EP1550629B1 - Elevator system - Google Patents

Description

The invention relates to an elevator system according to the preamble of claim 1.

The invention is particularly, but not exclusively, suitable for use in connection with a machine room-less elevator system. Such a machine room-less elevator system has the advantage that it takes up less space compared to conventional elevator systems with machine rooms, and in particular it is not necessary to provide above the roof edge upwardly projecting superstructures when installed in flat roof buildings.

From WO 03043922 a flat belt is already known, which is guided around several drive or deflection rollers. With the disposition shown, the shaft space can not be optimally utilized in every case. In particular, the profiled side of the belt can not be used with opposite bending.

The object of the invention is to propose an improved elevator system of the type mentioned, which allows a wider application of a one-sided profiled belt.

This object is achieved in an elevator system of the type mentioned according to the invention by the features of independent claim 1.

Preferred developments and details of the elevator system according to the invention are defined by the dependent claims.

In the new elevator system, the textured belt main surface is engaged with the peripheral surface of both rollers, even when the first one of the rollers rotates counter to the second one of the rollers. This is achieved by the respective located between the two roles Section of the belt is rotated about a rotational angle about its longitudinal central axis.

With this new belt guide it is achieved that the system of rollers and belts can optimally perform a driving function, a supporting function and a guiding function.

The angle of rotation by which the belt is twisted between two rollers running in opposite directions is in some embodiments about 180 ° when the axes of rotation of the two rollers are parallel and the rollers lie approximately in a common plane. There are also roller assemblies in which the axes of rotation of the two rollers are approximately perpendicular to each other. In this case, the angle of rotation of the belt is about 90 °.

According to the invention, the angle of rotation of the belt is equal to the angle through which the directional axes of rotation of the two rollers are rotated against each other. In addition, the direction of rotation in which the belt is rotated is equal to the direction of rotation about which the axis of rotation of the first roller would have to be rotated in order to align it parallel to the axis of rotation of the second roller.

The twist angle is according to the invention between 70 - 200 °, and preferably between 70 and 110 °, and between 160 and 200 °.

It is true that during the rotation of the belt, a certain load on the respectively twisted region of the belt arises. However, this stress is, at least with a suitable design of the belt, insignificant.

By contrast, the flexural bending stress that would act on the belt if it were not twisted and therefore bent alternately in different directions about transverse axes would be avoided, which would be the case if it were to rotate non-co-rotatingly without being rotated , By eliminating this Bending cycling increases the life of the belt.

It is also advantageous that the structured belt surface when circulating around the rollers is essentially subjected to pressure and not to tension, as is the outer belt main surface. Although the belt is under bending stress in the area of the outer belt main surface when it revolves around the rollers, it is always bent in such a way that the outer belt main surface faces away from the roller and therefore undergoes essentially only tensile stress. By contrast, the belt area adjoining the structured belt area only experiences a compressive stress.

Another advantage of the new arrangement is that the unstructured belt main surface is virtually unrestrained because this unstructured belt main surface does not come into contact with circumferential surfaces of the rollers. The usual coating of the unstructured belt main surface can therefore be omitted without affecting the life of the belt.

It is also possible to use the unstructured belt main surface for other purposes, for example, this belt main surface may be provided with a stress varying coating, the respective aspect of which allows conclusions to be drawn about the deformation, temperature or speed of the belt.

In order to perform a supporting function or to be able to act as a carrying roller, a roller must be wrapped at least 45 ° from the belt.

In order to be able to perform a driving function, the traction sheave should be able to transmit the greatest possible driving force (traction force) to the belt. To this end, it is important that belts and rollers have a contact surface which enhances traction capability, for example by V-shaped ribs and grooves or by serrated transverse ribs and transverse grooves.

In addition, it is important that the belt be guided in the correct lateral position about the rollers, which can be achieved by suitable interlocking complementary structures in the rollers and in the belt.

The belt ribs and belt grooves preferably extend parallel to the longitudinal axis of the belt and, correspondingly, the complementary roller ribs and grooves extend along the roll periphery. This substantially improves the guiding properties between the rollers and the belt. In addition, transverse belt grooves can lead to a reduction of the bending stress in the belt.

The belt ribs and belt grooves may also be transverse to the longitudinal axis of the support and / or drive element and, accordingly, the roller ribs and roller grooves run at least approximately in the direction of the axes of rotation of the rollers. This essentially improves the blowing properties between the rollers and the belt.

During the rotation of the belt according to the invention, the deformation increases from the belt middle region to the belt edge regions. Preferably, therefore, a belt is used which has a lower elastic deformability in the belt middle region than in the belt edge regions. In this way it is prevented that the belt edge areas are subject to an inadmissibly strong deformation during the rotation of the belt.

It has proven to be advantageous to provide the belt with reinforcing inserts extending predominantly in the direction of its longitudinal axis. Such reinforcing inserts can be arranged, for example, in a greater training or in a denser arrangement in the region of the longitudinal axis, whereby the belt in the belt edge region easier is deformable than in the belt center area.

Since the edge regions of the belt are exposed due to the rotation of a relative to the central regions increased longitudinal strain, reinforcing inserts can be provided in the belt edge regions, the stress / strain ratio (modulus of elasticity) is correspondingly lower. In the case of reinforcing inserts in the form of steel strands, this can be achieved, for example, by different production methods of the strands (eg by twisting of different degrees).

Further details and advantages of the invention will be described below by way of examples and with reference to the drawings. Show it:

Figure 1 shows an arrangement according to the invention with two rollers and a directly between them belt.

2A is a partial cross-section through a roller with a

structured peripheral surface;

Fig. 2B is a cross-section through a belt having a textured belt main surface, suitable for the roller shown in Fig. 2A;

3A shows a cross section through a further belt with a structured belt main surface.

FIG. 3B shows the belt shown in FIG. 3A, looking at the belt main surfaces; FIG.

4A is a side view of a portion of another belt with a textured belt main surface in an extended position;

FIG. 4B shows the belt shown in FIG. 4A, running in a curved position over a roller, in the same representation as FIG. 4A; FIG.

Fig. 5A shows another arrangement according to the invention, with two rollers whose axes of rotation intersect at an angle of about 90 °, and with a belt running directly between them, in a first embodiment;

Fig. 5B shows a further arrangement according to the invention, with two rollers whose axes of rotation intersect at an angle of approximately 90 °, and with a belt extending directly between them, in a second embodiment; and

Fig. 6 shows an elevator system according to the invention, in a simplified representation.

Fig. 1 shows an arrangement for an elevator system, with a first roller 10, a second roller 20 and a belt 30, which forms a supporting and / or driving element of the elevator system. The belt 30 coupled in terms of movement and in a suitable order various elements of the elevator system, not shown, in particular an elevator car, a counterweight and a roller assembly, of which only the rollers 10 and 20 are shown. The belt 30 runs at a certain direction of movement of the elevator car from the first roller 10 directly to the second roller 20, or, in other words, the rollers 10 and 20 are, viewed in the direction of movement of the belt 30, arranged directly in direct succession.

In a movement of the elevator car, or at a taking place with the movement of the elevator car movement of the belt 30, the rollers 10 and 20 rotate in opposite directions. If, for example, the belt 30 moves in the direction of the arrow 31, then the roller 10 rotate in the direction of the arrow 11 about a first axis of rotation 12 and the roller 20 in the direction of the arrow 21 about a second axis of rotation 22.

The rollers 10 and 20 are arranged so that the rotation axes 12 and 22 extend at least approximately parallel, and that the belt 30 does not have to move or hardly in the direction of the rotation axes 30, but always between two parallel, perpendicular to the axes of rotation 12 and 22nd extending levels remains. In the illustrated in Fig. 1 Arrangement are the front end surfaces 14 and 24 in a plane (offset roller assembly).

The roller 10 has a textured peripheral surface 13, wherein its structuring in Fig. 1 is given by way of simplification by a first pattern, which is visible, because for this purpose an abutting on the roller 12 edge portion of the belt 30 is omitted.

The roller 20 also has a structured peripheral surface 23, wherein the structuring in FIG. 1 is indicated by a second pattern in a simplified manner.

The belt 30 has a longitudinal geometric center axis 32 and a cross-section bounded by two belt main surfaces 33, 34 and by two belt side surfaces 35, 36 (edges). The belt main surface 33 has a structure that is complementary to the structure of the peripheral surface 13 of the roller 10 and also complementary to the structure of the peripheral surface 23 of the roller 20. The term 'complementary' should not be said that the structuring of the rollers 10, 20 on the one hand and the belt 30 on the other hand are geometrically exactly complementary with just running belt 30. The term 'complementary' is merely intended to indicate that the structures of the rollers 10, 20 and the belt 30 are designed so that the rollers 10, 20 and the belt 30 in the existing geometric relationships at the contact areas between the belt 30 and the roller 10 and 20 are complementary in a way that a satisfactory interaction comes about.

The belt 30 is rotated according to the embodiment shown in an area between the rollers 10 and 20 by a twist angle of at least approximately 180 ° about its longitudinal central axis 32. There are also other embodiments possible in which the belt is rotated by approximately 90 ° about its longitudinal central axis. This is achieved that both the roller 10 and the roller 20, the textured belt main surface 33 comes into abutment with the structured peripheral surface 13 and 23, respectively.

Fig. 2A shows the roller 10 having a structure which is complementary to the structure of the belt according to Fig. 2B. This structure is formed by roller grooves 17.2 and roller ribs 17.1 on the circumferential surface 13 of the roller 10.

FIG. 2B shows the (longitudinal rib) belt 30 in cross-section, which in particular has good guiding properties when used in accordance with the invention. The belt 30 according to FIG. 2A is wedge belt-like and has on its main surface 33 a structure which is formed by belt ribs 37.1 running in the belt longitudinal direction and belt grooves 37.2 lying between the belt ribs 37.1. The roller 10 is wider in the direction of its axis of rotation 12 than the belt 30 and has an edge portion 17.3, which is not structured. In an analogous manner, a toothed belt could be used instead of the V-belt belt 30.

FIG. 3A shows a cross-section of a (longitudinal rib) belt 30 which is here formed with triangular ribs 37.1. The belt 30 according to FIG. 3A essentially consists of a suitable flexible material (preferably EPDM or PU) and has longitudinal reinforcing elements 38 (for example made of steel wire strands).

FIG. 3B schematically shows a side view of this belt 30. In particular, it can be seen from FIG. 3B that the area in which the belt 30 is twisted has a length L. This area is also referred to below as area A. From the belt 30, only the longitudinal axis 32 in this region A retains substantially the length L. All belt parts laterally spaced from the longitudinal axis 32 are elastically stretched in the region A to a length which is greater than L, wherein the Belt edge areas 35, 36 are stretched the most.

By locating the reinforcing elements 38 from the longitudinal axis 32 to the belt edge regions 35 and 36, either in lesser or lesser numbers, the belt edge regions are given increased elastic extensibility. It is also possible to make the belt edge areas more elastic, that the cross section of the actual belt does not remain the same over the belt width B, but changes in accordance with the stress.

Since the edge portions of the belt 30 are subjected to elongation increased in comparison with the central portions due to the rotation, reinforcing inserts whose stress / strain ratio (Young's modulus) is smaller can be provided in the edge portions. In the case of reinforcing inserts in the form of steel wire strands, this can be achieved, for example, by different production methods of the strands (eg by different degrees of twisting).

It should be noted that the length L of the region A, in which the rotation of the belt 30 takes place, on the one hand depends on the distance L1 of the rollers 10, 20 (see FIG. 1), but that a certain minimum length L, or a minimum distance L1 between the rollers 10, 20, should not fall below. Particularly advantageous arrangements in which the distance L is at least 30 times greater than the width B of the belt. According to the invention, arrangements are therefore preferred in which the ratio L / B is> 30.

A belt 30 having a transverse toothed structure is shown in Figs. 4A and 4B. This belt 30 has on its main belt surface 33 belt ribs 39.1 and belt grooves 39.2, which extend at right angles to the longitudinal axis 32. Accordingly, an associated, not shown role on a peripheral surface in the manner of a gear. Such a belt / roller combination gives especially good blowing properties. Fig. 4A shows the belt 30 in an elongated or straight arrangement, Fig. 4B in a bent arrangement, when it wraps around a roll with a roll diameter r (a). As shown in Fig. 4A, when the belt 30 is stretched, the belt rib 39.1 has a width a1 measured at the level of the rib foot, and the belt groove 39.2 has a width b1 measured at the height of the rib head. As shown in Fig. 4B, when the belt 30 is bent, the belt rib 39.1 has a width a2 measured at the level of the rib base, and the belt groove 39.2 has a width b2 measured at the height of the fin head. As a result of the belt bending, the width b2 becomes smaller than the width b1. Likewise, a2 becomes smaller than a1 as a result of the compressive stresses generated by belt deflection in this belt zone.

FIGS. 5A and 5B show arrangements in which the vertical projection of the axis 22 of the roller 20 intersects with the vertical projection of the axis 12 of the roller 10 and enclose an angle of 90 °. In the arrangement shown in Fig. 5A, the axis of rotation 12 of the first roller 10 would have to be rotated about an axis R to be parallel to the axis 22 of the second roller 20. At this angle of 90 ° and in the same direction of rotation, the belt 30 is rotated in the area between the rollers 10 and 20. As a result, the textured belt main surface 33 is engaged with both the textured peripheral surface 13 of the roller 10 and the textured peripheral surface 23 of the roller 20.

In the arrangement shown in Fig. 5B, the roller 20 rotates opposite to the roller 20 shown in Fig. 5A. Accordingly, in the area between the rollers 10 and 20, the belt 30 is rotated in the reverse direction than the belt shown in Fig. 5A 30. Also in the arrangement shown in Fig. 5B, it is achieved that the structured belt main surface 33 is engaged both with the textured peripheral surface 13 of the roller 10 and with the structured one Peripheral surface 23 of the roller 20th

6 shows an elevator installation 100 according to the invention, comprising a drive unit 40, the first roller 10, which forms a traction sheave, the second roller 20, which forms a carrying roller / deflection roller, a further roller 50, the belt 30 and an elevator car 60 In a movement of the elevator car 60, in which the belt 30 moves in the direction of arrow 31, the roller 10 according to arrow 11, the roller 20 in the opposite direction to the roller 10 according to arrow 21 and the roller 50 in the same direction as indicated by arrow 51 as the Roller 20. The belt 30 is rotated between the first roller 10 and the second roller 20 by at least approximately 180 °, while it is not twisted between the second roller 20 and the third roller 50. As a result, the structured belt surface 33 is always in contact with the peripheral surfaces 13 or 23 or 53 of the rollers 10, 20 and 50.

In addition to the elements mentioned, the elevator installation 100 comprises an elevator shaft 80, vertical guide rails 72, a counterweight 70 and a roller 71. The belt 30 is connected at point 73 to one of the vertical guide rails 72 of the elevator installation 100 and runs around the counterweight support roller 71 around. The other end of the belt 30 is secured in the region 74 of the upper end of the second vertical guide rails 72.

The structure of the belt 30 and the structures of the rollers 10 and 20 are optimally complementary when either the diameters and also the structures of the rollers 10 and 20 are the same or when the diameters of the rollers are different and then their structures are correspondingly different , But it is obvious that only the geometry, but also the material properties of the belt 30, set a lower limit for the roll diameter, which must not be fallen below.

Suitable widths B and thicknesses H of the belt 30, suitable wrap angles g, suitable diameters r of the rollers 10, 20 or suitable radii of curvature for the belt and suitable distances L1 between the rollers 10, 20 were determined partly mathematically, but in part also by tests.

Suitable belts 30 preferably have a width / thickness ratio (B / H) which is less than or equal to 10, that is, for example, a width B of 5 cm and, correspondingly, a thickness H of 0.5 cm.

Suitable wrap angles g are between 60 ° and 180 °. Preferably, these are between 90 ° and 180 °.

Suitable roll diameters r are between 6 cm and 20 cm.

The distance L1 between the two immediately successive rollers 10 and 20 should be at least 100 cm. Preferably, the distance L1 is between 100 cm and 300 cm. Experiments have shown that in the interests of a perfect belt travel and sufficient life, the ratio between the distance L1 and the width B of a belt rotated by 180 ° about its longitudinal axis should not fall below a value of 30 and preferably should be in the range of 50. For smaller angles of rotation, these values are to be reduced proportionally.

Suitable material for a belt 30 having a textured belt main surface 33 suitable for use in an elevator system 100 are suitable rubbers and elastomers (plastics), in particular polyurethane (PU) and ethylene propylene copolymer (EPDM). Optionally, the belt 30 may be equipped with reinforcing inserts 38 oriented in the longitudinal direction of the belt and / or net-like reinforcing inserts. For example, twisted steel wire strands are suitable as reinforcement inserts 38 oriented in the longitudinal direction of the belt. To the belt in the edge region 35, 36 a higher For example, to give elasticity, the strands 38 in the edge region can be more strongly twisted than the strands in the middle region of the belt 30. This results in a lower stress / strain ratio for the strands in the edge region of the belt, so that in a loaded and in order its longitudinal axis twisted belts in the wires of the central and outer strands result in approximately equal tensile stresses.

Claims (10)

1. Lift system (100), comprising a lift cage (60), a roller arrangement with a plurality of rollers (10, 20), wherein the rollers (10, 20) have structured circumferential surfaces (13, 23) with depressions and/or elevations, and at least one support and/or drive element in the form of a belt (30) with a longitudinal axis (32), which belt extends directly from the first roller (10) to the second roller (20) and has a structured belt main surface (33) with depressions and elevations which are formed to be complementary to the depressions and elevations of the structured circumferential surfaces (13, 23) of the rollers (10, 20), characterised in that a first roller (10) is rotatable about a first axis (12) of rotation and a second roller (20) is rotatable about a second axis (22) of rotation and the support element (30) is twisted about the longitudinal axis (32) thereof in a region (A) disposed between the two rollers (10, 20) so that the structured belt main surface (33) comes into engagement with the structured circumferential surfaces (13, 23) of the two rollers (10, 20).
2. Lift system (100) according to claim 1, characterised in that the depressions and/or elevations in the structured belt main surface (33) and in the structured circumferential surfaces (13, 23) of the two rollers (10, 20) have the form of ribs and grooves, i.e. that the belt (30) is provided with belt grooves (37.2; 39.2) and belt ribs (37.1; 39.1) and that the rollers (10, 20) are provided with roller ribs (17.1) and roller grooves (17.2).
3. Lift system (100) according to claim 2, characterised in that the belt ribs (37.1) and belt grooves (37.2) as also the roller ribs (17.1) and roller grooves (17.2) extend parallel to the longitudinal axis (32) of the belt (30) in order to improve guidance characteristics between the rollers (10, 20) and the belt (30).
4. Lift system (100) according to claim 3, characterised in that the belt ribs (37.1) and belt grooves (37.2) as also the roller ribs (17.1) and roller grooves (17.2) have triangular cross-sections.
5. Lift system (100) according to claim 2, characterised in that the belt ribs (39.1) and belt grooves (39.2) extend transversely to the longitudinal axis (32) of the belt (30) substantially in order to improve the bending capability and/or traction capability between the rollers (10, 20) and the belt (30).
6. Lift system (100) according to claim 5, characterised in that the belt (30) has a lower elastic deformability in the region along its longitudinal axis (32) than in the vicinity of its edges (35, 36).
7. Lift system (100) according to one of the preceding claims, characterised in that the belt (30) contains reinforcing inserts (38) or steel wire strands oriented in belt longitudinal direction, wherein the reinforcing inserts (38) or steel wire strands in the edge regions of the belt have a smaller stress/strain ratio than those in the middle region.
8. Lift system (100) according to one of the preceding claims, characterised in that the belt (30) is twisted in the region (A) through an angle between 70° and 200°, preferably between 160° and 200° or preferably between 70° and 110°.
9. Lift system (100) according to one of the preceding claims, characterised in that in the case of a belt (30), which extends with a twist between two rollers (10, 20), with the width B the spacing L present between the first roller (10) and the second roller (20) should not fall below the following values L > 30 x B for a twist angle of approximately 180° and L > 15 x B for a twist angle of approximately 90°.
10. Lift system (100) according to one of the preceding claims, characterised in that the first roller (10) is a drive pulley and the second roller (20) is a deflecting or supporting pulley.

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