EP2203373B1 - Elevator having a suspension - Google Patents

Abstract

An elevator includes a car, a counterweight, a suspension working together with the car and the counterweight, and a wheel at least partially wound around by the suspension, wherein the suspension comprises a tie beam arrangement made of two tie beams and a shell encasing the tie beam arrangement, said shell comprising a longitudinal structure in an area of an outer surface partially winding around the wheel, and wherein the ratio of the width of the suspension to the height thereof is greater than one and less than or equal to three. The wheel comprises a groove for guiding the suspension on the sides, in which the suspension is at least partially received, and the groove floor thereof being formed flat. The shell is coated, at least in areas, on the outer surface thereof, wherein the coating optionally has a friction-reducing, friction-increasing, and/or wear-reducing effect.

Description

The present invention relates to an elevator.

An elevator usually comprises a traversable in a bay cabin, which can be coupled to reduce the applied lifting work via a support means with a counterweight to the cabin counterweight. The support means may at least partially wrap around one or more drive wheels on which a drive of the elevator applies a torque to hold the car or to proceed. Here, the counterweight can ensure the driving ability of such drive wheels. In order to reduce the torque to be applied by the drive, the suspension element can wrap around pulley block-like deflection wheels, which are fastened firmly to the car, the counterweight or inertially in the shaft. Driving and deflection wheels are referred to collectively as wheels.

In addition to steel cables are, for example from the WO 99/43885 and the JP 49-20881 A Also known as flat belts as suspension means for elevators, in which four, five or six tension members are arranged side by side in a jacket which surrounds them. These flat belts have a longitudinal structure in the form of a plurality of grooves formed between adjacent tension members, which run in the longitudinal direction of the suspension element. The WO 99/43885 also proposes in this context, a drive wheel with a groove in which the flat belt is received and whose groove base has a complementary to the longitudinal profile of the flat belt outer contour with projections which engage in the longitudinal grooves and thus additionally guide the flat belt in the axial direction.

Due to the at least four juxtaposed tensile carriers and a jacket enveloping them with essentially the same wall thickness, the known flat belts have a width / height ratio, ie a quotient of the axial flat belt which wraps around the wheel, which is significantly greater than 1. The WO 99/43885 gives values of 2, preferably 5, as preferred lower limits of the width / height ratio.

Out US-A-6508051 is also a suspension with a width / height ratio greater than 1 known. Here, two parallel tension members are arranged in a dumbbell-shaped jacket.

Such flat belts have the advantage over conventional steel cables to allow smaller deflection radii.

In particular, by skewing on the wheels looped by such flat belts, but also, for example, in a twisting of such flat belts around their longitudinal axis to wrap successive wheels in opposite directions with the same side, occur in such broad support means, which have a high area moment of inertia in the direction of their width , but high lateral forces on. These can lead to premature wear of the suspension element or the wheel. In addition, the mounting of such stiff in the width direction support means is difficult.

Is the groove bottom, as in the WO 99/43885 proposed, contoured, obstructs a desired in particular during a displacement or rotation of the belt internal stress compensation within the suspension means, which also leads to premature wear. In addition, due to the necessary alignment of the groove and Tragmittellängsstruktur each other, the assembly even more difficult.

Out US 6,371,448 B1 is a suspension with a width / height ratio greater than 1 and less than 3 known. The support means may be received in a groove with a flat groove bottom. The groove is formed in a lateral guide area complementary to the shape of the support means.

Object of the present invention is therefore to reduce the wear of the suspension element and to increase the ease of installation.

This object is solved by the features of the independent claims.

A suspension element according to the present invention comprises a tension member arrangement and a jacket which encloses the tension member arrangement and whose outer surface has a longitudinal structure at least in the region which is provided for wrapping around a wheel of the elevator.

The Zugträgeranordnung consists only of two tension members. This makes it possible to form the suspension element with a width / height ratio that is greater than 1 and at the same time less than or equal to 3. By the lower limit of 1 it is ensured that the suspension element is flat overall and compared to known cables with a circular cross-section, ie a width / height ratio equal to 1, smaller deflection radii and thus allows smaller wheels. At the same time, the upper limit of 3 ensures that the transverse forces occurring in the suspension element do not become too great, thus preventing excessive wear. A suspension, whose width / height ratio due to the two Zugträger is in the proposed range, at the same time has sufficient flexibility in the width direction, which increases the ease of installation.

The tension members may consist of carbon, aramid or other plastics with sufficiently high tensile strength. However, they are preferably made of metallic wires, especially steel wires, which are particularly favorable in terms of manufacturing or deformability, strength and service life. The wires can be stranded one or more times to ropes, wherein a rope can be stranded from several strands, which in turn are made of stranded wires. In the strands and / or the rope, a soul, in particular a textile or plastic core can be arranged. Preferably, however, the spaces between the wires or strands are partially or completely filled by material of the jacket enclosing the tension members.

In a preferred embodiment, the two tension members are counter-struck, i. the rope forming the one tension member is struck to the right and the rope forming the other tension member of the tension member assembly is struck on the left. As a result, Verdrillneigungen the two tension members cancel each other and thus counteract a twisting of the support means advantageous.

Preferably, the tension members or the steel cables forming them or the wires stranded thereon have a maximum dimension in the range between 1.25 mm (millimeters) and 4 mm, preferably in a range between 1.5 mm and 2.5 mm and in particular substantially equal to 1.5 mm. This has proven to be the optimum compromise between weight, strength and manufacturability. In particular, small deflecting radii can advantageously be realized with such tension carriers. When using such suspension elements in elevators with large weights steel cables are preferably used with a diameter of up to 8 mm.

The tensile carriers may for example have a substantially round cross-section. In this case, the above-mentioned maximum dimension corresponds to the diameter of the tension member. Such a suspension means can be made particularly simple, since in the arrangement of the tension member in the jacket does not have to be paid to the orientation with respect to the longitudinal axis. Likewise, the tension members can also have oval or rectangular cross sections, which are particularly suitable for the realization of the width / height ratio between 1 and 3.

An alternative embodiment provides that the two tension members touch each other at least at certain points. This allows the production of particularly space-saving support means.

The longitudinal structure of the outer surface of the suspension element preferably has at least one groove extending in the longitudinal direction of the suspension element. This advantageously increases the flexibility of the suspension element without significantly reducing its tensile strength. A groove is preferably provided in the region of the outer surface, with which the support means wraps around a wheel of the elevator.

Such a groove can be produced, for example, in that the outer surface of the suspension element substantially follows an outer contour of the two adjacent tensile members. As a result, both tensile carriers are advantageously enveloped substantially at each point with the same wall thickness, so that stresses are distributed homogeneously within the suspension element. At the same time results in a simple manner on the opposite broad sides of the support means depending on an advantageous groove explained above between the two tension members. Furthermore, such an outer surface or casing can be designed with little casing material, which has a cost-effective effect.

The groove or a channel can also be arranged close to the outer surface of the support means, on the one hand transverse contraction, especially at distant tensile carriers allows and yet the support means pressing is concentrated in the areas of the tension member and a central region of the suspension element is relieved of pressure. The middle region, which corresponds to the pressure-relieved area of the suspension element and the groove, is advantageously approximately 20% to 50% of the suspension element width.

The jacket can enclose the two tension members respectively trapezoidal. This results in advantageously inclined outer edges of the support means, which advantageously increase the contact force and thus the driving ability of a drive wheel with the same bias due to the wedge effect.

Preferably, the support means is formed symmetrically with respect to its in the width direction, ie an axial direction of a looped by the suspension element wheel transverse axis. This facilitates assembly, since the support means also rotated by 180 ° can be applied, and advantageously allows the opposing wrap of successive wheels with identical outer surface contours.

An elastomer, for example polyurethane (PU) or ethylene-propylene-diene rubber (EPDM), which is advantageous in terms of damping and friction properties and wear behavior, has proved to be a suitable jacket material.

The outer surface can be selectively influenced, to different areas of the support means can be provided with coatings or with different coatings. Thus, an area may be provided with a coating to achieve a good sliding property. This area may be, for example, an area facing away from the traction area or it may be a lateral area of the suspension element. An area, in particular the traction area of the suspension element is advantageously provided with a coating to achieve a good traction or power transmission. Also, an area may be provided with a color coating. This is advantageous because it allows the suspension element can be easily mounted or placed as a possible unintentional twisting can be easily detected and corrected. Of course, the sheath can also be constructed in multiple layers. When using differently colored layers, it is easy to detect a state of wear or abrasion.

Such a coating can for example be sprayed, glued, extruded or flocked and made of plastic and / or tissue.

An elevator comprises a cabin and a counterweight coupled thereto via a suspension element. The support means cooperates with the car and the counterweight to hold or lift them and can be attached to the cabin and / or the counterweight each directly, for example via a wedgelock, or one or more with the car or the Contour counterweight connected wheels.

It has a tension member arrangement and a jacket enclosing the tension member arrangement, which has a longitudinal structure in a region of an outer surface which wraps around a wheel of the elevator, wherein the wheel has a groove for the lateral guidance of the suspension element, in which the suspension element is at least partially accommodated , The support means wraps around the wheel at least partially, for example by substantially 180 °.

The groove bottom of the groove, on which the support means rests with its one broad side and which is wrapped by the support means, is essentially flat or flat. This simplifies the manufacture of such a wheel. The ease of assembly of the elevator is increased because now the longitudinal structure of the support means does not have to be aligned with a complementary structure of the groove bottom. In particular, however, the planar groove bottom allows slight internal deformations within the suspension element, so that a tension in the suspension element can be distributed more uniformly over its cross section. The groove ensures a lateral stop sufficient lateral guidance of the support means without hindering such micro-deformations. Advantageously, the groove on the two-sided edges of the support means follows approximately the shape of the support means, that is, the groove knows an inlet region on which over the region of the wrap is usually not in contact with the support means, the inlet region goes into a guide region over which is over the area of the wrap in contact with the suspension element. This means that the groove at its lateral, the broad side of the belt corresponding limitations of the structure of the support means can follow, but that the groove bottom is extending between these lateral boundaries is flat, that is, he knows no intermediate surveys on.

The wheel, which is wrapped by the support means and receives it in its groove with a flat groove bottom, may equally be a deflection or drive wheel. It is also possible to provide a plurality, preferably all of the wheels of the elevator, which are looped around by the suspension element, with grooves in which the suspension element is in each case at least partially received and which have a flat or flat groove bottom. In an advantageous embodiment, the wheel is designed such that a plurality of grooves with a flat groove bottom are arranged side by side. As a result, a plurality of similar support means can be side by side guided, deflected and / or driven.

One or more drive wheels can be coupled to a drive of the elevator, the torque applied to the wheel are frictionally introduced as longitudinal forces in the support means. Such a drive may comprise one or more asynchronous motors and / or permanent magnet motors. This design allows drives of small dimensions, so that the total space required for the elevator in a building can be reduced. For this purpose, the elevator may be designed in particular without a machine room.

With particular advantage, a suspension element is used in an elevator, as has been described above. The advantages explained in this regard, in particular with regard to lesser wear and higher ease of installation, arise accordingly.

The wheel, in particular the drive wheel is advantageously made of steel or cast material (GG, GGG). Preferably, the grooves of the drive wheel are incorporated directly into a shaft which is directly, preferably integrally connected to a motor. In a preferred embodiment, the groove bottom has an average roughness in the circumferential direction between 0.1 μm (micrometers) and 0.7 μm, in particular between 0.2 μm and 0.6 μm and particularly preferably between 0.3 μm and 0.5 μm. In the axial direction, the groove bottom preferably has an average roughness in a range between 0.3 μm and 1.3 μm, in particular between 0.4 μm and 1.2 μm, and particularly preferably between 0.5 μm and 1.1 μm. Through these roughnesses, a coefficient of friction can be set in the circumferential direction, which gives a sufficient driving ability, while the support means is frictionally guided in the axial direction and thus excessive wear on the groove flanks is prevented. To achieve a desired surface property, the wheel may also be coated. Alternatively, the wheel, in particular a deflection wheel without a driving function, be made of plastic, in which the required grooves are incorporated or formed directly.

• Fig. 1: einen Aufzug nach einer Ausführung der vorliegenden Erfindung in einem seitlichen Querschnitt;
• Fig. 2: ein Tragmittel mit Tragmittelaufnahme;
• Fig. 3: ein Tragmittel mit Tragmittelaufnahme;
• Fig. 4: ein anderes Tragmittel mit Tragmittelaufnahme;
• Fig. 5: ein alternatives Tragmittel mit Tragmittelaufnahme;
• Fig. 6: ein anderes Tragmittel mit Tragmittelaufnahme;
• Fig. 7: ein weiteres alternatives Tragmittel mit Tragmittelaufnahme;
• Fig. 8: eine Ausführungsform einer Rille mit Tragmittel; und
• Fig. 9: eine Anordnung von Tragmittel mit Treibrad nach einer Ausführung der vorliegenden Erfindung.

Further advantages and features of the present invention will become apparent from the dependent claims and the embodiments. This shows, partially schematized:

• Fig. 1 a lift according to an embodiment of the present invention in a lateral cross section;
• Fig. 2 : a suspension with Tragmittelaufnahme;
• Fig. 3 : a suspension with Tragmittelaufnahme;
• Fig. 4 : another suspension with support means receptacle;
• Fig. 5 : an alternative suspension with Tragmittelaufnahme;
• Fig. 6 : another suspension with support means receptacle;
• Fig. 7 : another alternative suspension with support means receptacle;
• Fig. 8 an embodiment of a groove with support means; and
• Fig. 9 an arrangement of traction means with traction wheel according to an embodiment of the present invention.

Corresponding components or features are designated in the figures by identical reference numerals.

In Fig. 1 schematically an elevator according to an embodiment of the present invention is shown. This comprises a longitudinally movable rails 5 in a slot 1 cabin 3 and a coupled thereto, counterweight traversing counterweight 8, which is guided on a rail 7. A support means 12 described in more detail below is attached with its one end inertially in a first suspension point 10 in the shaft 1. Starting there, it wraps around a deflecting wheel 4.3 connected to the counterweight 8 by 180 ° and subsequently also a driving wheel 4.1 likewise by 180 °. Starting there, it wraps around a twist by 180 ° about its longitudinal axis two in the bottom 6 of the car 3 integrated guide wheels 4.2 in the same direction by 90 ° and is attached at its other end in a second suspension point 11 in the shaft 1. Between the two reversing wheels 4.2 connected to the cab 3, two further deflecting wheels 4.4, which each wrap around the suspension element 12 by approximately 12 °, clamp the suspension element against the cabin floor 6 and thus improve its guidance in the deflecting wheels 4.2. The drive wheel 4.1 of the machine-room-less elevator is driven by an asynchronous motor 2 arranged in the shaft 1 in order to hold or lift the car 3 and the counterweight 8.

Fig. 2 shows the upper half of a drive wheel 4.1 of the elevator Fig. 1 and that this wrap-around support means 12 in cross section.

The support means 12 has two laterally, ie with respect to the drive wheel axially juxtaposed tensile carrier 14, each consisting of nine stranded strands. The core strand is made of three layers of 19 stranded steel wires and surrounded by eight two-ply outer strands, each consisting of seven steel wires are stranded. The two tension members 14 have opposite directions of impact. For this purpose, the outer strands of a train carrier right-handed, the other of the other left-beaten to the respective core strand. This counteracts a rotation of the support means 12.

The tension members 14 have a diameter of about 2.5 mm. In this way, while maintaining an advantageous diameter ratio of, for example, D / d ≥ 40, where D denotes the diameter of the drive wheel and d the diameter of a steel cable, advantageously significantly smaller deflection radii and thus smaller driving and deflection wheels can be realized, which the necessary space of the elevator advantageous reduced. Of course, smaller diameter ratios can be achieved using high tensile tension members.

The two tension members 14 are embedded in a jacket 13 made of EPDM. This has an outer surface 13.1, which is substantially the in Fig. 2 dashed lines indicated outer contour 14.1 of the two tension members 14 follows. Since these adjacently arranged tensile carriers each have a substantially circular outer contour 14. 1, the outer surface 13. 1 has the shape of a horizontal hourglass in cross-section, wherein the two broad sides (top, bottom in FIG Fig. 2, 3rd ) is formed in each case a groove 13.2 in the longitudinal direction of the support means 12.

As a result, the wall thickness of the jacket 13 surrounding the tension member 14 is advantageously substantially the same everywhere, which leads to an improved stress distribution in the suspension element 12. At the same time, the projections 13.2 facilitate a slight, internal movement of the tension members 14 in the shell 13 against each other, so that lateral forces in the tension member 12 can be reduced. However, it may also be desirable that the tension members 12 are firmly embedded in the shell 13. Accordingly, a sheath material or a production method is selected, which allows a good integration of the sheath material in the tension member.

The support means 12 has due to its structure a ratio of its width B in the axial direction of the drive wheel 4.1 to its height H in the radial direction of the drive wheel 4.1 of FIG. As a result, equally small deflection radii and nevertheless sufficient flexibility of the suspension element are ensured, in particular in its width direction. This increases in particular the ease of installation of the flexible suspension element 12, which can be easily placed on the wheels 4.1 to 4.4. In order to increase the ease of assembly even further, the support means is symmetrical with respect to its perpendicular to its longitudinal direction extending in the width or height direction transverse or vertical axis, so that it is placed rotated by 180 ° and successive wheels in opposite directions can wrap around identical outer surface contours.

The support means 12 is received in a groove 15 of the drive wheel 4.1 so that it is approximately completely within the groove 15 in the example, the two lateral flanks or inlet area 15.2 (left, right in Fig. 2 ) touches the groove 15 and rests on the groove bottom 15.1 of the groove. The looped around by the support means 12 groove bottom 15.1 is flat or flat. This facilitates the above-described internal movement of the support means 12, so that lateral forces in the support means 12 and thus wear of the support means 12 and the drive wheel 4.1 are reduced.

The guide wheels 4.2 to 4.4 also have such grooves with a flat groove bottom (not shown), in which the guide wheels 4.2 to 4.4 wrapped around each support means 12 is received in each case in the same manner as with reference to Fig. 2 has been described for the drive wheel 4.1.

Fig. 3 shows a support means 12 as it is Fig. 2 already known. The support means 12 is in turn taken up in this example in a groove 15 of the drive wheel 4.1. The groove 15 includes the groove bottom 15.1, a lateral guide portion 15.3 and a lateral inlet portion 15.2. The groove base is flat or flat. The groove 15 follows at the two-sided edges of the support means in approximately the shape of the support means 12. The inlet region 15.2 is not in contact with the support means over the region of the wrap. The inlet region 15.2 goes into the guide region 15.3 via which over the region of the wrap is in contact with the support means 12. This means that the groove follows at its lateral, the broad side of the support means 12 corresponding boundaries of the structure of the support means, the groove bottom 15.1 extending between these lateral boundaries is flat, he knows no intermediate surveys on. In the Fig. 2 and the one described below Fig. 4 eliminates the guide portion 15.3 practical, since the insertion portion 15.2 and the groove bottom 15.1 meet substantially directly to each other. If the groove 15 of a drive wheel is provided, for example, with friction-influencing surfaces, the introduction region 15. 2 is advantageously reibwertvermindernd, and the groove bottom 15.1 is designed to increase friction. The guide area 15.3 is designed as a transition. The part close to the introduction area 15.2 is friction-reducing, and the part lying close to the groove base 15.1 is designed to increase the coefficient of friction, thereby achieving reliable traction transmission from the groove to the suspension element and at the same time carrying out the lateral guidance as frictionless as possible.

Fig. 4 now shows a modification of the drive wheel 4.1 of in Fig. 1 shown elevator, which is looped by a support means 12 according to a further embodiment of the present invention. The following only refers to the differences from the execution Fig. 1 to 3 received.

The jacket 13 of the support means 12 according to the further embodiment of the present invention according to Fig. 4 is trapezoidal. In particular, the jacket regions respectively surrounding a tension member 14 have opposing broad sides (top, bottom in FIG Fig. 4 ) of the support means 12 has a trapezoidal cross-section. Thus, both the two formed between the tension members 14 grooves 13.2 and the adjoining areas of the outer surface 13.1 of the support means 12 on both broad sides each have a trapezoidal cross-section. The opposite narrow sides (left, right in Fig. 4 ) of the support means 12 are therefore also trapezoidal and have with respect to the radial direction of the drive wheel 4.1 an angle.

The mutually in the axial direction opposite flanks 15.2 formed in the drive wheel 4.1 groove 15 are inclined relative to the radial direction by the same angle, so that the recorded in the groove 15 with trapezoidal cross-section support means 12 with its the drive wheel 4.1 facing outer inclined surfaces on these flanks 15.2 rests. Due to the wedge effect caused thereby, the driving ability is advantageously increased at the same bias in the support means 12.

As indicated in the figures, the support means in the radial direction does not have to be completely accommodated in the groove 15, but can protrude radially outwardly beyond it. In a modification, not shown, however, the support means 12 is completely received in the groove 15 to protect it from damage.

Fig. 5 shows an alternative embodiment of a support means 12 based on the embodiment according to Fig. 3 , According to this embodiment, the two tension members 14 touch each other at least at certain points. An outer contour of the individual tension member 14 is naturally structured, since the tension member 14 is composed of individual wires. The two tension members 14 are now pushed together so far that they touch the outermost wires. In the jacket area between the two tension members is the groove 13.2 or a recess. The groove bottom 15.1 of the groove 15 of the drive wheel 4.1 is flat. Over a region R of the groove bottom, a pressure between groove bottom 15.1 and jacket 13 is correspondingly small. The support means shown has the width B and in the example shown, the proportion (R / B) squeeze-free region R is about 30%.

Fig. 6 now shows a combination of the embodiments according to Figure 4 and the Zugträgeranordnung according to Fig. 5 , The groove 13.2 allows the jacket material 13 to be slightly adjusted according to an effective groove width and shape. Minor deviations result from manufacturing tolerances of the parts involved such as drive wheel 4.1 and suspension 12. This is not only by the execution according to Fig. 6 , this is valid for all illustrated embodiments.

Fig. 7 shows a further embodiment of a support means 12 which is received in a groove 15 with a flat groove bottom 15.1. The groove 13.2 or a channel is arranged in this embodiment of the support means 12 close to the outer surface 13.1 of the support means 12. Thus, a transverse contraction is also made possible and nevertheless the suspension element pressure is concentrated in the areas of the tension members 14 and a center region R of the suspension element 12 remains relieved of pressure.

Fig. 8 shows an embodiment of the groove 15 with a flat groove bottom 15.1 for receiving the support means 12. The guide portion 15.3 is widened in the direction of the inlet region 15.2 such that between the guide portion 15.3 and the unloaded support means 12, an air gap 19 is. This is advantageously realized in that a guide region radius RR of the guide region 15.3 is greater than a suspension element radius RT of the unloaded suspension element 12. The support means 12 deforms under load. The resulting form under load results as a result of tensile stress, which arises for example by a hanging on the suspension means cabin load and a bending stress, which results from the folding of the support means to the drive wheel 4.1. The widening of the guide area 15.3 causes now, that the support means freely, without restrictive transverse boundaries, under stress can take a natural form.

Advantageously, the guide region radius RR or the widened guide region 15.3 is designed such that the support means 12 can ovalize at a deflection via the drive wheel 4.1 under a normally expected loading force such that it substantially matches the guide region radius RR or the widened guide region 15.3. The normal expected load force usually corresponds to a normal operating condition of the elevator system. This causes the support means 12 in the loaded state, when it runs under power to the drive wheel 4.1, ovalize or may result as in the Figure 8 shown by dashed line 12.1. As a result, the suspension element 12 is not obstructed in the transverse contraction, which reduces lateral wear, and despite this, centering of the suspension element in the groove 15 is provided by the shape of the guide region.

Fig. 9 schematically shows a drive as he in an elevator to Fig. 1 would be usable. A motor 2 drives a drive wheel 4.1, which is integrated directly into a shaft of the drive or the motor 2 in the example shown. The drive wheel 4.1 has a plurality of grooves 15, in which grooves 15 each have a support means 12 is placed. The groove bottom 15.1 is flat and it goes over by means of radius in the lateral introduction areas 15.2. The radius corresponds approximately to an outer shape of the suspension element in this area. The number of required grooves or support means depends on a load capacity of the suspension element and the weight of the car or counterweight.

The above explanations are made mainly with respect to a driving wheel 4.1. They apply mutatis mutandis to pulleys 4.2, 4.3, 4.4. Of course, the embodiments shown can be combined. Thus, of course, the support means 12 of the embodiments according to the Fig. 2 to 6 be provided with tightly below the outer surface 13.1 of the support means 12 lying grooves 13.2 or channel and the outer contours of the support means 12 are changeable by a person skilled in the art. In particular, it can also be oval, ribbed or corrugated, or symmetric and asymmetrical outer surfaces 13.1 or sheaths can be used. In addition, the ovalized groove shape according Fig. 8 can also be applied to other external contours.

Claims (11)

1. Elevator with at least one cab (3), a counterweight (8), a suspension (12) interacting with the cab and the counterweight, a wheel (4.1, 4.2, 4.3, 4.4) at least partially looped around by the suspension, and at least one drive (2) for driving the cab (3), the counterweight (8) and the suspension (12), the elevator being arranged with the cab (3), counterweight (8), suspension (12) and drive (2) in a common shaft (1), the ratio of a width (B) of the suspension to the height (H) thereof being greater than one (B/H > 1) and less than or equal to three (B/H ≤ 3) and the suspension also having a tie beam arrangement and a shell (13) which encases the tie beam arrangement and has a longitudinal structure with at least one groove (13.2) running in the longitudinal direction of the suspension in a region of an outer surface (13.1) that partially loops around the wheel (4.1, 4.2, 4.3, 4.4), and the wheel having a flute (15) in which the suspension is at least partially received, a flute base (15.1) of the flute, which is at least partially looped around by the suspension, being formed so as to be substantially planar, and the shell (13) being coated on its outer surface (13.1) at least in certain regions, the coating selectively having a friction-reducing, friction-increasing and/or wear-reducing effect, and the flute (15) being determined by the flute base (15.1), a lateral guide region (15.3) and a lateral inlet region (15.2), and the guide region (15.3) being widened in the direction of the inlet region (15.2) in such a way that an air gap (19) is left between the guide region (15.3) and the unloaded suspension (12), the suspension (12) being widened, in the event of a deflection via the wheel (4.1) under a loading force which is normally to be expected, in such a way that the suspension is substantially adapted to the widened guide region (15.3).
2. Elevator according to Claim 1, characterized in that the tie beam arrangement consists of two or more tie beams (14), the two or more tie beams (14) touching one another at least at certain points.
3. Elevator according to Claim 2, characterized in that the tie beams (14) comprise metallic wires, in particular comprise singly or multiply stranded steel cables, the two tie beams (14) advantageously being laid in opposite directions.
4. Elevator according to Claim 2 or 3, characterized in that the metallic wires, steel cables or tie beams have a maximum dimension, in particular a diameter which is in a range between 1.25 mm and 8 mm, preferably in a range between 1.5 mm and 2.5 mm, and is particularly preferably substantially 1.5 mm.
5. Elevator according to one of Claims 2 to 4, characterized in that the tie beams have a substantially round, oval or rectangular cross section.
6. Elevator according to one of the preceding claims, characterized in that the groove (13.2) and/or adjoining regions of the outer surface (13.1) of the suspension (12) are embodied in a trapezoidal manner.
7. Elevator according to one of the preceding claims, characterized in that it has a drive (2) for driving the suspension by rotating the wheel (14.1) which is at least partially looped around by the suspension, the drive comprising an asynchronous motor or a permanent magnet motor.
8. Elevator according to one of the preceding claims, characterized in that a guide region radius RR of the guide region (15.3) is larger than a suspension radius RT of the unloaded suspension (12), the suspension (12) being ovalized, in the event of a deflection via the drive wheel (4.1) under a loading force which is normally to be expected, in such a way that the suspension is substantially adapted to the guide region radius RR.
9. Elevator according to one of the preceding claims, characterized in that the flute (15) is partially coated.
10. Elevator according to one of the preceding claims, characterized in that the flute base (15.1) has in the circumferential direction an average roughness (Ra), in particular in accordance with DIN EN ISO 4287, in a range of between 0.1 µm and 0.7 µm, in particular between 0.2 µm and 0.6 µm, in particular between 0.3 µm and 0.5 µm.
11. Elevator according to one of the preceding claims, characterized in that the flute base (15.1) has in the axial direction an average roughness (Ra), in particular in accordance with DIN EN ISO 4287, in a range between 0.3 µm and 1.3 µm, in particular between 0.4 µm and 1.2, in particular between 0.5 µm and 1.1 µm.

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