EP3573918A1

EP3573918A1 - Continuous cable winch

Info

Publication number: EP3573918A1
Application number: EP18700911.3A
Authority: EP
Inventors: Paul Schumann; Thorsten Schmidt; Thomas Leonhardt
Original assignee: Technische Universitaet Dresden
Current assignee: Planeta-Hebetechnik GmbH
Priority date: 2017-01-27
Filing date: 2018-01-19
Publication date: 2019-12-04
Anticipated expiration: 2038-01-19
Also published as: WO2018138000A1; EP3573918B1; EP3573918C0; DE102017101656A1

Abstract

The invention relates to a continuous cable winch (1), comprising a traction sheave (2) having a traction groove (22) around the perimeter for receiving a cable (3, 3'), and a belt drive assembly (60) which is opposite the traction groove (22) on a cable-driving part of the perimeter of the traction sheave (2) for frictionally pressing the cable (3, 3') against the traction groove (22), and which has a circulating continuous element (4) that is placed on belt drive support elements (6) with a first side and on the cable-driving part of the perimeter of the traction sheave (22) with a second side, wherein the traction sheave (2) and the belt drive assembly (60) are synchronised in such a way that the surfaces of the traction groove (22) and belt drive assembly (60), which are provided for making contact with the cable (3, 3'), can be moved in the same direction and at the same speed. According to the invention, the traction sheave (2) having the traction groove (22) and the front surface of the belt drive assembly (60) pointing towards the traction groove (22) and having a pressure groove (50) each comprise a contour that substantially complements the profile of the cable (3, 3').

Description

Cable winch

The invention relates to a rope pulley, comprising a traction sheave with a circumferentially introduced at its periphery drive groove for receiving a rope and opposite the drive groove in the region of a rope-driving part of the circumference of the traction sheave for frictional pressure of the rope against the drive groove formed Hülltriebanordnung, the circulating endless element which is placed with a first strand at least via Hülltriebstützelemente and with a second strand over the cable-driving part of the circumference of the traction sheave, wherein the traction sheave and the Hülltriebanordnung are synchronized in such a way that those surfaces of the drive groove and Hülltriebanordnung that is in contact with the rope are provided, are movable in the same direction and at the same speed.

Rope pulleys are used in numerous applications. Especially in the field of small goods, facade and maintenance lifts they are used. In addition, there are applications on construction sites in which rope traction winches are used as traction means for temporarily moving, moving or holding loads. Rope winches are based on a frictional connection between the drive element and the rope. The frictional force caused by the frictional engagement must be greater than the maximum tensile force to be transmitted. In the prevailing principle of operation of a rope winch rope runs in the groove of a traction sheave. The relationships between the traction sheave and the rope are in the equation of Eytelwein

S ₁ <F ₁ = S ₂ with

F ₁ maximum driving force

5 ₁ currently acting cable force due to load

5 ₂ preload force

a _w wrap angle

μ friction coefficient between rope and groove expressed. It becomes clear that it is possible to maximize the driving force F ₁ by three variables. With the same preload force initially only the possibility of maximizing the wrap angle and the coefficient of friction remains. The increase of the wrap angle over 180 ° involves the problem that the on and the expiring rope section without opposing bending must be passed to each other.

Increasing the coefficient of friction offers another possibility for increasing the driving force. Efforts have been made in the prior art to increase the coefficient of friction by suitable grooved materials and corresponding rope constructions. Furthermore, the shape of the groove offers a possibility for increasing the coefficient of friction. In order to achieve a high coefficient of friction, very steep V-grooves are used in rope-passing winches instead of round grooves. The disadvantage of this possibility is that the rope is very much deformed during the passage through the cable winch and thus mechanically highly stressed. This generally leads to increased wear.

Between the rope and the traction sheave in the unworn state takes place with wedge-shaped grooves a line contact, which leads to an excessive pressure at the contact points. Heavy use of rope and groove are the consequences.

To further increase the driving force, the rope is additionally pressed by pressure elements in the groove. These pressure elements are usually designed as rollers or clamping mechanisms that load the rope with another pressure point in line contact. For this purpose, various solutions are known, which act on the rope at one or more locations. A solution with a strong localized action on the rope is shown in US Pat. No. 4,706,940, wherein at least one pressure roller presses the rope into a very steep wedge groove and causes corresponding wear.

An improved embodiment provides a greater part of the circumference of a traction sheave for the pressure to which the load is distributed. According to the document US 4,555,091 a variant is provided in which by a plurality of rollers which are interconnected by standing chain links, the rope is pressed against the traction sheave. Each roller touches the rope, however, by a line contact and claimed thereby also very high.

A similar solution is described in the document US Pat. No. 6,247,680, which is characterized by a very simple principle for driving force generation. The load is at an upper end of the rope. After running in the loaded rope end on the Driving pulley, the rope is additionally pressed by several pinch rollers to the traction sheave. The pinch rollers are connected by several tabs and are held in position. A first tab end is connected to the housing. The pressure force is load-dependent. It is generated by the roller at the incoming rope end. When a load is acting, the pressure rollers are used on the traction sheave. The disadvantage of this solution that the rope undergoes a total of three bending change when passing through the traction sheave. The bending radii on the pinch rollers are very small in relation to the rope diameter. There is a significant rope bending stress. The pinch rollers touch the rope by a line load and press this in a again the rope high-stressing V-groove. Due to the load-dependent pressure force, it can also lead to slippage of the rope under jerky load. In addition, a V-groove is used, so that even with this construction, a high stress of the rope in the groove occurs.

Another solution, which provides individual pressure rollers is presented in the document US 3,329,406, the winch is based on the principle of a conventional capstan with additional pinch rollers and the rope wraps around the traction sheave several times. To make this possible, the traction sheave is designed as a smooth cylinder. Due to the multiple wrapping, the wrap angle is increased and the driving force is increased. By pressing rollers, the rope is held on the traction sheave in position and additionally pressed against this. The pressure rollers are firmly screwed to the housing. A disadvantage of this invention is that the rope is laterally twisted by the helical winding on the traction sheave. Line contacts occur between the traction sheave and the rope as well as between the wedge-shaped grooves of the pinch rollers and the rope. These strain the rope very high. Furthermore, separate measures are necessary for placing the rope, the rope is not pulled in automatically. Since the pressure rollers are screwed tight, no fluctuations in the rope diameter can be compensated. Also, the compensation of deviations that occur, for example, as a result of wear is not possible.

To regulate or adjust the force acting on the rope pressure force various solutions are known. These are in the publications DE 03 60 033 B1 (a cable pulling device with traction sheave and automatic Seilanpressung), DE 10 2012 100 099 A1 (continuous winch) and EP 0677480 B1 (compact continuous cable device) shown.

The cable pulling device according to document EP 03 60 033 B1 has an automatic contact pressure regulation. In order to produce the necessary frictional engagement between cable and traction sheave, the traction sheave is mounted on a movable carriage. This sits in a rigid housing to which the pinch roller (reference numeral 4) is attached. Depending on the cable force, the traction sheave is pressed more or less strongly against the pinch roller during operation and so the frictional connection is produced. In order to avoid slippage at very low rope forces, a spring is additionally attached to the traction sheave. This maintains a minimum bias. A disadvantage of this variant is that the rope high-stress line load acts on the rope by the pinch roller. Despite the high pressure of the pressure roller, the driving force remains low. Despite the biasing device there is a risk of slipping of the rope through the traction sheave.

Document DE 10 2012 100 099 A1 describes a continuous winch comprising a traction sheave (reference numeral 4) mounted in a rigid housing (reference numeral 2) on which a rope (reference numeral 3) runs, which is driven by a pressure roller (reference numerals 8, 9). is pressed onto the traction sheave. The pressure rollers are mounted on movable levers (reference numerals 13 and 14). Depending on the design, the levers are coupled to one another via a tension spring or individually connected to the housing by compression springs (reference numeral 29). In addition, there is a coupling member (reference numeral 21) between the two roles to guide. The principle of the proposed continuous winch provides that under load standing rope end (reference L) deflects the pressure roller of the respective side and thus presses the other role to the traction sheave to increase the frictional engagement between the rope and the traction sheave. The pressure force behaves proportionally to the cable force. The symmetrical design enables the lifting operation at both ends of the rope. The disadvantage of this construction are high pressures between pinch roller and rope. Due to the pinch rollers, only one line load is applied to the rope. In addition, the rope undergoes one and a half counterbends when passing through the winch, which also stress the rope. The risk of slipping of the rope by the traction sheave with jerky load is also here. A scaling of the principle is not feasible, since the driving forces are firmly coupled to geometric conditions.

The compact continuous cable device according to document EP 06 77 480 B1 generates a load-dependent contact pressure. The cable (reference numeral 2) is here pressed by rollers (reference numeral 4) against a traction sheave (reference numeral 1) to produce an additional frictional engagement. The contact force can be applied via the cable force or a permanently installed spring. If the contact force is to be generated via the cable force, a tie rod (reference A) must be firmly connected to an anchoring point (reference 5). The tie rod then presses the rollers against the traction sheave with a force proportional to the rope force. Alternatively, however, the tie rod can apply the contact force with a spring mounted between the armature end and the housing of the continuous winch. Due to the pinch rollers, two line loads of high stress act on the rope. The second pinch roller is positioned so that the rope undergoes a reverse bending change. This claimed the rope high. With jerky load, the rope can slip through the traction sheave. The contact force and thus the driving force are coupled to fixed geometric conditions. An increase in the contact pressure is not easily possible.

Different solutions provide instead of the radial pressure of a rope against a traction sheave before a lateral, ie axial clamping of the rope. In this case, individual jaws or movable disc halves are usually provided. Examples of this group of solutions include the documents DE 518 706 A (drive pulley), US 4,193,311 A (traction sheave mechanism), DE 10 2012 1 10 782 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 (pulley), DE 449 153 A (pulley with clamped rope), DE 636 412 A (rope friction pulley), DE 429 820 A (two-part pulley), DE 720 955 A (traction sheave for traction cables and conveyor chains), DE 416 051 A (drive sheave) and DE 284 134 A (sheave with jaws displaceably arranged in the rope groove and a stop influencing the jaws).

The lateral clamping, which is to be solved in the rope run in permanent change and to fix again, usually requires a higher expenditure on equipment and is therefore relatively expensive, maintenance-intensive and susceptible to wear. In addition, wedge groove and jaws exert line contact on the rope and thus stress it up. Furthermore, with spring-loaded clamping, the clamping force is very limited by the individual, small leaf springs. It can only be increased by considerable extra effort. In addition, the clamping mechanism is sensitive to manufacturing deviations and dimensional and shape changes due to wear. These factors greatly affect the clamping and pulling force. The correct position between jaw and 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 conveyor speeds, there is the danger that the clamping mechanism can not open fast enough due to the inertia and the rope is torn out of this.

If the clamping and opening of the traction sheave is done in principle by tilting at least one traction sheave half, the rope is clamped only on a very short section of the traction sheave circumference. Due to the principle, no larger wrap angles than 180 ° are possible. Otherwise, the clamp could not work because the axial clamping forces would cancel. In case of segmentation of the traction sheave, there is only one line contact to the rope. The rope stress is then significant. A simple scaling of the principle is not possible. The clamping and thus the driving force of the proposed solution are coupled to fixed geometric relationships. With a jagged undercut there is a risk of pinching individual rope wires. In this case, the driving force is no longer given. Furthermore, the traction sheave is sensitive to dirt. Dirt particles in the groove undercut, the driving force is no longer given. For individual solutions deviations in the nominal dimensions of rope, groove lining and jaws can be compensated only to a small extent. Individual elements do not carry then. The disadvantage is usually the high number of very specific parts to be manufactured.

In another group of solutions, a passively circulating pressure chain is provided on a section of the traction sheave. With this construction, the pressure elements cause an additional load on the rope. Such a solution is described in the document DE 43 30 162 A1. The pressure chain affects the design but only on a very short section of the traction sheave on the rope. There is no uniform, area pressure, so there is no uniform surface load. Manufacturing deviations and wear of the kidney-shaped chain roller conveyor can lead to deviations of the pressure height. In the worst case, not several pressure elements press the rope into the groove, but only the furthest protruding. The same effect occurs in manufacturing deviations of the groove. That always several pressure elements act on the rope at the same time, is in the practical embodiment rather rarely the case, since each production is tolerant and also verscheiss can not be excluded. Also in this solution, grooved grooves are used, so there is also a high stress on the rope in the groove.

Another similar solution describes the document DE 22 01 548 C3 with a traction sheave for unlimited rope run. In this, the rope located on the traction sheave is additionally pressed by individual members of a circulating pressure chain on the traction sheave. On the chain links Andruckelemente are attached, which correspond to the negative of the rope on the traction sheave. As a result, the contact area between the pressure element and the rope is large. The chain itself runs loosely around mounted in the housing guide rails. The pressure force is generated by a lever mechanism. It is transferred by rolling on the chain inside. The clamping force itself is load-dependent. It is generated by a pulley acting in the loaded cable section. A spring maintains a minimum biasing force. To strengthen the driving force, the chain is positively driven by the traction sheave. However, the construction is characterized by the following disadvantages: It will find when passing through the rope a total of three bends in the loaded rope section even a reverse bend instead. Each bending change is associated with an increased rope stress, because Gegenbiegewechsel on narrow sections stress the rope particularly strong. The pulley in the incoming cable area also has a very small bending radius, which also causes a high rope stress. Another, particularly serious problem is that the rope is pressed only on a very short portion of the traction sheave circumference by the pressure elements of the chain, since the design of the pressure mechanism allows no further wrap. The driving force remains relatively low despite high pressure forces. By applying the clamping force by means of individual rollers on the chain inside the pressure of the clamping elements is not constant. When driving through one link after the other under the role, the loaded links alternate. As a result, the clamping force and thus the driving force fluctuate. At high Conveying speeds consists in the consequence of the possibility of lifting the pressure rollers, a clamping and driving force loss is the result. Due to the load-dependent pressure mechanism there is also the risk of slipping of the rope through the traction sheave with jerky rope loading.

Another principle of this group of solutions is described in document US 2 628 813 A. The rope is additionally pressed by a circulating pressure chain in a turn wedge-shaped groove of a traction sheave. The pressure force is transmitted by pressure rollers acting on the inside of the chain on this. The pressing force is dependent on the load and is transmitted by a mechanism between pinch rollers and anchor point of the winch. The pressure force represents the reaction force of the cable force generated by the load. The chain runs passively with. A disadvantage of this design is that the pressing force is dependent on the cable force. With jerky load, therefore, the rope can slip through the traction sheave. Furthermore, the chain is not driven separately, but passively set by the frictional engagement with the rope in motion. It thus serves only the pressure of the rope and provides no drive on the side facing away from the groove of the rope. The friction losses through the chain reduce the driving force of the winch. The Hauptandruckbereich is, mainly due to the design of the pressure mechanism, in relation to the traction sheave circumference very low. The pressure chain follows in its profile not the outer rope contour, it instead touches the rope with a flat surface and claimed by the line contact considerably. In addition, the rope is pressed into a steep V-groove, which also leads to high rope loads. The loaded members alternate when passing through one link to the other under the role. As a result, the clamping and driving force fluctuate. At high conveyor speeds there is a risk of lifting the pinch rollers. A clamping and driving force loss are the consequences. Solutions are also offered in the state of the art in order to avoid the disadvantages of passive pressure means, in particular pressure chains, which entail additional friction losses. These solutions provide actively driven nip chains and are described in US Pat. Nos. 3,018,934 and 2,875,890. The document US 3 018 934 A describes a winch (title: Windlass, from the year 1962). The proposed solution provides that the rope when passing through the winch a traction sheave (Fig. 1, reference numeral 50) rotates, but which is formed angularly at its periphery. This should be achieved in addition to the friction a kind of positive engagement between the traction sheave and rope and the driving force can be increased. A driven chain (reference numeral 24) additionally presses the rope into the groove of the traction sheave. The wrap angle is approximately 180 °. The tensioning of the chain is achieved by a lever (reference numeral 26) with leg spring (reference numeral 27). Before leaving the rope to the right side, the rope wraps around another traction sheave at approximately 80 ° wrap angle (reference numeral 32). The solution is characterized by the following disadvantages. There are a total of one and a half Gegenbiegewechsel when passing through the rope by the winds on the rope. This takes up the rope very high. In addition, the diameter of the traction sheaves in relation to the rope diameter is very low. In addition, this causes a very high rope stress every time a bend is changed. Of the two traction sheaves only a very small part of the traction sheave circumference is used for the frictional engagement. Although the proposed device is material-intensive, the usable driving force remains low. The square traction sheave also stresses the rope strongly by the line touches transverse to the rope longitudinal axis. Furthermore, the chain lies directly on the rope. The bushes and lugs of the chain touch the rope so that line and point loads arise and additionally stress the rope considerably.

The document US 2 875 890 A (title: Windlass, 1959) describes a winch, in which the drive of the rope exclusively by the frictional engagement between two chains (Figures 1 and 2, reference numerals 14 and 15) is formed. Both chains are driven to it. The cable runs under several bends through the winch to increase the frictional engagement. Each bend acts like a slight wrap around a traction sheave that does not exist here. The pressing force between both chains is caused by spindles (reference numerals 27 and 34) and is manually adjustable. Intermediate springs (reference numerals 28 and 36) cause a balance of deviations of Reibschlusspartner. The following disadvantages become clear. The rope undergoes two and a half Gegenbiegewechsel when passing through the wind, which strain the rope considerably. Furthermore, the frictional engagement takes place directly between the rope and the chains, so that undefined point-like touches are the consequences. These cause high pressures on the rope and stress it considerably.

The solutions known from the prior art have overall an insufficient reliability at high loads, stress the rope considerably and are often also complex in construction.

The object of the invention is to provide a winch, which achieves a uniform, flat applied Andruckraft at high constant driving force even at high cable speeds and regardless of the load at the expiring end of the rope and minimizes the rope wear.

The object is achieved by a rope winch, comprising a

Traction sheave shaft, which is provided in particular for driving or driven, with a traction sheave with a peripheral circumferential drive groove. The traction sheave shaft is at least rotatably connected to the traction sheave. The peripheral circumferential drive groove serves to receive a rope. A relative to the drive groove, for example, on a rope-driving part of the circumference of the traction sheave arranged Hülltriebanordnung is designed for frictional pressure of the rope against the drive groove. The Hülltriebanordnung comprises a revolving endless element which is placed with a first strand on Hülltriebstützelemente and with a second strand on the cable driving part of the circumference of the traction sheave. The traction sheave and the hull drive arrangement are synchronized in such a way that those surfaces of the drive groove and Hülltriebanordnung are movable in the same direction and at the same speed, which are provided for contact with the rope. According to the invention, the traction sheave with the drive groove and the front surface of the hull drive arrangement with a pressure groove pointing toward the drive groove each have a contour that is substantially complementary to the profile of the rope, so that the rope is caught on a large part of its lateral surface; As a result, profile cables are also included in the invention. The frictional pressure of the rope against the drive groove by means of the Hülltriebanordnung via a rope-driving part of the circumference of the traction sheave.

The envelope drive arrangement comprises at least one endless element and pressure elements connected to or formed in one piece from the endless element. Necessary for the function of the Hülltriebanordnung are the Endloselement supporting Hülltriebstützelemente that allow a circulation of the endless element. 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 an endless element, as described below, the envelope drive support elements are designed, for example, as sprockets. The Hülltriebstützelemente include according to the invention but also other means that support the circulation of the endless element, such. B. a roller conveyor or even a slide. The rope traction winch according to the invention thus has a rope-gentle pressure mechanism, which is the rope

• with low cable load and high driving force,

• with constant clamping and driving forces, regardless of the state of wear of the traction sheave, the rope and the pressure elements,

• with high conveying speed,

• with uniform contact force applied flat to 3/4 or 270 ° of the traction sheave circumference (or more, in special cases up to 360 °) and with

• Promotes self-centering of the pressure elements on the rope in radial as well as axial traction sheave direction.

Advantageously, the envelope drive arrangement as endless element does not only comprise 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 spliced ropes is designed with a rope for a deep rope groove or more, connected to the lateral surface ropes. If the endless element of the Hülltriebanordnung designed as a toothed belt or flat belt, the toothed belt or the flat belt on such a cross-sectional profile, that the driving groove toward side facing the toothed belt or flat belt has a profile of the rope substantially complementary contour. 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 in other types of endless element in this. This applies, for example, timing belt, which then have on one side a profile that takes over the function of the pressure elements. It is thus advantageous if the envelope drive arrangement comprising the conveyor chain has pressure elements which are arranged continuously on one side of the conveyor chain and form the front surface facing the drive groove with a quasi-continuous pressure groove forming the envelope drive arrangement, the envelope drive support elements and the envelope drive coupling element being sprockets, namely as Stützkettenrad or Tre ib chain nrad, are formed. The Hülltriebkoppelelement has in addition to the support function, as well as the Hülltriebstützelemente also, the function of transmitting force and movement of a drive assembly, for. As a motor with drive shaft, on the endless element. Thus, if the Hülltriebstützelemente designed as sprockets, especially as support sprockets, the Hülltriebkoppelelemente are designed as a drive sprockets.

As favorable for the reliability, a conveyor chain, designed as a skew-capable chain has proven. Advantageously, the conveyor chain is designed as a wide chain or as a multiple chain. With these versions, a particularly high driving force is transferable.

For the operation of the invention, the synchronization between the rotational movement of the traction sheave and the movement of the Hülltriebanordnung, so that the peripheral speeds between the traction sheave and Hülltriebanordnung match, in particular with respect to the surfaces which are provided for contact with the rope, which then in the same direction and are movable at the same speed. The synchronization is preferably carried out by a gear technical positive connection. This can be achieved for example by meshing gears on the drive pinion and traction sheave. The drive is then for example by means of a drive pinion, which is for example driven by a motor and with its toothing is 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 by a compensation possibility between enveloping drive and traction sheave, for which example a countershaft differential can be used. As a result, influences such as a game in the chain or its wear-related elongation compensated, so that always a sufficient synchronization can be achieved.

According to a further, particularly advantageous embodiment of the invention, the synchronization between the traction sheave and Hülltriebanordnung by at least one side, preferably double-sided Hülltriebverzahnung the traction sheave and side of the front surface arranged on the Hülltriebanordnung engagement means, such as drive rollers for a running as a spline Hülltriebverzahnung. The A handle medium, z. As the drive rollers, are arranged and arranged so that they in the Hülltriebverzahnung, z. B. the roller teeth, engage and form with the traction sheave a temporary positive connection in the region of the circumference of the traction sheave, in which the frictional pressure of the rope is provided against the drive groove. A double-sided Hülltriebverzahnung the traction sheave is disposed on both sides of the drive groove and appropriately arranged A handle medium on the Hülltriebanordnung are provided.

Particularly preferred for this embodiment is a cable winch which comprises a conveyor chain, but this type of synchronization is also applicable, for example, to flat belts or toothed belts, wherein instead of the drive rollers also corresponding formations of the edges of the drive pulley suitable for engagement in the roller teeth of the traction sheave are used. or toothed belt can be used. Multiple chains can also be a different arrangement of the drive rollers, so that they do not necessarily have to be arranged laterally of the front surface of the Hülltriebanordnung, but for example, additionally or exclusively between individual strands of the multiple chain.

At least one Hülltriebkoppelelement is provided, wherein the Hülltriebkoppelelement is at least rotatably connected to a Hülltriebwelle, driven by the drive assembly, as the drive is generally referred to below. The Hülltriebkoppelelement allows the power or energy flow between the drive assembly and the Hülltriebanordnung, so that the Hülltriebanordnung is driven.

The rope hoist winch according to the invention is used, for example, to move a load on the rope or on the housing of the cable winch by the work of the drive motor acts on the rope, especially the incoming part of the cable rope winch part of the rope. In other applications, there is a drive of the then used as a generator drive motor through the rope pulley when a load on the rope or on the housing of the rope pulley the traction sheave and thus the drive motor moves, z. B. for energy or energy conversion. The drive motor used as a drive or as a generator is therefore also referred to below generally as a traction sheave drive arrangement. A drive of a preferred embodiment of the cable winch or a drive through the cable winch are thus provided by means of Treibscheibenantriebsanordnung, Hülltriebantriebsanordnung and / or a direct drive of the endless element, wherein the power transmission between the traction sheave and the drive pulley, the Hülltriebantriebsanordnung and the Hülltrieb 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 Hülltriebantriebsanordnung or the direct drive, all three generally referred to as a drive arrangement, designed as a drive motor. In the traction sheave drive arrangement of the drive motor acts on the traction sheave, in the Hülltriebantriebsanordnung the drive motor acts on the envelope and in the direct drive of the endless element of the drive motor acts directly on the endless element, wherein a pinion, sprocket or the like may be present, the rotational movement of the motor of a drive shaft on traction sheave, envelope or endless element transmits. Advantageously, furthermore, the gear arrangement is designed as a gear transmission, as a chain transmission or as a belt transmission.

Particular advantages result from a clamping device which acts on an envelope drive clamping element and causes a tension of the endless element or the entire Hülltriebanordnung. For this purpose, the endless element has a first and a second strand, wherein the first strand of the endless element, which is located between a first envelope drive support element, for example a sprocket, and a last one Hülltriebstützelement is placed over at least one further Hülltriebstützelement and extending over at least the Hülltriebspannelement, designed for tensioning the endless element Hülltriebstützelement. Then, the first strand through the Hülltriebspannelement, such as a Spannkettenrad, set under mechanical tension, so that further the second strand, which extends between the last sprocket and the first sprocket, is pressed against the traction sheave. As a result, the Hülltriebanordnung, so the endless element with the pressure elements, fixed to the traction sheave in the area in which the rope runs. As a result, the rope is clamped, increases the static friction in both the drive groove and in the pressure groove and improves the transmission of power from the traction sheave and the Hülltriebanordnung on the rope or vice versa. The Hülltriebstützelement is designed in one or more embodiments as Hülltriebkoppelelement, for example as Treibkettenrad. A preferred embodiment of the clamping device provides that the mechanical stress is generated by a constant-force device, in particular a simple and inexpensive spring arrangement. As a result, a uniform pressure force of the spring-loaded Hülltriebanordnung is achieved in the direction of rope, also takes place a balance of thickness variations of the rope. It has proved to be advantageous in this case a tensioning device which comprises a spring arrangement whose spring force is caused by disc springs, in particular those with a strongly degressive characteristic. Advantageously, an area of the spring characteristic is used in which the force changes little and which is referred to below as the constant force range. As a result, no force change 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 which is mounted so as to be movable radially with respect to the axis of the traction sheave in the housing. The clamping axis is arranged in the region of a first end of the clamping fork and for receiving one of the Hülltriebstützelemente, when using a conveyor chain thus the Spannkettenrads provided. The tensioning fork is mounted in the housing at a second end lying opposite the clamping axis, so that the spring force acts between the housing and the tensioning axis and is transmitted to the tensioning axis, that is to say the force flow through the housing is closed. Also advantageous are a mehrrillige design of the traction sheave, so that several ropes can be taken at the same time, and a corresponding design with multiple Hülltriebanordnungen.

If the device described above is in operation, the rope is almost completely enclosed by the pressure elements as part of the Hülltriebanordnung after entering the rope on the rope-protecting round groove of the traction sheave. The pressure surfaces of the pressure elements, for example, designed as pressure grooves or integrated into the endless element, advantageously represent almost completely the negative of the rope. The conveyor chain is in a preferred embodiment of the Hülltriebanordnung as a conveyor chain through the drive sprocket, which is fixed to the seated on the motor shaft drive pinion can be connected, powered directly by motor. The traction sheave is toothed in this case and is driven by the drive pinion.

As a result, both the frictional engagement between the cable and the traction sheave and the frictional engagement between the rope and the pressure elements act to drive the rope. The maximum possible contact surface is used to produce the rope-friendly frictional engagement, so that the peripheral surface of the rope is almost completely enclosed and in contact with driving groove and pressure groove.

In the pressure range works in contrast to the prior art, a uniform pressure force. This remains even with manufacturing or wear-related dimensional deviations of rope, traction sheave and pressure element obtained. The pressure force is preferably generated by a suitable constant-force device, as approximately in practice a disc spring column. In this case, for example, disc springs are used with a strong degressive curve or another constant-force device in which no drop in the force occurs.

For the generation of the pressing force of the constant force range of the spring characteristic, in which the spring force changes only slightly over the spring travel, used, so that when a path change, the force remains substantially constant. The disc springs are supported between the housing and the tension fork. The tensioning fork transmits the pressure force over the clamping axis and the Hülltriebspannelemente, z. B. the sprocket, on the conveyor chain in the present embodiment. The clamping axle is mounted with a translational degree of freedom radially or perpendicular to the main axis movable in the housing. As a result, the clamping path can be realized for the endless element. An elongation of the endless element or the chain is also compensated without significant force drop.

All other Hülltriebstützelemente such. B. sprockets, are preferably mounted in the housing on bearings. They have only one rotational degree of freedom. By means of the corresponding arrangement of the Hülltriebstützelemente or sprockets, the endless element or the conveyor chain wrap around the traction sheave on the circumference. In an advantageous embodiment of the invention, the rope leaves the traction sheave at approximately 270 ° offset from the entry point. Before that, the pressure elements detach from the rope and release it for leaving the traction sheave. In this case, the expiring, unloaded rope end runs past the incoming, loaded rope end laterally. The rope is guided by the Seilfinger component.

The location of the pressing and releasing of the pressure elements with respect to the rope is determined by the size and position of the Hülltriebstütz- or coupling elements located at the cable inlet and cable outlet, in particular sprockets.

The endless element or the conveyor chain centers itself axially in the pressure area on the rope. The characteristic is made possible by the use of a conveyor chain due to the considerable skewing ability of chains. Lateral wear or manufacturing deviations are compensated without additional effort. The traction sheave has lateral limits which prevent the pressure elements and the conveyor chain from slipping laterally from the traction sheave when there is no rope in the rope traction winch which can be used, in particular, as a high-load pressure winch. The clamping of the rope takes place in the preferred embodiment of the invention almost completely up to 3/4 (270 °) of the traction sheave circumference, in special cases more, to approximately 360 °. Due to the large pressure surface between the rope and the pressure elements or the circular groove of the traction sheave, large pressure forces can act on the rope and the stress of the rope remains low. Due to the simple and laterally narrow construction particularly wide chains or double or multiple chains can be used to achieve a high driving force. The construction effort to increase the driving force thus remains in contrast to the prior art at a low level.

If there is no rope in the high-load pressure winch, the pressure elements lie next to the rope groove on the traction sheave and run along with the traction sheave. To insert a new rope in the Hochlastandruckwinde no separate tools are required. Due to the constant pressure, a wide variety of ropes can be used in practice. This can be both steel and textile fiber ropes. The different transverse pressure stability of the ropes used does not play a significant role in contrast to the prior art.

Due to its construction, the rope hoist winch according to the invention is also suitable for conveying at high speed. The pressure elements are attached separately to the links of the conveyor chain, if such is used as an endless element. Thus, they can be exchanged economically and with little effort for different requirements or in the event of wear without the entire conveyor chain having to be replaced.

In contrast to the state of the art, mostly standard and simple identical parts are used in the high-load pressure winch. This guarantees robustness and economy. Due to the high tensile strength and the extremely low cable wear, the cable traction winch according to the invention can be advantageously used in various areas of conveyor technology and hoists. By the pressure elements, it is possible to operate the Hochlastandruckwinde so that the expiring rope end of Hochlastandruckwinde is completely relieved. It can still be generated a driving force. With a classic traction sheave this is not possible according to the initially mentioned Eytelwein equation.

The situation is from the valid for Hochlastandruckwinden, as well as the rope hoist according to the invention, valid extended Eytelwein equation

F ₁ = β ^μα S ₂ + q _m R (β ^μα - 1) + q _m R _ i) with q _m contact load

μ _Αη Friction coefficient between rope and _{pressure element} R traction sheave radius

clear. If the biasing force S ₂ is zero, then the first term is eliminated. Nevertheless, a driving force is generated by the Andruckstreckenlast.

In a preferred embodiment of the rope winch according to the invention, the looping of the traction sheave through the rope is 180 °. This embodiment offers further great potential because it can substitute for all classic traction sheave applications, such as those of the counterweight hoists. Due to the increased propulsion capability of the above-mentioned extended Eytelwein equation with the same payload, the mass of cabin and counterweight, which provide in the prior art for a corresponding pressure of the rope on the traction sheave, be significantly reduced. Enormous energy and cost savings are possible.

In a further embodiment of the rope-passing winch according to the invention, the looping of the traction sheave through the rope is greater than 180 ° and in a particularly preferred case, which is also shown in the figures, 270 °. As a result, high forces can be transmitted to the rope. However, it must be ensured that the incoming can run past the running rope. For this purpose, a rope finger is provided, which preferably diverts the unloaded rope when driving through the cable winch and past the loaded rope, so that it can run on a straight path on the traction sheave.

Provided is also a rope traversing winch, in which the looping of the traction sheave through the rope is 180 °. Alternatively, the wrap of the traction sheave be provided by the rope less than or greater than 180 ° and a rope finger to pass the incoming rope and the expiring rope at a wrap greater than 180 ° to each other. The wrap can also be more than 270 °, up to approximately 360 ° in special cases.

A particularly advantageous use of the cable winch according to the invention is when it is combined with a cable storage winch in such a way that storage of the rope can be done and / or relieved Rope end can be biased to increase the driving force of the Hochlastandruckwinde. This fact is represented by the extended equation of Eytelwein described above. However, it is also possible to use non-driven, ie passive cable stores.

The rope hoist winch according to the invention has the following advantages over the prior art:

• Resolving the previous conflict of objectives between high driving force and high rope life of rope pulleys, thus lower rope stress combined with high driving force;

• Constant clamping and driving forces, regardless of the state of wear of the traction sheave, the rope and the pressure elements, thus avoiding tension and clamping force fluctuations;

· Enables safe, trouble-free operation at high levels

Conveyor speeds;

• uniform, surface pressure of the rope to the traction sheave up to 3/4 of the traction sheave circumference, with a high ratio of diameter of the traction sheave to rope diameter also possible up to 360 °;

· Simple structure through simple components and many standard and identical parts;

• self-centering of the pressure elements on the rope, thus compensation of variations in the rope diameter and compensation of wear and manufacturing tolerances to a large extent without clamping force variation possible;

• By balancing different transverse pressure stabilities of the cables used, it is possible to use both textile fiber ropes and steel cables without retrofitting;

• Machining deviations of the roundness of the traction sheave have no negative effects on the pressure of the rope on the traction sheave and on the driving force, thereby economical production and profitable products;

· No separate tools for inserting the rope required;

• easy scalability of power, pulley and pulley diameter for a wide variety of applications;

• Increasing the pressure force by wider enveloping arrangements, so especially chains or belts, easily possible and • Insensitive to contamination and thus guaranteeing a high degree of operational safety and availability in a wide range of applications. The design of chains or belts is thoroughly researched and standardized. Thus, reliable maintenance intervals for the rope traversing winches according to the invention can be defined.

Reference to the description of exemplary embodiments and their representation in the accompanying drawings, the invention is explained in more detail below. Show it:

1 shows a schematic perspective view with the housing open and the cable spring open, an embodiment of a rope-type winch according to the invention;

FIG. 2 shows a detail of the rope-passing winch according to the invention from FIG. 1; FIG.

3 is a schematic cross-sectional view of an embodiment of a rope hoist according to the invention;

4 shows a schematic longitudinal section of an embodiment of a rope hoist according to the invention;

Fig. 5: a detail of the rope hoist winch according to the invention from Fig. 4;

6 shows a schematic perspective view with the housing open and the cable spring closed, an embodiment of a rope-passing winch according to the invention;

FIG. 7 shows the cable winch according to the invention from FIG. 6 with the housing closed; FIG.

8 shows schematically a detail of an embodiment of a rope hoist according to the invention in a sectional illustration;

9 shows a schematic side view of an embodiment of a link of a conveyor chain with pressure element;

10 is a schematic perspective view of an embodiment of a link of a conveyor chain with pressure element;

Fig. 1 1: schematically in perspective view with the housing open and closed rope finger another embodiment of a rope hoist according to the invention;

Fig. 12: a detail of the rope hoist winch according to the invention from Fig. 1 1; FIG. 13 shows an embodiment of a link of a conveyor chain with pressure element in a perspective view as a detail of the rope passage winch according to the invention from FIG. 1; FIG.

FIG. 14 is a schematic longitudinal sectional view of the embodiment of the rope-passing winch according to the invention from FIG. 11; FIG.

FIG. 15 is a schematic sectional view of a detail of the embodiment of a rope-passing winch according to the invention from FIG. 1; FIG.

16 shows schematically in side view with a closed housing an embodiment of a rope hoist winch according to the invention with a tensioning fork;

FIG. 17 is a schematic sectional view of the embodiment of a rope-type winch according to the invention with a tensioning fork according to FIG. 16; FIG.

FIG. 18 is a schematic perspective view of an embodiment of a rope storage winch in combination with a rope-type winch according to the invention with the housing open. FIG.

FIG. 1 shows an embodiment of a cable winch 1 according to the invention schematically in a perspective view with the housing open (only housing part 12 visible) and likewise open loop finger 20, FIG. 2 shows the enlarged detail X of FIG. 1. Fig. 3 shows schematically in a cross-sectional view of this embodiment of the cable winch 1 according to the invention with two housing parts 12, 13. A rope 3, 3 'enters with an incoming portion of the rope 3 in the rope winch 1 and with a running portion of the rope 3' from this again out, with an angle of 270 ° is spanned between the two sections, accordingly, the wrap is 270 ° on a traction sheave 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 on its circumference a drive groove 22, in which the cable 3, 3 'on or runs from this, as seen especially in Fig. 2. As soon as the cable 3, 3 'is in the drive groove 22, it is pressed into the drive groove 22 by pressure elements 5. The pressure elements 5 are individually designed on a side facing the traction sheave 2 side of a conveyor chain 4 so that a Andruckrille 50 reproduces the rope shape in the negative and thereby closely and evenly to the rope 3,3 'hugs. In addition, the length of the Andruckrillen 50 of the individual pressure elements 5 is dimensioned so that they are close to each other, virtually gapless, abut each other when the chain rotates about the traction sheave 2 and is curved in the radius of the traction sheave 2. As a result, a very uniform, the frictional force in the drive groove 22 reinforcing pressure loads while avoiding high-stress load peaks on the rope 3,3 '.

In addition, the power transmission takes place not only on the static friction between the drive groove 22 and rope 3, 3 ', because the conveyor chain 4 is also connected to a motor 42, which serves as a drive, transmission technology, such as the traction sheave 2. The drive of the traction sheave 2 takes place via a drive pinion 46, the toothing of which is in engagement with the external drive toothing 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.

About the Tre ib chain nrad 9 runs the conveyor chain 4, which is also supported by Stützkettenräder 6 and a Spannkettenrad 7. These are in turn supported by a bearing 10 in the housing and in the housing (only housing part 12 visible) arranged axis 1 1. The conveyor chain 4 forms a first strand, spanned between the drive chain nrad 9 and the last Stützkettenrad 6, and a second strand, clamped between the last in the direction of rotation Stützkettenrad 6 and the drive sprocket 9, considered when driving the incoming rope 3. The second strand thus serves the pressure of the rope 3, 3 'in the drive groove 22, while the conveyor chain 4 runs back over the first strand. In addition, the conveyor chain 4 is tensioned in the first strand by the Spannkettenrad 7, so that the voltage in the conveyor chain 4 increases overall and also the pressure of the pressure elements 5 is increased to the drive wheel 2 and is adaptable.

For this purpose, the Spannkettenrad 7 is arranged radially movable relative to the traction sheave 2. This mobility allows a on both sides of the housing (only housing part 12 visible) supporting the clamping fork 14 which acts on a clamping axis 8, on which the Spannkettenrad 7 runs. The voltage is caused by a package disc springs 15 and is adjustable via a nut 17. The previously described embodiment of the rope-passing winch 1 is again shown schematically in FIG. 4, but there in longitudinal section. To FIG. 5 shows a detail Y of the rope-passing winch according to the invention from FIG. 4. The section through the rope 3 'and the traction sheave 2 clearly shows how the rope 3' runs out of the drive groove 22 and is deflected by the rope finger 20, to make a collision to avoid with the incoming rope 3. It can also be seen how the pressure elements 5 with the pressure grooves 50 through the conveyor chain 4, which runs on the Stützkettenrad 6, are first pressed against the cable 3 'and then release it again at the expiration of the traction sheave 2. The conveyor chain 4 runs over the drive chain nrad 9, the support sprockets 6 and the Spannkettenrad 7. Fig. 6 shows schematically in perspective view with the housing open (only housing part 12 visible), but with a closed cable finger 20 an embodiment of a rope hoist according to the invention. 1 In contrast to the above-described Figures 1 to 5, the cable guide is recognizable by the incoming, loaded rope 3 stretched enters the rope pulley 1, while the running, unloaded rope 3 'deflected by the rope finger 20 and out of the path of the incoming rope 3 is conducted. The clamping fork 14 with the disc springs 15 acts on the clamping axis 8 and thus on the Spannkettenrad 7, so that the conveyor chain 4 is tensioned with the pressure elements 5. Fig. 7 shows the rope traction winch according to the invention from Fig. 6 with a closed housing, consisting of the housing parts 12, 13. Thus, construction and function of the clamping fork 14 are illustrated. This is guided on both sides in each case a clamping fork abutment 19 and supported on the housing 12, 13. The package disc springs 15 pushes the tensioning fork 14 away from the tensioning fork abutment 19, the spring force being adjustable by the nut 17. A nut 17 'limits the path of the clamping fork 14. The clamping fork 14 acts on the clamping axis 8 with the not visible here Spannkettenrad inside the housing 12, 13th

Fig. 8 shows schematically a detail of an embodiment of a rope hoist according to the invention 1 in transverse to the longitudinal axis of the rope 3, 3 'cut representation. This clearly shows how closely the drive groove 22 and the pressure groove 50 rest against the cable 3, 3 'and enclose it on almost its entire circumference. The drive groove 22 is part of the traction sheave 2, the pressure groove 50 is part of the pressure element 5, which is supported by the conveyor chain 4 and pressed against the traction sheave 2. Fig. 9 shows schematically in side view an embodiment of a member of a conveyor chain 4 with pressure element 5 and Fig. 10 shows schematically in perspective the link of the conveyor chain 4 with pressure element 5, wherein the pressure groove 50 is visible.

Fig. 1 1 shows schematically in perspective view with the housing open and closed rope finger 20, a further embodiment of a rope hoist according to the invention 100, which differs above all in the manner of driving the conveyor chain 140 from the previously explained in the description of Figures 1 to 10 embodiment , FIG. 12 shows a detail of the rope-passing winch 100 according to the invention from FIG. 11. Namely, in the illustrated embodiment, the drive acts exclusively on a traction sheave 120 which has internal drive teeth 122 in which the pinion of the motor 42 engages. As an alternative to the illustrated embodiment, an external toothing would also be possible.

A conveyor chain 140 as an endless element of a Hülltriebanordnung 160, however, is driven by a roller teeth 124 on the traction sheave 120. It comes to engagement of the conveyor chain 140 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 of the traction sheave 120 approaches. Also shown are the pressure elements 5 and the cable 3, 3 '. In the housing part 12, the support sprockets 6 and the clamping shaft 8 are received on the clamping fork 14. The tensioning fork 14 carries the cup springs 15 and the nut 17. The traction sheave 120 is supported by the main shaft 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 rope pass winch 100 according to the invention from FIG. The drive rollers 142 are rotatably mounted on or with an axis which is arranged transversely to the running direction of the conveyor chain 140.

Fig. 14 shows schematically in longitudinal section representation of the embodiment of Fig. 1 1 of a rope hoist 100 according to the invention. Fig. 15 shows schematically a detail of the embodiment of Fig. 1 1 of a rope hoist according to the invention 100 in transverse to the axis of the rope 3 cut representation. 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 tensioning fork 14 with cup springs 15, nut 17 and the tensioning axis 8 and the tensioning fork abutment 19. The position of the sections AA (FIG. see Fig. 17) and BB (see Fig. 18), the function and the position of the components to each other can be better understood. 17 shows a schematic sectional view of a section AA of an embodiment of a cable winch 1 according to the invention with a tensioning fork 14 according to FIG. 16, wherein once again the function of the cable finger 20 is clearly recognizable. FIG. 18 shows diagrammatically, in a further illustration cut in sectional plane BB, an embodiment of a rope-passing winch 1 according to the invention with a tensioning fork 14 according to FIG. 16.

19 schematically shows a perspective view of an embodiment of a cable storage winch 170 in combination with a cable winch 1 according to the invention with the housing 12, 13. The cable 3 'running out of the cable winch 1 is taken up by a cable storage 174, which is driven by a cable storage drive 175 , The cable storage drive 175 thus not only ensures a clean and space-saving winding of the rope, but can enhance the driving force of the rope winch 1, since the expiring rope 3 'is acted upon by a biasing force which increases the cable force.

LIST OF REFERENCE NUMBERS

1, 100 rope winch

2, 120 traction sheave

3, rope (loaded)

3 'rope (relieved)

4, 140 conveyor chain, endless element

5 pressure element

6 backup sprocket, hull drive support, sprocket

7 clamping chains wheel, Hülltriebspannelement, sprocket

8 clamping axis

9 envelope drive coupling element, drive sprocket, sprocket

10 bearing sprocket

1 1 axle sprocket

12 housing, housing part (first half)

13 housing, housing part (second half)

14 tension fork

15 constant-force device, spring arrangement, plate spring

17, 17 'mother

19 tensioning abutment

20 rope fingers

22 drive groove

24 toothing

26 ball bearing traction sheave

30 control

37 main axis

38 external drive toothing

40 frame

42 motor, drive, drive arrangement

46 drive pinion

48 drive sprocket

50 pressure groove

60, 160 envelope drive arrangement

122 Internal drive toothing

124 Hülltriebverzahnung, Rollenverzahnung Engaging means, driving pulley rope storage winch cable storage

Cable storage drive

Claims

claims

1 . Rope-passing winch (1, 100), comprising a traction sheave (2, 120) with a drive groove (22) circumferentially introduced thereon for receiving a cable (3, 3 ') and one opposite the drive groove (22) for frictionally pressing the rope ( 3, 3 ') formed against the drive groove (22) Hülltriebanordnung (60, 160) comprising a continuous endless element (4, 140) with a first strand at least on Hülltriebstützelemente (6) and with a second strand on the cable driving part the circumference of the traction sheave (22), wherein the traction sheave (2, 120) and the Hülltriebanordnung (60, 160) are synchronized in such a way that those surfaces of the drive groove (22) and Hülltriebanordnung (60, 160), the Contact with the cable (3, 3 ') are provided, in the same direction and at the same speed are movable, wherein the drive groove (22) and the drive groove (22) facing the front surface of the Hülltriebanordnung (60) acting as a Pressure groove ( 50) is formed, each having a profile of the rope (3, 3 ') substantially complementary contour, characterized in that the frictional pressure of the rope (3, 3') against the drive groove (22) by means of the Hülltriebanordnung (60, 160) via a cable-driving part of the circumference of the traction sheave (2, 120).

A rope hoist winch as claimed in claim 1, wherein the hull drive assembly (60, 160) comprises a conveyor chain as an endless element (4, 140), which is designed as or comprises a toothed belt, a flat belt or an arrangement of spliced ropes.

3. rope-type winch according to claim 2, wherein the conveyor chain (4, 140) comprising Hülltriebanordnung (60, 160) pressure elements (5) which are arranged on one side of the conveyor chain (4, 140) close to each other and to the drive groove ( 22) facing out front surface of the Hülltriebanordnung (60, 160) form, wherein the Hülltriebstützelemente and the Hülltriebkoppelelement as sprockets (6, 9) are formed.

4. rope winch according to claim 2 or 3, wherein the conveyor chain (4, 140) is designed as a wide chain or as a multi-chain.

5. rope winch according to claim 2, wherein the toothed belt or the flat belt having such a cross-sectional profile, that to the drive groove (22) side facing the toothed belt or the flat belt to the profile of the rope (3, 3 ') has substantially complementary contour , Rope winch according to one of the preceding claims, wherein a mechanical synchronization between the traction sheave (2, 120) and Hülltriebanordnung (60, 160) by means of a gear arrangement by a gear technical form fit, carried out as a gear transmission or as a chain transmission, takes place or is designed as a belt transmission.

A rope-type winch according to claim 6, wherein for synchronization between the traction sheave (2) and the sheathing drive arrangement (60) an external drive toothing (38) and a meshing therewith toothing of a drive arrangement (42) drivable drive pinion (46) are provided, wherein the drive arrangement ( 42) at the same time for driving the endless element (4) via a Hülltriebkoppelelement (9) is provided, wherein Hülltriebkoppelelement (9) and drive pinion (46) rotatably connected to the drive assembly (42) are connected.

Rope winch according to claim 6, wherein for synchronization between traction sheave (120) and Hülltriebanordnung (160) at least one side Hülltriebverzahnung (124) of the traction sheave (120) and laterally of the front surface on the Hülltriebanordnung (160) arranged engagement means (142) are provided, the so are arranged and arranged such that the engagement means (142) engage in the Hülltriebverzahnung (124) and with the traction sheave (120) form a temporary positive connection in the region of the circumference of the traction sheave (120) in which the frictional pressure of the rope (3 , 3 ') is provided against the drive groove (22).

A rope hoist winch according to any one of the preceding claims, wherein the endless element (4, 140) has first and second strands, the first strand of the endless element (4, 140) extending between a first sheath drive support element (6) and a last sheath drive support element (6 ) is laid over at least one further Hülltriebstützelement (6) and at least one Hülltriebstützelement (6), the Hülltriebspannelement (7) at least radially to the main axis (37) by a tensioning device deflectable for clamping the endless element (4, 140) is formed extends, so that the first strand and thus the second strand are set by the Hülltriebspannelement (7) under tension, so that the second strand extending between the last Hülltriebstützelement (6) and the first Hülltriebstützelement (6), against the Drive groove (22) of the traction sheave is pressed.

10. rope winch according to claim 9, wherein the clamping device comprises a clamping fork (14) and a translational degree of freedom radially movable to a main axis (37) of the traction sheave (2) in the housing (12, 13) mounted clamping axis (8), wherein the clamping axis (8) for receiving one of the Hülltriebstützelemente (6) is provided, and wherein the clamping fork (14) at one of the clamping axis (8) opposite end in the housing (12, 13) is mounted, so that a clamping force between the housing ( 12, 13) and the clamping axis (8) acts and is transmitted to the clamping axis (8).

1 1. A rope-type winch according to claim 10, wherein the deflection of the envelope drive clamping element (7) and the clamping force are caused by a constant-force device (15).

12 rope winch according to claim 1 1, wherein the constant-force device (15) comprises disc springs with a degressive spring characteristic and a spring travel is chosen in such a way that a nearly constant force range of the spring characteristic is used.

13. Rope winch according to one of the preceding claims, which is combined with a rope storage winch (170) in such a way that a storage of the rope (3, 3 ') can take place and / or the unloaded rope end can be biased to the driving force of the cable winch (1) increase.