FI123919B - Suspension arrangement for a drive pulley elevator - Google Patents

Abstract

The invention relates to a suspension arrangement for a traction elevator, said elevator comprising at least a hoisting machine (5) and an elevator car (1) suspended on and supported by a set of hoisting ropes (3) by means of at least rope sheaves (11, 12) serving as diverting pulleys, which elevator car (1) has been fitted to travel in a substantially vertical direction along guide rails (4), and a substantially vertically movable counterweight (8) provided with a rope sheave (13) and fitted to move along guide rails (9), said elevator additionally comprising at least one fixed rope sheave (6) rotating in place. The rope force (Fc, Fcw) of the hoisting ropes in the hoisting rope portion (3a, 3b) between a rope sheave (12, 13) moving substantially vertically in the elevator shaft and the fixed rope sheave (6) rotating in place has been adapted to vary as a function of the vertical distance between the vertically movable rope sheave (12, 13) and the rope sheave (6) fixedly mounted in place.

Description

DRIVE WHEEL ASSEMBLY

The invention relates to a suspension arrangement of a traction sheave elevator as defined in the preamble of claim 1.

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In counterbalanced traction sheaves, the weight of the hoisting rope causes an imbalance between the elevator car and the counterweight when the height difference between the elevator car and the counterweight is large. The imbalance is greatest with the elevator car at the top of the his-10 shaft and the counterweight at the bottom of the shaft or vice versa. This is a problem with high-lift elevators because these lifts have long and heavy lifting ropes. Due to the large height difference between the elevator car and the counterweight and the heavy lifting ropes, the imbalance may increase to such an extent that the friction between the lifting ropes and the traction sheave ropes is not sufficient to allow the lifting rope to slip on the traction sheave. The imbalance caused by the hoisting ropes in elevators with lower lifting heights is not essential because it is relatively small, so that it can be neglected, but the large imbalance at higher lifting heights must be compensated in some way. The aforementioned imbalance must generally be compensated for in elevators whose lift height exceeds a certain limit, typically about 30 to 40 meters.

25 ^ It is known that the imbalance o cvJ between the elevator car and the counterweight is compensated by the so-called. with compensating ropes secured at their first ends to the lower part of the elevator car and from their second ends to the lower part of the counterweight. When the elevator car is at the bottom of the elevator shaft x 30, there is a counterweight at the top of the shaft and

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The hoisting rope portion o g of the traction sheave of the traction sheave is long and heavy. However, in this case, the compensation ropes hanging from the lower part of the counterweight are also long and heavy, thereby compensating for the imbalance caused by the hoisting ropes in the traction sheave. However, the problem with the use of compensation ropes is that the compensation ropes cause additional costs and in addition, the ropes may be in the way in some cases, such as in maintenance situations. In addition, compensating ropes increase the weight of the entire elevator 5, which may require the structures of the elevator to be made stronger, which also increases costs.

EP1724229 A1 shows in Fig. 9 an elevator suspension arrangement in which the angle of the hoisting rope 10 from the traction sheave to the counterweight changes with the vertical as the height of the counterweight changes. However, said publication is not intended to solve the same problem as in the arrangement of the present invention, and there is no mention of angle change in the specification. The angle change results from the placement of the hoisting machinery in a lay-out position as close as possible to the elevator car. Hereby, the traction sheave has had to be positioned laterally further away from the counterweight deflection pulley, whereby said angle is created.

It is an object of the present invention to eliminate the aforementioned drawbacks and to provide a simple and inexpensive suspension arrangement for a counterweight elevator by means of which the imbalance of the rope forces, i.e. the difference between the two sides of the traction sheave, can be reduced. At the same time, the goal is to build 25 elevators with higher lifting heights without the use of compensating ropes. It is a further object of the invention that, in lifts with a lifting height so high that compensation ropes are required anyway,

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less known solutions are needed. According to the invention,

The arrangement 30 is characterized by what is set forth in the characterizing part of Q 1. Similarly, other embodiments of the invention are characterized by what is disclosed in other claims,

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Inventive embodiments are also disclosed in the specification of this application. The inventive content contained in the application may also be defined otherwise than as set forth in the claims below. The inventive content may also consist of several separate inventions, especially if the invention is considered in the light of its expressions or implicit subtasks, or in terms of the benefits or classes of benefits achieved. In this case, some of the attributes contained in the claims below may be redundant for individual inventive ideas. Similarly, the various details presented in connection with each embodiment of the invention may also be used in other embodiments. In addition, it can be noted that at least some of the sub-claims can be considered as inventive as such, at least in appropriate situations.

An advantage of the arrangement according to the invention is that the height imbalance caused by the height difference between the elevator car and the counterweight is not as great as in conventional suspension solutions, whereby the compensating ropes can be omitted at higher lifting heights. This can reduce costs. A further advantage is that the arrangement is simple and inexpensive to implement.

The invention will now be described in more detail by way of one embodiment with reference to the accompanying drawings, in which FIG. 1 is a simplified, schematic view of x 30 and a side view of an

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Fig. 2 is a simplified and schematic view oo and a side view of another counterweight 4-wheel drive elevator using another embodiment of the solution of the invention, Figs. 3-5 showing a different embodiment of the solution of Fig. 2. Fig. 6 is a schematic and simplified plan view of the embodiment of Fig. 4, and Fig. 7 is a simplified and schematic view of the third embodiment of a traction sheave elevator according to the third embodiment of the invention. .

Figure 1 is a side elevational and schematic view of one elevator solution in which the invention can be applied. The elevator in the figure is a counterweight and non-machine driven traction sheave elevator, in which the hoisting machine 5 with traction sheave 6 controlled by the control unit 7 is located at the top of the elevator shaft 20. The elevator car 1 is disposed within the basket frame 2 and is suspended from the hoisting rope 3 and adapted to move back and forth in the elevator shaft substantially vertically along the rails 4. The lift receives its lifting power from the hoisting machine 5 due to the friction between the traction sheave 6 and the hoisting rope 3. The elevator counterweight 8 is suspended from the hoisting rope 3 Γ "» o on the opposite side of the traction sheave 6 as the elevator car c \ i τΐ 1. The counterweight 8 is adapted to move in the elevator shaft substantially vertically guided by its own guides 9. FIG.

£ 30 § The hoisting rope 3 is secured at its first end to the first anchorage point o £ 3 10 at the top of the elevator shaft, from which it is guided to rotate underneath the folding wheels 11 and 5 12 mounted on the underside of the car frame 2. The hoisting rope 3 is arranged to rotate over the traction sheave 6, after which the hoisting rope 3 is guided beneath a diverting pulley 13 attached to the upper part of the counterweight 8, from which the hoisting rope 3 is secured at its other end. The part of the hoisting rope 3 relative to the drive wheel 6 of the lift car 1 is indicated in the figure by 3a and the part of the counterweight 8 by 3b.

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The counterweight 8 is disposed such that the outer edges of the traction sheave 6 and the diverting pulley 13 attached to the upper part of the counterweight 8 are horizontally spaced "a" apart so that the portion of the hoisting rope 3 between the diverting pulley 13 and the traction sheave 15 6 is vertical. a variable angle α, the magnitude of which depends on the height at which the counterweight 8 is at any time in the elevator shaft. Correspondingly, the second lashing strap 14 of the hoisting rope 3 is disposed horizontally at the same distance 20 "a" from the second outer edge of the diverting pulley 13 so that also the portion 3b of the hoisting rope 3 between the second anchorage point 14 and the diverting pulley 13 forms an angle? The suspension of the counterweight 8 is thus symmetrical with respect to the vertical line, since the angle 25 of the hoisting rope part 3b 3b with respect to the vertical line is the same on both sides of the counterweight 8. The higher the counterweight 8, the greater

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angle a is. Correspondingly, as counterweight 8 moves downward in the shaft, angle α decreases.

x tr 30 The rope forces acting on the traction sheave 6 with the elevator car stationary § in place may be represented by the following formulas: coo n- o Fc = (C / 2 + h * mr) * g (Formula 1) 6 where:

Fc = rope force on the lift car side C = total mass of the car and load 5 h = lifting height mr = metric weight of the rope g = acceleration due to gravity of the ground

Fot = (CW / 2 + b * mr) * SQRT (a2 + b2) / b) * g (Formula 2) 10 where: F ^ = rope force on the counterweight side CW = counterweight mass 15 b = vertical distance of the center line of the counterweight pulley from the attachment point mr = meter weight of rope g = acceleration rate of fall caused by the gravity of the ground 20 As the elevator car moves, the effect of the acceleration of the elevator car must be added to the formula so that depending on the direction of the elevator it increases or decreases g.

In the following, the rope forces on both sides of the traction sheave will be calculated, by way of example, in the solution according to the invention and in comparison with a known structure in which the portion of the hoisting rope between the wheel 13 and the traction sheave

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is vertical, with the angle a = 0 and the aforementioned horizontal distance "a" = 0.

^ 30 x £ Suppose: o co g C = 1300 kg m § CW = 1000 kg

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35 mr = 1.2 kg / m 7 a = 0, 33 m h = 30 m g = 9.81 m / s 2 5 The values used in the prior art elevator are otherwise the same, but the horizontal distance "a" is thus zero. The differences in rope forces are shown in the following table with the elevator car 1 in three different elevation positions, i.e., just below, approximately in the middle and just above. In this case, the counterweight 8 10 is respectively in the opposite elevation positions except for the center position.

Elevator according to the invention Prior Art Elevator (a = 0)

Basket down h = 31, b = l Basket down h = 31, b = l Fc = 6741 N Fc = 6741 N

Fot = 5178 N F ^ = 4917 N

Fc ^ cw = 1563 N F ^ F * = 1824 N

Basket in the middle h = 16, b = 16 Basket in the middle h = 16, b = 16 Fc = 6565 N Fc = 6565 N

FCT = 5094 N F ^ = 5093 N

Fc _ F ^ = 1471 N Fc-Fa. = 1472 N

Basket down h = 31, b = l Basket down h = 31, b = l F_ = 6388 N F = 6388 N

g FCT = 5270 N F ^ = 5270 N

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^ FC.FCW = 1118 N Fc _ F ^ = 1118 N

V 15

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The difference in the difference between the rope forces in the lower and upper positions of the elevator car, i.e. (Fc F ^) DOWN POSITION0 - (Fc F ^ Jy ^^ j ^, o

g 445 N 706 N

From the above it is clearly seen that the solution according to the invention significantly increases the rope force of the rope portion 3b of the counterweight 8 of the traction sheave 6 when the elevator car 1 is in the down position and the counterweight 8 in the up position. In this way, the difference in rope forces on each side of the drive wheel 6 is reduced, and thus the imbalance is also reduced. From the mass of the calculation-5, it is also seen that the imbalance between the lower and upper positions of the elevator car 1 is significantly reduced. Due to the suspension arrangement according to the invention, the imbalance caused by the height difference between the elevator car 1 and the counterweight 8 is not as great as in conventional suspension solutions and the compensation ropes 10 can be omitted at higher lifting heights.

Figure 2 is a side elevational view, both simplified and schematically, of an elevator solution 15 similar to Figure 1, in which another embodiment of the arrangement according to the invention is used. This embodiment differs from that shown in Fig. 1 in that the lifting rope 3 is guided from the drive wheel 6 to rotate the diverting wheel 13 attached to the upper part of the counterweight 8 in a different manner than in the solution of Fig. 1. In this case, the lifting ropes coming from the pulley 6 of the pulley 20 13 are obliquely downwardly directed to the pulley 13 via an edge further away from the pulley 6 of the pulley. Thereafter, the lifting ropes rotate underneath the diverting pulley 13 and rise through the proximal edge of the diverting pulley 6, and the vi-25 lifts up when it intersects with the incoming lifting ropes o above the diverting pulley 13.

Figures 3-5 illustrate schematically and simplified embodiments of the solution of Figure 2, and

Er 30 viewed from above. In the figures, reference numeral 3b

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only one hoisting rope. This hoisting rope 3b is the pulling rope of the outermost wheel 6 and is illustrated by marking the same rope 3b o 13 also on the diverting wheel 13 or on the other side of the diverting wheel.

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In the embodiment shown in Fig. 3, the counterweight diverting pulley 13 is rotated sideways with respect to the traction sheave 6 so that the lifting ropes inclined obliquely from the diverting pulley 13 do not hit the diverting pulley 13 at the intersection of the lifting ropes. In this case, the rope mat consisting of the lifting ropes 3b exiting obliquely upwardly from the diverting pulley 13 completely overrides the roping mat inclined at the intersection at the intersection of the diverting pulley 13. Further, the diverting wheel 13 may be tilted such that the diverting axis 10 forms an angle with respect to the horizontal. The inclination increases the distance of the intersecting lifting ropes at the intersection, so that by suitably tilting the diverting pulley 13, the angle of rotation of the diverting pulley 13 can be reduced. Furthermore, it is possible to turn and / or tilt the drive wheel 6 accordingly.

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In the embodiment shown in Fig. 4, the rope mat guided from the traction sheave 6 obliquely downward to the diverting pulley 13 is wound around the centerline of the rope mat approximately 1802 before guiding the lifting ropes into the rope grooves of the diverting pulley 13. Thus, the rope-20 carpet has pivoted about its longitudinal axis and positioned against the diverting pulley 13 such that the outermost ropes of the rope mat have moved to the opposite side of the middle ropes or middle rope in the case of a rope comprising a plurality of ropes. In this way, the rope mat in the pivoting position 25 comprises a point where the rope ropes are overlaid. In Figure 4, this occurs at the intersection of §, since the arrangement is illustrated from above. In Figure

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the single rope to which reference numeral 3b indicates is the lowest at the point of crossing. Otherwise, the ropes are guided

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30 along the surface of the top wheel 13 in a normal manner j | and in Fig. 4 would appear from the left side o of the diverting pulley 13. This is not shown in the figure for clarity.

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It would be advantageous to arrange the ropes rising from the left to pass past the carpet of the traction sheave 6 at a point where the level of the rope rope from the traction sheave is vertical or at least near this point where the ropes can easily be passed without touching one another. The diverting wheel 13 is preferably, but not necessarily, positioned as shown in the figure, in an oblique position with respect to the traction sheave 6, so that the crossed ropes 5 shown in the figure do not quite touch each other. If the traction sheave 6 and the sheave 13 are positioned in parallel, the ropes will lean against each other. By rotating in Figure 4, the individual ropes drawn into the image are spaced apart. Correspondingly, the lifting ropes rising from the sheave 13 to their anchorage 10 may be guided directly to their anchorage points 14 or, if necessary, twisted once more about the centerline of the rope prior to the anchoring of the ropes to the anchorage points. arranged as shown in Figure 2. Even the slightest twisting of the ropes provides the said benefit as the ropes, when viewed laterally, the more closely they are twisted. As a result of the twisting, the twisted single-strand ropes are spaced vertically apart. Even a slight twisting of the ropes rising from the flywheel to the attachment point is possible because they can be attached to the attachment point 14 with respect to each other in any position. If necessary, in this embodiment as well, the diverting pulley 25 13 and / or the traction sheave 6 may be tilted relative to the horizontal.

The traction sheave 6 and the diverting pulley may also be displaced horizontally relative to that shown in the figure.

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Figure 6 illustrates a three-dimensional view of an embodiment of the embodiment of Figure 4, in which Figure 30 shows the rotation and travel of the ropes around the diverting wheel 13. The rugs formed by the inclined ropes forming the diverting wheel are both twisted o around her shoulders. In the figure, denoted by reference numeral 3b, only 35 of the top wheels 13 are illustrated by the marking of one hoisting rope. The distance of this hoisting rope 3b

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11 individual ropes 3b at different points on the carpet formed by the rope wheels.

In the embodiment shown in Fig. 5, the crossing of the lifting ropes 5 is implemented such that the rope rising obliquely from the diverting wheel 13 is always adjacent to the oblique-down part of the same rope. In this case, each rope intersects with itself, not as in Figure 3 as a whole rope mat. In this embodiment, the spacing between the rope grooves is greater than in the two solutions described above. Likewise, at least the thickness of the folding wheel 13 and, if necessary, the drive wheel 6 is greater than in the above solution. In the figure, the folding wheel 13 is positioned at an oblique position relative to the drive wheel. The diverting pulley 13 and the traction sheave 6 would not necessarily need to be rotated horizontally and / or tilted relative to the horizontal plane, but can be done if necessary.

Fig. 7 is a simplified diagrammatic and side view of yet another counterweight elevator wheel 20 which uses a solution according to the invention. In this solution, in addition to the solution shown in Fig. 1, the angle · of the lifting rope 3 of the hoisting rope 3 between the traction sheave 6 and the elevator car 1 is also changed with respect to the vertical direction as the elevator car 1 moves in the elevator shaft. In Figure 6, the elevator car 25 is depicted with an intact line in its lower position and a dotted line in its up position. With the elevator car 1 in its upper position I · '- § angle · and the rope force Fc acting on the rope section 3a

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i got it up. Similarly, with the elevator car 1 in its lowered position, the angle · and the rope force F acting on the rope part 3a are

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30 at its core. x

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a.

The angle · of the rope section 3a shown in Fig. 7 can also be accomplished by co-locating the lifting ropes 3a with each other as shown in Figs. 2-6. In this case, the hoisting ropes 3a descending from the traction sheave 6 first rotate the diverting pulley 11 located further away from the traction sheave 12 and laterally the horizontal diverting pulley 12, from which the hoisting ropes 3a are inclined obliquely. in the embodiment, the sideways need of the elevator Ti-5 is narrower than in the solution shown in Fig. 7. Also in the arrangement according to this embodiment, the suspension of the rope section 3b can be implemented as in Figs.

It is common to all the above-described embodiments of the invention that the lifting rope portion 3b of the lifting rope of the lifting rope 15b as a function of the vertical distance between the rope pulley 13 and the rigid pulley 6. Hereby, said rope force is increased as the moving rope pulley 13 approaches the rigidly fixed rope pulley 6, and respectively, said rope force F ^ pie-20 is increased as the rope pulley 13 moves away from the rigidly stationary rope pulley 6. The rope of the hoisting ropes portion 3b of the hoisting rope portion 3b between the rope wheel 6 and the hoisting rope 13 moving vertically. The rope force F ^ is then increased by a large ejection of said angle α and, accordingly, the rope force F ^ i ^ is reduced by decreasing said angle a.

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x 30 The rope forces Fc of the hoisting rope 3 on the elevator car 1 side 3a are analogous to that described above in the kappa-o gle. Then the angle is only ·, and as the moving ^ rope pulley, the other impeller 12 of the elevator car.

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It will be apparent to one skilled in the art that various embodiments of the invention are not limited to the examples set forth above, but may vary within the scope of the following claims. Thus, for example, the reduction of the difference in rope power between the traction sheave and the counterweight by said angle can be accomplished by the variable rope angles of the traction sheave and the elevator car instead of the variable rope angles of the counterweight pulley.

10 It will also be clear to one skilled in the art that the suspension of the counterweight or elevator car need not necessarily be symmetrical, i.e. the angle a on both sides of the diverting wheel and the angle of the elevator car respectively need not be equal to each other; may also have a value of zero, whereby the outermost parts of the hoisting rope are substantially vertical.

It will be further apparent to one skilled in the art that a conventional pivoting wheel may also be provided in place of a fixed rotating drive wheel, with the drive wheel being positioned elsewhere in the structure.

It will also be clear to one skilled in the art that lifting ropes ^ 25 may be made to cross in ways other than those described above.

It is also clear to one of ordinary skill in the art that the invention x can be used as well with other suspension ratios and cc 30 in other types of suspension than those exemplified herein. Thus, for example, the number and positioning of the pulleys may vary from the above.

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Claims (10)

1. The invention relates to a suspension arrangement in a drive disk elevator, which elevator comprises at least one lifting machine (5) and a lifting basket (1) which is arranged to move with the aid of eating at least as breaking discs (11, 12). substantially in vertical direction along guides (4), and a counterweight (8) provided with lens disk (13) arranged to move substantially in vertical links along guides (9), and which elevator further comprises at least one fixed, rotating lens disk ( 6), and in which the lift link force (Few) in the rope section (3b) between the substantially vertical link in the lift hook, movable, in the counterweight (8) and the fixed, rotating rope plate (6) is arranged to be changed as a function of the vertical distance between the movable lens plate (13) and the fixed, rotationally positioned lens plate (6), which change of the link force (Few) is arranged by angling (a) between the carrier lines in the line the section (3b) between the movable lining disk (13) and the fixed, rotatable lens plate (6) and the vertical line changes as the movable lens disc (13) moves vertically, characterized in that the changing winch (a) is formed by the movable lens plate (13) in its path of movement is positioned at a horizontal distance from the fixed mounting plate (6) and by means of the carrier lines running downwards to the lens disk (13) and the carrier lines running upwards from the lens disk (13) are intersected above the lens plate (13). Arrangement according to claim 1, characterized in that the link force (Fc, Few) is arranged to be increased as the movable lens plate (12, 13) approaches the vertical mounted plate (6) mounted in a vertical direction and correspondingly is the link force ( Fc, Few) arranged to be reduced when the movable lens plate (12, 13) in vertical direction distances itself from the fixed plate mounted on the rack (6). 3. Arrangement according to claim 1 or 2, characterized in that the link force (Fc, Few) is arranged to be increased by increasing the winkein (β, a) and correspondingly the link force (Fc, Few) is arranged to be reduced by the winkein ( β, a) is reduced. 4. Arrangement according to any of the preceding claims, characterized in that the fixed disk mounted on the rack is the drive disk (6) of the elevator machinery (5). Arrangement according to any one of claims 1-4, characterized in that the vertical plate (13) and the lifting plate (1) fixed in the counterweight (8) and the lifting basket (1) are mounted in the counterweight (8) and fixed in place. the lining disk is the lifting disk (6) of the elevator machinery (5). co Arrangement according to any one of the preceding claims, characterized in that the fixed disk mounted on the rack is a break disc placed in the elevator shaft or in the engine room. i co Arrangement according to any of the preceding claims, characterized in that the carrier lines running downwards to the rope plate (13) and the supporting ropes running upwards from the rope plate (13) are arranged to intersect, for example, in one of the following ways: o the rope plate (13) ) has been laterally rotated so that in relation to the fixedly mounted co-lining plate (6), it is eaten up from the lining disc (13), running from the lining (3b), the lining mat at the intersection point completely and poured downwards against the lining disc (13). o the running lining mat, C \ 1 the entire lining mat which is guided obliquely downwardly into the lining sheet (13) from the fixed mounting plate (6) is twisted like a bundle around the center line of the lining mat (3b) to the lining of the lining sheet (13), each a carrier line running from the rope plate (13) obliquely upright is arranged to always run upright next to the obliquely downwardly running section of the same carrier line, such that each carrier rope crosses itself. Arrangement according to any one of claims 1-6, characterized in that the changing winch (β) of the rope section (3a) between the vertically movable rope plate (12) in the lift basket (1) and the fixed rope plate (6) mounted is formed by placing the movable lens plate (12) in the elevator basket (1) in its movement path at a horizontal distance from the fixed plate mounted on the rack (6). Arrangement according to claim 8, characterized in that the changeable vinkein (β) is formed by the carrier liners (3a) running downwards to the lift basket (1) acting as breaking discs (11, 12) and the carrier liners (3a) running upwards from the the liners (11, 12) are arranged to intersect above the liners (11, 12). Arrangement according to Claim 9, characterized in that the support liners (3a) are arranged to intersect above the lining discs (11, 12) so that the support liners (3a) from the fixed mounting plate (6) are first led obliquely downwards around the longitudinally spaced from the lining disk (6) located the lining disk (11) and thereafter with the shorter horizontal distance spaced from the lining disk (6), and when the carrier liners (3a) have manned them below, they are obliquely upright where they intersect and attached to the sinew fastener (10). co δ c \ j i O) o CO C \ l X cc CL O CO CO o 1 ^ o o CM