EP3573918B1 - Treuil à câble passant - Google Patents

Treuil à câble passant Download PDF

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Publication number
EP3573918B1
EP3573918B1 EP18700911.3A EP18700911A EP3573918B1 EP 3573918 B1 EP3573918 B1 EP 3573918B1 EP 18700911 A EP18700911 A EP 18700911A EP 3573918 B1 EP3573918 B1 EP 3573918B1
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EP
European Patent Office
Prior art keywords
drive
rope
cable
traction sheave
flexible drive
Prior art date
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EP18700911.3A
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German (de)
English (en)
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EP3573918C0 (fr
EP3573918A1 (fr
Inventor
Paul Schumann
Thorsten Schmidt
Thomas Leonhardt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Planeta-Hebetechnik GmbH
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Planeta Hebetechnik GmbH
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Publication of EP3573918A1 publication Critical patent/EP3573918A1/fr
Application granted granted Critical
Publication of EP3573918C0 publication Critical patent/EP3573918C0/fr
Publication of EP3573918B1 publication Critical patent/EP3573918B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B66D1/7415—Friction drives, e.g. pulleys, having a cable winding angle of less than 360 degrees

Definitions

  • the invention relates to a continuous rope winch, comprising a traction sheave with a drive goggle installed circumferentially on its circumference for receiving a rope and an envelope drive arrangement designed opposite the drive goggle in the area of a rope-driving part of the circumference of the traction sheave for frictionally pressing the rope against the drive goggle, which is a revolving endless element comprises, which is placed with a first strand at least over Hülltrieb support elements and with a second strand over the cable-driving part of the circumference of the traction sheave, the traction sheave and the Hülltrieb arrangement being synchronized in such a way that those surfaces of the drive goggle and Hülltrieb arrangement that come into contact with provided on the rope, can be moved in the same direction and at the same speed.
  • Rope winches are used in numerous applications. They are particularly used in the area of small goods, facade and maintenance elevators. There are also applications on construction sites in which continuous rope winches are used as traction devices for temporarily moving, shifting or holding loads.
  • the rope is additionally pressed into the groove by pressure elements.
  • These pressure elements are usually designed as rollers or clamping mechanisms that load the rope with another pressure point in line contact.
  • Various solutions are known for this, which act on the rope at one or more locations.
  • the publication shows a solution with a very localized effect on the rope US 4,706,940 , whereby at least one pressure roller presses the rope into a very steep V-groove and causes corresponding wear.
  • An improved embodiment provides a larger part of the circumference of a traction sheave for the pressure over which the load is distributed.
  • a variant is provided in which the rope is pressed against the traction sheave by a large number of rollers that are connected to one another by standing chain links. However, each roller touches the rope through line contact and therefore puts a lot of strain on it.
  • the bending radii on the pressure rollers are very small in relation to the rope diameter. Significant rope bending stress occurs.
  • the pressure rollers touch the rope through a line load and press it into a V-groove that again places high stress on the rope.
  • the load-dependent pressure force can also cause the rope to slip under jerky load.
  • a V-groove is used, so that this construction also places high stress on the rope in the groove.
  • the cable pull device has automatic contact pressure regulation.
  • the traction sheave is attached to a movable carriage. This sits in a rigid housing to which the pressure roller (reference number 4) is also attached.
  • the pressure roller reference number 4
  • the traction sheave is pressed more or less strongly against the pressure roller during operation, thus creating a frictional connection.
  • an additional spring is attached to the traction sheave. This maintains a minimum preload.
  • the disadvantage of this variant is that the pressure roller puts a high-stress line load on the rope. Despite the high pressure of the pressure roller, the driving force remains low.
  • the pre-tensioning device there is a risk of the rope slipping through the traction sheave; This document discloses the preamble of claim 1.
  • the publication DE 10 2012 100 099 A1 describes a continuous winch which includes a traction sheave (reference numeral 4) mounted in a rigid housing (reference numeral 2), on which a rope (reference numeral 3) runs, which is pressed onto the traction sheave by a pressure roller (reference numeral 8, 9).
  • the pressure rollers are mounted on movable levers (reference numbers 13 and 14).
  • the levers are coupled to one another via a tension spring or are individually connected to the housing using compression springs (reference number 29).
  • the principle of the proposed continuous winch is that the end of the rope under load (reference symbol L) deflects the pressure roller on the respective side and thus presses the other roller onto the traction sheave in order to increase the frictional connection between the rope and the traction sheave.
  • the pressure force is proportional to the rope force.
  • the symmetrical structure enables lifting operation at both rope ends.
  • the disadvantage of this design is high pressure between the pressure roller and the rope. Due to the pressure rollers, only a line load acts on the rope. In addition, the rope undergoes one and a half counter-bends as it passes through the winch, which also puts strain on the rope. There is also a risk of the rope slipping through the traction sheave when subjected to jerky loads. A scaling of the principle is not feasible because the driving forces are firmly linked to geometric conditions.
  • the compact continuous cable pull device according to the publication EP 06 77 480 B1 generates a load-dependent contact force.
  • the rope (reference number 2) is pressed against a traction sheave (reference number 1) by rollers (reference number 4) in order to create an additional frictional connection.
  • the contact pressure can be applied via the cable force or via a permanently installed spring. If the contact force is to be generated via the rope force, a tie rod (reference number A) must be firmly connected to an anchoring point (reference number 5). The tie rod then presses the rollers against the traction sheave with a force proportional to the rope force. Alternatively, the tie rod can also apply the contact force with a spring mounted between the end of the anchor and the housing of the continuous winch.
  • the lateral clamping which has to be loosened and re-fixed constantly as the rope passes through, usually requires a higher level of equipment and is therefore comparatively expensive, maintenance-intensive and susceptible to wear.
  • the V-groove and clamping jaws exert line contact on the rope and therefore put a lot of strain on it.
  • the clamping force is very limited by the individual, small leaf springs. It can only be increased through considerable additional effort.
  • the clamping mechanism is sensitive to manufacturing deviations as well as dimensional and shape changes due to wear. These factors greatly influence the clamping and pulling force. The correct position between the clamping jaw and the rope must be enforced by tight manufacturing tolerances.
  • Another disadvantage is that the pressure force on the circumference of the traction sheave is not constant. At high conveying speeds, there is a risk that the clamping mechanism cannot open quickly enough due to inertia and the rope is torn out of it.
  • the clamping and opening of the traction sheave takes place by tilting at least one half of the traction sheave, the rope is only clamped on a very short section of the circumference of the traction sheave. Due to the principle, wrap angles greater than 180° are not possible. Otherwise the clamping could not work because the axial clamping forces would cancel each other out. If the traction sheave is segmented, there is only line contact with the rope. The strain on the rope is then considerable. A simple scaling of the principle is not possible. The clamping and thus the driving force of the proposed solution are linked to fixed geometric conditions. With a jagged undercut, there is a risk of individual cable wires becoming trapped. In this case the driving force is no longer present.
  • the traction sheave is sensitive to dirt. If dirt particles get stuck in the undercut of the groove, the driving force is no longer available. With individual solutions, deviations in the nominal dimensions of the rope, grooved chuck and clamping jaws can only be compensated for to a small extent. Individual elements then do not support. The disadvantage is usually the high number of special parts that have to be manufactured very precisely.
  • a passively rotating pressure chain is provided on a section of the traction sheave.
  • the pressure elements put an additional surface load on the rope.
  • Such a solution is in publication DE 43 30 162 A1 described.
  • the pressure chain only acts on the rope over a very short section of the traction sheave. There is no even, flat pressure, so there is no pressure uniform surface load. Manufacturing deviations and wear on the kidney-shaped chain roller track can lead to deviations in the pressure height. In the worst case scenario, it is not several pressure elements that press the rope into the groove, but only the one that protrudes furthest. The same effect occurs with manufacturing deviations in the groove.
  • the publication describes another, similar solution DE 22 01 548 C3 with a traction sheave for unlimited rope passage.
  • the rope on the traction sheave is additionally pressed onto the traction sheave by individual links of a rotating pressure chain.
  • Pressure elements are attached to the chain links, which correspond to the negative of the rope on the traction sheave. This means that the contact area between the pressure element and the rope is large.
  • the chain itself runs loosely around guide rails installed in the housing.
  • the pressing force is generated by a lever mechanism. It is transferred to the inside of the chain by rollers.
  • the clamping force itself is load dependent. It is generated by a rope pulley acting in the loaded rope section.
  • a spring maintains a minimum preload force.
  • the chain is positively driven by the traction sheave.
  • the construction is characterized by the following disadvantages: When the rope passes through a total of three bends, there is even a counter-bend in the loaded rope section. Every change in bending is accompanied by increased stress on the rope, because counter-bending changes in narrow sections place particular strain on the rope.
  • the rope pulley in the incoming rope area also has a very small bending radius, which also causes high rope stress.
  • Another particularly serious problem is that the rope is only pressed by the pressure elements of the chain over a very short area of the circumference of the traction sheave, since the design of the pressure mechanism does not allow any further wrapping.
  • the driving force remains comparatively low despite high pressure forces.
  • the main pressure area is very small in relation to the circumference of the traction sheave, primarily due to the design of the pressure mechanism.
  • the profile of the pressure chain does not follow the outer rope contour; instead, it touches the rope with a flat surface and puts considerable strain on it due to the line contact.
  • the rope is pressed into a steep V-groove, which also leads to high rope stress.
  • the loaded links alternate as one link passes through the other under the roller. This causes the clamping and driving force to fluctuate. At high conveying speeds there is a risk of the pressure rollers lifting off. The consequences are a loss of clamping and driving force.
  • the rope Before leaving the rope to the right side, the rope wraps around another traction sheave (reference number 32) with an approximately 80° wrap angle.
  • the solution is characterized by the following disadvantages. A total of one and a half counter-bending changes act on the rope as it passes through the winch. This puts a lot of strain on the rope.
  • the diameter of the traction sheaves is very small in relation to the rope diameter. This also causes very high rope stress with every bending change. Of the two traction sheaves, only a very small part of the circumference of the traction sheave is used for frictional engagement.
  • the proposed device is designed to be material-intensive, the usable driving force remains low.
  • the square traction sheave also puts a lot of strain on the rope due to the line contact across the longitudinal axis of the rope. Furthermore, the chain lies directly on the rope. The bushings and plates of the chain touch the rope in such a way that line and point loads are created and put additional strain on the rope.
  • the object of the invention is to offer a cable winch which, with a high, constant driving force, achieves a uniform, flat pressure force even at high cable speeds and regardless of the load at the outgoing cable end and minimizes cable wear.
  • a continuous cable winch comprising a traction sheave shaft, which is intended in particular for driving or taking off, with a traction sheave with a driving goggle running around the circumference.
  • the traction sheave shaft is at least non-rotatably connected to the traction sheave.
  • the driving goggles around the circumference are used to hold a rope.
  • An enveloping drive arrangement arranged opposite the drive goggle, for example on a cable-driving part of the circumference of the traction sheave, is designed for frictionally pressing the rope against the drive goggle.
  • the Hülltrieb arrangement comprises a revolving endless element, which is placed with a first strand over Hülltrieb support elements and with a second strand over the cable-driving part of the circumference of the traction sheave.
  • the traction sheave and the enveloping drive arrangement are synchronized in such a way that those surfaces of the driving goggle and enveloping drive arrangement that are intended for contact with the rope can be moved in the same direction and at the same speed.
  • the traction sheave with the drive goggle and the front surface of the enveloping drive arrangement with a pressure groove facing the drive goggle each have a contour that is essentially complementary to the profile of the rope, so that the rope is gripped on a large part of its lateral surface;
  • profile ropes are also included in the invention.
  • the frictional pressure of the rope against the drive goggle takes place by means of the enveloping drive arrangement via a rope-driving part of the circumference of the traction sheave, with the rope being pressed into the drive goggle by pressure elements as soon as the rope is in the drive goggle.
  • the enveloping drive arrangement comprises at least one endless element and pressure elements connected to the endless element or formed in one piece from it. These are necessary for the function of the enveloping shoot arrangement Envelope drive support elements supporting the endless element, which enable the endless element to rotate. If the endless element is designed as a belt, the envelope drive support elements are designed, for example, as pulleys. If a chain or a conveyor chain is provided as the endless element, as described below, the envelope drive support elements are designed, for example, as chain wheels. In the context of the invention, the enveloping support elements also include other means that support the circulation of the endless element, such as. B. a roller conveyor or even a slideway.
  • the enveloping drive arrangement as an endless element not only comprises a conveyor chain, it can also be designed as a toothed belt, as a flat belt or as an arrangement of spliced ropes.
  • the variant with an arrangement of spliced ropes is designed with a rope for a deep rope groove or several ropes connected to the lateral surface.
  • the endless element of the enveloping drive arrangement is designed as a toothed belt or flat belt
  • the toothed belt or the flat belt has such a cross-sectional profile that the side of the toothed belt or the flat belt facing the drive goggle has a contour that is essentially complementary to the profile of the rope.
  • the endless element is designed as a conveyor chain
  • pressure elements are arranged on the conveyor chain, while the function of the pressure elements is preferably integrated into the endless element in other types of endless element. This applies, for example, to toothed belts, which then have a profile on one side that takes on the function of the pressure elements.
  • the enveloping drive arrangement comprising the conveyor chain has pressure elements which are arranged continuously on one side of the conveyor chain and the front surface facing the drive plate forms the enveloping drive arrangement with a quasi-continuous pressure groove, with the enveloping drive support elements and the Hülltrieb coupling element as chain wheels, namely as a support chain wheel or drive chain wheel.
  • the Hüllrete coupling element like the Hüllrete support elements, also has the function of transmitting force and movement from a drive arrangement, e.g. B. a motor with a drive shaft, on the endless element. So if the Hüllrete support elements are designed as chain wheels, specifically as support chain wheels, the Hüllrete coupling elements are designed as drive chain wheels.
  • a conveyor chain designed as a chain that can run at an angle has proven to be beneficial for operational safety.
  • the conveyor chain is advantageously designed as a wide chain or as a multiple chain. With these versions, a particularly high driving force can be transmitted.
  • What is required for the function of the invention is the synchronization between the rotational movement of the traction sheave and the movement of the enveloping drive arrangement, so that the peripheral speeds between the traction sheave and the enveloping drive arrangement match, in particular with regard to the surfaces that are intended for contact with the rope, which then move in the same direction can be moved at the same speed.
  • the synchronization is preferably carried out by means of a positive locking mechanism. This can be achieved, for example, by interlocking gears on the drive pinion and traction sheave.
  • the drive then takes place, for example, by means of a drive pinion, which is driven, for example, by a motor and whose teeth are in engagement with a toothing of the traction sheave, in particular an external drive toothing in the preferred embodiment.
  • Manufacturing or wear-related deviations can cause differences in the envelope drive and traction sheave speed. These differences are advantageously compensated for by a compensation option between the enveloping drive and the traction sheave, for which a countershaft differential can be used, for example. This means that influences such as play in the chain or wear-related elongation can be compensated for, so that sufficient synchronization can always be achieved.
  • the synchronization between the traction sheave and the enveloping drive arrangement takes place through an at least one-sided, preferably double-sided enveloping drive toothing of the traction sheave and engagement means arranged on the side of the front surface on the enveloping drive arrangement, for example drive rollers for an enveloping drive toothing designed as a roller toothing.
  • the means of intervention e.g. B. the drive rollers are designed and arranged in such a way that they fit into the enveloping drive teeth, e.g. B.
  • a double-sided enveloping drive toothing of the traction sheave is arranged on both sides of the drive plate and correspondingly arranged engagement means on the enveloping drive arrangement are provided.
  • a continuous cable winch that includes a conveyor chain
  • this type of synchronization can also be used, for example, with flat or toothed belts, whereby instead of the drive rollers, corresponding shapes of the edges of the flat belt are also suitable for engaging in the roller teeth of the traction sheave. or timing belt can be used.
  • Multiple chains also allow for a different arrangement of the drive rollers, so that they do not necessarily have to be arranged on the side of the front surface on the enveloping drive arrangement, but, for example, additionally or exclusively between individual strands of the multiple chain.
  • At least one Hüllrete coupling element is provided, the Hüllrete coupling element being connected at least in a rotationally fixed manner to an Hüllrete shaft, driven by the drive arrangement, as the drive is generally referred to below.
  • the Hüllrete coupling element enables the flow of force or energy between the drive arrangement and the envelope drive arrangement, so that the envelope drive arrangement can be driven.
  • the rope winch according to the invention is used, for example, to move a load on the rope or on the housing of the rope winch by the work of the drive motor acting on the rope, especially the part of the rope entering the rope winch.
  • the drive motor which is then used as a generator, is driven by the rope winch when a load on the rope or on the housing of the rope winch moves the traction sheave and thus the drive motor, e.g. B. for energy production or energy conversion.
  • the drive motor used as a drive or as a generator is therefore also generally referred to below as a traction sheave drive arrangement.
  • a drive of a preferred embodiment of the continuous cable winch or a drive by the continuous cable winch are thus provided by means of the traction sheave drive arrangement, the enveloping drive arrangement and/or a direct drive of the endless element, with the power transmission between the traction sheave drive arrangement and the traction sheave, the enveloping drive arrangement and the enveloping drive or the direct drive of the endless element and the endless element via a gear arrangement, as explained below.
  • the traction sheave drive arrangement, the envelope drive drive arrangement or the direct drive, all three generally referred to as a drive arrangement are designed as a drive motor.
  • the drive motor acts on the traction sheave
  • the drive motor acts on the enveloping drive
  • the drive motor acts directly on the endless element, whereby a pinion, chain wheel or similar can be present, which controls the rotational movement of the motor a drive shaft is transferred to the traction sheave, enveloping drive or endless element.
  • the transmission arrangement is also designed as a gear transmission, as a chain transmission or as a belt transmission.
  • the endless element has a first and a second strand, the first strand of the endless element being between a first Hüllretesharielement, for example a chain wheel, and a last Hüllrete support element is placed over at least one further Hüllrete support element and extends over at least the Hüllrete tensioning element, an Hüllrete support element designed for tensioning the endless element.
  • the first strand is placed under mechanical tension by the Hülltrieb tensioning element, for example a tensioning chain wheel, so that the second strand, which extends between the last chain wheel and the first chain wheel, is still pressed against the traction sheave.
  • the enveloping drive arrangement i.e. the endless element with the pressure elements, rests firmly on the traction sheave in the area in which the rope runs. This clamps the rope, increases the static friction in both the drive plate and the pressure groove and improves the power transmission from the traction sheave and the enveloping drive arrangement to the rope and vice versa.
  • the Hülltrieb support element is designed as a Hülltrieb coupling element, for example as a drive chain wheel.
  • a preferred embodiment of the tensioning device provides that the mechanical tension is generated by a constant force device, in particular a simple and inexpensive spring arrangement. This achieves a uniform pressure force of the spring-loaded enveloping drive arrangement in the direction of the rope, and fluctuations in the thickness of the rope are also compensated for.
  • a tensioning device which comprises a spring arrangement, the spring force of which is caused by disc springs, in particular those with a strongly degressive characteristic, has proven to be advantageous.
  • a range of the spring characteristic is used in which the force changes little and which is referred to below as the constant force range. This means that no change in force is caused when the path changes.
  • a preferred tensioning device provides a spring arrangement as a constant force device, which comprises a tensioning fork and a tensioning axis mounted in the housing with a translational degree of freedom so as to be radially movable relative to the axis of the traction sheave.
  • the tensioning axis is arranged in the area of a first end of the tensioning fork and is intended to accommodate one of the enveloping drive support elements, i.e. the tensioning chain wheel when using a conveyor chain.
  • the clamping fork is mounted in the housing at a second end opposite the clamping axis, so that the spring force acts between the housing and the clamping axis and is transmitted to the clamping axis, i.e. the flow of force via the housing is closed.
  • a multi-groove design of the traction sheave so that several ropes can be gripped at the same time, and a corresponding design with several enveloping drive arrangements are also advantageous.
  • the conveyor chain is as a conveyor chain through the drive chain wheel, which is fixed to the drive pinion seated on the motor shaft can be connected, driven directly by motor.
  • the traction sheave is toothed and is driven by the drive pinion.
  • both the frictional connection between the rope and the traction sheave and the frictional connection between the rope and the pressure elements act to drive the rope.
  • the maximum possible contact surface is used to create a frictional connection that protects the rope, so that the circumferential surface of the rope is almost completely enclosed and in contact with the driving groove and pressure groove.
  • the pressing force is preferably generated by a suitable constant force device, such as a disc spring column in practice.
  • a suitable constant force device such as a disc spring column in practice.
  • disc springs with a strongly degressive characteristic curve or another constant force device in which no drop in force occurs at all are used.
  • the constant force range of the spring characteristic in which the spring force changes only slightly over the spring travel, is used, so that the force remains essentially constant when the travel changes.
  • the disc springs are supported between the housing and the clamping fork.
  • the clamping fork transmits the pressure force via the clamping axis and the enveloping drive clamping elements, e.g. B. the sprocket, on the conveyor chain in the present exemplary embodiment.
  • the tension axis is movably mounted in the housing with a translational degree of freedom radially or perpendicular to the main axis. This allows the clamping path to be realized for the endless element. Elongation of the endless element or chain is also compensated for without a significant loss of force.
  • All other enveloping support elements such as. B. chain wheels are preferably mounted in the housing on roller bearings. They only have one rotational degree of freedom.
  • the endless element or the conveyor chain can wrap around the circumference of the traction sheave.
  • the rope leaves the traction sheave at an offset of approximately 270° from the entry point.
  • the pressure elements detach from the rope and release it to leave the traction sheave.
  • the outgoing, unloaded rope end runs laterally past the incoming, loaded rope end.
  • the rope finger component takes over the guidance of the rope.
  • the location of the pressing and releasing of the pressure elements in relation to the rope is determined by the size and position of the enveloping support or coupling elements, in particular chain wheels, located at the rope inlet and rope outlet.
  • the endless element or the conveyor chain centers itself axially on the rope in the pressure area.
  • This property is made possible by the significant skewing ability of chains. Lateral signs of wear or manufacturing deviations are compensated for without additional effort.
  • the traction sheave has lateral boundaries that prevent the pressure elements and the conveyor chain from slipping laterally from the traction sheave when there is no rope in the rope winch, which can be used in particular as a high-load pressure winch.
  • the rope is clamped almost completely up to 3/4 (270°) of the traction sheave circumference, in special cases even more, up to approximately 360°. Due to the large pressure surface between the rope and the pressure elements or the round groove of the traction sheave, large pressure forces can act on the rope and the stress on the rope remains low. Due to the simple and narrow side design, particularly wide chains or double or multiple chains can be used to achieve high driving force. In contrast to the state of the art, the design effort to increase the driving force remains at a low level.
  • the rope winch according to the invention is also suitable for conveying at high speeds.
  • the pressure elements are attached separately to the links of the conveyor chain if one is used as an endless element. This means they can be replaced economically and with little effort for different requirements or when they are worn out, without the entire conveyor chain having to be replaced.
  • the rope winch according to the invention can be used advantageously in various areas of conveyor technology and lifting equipment.
  • the pressure elements make it possible to operate the high-load pressure winch in such a way that the outgoing rope end of the high-load pressure winch is completely relieved. A driving force can still be generated. With a classic traction sheave, this is not possible according to the Eytelwein equation mentioned at the beginning.
  • the wrap around the traction sheave by the rope is 180°.
  • This embodiment offers further great potential because it can replace all classic traction sheave applications, such as counterweight elevators. Due to the increased driving capacity according to the extended Eytelwein equation listed above, the mass of the cabin and counterweight, which according to the state of the art ensure the appropriate pressure of the rope on the traction sheave, can be significantly reduced for the same payload. Enormous energy and cost savings are possible.
  • the wrap around the traction sheave by the rope is greater than 180° and in a particularly preferred case, which is also shown in the figures, is 270°.
  • a rope finger is provided, which preferably redirects the relieved rope when it is driven by the rope winch and leads it past the loaded rope so that it can run straight onto the traction sheave.
  • a continuous rope winch is also planned, in which the rope wraps around the traction sheave at 180°.
  • the rope can be wrapped around the traction sheave smaller or larger than 180° and a rope finger can be provided in order to guide the incoming rope and the outgoing rope past each other with a loop greater than 180°.
  • the wrap can also be more than 270°, up to almost 360° in special cases.
  • a particularly advantageous application of the rope winch according to the invention is when it is combined with a rope storage winch in such a way that the rope can be stored and/or the rope is relieved Rope end can be pre-tensioned to increase the driving force of the high-load pressure winch. This fact is reflected by the extended Eytelwein equation listed above. However, non-driven, i.e. passive rope storage systems can also be used.
  • Fig. 1 shows an embodiment of a rope winch 1 according to the invention schematically in a perspective view with the housing open (only housing part 12 visible) and the rope finger 20 also opened Fig. 2 the enlarged detail X of the Fig. 1 .
  • Fig. 3 shows schematically in a cross-sectional view this embodiment of the cable winch 1 according to the invention with both housing parts 12, 13.
  • a rope 3, 3' enters the rope winch 1 with an incoming section of the rope 3 and exits it again with an outgoing section of the rope 3', with an angle of 270° being spanned between the two sections, correspondingly the wrap being 270° on a traction sheave is 2.
  • the traction sheave 2 is mounted with its main axis 37 via a ball bearing 26 in the housing (only housing part 12 visible).
  • the traction sheave 2 has a traction goggle 22 on its circumference, into which the rope 3, 3 'runs in or out, as shown above all in Fig. 2 recognizable.
  • the pressure elements 5 are individually designed on a side of a conveyor chain 4 facing the traction sheave 2 in such a way that a pressure groove 50 reproduces the rope shape in negative and This means it fits snugly and evenly against the rope 3.3'.
  • the length of the pressure grooves 50 of the individual pressure elements 5 is dimensioned such that they lie close together, virtually without gaps, when the chain rotates around the traction sheave 2 and is curved in the radius of the traction sheave 2.
  • a very even pressure that increases the frictional force in the drive goggle 22 is applied to the rope 3, 3' while avoiding highly stressful load peaks.
  • the power transmission does not only take place via the static friction between the drive goggle 22 and the rope 3, 3 ', because the conveyor chain 4 is also connected to a motor 42, which serves as a drive, in terms of transmission technology, as is the traction sheave 2.
  • the drive of the traction sheave 2 takes place via a drive pinion 46, the teeth of which are in engagement with the external drive teeth 38 of the traction sheave 2.
  • the motor 42 also drives a drive sprocket 9, which is arranged on the same drive shaft as the drive pinion 46.
  • the conveyor chain 4 runs over the drive chain wheel 9 and is also carried by support chain wheels 6 and a tension chain wheel 7. These are in turn supported by an axle 11 mounted in the bearing 10 and arranged in the housing (only housing part 12 visible).
  • the conveyor chain 4 forms a first run, stretched between the drive chain wheel 9 and the last support chain wheel 6, and a second run, stretched between the last support chain wheel 6 in the direction of rotation and the drive chain wheel 9, viewed when the incoming rope 3 is driven.
  • the second run thus serves the pressure of the rope 3, 3 'into the drive goggle 22, while the conveyor chain 4 runs back over the first strand.
  • the conveyor chain 4 is tensioned in the first run by the tensioning chain wheel 7, so that the tension in the conveyor chain 4 increases overall and the pressure of the pressure elements 5 on the drive wheel 2 is also increased or can be adjusted.
  • the tension chain wheel 7 is arranged to be radially movable relative to the traction sheave 2.
  • This mobility enables a clamping fork 14, which is supported on both sides of the housing (only housing part 12 visible), and which acts on a clamping axle 8 on which the clamping chain wheel 7 runs.
  • the tension is caused by a package of disc springs 15 and is adjustable via a nut 17.
  • the previously described embodiment of the cable winch 1 is shown again schematically Fig. 4 shown, but there in a longitudinal section.
  • Fig. 5 a detail Y of the cable winch according to the invention Fig. 4 .
  • the section through the rope 3 'and the traction sheave 2 clearly shows how the rope 3' runs out of the traction goggle 22 and is deflected by the rope finger 20 in order to avoid a collision with the incoming rope 3.
  • the pressure elements 5 with the pressure grooves 50 are first pressed against the rope 3' by the conveyor chain 4, which runs on the support chain wheel 6, and then release it again when it runs off the traction sheave 2.
  • the conveyor chain 4 runs over the drive sprocket 9, the support sprockets 6 and the tension sprocket 7.
  • Fig. 6 shows schematically in a perspective view with the housing open (only housing part 12 visible), but with the rope finger 20 closed, an embodiment of a rope winch 1 according to the invention.
  • the rope guide can be seen through which the incoming, loaded rope 3 runs stretched into the rope winch 1, while the outgoing, unloaded rope 3 'is deflected by the rope finger 20 and guided out of the path of the incoming rope 3.
  • the tensioning fork 14 with the plate springs 15 acts on the tensioning axis 8 and thus on the tensioning chain wheel 7, so that the conveyor chain 4 is tensioned with the pressure elements 5.
  • Fig. 7 shows the rope winch according to the invention Fig. 6 with a closed housing, consisting of the housing parts 12, 13. This makes the structure and function of the clamping fork 14 clear. This is guided on both sides in a clamping fork abutment 19 and supported on the housing 12, 13. The package of disc springs 15 pushes the clamping fork 14 away from the clamping fork abutment 19, the spring force being adjustable by the nut 17. A nut 17 'limits the path of the tension fork 14. The tension fork 14 acts on the tension axis 8 with the tension chain wheel, not visible here, inside the housing 12, 13.
  • Fig. 8 shows schematically a detail of an embodiment of a rope winch 1 according to the invention in a section cut transversely to the longitudinal axis of the rope 3, 3 '. This makes it clear how closely the drive goggle 22 and the pressure groove 50 rest on the rope 3, 3 'and enclose it over almost its entire circumference.
  • the drive goggle 22 is part of the traction sheave 2
  • the pressure groove 50 is part of the pressure element 5, which is carried by the conveyor chain 4 and pressed against the traction sheave 2.
  • Fig. 9 shows schematically in side view an embodiment of a link of a conveyor chain 4 with pressure element 5 and Fig. 10 shows a schematic perspective view of the link of the conveyor chain 4 with the pressure element 5, with the pressure groove 50 also being visible.
  • Fig. 11 shows schematically in a perspective view with the housing open and the cable finger 20 closed a further embodiment of a cable winch 100 according to the invention, which differs primarily in the type of drive of the conveyor chain 140 from that previously described in the description of Figures 1 to 10 explained embodiment differs.
  • Fig. 12 shows a detail of the cable winch 100 according to the invention Fig. 11 .
  • the drive acts exclusively on a traction sheave 120, which has an internal drive toothing 122 into which the pinion of the motor 42 engages.
  • external teeth would also be possible.
  • a conveyor chain 140 as an endless element of an envelope drive arrangement 160 is driven by roller teeth 124 on the traction sheave 120.
  • the conveyor chain 140 engages with the roller teeth 124 via drive rollers 142, which are arranged laterally on the conveyor chain 140 as soon as the conveyor chain 140 approaches the traction sheave 120.
  • the support chain wheels 6 and the tensioning axle 8 are accommodated on the tensioning fork 14 in the housing part 12.
  • the tension fork 14 carries the plate springs 15 and the nut 17.
  • the traction sheave 120 is carried by the main axle 37 mounted in the ball bearing 16.
  • Fig. 13 shows an embodiment of a link of a conveyor chain 140 with pressure element 5 and drive rollers 142 in a perspective view as a detail of the cable winch 100 according to the invention Fig. 11 .
  • the drive rollers 142 are rotatably mounted on or with an axle that is arranged transversely to the direction of travel of the conveyor chain 140.
  • Fig. 14 shows schematically a longitudinal sectional view of the embodiment Fig. 11 a rope winch 100 according to the invention.
  • Fig. 15 shows schematically a detail of the embodiment Fig. 11 a rope winch 100 according to the invention in a cross-sectional view to the axis of the rope 3.
  • Fig. 16 shows schematically in a side view with a closed housing, consisting of the housing parts 12, 13, an embodiment of a cable winch 1 according to the invention with a tension fork 14 with plate springs 15, nut 17 as well as the tension axle 8 and the tension fork abutment 19. Due to the position of the cuts AA (see Fig. 17 ) and BB (see Fig. 18 ), the function and position of the components in relation to each other are easier to understand.
  • Fig. 17 shows a schematic representation in section plane AA of an embodiment of a cable winch 1 according to the invention with tensioning fork 14 according to Fig. 16 , whereby the function of the rope finger 20 can again be clearly seen.
  • Fig. 18 shows schematically in a further representation, cut in section plane BB, an embodiment of a cable winch 1 according to the invention with tensioning fork 14 according to Fig. 16 .
  • Fig. 19 shows a schematic perspective view of an embodiment of a rope storage winch 170 in combination with a rope winch 1 according to the invention with an open housing 12, 13.
  • the rope 3 'running out of the rope winch 1 is picked up by a rope storage 174, which is driven by a rope storage drive 175.
  • the rope storage drive 175 not only ensures a clean and space-saving winding of the rope, but can also increase the driving force of the rope winch 1, since the running rope 3 'is subjected to a pre-tensioning force that increases the rope force.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pulleys (AREA)

Claims (13)

  1. Treuil à câble continu (1, 100), comprenant une poulie motrice (2, 120) avec une gorge motrice (22) introduite de manière périphérique à sa circonférence pour la réception d'un câble (3, 3') et un agencement de transmission par courroie (60, 160) réalisé en face de la gorge motrice (22) pour la pression entraînée par friction du câble (3, 3') contre la gorge motrice (22), qui comprend un élément sans fin périphérique (4, 140), caractérisé en ce que l'élément sans fin est posé avec un premier brin au moins au-dessus d'éléments d'appui de transmission par courroie (6) et avec un second brin au-dessus de la partie d'entraînement de câble de la circonférence de la poulie motrice (22), dans lequel la poulie motrice (2, 120) et l'agencement de transmission par courroie (60, 160) sont synchronisés de telle sorte les faces de la gorge motrice (22) et de l'agencement de transmission par courroie (60, 160) qui sont prévues pour le contact avec le câble (3, 3') peuvent être déplacées dans la même direction et avec la même vitesse, dans lequel la gorge motrice (22) et la face avant tournée vers la gorge motrice (22) de l'agencement de transmission par courroie (60) qui est réalisée en tant que gorge de pression (50) présente à chaque fois un contour essentiellement complémentaire au profil du câble (3, 3'), dans lequel la pression entraînée par friction du câble (3, 3') contre la gorge motrice (22) s'effectue au moyen de l'agencement de transmission par courroie (60, 160) par le biais d'une partie d'entraînement de câble de la circonférence de la poulie motrice (2, 120), dans lequel le câble (3, 3') est enfoncé dans la gorge motrice (22) par des éléments de pression (5) dès que le câble (3, 3') se trouve dans la gorge motrice (22).
  2. Treuil à câble continu selon la revendication 1, dans lequel l'agencement de transmission par courroie (60, 160) comprend en tant qu'élément sans fin (4, 140) une chaîne à raclettes qui est réalisée en tant que courroie dentée, courroie plate ou agencement de câbles épissés ou comprend ceux-ci.
  3. Treuil à câble continu selon la revendication 2, dans lequel l'agencement de transmission par courroie (60, 160) comprenant la chaîne à raclettes (4, 140) présente des éléments de pression (5) qui sont disposés étroitement côte à côte sur un côté de la chaîne à raclettes (4, 140) et forment la face avant tournée vers la gorge motrice (22) de l'agencement de transmission par courroie (60, 160), dans lequel les éléments d'appui de transmission par courroie et l'élément de couplage à transmission par courroie sont réalisés en tant que pignons à chaîne (6, 9).
  4. Treuil à câble continu selon la revendication 2 ou 3, dans lequel la chaîne à raclettes (4, 140) est réalisée en tant que chaîne large ou en tant que chaîne multiple.
  5. Treuil à câble continu selon la revendication 2, dans lequel la courroie dentée ou la courroie plate présente un profil en coupe transversale tel que le côté tourné vers la gorge motrice (22) de la courroie dentée ou de la courroie plate présente un contour essentiellement complémentaire au profil du câble (3, 3').
  6. Treuil à câble continu selon une des revendications précédentes, dans lequel une synchronisation mécanique entre poulie motrice (2, 120) et agencement de transmission par courroie (60, 160) s'effectue au moyen d'un agencement d'engrenage par une conjugaison de formes de technique d'engrenage, réalisé en tant qu'engrenage à roue dentée ou engrenage à chaîne, ou est réalisée en tant qu'engrenage à courroie.
  7. Treuil à câble continu selon la revendication 6, dans lequel une denture d'entraînement externe (38) et une denture s'engrenant avec celle-ci d'un pignon d'entraînement (46) pouvant être entraîné par un agencement d'entraînement (42) sont prévues pour la synchronisation entre poulie motrice (2) et agencement de transmission par courroie (60), dans lequel l'agencement d'entraînement (42) est prévu en même temps pour l'entraînement de l'élément sans fin (4) par le biais d'un élément de couplage à transmission par courroie (9), dans lequel l'élément de couplage à transmission par courroie (9) et le pignon d'entraînement (46) sont connectés de manière fixe en rotation à l'agencement d'entraînement (42).
  8. Treuil à câble continu selon la revendication 6, dans lequel sont prévus pour la synchronisation entre poulie motrice (120) et agencement de transmission par courroie (160) une denture de transmission par courroie au moins d'un côté (124) de la poulie motrice (120) et des moyens d'engrènement (142) disposés latéralement de la face avant sur l'agencement de transmission par courroie (160) qui sont fournis et disposés de sorte que les moyens d'engrènement (142) s'engrènent dans la denture de transmission par courroie (124) et forment avec la poulie motrice (120) une connexion temporaire par conjugaison de formes dans la région de la circonférence de la poulie motrice (120) dans laquelle la pression entraînée par friction du câble (3, 3') contre la gorge motrice (22) est prévue.
  9. Treuil à câble continu selon une des revendications précédentes, dans lequel l'élément sans fin (4, 140) présente un premier et un second brin, dans lequel le premier brin de l'élément sans fin (4, 140), qui est posé entre un premier élément d'appui de transmission par courroie (6) et un dernier élément d'appui de transmission par courroie (6) au-dessus d'au moins un autre élément d'appui de transmission par courroie (6), et s'étend sur au moins un élément d'appui de transmission par courroie (6) qui est réalisé en tant qu'élément de serrage de transmission par courroie (7) de manière à pouvoir être dévié au moins radialement vers l'axe principal (37) par un dispositif de serrage pour le serrage de l'élément sans fin (4, 140), de sorte que le premier brin et ainsi également le second brin sont amenés sous pression mécanique par l'élément de serrage de transmission par courroie (7) de sorte que le second brin qui s'étend entre le dernier élément d'appui de transmission par courroie (6) et le premier élément d'appui de transmission par courroie (6) est poussé contre la gorge motrice (22) de la poulie motrice.
  10. Treuil à câble continu selon la revendication 9, dans lequel le dispositif de serrage comprend une fourche de serrage (14) et un essieu de serrage (8) logé avec un degré de liberté par translation de manière radialement mobile par rapport à un axe principal (37) de la poulie motrice (2) dans le logement (12, 13), dans lequel l'essieu de serrage (8) est prévu pour la réception d'un des éléments d'appui de transmission par courroie (6), et dans lequel la fourche de serrage (14) est logée sur une extrémité opposée à l'essieu de serrage (8) dans le logement (12, 13) de sorte qu'une force de serrage agit entre le logement (12, 13) et l'essieu de serrage (8) et est transmise à l'essieu de serrage (8).
  11. Treuil à câble continu selon la revendication 10, dans lequel la déviation de l'élément de serrage de transmission par courroie (7) et la force de serrage sont produites par un dispositif à force constante (15).
  12. Treuil à câble continu selon la revendication 11, dans lequel le dispositif à force constante (15) comprend des ressorts à disques avec une caractéristique de ressort dégressive et une course de ressort est choisie de telle sorte qu'une gamme de force presque constante de la caractéristique de ressort est utilisée.
  13. Treuil à câble continu selon une des revendications précédentes, qui est combiné à un treuil de magasin à câble (170) de telle sorte qu'un stockage du câble (3, 3') peut avoir lieu et/ou l'extrémité de câble délestée peut être précontrainte pour augmenter la force motrice du treuil à câble continu (1).
EP18700911.3A 2017-01-27 2018-01-19 Treuil à câble passant Active EP3573918B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017101656.2A DE102017101656A1 (de) 2017-01-27 2017-01-27 Seildurchlaufwinde
PCT/EP2018/051259 WO2018138000A1 (fr) 2017-01-27 2018-01-19 Treuil à câble passant

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CN108717303B (zh) * 2018-09-07 2024-04-05 上海施步新能源科技有限公司 定量输出装置及群控跟踪支架
CN109879190B (zh) * 2019-03-07 2023-12-19 山东万仞机电科技股份有限公司 一种绳索攀爬输运装置
CN116281495B (zh) * 2023-04-12 2024-01-02 杭州欣源电梯部件有限公司 一种电梯轿厢钢丝绳锁定结构
CN116253263B (zh) * 2023-05-15 2023-10-20 河南工学院 一种牵引力恒定的自动排绳电动绞车

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Also Published As

Publication number Publication date
EP3573918C0 (fr) 2023-10-04
DE102017101656A1 (de) 2018-08-02
EP3573918A1 (fr) 2019-12-04
WO2018138000A1 (fr) 2018-08-02

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