EP0509404A2 - Transporting equipment on cableways for driving haulage cables - Google Patents

Abstract

Transporting equipment on cableways for driving at least one haulage cable run over a driving pulley (3) and partly winding around the latter, having endless outer cables run around the haulage cable (1) and the driving pulley (3), partly winding under pretension around the driving pulley (3) and exerting increased frictional resistance between haulage cable (1) and driving pulley (3), the haulage cable (1) being run around a non-driven deflection pulley (2) mounted at a centre distance B from the driving pulley, and the endless outer cables (4) being run around deflection rollers (5, 6) which are mounted on either side parallel to the driving pulley (3) and the deflection pulley (2) and with respect to which the driving pulley (3) is mounted at a variable centre distance A. <IMAGE>

Description

The invention relates to a conveying device on cable conveying systems for driving at least one endless cable which is guided over a traction sheave and partially wrapped around it, with endless outer cables guided around the conveying rope and the traction sheave, wrapping the traction sheave partially under tension and exerting an increased frictional connection between the conveying rope and the traction sheave.

From DE-PS 497 310 and DE-PS 514 270 generic conveyors on rope conveyors for driving conveyor cables are known, in which acting on a deflection roller of the endless outer ropes, the preloading weight increases the frictional connection between the conveyor cable and traction sheave. These were also described in an article by H. Knaust in the journal of the Association of German Engineers, Volume 76, Number 36, dated September 3, 1932, pages 861-865. The known conveyor devices have several disadvantages. This is, on the one hand, the large construction volume of the device, which is caused by the large diameter of the deflecting pulleys of the endless outer ropes and their arrangement, in particular when there are high tensile forces many applications is unfavorable, and also the consequent high weight. Another disadvantage is that the endless outer ropes and the conveyor cable wear very quickly with such designs, because a very high pre-tension designed for the maximum load of the conveyor device is constantly exerted, and because the conveyor cable is exposed to many bending cycles that shorten the service life.

Another possibility of the frictional connection between the conveyor cable and the traction sheave is to use multiple wrapping. For larger tensile forces, multiple wrapping is used using a counter pulley. All multi-disc drives have the disadvantages that the conveyor cable is exposed to considerably more bends, very high wrap forces and lacing forces occur and differential gears are required.

Based on this prior art, the object of the invention is to provide a conveyor device which has a small construction volume and a low weight even with high tensile forces, only generates the pretension required for the prevailing tensile force by self-pressing, exposes the ropes to a few bending changes and also avoids the disadvantages of multiple wrapping.

The solution according to the invention is based on a generic conveyor device on cable conveyor systems for driving conveyor cables, and it consists in that the conveyor cable is guided around a non-driven deflection pulley mounted at an axial distance B from the traction sheave and the endless outer cables are parallel to the traction sheave on both sides and Deflection pulley mounted guide pulleys are guided, to which the traction sheave is variable in distance is stored at an axial distance A. The deflection pulley, which is supported at an axial distance B from the traction sheave, serves to deflect the conveyor cable. The endless outer ropes are guided around the traction sheave, which is variable in the distance between the axes A to the deflection pulleys. This configuration according to the invention ensures that when the conveyor cable is loaded with a tensile force which acts on the deflection pulley and the traction sheave mounted with the center distance B, the center distance A seeks to increase and the pretensioning of the endless outer ropes thus increases with increasing tractive force, as a result of which the frictional connection between the conveyor cable and the traction sheave is increased by self-pressing to such an extent that it is adapted to the momentary tensile force and is necessary to prevent the conveyor cable from slipping on the traction sheave.

An advantageous embodiment consists in that the deflection rollers are mounted with different axes at axial distances A1, A2 to the drive pulley. This design makes it possible for the endless outer ropes to have different lengths.

A first preferred embodiment is that the axis of the deflection pulley lies in the area of the center distance A between the traction sheave and the deflection pulleys. and another preferred embodiment can be that the axes of the deflection rollers lie in the region of the center distance B between the traction sheave and the deflection sheave. Through these designs it is achieved that the axes of the traction sheave, the deflection pulley and the deflection rollers are arranged approximately side by side in one direction, which is expedient for a small design and an advantageous effect of the forces developing in the direction of the center distances.

A second preferred embodiment can be that the axis of the deflection disc, the axis of the traction sheave and the axes of the deflection rollers lie in one plane. In this case, the axes of the traction sheave, the deflection sheave and the deflection rollers are arranged next to one another in exactly one direction, which can be particularly advantageous for the forces which develop in the direction of the center distances.

Another advantageous embodiment can be seen in the fact that the deflection pulley and the traction sheave are mounted by means of bearings in bearing housings which are connected to one another by means of a spacing connecting element. The spacing connecting element serves to limit the shortest center distance B between the deflection pulley and traction sheave, as a result of which the pulling force exerted on the deflection pulley and aiming to shorten the center distance B, exerted by the load end of the conveyor cable, by means of the spacing connecting element delimiting the center distance B on the traction sheave, which is mounted at a variable distance in the center distance A from the deflection pulleys, in a way to increase the center distance A , the tension of the endless outer ropes increases. An alternative embodiment can consist in that the spacing connecting element is formed from a fixed connection of the bearing housing of the deflection pulley with the bearing housing of the traction sheave or from a common bearing housing of deflection pulley and traction sheave.

Advantageously, the conveyor device according to the invention is designed so that the deflection rollers are mounted by means of bearings in a spring-loaded holder which can be displaced by means of a straight guide relative to the bearing housing of the deflection pulley and / or the bearing housing of the traction sheave is. The straight guide serving as a torque support prevents the axis of the traction sheave from laterally deviating with respect to the axis of the deflection rollers under load. The straight guide can expediently be designed as a round guide. The straight guide can also consist of another device, such as a guide pin, which prevents the axis of the traction sheave from tilting relative to the axis of the deflection rollers. The spring tension creates a pretension of the endless outer ropes even without a tensile force acting on the conveyor rope. The bracket can be connected to one or more attachment points to a load-bearing suspension to attach the conveyor.

An additional preferred embodiment of the conveyor device according to the invention is that the spring tension is directed to an increase in the center distance A between the traction sheave and the deflection rollers and is generated by compression springs or tension springs. As a result, the endless outer ropes are pretensioned even without a tensile force acting on the conveyor rope.

Advantageously, the conveying device is further configured such that the pretension of the compression springs or the tension springs can be adjusted by means of adjusting elements. With this design, the pretensioning of the endless outer ropes can be adjusted. Another advantage of this training is the fact that it facilitates or enables the assembly of the conveyor device and the replacement of the endless outer cables. A practical training can be that the adjusting elements are set screws and the compression springs or tension springs are coil or disc springs.

Advantageously, it is also provided that the guide of the conveyor cable on the traction sheave is shaped as a radial groove with wedge-shaped flanks adjoining on both sides. The conveyor cable is guided securely in the radius groove, and the wedge-shaped flanks can be designed so that the endless outer cables are protected in a manner that protects the cable come to rest non-positively on the conveyor cable.

A further expedient embodiment of the conveying device according to the invention is that one or two adjustable eccentric disks arranged on the support of the deflection rollers can adjust one or both distances A1, A2 between the drive pulley and the two deflection rollers independently of one another. This configuration allows different lengths of the endless outer ropes to be compensated for when the conveyor device is installed, so that both act on the conveyor rope with the same pretension. With the eccentric discs, aging-related elongation of the endless outer ropes can also be compensated for by retensioning. The adjustment of the eccentric discs can expediently take place in that they can be adjusted by means of a clamping tool engaging in mounting bushings and can be locked by means of fastening elements.

Advantageously, the conveyor device according to the invention can be designed so that a hand crank or a motor drive can be connected to the shaft used to support the traction sheave. Advantageous for the application of high tractive forces can be that a gear, preferably a planetary reduction gear or, between the traction sheave and the drive a spur gear is switched on or that the gear can be driven by means of an oil motor.

An advantageous embodiment consists in the fact that the traction sheave, the motor drive or the transmission can be braked by means of a holding brake, since the conveyor cable can thereby be ascertained without further application of force or can be released from the conveying device in a controlled manner.

A less space-consuming construction of the conveying direction can be made possible by the fact that the gear is installed in the traction sheave. This can also be favorable for a high power delivery of the conveyor.

A conveyor device according to the invention can serve as a lifting, pulling or conveying unit for lifting, lowering, recovery or similar conveyor systems for loads, such as e.g. for goods and passenger lifts, cranes, cable cars, cable winches, pulling devices for external and self-mining operations, for example for vehicle installation, for baskets that can be lowered on the outside of high-rise buildings, in forestry operations, for the fire service or in construction, and in general for all applications, where loads are lifted, pulled or conveyed.

The design of the conveyor device according to the invention ensures that the conveyor device has a small construction volume and a low weight even with high tensile forces and the required pretensioning of the endless outer ropes, which can be increased by a usual safety factor for the current load on the conveyor rope, in rope-friendly and safe way is generated by self-pressing. Further advantages of the conveying device according to the invention can be seen in the fact that it can exert a constant lifting and pulling force, the conveying rope can be conveyed at a constant rope speed, the rope winding and the frictional engagement are kept constant and the loose end of the rope can be stored without load. In particular, the load-free rope storage, which avoids winding problems, has the further advantage that the length of the conveyor rope can be of unlimited length.

The following exemplary embodiments of the invention reveal further advantageous features and special features, which are described and explained in more detail below with reference to the illustration in the drawings.

Fig. 1

eine Prinzipskizze des Ausbildungsschemas;

Fig. 2 bis 5

Abwandlungen der Prinzipskizze nach Fig. 1;

Fig. 6

eine Seitenansicht eines Ausführungsbeispieles einer Fördervorrichtung nach Fig. 4 mit Teil-Schnitt A-A' gemäß Fig. 7;

Fig. 7

eine Vorderansicht mit Teil-Schnitt B-B' einer Fördervorrichtung gemäß Fig. 6;

Fig. 8

einen Teil-Querschnitt durch die Treibscheibe.

Show it

Fig. 1

a schematic diagram of the training scheme;

2 to 5

Modifications to the schematic diagram of Fig. 1;

Fig. 6

a side view of an embodiment of a conveyor device of Figure 4 with partial section AA 'of FIG. 7.

Fig. 7

a front view with partial section BB 'of a conveyor device according to FIG. 6;

Fig. 8

a partial cross section through the traction sheave.

In Fig. 1 the basic operation of the conveyor device according to the invention is shown. The load 38 exerts a tensile force on the load end 36 of the conveyor cable 1, which is guided around the deflection pulley 2 and the traction sheave 3 and exits the conveyor device with its loose end 37. The deflection pulley 2 and the traction sheave 3 are mounted with the center distance B from one another. The deflection rollers 5, 6 are at an attachment point 39 attached to a fixed, load-bearing suspension point. The endless outer ropes 4 are guided around the deflection rollers 5, 6 and the traction sheave 3, the conveyor cable 1 resting on the traction sheave 3 between the endless outer ropes 4 and the traction sheave 3. By means of a compression spring 21 acting between the axes 12, 13 of the deflection rollers 5, 6 and the axis 11 of the traction sheave, the endless outer ropes 4 are pretensioned even without an active load 38. The pulling force exerted by the load 38 on the conveyor cable 1 now causes the deflecting disc 2, which is variable in the distance to the deflecting rollers 5, 6, and the deflecting disc 2, which is mounted in the center distance B for this purpose, connected by means of the spacing and the shortest center distance B connecting element 7, in which distance-variable center distance A to the deflection rollers 5, 6 mounted traction sheave 3 together move away from the deflection rollers 5, 6. By increasing the center distance A, the pretensioning of the endless outer ropes 4 and, by self-pressing, the frictional engagement between the conveyor rope 1 and the drive pulley 3 increase. 6, the deflection pulley 2 and the traction sheave 3 are arranged next to one another in approximately the same direction, because then the force effects on the center distances A, B come into play best.

FIG. 2 shows the same as FIG. 1, and FIGS. 3 to 5 show, for comparison, other possible arrangements that work according to the same principle that effects self-pressing. The basic arrangement shown in Fig. 3 differs from that in Fig. 2 in that the compression spring 21 does not act between the deflection rollers 5, 6 and the drive pulley 3, but between the deflection rollers 5, 6 and the deflection pulley 2. Because of the spacing Connecting element 7, the shortest Center distance B between the deflection pulley 2 and the traction sheave 3 is limited, but the pressure force exerted by the compression spring also has an increasing effect on the axis distance A between the deflection rollers 5, 6 and the traction sheave 3.

4 shows an arrangement in which, in contrast to FIGS. 2 and 3, the axis 10 of the deflection sheave 2 is not arranged in the region of the center distance A between the deflection sheaves 5, 6 and the drive sheave 3, but the deflection sheaves 5, 6 are arranged in the region of the center distance B between the deflection disk 2 and the drive disk 3. The deflection rollers 5, 6 are again fastened to an attachment point 39 at a fixed, load-bearing point. The spacing connecting element 7 delimits the shortest center distance B between the deflection sheave 2, which is mounted variable in distance to the deflection rollers 5, 6, and the traction sheave 3, which is also shiftable in the distance between the axes A, with respect to the deflection rollers 5, 6. One acting between the deflection rollers 5, 6 and the drive sheave 3 Compression spring 21 brings about the pre-tensioning of the endless outer ropes 4 without load 38. When the load is on, the deflection pulley 2 moves towards the deflection pulleys 5, 6 and the traction sheave 3 away from them.

Fig. 5 shows a further basic arrangement, which differs from that in Fig. 4 in that instead of the compression spring 21 between the guide rollers 5, 6 and the drive pulley 3, a tension spring 22 is arranged between the guide plate 2 and the guide rollers 5, 6 .

Fig. 6 shows an embodiment of the pulling device according to the principle of Fig. 4 in a side view. The deflection rollers 5, 6 can be adjusted separately from one another in their axial distances A1 and A2 from the conveyor disc 3 by means of eccentric disks 29, to compensate for different lengths of the endless outer ropes 4, for example when assembling the conveyor device or when replacing worn endless outer ropes 4, or to be able to retension them as they age. The eccentric discs 29 are adjustable by means of a clamping tool engaging in the mounting bushes 30 and can be locked by means of the fastening elements 31. The spacing connecting element 7 acts between the bearing housing 18 of the deflection pulley 2 and the bearing housing 19 of the traction sheave 3. Alternatively, instead of the spacing connecting element 7, a common bearing housing defining a fixed center distance B between the deflection pulley 2 and traction sheave 3 can be formed. In the holder 20 of the deflection rollers 5, 6, which is connected to the eccentric discs 29, a cutout 40 is arranged, which allows the movement of the shaft 27 of the deflection pulley 2 when the conveyor device is loaded or when the endless outer cables 4 are elongated due to aging. The guide pin 9 prevents the bearing housing 19 of the traction sheave 3 from rotating relative to the holder 20. The traction sheave 3 can be driven by means of the oil motor 34 serving as drive 32 and a gear 33 and the holding brake 35 can be braked.

In Fig. 7, the conveyor device according to Fig. 6 is shown in front view, in contrast to Fig. 6, the deflection rollers 5, 6 in the same-axis storage, as is the case with identical lengths of the endless outer cables 4, are shown, so that the center distances A1 and A2 to the traction sheave 3 are both equal to A. The torque support 8 designed as a round guide prevents the traction sheave 3 from evading laterally when the conveyor cable 1 is loaded. The axis 10 of the deflection pulley 2, the axis 11 of the traction sheave 3 and the axes 12, 13 of the deflection rollers 5, 6 are not exactly next to one another here in one direction arranged, but the axis 11 of the traction sheave 3 is offset slightly to the side, which simplifies the cable guide in the conveyor device on the loose end 37 of the conveyor cable 1. The force of the compression springs 21 can be adjusted by means of the adjusting elements 23. By means of the end stops 24, which are designed as bolts, of the adjusting elements 23, the force of the compression springs 21 can be easily adjusted to the value provided in the factory when the conveyor device is installed.

8 shows in a partial cross section through the traction sheave 3 how the guidance of the conveyor cable 1 on the traction sheave is shaped as a radius groove 25 with wedge-shaped flanks 26 adjoining on both sides, which guide the endless outer cables 4.

Claims (20)

Conveying device on rope conveying systems for driving at least one conveyor rope guided over a traction sheave, partially wrapping around it, with endless outer ropes guided around the conveyor rope and the traction sheave, wrapping the traction sheave partially under tension and exerting an increased frictional connection between the conveyor rope and the traction sheave,

characterized,

that the conveyor cable (1) is guided around a non-driven deflection sheave (2) which is mounted at an axial distance (B) from the drive sheave (3) and the endless outer cables (4) are parallel to the drive sheave (3) and deflection sheave (2) on both sides Supported deflection rollers (5, 6) are guided, to which the traction sheave (3) is mounted at an axial distance (A) which is variable in distance. Conveying device according to claim 1, characterized in that the deflection rollers (5, 6) are mounted with different axes at axial distances (A1, A2) to the drive pulley (3). Conveying device according to claim 1, characterized in that the axis (10) of the deflection sheave (2) lies in the region of the center distance (A) between the drive sheave (3) and the deflection rollers (5, 6). Conveying device according to claim 1, characterized in that the axes (12, 13) of the deflecting rollers (5, 6) lie in the region of the center distance (B) between the drive pulley (3) and the deflecting pulley (2). Conveying device according to claim 1, characterized in that the axis (10) of the deflecting disc (2), the axis (11) of the traction sheave (3) and the axes (12, 13) of the deflecting rollers (5, 6) lie in one plane. Conveying device according to claim 1, characterized in that the deflecting disc (2) and the traction sheave (3) are mounted by means of bearings (14, 15) in bearing housings (18, 19) which are connected to one another by means of a spacing connecting element (7). Conveying device according to claim 6, characterized in that the deflecting rollers (5, 6) are mounted by means of bearings (16, 17) in a spring-loaded holder (20) which, by means of a straight guide (8), is opposite the bearing housing (18) of the deflecting disc (2) and / or the bearing housing (19) of the traction sheave (3) is displaceable. Conveying device according to claim 6, characterized in that the straight guide (8) is designed as a round guide. Conveying device according to claims 3 and 7 or claims 4 and 7, characterized in that the spring tension is directed to an increase in the center distance (A) between the traction sheave (2) and the deflecting rollers (5, 6) and from compression springs (21) or Tension springs (22) is generated. Conveying device according to claim 9, characterized in that the prestressing of the compression springs (21) or the tension springs (22) can be adjusted by means of adjusting elements (23). Conveying device according to claim 10, characterized in that the adjusting elements are set screws (23) and the compression springs (21) or tension springs (22) are helical or cup springs. Conveying device according to claim 1, characterized in that the guide of the conveyor cable (1) on the traction sheave (3) is shaped as a radius groove (25) with wedge-shaped flanks (26) adjoining on both sides. Conveying device according to claims 2 and 7, characterized in that one or both distances (A1, A2) between the traction sheave (3) by means of one or two adjustable eccentric disks (29) arranged on the holder (20) of the deflecting rollers (5, 6) ) and the two deflection rollers (5, 6) can be adjusted independently of one another. Conveying device according to claim 13, characterized in that the eccentric discs (29) are adjustable by means of a clamping tool engaging in mounting bushes (30) and can be locked by means of fastening elements (31). Conveying device according to claim 1, characterized in that a hand crank or a motor drive (32) can be connected to the shaft (28) serving to support the traction sheave (3). Conveying device according to claim 15, characterized in that between the traction sheave (3) and the drive (32) a gear (33), preferably a planetary reduction gear or a spur gear is engaged. Conveying device according to claim 16, characterized in that the gear (33) can be driven by means of an oil motor (34). Conveying device according to one of claims 15 to 17, characterized in that the traction sheave (3), the motor drive (32) or the gear (33) can be braked by means of a holding brake (35). Conveying device according to at least one of claims 16 to 18, characterized in that the gear (33) is installed in the traction sheave (3). Conveying device according to at least one of claims 1 to 19, characterized by the use as a lifting, pulling or conveying unit for lifting, lowering, recovery or similar conveyor systems for loads.

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