ROPE DRIVE WITH SHEATHED TENSION ELEMENT

Description

Technical area

[0001] The invention relates to a rope drive, in particular for cranes and / or series hoists. The rope drive comprises a drum and a traction element that runs on the drum and comprises at least one support element. The invention further relates to a lifting drive comprising a rope drive and a drive that acts on the drum and can thus cause a movement of the traction element. The invention further relates to a lifting machine comprising a lifting drive and a mounting. The mounting absorbs at least some of the forces acting on at least part of the lifting drive. The invention further relates to manufacturing methods of a rope drive, a lifting drive, and a lifting machine. State of the art

[0002] DIN 15 020, Sheet 1, from February 1974, describes the principles for standard-compliant rope drives for cranes and series-produced hoists. Rope drives with traction sheave drives are 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, 2160, and 2450 N / mm². According to Sheet 2 of DIN 15 020 from April 1974, wire ropes coated or sheathed with plastic are not permitted. For monitoring purposes, the number of wire breaks should be counted, which is not possible with coated or sheathed wire ropes. To protect against mechanical damage, severe external wear, or corrosion, the use of thick outer wires is recommended. The use of lubricants reduces friction between the grooves of the rope pulleys or drums. The omission of lubrication results in a shorter service life of the rope.

[0003] JP 2008 308 265 A describes a rope drive according to the preamble of claim 1. This document describes the use of a coated wire rope loop as a traction element in a storage and retrieval machine for clean rooms. The goal of JP 2008 308 265 A is to minimize the abrasion of the rope and the deflection pulleys in order to minimize contamination of the clean room atmosphere. The wire rope loop is driven by a traction sheave drive.

[0004] JP 09-021084 describes a covered round rope and a covered belt for use in a weaving machine, for transmitting drive power in various machines, and for lifting goods. JP 09-021084 does not disclose how the rope drives are implemented in these applications, or whether traction sheave drives or drums are used. Rope loops are generally used to transmit drive power. Rope loops and traction sheave drives are also often used in freight elevators for lifting goods.

[0005] Hoists with rope drums are known from DE 37 41 192 A1 (MAN), FR 2 119 592 A5 (Gen Electric) and JP 2013 14 2202 A (Endo Kogyo).

[0006] Another coated rope, driven by a traction sheave, is used by the elevator disclosed in US 9 315 363 B2 (Kone).

[0007] As described in the DIN 15 020 standard, the service life of a rope without lubrication between the drum, rope pulleys and rope is significantly reduced. This reduces the economic efficiency of such a rope drive. Systems with closed rope loops driven by traction sheaves are quite complex to maintain, as the rope must be cut to exactly the right length on site and then closed into a rope loop. Drives without a closed rope loop with traction sheave drive usually use a counterweight to, on the one hand, always apply sufficient load to the traction sheave and thus maintain the necessary friction, and on the other hand to keep the force required low. However, counterweights can only be used advantageously if the load is essentially always the same. Description of the invention

[0008] The object of the invention is to create a rope drive belonging to the aforementioned technical field, which is characterized by low installation costs. In contrast to passenger elevators and other systems without drums, rope drives according to the invention are particularly suitable for intensive use with high but fluctuating loads.

[0009] The solution to the problem is defined by the features of claim 1: According to the invention, a rope drive, in particular a rope drive for cranes or serial hoists, comprises a drum and a traction element. The traction element runs on the drum and comprises at least one support element. The support element is at least partially surrounded by a casing comprising a polymer. At least part of the casing represents the support surface of the traction element. Preferably, at least one support element is completely surrounded by a casing along its length.

[0010] 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 rope drive that come into contact with the tension member during operation. Furthermore, the sheath can protect the support element from environmental influences such as moisture. The materials and structure of the support element can be optimized to the requirements of the work to be performed, such as the number of bending cycles within a period of time and / or the loads to be moved. The materials and structure of the sheath can be optimized in the rope drive according to the invention to ensure optimal interaction between the drum and tension member, as well as between the tension member and other components.This optimization extends the service life of the tension member and / or drum and / or other components. Surprisingly, it has been found that the use of a coated tension member in rope drives extends the service life of the tension member up to 10 times compared to a non-coated tension member of a comparable design.

[0011] The casing and the combination of several support elements in a single tension member enable small bending radii for the tension member, thus allowing the use of smaller components such as pulleys, drums, and drives. This also reduces the system's costs and saves space.

[0012] It was also discovered that the necessary maintenance work can be carried out with sufficient reliability even on sheathed tension members: Surprisingly, it was discovered that the number of bending cycles experienced by a sheathed tension member in a rope drive is a reliable indicator of the tension member's wear. Therefore, by counting the bending cycles, it is possible to determine when the tension member needs to be discarded. A visual inspection is now only necessary to detect mechanical damage to the sheath in a timely manner. A visual inspection of the supporting elements is no longer necessary. Definition:

[0013] A rope drive as defined in the application comprises a drum on which the traction element is wound and unwound during operation. Winding and unwinding can occur, in particular, through active rotation of the drum (hereinafter "drum drive") and / or through the action of traction sheaves on the traction element (hereinafter "traction sheave drive"). The name of the drive should preferably indicate which drive primarily applies the power to move a payload attached to the traction element. If traction sheaves are used for the controlled movement of the traction element, the drum is preferably slightly pre-tensioned so that when the tension on the traction element is released, it rotates in such a way that the traction element is wound onto it. In one embodiment, such pre-tensioning is generated by a spring. In one embodiment of a rope drive with a traction sheave drive, a drive, for example a motor, generates the drum movement for winding up the traction element when the tension is released.

[0014] A traction element within the meaning of the application comprises a supporting element and a casing. In the terms "cable pulley," "cable traction force," "cable drive," and "cable fastening," the word component "cable" should preferably be synonymous with "traction element."

[0015] A supporting element preferably consists of twisted or stranded elements. Such a preferred supporting element is not itself stranded with other elements. A stranded or twisted element, which, when stranded with other elements, forms a supporting element, is referred to below as a stranded wire. A stranded wire can, for example, be stranded together with other strands to form a supporting element. A stranded wire can also be stranded with individual wires or individual fibers or strands of metal or fibers to thus form a supporting element. A stranded wire can be made from metal wires or fibers (for example, from aramid, polyamide, carbon, or polyethylene) or from a mixture of materials.

[0016] A load-bearing element can also consist of individual links that transmit the tensile force to each other when loaded, such as a chain. A load-bearing element can also consist of a strand or bundle of individual wires or a wire mesh. A load-bearing element can also consist of a strand or bundle of fibers or a fiber mesh.

[0017] The supporting elements of a tension member are preferably those components of the tension member that have a significantly higher tensile strength than the sheath material. A significantly higher tensile strength is a tensile strength that is preferably greater than twice the lower tensile strength, particularly preferably greater than five times the lower tensile strength. In this case, the sheath material, in particular, has the lower tensile strength.

[0018] The sheath material is in particular the material that forms the support surface of the tension member, preferably the material that makes up the largest part of the volume between the support element and the support surface of the tension member. The sheath material is in particular a different material than that of the support element. In one embodiment, the sheath 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 sheath can also contain reinforcing additives such as fibers, fabrics or particles. The sheath can be coated.

[0019] The support surface of the tension member is preferably that part of the surface of the tension member which, at any given time during operation, comes into contact with the drum or, if the rope drive comprises pulleys, at least one of the pulleys. Depending on the design of the rope drive, this may, for example, be a single line (in the case of a perfect round rope on flat drums and pulleys and a tension member guide with only one bending direction) or wide strips on different sides of the tension member (in the case of a tension member which runs at least partially on or over suitably shaped drums and pulleys and which changes its bending direction). Depending on the shape of the drums and pulleys as well as the tension member, the support surface may also comprise more than two strips.

[0020] The casing forms the support surface of the tension member and is preferably in contact with the support element at the same time. A casing can preferably also comprise a plurality of materials. In particular, within the meaning of the invention, it is still a casing if it is coated on the outside or inside with a layer whose thickness is insignificant compared to the thickness of the casing. In particular, a layer thickness is insignificant compared to the thickness of the casing if it is less than approximately 1 / 10 of the casing thickness at the coated location; particularly preferably, a layer thickness is insignificant if it is less than approximately 1 / 100 of the casing thickness at the coated location. The layer thickness and the casing thickness should preferably be measured along the surface normal of the coated location.

[0021] A tension member can comprise more than one support element. The casing can enclose the support element on only one side. Preferably, the casing completely encloses the support element along its length. The casing can penetrate into the support element.

[0022] The dimensions of a tension member are preferably determined as follows: Consider the cross-section of the tension member, perpendicular to the longitudinal axis. The first diameter of the tension member is the smallest distance between two non-identical parallel lines that touch but do not intersect the outside of the cross-section. The second diameter of the tension member is the largest distance between two non-identical parallel lines that touch but do not intersect the outside of the cross-section. This procedure is described in Figures 8a and 8b illustrated.

[0023] The tension member should preferably be referred to as a "round rope" if the first diameter is greater than 9 / 10, preferably greater than 19 / 20, particularly preferably greater than 99 / 100 of the second diameter.

[0024] The traction element shall be referred to as a "belt" if the first diameter is less than 4 / 5; preferably less than 3 / 4, particularly preferably less than half of the second diameter.

[0025] The dimensions of the support element should be determined analogously to the dimensions of the tension member, whereby the position of individual components of the support element relative to each other is the same as their position within the tension member. If a tension member comprises several support elements, the dimensions of each support element should be determined individually and independently of the other support elements. The parallels whose distance defines the first and second diameters should preferably touch the outer surface of any component of the support element during this measurement, but should not intersect any component of the support element. However, the parallels may intersect the shell.

[0026] 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, further preferably between 10 and 30 mm, and most preferably between 12 and 24 mm. Support elements between 1 and 20 mm are preferably used, particularly in belts, and support elements between 8 and 40 mm are particularly preferred in round ropes. 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 enable particularly cost-effective rope drives.

[0027] Unless otherwise specified, the sheath thickness is preferably measured as follows: In a cross-section through the tension member, a straight line is drawn from all points of the support surface to the geometric center of gravity of each supporting element. All straight lines that run at least partially outside the cross-sectional area of ​​the tension member and all straight lines that at least partially cross two or more supporting 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 supporting element is determined. The shortest of these distances is preferably referred to as the sheath thickness. This procedure is carried out using the Figures 9a, b and c illustrated.

[0028] In one embodiment, the sheath thickness is in the range of 0.05 to 20 mm, in particular 0.1 to 10 mm, and particularly preferably between 0.8 and 1.2 mm. Surprisingly, it has been found that sheath thicknesses in this range are easy to manufacture and that such sheaths deform only slightly during use on tension elements in cable drives, thus contributing to a long service life.

[0029] A pulley 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 member is deflected by the pulley.

[0030] A compensating pulley is used to balance the tension in the opposite section of a tension member. It differs from a deflection pulley in that it hardly moves during operation. During operation, a tension member preferably moves over a compensating pulley a maximum distance equal to three times the diameter of the tension member.

[0031] A traction sheave is an actively and / or controlled driven and / or braked roller over which the traction element runs in such a way that the drive or the brakes of the traction sheave influence the movement of the traction element due to friction between the traction sheave and the traction element. In this context, actively driven or braked means that a motor or other drive that acts directly on the traction sheave exerts a torque on the traction sheave in one direction or the other. In this context, controlled driven or braked means that the movement and load of the traction sheave and / or other parameters of the rope drive are observed and the traction sheave is driven or braked depending on these observations. An active drive orIn this sense, an active brake without control would, for example, simply use a motor to exert a constant torque in one direction or the other on the traction sheave. An example of a controlled but non-active drive or brake is a traction sheave biased in one direction by a spring, whose rotation is controlled by the controlled application of a brake. A traction sheave driven by a motor depending on a measured value, such as a measured cable speed, is an example of an actively and controlled driven traction sheave. If such a motor rotates in the opposite direction or at a reduced speed, it can be considered an active and controlled brake.

[0032] The drum is a device onto which the traction element is wound. The winding and unwinding of the traction element onto and from the drum is used in a rope drive to specifically control the length of the traction element. In particular, the drum is therefore a rope drum suitable for winding and unwinding the traction element. Drums according to the invention can therefore be used in particular for round ropes if the traction element is a round rope, for belts if the traction element is a belt, or for other types of traction elements if the traction element is of a different design.

[0033] The rope attachment to the drum should preferably be designed in such a way that, taking into account the friction of the turns remaining on the drum, 2.5 times the rope tensile force can be absorbed. The coefficient of friction between the covered tension elements and the base is preferably determined using a conventional measuring or calculation method: For example, the force F can be measured that is necessary to set a rope simply resting on the drum and hanging down the same length on both sides in motion by pulling straight downwards against a motionless drum with a radius r. If the rope has a mass per unit length of ρ, then µ = F / (2rpg) can be estimated, with g as the gravitational acceleration. If the length difference Δl between the rope end on one side of the drum and the other at which the rope starts to slip is known, then µ = Δl / (2r) can be estimated.As a result, a coated rope is generally expected to have a higher coefficient of friction than a steel rope. This can be up to 1.5, for example; however, the value can vary considerably in all directions depending on the design, particularly the material and structure of the sheath.

[0034] The rope attachment to the drum, i.e. the attachment of the traction element to the drum, is preferably achieved at least partially by a wedge lock, a clamping collar, or pressed-on, welded, or cast-on end pieces. Part or all of the rope attachment can be achieved by friction of the traction element on the drum: This ensures that a minimum number of turns of the traction element rests on the drum at all times during operation. This minimum number can be, for example, 2.5 turns. Various attachment methods, such as the use of friction and a clamping collar, can be used simultaneously. End pieces, collars, wedge locks, and other fastening elements can be located outside the support surface of the drum, for example, on its outer side. Single-shift operation.

[0035] In one embodiment, the traction element and drum of a rope drive are dimensioned in such a way, i.e., their dimensions are coordinated so that the traction element rests on the drum in a maximum of one layer at any time during operation of the rope drive. Preferably, this is a rope drive with a drum drive.

[0036] In this case, the traction element can 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 less space on the drum in a single layer and can therefore be longer than a comparable belt for the same drum length.

[0037] This dimensioning can be achieved by coordinating various parameters: The length of the traction element, the diameter and width of the drum, and / or the guide of the traction element can be appropriately matched. A control system for the rope drive can also be used to ensure that the traction element rests on the drum in a maximum of one layer during operation. Delivery, storage, and installation of the rope drive or individual parts of the rope drive are not considered "operation," so during these times the traction element may rest on the drum in a single layer, multiple layers, or not at all.

[0038] The advantage of supporting the tension member in a single layer is that it provides a technically simple way to prevent the tension member's sheath from being crushed between sections of the supporting element. The sheath material is thus subjected to minimal deformation, which reduces the requirements for the material selection and thus facilitates the selection of a sheath material. Fewer forces perpendicular to its longitudinal extension also act on the supporting element.

[0039] In a preferred embodiment, the surface of the drum on which the tension member rests is shaped in such a way that the tension member is supported in its outer shape. This ensures that the force exerted by the tension member on its support surface on the drum acts over a larger area and also minimizes shear forces. This further reduces the load on the casing material compared to embodiments with a single-layer support on a differently shaped, particularly non-adapted, support surface. Multi-shift operation.

[0040] In one embodiment, the traction element and drum of a rope drive are dimensioned in such a way, i.e., their dimensions are coordinated so that the traction element rests on the drum in more than one layer during the times of rope drive operation when most of the length of the traction element is wound up. Preferably, this is a rope drive with a traction sheave drive.

[0041] A multi-layered support for the tension element can be combined with other technical aids to relieve the tension element and, in particular, its casing. For example, the rope drive can have a deflection pulley, which acts as a "quasi-traction pulley" and absorbs part of the tensile forces through friction between the tension element and the quasi-traction pulley. If a traction pulley drive is used, the traction pulley absorbs a large portion of the tensile forces. In this way, the tension element is wound onto the drum under only slight tension. Therefore, the force exerted by higher layers of the tension element on the lower layers is lower than when wound under higher tensile force. The tension element is therefore less crushed and thus relieved of stress.

[0042] It is also possible to install load-relieving materials between different layers of the tension member. Such load-relieving materials can, for example, redirect the forces that an upper tension member layer would exert on a lower tension member layer to the drum and / or increase the contact area of ​​the tension member itself, thus preventing particularly damaging high local load peaks. A load-relieving material can also act by reinforcing the lower tension member layer. Load-relieving materials can wrap around, under, or over the tension member when it is rolled up, or they can be provided by a special shape of the drum, for example, in the form of a spiral with an open side.

[0043] If the support element rests on the drum in multiple layers and there are no other technical aids, traction sheaves or relief materials, the casing material and the support element material can also be selected in such a way that the tension element is not damaged under the loads during operation and achieves a useful service life.

[0044] In all cases, a multi-layer support of the tension member allows the use of a more compact drum for a given tension member length. Rope pulley.

[0045] In one embodiment, the cable drive comprises at least one cable pulley. This cable pulley is in contact with the traction element. The cable pulley is preferably a deflection pulley or a compensating pulley.

[0046] The use of pulleys makes it possible to make the path of the pulling element and the distribution of forces more flexible.

[0047] In the simplest form, the path of the traction element in a rope drive is determined only by the drum and external forces, such as gravity: For example, the traction element hangs straight down from a drum mounted at a certain height, and how far the traction element hangs down is controlled by how much of the traction element is wound onto the drum.

[0048] The pulleys now allow the drum to be selected independently of the desired working direction and working position of the traction element, since the direction of the pulling force and the position of the traction element can be determined by a suitable positioning of one or more pulleys.

[0049] Using free and fixed pulleys, a smaller force can be applied over a longer distance, similar to the principle of a pulley system, to exert a greater force over a shorter distance. Compensating pulleys allow for a more even load distribution on pulleys, for example, when multiple pulleys running on a drum act on a pulley. Round rope.

[0050] In one embodiment, the tension member is a round rope whose supporting element is formed by a stranded rope. The stranded rope comprises one or more strands. At least some of the strands of the stranded rope comprise steel wires. These steel wires preferably have a tensile strength of >2160 N / mm2<, in particular of >2300 N / mm2<, in particular of >2500 N / mm2<, especially of >2600 N / mm2<, very especially of >2800 N / mm2<.

[0051] Round ropes are comparatively easy to manufacture.

[0052] In order to be able to work with small bending radii, i.e., small pulleys and drums, even with high loads, the use of tension elements in the form of belts is also possible. These are referred to below as "belts." In belts, the cross-section perpendicular to the longitudinal dimension, the extension in a first direction is significantly greater than the extension in a second direction perpendicular to the first. In particular, the extension in a first direction can be greater than or equal to twice the extension in the second direction. Belts can comprise more than one support element. The support elements then run essentially parallel to one another and are each at least partially enclosed by a common casing.

[0053] Tension elements can also be designed differently: A tension element with a single support element and a casing that is flattened on one side, two parallel flat surfaces or a casing that is polygonal in cross-section can, for example, be advantageous in order to transfer forces more evenly to the support surface of the drum or to enable a multi-layer support element development on the drum.

[0054] A stranded rope comprises one or more stranded strands. A stranded rope may also contain individual wires or other fibers that are stranded with the strands.

[0055] Alternatively, in a round rope or a differently shaped tension member, several strands can be arranged parallel to each other, or a larger number of individual wires or fibers can run parallel to each other. A load-bearing element can also consist of braided or woven wires or fibers.

[0056] Steel wires have the advantage of high tensile strength. By selecting the right material and applying appropriate 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 rope pulleys, is eliminated by the sheathing of the support element. In a rope drive according to the invention, tension elements with particularly high-tensile support elements can therefore be used. Such tension elements can be thinner than tension elements with lower tensile strength, while maintaining the same breaking load.

[0057] The tensile strength of the wires here refers to the tensile strength determined after wire production, which is specified based on consistent manufacturing conditions and, if applicable, sample measurements for a single batch of wire. The wires are, in particular, cold-drawn. This manufacturing process and the increase in tensile strength are well known, so that a tensile strength value for the wires can be determined from the manufacturing process alone. The specified values ​​should be understood as values ​​with the usual tolerances of -0 and +350 N / mm².

[0058] According to the invention, at least one of the support elements is a stranded rope with six or more outer strands. In a particular embodiment, at least one of the support elements is a stranded rope with nine outer strands.

[0059] The use of many strands, particularly six or more, for example nine, has the advantage that the resulting stranded rope exhibits high bending fatigue performance, which means a longer service life. Furthermore, the use of many outer strands allows for the use of comparatively thin wires. Since high nominal wire strengths can primarily be achieved with thin wires, a load-bearing element with many outer strands made of thin wires can comprise wires with nominal strengths of, for example, > 2160 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.

[0060] An outer strand count of between six and nine results in stranded ropes with a comparatively high bending fatigue performance that are comparatively inexpensive to manufacture.

[0061] InIn one embodiment, at least one of the supporting elements is a "wire core" or WC rope, i.e. a single-layer rope with a steel core, or an "independent wire rope core" or IWRC rope, i.e. a single-layer rope with a separately stranded wire rope core, or a "parallel wire rope core" or PWRC rope, i.e. a rope in which a wire rope core and the outer strands are stranded in parallel, in particular in one work step, or a "fibre core" or FC rope, i.e. a rope, in particular a stranded rope, with a fibre core as the central element, i.e. as the core.

[0062] For the core and strands, especially the steel core, the Warrington, Seale, or Filler constructions are preferred, or a combination of these. However, less well-known and other constructions are also possible. The choice of core construction and the various outer strands and other strands of a stranded rope are independent of each other.

[0063] According to the invention, the cable lay length is less than or equal to 7.5 times the diameter of the supporting element, in particular less than or equal to 6.8 times the diameter of the supporting element. A short cable lay length increases the flexibility of the supporting element and thus also of the tension element in which it is used. A short cable lay length therefore enables even smaller bending radii.

[0064] In one embodiment, the tension member comprises a sheath with a constant thickness of 0.8 to 1.2 mm and precisely one supporting element. The supporting element is a stranded rope with a wire rope core as a core and outer strands. Furthermore, the supporting element is a regular lay rope. The wire rope core of the supporting element is stranded parallel to the outer strands.

[0065] The wire rope core comprises a core strand and intermediate strands. The core strand can be surrounded, for example, by nine intermediate strands. This core, i.e. the wire rope core, is in turn surrounded by outer strands. There can be, for example, nine outer strands. The core strand, the intermediate strands, and the outer strands are made of steel wires. The diameters and number of steel wires can vary in the different strands. The steel wires preferably have a nominal wire strength of more than 2600 N / mm².

[0066] The load-bearing element is a regular lay rope: While the outer strands are right-handed (Z) relative to the rope, the outer wires of the outer strands are left-handed (s) relative to the outer strands. The entire rope, i.e., the wire rope core and the outer strands, are stranded in a single operation, resulting in a parallel-stranded rope. Conversely, the outer strands could also be left-handed relative to the rope and the wires of the outer strands right-handed relative to the outer strands.

[0067] The wire rope core is preferably a Warrington strand. A Seale or Filler construction, for example, or a combination of the different constructions, could also be used.

[0068] In one embodiment, the intermediate strands are single-layer strands.

[0069] In one embodiment, the outer strands are Seale-I strands <onstruktion. Es könnte beispielsweise auch eine Warrington- oder Filler-Konstruktion genutzt werden. In einer Ausführungsform werden die Aussenlitzen mit der oben beschriebenen oder einer ähnlichen Stahlseil-Einlage parallel verseilt.

[0070] In one embodiment, the outer strands, intermediate strands and the core strand each consist of wires that are twisted in a helical manner.

[0071] Tension elements designed in this way have proven themselves in rope drives according to the invention. Lifting drive.

[0072] A lifting drive comprises a rope drive according to the invention and a drive which acts on the drum and / or on a traction sheave and can thus cause a movement of the traction element.

[0073] In particular, it is a rope drive with a drum drive or a rope drive with a 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.

[0074] In particular, it is a rope drive with traction sheave drive if the drive acts on the traction sheave.

[0075] In a preferred embodiment, a lifting drive further comprises a load-bearing device, the movement of which can be controlled by a movement of the traction element. In particular, the load-bearing device can be driven by the movement of the traction element.

[0076] The drive acting on the drum and / or traction sheave can be a motor, a manual drive, or a drive that utilizes forces such as wind, current, tides, or other movements. Different drive types can also be used simultaneously and / or complement and / or replace one another on a drum and / or traction sheave.

[0077] The traction element is wound onto or unwound from the drum by the movement of the drum, thus setting it in motion. The tensile force required to move loads is generated by the movement of the drum and / or the traction sheave, generated by at least one drive.

[0078] The movement of the traction element is preferably used to move changing loads. A load suspension device can be used to move different loads using a traction element. A load suspension device is a device with which loads can be releasably connected or a device that can hold loads. Load suspension devices can be hooks, eyelets, baskets, platforms, slings, buckets, and the like. A lifting drive with such a load suspension device can be used, for example, in a crane, a storage and retrieval machine, a recovery device, or a conveyor system.

[0079] However, if the load is not to be changed frequently, the traction element of the lifting drive can also be connected directly to the load. Such applications include a lock gate, a theater curtain, or a drawbridge. Gripper and platform.

[0080] InIn one embodiment of a lifting drive, the load receiving device is designed as a gripper or platform and is attached at least, among other things, to one end of the traction element or to a loose deflection pulley.

[0081] For the application of the lifting drive in automated storage and retrieval machines, load handling devices in the form of grippers and platforms are suitable, as these load handling devices allow for comparatively easy mechanical gripping of the goods to be transported. For example, a platform can be moved under a load, or the load can be pushed onto a platform using a mechanically generated impact or pressure movement. A gripper can grip a load automatically. Depending on the design of the gripper, however, the load may have to consist of standardized items or standardized transport containers to ensure smooth operation. Grippers that can safely grip variable and a priori unknown loads can also be used. Grippers for standardized items or transport containers have a simpler design and are therefore less expensive.

[0082] A load-bearing device that is attached, among other things, to at least one end of the tension member has the advantage that a movement of the tension member affects the load-bearing device to exactly the same extent. The load-bearing device is thus moved directly. Rapid movement of the load-bearing device is possible.

[0083] By attaching a load to a loose pulley, the change in position of the load is only a fraction of the movement of the traction element caused by the drive. Following the principle of a pulley system, the tensile force exerted by the pulley or its drive decreases with the increasing number of pulleys. Therefore, the load on the pulley and drive is reduced.

[0084] In addition to the pulley or the end of the traction element, the load suspension device can also be additionally attached and, for example, move on rails or be held on a special track with additional ropes, traction elements and / or guide elements.

[0085] A load-bearing device can also be attached to a point on the traction element other than just the end. For example, several load-bearing devices, such as platforms, can be attached to a traction element at equal intervals. A load-bearing device, such as a gripper, can also be mounted at a certain distance from the end of the traction element. The part of the traction element between the end and the load-bearing device can be used, for example, to stabilize the position of the load-bearing device in a plane perpendicular to the direction of pull or to guide the load-bearing device. Lifting machine.

[0086] A lifting machine comprises a lifting drive and a support. The support absorbs at least part of the forces acting on at least part of the lifting drive.

[0087] Different forces can act on the lifting drive: For example, these are the forces required to hold the load-bearing device and the load on it. Forces can also act on any rope pulleys that may be present, which can absorb the support. Furthermore, depending on the positioning of the drive and / or drum, it may also be necessary to support these or other components with support brackets.

[0088] A bracket preferably comprises a mounting device for the fixed pulleys and / or the drum and / or their drive. The bracket can consist of several pieces and, for example, consist of hooks, brackets, rods, or other designed holding devices that can be attached to the walls, ceiling, or floor of a building or room, or to a supporting structure, such as beams. The attachment can be achieved using conventional means, such as screwing, nailing, riveting, welding, lashing, gluing, encasing in concrete, bricking in and / or casting in, and the like, as well as by combinations of different fastening means, for example screwing followed by casting in. Each piece of the bracket can be attached to a different location (wall, ceiling, floor, beam, etc.) using different means.

[0089] A support preferably also comprises a frame to which one or more mounting devices for deflection pulleys and / or the drum and / or the drive and / or optionally the traction sheave are attached. Such a frame can, for example, consist of a single support, form a portal structure, or comprise a boom that is held at a certain height or position by other elements. A frame within the meaning of the invention should preferably be self-supporting, but can, for example, be attached to a building, a ceiling, rails, and / or similar external structures, or at least partially touch them, for example to improve stability, to prevent tipping, and / or for positioning.

[0090] Rope pulleys that are not attached with mounting devices are, for example, loose rope pulleys. Fixed rope pulleys can also be designed so massive that they rest on the ground under their own weight and do not require any holding devices. The drum and drive can also be so heavy that their own weight fixes them in the desired position. Furthermore, the rope drive can be designed in such a way that the forces required to move the load with the load suspension hold the drum, drive, traction sheave and / or rope pulleys in the desired positions: If, for example, a first deflection pulley is located below the drum and / or traction sheave, the tensile force of the pulling element can pull the drum or traction sheave down and thus press it against the ground on which the drum and / or traction sheave stands.

[0091] The mounting devices can be attached to the walls, ceiling, or floor of a building or room, or to a support structure or scaffolding, in such a way that they can move relative to the mounting location, or they can be fixed relative to the mounting location. A movable mounting device can, for example, run on rails or be held at the mounting location by another, adjustable rope drive. Such a movable mounting allows for more flexible use of the rope drive. A "movable mounting device" comprises at least two parts: One part is fixed to the mounting location (for example, rails or rollers of a rope drive), while a second part can move in a controlled manner relative to the first part. The rope pulley, drive, traction sheave, or drum can then be attached to this second part.

[0092] A fixed installation of a mounting device or a bracket, for example by screwing it to a support or scaffolding, is technically simpler, cheaper and in many cases more stable. Sleds.

[0093] In In one embodiment, a lifting machine comprises a carriage that can be moved relative to the support. This movement is referred to as the carriage movement. The carriage movement can control a lifting drive movement. The lifting drive movement is a movement of at least a portion of the lifting drive relative to the support.

[0094] A carriage is one embodiment of a movable assembly device. A carriage movement preferably occurs when the carriage can move relative to at least part of the support. The carriage can, in particular, move relative to the scaffold. One or more cable pulleys can be attached to a carriage, so that the load-bearing device of the lifting machine can be moved by the movement of the carriage. This preferably involves a movement in a plane perpendicular to the tensile force exerted on the load-bearing device by the tensile element.

[0095] In particular, the drum and / or the drive pulley can be located on the carriage. InIn this case, a rope drive can simply comprise a traction element that can be wound up and down from a drum mounted on a carriage. The traction element can exert a desired tensile force on a load by controlling its movement through a controlled movement of the drum and / or a traction sheave: By winding up and down the traction element, a load can be moved in one direction. The carriage movement causes a movement of the traction element and thus, if necessary, a movement of the load in a second direction. This enables bidirectional transport.

[0096] A carriage according to the invention preferably moves on a carriage guide, such as rails, guide cables, guide elements, or markers. The carriage can slide and / or slide and / or roll along this carriage guide. The carriage can have its own carriage drive or be accelerated, moved, and decelerated by an external device using tension, pressure, and / or forces such as magnetism and / or its own weight. Limitations and / or changes in the structure of the carriage guide can also control or limit the carriage movement.

[0097] A carriage can be mounted on a second carriage or moved by a second carriage in some other way. If the direction of movement of one carriage is different from that of the second carriage, the lifting machine can allow transport in three directions. Hoisting machine structure.

[0098] A lifting machine structure comprises a lifting machine and a reference surface that absorbs the forces acting on the lifting machine, as well as a displacement device that enables movement of at least a portion of the support relative to the reference surface, in particular by rolling wheels. The reference surface is preferably a floor or a ceiling.

[0099] A hoisting machine structure is a lifting machine that can move relative to a reference surface using a sliding mechanism. An example is a crane mounted on a trailer. In this case, the reference surface is the road on which the trailer can move. The frame, rope drive, and drive of the crane's rope drive form the hoisting machine in this example. The frame represents the support. The trailer with its wheels forms the sliding mechanism in this example.

[0100] Another example is a crane mounted on ceiling rails: Since the ceiling rails support the hoist, they define the reference surface. The shifting device and scaffolding can be a crossbeam that can be moved along the rails. This crossbeam can, but does not have to, support a carriage. The drum and / or traction sheave and their respective drives, as well as individual rope pulleys, are preferably attached to the ceiling rails or to the crossbeam, or even to the carriage that runs on the crossbeam.

[0101] The movement of the displacement device can, but does not have to, occur along displacement guides. Displacement guides can be implemented, for example, by rails, guide cables, guide elements, or markings. The displacement device can slide, slide, or roll over or at a defined distance from the displacement guides. The displacement device can have its own displacement drive or be accelerated, moved, and decelerated by an external device using tension, compression, and / or forces such as magnetism and / or its own weight. Limitations and / or changes in the structure of the displacement guide can also control or limit the movement of the displacement device.

[0102] A movement of the displacement device without displacement guides is given, for example, if the displacement device is a carriage that can be controlled in any direction, for example by a person.

[0103] It is also possible for a displacement device to be used in one operating mode without displacement guides and in a second operating mode with displacement guides. For example, a freely controllable carriage can be equipped with sensors that can be used to automatically guide the carriage along certain markings. Manufacturing of the rope drive.

[0104] A method for manufacturing a rope drive comprises the following steps: a) a drum is provided, b) a traction element comprising a support element and a casing which represents the support surface of the traction element is provided, c) the traction element is applied to the drum in such a way that it can run on the drum.

[0105] Step c) usually consists of attaching one end of the tension member to a point on the drum so that the tension member winds up properly around the drum when the drum rotates. The contact between the drum and the tension member should be so firm and stable that the movement of the drum can be transmitted to the tension member in all operating conditions. The contact or coupling between the drum and the tension member can be established using known tension member coupling methods. One possibility is, for example, the use of a wedge lock, a clamping collar or pressed-on, welded-on or cast-on end pieces. Furthermore, the friction of the tension member on the drum can be used to ensure that a minimum number of windings of the tension member are in contact with the drum at all times during operation.In particular, it is possible for one end of the tension member to be led out of the drum at the side and secured there with a wedge lock. Alternatively, the end of the tension member can be secured with a clamping collar, and the control of the rope drive ensures that at least 2.5 windings of the tension member are always resting on the drum.

[0106] If a traction sheave drive is used, meaning the process for manufacturing a rope drive also includes the provision of a traction sheave, the traction element can also be controlled so that fewer than 2.5 windings are applied, and in particular, no winding of the traction element is applied at any given time. However, the traction element should always remain in contact with the drum. However, fastening with a wedge lock, clamping strap, pressed-on, welded-on, or cast-on end pieces may be less stable than in the case of a rope drive with a drum drive. Manufacturing of the lifting drive.

[0107] The process for manufacturing a lifting drive includes the following steps: a) The method for producing a rope drive, b) coupling a drive to the drum and / or a traction sheave so that the drive can cause a movement of the drum and / or the traction sheave, preferably a rotation, and the drum and / or traction sheave can thus cause a movement of the traction element, c) and preferably mounting a load suspension which can be controlled in its movement and in particular driven by a movement of the traction element.

[0108] Couplings between drives and drums, traction sheaves, and / or axles of various types are known to those skilled in the art. The drive axle of a motor can, for example, be connected to the drum or traction sheave axle with a positive connection, either directly or via a gear, or alternatively directly or via a gear. A drive could also act on one or more points on the drum or traction sheave that are located as far away as possible from the axis of rotation. For example, a tappet can strike such points, and a locking mechanism can prevent the drum or traction sheave from accidentally rotating backwards. Coupling via a drive belt, i.e., using a frictional connection, is also possible.The choice of coupling can be determined, among other things, by the drive system used: Water and wind movements might make a "ram / ratchet coupling" advantageous, as naturally irregular movements can be used in these cases. A coupling with a drive belt, on the other hand, is "softer": sudden fluctuations in the power generated by the drive are only transmitted to the drum or drive sheave up to a certain amount, as the drive belt slips at higher accelerations. This further transmission can reduce the mechanical stress on the various components of the lifting drive.

[0109] The tension member can control the movement of the load-bearing element through controlled driving, controlled braking, or directional control, among other things. In all cases, the tension member preferably generates a controlled pull in the direction opposite to the other forces acting on the load or load-bearing element. Manufacturing lifting machine.

[0110] The method for manufacturing a lifting 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 can absorb the forces acting on at least part of the lifting drive.

[0111] In addition to the bracket, part of the forces can also be absorbed by the base surfaces of various components of the lifting drive, such as the drum, the traction sheave or the drive.

[0112] Further advantageous embodiments and combinations of features of the invention emerge from the following detailed description and the entirety of the patent claims. Short description of the drawings

[0113] The drawings used to explain the embodiment show: Fig. 1aA rope drive with a drum and a traction element Fig. 1b and cA first and a second embodiment of the support surface of a drum Fig. 2a, b and cThree embodiments of the traction element as a round rope Fig. 2d, e, f, gThree embodiments of the traction element as a belt Fig. 3An embodiment of a traction element as a round rope with a stranded rope as the supporting element Fig. 4a, bTwo embodiments of a lifting drive Fig. 5A lifting machine Fig. 6a, bTwo embodiments of lifting machines with differently controlled carriages Fig. 7a and bTwo embodiments of lifting machine structures Fig. 7cA lifting machine structure used as a storage and retrieval device Fig. 8a, bExplanation of the dimensions of a traction element Fig. 9a-cExplanation of the determination of the sheath thickness

[0114] In principle, identical parts in the figures are provided with identical reference symbols. Ways to implement the invention

[0115] Figure 1ashows a rope drive 100 comprising a drum 1 and a traction element 2. The traction element 2 can be wound onto and unwound from the drum 1 by rotation. The traction element 2 rests on the support surface 11 of the drum 1. In multi-layer operation, the traction element 2 rests only partially on the support surface 11 of the drum 1 and partially on itself.

[0116] The Figures 1b and 1c show two different drums 1. The drum in Figure 1b has a support surface 11 that is adapted to the outer shape of the tension member 2. This allows for a large contact area between the tension member 2 and the support surface 11. This can protect the tension member 2 from deformation and guide the tension member 2 into the desired winding during the winding process.

[0117] The drum in Figure 1c has a flat support surface 11. Such a support surface 11 can be used for tension elements 2 of different cross-sectional shapes and cross-sectional dimensions.

[0118] The Figures 1b and 1c are just two examples. Other shapes of the support surface 11 are possible. For example, the support surface 11 can be more concave or convex than the exact complementary shape of the tension member 2. This allows, for example, the pressure to be distributed specifically to areas of the tension member 2 that are not directly directed toward the axis of the drum 1. Or the support surface 11 can direct the winding process of the tension member 2 with the aid of additional devices or on its own. The winding of the tension member 2 can alternatively or additionally be carried out or supported by a tension member guide.

[0119] The Figures 2 a to g show a number of different embodiments of tension elements 2. All tension elements 2 comprise at least one support element 21 and a casing 22.

[0120] Even if the Figures 2a to gWhile the boundary between the supporting element 21 and the casing 22 appears to be clear, this is not necessarily the case: The supporting element 21 may have unevenness on its exterior or may have cavities within it into which casing material can penetrate and partially or completely fill them, or cavities and unevenness may be filled with casing material at earlier stages of production. In such a case, the boundary between the casing 22 and one of the supporting elements 21 is preferably defined by the envelope of the respective supporting element 21.

[0121] The Figures 2a and c show different embodiments of tension members 2 in the form of round ropes 2a. All tension members 2, and therefore also all round ropes 2a, comprise at least one supporting element 21 and a sheath 22. Figure 2b shows a further embodiment of a pulling element 2.

[0122] Figure 2ashows a cross-section through a round cable 2a with a single support element 21. The support element 21 also has a substantially round cross-section. The support element 21 is surrounded by a sheath 22 along its entire circumference, and the thickness of the sheath 22 is substantially uniform throughout. The thickness of the sheath 22 can, for example, be 1 / 5 or 1 / 10 of the diameter of the support element 21 in such an embodiment, or even thinner or thicker.

[0123] Figure 2b shows a cross-section through a tension member 2 with a single support element 21. The support element 21 also has a substantially round cross-section. Unlike in Figure 2aHowever, the casing 22 now surrounds the support element 21 only along part of its circumference. The thickness of the casing 22 also varies along the circumference of the support element 21. The maximum thickness of the casing 22 can be, for example, 1 / 5 or 1 / 10 of the diameter of the support element 21 in such an embodiment, or even thinner or thicker.

[0124] Figure 2c shows a cross-section through a round rope 2a with four supporting elements 21a-d. These four supporting elements 21a-d are only in contact with each other via the sheath material. If the supporting elements 21a-d were stranded together or could absorb significant tensile forces from each other via connections, one would speak of a single supporting element in the sense of the application and not of four. All supporting elements 21a-d are surrounded by a sheath 22. The outer side of the sheath 22 is in Figure 2c circular.

[0125] The Figures 2d, e, f and gshow different embodiments of tension elements 2 in the form of belts 2b. All tension elements 2, and therefore also all belts 2b, comprise at least one support element 21 and a casing 22.

[0126] Figure 2d shows a cross-section through a belt 2b with two support elements 21a, b. Both support elements 21a and b have a substantially circular cross-section and are substantially the same size. The support elements 21a and b are surrounded by a casing 22 along their entire circumference. The outer shape of the cross-section of the casing 22 is substantially rectangular. The smallest value for the combined casing thickness can be, for example, 1 / 5 or 1 / 10 of the diameter of one of the support elements 21a or b in such an embodiment, or even thinner or thicker.

[0127] Figure 2eshows a cross-section through a belt 2b with three support elements 21a-c. The support elements 21a-c have a substantially circular cross-section but partially differ in diameter. The support elements 21a and c have the same, smaller diameter and are completely surrounded by the casing 22. In contrast, the casing 22 surrounds the support element 21b only along part of its circumference. The outer shape of the cross-section of the casing 22 is essentially a rectangle.

[0128] Figure 2fshows a cross-section through a belt 2b with two support elements 21a, b. Both support elements 21a and b have a substantially round cross-section and are substantially the same size. The support elements 21a and b are surrounded by a casing 22 along their entire circumference. The casing 22 encloses the two support elements 21a and b with a uniform thickness. In addition, the casing 22 forms a web between the two support elements 21a and b. The thickness of this web is smaller than the diameter of each of the two support elements 21a and b. The smallest value for the joint casing thickness can be, for example, 1 / 5 or 1 / 10 of the diameter of one of the support elements 21a or b in such an embodiment, or even thinner or thicker.

[0129] Figure 2gshows a cross-section through a belt 2b with a support element 21. The support element 21 has a substantially rectangular cross-section and can be, for example, a braided belt or a woven fabric. The support element 21 is surrounded by a casing 22 along its entire circumference. The casing 22 encloses the support element 21 with a uniform thickness on all sides. The smallest value of the casing thickness can be, for example, 1 / 5 or 1 / 10 of the smaller diameter of one of the support elements 21, or even thinner or thicker. The outer shape of the cross-section of the casing 22 is essentially a rectangle.

[0130] Figure 3shows a tension member 2 in the form of a round rope 2a with a uniformly thick sheath 22. The sheath 22 preferably has a thickness of 0.8 to 1.2 mm. The support element 21 is designed as a stranded rope. It comprises a core 212 and outer strands 211a. The core 212 is a wire rope core comprising a core strand 211c and intermediate strands 211b. In the case shown, the core strand 211c is surrounded by nine intermediate strands 211b. This core 212 is in turn surrounded by nine outer strands 221a. The core strand 211c, the intermediate strands 211b, and the outer strands 211a consist of steel wires 213a-d. The diameters and number of steel wires differ in the various strands. The steel wires preferably have a nominal wire strength of more than 2600 N / mm 2< .The supporting element 21 is a regular lay rope: While the outer strands 211a of the round rope 2a are right-handed (Z) relative to the round rope 2a, the wires 213b of the outer strands 211a are left-handed (s) relative to the outer strands 211a. The wire rope core, which forms the core 212, is stranded parallel to the outer strands 211a. This is achieved by preferably stranding the entire rope, i.e., the wire rope core and the outer strands 211a, in a single operation.

[0131] The core strand 211c 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 arranged in the outermost layer between two steel wires with the first diameter. Inside the core strand 211c, six steel wires of the first diameter are arranged around a steel wire of the first diameter. The core strand 211c is a strand of the Warrington construction. For example, a Seale or Filler construction could also be used, or a combination of the different constructions. The core strand 211c represents the insert here.

[0132] The intermediate strands 211b each comprise seven steel wires 213a with a third diameter. Six of the steel wires with the third diameter 213a are arranged around another steel wire of the third diameter 213a. The intermediate strands 211b are single-layer strands.

[0133] The outer strands 211a each comprise a steel wire 213d with a fourth diameter. Nine steel wires 213c with a fifth diameter are arranged around this steel wire 213d with the fourth diameter. The outer layer of the outer strands 211a is formed by nine steel wires 213b with a sixth diameter. The outer strands 211a are Seale strands. Alternatively, outer strands consisting of more wires and a filler construction can be used and stranded in parallel with the steel rope core described above or a similar one.

[0134] The outer strands 211a, intermediate strands 211b and the core strand 211c each consist of wires that are twisted in a helical manner.

[0135] In the illustrated embodiment, the jacket 22 has a thickness of 0.8 mm, the first, fourth, and sixth diameters are the same; the second and third diameters are the same 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 can be 1 mm, the second and third diameters 0.7 mm, and the fifth diameter 0.5 mm. The jacket 22 can also be thicker, for example, 1 mm or 1.2 mm.

[0136] The Figure 3 The dashed line shown around the intermediate strands 211b serves only to illustrate the insert 212. It does not represent a mandatory material or manufacturing boundary.

[0137] Also the Figure 3The indicated inner boundary of the sheath 22 serves primarily for illustration and outlines the envelope of the support element 21. Sheath material is preferably also located within the sheath of the support element 21 in the spaces between at least some of the strands 211a-c and possibly also in the spaces between at least some of the wires 213. Instead of sheath material, spaces within the sheath of the support element 21 can also be at least partially filled with other fibers, lubricants, plastics, and similar materials. Different fillings can occur at different locations in the same support element 21.

[0138] Part of the steel wires in a supporting element 21 according to 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.

[0139] The jacket 22 is made of a polymer. This can be materials such as polyurethane or EDPM or other thermoplastics and / or elastomers.

[0140] The Figures 4a and 4b show two embodiments of a lifting drive 200 with a drum drive. This comprises a cable drive 100 with a drum 1 and a traction element 2 in the form of a round cable 2a, which rests in a single layer on the drum 1. Furthermore, the cable drive 100 in these two embodiments comprises cable pulleys 3a, 3b. The drum 1 is driven by a drive 5. Furthermore, two embodiments of a load suspension device are shown: a platform 4a and a hook 4b.

[0141] In Figure 4aThe drive 5 comprises a motor 51 and a transmission 52 to the drum 1. The transmission 52 is implemented here, to show a possible example, by a drive belt 521, which can rotate the drum 1 around its longitudinal axis and thus winds or unwinds the round rope 2a, depending on the direction of rotation. The round rope 2a runs over a fixed deflection pulley 3a: At this point, the direction of pull from the round part 2a changes from "toward the deflection pulley 3a" to "toward the drum 1" when the round rope 2a is wound up. A fixed deflection pulley is a deflection pulley that cannot adjust its position due to the movement of the traction element. However, it can usually rotate around its axis in response to the movement of the traction element, so that the movement of the traction element is only slightly slowed by the interaction with the deflection pulley. A platform 4a is attached to the free end of the round rope 2a.Loads can be placed on these, which are then lifted by winding up the round rope 2a and put down by unwinding the round rope 2a, since the pulley 3a is located above the platform 4a.

[0142] Figure 4bdepicts a further embodiment of a lifting drive 200: A drive 5, comprising a motor 51 and a transmission 52, acts on the drum 1. The transmission 52 depicted here is a suitably shaped motor axle, the rotation of which, for example, via a positive connection with an opening in the drum 1, causes the drum 1 to rotate. The round rope 2a, in turn, runs over a free deflection pulley 3a. The end of the round rope 2a is attached to a fixed point 6. On the round rope 2a, between the fixed deflection pulley 3a and the fixed point 6, a loose deflection pulley 3b rests on the round rope 2a. A hook 4b is attached to the axle of this loose deflection pulley 3b. If the round rope 2a is now wound up by the movement of the drum 1 caused by the drive 5, the round rope section between the deflection pulley 3a and the fixed point 6 is shortened. The loose deflection pulley 3b is thereby lifted and thus also a load attached to the hook 4b.When the rope pulley 1 rotates in the opposite direction, the round rope section between the pulley 3a and the fixed point 6 is extended and the loose pulley 3b is lowered, as is the load attached to the hook 4b.

[0143] In addition to the motors shown here, drums 1 can also be operated by other drives, such as water or windmills, treadmills, or cranks. The direction of rotation can be determined either directly by the drive 5 or by a suitable coupling. The unwinding of the traction element 2 can also occur simply by its own weight or the weight of objects attached to the traction element 2 and can be controlled and / or steered only by a brake or a motor brake or a controlled throttled drive 5.

[0144] Examples of rope drives with traction sheave drive can be designed very similarly: For this purpose, the Figures 4a and 4bthe deflection pulley 3a as a traction sheave. A traction sheave differs from a deflection pulley 3a primarily in that the traction sheave is driven and that a high level of friction is desired between the traction element and the traction sheave. The drive 5 acts on the traction sheave and no longer on the drum 1. In both cases, the drum 1 is pre-tensioned by a spring. The drum 1 can also have its own drive or be driven by the drive of the traction sheave or the traction sheave via a gear or drive belt. Likewise, the drive can act on the drum and either the drive or the movement of the drum can also drive the traction sheave, for example via a gear or drive belt. In a rope drive with a traction sheave, the traction element 2 can rest on the drum 1 in one or more layers.

[0145] Figure 5shows a lifting machine 300, which comprises a lifting drive 200 and a holder 7. The lifting drive 200 comprises a rope drive 100 with a rope pulley 1, a round rope 2a, rope pulleys in the form of a fixed deflection pulley 3a and a loose deflection pulley 3b. Furthermore, the lifting drive 200 comprises a drive 5, consisting of a motor 5 and transmission 52, as well as a load receiving device in the form of a gripper 4c. Similar to the embodiment of Figure 4b, one end of the round rope 2a is attached to a fixed point 6 and the load bearing device is attached to the loose deflection pulley 3b, which in turn rests on the round rope 2a between the deflection pulley 3a and the fixed point 6. The bracket 7 is a stable frame which, in the case shown here, can partially absorb the lifting drive 200 and the forces acting on it. The bracket 7 comprises a mounting device 71 for the fixed deflection pulley 3a. Such a mounting device 71 can, for example, be provided by a tension element, rope or chain loop which runs through an opening along the axis of the deflection pulley 3a and over a horizontal strut of the bracket 7. Other mounting devices 71 are, for example, suitable hooks, receptacles, axles and the like. The drive 5 and the drum 1 here stand on a base 72, which is also part of the bracket 7.

[0146] The fixed point 6, however, is not part of the holder 7 in this embodiment, but is realized, for example, on the wall of a room.

[0147] In other embodiments, fixed points 6 can also be provided on the holder 7. Likewise, a base 72 can be omitted or used only for individual parts. The mounting device 71 can also be omitted. There can also be more than one base 72 and more than one mounting device 71, or a hybrid of both: In the present case, the weight holds parts on a base 72. All other types of fastening preferably define a mounting device 71. A surface onto which a drum 1 presses due to its weight, but which is additionally screwed to the surface, is therefore an example of a hybrid between a base 72 and a mounting device 71 and should preferably also be encompassed by the term "mounting device."

[0148] Figure 6a shows a lifting machine 300, which is largely made of the lifting machine Figure 5 Unlike Figure 5Here, the mounting device 71 of the fixed deflection pulley 3a is not attached to a stationary part of the holder 7, but to a carriage 8. In the embodiment shown, the carriage 8 has wheels 8a and a carriage drive inside it. With the help of this carriage drive, the carriage 8 can move its wheels 8a in a controlled manner and thus change its position relative to the holder 7. The fixed deflection pulley 3a attached to the carriage 8 with the mounting device 71 follows the change in position of the carriage 8. By changing the position of the fixed deflection pulley 3a, in interaction with the winding or unwinding of the round rope 2a from the drum 1, the position of the loose deflection pulley 3b and thus of the gripper 4c can be controlled. By this position, not only the height but also the position in the direction of movement of the carriage 8 can be changed.

[0149] Figure 6bshows a further embodiment of a lifting machine 300: Here, the rope drive 100 does not comprise any rope pulleys, but only a drum 1 and a traction element 2. A load-bearing device in the form of a bucket 4d is attached to the traction element 2. The rope pulley is located on a carriage 8, which in turn can be moved on a holder 7. A drive for the drum 1, not shown here, is also 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 gravity pulls the carriage 8 in one direction. A push rod 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 due to gravity and allow the carriage 8 to be returned to its starting position.

[0150] The bracket 7 here has only one vertical column and a cantilever extending laterally from it. This geometry can also be used together with the Figure 6a shown carriage 8 and other cable drives 100.

[0151] The Figures 7a and 7b show lifting machine superstructures 400.

[0152] In Figure 7a is a lifting machine 300, similar to the one from Figure 6a , shown. In contrast to the lifting machine 300 from Figure 6aHere, the fixed point 6 is on the bracket 7. The lifting machine 300 is located as a whole on a carriage 9 with wheels 9a. The carriage 9 can move relative to a reference surface 10. The reference surface 10 here is an external location. The carriage 9 and the slide 8 can be aligned such that the direction of movement of the carriage 19 is different from the direction of movement of the slide 18. Thus, the gripper 4c can be moved in several dimensions relative to the reference surface 10: Its height can be determined primarily by the drum 1, its position in direction 18 by the slide 8, and its position in direction 19 by the carriage 9. It is of course also conceivable that the slide 8 and the carriage 9 can both move in several directions. In this case, a combination of the slide 8 and the carriage 9 can improve the extent and precision of the movement or accelerate it.Furthermore, it is also possible to provide only one carriage 9 but no slide 8 in a lifting machine structure 400.

[0153] In Figure 7b A hoisting machine structure 400 is also shown. In this case, the reference surface 10 is formed by a roof girder of a building. A trolley 9 with wheels can move on this girder. This trolley 9, in turn, carries a simple rope drive 100, which comprises a drum 1 and a round rope 2a. A load suspension device in the form of a bucket 4d is mounted on the round rope 2a.

[0154] Figure 7cshows a lifting machine structure 400 used as a storage and retrieval machine. A drum 1 with its drive (not shown) is mounted on a carriage 9 with wheels 9a. Furthermore, a bracket 7 is mounted on the carriage 9, which supports a deflection pulley 3a on one side and a platform 4a on the other. The platform 4a serves to support the load. Goods 11 are located in a shelf 12, which can be moved onto the platform 4a of the lifting machine structure 400 with the aid of a removal device 13.

[0155] The lifting machine structure 400 now allows the height at which the goods 11 are located to be controlled by winding or unwinding the round rope 2a onto the rope pulley 1 and to change the position relative to the shelf 12, which has a fixed position with respect to the reference surface 10, using the carriage 9. Goods 11 can, for example, be automatically placed back on a shelf 12 or at a retrieval point by slightly tilting the platform 4a.

[0156] Storage and retrieval machines are conceivable in many variants: For example, the support 7 can be designed in a variety of variants, such as a portal structure. Instead of movement by a carriage 9, the use of a slide 8 is also possible if the support 7 can carry or guide such a carriage. Furthermore, a storage and retrieval machine can essentially only control the vertical movement of goods and therefore dispense with carriage 9 and slide 8, while horizontal movement is realized by an additional transport device. Furthermore, the cable drive 100 can have more or fewer cable pulleys than in Figure 7c shown and / or the pulleys may be arranged differently than in Fig. 7cInstead of a round rope 2a, a belt 2b or another traction device 2 can also be used. The load suspension device can be designed differently, for example, as a basket, hook, gripper, bucket, or similar. A removal device 13 can also be part of the load suspension device 4, mounted on the load suspension device 4, or be part of the storage and retrieval machine or mounted on it.

[0157] Car 9, which is in the Figures 7a-c shown is one embodiment of a displacement device. Another 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, a type of air cushion or magnetic levitation can be used to reduce the friction between the holder 7 and the reference surface 10 or the guide of the displacement device, and also to generate a movement of the holder 7 relative to the reference surface 10.

[0158] To illustrate the preferred determination of the dimensions of a tension member 2, the Figures 8a and 8b be used: Fig. 8a shows a section of the tension member 2, which comprises a casing 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 perpendicular to its longitudinal axis 900 is in Figure 8b This cross section is essentially the same as in Figure 2b shown cross-section and the explanations of the Figure 2bapply here as well. Furthermore, three pairs of two non-identical parallels 901a.i and 901b.i, with i=1, 2, and 3, are drawn. Parallels 901a and 901b each touch the cross-section of tension member 2, but do not intersect it. Their distance 902 is therefore a kind of diameter of tension member 2. Of all the possible distances 902 that can be determined in this way, one is the largest and one is the smallest. The smallest distance is the first diameter 902.1 of tension member 2, and the largest distance is the second diameter 902.2 of tension member 2.

[0159] To illustrate the preferred determination of the jacket thickness 907, the Figures 9a, b and c be used: Fig. 9a shows a section of the tension member 2, which comprises a casing 22 and a support element 21. In Fig. 9aonly the casing 22 is visible. The tension member 2 is significantly longer in one direction than in the directions perpendicular to it and therefore has a longitudinal axis 900. The cross section of the tension member 2 perpendicular to its longitudinal axis 900 is shown in the Figures 9b and c shown.

[0160] To determine the sheath thickness 907, the geometric center of gravity 903 of each support element 21 present in this tension member 2 is first determined. Furthermore, the support surface 904 is determined. For an assembled tension member, this can be determined, for example, by applying an easily abradable layer or a pressure-sensitive layer (e.g., similar to carbon paper) to a suitable location on the tension member 2 over its entire circumference. When the tension member prepared in this way is then put into operation, the support surface 904 is distinguished, depending on the method, by the missing or newly created marking. For rope drives in the planning stage or for which only plans are available, these can be used to determine whether a special support surface 904 of the tension member 2 is desired. If this is not the case, the entire outer surface of the tension member 2 is considered the "support surface 904" to determine the sheath thickness.

[0161] Figure 9bshows the first step of the analysis: All straight lines passing through the center of gravity 903 of a selected support element 21 and the support surface 904 in the Fig. 9b shown example lie within the roughly hatched area 905. (For the sake of clarity, the straight lines starting from the center of gravity 903 in the other direction were omitted.) Some of the straight lines 905 intersect two support elements 21. These should not be used to determine the shell thickness 907. Starting from the selected support element 21, the straight lines that extend within the area 906 remain for further evaluation.

[0162] Figure 9c shows the situation after the analysis of Figure 9bwas repeated for all supporting elements 21: There are now a multitude of surfaces 906, starting from the different centers of gravity of the supporting elements 21. Among all the straight lines shown there, the task is to find the one for which the distance between the support surface and the first intersection point with the envelope of the corresponding supporting element 21 is the shortest. This is the shell thickness 907.

Claims

1. Cable drive, in particular for cranes or mass hoists, comprising a) a drum (1) and b) a pulling member (2), b1) which runs on the drum (1), b2) which is wound and unwound on the drum during operation, and b3) which comprises at least one supporting element (21). b4) wherein the supporting element (21) consists of strands which are produced from metal wires, the at least one supporting element (21) being at least partially surrounded by a sheath (22) which comprises a polymer and wherein at least a part of the sheath (22) constitutes a bearing surface of the pulling member (2), wherein at least one of the supporting elements is a stranded cable with six or more outer strands, in particular with exactly nine outer strands, characterized in that the supporting element has a cable lay length of less than or equal to 7.5 times the supporting element diameter, in particular preferably of less than or equal to 6.8 times the supporting element diameter.

2. Cable drive according to claim 1, characterized in that a) the sheath consists substantially completely of the polymer, and b) in that the polymer is in particular a thermoplastic and / or an elastomer.

3. Cable drive according to one of claims 1 to 2, characterized in that the dimensions of the pulling member (2) and the drum (1) are matched to one another such that the pulling member (2) rests on the drum (1) in a maximum of one layer at any time during operation of the cable drive.

4. Cable drive according to one of claims 1 to 2, characterized in that the dimensions of the pulling member and the drum of a cable drive are matched to one another such that the pulling member rests on the drum in more than one layer at the times of operation of the cable drive at which the length of the pulling member is wound up to the greatest extent.

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

6. Cable drive according to one of claims 1 to 5, characterized in that the pulling member (2) is a round cable (2a), the supporting element (21) of which is formed by a stranded cable which comprises one or more strands (211a, b, c), and wherein at least a part of the strands (211a, b, c) of the stranded cable comprise steel wires (213) which preferably have a tensile strength of > 2160 N / mm2, in particular of > 2300 N / mm2, in particular of > 2500 N / mm2, especially of > 2600 N / mm2, very especially of > 2800 N / mm2.

7. Cable drive according to one of claims 1 to 6, characterized in that a) the pulling member comprises a sheath with a constant thickness of 0.8 to 1.2 mm, and b) the pulling member comprises exactly one supporting element, wherein b1) the supporting element is a stranded cable with a wire cable core as an insert and outer strands, and b2) the supporting element is a cross-over cable, and b3) the wire cable core of the supporting element is stranded in parallel with the outer strands.

8. Lifting drive, comprising a) a cable drive according to one of claims 1 to 7, and b) a drive (5) which acts on the drum (1) and / or a traction sheave and can thus bring about a movement of the pulling member (2), c) and preferably a load receiving means (4) which can be controlled, in particular driven, in its movement by a movement of the pulling member (2).

9. Lifting drive according to claim 8, characterized in that a) the load receiving means (4) is configured as a gripper (4c) or platform (4a), and b) the load receiving means (4) is fastened at least inter alia to one end of the pulling member (2) or to a loose deflection roller (3a).

10. Lifting machine, comprising a) a lifting drive according to one of claims 8 to 9, and b) a holder (7) which at least partially absorbs forces which act on at least a part of the lifting drive.

11. Lifting machine according to claim 10, further comprising a) a carriage (8) which can be moved with respect to the holder (7) and thus performs a carriage movement. a1) wherein the carriage movement can control a lifting drive movement, a1a) wherein the lifting drive movement is a movement of at least a part of the lifting drive with respect to the holder (7).

12. Lifting machine construction, comprising a) a lifting machine according to one of claims 10 to 11 and b) a reference surface (10) which absorbs the forces acting on the lifting machine, preferably in the form of a floor or a ceiling and c) a displacement device which allows a movement of at least a part of the holder (7) with respect to the reference surface (10), specifically in particular by the rolling of wheels (9a).

13. Method for producing a cable drive according to one of claims 1 to 7, characterized in that a) a drum (1) is provided, b) a pulling member (2) comprising at least one supporting element (21) and a sheath (22) which constitutes the bearing surface of the pulling member (2) is provided, wherein at least one of the supporting elements is a stranded cable with six or more outer strands, in particular with exactly nine outer strands, and the supporting element has a cable lay length of less than or equal to 7.5 times the supporting element diameter, in particular preferably of less than or equal to 6.8 times the supporting element diameter, and c) the pulling member (2) is applied to the drum (1) in such a way that it can run on the drum (1).

14. Method for producing a lifting drive, comprising a) the method for producing a cable drive according to claim 13 and b) the coupling of a drive (5) to the drum (1) and / or a traction sheave, so that the drive (5) can bring about a movement of the drum (1) and / or traction sheave, preferably a rotation, and the drum (1) and / or traction sheave can thus bring about a movement of the pulling member (2), c) and preferably the mounting of a load receiving means (4) which can be controlled and in particular driven in its movement by a movement of the pulling member (2).

15. Method for producing a lifting machine, comprising a) the method for producing a lifting drive according to claim 14 and b) the provision of a holder (7), c) the combination of the lifting drive and the holder (7) in such a way that the holder (7) can absorb the forces acting on at least a part of the lifting drive.