys, contacts at least one of the pulleys. Depending on the design of the cable drive may be, for example, a single line (in a perfect round rope on flat drums and pulleys and a Zugorganführung with only one bending direction) or to wide strips on different sides of the tension member (at a tension member, which at least partially on or over suitably shaped drums and pulleys and its bending direction changes). Depending on the shape of the drums and pulleys and the tension member, the support surface may also comprise more than two strips.

The jacket forms the bearing surface of the tension member and is preferably simultaneously in contact with the support element. Preferably, a jacket may also comprise a plurality of materials. In particular, according to the invention, it is still a jacket, if it is coated on the outside or inside, with a layer whose thickness is insignificant with respect to the thickness of the jacket. In particular, a layer thickness is insignificant to the thickness of the shell when it is less than about 1/10 of the shell thickness at the coated site, more preferably a layer thickness is insignificant if it is less than about 1/100 of the shell thickness at the coated site is. The layer thickness and the cladding thickness should preferably be measured along the surface normal of the coated site.

A pulling member may comprise more than one support member. The jacket can enclose the support element only on one side. Preferably, the jacket completely encloses the support element along its length. The jacket can penetrate into the support element. The dimensions of a tension member are preferably determined as follows: Consider the cross section, perpendicular to the longitudinal axis, of the tension member. A first diameter of the tension member is the smallest distance between two, not identical, parallels which touch but do not intersect the outside of the cross section. A second diameter of the tension member is the greatest distance between two, not identical, parallels that touch but do not intersect the outside of the cross section. This procedure is illustrated by FIGS. 8a and 8b.

The tension member should preferably be referred to as "round rope" if the first diameter is greater than 9/10, preferably greater than 19/20, more preferably greater than 99/100 of the second diameter.

The tension member shall be referred to as a "belt" if the first diameter is less than 4/5, preferably less than 3/4, more preferably less than half of the second diameter The dimensions of the support element shall be determined analogously to the dimension of the tension member , In which the position of individual components of the support element is equal to the position in which they are located in the tension member, If a tension member comprises a plurality of support elements, the dimensions of each support element are to be determined individually and independently of the other support elements In this measurement, the outside of any component of the support element should preferably touch the first and the second diameter, but should not intersect any component of the support element, but the parallels may now cut the shell.

In one embodiment, at least one of the diameters of at least one of the support elements is between 1 and 40 mm, in particular between 2 and 38 mm, preferably between 6 and 34 mm, especially preferably between 8 and 32 mm, more preferably between 10 and 30 mm and most preferably between 1 2 and 24 mm. In this case, in particular in Belts preferred support elements between 1 and 20 mm are used and in particular in round cables supporting elements between 8 and 40 mm. Small support element diameters enable particularly small bending radii, while larger support element diameters reduce the number of support elements required for a given load. The specified diameter intervals allow particularly favorable cable drives.

Unless otherwise specified, the jacket thickness is preferably measured as follows: In a cross section through the tension member, a straight line becomes from all points of the contact surface drawn to the geometric center of gravity of each support element. All straight lines that run at least partially outside the cross-sectional area of the tension member and all straight lines that intersect at least partially two or more support elements are not considered further. Along all other straight lines, the distance between the support surface and the first intersection point with the envelope of the support element is determined therefrom. The shortest of these distances is preferably referred to as the jacket thickness. This procedure is illustrated by FIGS. 9a, b and c.

In one embodiment, the jacket thickness is in the range of 0.05 to 20 mm, in particular 0.1 to 10 mm, particularly preferably 0.8 to 1.2 mm. It has surprisingly been found that sheath thicknesses can be produced well in this area and that such shells deform only slightly in use on traction elements in cable drives and thus contribute to a long resting time.

A deflection roller is a roller over which the tension member runs and in which the direction in which the longitudinal axis of the tension member points changes: The tension element is deflected by the deflection roller.

By means of a compensating roller, the tension in the opposite section of a tension member is compensated. It differs from a pulley in that it hardly moves during operation. During operation, a tension member preferably runs over a compensating roller a maximum of one distance, which corresponds to three times the diameter of the tension member.

A traction sheave is an actively and / or controlled driven and / or braked roller, over which the tension member runs in such a way that, due to friction between traction sheave and traction element, the drive or the brakes of the traction sheave affect the movement of the traction element. Actively driven or braked in this context is understood to mean that a motor or another drive, which acts directly on the traction sheave, exerts a torque in one or the other direction on the traction sheave. Under controlled driven or braked is understood in this context that the movement and loading of the traction sheave and / or other parameters of the rope drive are observed and the traction sheave in response to these observations is driven or braked. An active drive or an active brake without control would in this sense, for example, with a motor simply exert a constant torque in one direction or the other direction of the traction sheave. An example of a controlled but non-active drive or brake is a traction sheave biased in one direction with a spring whose rotation is controlled by a controlled application of a brake. A traction sheave driven by a motor in response to a measured value, such as a measured rope speed, is an example of an actively and controllably driven traction sheave. If such a motor turns in the opposite direction or at reduced speed, it can be an active and controlled brake.

The drum is a device on which the tension member is wound up. The winding and unwinding of the tension member on or from the drum is used in a cable drive to control the length of the tension member targeted. In particular, the drum is thus a cable drum which is suitable for winding and unwinding the tension member. Drums according to the invention can thus be used in particular for round cables, if the tension element is a round rope or for Belts, if the tension element is a belt or for differently shaped tension elements, if the tension element is designed differently.

The cable attachment to the drum should preferably be designed so that, taking into account the friction of the remaining on the drum turns the 2.5 times the cable traction can be absorbed. The coefficient of friction between sheathed traction elements and the base is preferably determined by a conventional measuring or calculation method: For example, the force F can be measured, which is necessary for a rope resting on the drum and hanging down on both sides with an equal length to a motionless drum to move the radius r in by pulling straight down. If the rope has a mass per unit length of p, then μ = F / (2rpg), with g as gravitational acceleration can be estimated. If the difference in length ΔΙ between the rope end on one side and the other side of the drum is known at which the rope slips, then μ = Al / (2r) can be estimated. As a result, a sheathed rope is generally expected to have a higher coefficient of friction than a steel rope. This can be up to 1.5, for example; But the value can be in all directions strong, depending on the embodiment, in particular depending on the material and structure of the shell vary.

The cable attachment to the drum, so the attachment of the tension member to the drum, is preferably achieved by a wedgelock, a Klemmbriede or pressed, welded or molded end pieces at least partially. Part or all of the rope attachment can be done by friction of the tension member on the drum: This ensures that at all times in operation a minimum number of turns of the tension member rests on the drum. This minimum number can be 2.5 turns, for example. Various attachment methods, for example, the use of friction and a Klemmbriede can be used simultaneously. End pieces, Brieden and wedge locks and other fasteners may be located outside of the support surface of the drum, for example on the outside thereof.

Single-layer operation.

In one embodiment, the traction element and the drum of a cable drive are dimensioned in such a way, that is matched in their dimensions to each other so that the tension member rests on the drum at most one layer during operation of the cable drive at any time. It is preferably a cable drive with drum drive.

The tension member may in this case be a belt or a round rope. A belt has the advantage of particularly small bending radii. A round rope has the advantage of requiring a single layer on the drum less space and thus to be able to be longer than a comparable belt with the same drum length.

This dimensioning can be done by tuning various parameters: The length of the tension member, diameter and width of the drum and / or the leadership of the tension member can be suitably matched to each other. Also, a control of the cable drive can be used to ensure that the Zugorgan rests maximally single layer on the drum during operation. The delivery, storage and installation of the rope drive or individual parts of the rope drive should not be considered "operation", so that during these times the tension member can rest in one layer, multi-layer or not at all on the drum. The advantage of the single-layer bearing of the tension member is that it is prevented in a technically simple way that the jacket of the tension member is squeezed between sections of the support element. The jacket material is therefore only slightly deformed, which reduces the requirements for the choice of material and thus facilitates the selection of a jacket material. Also on the support element act less forces perpendicular to its longitudinal extent.

In a preferred embodiment, the surface of the drum on which the tension member rests, shaped so that the tension member is supported in its outer shape. Thus it can be achieved that the force exerted by the tension member on its support surface on the drum, acts on a larger surface and also shearing forces are minimized. This relieves in particular the casing material again compared to embodiments with a single-layer support on a differently shaped, in particular a non-adapted, support surface.

Multi-layer operation.

In one embodiment, the tension member and the drum of a cable drive are so dimensioned, that is matched in their dimensions to one another that the tension member at the times of operation of the cable drive, in which most of the length of the tension member is rolled, more than one layer on the Drum rests. Preferably, it is a rope drive with traction sheave drive.

A multi-layer edition of the tension member can be combined with other technical aids to relieve the tension member and in particular its coat: Thus, for example, the cable drive have a deflection, which as a "quasi-traction sheave" a portion of the tensile forces on friction of the tension member If a traction sheave drive is used, the traction sheave absorbs a large part of the traction forces, so that the traction element is wound on the drum with only slight tension, so that the force with the higher layers of the traction element is on the lower one Layers exert less weight than winding under higher tensile force, so the tension element is less squeezed and thus relieved.

It is also possible to attach relief materials between different layers of the tension member. Such relief materials can, for example, the forces that a Upper Zugorgan-Heath would exert on a lower Zugorgan- Iage, redirect to the drum and / or increase the contact surface of the tension member on itself and thus prevent particularly harmful high local load peaks. A relief material may continue to act by strengthening the lower tension member halyard. Relief materials may be placed around, under or over this during reeling of the tension member, or through a special form of the reel, for example in the form of a laterally open spiral.

If the support member is multi-layered on the drum and there are no other technical aids, traction sheaves or relief materials, the sheath material and the support element material can also be chosen such that the tension member takes no damage under the loads during operation and reaches a useful life.

In all cases, a multi-layer support of the tension member allows the use of a more compact drum at a given Zugorganlänge.

Pulley. In one embodiment, the cable drive comprises at least one pulley. This pulley is in contact with the tension member. The pulley is preferably a deflection roller or a compensating roller.

The use of pulleys makes it possible to make the course of the tension member and the distribution of forces more flexible. In the simplest form, the course of the traction element in a rope drive is determined only by the drum and the external forces, such as gravity: for example, the traction device hangs down from a drum mounted at a certain height and how far the traction element hangs is controlled by how much of the tension member is wound on the drum. The pulleys now allow the drum to be selected independently of the desired working direction and working position of the tension member, since the direction of the tension and the position of the tension member can be determined by suitable positioning of one or more pulleys. With the help of free and fixed pulleys, a smaller force can act on the principle of a pulley a longer way to exercise a greater force along a smaller path. Balancing rollers allow a more even load of traction elements, for example, when several traction elements that run on a drum act on a bottle.

Round rope.

In one embodiment, the tension member is a round rope whose support element is formed by a stranded rope. The stranded rope comprises one or more strands. At least a portion of the strands of the stranded rope comprises steel wires. These steel wires preferably have a tensile strength of> 21 60 N / mm ² , in particular of> 2300 N / mm ² , in particular of> 2500 N / mm ² , especially of> 2600 N / mm ² , especially of> 2800 N / mm ² .

Round ropes can be produced comparatively easily.

In order to be able to work with small bending radii, ie small pulleys and drums, even at high loads, the use of tension members in belt form is also possible. In the case of Belts, in cross section perpendicular to the longitudinal extent, the extent in a first direction is significantly greater than the extent in a second direction perpendicular to the first In particular, the extent in a first direction may be greater than or equal to Belts may comprise more than one support member, the support members then being substantially parallel to one another and each at least partially surrounded by a common jacket.

Tension members can also be designed differently: A tension member with a single support element and a jacket flattened on one side, two parallel flat surfaces or a polygonal cross-section jacket, for example, be advantageous to transmit forces evenly on the support surface of the drum or also to allow a multi-layer support element winding on the drum.

A stranded rope comprises one or more stranded strands. A stranded rope may also comprise individual wires or other fibers stranded with the strands. Alternatively, in a round rope or in a differently shaped tension member, a plurality of strands may be parallel to one another or a larger number of individual wires or fibers may run parallel to one another. A support member may also consist of interwoven or woven wires or fibers. Steel wires have the advantage of high tensile strength. By suitable choice of material and processing steps, steel wires with tensile strengths of> 2160 N / mm ² or> 2300 N / mm ² or even> 2500 N / mm ² or> 2600 N / mm ² or> 2800 N / mm ^{2 can be} produced. The disadvantage of using such wires, namely that the high strength damages the drum and pulleys, is lifted by the sheathing of the support element. In a cable drive according to the invention, it is thus possible to use traction elements with particularly high-tensile load bearing elements. Such tension members may be thinner at the same breaking load, as tension members with less tensile strength support elements.

The tensile strength of the wires here refers to the tensile strength determined after wire manufacture, which is given due to the same manufacturing conditions and, where appropriate, sample measurements for a batch of wire. The wires are in particular cold drawn. This manufacturing process and the increase in tensile strength are well known, so that even from the manufacturing process, a tensile strength value can be determined for the wires. The specified values should be understood in particular as values with the usual tolerances of -0 and +350 N / mm ² . Instead of steel wires and plastic fibers and / or natural fibers such as aramid, polyamide, carbon, polyethylene or hemp can be used. In particular, it is also possible to combine different fiber materials and wire materials within a support element. Such combinations have the advantage that the friction and pressure of the wires, fibers and / or strands can be positively influenced against each other. Also, individual fibers, wires or strands can take on specific tasks, such as pointing to damage to the support element or to facilitate their detection. Also for signal transmission single fibers, wires or strands can be used.

Many outer strands. In one embodiment, at least one of the support members is a stranded rope having six or more outer strands. In a particular embodiment, at least one of the support elements is a stranded rope with nine outer strands.

The use of many strands, in particular six or more, for example nine, has the advantage that the resulting stranded cable has a high flexural fatigue performance, which means a longer service life. Furthermore, comparatively thin wires can be used when using many outer strands. Since high wire denier strengths can be achieved primarily with thin wires, a support element with many outer strands of thin wires, wires with nominal strengths of for example> 21 60 N / mm ² ,> 2300 N / mm ² ,> 2500 N / mm ² ,> 2600 N / mm ² ,> 2800 N / mm ² or 3400 N / mm ² or more.

Embodiments of support elements with less than six strands have the advantage that they are simpler and cheaper to manufacture. In one embodiment, therefore, at least one of the support elements is a stranded rope with two, three, four or five outer strands. An outer strand number between six and nine gives stranded cables with a comparatively high bending fatigue performance, which are relatively inexpensive to manufacture.

In one embodiment, at least one of the support elements is a "wire-core" or WC-cable, that is to say a single-layer cable with steel insert, or an "in-dependent wire-rope core" or IWRC-cable, that is, a single-ply rope with separately stranded wire rope liner, or a "parallel wire rope core" - or PWRC rope, that is, a rope in which a wire rope liner and the outer strands, in particular in one step, are stranded in parallel or a "fiber insert" (English: "fiber core") - or FC rope, so a rope, in particular a stranded rope, with a fiber core as a central element, ie as a deposit for the deposit and for the strands, especially the Steel insert, preferably using the Warrington, Seale or Filler construction, or a combination of different constructions, but less well-known and other constructions are also possible The choice of construction of the insert and the underside different outer strands and other strands of a strand rope is independent of each other. In one embodiment, the cable length is less than or equal to 7.5 times the support element diameter, in particular less than or equal to 6.8 times the support element diameter. A small cable length increases the flexibility of the support element and thus also of the tension member in which it is used. A small cable length thus allows even smaller bending radii.

In one embodiment, the tension member comprises a jacket with a constant thickness of 0.8 to 1 .2 mm and exactly one support element. The support element is a stranded rope with a wire rope core as a deposit and outer strands. In addition, it is the support element is a Kreuzschlagseil. The wire rope core of the support element is parallelepiped with the outer strands.

The wire rope core comprises a core strand and intermediate strands. The core strand may, for example, be surrounded by nine intermediate strands. This insert, so the wire rope core is in turn surrounded by outer strands. For example, there can be nine outer strands. The core strand, the intermediate strands and the outer strands consist of steel wires. The diameters and the number of steel wires can differ in the different strands. The steel wires preferably have a wire nominal strength of more than 2600 N / mm ² .

The support element is a cross-cut rope: While the outer strands as such are right-handed (Z) opposite the rope, the outer wires of the outer strands are left-handed (s) opposite the outer strands. The entire rope, so the wire rope core and the outer strands are stranded in one operation, so that there is a parallel-stranded rope. Conversely, the outer strands could be left-handed with respect to the rope and the wires of the outer strands could be right-handed with respect to the outer strands.

The wire rope core is preferably a strand of Warrington construction. It could also be used, for example, a Seale or Filler construction or a combination of different constructions.

In one embodiment, the intermediate strands are single-layer strands.

In one embodiment, the outer strands are strands of the Seale construction. It could, for example, a Warrington or Filler construction used become. In one embodiment, the outer strands are stranded in parallel with the o-described above and a similar steel cable insert.

The outer strands, intermediate strands and the core strand in one embodiment each consist of wires that are twisted helically. Traction members designed in this way have proven useful in cable drives according to the invention.

Lifting drive.

A lifting drive comprises a cable drive according to the invention and a drive which acts on the drum and / or on a traction sheave and can thus effect a movement of the traction member.

It is thus in particular a cable drive with drum drive or a rope drive with traction sheave drive, in which the winding of the rope is controlled by a drive on the drum when the drive acts on the drum.

It is therefore in particular a rope drive with traction sheave drive when the drive acts on the traction sheave.

In a preferred embodiment, a lifting drive further comprises a load bearing, which can be controlled by a movement of the tension member in their movement. In particular, the load bearing can be driven by the movement of the tension member.

The drive acting on the drum and / or the traction sheave may be a motor or a hand drive or a drive utilizing forces such as wind, current, tides or other motions. It is also possible to use different types of drive simultaneously and / or as a supplement to and / or as a replacement for a drum and / or traction sheave.

The tension member is wound or unwound by the movement of the drum on this and set in motion. The necessary to move loads tensile force is generated by the movement of the drum and / or the traction sheave, generated by the at least one drive. The movement of the tension member is preferably used for the movement of changing loads. To move various loads through a pulling member, a load bearing can be used. The load bearing is a device with which loads can be detachably connected or a device can absorb the loads. Load receptacles may be, for example, hooks, eyes, baskets, platforms, slings, buckets and the like. A lifting drive with such a load bearing can be used for example in a crane, in a storage and retrieval unit, in a salvage or in a conveyor.

If, on the other hand, the load is not to be changed frequently, the pulling mechanism of the lifting drive can also be connected directly to this load. Such applications are for example a floodgate, a theater curtain or a drawbridge.

Gripper and platform.

In one embodiment of a lifting drive, the load bearing is designed as a gripper or platform and secured at least inter alia at one end of the tension member or on a loose pulley.

For the application of the lifting drive in automated storage and retrieval devices load receptacles offer in the form of grippers and platforms, as these load receptacles relatively easy allow a machine grasping the goods to be transported. For example, a platform may be driven under a load, or the load may be pushed onto a platform by a mechanically generated shock or pressure movement. A gripper can take a load automatically. Depending on the configuration of the gripper, however, it may be the case that the load must consist of standardized pieces or standardized transport containers in order to allow a smooth flow. Grippers that hold variable and a priori unknown loads safely can also be used. Grippers for standardized pieces or transport containers are simpler and thus cheaper.

A load bearing, which is fastened at least inter alia at one end of the tension member, has the advantage that a movement of the tension member acts in exactly the same extent on the load bearing. The load bearing is thus moved directly. A fast movement of the load suspension is possible. A load on a loose pulley causes the change in position of the load bearing is only a fraction of the movement of the tension member by the drive. According to the principle of pulley, the, applied by the drum or its drive, pulling force decreases with increasing number of discs. Drum and drive are therefore less stressed.

In addition to the pulley or the Zugorgan- end, the load bearing can also be additionally attached and move, for example, on rails or be held with other ropes, traction devices and / or vanes on a special track.

A load bearing can also be attached to a different location of the tension member, as only at the end. Thus, for example, at uniform distances from each other several load receptacles, such as platforms, be attached to a pulling member. Also, a load bearing, for example, a gripper, be mounted at a certain distance from the end of the tension member. The part of the tension member between the end and the load bearing can be used, for example, to stabilize the position of the load bearing in the plane perpendicular to the fastener or to guide the load bearing.

Hoist.

A hoist comprises a lift drive and a bracket. The bracket at least partially absorbs the forces acting on at least a portion of the lift drive.

Different forces can act on the lift drive: For example, these are the forces needed to hold the load bearing and the load thereon. Even on existing pulleys can act forces that can accommodate the holder. Further, depending on the positioning of the drive and / or the drum, it may also be necessary to support these or other components by brackets. A holder preferably comprises a mounting device for the fixed guide rollers and / or the drum and / or its drive. The bracket may consist of several pieces and consist for example of hooks, angles, rods or other designed holding devices that adhere to walls, the ceiling or the floor of a building or a room or on a support structure, such as beams fasten. The attachment can by conventional means, such as by screwing, nailing, riveting, welding, lashing, gluing, Einbetonieren, walling and / or pouring and the like and by combinations of different fasteners, for example screws with subsequent pouring, done. Each piece of bracket can be fixed to another location (wall, ceiling, floor, bracket, etc.) by other means.

A holder preferably also comprises a framework to which one or more mounting devices for deflection rollers and / or the drum and / or the drive and / or optionally the traction sheave are attached. For example, such a framework may consist of a single support, forming a gantry structure, or comprising a cantilever held in some height or position by other elements. For the purposes of the invention, a scaffold should preferably be self-supporting, but may be fastened to a building, to a ceiling, to rails and / or similar external structures, for example to improve stability, to prevent tilting and / or positioning partially touch.

Pulleys not fastened with mounting devices are, for example, loose pulleys. Fixed pulleys can also be designed so massive that they rest on their own weight on the ground and do not require a holding device. Also, the drum and the drive can be so heavy that the dead weight fixes them at the desired position. Further, the cable drive can be designed such that the forces that are necessary for moving the load with the load, drum, drive, traction sheave and / or pulleys in the desired positions hold: For example, if a first pulley below the drum and / or Traction sheave, so the pulling force of the tension member can pull down the drum or traction sheave and thus press against the ground on which the drum and / or traction sheave is.

The mounting devices may be attached to the walls, ceiling or floor of a building or room, or to a support structure or to a scaffold so that they can move with respect to the location of attachment or that they are fixed to the location of attachment. A movable mounting device can, for example Run rails or held by another adjustable cable drive at the mounting location. Such a movable mounting allows a more flexible use of the cable drive. A "movable mounting device" comprises at least two parts: one part is fixed immovably at the mounting location (for example rails or rollers of a cable drive) while a second part can be controlled to move relative to this first part Drive, the traction sheave or the drum to be attached.

A fixed assembly of a mounting device or a holder, for example by screwing to a carrier or to a scaffold, is technically simpler, cheaper and in many cases more stable.

Carriage.

In one embodiment, a hoisting machine comprises a carriage which can be moved relative to the holder. This movement is called a carriage movement. The carriage movement can control a lift drive motion. The lift drive movement is a movement of at least a portion of the lift drive relative to the support.

A carriage is an embodiment of a movable mounting device. A carriage movement is preferred when the carriage can move relative to at least a portion of the support. The carriage can move in particular with respect to the framework. In particular, one or more pulleys may be attached to a carriage, so that the load bearing of the hoisting machine can be moved by the movement of the carriage. This is preferably in particular a movement in a plane perpendicular to the tensile force on the load absorption by the tension member.

In particular, the drum and / or the traction sheave may be located on the carriage. In this case, a cable drive may simply comprise a pulling member that can be rolled up and down by a drum located on a carriage. The pulling member can exert a desired tensile force on a load by controlling its movement by a controlled movement of the drum and / or a traction sheave. By rolling up and down the traction member, a movement of a load in one direction can be generated become. The carriage movement causes a movement of the tension member and thus possibly also a movement of the load in a second direction. Thus, a transport in two directions can be made possible.

A carriage according to the invention preferably moves on a carriage guide, such as rails, guide cables, guide elements or markings. The carriage can slide and / or slide and / or roll over this slide guide. The carriage may have its own carriage drive or be accelerated, moved and braked by an external device by train, pressure and / or by forces such as magnetism and / or by its own weight. Also, limitations and / or changes in the structure of the carriage guide may control or limit the carriage movement.

A carriage may be on a second carriage or otherwise moved by a second carriage. If the direction of movement of a carriage is chosen differently than the direction of movement of the second carriage, the lifting machine can allow transport in three directions. Hoist construction.

A hoisting machine assembly comprises a hoisting machine and a reference surface which receives the forces acting on the hoisting machine and a displacing device which allows movement of at least part of the support relative to the reference surface, in particular by rolling wheels. The reference surface is preferably a floor or a ceiling.

A hoist assembly is a hoist that can move through the shifter relative to the reference surface. An example is a crane, which is mounted on a trailer. In this case, the road on which the trailer can move is the reference surface. Scaffolding, rope drive and drive of the rope drive of the crane in this example form the hoist. The framework represents the holder. The trailer with its wheels forms the displacement device in this example. Another example is a crane mounted on rails on the ceiling: since the rails on the ceiling support the hoist, they define the reference surface. Shifter and scaffolding can be a crossbeam, which can be moved on the rails. This truss can now, but not necessarily, carry a sledge. The drum and / or traction sheave and their respective drive and individual pulleys are preferably attached to the rails on the ceiling or on the crossbar or on the carriage, which runs on the crossbar attached.

The movement of the displacement device may, but need not, occur along displacement guides. Displacement guides can be realized, for example, by rails, guide cables, guide elements or markings. The shifter may slide or slip or roll over or at a defined distance from the shift guides. The displacement device may have its own displacement drive or be accelerated, moved and braked by an external device by train, pressure and / or by forces such as magnetism and / or by its own weight. Also, limitations and / or changes in the structure of the displacement guide may control or limit the movement of the displacement device.

A movement of the displacement device without displacement guides is given, for example, when the displacement device is a carriage that can be controlled in any direction, for example by a human. It is also possible that a displacement device is used in an operating state without displacement guides and in a second operating state displacement guides are used. Thus, for example, an arbitrarily controllable car can be equipped with sensors that can be used to automatically follow the car to certain markings. Production of the rope drive.

A method for producing a cable drive comprises the following steps: a) a drum is provided, b) a tension member comprising a support element and a jacket which constitutes the support surface of the tension member is provided; c) the tension member is applied to the drum such that it can run on the drum. Step c) is usually that one end of the tension member is fixed at a position of the drum, so that the tension member neatly wound on rotation of the drum on the drum. The contact between the drum and tension member should be so strong and stable that the movement of the drum can be transferred to the tension member in any operating condition. The contact or the coupling between drum and tension member can be prepared by known Zugorgankopplungsmethoden. One possibility is, for example, the use of a wedge lock, a clamping bolt or of pressed-on, welded-on or cast-on end pieces. Further, the friction of the tension member can be used on the drum in which is ensured at any time during operation, that a minimum number of windings of the tension member is on the drum. In particular, it is possible that a Zugorgangende is guided laterally out of the drum and is fixed there with a wedgelock. Alternatively, the end of the tension member can be fixed with a Klemmbriede and be ensured by the control of the cable drive that always at least 2.5 windings of the tension member rest on the drum.

If a traction sheave drive is used, the method for producing a cable drive thus additionally comprises the provision of a traction sheave, the traction element can also be controlled such that less than 2.5 windings, in particular no winding of the traction element at individual times, rest. The tension member should always remain in contact with the drum. An attachment with a wedge lock, clamping bolt, pressed-on, welded-on or cast-on end pieces may, however, be less stable than in the case of a cable drive with a drum drive.

Production of the lifting drive.

The method for producing a lifting drive comprises the following steps: a) The method for producing a cable drive, b) coupling a drive to the drum and / or a traction sheave so that the drive can cause movement of the drum and / or the traction sheave, preferably a rotation, and thus cause the drum and / or traction sheave to move the traction element; c) and preferably the mounting of a load bearing, which can be controlled by a movement of the tension member in their movement and in particular can drive.

Couplings between drives and drums, traction sheaves and / or axles of different types are known in the art. The drive axle of an engine can be connected, for example, with a positive engagement directly or via a transmission or, alternatively, directly or via a transmission to the axis of the drum or traction sheave. A drive could also act on one or more points of the drum or traction sheave, which are located at the greatest possible distance from the axis of rotation. For example, a plunger can hit such points and a detent mechanism prevents unintentional turning back of the drum or traction sheave. A coupling via a drive belt, so with the help of a frictional connection, is possible. The choice of coupling can be determined, among other things, by which drive is used: Water and wind movements could make a "ram / detent coupling" advantageous, since naturally uneven movements can be used in this case, the coupling with drive belt is "softer ": Sudden fluctuations in the force generated by the drive, which are only up to a certain amount transferred to the drum or traction sheave because slipping at higher accelerations of the drive belt. This further transfer can reduce the mechanical loads on the various components of the lift drive.

The control of the movement of the load absorption by the tension member can be done inter alia by a controlled driving, a controlled braking or the control of the direction. In all cases, the tension member preferably produces a controlled tension in the opposite direction to the other forces acting on the load or load bearing.

Production hoist. The method for manufacturing a hoisting machine comprises a) the method for producing a lifting drive, b) providing a holder, and c) combining the lifting drive and the holder, such that the holder fits onto at least a part of the lifting drive can absorb acting forces.

In addition to the holder, a part of the forces can also be absorbed by the footprints of various components of the lifting drive, such as the drum, the traction sheave or the drive.

From the following detailed description and the totality of the claims, further advantageous embodiments and feature combinations of the invention result.

Brief description of the drawings

The drawings used to explain the embodiment show:

1 a shows a cable drive with a drum and a tension member. FIGS. 1 b and c show a first and a second embodiment of the support surface of a

drum

Fig. 2a, b and c Three embodiments of the tension member as a round rope

Fig. 2d, e, f, g Three embodiments of the tension member as a belt

Fig. 3 shows an embodiment of a tension member as a round rope with a Litzenseil as a support element.

Fig. 4a, b Two embodiments of a lifting drive

Fig. 5 is a hoist Fig. 6a, b Two embodiments of lifting machines with different con trolled carriage

Fig. 7a and b Two embodiments of hoisting machine abutments

Fig. 7c lifting machine structure in the application as a stacker crane Fig. 8a, b explanation of the dimension of a tension member

Fig.9a-c explanation for the determination of the jacket thickness

Basically, the same parts are provided with the same reference numerals in the figures.

Ways to carry out the invention

FIG. 1 a shows a cable drive 100, which comprises a drum 1 and a pulling member 2. The tension member 2 can be wound up and unwound by rotation on the drum 1. The tension member 2 lies on the support surface 1 1 of the drum 1. In a multi-layer operation, the tension member 2 is only partially on the support surface 1 1 of the drum 1 and partly on itself.

Figures 1 b and 1 c show two different drums 1. The drum in Figure 1 b has a support surface 1 1, which is adapted to the outer shape of the tension member 2. Thus, a large contact surface between the tension member 2 and bearing surface 1 1 is possible. This can protect the tension member 2 from deformation and guide the tension member 2 during winding in a desired winding.

The drum in Figure 1 c has a flat support surface 1 first Such a bearing surface 1 1 can be used for traction elements 2 of different cross-sectional shapes and cross-sectional dimensions.

Figures 1 b and 1 c represent only two examples. Other forms of support surface 1 1 are possible. Thus, the bearing surface 1 1 may, for example, be concave or convex shaped than the exact complementary shape of the tension member 2. Thus, for example, the pressure can be selectively distributed to areas of the tension member 2, not directly in the direction Axis of the drum 1 are directed. Or the bearing surface 1 1 can steer by means of other devices or alone the winding process of the tension member 2. The winding of the tension member 2 can be done or supported alternatively or in addition by a Zugorganführung. FIGS. 2 a to g show a number of different embodiments of tension members 2. All tension members 2 comprise at least one support element 21 and a jacket 22.

Although FIGS. 2 a to g appear to show a clear boundary between the support element 21 and the jacket 22, this is not necessarily the case: the support element 21 may have unevennesses on its outside or may also have cavities in its interior into which shell material can penetrate and these partially or completely fill or cavities and bumps can be filled at earlier points in time with the production of jacket material. The boundary between jacket 22 and one of the support elements 21 is preferably defined in such a case by the envelope of the respective support element 21. Figures 2a and c show different embodiments of tension members 2 in the form of round cables 2a. All tension members 2, and therefore also all round cables 2 a, comprise at least one support element 21 as well as a jacket 22. FIG. 2 b shows a further embodiment of a tension member 2.

Figure 2a shows a cross section through a round rope 2a with a single support member 2 1. The support member 21 also has a substantially round cross-section. The support member 2 1 is surrounded by a shell 22 along its entire circumference and the thickness of the shell 22 is substantially the same everywhere. The thickness of the shell 22 may be, for example, 1/5 or 1/10 of the diameter of the support member 21 in such an embodiment, or even thinner or thicker. Figure 2b shows a cross section through a pulling member 2 with a single support member 2 1. The support member 2 1 also has a substantially round cross-section. Unlike in Figure 2a, the jacket 22 surrounds the support element 21 but only along a part of its circumference. Also, the thickness of the shell 22 varies along the circumference of the support The maximum thickness of the shell 22 may be, for example, 1/5 or 1/10 of the diameter of the support member 21 in such an embodiment, or even thinner or thicker.

Figure 2c shows a cross section through a round rope 2a with four support elements 2 1 a-d. These four support members 21 a-d are only in contact with each other via the jacket material. If the support elements 21 a-d would be stranded together or could absorb significantly tensile forces from one another via connections, one would speak in the sense of the application of a single support element and not four. All support elements 21 a-d are surrounded by a jacket 22. The outside of the jacket 22 is circular in FIG. 2c. Figures 2d, e, f and g show different embodiments of tension members 2 in the form of belts 2b. All tension members 2, and therefore also all Belts 2b, comprise at least one support element 2 1 and a jacket 22nd

Figure 2d shows a cross section through a belt 2b with two support elements 21 a, b. Both support elements 2 1 a and b have a substantially circular cross-section and are essentially the same size. The support members 2 1 a and b are surrounded by a jacket 22 along its entire circumference. The outer shape of the cross section of the shell 22 is substantially a rectangle. The smallest value for the common jacket thickness may for example be 1/5 or 1/10 of the diameter of one of the support elements 21 a or b in such an embodiment or even thinner or thicker. Figure 2e shows a cross section through a belt 2b with three support elements 21 a-c. The support elements 21 a-c have a substantially round cross section but partially different diameters. The support members 21 a and c have the same, smaller diameter and are completely surrounded by the jacket 22. In contrast, the shell 22 surrounds the support member 2 1 b only along part of its circumference. The outer shape of the cross section of the shell 22 is substantially a rectangle.

Figure 2f shows a cross section through a belt 2b with two support elements 2 1 a, b. Both support elements 2 1 a and b have a substantially round cross section and are substantially equal in size. The support members 2 1 a and b are surrounded by a jacket 22 along its entire circumference. The jacket 22 encloses the two support elements 2 1 a and b uniformly thick. In addition, the jacket 22 forms a web between the two support elements 2 1 a and b. The thickness of this web is smaller here than the diameter of each of the two support elements 2 1 a and b. The smallest value for the common jacket thickness can be, for example, 1/5 or 1/10 of the diameter of one of the support elements 21 a or b in such an embodiment, or even thinner or thicker.

Figure 2g shows a cross section through a belt 2b with a support member 2 1. The support member 2 1 has a substantially rectangular cross-section and may be, for example, a braid or a fabric. The support element 21 is surrounded by a jacket 22 along its entire circumference. The jacket 22 envelops the support member 21 on all sides uniformly thick. The smallest value of the cladding thickness may, for example, be 1/5 or 1/10 of the smaller diameter of one of the support element 21, or even thinner or thicker. The outer shape of the cross section of the shell 22 is substantially a rectangle.

FIG. 3 shows a pulling member 2 in the form of a round rope 2 a with a uniformly thick jacket 22. The jacket 22 preferably has a thickness of 0.8 to 1.2 mm. The support member 21 is formed as a stranded rope. It includes an insert 2 1 2 and outer strands 2 1 1 a. The insert 21 2 is a wire rope core comprising a core strand 21 1 c and intermediate strands 2 1 1 b. In the case shown, the core strand 2 1 1 c is surrounded by 9 intermediate strands 2 1 1 b. This insert 21 2 is in turn surrounded by nine outer strands 221 a. Kernlitze 2 1 1 c, the intermediate strands 21 1 b and the outer strands 2 1 1 a are made of steel wires 2 13a-d. The diameters and the number of steel wires differ in the different strands. The steel wires preferably have a wire nominal strength of more than 2600 N / mm ² . The support element 21 is a Kreuzschlagseil: While the outer strands 2 1 1 a of the round rope 2a to the right (Z) relative to the round rope 2a, the wires 2 13b of the outer strands 21 1 a left-handed (s) relative to the outer strands 21 1 a. The wire rope core, which forms the insert 21 2, is parallel-stranded with the outer strands 2 1 1 a. This arises in which preferably the entire cable, so the wire rope core and the outer strands 2 1 1 a, are stranded in a single operation.

The core strand 2 1 1 c comprises 13 steel wires with a first diameter and six steel wires with a second diameter. The first diameter is larger than the second diameter. The steel wires with the second diameter are in the outermost Position between each two steel wires arranged with the first diameter. Inside the core strand 21 1 c six steel wires of the first diameter are arranged around a steel wire of the first diameter. It is in the core strand 21 1 c to a strand of Warrington construction. It could also be used, for example, a seale or Filier construction or a combination of different constructions. The core strand 21 1 c here represents the deposit.

The intermediate strands 2 1 1 b each comprise seven steel wires 213 a with a third diameter. Six of the third diameter steel wires 213a are arranged around another third diameter steel wire 213a. It is in the intermediate strands 21 1 b to single-layer strands.

The outer strands 21 1 a each comprise a steel wire 2 13d with a fourth diameter. Around this steel wire 2 13d having the fourth diameter, nine steel wires 231 c having a fifth diameter are arranged. The outer layer of the outer strands 21 1 a is formed by nine steel wires 2 13 b with a sixth diameter. It is at the outer strands 21 1 a to strands of seale construction. Alternatively, outer strands of more wires and a filler construction can be used and stranded in parallel with the above-described or a similar steel cable insert.

The outer strands 2 1 1 a, intermediate strands 21 1 b and the core strand 2 1 1 c each consist of wires that are twisted helically. In the illustrated embodiment, the shell 22 has a thickness of 0.8 mm, the first, fourth and sixth diameters are equal; the second and third diameters are equal and smaller than the first diameter. The fifth diameter is smaller than the second diameter and substantially half the size of the first diameter. For example, the first, fourth and sixth diameters may be 1 mm, the second and third diameters 0.7 mm and the fifth diameter 0.5 mm. The jacket 22 may also be thicker, for example 1 mm or 1.2 mm.

The dashed line shown in Figure 3, around the intermediate strands 21 1 b around, serves only to illustrate the insert 2 1 2. It is not necessarily existing material or manufacturing limit. The inner boundary of the jacket 22 indicated in FIG. 3 also serves primarily for illustration and outlines the envelope of the support element 21. The jacket material is preferably also located within the envelope of the support element 2 1 in the spaces between at least part of the strands 2 1 1 ac and possibly also In the spaces between at least a portion of the wires 2 13. Instead of casing material spaces within the envelope of the support member 2 1 may be at least partially filled by other fibers, lubricants, plastics and similar materials. There may be different fillings at different locations in the same support member 21.

A portion of the steel wires in a support member 2 1 of Figure 3 can be replaced or supplemented by another metal or synthetic fibers such as aramid, polyamide, carbon, polyethylene, and similar or natural fibers such as hemp, sisal or flax.

The jacket 22 is made of a polymer. These may be, for example, materials such as polyurethane or EDPM or other thermoplastics and / or elastomers.

Figures 4a and 4b show two embodiments of a lifting drive 200 with drum drive. This comprises a cable drive 100, with a drum 1 and a pulling member 2 in the form of a round rope 2a, which rests on the drum 1 in one layer. Furthermore, the cable drive 100 comprises pulleys 3a, 3b in these two embodiments. The drum 1 is driven by a drive 5. In addition, two embodiments of a load bearing are shown: a platform 4a and a hook 4b. In Figure 4a, the drive 5 comprises a motor 5 1 and a transmission 52 on the drum 1. The transmission 52 is here, to show a possible example, realized by a drive belt 52 1, which can rotate the drum 1 about its longitudinal axis and thus the round rope 2a, depending on the direction of rotation or unwinds. The round rope 2 a passes over a fixed deflection roller 3 a: The pulling direction from the round part 2 a changes at this point from "in the direction of the deflection roller 3 a" to "in the direction of the drum 1" when the round rope 2 a is wound up. A fixed pulley is a pulley that can not adjust its location by the Zugorganbewegung. However, it can turn as a rule in response to the Zugorganbewegung about its axis, so that the Zugorganbewegung only slightly by the interaction with the deflection roller is braked. At the free end of the round rope 2a, a platform 4a is attached. On these loads can be made, which are then raised by winding the round rope 2a and are stored by unwinding of the round rope 2a, since the deflection roller 3a is located above the platform 4a. Figure 4b illustrates another embodiment of a lift drive 200: A drive 5 comprising a motor 51 and a transmission 52 acts on the drum 1. The transmission 52 shown here is a suitably shaped axle of the motor, the rotation thereof For example, via a positive connection with an opening in the drum 1, this set in rotation. The round rope 2a in turn passes over a free deflection roller 3a. The end of the round rope 2 a is fixed to a fixed point 6. On the round rope 2 a, between the fixed deflection roller 3 a and the fixed point 6, there is a loose deflection roller 3 b on the round rope 2 a. On the axis of this loose pulley 3b a hook 4b is attached. If now the round rope 2a is rolled up by the movement of the drum 1 caused by the drive 5, then the round rope section between the deflection roller 3a and the fixed point 6 shortens. The loose deflection roller 3b is thereby lifted and thus also a load fastened to the hook 4b. Upon rotation of the pulley 1 in the opposite direction, the round cable between the pulley 3a and fixed point 6 extends and the loose pulley 3b lowers, as well as attached to the hook 4b load.

In addition to the motors shown here, drums 1 can also be actuated by other drives, such as water or wind mills, treadmills or cranks. The direction of rotation can be determined either by the drive 5 directly or by a suitable coupling. Also, a rolling of the tension member 2 can be done simply by its own weight or the weight of things attached to the tension member 2 and controlled only by a brake or a motor brake or a controlled throttled drive 5 and / or controlled.

Examples of rope drives with traction sheave drive can be designed very similar: For this purpose, the deflection roller 3a is used as a traction sheave in Figures 4a and 4b. A traction sheave differs from a deflecting roller 3a primarily in that the traction sheave is driven and that high friction between traction member and traction sheave is desired becomes. The drive 5 acts on the traction sheave and no longer on the drum 1. The drum 1 is biased in both cases by a spring. The drum 1 may also have its own drive or be driven by a drive or drive belt of the drive of the traction sheave or the traction sheave with. Likewise, the drive can also act on the drum and either the drive or the movement of the drum drive the traction sheave via, for example, the transmission or drive belt. In a rope drive with traction sheave, the tension member 2 one or more layers rest on the drum 1.

FIG. 5 shows a hoisting machine 300, which comprises a lifting drive 200 and a holder 7. The lifting drive 200 comprises a cable drive 100 with a pulley 1, a round rope 2 a, pulleys in the embodiments as a fixed deflection roller 3 a and a loose deflection roller 3 b. Further, the lifting drive 200 comprises a drive 5, consisting of motor 5 and transmission 52 and a load bearing in the form of a gripper 4c. Similar to the embodiment of Figure 4b, one end of the round rope 2a is fixed to a fixed point 6 and the load bearing is attached to the loose guide pulley 3b, which in turn rests on the round rope 2a between the deflection roller 3a and the fixed point 6. The holder 7 is a stable frame, which in the case shown here can partially accommodate the lifting drive 200 and the forces acting on it. The holder 7 comprises for this purpose a mounting device 7 1 for the fixed guide roller 3a. Such a mounting device 7 1 can for example be given by a Zugelement-, rope or chain loop, which runs through an opening along the axis of the guide roller 3a and a horizontal strut of the holder 7. Other mounting devices 7 1 are for example suitable hooks, receptacles, axles and the like. The drive 5 and the drum 1 are here on a base 72, which is also part of the holder 7.

The fixed point 6, however, is not part of the holder 7 in this embodiment, but realized, for example, on the wall of a room.

In other embodiments, fixed points 6 may also be provided on the holder 7. Likewise, can be dispensed with a base 72 or this can be used only for individual parts. Also can be dispensed with the mounting device 7 1. There may also be more than one pedestal 72 and more than one fixture 71, or blends of both things: in the present case, the weight force holds parts on a pedestal 72. All A mounting device 7 preferably defines other types of fastening. A surface to which a drum 1 presses by its weight, but which is additionally screwed to the surface, is therefore an example of a mixed form between base 72 and mounting device 71 and is preferred also be covered by the term "mounting device".

FIG. 6a shows a hoisting machine 300, which is similar in large part to the hoisting machine from FIG. In contrast to FIG. 5, in this case the mounting device 7 1 of the fixed deflection roller 3 a is not fastened to an immovable part of the holder 7 but to a carriage 8. The carriage 8 has wheels 8 a and a slide drive in its interior in the shown embodiment. With the aid of this carriage drive, the carriage 8 can move its wheels 8a in a controlled manner and thus change its position in relation to the holder 7. The fixed deflection roller 3a attached to the carriage 8 with the mounting device 7 1 follows the change in position of the carriage 8. The changing location of the fixed deflection roller 3a, in conjunction with the winding or unrolling of the round rope 2a from the drum 1, can Position of the loose guide roller 3b and thus the gripper 4c are controlled. By this position, the location in the direction of movement of the carriage 8 can be changed in addition to the height.

FIG. 6b shows a further embodiment of a hoisting machine 300: Here, the cable drive 100 does not comprise rope pulleys, but only a drum 1 and a pulling element 2. A load bearing in the form of a bucket 4d is attached to the pulling element 2. The pulley is located on a carriage 8, which in turn can be moved on a bracket 7. Also, not shown here, drive the drum 1 is located on or in the carriage 8. The carriage 8 in turn has wheels 8a. The holder 7 on which the carriage 8 can move, is designed such that the gravity pulls the carriage 8 in one direction. A bumper 8b and a stopper 8c prevent the carriage 8 from leaving the desired area of the holder 7. A brake cable 8e and a brake cable control 8d control the movement by gravity and allow the carriage 8 to be returned to an initial position. The holder 7 has here only a vertical stand and one of them laterally continuing boom. This geometry can also be used together with the carriage 8 and other cable drives 100 shown in FIG. 6a.

Figures 7a and 7b show hoist assemblies 400. In Figure 7a, a hoist 300, similar to that of Figure 6a, is shown. In contrast to the hoisting machine 300 from FIG. 6 a, the fixed point 6 on the holder 7 is here. The hoisting machine 300 is located as a whole on a carriage 9 with wheels 9 a. The carriage 9 can move relative to a reference surface 10. The reference surface 10 is here an outdoor place. The carriage 9 and the carriage 8 can be oriented such that the direction of movement of the carriage 19 is different from the direction of movement of the carriage 18. Thus, the gripper 4c can be moved in several dimensions relative to the reference surface 10: its height can be significant determined by the drum 1, the position in the direction 18 by the carriage 8 and the position in the direction 19 by the carriage 9. It is of course also conceivable that carriage 8 and carriage 9, both can move in several directions. Then, a combination of carriages 8 and carriages 9 can improve or accelerate the degree and precision of the movement. Further, it is also possible to provide only one carriage 9, but no carriage 8 in a hoist assembly 400.

Also shown in Figure 7b is a hoist assembly 400. In this case, the reference surface 10 is formed by a roof rack of a building. On this carrier, a carriage 9 can move with wheels. This carriage 9 in turn carries a simple cable drive 100 comprising a drum 1 and a round rope 2a. At the round rope 2a, a load bearing in the form of a bucket 4d is mounted here.

FIG. 7c shows a lifting machine superstructure 400 which is used as a storage and retrieval unit. On a carriage 9 with wheels 9a, a drum 1 is fastened with its drive, not shown. Next, a bracket 7 is fixed to the carriage 9, on the one hand carries a guide roller 3a and on the other hand, a platform 4a leads. The platform 4a is used for lifting the load. In a shelf 1 2 are goods 1 1, which can be moved by means of a removal device 1 3 on the platform 4a of the hoist body 400. The hoist assembly 400 now allows the height at which the product 1 1 is to be controlled by winding or unrolling the round rope 2a onto the pulley 1 and the position opposite the shelf 1 2 having a fixed position with respect to the reference surface 10, to change by the carriage 9. Goods 1 1, for example, by automatically tilting the platform 4a automatically put back into a shelf 1 2 or to a sampling.

Storage and retrieval machines are conceivable in many variants: Thus, the holder 7 can be designed in a variety of variants, such as a portal structure. Instead of a movement by a carriage 9, the use of a carriage 8 is possible if the holder 7 can carry or lead such. Furthermore, a storage and retrieval device can also essentially control only the vertical movement of goods and therefore dispense with carriage 9 and carriage 8, while a horizontal movement is realized by a further transport device. Furthermore, the cable drive 100 may comprise more or fewer pulleys than shown in FIG. 7c and / or the pulleys may be arranged differently than in FIG. 7c. Instead of a round rope 2a, a belt 2b or another tension member 2 can also be used. The load bearing can be designed differently, for example as a basket, hook, grapple, bucket or the like. A removal device 13 may also be part of the load receptacle 4, be mounted on the load receptacle 4 or be part of the stacker crane or be mounted on this.

The carriage 9 shown in FIGS. 7a-c is an embodiment of a shifting device. A further embodiment of a displacement device is, for example, a sliding guide in which the holder 7 is displaced relative to the reference surface 10. On a smooth floor, for example with a type of air cushion or by magnetic levitation, the friction between holder 7 and reference surface 10 or guidance of the displacement device be reduced and on the other hand, a movement of the holder 7 relative to the reference surface 10 are generated.

To illustrate the preferred determination of the dimensions of a tension member 2, FIGS. 8a and 8b can be used: FIG. 8a shows a section of the tension member 2, which comprises a shell 22 and a support element 21. The tension member 2 is significantly longer in one direction than in the directions perpendicular thereto and therefore has a longitudinal axis 900. The cross section of the tension member 2 is perpendicular to its longitudinal axis 900 is shown in FIG. 8b. This cross-section is substantially equal to the cross section shown in Figure 2b and the explanations of Figure 2b also apply here accordingly. Next, however, three pairs of two, not identical parallels 901 ai and 901 bi with i = 1, 2 and 3 are drawn. The parallels 901 a and 901 b each touch the cross section of the tension member 2, but without cutting it. Their distance 902 is therefore a kind of diameter of the tension member 2. Of all possible distances 902, which can be determined in such a way is one of the largest and one of the smallest. The smallest distance is the first diameter 902.1 of the tension member 2 and the largest distance is the second diameter 902.2 of the tension member 2. To illustrate the preferred determination of the shell thickness 907, FIGS. 9a, b and c can be used. FIG Zugorgans 2, which comprises a jacket 22 and a support member 21. In Fig. 9a, only the jacket 22 is visible, the tension member 2 is significantly longer in one direction than in the perpendicular directions and therefore has a longitudinal axis 900. The cross section of the tension member 2 perpendicular to its longitudinal axis 900 is shown in Figures 9b and c shown.

In order to determine the jacket thickness 907, first of all the geometric center of gravity 903 of each supporting element 2 1 occurring in this pulling element 2 is determined. In addition, the support surface 904 is detected. In the case of an assembled tension member, this can be determined, for example, by applying a layer or pressure-sensitive layer (for example, similar to carbon paper) at a suitable point on the tension member 2 over its entire circumference: If the tension member thus prepared is now put into operation, then Depending on the method, the support surface 904 is characterized by the missing or newly created marking. For rope drives in the planning or in which only plans are available, it can be determined from these, whether a special support surface 904 of the tension member 2 is desired. If this is not the case, then the entire outer surface of the tension member 2 is considered as "bearing surface 904" for determining the jacket thickness.

Figure 9b shows the first step of the analysis: All straight lines passing through the center of gravity 903 of a selected support member 21 and the support surface 904 in the example shown in Figure 9b are within the roughly hatched area 905. (For clarity, this has been omitted the straight lines, starting from the center of gravity 903 in the other Direction to draw). Some of the lines 905 intersect two support elements 2 1. These should not be used for the determination of the jacket thickness 907. Starting from the selected support element 2 1 therefore remain the straight lines for further evaluation, which extend within the surface 906. FIG. 9c shows the situation after the analysis of FIG. 9b has been repeated for all supporting elements 21: there are now a multiplicity of surfaces 906, starting from the different centers of gravity of the supporting elements 2 1. Among all the straight lines shown there, the one now applies find, in which the distance between the support surface and from there first intersection with the envelope of the associated support member 2 1 is the shortest. This is the jacket thickness 907.

Claims

claims

1. rope drive, in particular for cranes or Serienhebezeuge, comprising a) a drum (1) and b) a tension member (2),> 1) which runs on the drum (1) and b2) which comprises at least one support element (21) characterized in that b2a) the at least one support element (21) is at least partially surrounded by a jacket (22) comprising a polymer, b2b) wherein at least a part of the jacket (22) constitutes a contact surface of the tension member (2).

2. A cable drive according to claim 1, characterized in that a) the jacket consists essentially completely of the polymer and b) that the polymer is in particular a thermoplastic and / or an elastomer.

3. rope drive according to one of claims 1 to 2, characterized in that

Tension member (2) and drum (1) are matched in their dimensions to one another that the tension member (2) rests at most at one time during operation of the cable drive single-layered on the drum (1).

4. rope drive according to one of claims 1 to 2, characterized in that

Tension member and drum of a cable drive are so matched in their dimensions to each other that the tension member at the times of operation of the cable drive where most of the length of the tension member is rolled up, the tension member rests more than a single layer on the drum.

Cable drive according to one of claims 1 to 4, characterized in that the cable drive comprises at least one pulley (3) which is in contact with the tension member (2), wherein the pulley (3) preferably as a deflection roller (3a, 3b) or compensating roller is designed.

Cable drive according to one of claims 1 to 5, characterized in that the tension member (2) is a round rope (2a), the support element (21) is formed by a stranded cable, which one or more strands (21 1 a, b, c) and wherein at least a part of the strands (21 1 a, b, c) of the stranded cable comprise steel wires (2 13), which preferably has a tensile strength of> 2 160 N / mm ² , in particular of> 2300 N / mm ² , in particular of > 2500 N / mm ² especially of> 2600 N / mm ² , especially of> 2800 N / mm ² .

Cable drive according to one of claims 1 to 6, characterized in that a) at least one of the support elements is a stranded cable with six or more Außenlit- zen, in particular with exactly nine outer strands, and b) the support member preferably a cable length of less than or equal to a 7th , 5 times the support element diameter, particularly preferably less than or equal to 6.8 times the support element diameter.

Cable drive according to one of claims 1 to 7, characterized in that a) the tension member comprises a jacket with a constant thickness of 0.8 to 1.2 mm and the tension member comprises exactly one support element, wherein b 1) the support member a stranded rope with a wire core core as insert and outer strands is and b2) it is the support member is a Kreuzschlagseil and b3) parallel to the supporting element, the wire rope core is stranded with the outer strands.

9. Lifting drive, comprising a) a cable drive according to one of claims 1 to 8 and b) a drive (5) which acts on the drum (1) and / or a traction sheave and can thus effect a movement of the traction member (2), c) and preferably a load bearing (4), which control by movement of the tension member (2) in their movement, in particular drive, leaves.

10. Lifting drive according to claim 9, characterized in that a) the load bearing (4) as a gripper (4c) or platform (4a) is designed and b) that the load bearing (4) at least among other things at one end of the tension member (2) or is attached to a loose pulley (3a).

1 hoist, comprising a) a lifting drive according to one of claims 9 to 1 0 and b) a holder (7), which at least partially absorbs forces acting on at least a part of the lifting drive.

1 2. Hoisting machine according to claim 1 1, further comprising a) a carriage (8) which can be moved relative to the holder (7) and thus performs a carriage movement a 1) wherein the carriage movement can control a lifting drive movement, a 1 a) the lifting drive movement is a movement of at least part of the lifting drive relative to the holder (7).

13. A hoisting machine assembly comprising a) a hoisting machine according to any one of claims 1 1 to 1 2 and b) a reference surface (10) which receives the forces acting on the hoisting machine, preferably in the form of a floor or ceiling and c) a Displacement device, which allows a movement of at least a part of the holder (7) relative to the reference surface (1 0) and in particular by the rolling of wheels (9a).

14. A method for producing a cable drive according to one of claims 1 to 8, characterized in that a) a drum (1) is provided, b) a tension member (2) comprising a support element (2 1) and a jacket (22 ), which is the bearing surface of the tension member (2) is provided, and c) the tension member (2) is applied to the drum (1) so that it can run on the drum (1). 15. A method for producing a lifting drive comprising a) the method for producing a cable drive according to claim 14 and b) coupling a drive (5) to the drum (1) and / or a traction sheave, so that the drive (5) movement the drum (1) and / or traction sheave, preferably a rotation, cause and the drum (1) and / or drive disc so can cause a movement of the tension member (2), c) and preferably mounting a load bearing (4) , which can be controlled by a movement of the tension member (2) in their movement and in particular can drive.

16. A method of manufacturing a hoist comprising a) the method for producing a lifting drive according to claim 1 5 and b) providing a holder (7), c) combining the lifting drive and the holder (7) such that the holding ^¬ tion (7) which can absorb forces acting on at least part of the lifting drive.