EP3573918A1 - Treuil à câble passant - Google Patents

Treuil à câble passant

Info

Publication number
EP3573918A1
EP3573918A1 EP18700911.3A EP18700911A EP3573918A1 EP 3573918 A1 EP3573918 A1 EP 3573918A1 EP 18700911 A EP18700911 A EP 18700911A EP 3573918 A1 EP3573918 A1 EP 3573918A1
Authority
EP
European Patent Office
Prior art keywords
rope
traction sheave
drive
cable
groove
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP18700911.3A
Other languages
German (de)
English (en)
Other versions
EP3573918C0 (fr
EP3573918B1 (fr
Inventor
Paul Schumann
Thorsten Schmidt
Thomas Leonhardt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Planeta-Hebetechnik GmbH
Original Assignee
Technische Universitaet Dresden
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Technische Universitaet Dresden filed Critical Technische Universitaet Dresden
Publication of EP3573918A1 publication Critical patent/EP3573918A1/fr
Application granted granted Critical
Publication of EP3573918C0 publication Critical patent/EP3573918C0/fr
Publication of EP3573918B1 publication Critical patent/EP3573918B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B66D1/7415—Friction drives, e.g. pulleys, having a cable winding angle of less than 360 degrees

Definitions

  • the invention relates to a 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 Hülltrieban nie, the circulating endless element which is placed with a first strand at least via Hüllrete nulemente and with a second strand over the cable-driving part of the circumference of the traction sheave, wherein the traction sheave and the Hülltrieban Aunt are synchronized in such a way that those surfaces of the drive groove and Hülltrieban kann 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
  • the rope is additionally pressed by pressure elements in the groove.
  • 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, 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.
  • 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.
  • 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.
  • a V-groove is used, so that even with this construction, a high stress of the rope in the groove occurs.
  • the cable pulling device has an automatic contact pressure regulation.
  • the traction sheave 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).
  • 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 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.
  • 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.
  • wedge groove and jaws exert line contact on the rope and thus stress it up.
  • the clamping force is very limited by the individual, small leaf springs. It can only be increased by considerable extra effort.
  • 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.
  • 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.
  • a passively circulating pressure chain is provided on a section of the traction sheave.
  • the pressure elements cause an additional load on the rope.
  • 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.
  • the chain is positively driven by the traction sheave.
  • 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 Gegenbiege Oli 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.
  • the Hauptan founded Switzerland 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.
  • 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.
  • 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).
  • leg spring reference numeral 27
  • the rope 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 Gegenbiege Functional when passing through the rope by the winds on the rope. This takes up the rope very high.
  • 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.
  • the object of the invention is to provide a winch, which achieves a uniform, flat applied Anyakraft 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.
  • 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 Hüllretean ever is designed for frictional pressure of the rope against the drive groove.
  • the Hülltrieban extract comprises a revolving endless element which is placed with a first strand on Hülltrieb nulemente 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 Hülltrieban himself are movable in the same direction and at the same speed, which are provided for contact with the rope.
  • 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;
  • profile cables are also included in the invention.
  • 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 Hülltrieban ever are the Endloselement supporting Hülltrieb nulemente 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 Hülltrieb nulemente 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
  • 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.
  • 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.
  • 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 Hüllrete nulemente also, the function of transmitting force and movement of a drive assembly, for. As a motor with drive shaft, on the endless element.
  • the Hüllrete needleholder designed as sprockets, especially as support sprockets
  • the Hüllretekoppel element are designed as a drive sprockets.
  • a conveyor chain designed as a skew-capable chain has proven.
  • the conveyor chain is designed as a wide chain or as a multiple chain. With these versions, a particularly high driving force is transferable.
  • 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.
  • the synchronization between the traction sheave and Hülltrieban kann by at least one side, preferably double-sided Hülltriebverzahnung the traction sheave and side of the front surface arranged on the Hülltriebanssenung engagement means such as drive rollers for a running as a spline Hülltriebvertechnikung.
  • the drive rollers are arranged and arranged so that they in the Hüllreteverzahnung, 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 Hülltrieban kann are provided.
  • a cable winch which comprises a conveyor chain
  • 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 Hülltrieban emblem, 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 Hüllretewelle, driven by the drive assembly, as the drive is generally referred to below.
  • the Hüllretekoppelelement allows the power or energy flow between the drive assembly and the Hüllreteanowski, so that the Hüllretean ever 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.
  • 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 ofmaschinenantriebsan kann, Hülltriebantriebsan himself and / or a direct drive of the endless element, wherein the power transmission between the traction sheave and the drive pulley, the Hüllreteantriebsan himself and the Hüllrete or the direct drive of the endless element and the endless element via a gear arrangement, as explained below.
  • the traction sheave drive arrangement, the Hülltriebantriebsan himself or the direct drive all three generally referred to as a drive arrangement, designed as a drive motor.
  • the traction sheave drive arrangement of the drive motor acts on the traction sheave
  • 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.
  • the gear arrangement is designed as a gear transmission, as a chain transmission or as a belt transmission.
  • 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 Hülltrieb sublement is placed over at least one further Hülltrieb mainlement and extending over at least the Hülltriebspannelement, designed for tensioning the endless element Hüllrete basic element.
  • a first envelope drive support element for example a sprocket
  • the Hülltrieb the clamping device provides that the mechanical stress is generated by a constant-force device, in particular a simple and inexpensive spring arrangement.
  • a uniform pressure force of the spring-loaded Hülltrieban Aunt is achieved in the direction of rope, also takes place a balance of thickness variations of the rope.
  • a tensioning device which comprises a spring arrangement whose spring force is caused by disc springs, in particular those with a strongly degressive characteristic.
  • 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 Hülltrieb nulemente, 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.
  • a Patrillige design of the traction sheave so that several ropes can be taken at the same time, and a corresponding design with multiple Hüllmaschinean effet.
  • the rope is almost completely enclosed by the pressure elements as part of the Hülltrieban Ich 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 Hülltrieban Ich 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.
  • 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.
  • the pressure force is preferably generated by a suitable constant-force device, as approximately in practice a disc spring column.
  • a suitable constant-force device as approximately in practice a disc spring column.
  • disc springs are used with a strong degressive curve or another constant-force device in which no drop in the force occurs.
  • 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 Hülltriebspannide, 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 Hülltrieb allemente such. B. sprockets are preferably mounted in the housing on bearings. They have only one rotational degree of freedom.
  • the endless element or the conveyor chain wrap around the traction sheave on the circumference.
  • the rope leaves the traction sheave at approximately 270 ° offset from the entry point.
  • the pressure elements detach from the rope and release it for leaving the traction sheave.
  • 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 °.
  • 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.
  • the cable traction winch according to the invention can be advantageously used in various areas of conveyor technology and hoists.
  • 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.
  • 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 °.
  • 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.
  • a rope traversing winch in which the looping of the traction sheave through the rope is 180 °.
  • 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 Hochlastan horrwinde.
  • This fact is represented by the extended equation of Eytelwein described above.
  • FIG. 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.
  • FIG. 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;
  • FIG. 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
  • FIG. 9 shows a schematic side view of an embodiment of a link of a conveyor chain with pressure element
  • FIG. 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. 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. 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.
  • 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. 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. 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. 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. 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.
  • the pressure elements 5 are individually designed on a side facing the traction sheave 2 side of a conveyor chain 4 so that a An horrrille 50 reproduces the rope shape in the negative and thereby closely and evenly to the rope 3,3 'hugs.
  • the length of the Anticianrillen 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.
  • 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.
  • 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 forms a first strand, spanned between the drive chain nrad 9 and the last Stauerkettenrad 6, and a second strand, clamped between the last in the direction of rotation Stauerkettenrad 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • the drive acts exclusively on a traction sheave 120 which has internal drive teeth 122 in which the pinion of the motor 42 engages.
  • an external toothing would also be possible.
  • a conveyor chain 140 as an endless element of a Hülltrieban ist 160 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
  • BB see Fig. 18
  • FIG. 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.
  • FIG. 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.

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

Abstract

L'invention concerne un treuil (1) à câble passant, comprenant un disque de traction (2) pourvu d'une gorge motrice (22) périphérique destinée à recevoir un câble (3, 3') et un agencement de transmission par lien souple (60), réalisé en face de la gorge motrice (22) sur une partie d'entraînement du câble de la périphérie du disque de traction (2) pour pousser le câble (3, 3') par frottement contre la gorge motrice (22), qui comprend un élément continu (4) périphérique, qui est placé avec un premier brin autour d'éléments support (6) de la transmission par lien souple et avec un deuxième brin sur la partie d'entraînement de câble de la périphérie du disque de traction (22), le disque de traction (2) et l'agencement de transmission par lien souple (60) étant synchronisés de manière telle que les surfaces de la gorge motrice (22) et de l'agencement de transmission par lien souple (60), qui sont destinées à entrer en contact avec le câble (3, 3'), peuvent se déplacer dans la même direction et à la même vitesse. Selon l'invention, le disque de traction (2) présentant la gorge motrice (22) et la face frontale de l'agencement de transmission par lien souple (60), orientée vers la gorge motrice (22), présentant une gorge de poussée (50), présentent respectivement un contour sensiblement complémentaire au profil du câble (3, 3').
EP18700911.3A 2017-01-27 2018-01-19 Treuil à câble passant Active EP3573918B1 (fr)

Applications Claiming Priority (2)

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

Publications (3)

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EP3573918A1 true EP3573918A1 (fr) 2019-12-04
EP3573918C0 EP3573918C0 (fr) 2023-10-04
EP3573918B1 EP3573918B1 (fr) 2023-10-04

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EP (1) EP3573918B1 (fr)
DE (1) DE102017101656A1 (fr)
WO (1) WO2018138000A1 (fr)

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CN109879190B (zh) * 2019-03-07 2023-12-19 山东万仞机电科技股份有限公司 一种绳索攀爬输运装置
CN116253263B (zh) * 2023-05-15 2023-10-20 河南工学院 一种牵引力恒定的自动排绳电动绞车
CN120759203B (zh) * 2025-09-11 2025-11-25 成都人形机器人创新中心有限公司 一种攀爬装置和机器人

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Also Published As

Publication number Publication date
EP3573918C0 (fr) 2023-10-04
DE102017101656A1 (de) 2018-08-02
EP3573918B1 (fr) 2023-10-04
WO2018138000A1 (fr) 2018-08-02

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