EP3573918B1 - Continuous cable winch - Google Patents

Description

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.

mit

• F ₁ maximale Treibkraft
• S ₁ aktuell wirkende Seilkraft durch Last
• S ₂ Vorspannkraft
• α_w Umschlingungswinkel
• µ Reibungszahl zwischen Seil und Rille

ausgedrückt. Es wird deutlich, dass es möglich ist, durch drei Größen die Treibkraft F ₁ zu maximieren. Bei gleicher Vorspannkraft bleibt zunächst nur die Möglichkeit der Maximierung des Umschlingungswinkels und der Reibungszahl. Die Erhöhung des Umschlingungswinkels über 180° bringt das Problem mit sich, dass der ein- und der auslaufende Seilabschnitt ohne Gegenbiegung aneinander vorbeigeführt werden müssen.Rope continuous winches rely on a friction connection between the drive element and the rope. The frictional force caused by the frictional connection must be greater than the maximum cable pulling force to be transmitted. In the prevailing functional principle of a continuous rope winch, the rope runs in the groove of a traction sheave. The relationships between the traction sheave and the rope are expressed in Eytelwein's equation $$S_{}$$$${}_1\le {\mathrm{<figure-callout\; id="1"\; label="F"\; filenames="imgf0007.png"\; state="\{\{state\}\}">F</figure-callout>}}_1=e^{{\mathit{<figure-callout\; id="2"\; label="\mu \alpha \; w\; S"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">\mu \alpha </figure-callout>}}_w}{S}_{}{}_2$$

with

• F ₁ maximum driving force
• S ₁ currently acting rope force due to load
• S ₂ preload force
• α _w wrap angle
• µ Coefficient of friction between rope and groove

expressed. It becomes clear that it is possible to maximize the driving force F ₁ using three variables. With the same preload force, the only option left is to maximize the wrap angle and the coefficient of friction. Increasing the wrap angle above 180° brings with it the problem that the on and off Expiring rope sections must be guided past each other without counter-bending.

Increasing the coefficient of friction offers another way to increase driving force. According to the state of the art, efforts have been made to increase the coefficient of friction through suitable groove materials and appropriate rope constructions. Furthermore, the shape of the groove offers an opportunity to increase the coefficient of friction. In order to achieve a high coefficient of friction, very steep V-grooves are used instead of round grooves in rope winches. The disadvantage of this option is that the rope is very strongly deformed when passing through the rope winch and is therefore subjected to high mechanical stress. This generally leads to increased wear.

Between the rope and the traction sheave in the unworn state, there is line contact with wedge-shaped grooves, which leads to excessive pressure at the contact points. The consequences are high stress on the rope and groove.

To further increase the driving force, 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. According to the publication US 4,555,091 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.

A similar solution is in the publication US 6,247,680 described, which is characterized by a very simple principle for generating driving force. The load is at an upper end of the rope. After the loaded rope end has run into the traction sheave, the rope is additionally pressed against the traction sheave by several pressure rollers. The pressure rollers are connected to each other by several tabs and are thus held in position. A first tab end is connected to the housing. The pressure force depends on the load. It is created by the roller at the incoming rope end. When a load is applied, the pressure rollers are pulled towards the traction sheave. The disadvantage of this solution is that the rope undergoes a total of three bending changes as it passes through the traction sheave. 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. In addition, a V-groove is used, so that this construction also places high stress on the rope in the groove.

Another solution that provides individual pressure rollers is described in the publication US 3,329,406 presented, whereby the winch is based on the principle of a conventional capstan winch with additional pressure rollers and the rope wraps around the traction sheave several times. To make this possible, the traction sheave is designed as a smooth cylinder. The multiple wrapping increases the wrap angle and increases the driving force. The rope is held in position on the traction sheave by pressure rollers and is additionally pressed against it. The pressure rollers are firmly screwed to the housing. The disadvantage of this invention is that the rope is twisted laterally due to the helical winding on the traction sheave. Line contact occurs both between the traction sheave and the rope and between the wedge-shaped grooves of the pressure rollers and the rope. These put a lot of strain on the rope. Furthermore, special measures are necessary to attach the rope; the rope is not pulled in automatically. Since the pressure rollers are firmly screwed, no fluctuations in the rope diameter can be compensated for. It is also not possible to compensate for dimensional deviations that occur, for example, as a result of wear.

Various solutions are known for regulating or adjusting the pressure force acting on the rope. These are in the publications DE 03 60 033 B1 (a cable pull device with traction sheave and automatic cable pressure), EN 10 2012 100 099 A1 (continuous winch ) and EP 0677480 B1 (Compact continuous cable pull device ) shown.

The cable pull device according to the publication EP 03 60 033 B1 has automatic contact pressure regulation. In order to create the necessary frictional connection between the rope and the traction sheave, 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. Depending on the rope force, the traction sheave is pressed more or less strongly against the pressure roller during operation, thus creating a frictional connection. To prevent slipping when the rope forces are very low, 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. Despite 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). Depending on the version, the levers are coupled to one another via a tension spring or are individually connected to the housing using compression springs (reference number 29). In addition, there is a coupling link (reference number 21) between both rollers for guidance. 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. Through the pressure rollers, two line loads that place high stress on the rope act on the rope. The second pressure roller is positioned so that the rope experiences a counter-bending change. This puts a lot of strain on the rope. If the load is jerky, the rope can slip through the traction sheave. The contact force and thus the driving force are linked to fixed geometric conditions. Increasing the contact force is not possible without any problems.

Various solutions provide for lateral, i.e. axial, clamping of the rope instead of the radial pressure of a rope against a traction sheave. Individual clamping jaws or movable disk halves are usually provided. The publications contain examples of this group of solutions DE 518 706 A (drive pulley ), US 4 193 311 A (traction sheave mechanism ), DE 10 2012 110 782 A1 (clamping winch ), AT 359 691 B (traction sheave for a hoist ), DE 26 41 446 C2 (traction sheave for a hoist ), DE 325 438 A (rope pulley ), DE 449 153 A (rope pulley with clamped rope ), DE 636 412 A (cable traction sheave ), DE 429 820 A (two-part pulley ), DE 720 955 A (traction sheave for pull ropes and conveyor chains ), DE 416 051 A (drive pulley ) and DE 284 134 A (cable pulley with clamping jaws displaceably arranged in the cable groove and a stop influencing the clamping jaws ).

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.

In addition, the V-groove and clamping jaws exert line contact on the rope and therefore put a lot of strain on it. Furthermore, with spring-loaded clamping, the clamping force is very limited by the individual, small leaf springs. It can only be increased through considerable additional effort. In addition, 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.

If 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. Furthermore, 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.

In another group of solutions, a passively rotating pressure chain is provided on a section of the traction sheave. With this design, the pressure elements put an additional surface load on the rope. Such a solution is in publication DE 43 30 162 A1 described. However, due to its design, 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 fact that several pressure elements always act on the rope at the same time is rarely the case in practical design, since every production is subject to tolerances and wear cannot be ruled out. V-grooves are also used in this solution, which is why there is also a lot of stress on the rope in the groove.

The publication describes another, similar solution DE 22 01 548 C3 with a traction sheave for unlimited rope passage. In this case, 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. To increase the driving force, the chain is positively driven by the traction sheave. However, 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. By applying the clamping force with the help of individual rollers on the inside of the chain, the pressure on the clamping elements is not constant. As one link after the other passes under the roller, the loaded links alternate. This causes the clamping force and thus also the driving force to fluctuate. At high Conveying speeds result in the possibility of the pressure rollers lifting off, which results in a loss of clamping and driving force. Due to the load-dependent pressure mechanism, there is also a risk of the rope slipping through the traction sheave if the rope is loaded jerkily.

Another principle from this group of solutions is in the publication US 2,628,813 A described. The rope is additionally pressed into a wedge-shaped groove in a traction sheave by a rotating pressure chain. The pressure force is transmitted to it by pressure rollers that act on the inside of the chain. The pressure force depends on the load and is transmitted by a mechanism between the pressure rollers and the anchoring point of the winch. The pressure force represents the reaction force of the rope force generated by the load. The chain runs passively. The disadvantage of this design is that the pressure force depends on the rope force. If there is a jerky load, the rope can slip through the traction sheave. Furthermore, the chain is not driven separately, but is set in motion passively by the friction with the rope. It therefore only serves to apply pressure to the rope and does not provide any drive on the side of the rope facing away from the groove. The friction losses caused by the chain reduce the driving force of the winch. 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. In addition, 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 prior art also offers solutions to avoid the disadvantages of passive pressure means, in particular pressure chains, which entail additional friction losses. These solutions provide for actively driven pressure chains and are in the publications US 3,018,934 and US 2,875,890 described.

The publication US 3,018,934 A describes a winch (title: Windlass, from 1962 ). The proposed solution is for the rope to pass through a traction sheave ( Fig. 1 , reference numeral 50), which, however, is angular on its circumference. In addition to the friction, this should achieve a kind of positive connection between the traction sheave and the rope and increase the driving force. A driven chain (reference number 24) also presses the rope into the groove of the traction sheave. The wrap angle is approximately 180°. The chain is tensioned using a lever (reference number 26) with a torsion spring (reference number 27). 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. In addition, 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. Although 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 publication US 2,875,890 A (title: Windlass, from 1959 ) describes a winch in which the rope is driven exclusively by the friction between two chains ( Figures 1 and 2 , reference numbers 14 and 15). Both chains are driven to do this. The rope runs through the winch with several bends to increase friction. Each bend acts like a slight wrap around a traction sheave that is not present here. The pressure force between the two chains is caused by spindles (reference numbers 27 and 34) and can be regulated by hand. Intermediate springs (reference numbers 28 and 36) compensate for dimensional deviations of the friction partners. The following disadvantages become clear. As it passes through the winch, the rope undergoes two and a half counter-bending cycles, which place considerable strain on the rope. Furthermore, the frictional connection takes place directly between the rope and the chains, so that undefined, point-like touches are the consequences. These cause high pressure on the rope and put considerable strain on it.

The solutions known from the prior art have overall inadequate functional reliability at high loads, put considerable strain on the rope and are often complex to set up.

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.

The object is achieved by 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. According to the invention, 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; This means that 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.

• mit geringer Seilbeanspruchung bei gleichzeitig hoher Treibkraft,
• mit konstanten Klemm- und Treibkräften, unabhängig vom Verschleißzustand der Treibscheibe, des Seils und der Andruckelemente,
• mit hoher Fördergeschwindigkeit,
• mit gleichmäßiger, flächig eingeleiteter Andruckkraft auf 3/4 bzw. 270° des Treibscheibenumfangs (oder mehr, in Sonderfällen bis zu 360°) und mit
• Selbstzentrierung der Andruckelemente auf dem Seil, in radialer als auch axialer Treibscheibenrichtung

fördert.The rope winch according to the invention therefore has a pressure mechanism that protects the rope and which protects the rope

• with low rope stress and high driving force at the same time,
• with constant clamping and driving forces, regardless of the wear condition of the traction sheave, the rope and the pressure elements,
• with high conveying speed,
• with uniform, flat pressure force applied to 3/4 or 270° of the traction sheave circumference (or more, in special cases up to 360°) and with
• Self-centering of the pressure elements on the rope, in both the radial and axial direction of the traction sheave

promotes.

Advantageously, 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.

If 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.

If 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. It is therefore advantageous if 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. In addition to the supporting function, the Hülltrieb coupling element, like the Hülltrieb 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 Hülltrieb support elements are designed as chain wheels, specifically as support chain wheels, the Hülltrieb 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.

According to a further, particularly advantageous embodiment of the invention, 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. the roller toothing, intervene and form a temporary positive connection with the traction sheave in the area of the circumference of the traction sheave, in which the frictional pressure of the rope against the traction goggle is also provided. 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.

Particularly preferred for this embodiment is a continuous cable winch that includes a conveyor chain, but 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 Hülltrieb coupling element is provided, the Hülltrieb coupling element being connected at least in a rotationally fixed manner to an Hülltrieb shaft, driven by the drive arrangement, as the drive is generally referred to below. The Hülltrieb 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. In other applications, 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.

Preferably, 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. In the traction sheave drive arrangement, the drive motor acts on the traction sheave, in the enveloping drive arrangement, the drive motor acts on the enveloping drive and in the direct drive of the endless element, 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. Advantageously, the transmission arrangement is also designed as a gear transmission, as a chain transmission or as a belt transmission.

Particular advantages result from a tensioning device that acts on a Hülltrieb tensioning element and causes tension of the endless element or the entire Hülltrieb arrangement. For this purpose, the endless element has a first and a second strand, the first strand of the endless element being between a first Hülltriebsträgerelement, for example a chain wheel, and a last Hülltrieb support element is placed over at least one further Hülltrieb support element and extends over at least the Hülltrieb tensioning element, an Hülltrieb support element designed for tensioning the endless element. Then 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. As a result, 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. In one or more embodiments, 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. Advantageously, 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.

If the previously described device is in operation, after the rope has run into the round groove of the traction sheave that protects the rope, the rope is almost completely enclosed by the pressure elements as part of the enveloping drive arrangement. The pressure surfaces of the pressure elements, for example designed as pressure grooves or integrated into the endless element, advantageously represent the negative of the rope almost without gaps. In a preferred embodiment of the enveloping drive arrangement, 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. In this case, the traction sheave is toothed and is driven by the drive pinion.

As a result, 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.

In contrast to the prior art, a uniform pressure force acts in the pressure area. This remains the same even if there are dimensional deviations in the rope, traction sheave and pressure element due to manufacturing or wear. The pressing force is preferably generated by a suitable constant force device, such as a disc spring column in practice. For example, disc springs with a strongly degressive characteristic curve or another constant force device in which no drop in force occurs at all are used.

To generate the pressure force, 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. Through the appropriate arrangement of the enveloping drive support elements or chain wheels, the endless element or the conveyor chain can wrap around the circumference of the traction sheave. In an advantageous embodiment of the invention, the rope leaves the traction sheave at an offset of approximately 270° from the entry point. Beforehand, 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. When using a conveyor chain, 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.

In the preferred embodiment of the invention, 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.

If there is no rope in the high-load pressure winch, the pressure elements rest on the traction sheave next to the rope groove and move with the traction sheave. No special tools are required to insert a new rope into the high-load pressure winch. Due to the constant pressure force, a wide variety of ropes can be used in practice. These can be steel or textile fiber ropes. In contrast to the prior art, the different lateral pressure stability of the ropes used does not play a significant role.

Due to its structure, 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.

In contrast to the state of the art, standard and simple identical parts are largely used in the high-load pressure winch. This guarantees robustness and cost-effectiveness. Due to the high tensile force and the extremely low rope wear, 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.

mit

• q_m Andruckstreckenlast
• µ_An Reibungszahl zwischen Seil und Andruckelement
• R Treibscheibenradius

deutlich. Ist die Vorspannkraft S ₂ gleich Null, dann fällt der erste Term weg. Durch die Andruckstreckenlast wird dennoch eine Treibkraft erzeugt.The facts are based on the expanded Eytelwein equation that is valid for high-load pressure winches, as well as the rope continuous winch according to the invention $$F_{}$$$${}_1=e^{{\mathit{\mu \alpha }}_{\mathrm{<figure-callout\; id="2"\; label="w\; S"\; filenames="imgf0001.png,imgf0002.png"\; state="\{\{state\}\}">w</figure-callout>}}}{S}_{}{}_2+q_{m}R\left(e^{{\mathit{\mu \alpha }}_w}-1\right)+q_{m}R\left(e^{{\mu }_{\mathit{At}}{\alpha }_w}-1\right)$$

with

• q _m contact load
• µ _The coefficient of friction between the rope and the pressure element
• R traction sheave radius

clearly. If the preload force S ₂ is zero, then the first term is omitted. The pressure line load still generates a driving force.

In a preferred embodiment of the continuous rope winch according to the invention, 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.

In a further embodiment of the continuous rope winch according to the invention, 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°. This allows high forces to be transferred to the rope. However, it must be ensured that the incoming rope can pass the outgoing rope. For this purpose, 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°. Alternatively, 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.

• Lösung des bisherigen Zielkonflikts zwischen hoher Treibkraft und hoher Seillebensdauer von Seildurchlaufwinden, damit geringere Seilbeanspruchung bei gleichzeitig hoher Treibkraft;
• konstante Klemm- und Treibkräfte, unabhängig vom Verschleißzustand der Treibscheibe, des Seils und der Andruckelemente, damit Vermeidung von Zugkraft- und Klemmkraftschwankungen;
• ermöglicht einen sicheren, störungsfreien Betrieb bei hohen Fördergeschwindigkeiten;
• gleichmäßiger, flächiger Andruck des Seils an die Treibscheibe auf bis zu 3/4 des Treibscheibenumfangs, bei großem Verhältnis von Durchmesser der Treibscheibe zu Seildurchmesser auch bis zu 360° möglich;
• simpler Aufbau durch einfache Komponenten und viele Norm- und Gleichteile;
• Selbstzentrierung der Andruckelemente auf dem Seil, dadurch Ausgleich von Schwankungen des Seildurchmessers sowie Ausgleich von Verschleiß und Fertigungstoleranzen in hohem Maße ohne Klemmkraftschwankung möglich;
• durch Ausgleich unterschiedlicher Querdruckstabilitäten der eingesetzten Seile ist es möglich, ohne Umrüstung sowohl textile Faserseile als auch Stahlseile einzusetzen;
• Fertigungsabweichungen der Rundheit der Treibscheibe haben keine negativen Auswirkungen auf die Pressung des Seils auf der Treibscheibe und auf die Treibkraft, dadurch wirtschaftliche Fertigung und rentable Produkte;
• keine gesonderten Werkzeuge zum Einlegen des Seils erforderlich;
• problemlose Skalierbarkeit von Treibkraft, Seil- und Treibscheibendurchmesser für unterschiedlichste Anwendungen;
• Steigerung der Andruckkraft durch breitere Hülltriebanordnungen, also vor allem Ketten oder Riemen, problemlos möglich und
• unempfindlich gegen Verunreinigungen und damit Gewährleistung eines hohen Maßes an Betriebssicherheit und Verfügbarkeit in einem breiten Einsatzspektrum.

The continuous cable winch according to the invention has the following advantages compared to the prior art:

• Resolution of the previous conflict of objectives between high driving force and long rope service life of continuous rope winches, thus lower rope stress with high driving force at the same time;
• constant clamping and driving forces, regardless of the state of wear of the traction sheave, the rope and the pressure elements, thus avoiding fluctuations in tensile force and clamping force;
• enables safe, trouble-free operation at high conveying speeds;
• Even, flat pressure of the rope on the traction sheave up to 3/4 of the circumference of the traction sheave, with a large ratio of the diameter of the traction sheave to the rope diameter, up to 360° possible;
• simple structure thanks to simple components and many standard and identical parts;
• Self-centering of the pressure elements on the rope, thereby compensating for fluctuations in the rope diameter as well as compensating for wear and manufacturing tolerances to a large extent without fluctuations in clamping force;
• By compensating for different lateral pressure stability of the ropes used, it is possible to use both textile fiber ropes and steel ropes without retrofitting;
• Manufacturing deviations in the roundness of the traction sheave have no negative impact on the pressure of the rope on the traction sheave and on the driving force, thus economical production and profitable products;
• no special tools required to insert the rope;
• problem-free scalability of driving force, rope and traction sheave diameters for a wide range of applications;
• Increasing the pressure force is easily possible thanks to wider envelope drive arrangements, especially chains or belts
• insensitive to contamination and thus guarantees a high degree of operational safety and availability in a wide range of applications.

The design of chains and belts has been carefully researched and standardized. Reliable maintenance intervals for the rope winches according to the invention can thus be defined.

• Fig. 1: schematisch in perspektivischer Darstellung mit geöffnetem Gehäuse und geöffnetem Seilfinger eine Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde;
• Fig. 2: ein Detail der erfindungsgemäßen Seildurchlaufwinde aus Fig. 1;
• Fig. 3: schematisch in quergeschnittener Darstellung eine Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde;
• Fig. 4: schematisch in längsgeschnittener Darstellung eine Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde;
• Fig. 5: ein Detail der erfindungsgemäßen Seildurchlaufwinde aus Fig. 4;
• Fig. 6: schematisch in perspektivischer Darstellung mit geöffnetem Gehäuse und geschlossenem Seilfinger eine Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde;
• Fig. 7: die erfindungsgemäße Seildurchlaufwinde aus Fig. 6 mit geschlossenem Gehäuse;
• Fig. 8: schematisch ein Detail einer Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde in geschnittener Darstellung;
• Fig. 9: schematisch in Seitenansicht eine Ausführungsform eines Glieds einer Förderkette mit Andruckelement;
• Fig. 10: schematisch in perspektivischer Darstellung eine Ausführungsform eines Glieds einer Förderkette mit Andruckelement;
• Fig. 11: schematisch in perspektivischer Darstellung mit geöffnetem Gehäuse und geschlossenem Seilfinger eine weitere Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde;
• Fig. 12: ein Detail der erfindungsgemäßen Seildurchlaufwinde aus Fig. 11;
• Fig. 13: eine Ausführungsform eines Glieds einer Förderkette mit Andruckelement in perspektivischer Ansicht als ein Detail der erfindungsgemäßen Seildurchlaufwinde aus Fig.11 ;
• Fig. 14: schematisch in längsgeschnittener Darstellung der Ausführungsform der erfindungsgemäßen Seildurchlaufwinde aus Fig. 11;
• Fig. 15: schematisch ein Detail der Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde aus Fig. 11 in geschnittener Darstellung;
• Fig. 16: schematisch in Seitenansicht mit geschlossenem Gehäuse eine Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde mit Spanngabel;
• Fig. 17: schematisch in geschnittener Darstellung der Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde mit Spanngabel gemäß Fig. 16;
• Fig. 18: schematisch in einer weiteren geschnittenen Darstellung der Ausführungsform einer erfindungsgemäßen Seildurchlaufwinde mit Spanngabel gemäß Fig. 16 und
• Fig. 19: schematisch in perspektivischer Darstellung eine Ausführungsform einer Seilspeicherwinde in Kombination mit einer erfindungsgemäßen Seildurchlaufwinde mit geöffnetem Gehäuse.

The invention is explained in more detail below based on the description of exemplary embodiments and their representation in the associated drawings. Show it:

• Fig. 1 : schematically in a perspective view with an open housing and an open rope finger, an embodiment of a rope winch according to the invention;
• Fig. 2 : a detail of the cable winch according to the invention Fig. 1 ;
• Fig. 3 : Schematic cross-sectional representation of an embodiment of a rope winch according to the invention;
• Fig. 4 : schematically a longitudinal sectional view of an embodiment of a rope winch according to the invention;
• Fig. 5 : a detail of the cable winch according to the invention Fig. 4 ;
• Fig. 6 : schematically in a perspective view with the housing open and the rope finger closed, an embodiment of a rope winch according to the invention;
• Fig. 7 : the rope winch according to the invention Fig. 6 with closed housing;
• Fig. 8 : schematically a detail of an embodiment of a cable winch according to the invention in a sectional view;
• Fig. 9 : schematic side view of an embodiment of a link of a conveyor chain with a pressure element;
• Fig. 10 : schematically a perspective view of an embodiment of a link of a conveyor chain with a pressure element;
• Fig. 11 : schematically in a perspective view with the housing open and the rope finger closed, a further embodiment of a rope winch according to the invention;
• Fig. 12 : a detail of the cable winch according to the invention Fig. 11 ;
• Fig. 13 : An embodiment of a link of a conveyor chain with a pressure element in a perspective view as a detail of the cable winch according to the invention Fig.11 ;
• Fig. 14 : schematically a longitudinal sectional representation of the embodiment of the cable winch according to the invention Fig. 11 ;
• Fig. 15 : Schematic of a detail of the embodiment of a rope winch according to the invention Fig. 11 in sectional view;
• Fig. 16 : Schematic side view with closed housing of an embodiment of a cable winch according to the invention with a tension fork;
• Fig. 17 : Schematic sectional representation of the embodiment of a cable winch according to the invention with a tension fork Fig. 16 ;
• Fig. 18 : schematically in a further sectional representation of the embodiment of a cable winch according to the invention with a tension fork according to Fig. 16 and
• Fig. 19 : Schematic perspective view of an embodiment of a cable storage winch in combination with a cable winch according to the invention with an open housing.

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. As soon as the rope 3, 3 'is in the driving goggle 22, it is pressed into the driving goggle 22 by pressure elements 5. 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'. In addition, 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. As a result, 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.

In addition, 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. In addition to the drive pinion 46, 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. In addition, 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.

For this purpose, 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. In addition shows 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. It can also be seen how 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. In contrast to those described previously Figures 1 to 5 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 . In the embodiment shown, 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. As an alternative to the embodiment shown, external teeth would also be possible.

A conveyor chain 140 as an endless element of an envelope drive arrangement 160, on the other hand, 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. Also shown are the pressure elements 5 and the rope 3, 3`. 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.

Reference symbol list

1, 100

Rope winch

2, 120

traction sheave

3,

rope (loaded)

3'

Rope (relieved)

4, 140

Conveyor chain, endless element

5

pressure element

6

Support chain wheel, enveloping drive support element, chain wheel

7

Tensioning chain wheel, enveloping drive tensioning element, chain wheel

8th

Tension axis

9

Envelope drive coupling element, drive chain wheel, chain wheel

10

Bearing sprocket

11

Axle sprocket

12

Housing, housing part (first half)

13

Housing, housing part (second half)

14

Clamping fork

15

Constant force device, spring arrangement, disc spring

17, 17'

Mother

19

Clamping fork abutment

20

Rope fingers

22

driving goggles

24

gearing

26

Ball bearing traction sheave

30

steering

37

main axis

38

External drive gearing

40

frame

42

Motor, drive, drive arrangement

46

drive sprocket

48

drive sprocket

50

pressure groove

60, 160

Sheath shoot arrangement

122

Internal drive gearing

124

Envelope gearing, roller gearing

142

Engagement means, drive roller

170

Rope storage winch

174

Rope storage

175

Rope storage drive

Claims (13)

1. A continuous cable winch (1, 100), comprising a drive sheave (2, 120) with a drive groove (22) formed along its circumference for receiving a cable (3, 3') and a flexible drive assembly (60, 160) formed opposite the drive groove (22) for frictionally pressing the cable (3, 3') against the drive groove (22), which flexible drive assembly comprises a revolving continuous element (4, 140), characterized in that the continuous element is laid with a first side at least over flexible drive support elements (6) and with a second side over the cable-driving part of the circumference of the drive sheave (22), wherein the drive sheave (2, 120) and the flexible drive assembly (60, 160) are synchronized such that those surfaces of the drive groove (22) and the flexible drive assembly (60, 160) which are provided for contact with the cable (3, 3') are movable in a same direction and at a same speed, wherein the drive groove (22) and the front surface of the flexible drive assembly (60) facing the drive groove (22), which is configured as a pressure groove (50), each have a contour essentially complementary to the profile of the cable (3, 3'), wherein frictionally pressing the cable (3, 3') against the drive groove (22) is effected by means of the flexible drive assembly (60, 160) via a cable-driving part of the circumference of the drive sheave (2, 120), wherein the cable (3, 3') is pressed into the drive groove (22) by pressure elements (5) as soon as the cable (3, 3') is located in the drive groove (22).
2. The continuous cable winch according to claim 1, wherein the flexible drive assembly (60, 160) comprises as a continuous element (4, 140) a conveyor chain or is configured as or comprises a toothed belt, a flat belt, or an arrangement of spliced cables.
3. The cable drive winch according to claim 2, wherein the flexible drive assembly (60, 160) comprising the conveyor chain (4, 140) has pressure elements (5) which are arranged close to one another on one side of the conveyor chain (4, 140) and form the front surface of the flexible drive assembly (60, 160) facing the drive groove (22), wherein the flexible drive support elements and the flexible drive coupling element are configured as sprockets (6, 9).
4. The continuous cable winch according to claim 2 or 3, wherein the conveyor chain (4, 140) is designed as a wide chain or as a multiple chain.
5. The continuous cable winch according to claim 2, wherein the toothed belt or the flat belt have such a cross-sectional profile that the side of the toothed belt or the flat belt facing the drive groove (22) has a contour essentially complementary to the profile of the cable (3, 3').
6. The continuous cable winch according to any one of the preceding claims, wherein a mechanical synchronization between the drive sheave (2, 120) and the flexible drive assembly (60, 160) is achieved by means of a gearing assembly through a gearing-effected positive locking, implemented as a toothed gearing or as a chain gearing, or is implemented as a belt drive.
7. The continuous cable winch according to claim 6, wherein an external drive toothing (38) and a toothing of a drive pinion (46) drivable by a drive assembly (42), which engages the external drive toothing, are provided for synchronization between the drive sheave (2) and the flexible drive assembly (60), wherein the drive assembly (42) is also provided for driving the continuous element (4) via a flexible drive coupling element (9), wherein the flexible drive coupling element (9) and the drive pinion (46) are connected to the drive assembly (42) in a co-rotating manner.
8. The continuous cable winch according to claim 6, wherein an at least one-sided flexible drive toothing (124) of the drive sheave (120) and engagement means (142) arranged laterally of the front surface on the flexible drive assembly (160) are provided for synchronization between the drive sheave (120) and the flexible drive assembly (160), and are designed and arranged such that the engagement means (142) engage in the flexible drive toothing (124) and form a temporary positive connection with the drive sheave (120) in the region of the circumference of the drive sheave (120) in which the cable (3, 3') is frictionally pressed against the drive groove (22).
9. The continuous cable winch according to any one of the preceding claims, wherein the continuous element (4, 140) has a first and a second side, wherein the first side of the continuous element (4, 140), which is laid between a first flexible drive support element (6) and a last flexible drive support element (6) over at least one further flexible drive support element (6), extends over at least one flexible drive support element (6) which is configured as a flexible drive tensioning element (7) deflectable at least radially to the main axis (37) by a tensioning device for tensioning the continuous element (4, 140), so that the first side and thus also the second side are put under mechanical tension by the flexible drive tensioning element (7), so that the second side, which extends between the last flexible drive support element (6) and the first flexible drive support element (6), is pressed against the drive groove (22) of the drive sheave.
10. The cable drive winch according to claim 9, wherein the tensioning device comprises a tensioning fork (14) and a tensioning axle (8) mounted in the housing (12, 13) radially movable with a translational degree of freedom with respect to a main axis (37) of the drive sheave (2), wherein the tensioning axle (8) is provided for receiving one of the flexible drive support elements (6), and wherein the tensioning fork (14) is mounted in the housing (12, 13) at an end opposite the tensioning axle (8) so that a tensioning force acts between the housing (12, 13) and the tensioning axle (8) and is transmitted to the tensioning axle (8).
11. The continuous cable winch according to claim 10, wherein the deflection of the flexible drive tensioning element (7) and the tensioning force are caused by a constant force device (15).
12. The continuous cable winch according to claim 11, wherein the constant force device (15) comprises disc springs with a degressive spring characteristic and a spring travel is selected such that a nearly constant force range of the spring characteristic is used.
13. The continuous cable winch according to any one of the preceding claims, which is combined with a cable storing winch (170) such that the cable (3, 3') can be stored and/or the relieved cable end can be pre-tensioned to increase the driving force of the continuous cable winch (1).

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