EP1918171B1 - Pulley array for supporting and guiding a support/haulage cable and mechanical ascending system with such a pulley array - Google Patents

Abstract

The device (10) has rollers (G1-G8) assembled at ends of primary balancers (13a-13d) which are articulated by connecting axles (15a-15d) at secondary balancers (16a, 16b). The axles (15a-15d, 17a, 17b) are shifted with respect corresponding balancers, so that ratios of lever arms in a balance state with a tensioned cable cause a non-uniform angular deflection of the rollers. The deflection of the rollers is progressive at an input and degressive towards an output to obtain a preset trajectory of a mechanic ascending support/haulage cable (11) during its progression on the rollers.

Description

Technical field of the invention

The invention relates to an articulated rocking device for supporting and guiding a carrier-tractor-lift aerial rope, comprising a plurality of rollers rotatably mounted at the ends of primary rockers articulated by first link axes. secondary rockers, themselves articulated by second connecting pins to at least one other balance, and so on according to the number of rollers, and a pivot fixed to the carrier structure by a central balance, said pivot extending parallel to the connection axes of the different primary and secondary balances ...

State of the art

In transport installations of the chairlift or gondola type, the carrier-tractor cable is guided and maintained by a plurality of rollers disposed on support rockers and compression balances, which are carried by pylons distributed between the departure stations and the 'arrival. Seats or cabins are fixed to the cable by fixed or detachable gripping clamps. The rollers are generally associated in pairs by being mounted at the ends of primary balances, articulated in their middle part at the ends of secondary balances, themselves mounted in the same manner on tertiary balances, and so on depending on the number of pebbles. The last beam forms a hinged beam articulated in its middle part to a bracket constituting the carrying structure of the pylon. Such a standardized arrangement allows the rollers to follow the path of the cable with a homogeneous distribution of the load on the rollers, and secondly a homogeneous distribution of the deflection angle of the balance between the rollers.

In normal operation between two successive pylons, the vehicles carried and towed by the carrier-tractor cable are driven in a substantially straight motion before reaching the roller balancer on a pylon. During the passage of the latter, the abrupt change of the rectilinear trajectory into an arcuate trajectory generates a centripetal acceleration that affects the comfort of the passengers in the vehicle, and causes high mechanical stresses for the equipment. The feeling of discomfort is further amplified by the shock effect created when the vehicle's pliers come into contact with the first roller.

The document FR-A-2604138 describes a support beam comprising a succession of pairs of elementary rollers for maintaining in line an aerial cable to the right of a pylon. In order to keep all the rollers in contact with the cable, biasing means constantly exert pressure forces on the end rollers. The structure of such a balance remains complicated and expensive.

The document EP 230814 relates to a device for holding two parallel carrying cables and tractors, in which each beam is in two parts placed on either side of the rollers. The corresponding support rockers associated with the two cables are not connected mechanically between them, and means are provided to limit the amplitude of pivoting of the rockers about their axis.

Object of the invention

The object of the invention is to provide an articulated rocker device for supporting and guiding a tractor carrying cable of a mechanical lift, to improve the comfort of transport of travelers to the passage of a pylon.

The device according to the invention is characterized in that the first and second link axes are offset relative to the middle of the primary and secondary balances corresponding so that the reports of the lever arms in equilibrium with the tensioned cable , generate a non-uniform angular deflection of the rollers, which is progressive at the entrance and degressive towards the output to obtain a predetermined path of the cable during its path on the rollers.

According to a preferred embodiment, the path of the cable comprises a clothoid portion at the entrance and the exit. The pivot is located in the middle of the center beam, and the different eccentric rockers are arranged symmetrically with respect to the median plane passing through the pivot.

The trajectory in clothoid results from the choice of lever arm ratios, which acts on the centripetal acceleration during the path of the vehicle on the various rollers. The centripetal acceleration is relatively low at the inlet, then gradually increases at the level of the intermediate rollers up to a maximum value in the center. It then gradually decreases at the level of the rollers arranged towards the exit. This results in a reduction of the shock received by the vehicle during the passage to the right of the pylon. The radius of curvature of the trajectory is important at the entrance, then it gradually decreases to reach a minimum value in the middle of the pendulum device. It then gradually increases to the exit where the radius of curvature is important again.

The rollers can be mounted in pairs on the primary and secondary balances. It is also possible to distribute the pebbles sometimes in even numbers, sometimes in odd numbers on the different pendulums.

The rollers may have identical diameters or different sizes. In particular, the input and output rollers have smaller sizes than intermediate rollers.

Brief description of the drawings

• la figure 1 est une vue schématique en élévation d'un dispositif balancier à galets selon l'invention, lequel est représenté dans l'état d'équilibre avec le câble sous tension;
• la figure 2 montre un diagramme de l'accélération centripète d'un véhicule lors de son cheminement le long des galets du dispositif balancier de la figure 1 ;
• la figure 3 représente un diagramme de la répartition des charges sur les galets;
• les figures 4 et 5 sont des vues identiques de la figure 1 de deux variantes de réalisations.

Other advantages and features will emerge more clearly from the following description of an embodiment of the invention given by way of non-limiting example, and represented in the accompanying drawings, in which:

• the figure 1 is a diagrammatic elevational view of a roller balance device according to the invention, which is shown in the equilibrium state with the cable under tension;
• the figure 2 shows a diagram of the centripetal acceleration of a vehicle during its path along the rollers of the pendulum device of the figure 1 ;
• the figure 3 represents a diagram of the distribution of loads on the rollers;
• the figures 4 and 5 are identical views of the figure 1 two variants of achievements.

Description of a Preferred Embodiment

With reference to the figure 1 , a rocking device 10 for supporting and guiding an aerial cable 11 carrier-tractor lift mechanical, comprises a plurality of rollers G 1 to G8 mounted in pairs on primary balances 13a, 13b, 13c, 13d. The rollers G1 to G8 of each pair are mounted to rotate freely at opposite ends of the primary balances 13a, 13b, 13c, 13d.

Each roller G1 to G8 has on its periphery an annular groove (not shown) for guiding the cable 11 along the path of travel. The rollers G1 to G8 have the same diameters, and are rotatably mounted on pins 14, 12 by means of ball bearings. The figure 1 shows by way of example eight rollers G1 to G8 identical for four primary balances 13a, 13b, 13c, 13d.

The four primary balances 13a, 13b, 13c; 13d are articulated by first connecting pins 15a, 15b, 15c, 15d at the ends of two secondary balances 16a, 16b, which are themselves interconnected by a central beam 17 whose ends have second connecting pins 17a, 17b. Additional pendulums may of course be used depending on the number of rollers G1 to G8 elementaire equipping the device pendulum 10.

The central rocker 17 serves as a support rocker formed by a rectilinear beam connected to the supporting structure of the pylon (not shown) by a pivot 18, which extends parallel to the connecting axes 15a, 15b, 15c, 15d, 17a, 17b of the different primary and secondary balances.

The pivot 18 of the central balance 17 is located in the middle of the beam and in the median plane PM of the rocker device 10, while the connecting pins 15a, 15b, 15c, 15d, 17a, 17b are offset relative to the center of the rockers primary 13a, 13b, 13c, 13d and secondary 16a, 16b corresponding. The two primary balances 13a, 13b located to the left of the median plane PM are arranged symmetrically with respect to the other two primary balances 13c, 13d of right. It is the same secondary balances 16a, 16b arranged symmetrically with respect to the median plane PM.

In the state of equilibrium with the cable 11 under tension, the ratios of the lever arms at the first link axes 15a, 15b, 15c, 15d of the primary balances 13a, 13b, 13c, 13d and secondary 16a, 16b cause a distribution of the loads on the rollers G1 to G8 to obtain a predetermined trajectory. The latter is also defined by the reaction of the lever arm ratios of the central balance 17 on the secondary rockers 16a, 16b at the second link axes 17a, 17b.

The ratio K1 of the lever arms 15a-12 and 15a-14 of the left primary balance 13a is identical to that of the lever arms 15d-14 and 15d-12 of the right primary balance 13d. In the example of the figure 1 this ratio K1 is equal to 0.42.

The ratio K2 of the lever arms 15b-12 and 15b-14 of the primary balance 13b to the left of the plane PM is identical to that of the lever arms 15c-14 and 15c-12 of the primary beam 13c to the right of the plane PM. In the example of the figure 1 this ratio K2 is equal to 0.7.

The ratio K3 of the lever arms 17a-15b and 17a-15a of the secondary beam 16a of the left is identical to that of the lever arms 17b-15c and 17b-15d of the right secondary beam 16b right. This ratio K3 is equal to 0.37 in the example of the figure 1 .

With reference to the figure 2 it is noted that the adoption of the lever arm ratios K1, K2, K3 acts on the centripetal acceleration during the path of the vehicle on the various rollers G1 to G8. The centripetal acceleration is relatively low at the inlet (left end roller G1), then gradually increases at the intermediate rollers G2 and G3 to a maximum value in the center (rollers G4 and G5). It then gradually decreases at the rollers G6 and G7, to be low at the output (end roller G8 right). This results in a reduction of the shock experienced by the vehicle during passage in the pendulum device 10.

On the figure 3 the loading of the rocker device 10 by the tension of the cable 11 causes an angular deflection by progressive roller at the inlet (rollers G1 to G3), then constant (rollers G4 and G5 of the middle), and finally degressive at the outlet ( rollers G6 to G8). The reaction exerted by the cable 11 on the rollers G1 to G8 is no longer uniform as in the case of the rockers of the prior art, but is variable by gradually increasing the input of the rocker device 10, then is constant and gradually decreases in exit.

The path of the cable 11 on the rocker device 10 is determined by the lever arm ratios K1, K2, K3:

At the entrance, the trajectory of the cable 11 on the rollers G1 to G4 is no longer an arc as in a conventional balance wheel where each ratio of the lever arms K1, K2, K3 is equal to 1, but a portion of clothoid. It is the same on the rollers G5 to G8 at the output of the rocker device 10 with a second portion of clothoid. The two portions of clothoids can be joined at the median plane PM, or connected to each other in the central part by a small intermediate arc.

The radius of curvature of the path of the cable 11 is thus important at the input, then it gradually decreases to reach a minimum value in the middle of the balance device 10. It then increases progressively to the exit where the radius of curvature is again important .

According to the variant of the figure 4 , only the rollers G1, G2 and G7, G8 are mounted in pairs on the primary balances 13a and 13d at the ends of the rocker device 10. The secondary rockers 16a, 16b support at one of their ends a primary beam 13a, 13d, and at the other end a roller G3, G6 alone. The link axes 15a, 15d are also off-center as in the figure 1 so that the ratios of the lever arms make it possible to obtain equilibrium with the cable 11 under tension, a load distribution on the rollers adapted to the desired trajectory, in particular in the form of a portion of clothoid. In the same way, tertiary balances 20a, 20b support at one of their ends a secondary beam 16a, 16b and at the other end a roller G4, G5 alone. A central beam 21 supports the two tertiary beams 20a, 20b, with the eccentric connecting pins to create lever arm ratios to delimit the desired path. The central balance 21 serves as a support balance bearing in its center the central pivot 18, which extends parallel to the connecting axes of the different primary, secondary, and tertiary balances.

On the other variant of the figure 5 , the distribution of the primary balances 13a, 13b, 13c, 13d, secondary balances 16a, 16b, and the central balance 17 corresponds to that of the figure 1 , with end rollers G1, G2 and G7, G8 having diameters smaller than those of the intermediate rollers G3 to G6. This combination of several sizes of rollers makes it possible to make variable spacings between the rollers of the rocker device 10.

The clothoid portions of the path of travel of the cable 11 on the rocker device 10 according to any one of the embodiments of figures 1 , 4 and 5 , or by a combination of these, allow to better distribute the centripetal acceleration and efforts by pebbles, in order to improve the comfort of transport of travelers to the passage of a pylon.

Based on the calculation of the ratios of the lever arms K1, K2, K3, it is clear that the portions of clothoids of the trajectory can be replaced by other curves advantageously between a circular arc and a clothoid portion.

The invention is applicable to support beams and compression balances of a ropeway lift installation, including a gondola, a cable car, or a chairlift.

Claims (10)

1. An articulated sheave assembly for pressing and guiding an aerial carrying-hauling rope (11) of a mechanical lift, comprising:

   - a plurality of sheaves (G1 to G8) mounted rotating on the ends of primary sheave assemblies (13a, 13b, 13c, 13d) articulated by first connecting swivel-pins (15a, 15b, 15c, 15d) on secondary sheave assemblies (16a, 16b) themselves articulated by second connecting swivel-pins (15a, 15b, 15c, 15d) on at least one other sheave assembly, and so on depending on the number of sheaves,

   - and a pivot (18) fixed to the support structure via a central sheave assembly (17, 21), said pivot extending in a direction parallel to the connecting swivel-pins of the different primary, secondary etc. sheave assemblies,

   characterized in that the first and second connecting swivel-pins (15a, 15b, 15c, 15d; 17a, 17b) are offset with respect to the middle of the corresponding primary sheave assembly (13a, 13b, 13c, 13d) and secondary sheave assembly (16a, 16b) so that the leverage ratios (K1, K2, K3) in the equilibrium state with the taut rope cause a non-uniform angular deflection of the sheaves (G1 to G8), which deflection is progressive on ingress and degressive on egress to obtain a predetermined trajectory of the rope (11) when the latter is conveyed on the sheaves (G1 to G8).
2. The articulated sheave assembly according to claim 1, characterized in that the trajectory of the rope (11) comprises a clothoid portion on ingress and egress.
3. The articulated sheave assembly according to claim 1 or 2, characterized in that the pivot (18) is located in the middle of the central sheave assembly (17,21).
4. The articulated sheave assembly according to claim 3, characterized in that the different eccentric sheave assemblies located on each side of the pivot (18) are arranged symmetrically with respect to the mid-plane passing through said pivot (18).
5. The articulated sheave assembly according to any one of claims 1 to 4, characterized in that the sheaves (G1 to G8) are mounted in pairs on the primary sheave assembly (13a, 13b, 13c, 13d) and secondary sheave assembly (16a, 16b).
6. The articulated sheave assembly according to any one of claims 1 to 4, characterized in that the sheaves (G1 to G8) are mounted either in pairs or in an odd number on the different sheave assemblies.
7. The articulated sheave assembly according to claim 5 or 6, characterized in that the sheaves (G1 to G8) present identical diameters.
8. The articulated sheave assembly according to claim 5 or 6, characterized in that the sheaves (G1 to G8) present different diameters.
9. The articulated sheave assembly according to claim 8, characterized in that the ingress sheaves (G1, G2) and egress sheaves (G7, G8) have smaller sizes than those of the intermediate sheaves (G3 to G6).
10. A rope transport installation, in particular a chair-lift or a cable-car, comprising at least one articulated pressing and guiding sheave assembly according to any one of claims 1 to 9.

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