Patent Application
20080135343
The present invention relates to an elevator support means for an elevator system, to an elevator system with such an elevator support means and to a method for assembling such an elevator system.
In an elevator system, one or more elevator support means transmit forces from a drive to a car movable in an elevator shaft or along free-standing guide rails. A car can be coupled by way of the same or further support elevator support means to a compensating weight or counterweight which travels in opposite sense to the car.
Such an elevator system with an elevator support means is known from European patent EP 1 446 348 B1. In an example of embodiment the elevator support means has on a drive side five drive ribs of wedge-ribbed shape for engagement with a drive wheel and on a deflecting side opposite the drive side a guide rib similarly of wedge-ribbed shape for engagement with a deflecting wheel. Guide ribs and drive ribs engage in corresponding wedge-shaped grooves which are formed on deflecting and drive wheels.
A rib generally has two mutually opposite flanks which include a flank angle α as schematically indicated in
Due to the wedge effect the drive ribs of wedge-ribbed shape increase, for the same tension force in the elevator support means, the normal forces acting on the flanks of the drive ribs and thus the drive capability of the drive. In addition, they advantageously guide the elevator support means in transverse direction on the drive wheel.
The guide rib at the rear side guides the elevator support means in transverse direction on deflecting wheels over which the elevator support means is deflected so as to co-operate with, for example, the car or the counterweight.
It has proved advantageous to arrange the tensile carrier arrangement at not too wide a distance and at a spacing from the drive side or the flanks of the drive ribs which is as uniform as possible so as to provide a more homogenous distribution of force in the drive ribs. This results in drive ribs with smaller flank height and flank width as well as a flatter flank angle.
The elevator support means usually rests from above on a drive wheel of the elevator system so that it is redisposed by its own weight in the grooves in the drive wheel circumference. Conversely, it frequently loops around deflecting wheels laterally or from below so that its own weight does not redispose it or even urge it out of the grooves in the deflecting wheel circumference. If slackening of the elevator support means occurs due to, for example, inertias of the car or the counterweight or oscillations in the elevator support means this can have the consequence that a guide rib slides completely out of the associated groove in the deflecting wheel. Without the then absent transverse guidance on the deflecting wheel a diagonal tension, which is usually present in the elevator system due to assembly tolerances, twistings of the load run and the like, has the effect that the elevator support means then migrates in transverse direction from its desired position and the guide rib also no longer finds its way back into the groove in the deflecting wheel when the elevator support means tightens again.
The elevator support means usually loops around a drive wheel of the elevator system with a greater angle of wrap than deflecting wheels so as to prevent, at the drive wheel, slipping of the elevator support means in correspondence with the Euler-Eytelwein formula. Accordingly, a drive rib frequently engages over a greater angular range in a drive wheel than a guide rib in a deflecting wheel. In addition, in a deflecting wheel with a smaller angle of wrap the forces in radial direction, which constrain the rib in the groove at the wheel circumference, are less than in the drive wheel with greater angle of wrap. If, for example, the elevator support means loops around a drive wheel by 180°, but a deflecting wheel by only 90°, the resultant radial force on the elevator support means is then greater at the drive wheel by the factor √2 than at the deflecting wheel.
In addition, the stronger diagonal running, which is caused by, for example, assembly tolerances, of the elevator support means frequently occurs between adjacent deflecting wheels. Moreover, compensation for this by deformation of the elevator support means also cannot be sufficiently provided due to the frequently smaller spacings between adjacent deflecting wheels. The diagonal tension resulting therefrom seeks to displace the elevator support means on the deflecting wheels in transverse direction.
It is therefore the object of the present invention to improve the guidance of an elevator support means at its deflection side.
An elevator support means according to the present invention comprises a base body, a drive side, which is provided for friction-coupling engagement with the drive wheel of a elevator system and has at least one drive rib, and a deflecting side, which is disposed opposite the drive side and which is provided for contact with a deflecting wheel of the elevator system and has at least one guide rib. A tensile carrier arrangement is arranged in the base body for transmission of the tension forces.
When in the following reference is made to at least one drive rib or at least one guide rib in that case always several drive ribs or guide ribs can equally well be comprehended, wherein a feature defined for at least drive rib or guide rib then applies to at least one of these several drive or guide ribs, preferably for several drive and/or guide ribs, particularly preferably for all drive and/or guide ribs, of the support means.
According to a first embodiment of the present invention at least one, preferably each, guide rib now has a greater flank height than at least one, preferably each, drive rib. This ensures better guidance of the elevator support means in transverse direction.
The flank height determines the radial displacement which the elevator support means experiences relative to a drive or deflecting wheel before the rib exits entirely from an associated groove in the outer circumference of the drive or deflecting wheel and can no longer guide the elevator support means in transverse direction.
Through the extension of the flank height of the guide ribs relative to the drive ribs partial compensation can be provided for the effects identified above and at the same time a more homogenous forced distribution between the drive side and the tensile carrier arrangement can be realized.
The higher guide rib can, in the case of a microscopic or macroscopic slackening of the elevator support means, move radially further away from a deflecting wheel without the transverse guidance being completely lost. If the elevator support means tightens again, the guide rib, which always still enters partly into the groove of the deflecting wheel due to its greater flank angle, advantageously centers the elevator support means again on the deflecting roller. In addition, the flank area, which engages in the groove in the deflecting wheel circumference, of the guide rib increases and can thus ensure a sufficient transverse guidance even with smaller deflecting angles. A greater diagonal tension up to 4% can therefore preferably also be realized by an elevator support means according to the first embodiment of the present invention.
Through the drive rib, which is lower by comparison, the change in spacing and/or the maximum spacing of the tensile carriers from the drive side can at the same time be reduced so that a more homogenous distribution of force in the drive rib is achieved.
Preferably the ratio of the flank height of at least one, preferably each, guide rib to the flank height of at least one, preferably each, drive rib is at least 1.5, preferably at least 2.0 and particularly preferably at least 2.5. A ratio of at least 1.5 can, for example, be sufficient in order to provide compensation for the deterioration in guidance on a deflecting wheel due to a smaller angle of wrap. A ratio of at least 2.0 can, for example, be advantageous in order to provide compensation for the deterioration in the guidance on a deflecting wheel due to the intrinsic weight which does not return the elevator support means to its position on the deflecting wheel or even sets it away from this. A ratio of at least 2.5 can, for example, be advantageous in order to make possible a greater diagonal tension.
Additionally or alternatively to the greater flank height at least one, preferably each, guide rib can have a greater flank width than at least one, preferably each, drive rib. This, too, guarantees better guidance of the elevator support means in transverse direction.
The flank width determines the offset in the transverse direction by which a rib can run into a groove or run out of this and yet is automatically guided back into the groove, in other words the “capture range” within which a rib is still captured by a groove of a drive or deflecting wheel. Due to the fact that in accordance with the present invention the flank width of the guide rib is greater than the flank width of the drive rib, thus the guide rib is wider in transverse direction, a more homogenous distribution of force in the drive rib can be provided in the narrower drive rib due to the resulting smaller spacing of the tensile carriers from the drive side, whilst the elevator support means when deflected over a deflecting wheel at the same time has better guidance due to the wider guide rib.
This can similarly provide partial compensation for the above-explained effects of poorer guidance and/or stronger diagonal tension due to its intrinsic weight or a smaller angle of wrap at the deflecting side. In the event of microscopic or macroscopic slackening of the elevator support means the wider guide rib can displace more strongly in transverse direction on a deflecting wheel without completely losing transverse guidance. When the elevator support means tightens again the guide rib, which due to its greater flank width always still lies partly over the groove of the deflecting wheel, advantageously centers the elevator support means on the deflecting roller again. In addition, the flank area, which engages in the groove in the deflecting wheel circumference, of the guide rib increases and can thus ensure sufficient transverse guidance even in the case of smaller angles of wrap. Thus, a greater diagonal tension can equally be realized with an elevator support means in which the guide rib has a greater flank width than the drive rib.
The ratio of the flank width of at least one, preferably each, guide rib to the flank width of at least one, preferably each, drive rib is preferably at least 1.5, preferably at least 1.75 and particularly preferably at least 2.0. A ratio of at least 1.5, for example, can be sufficient in order to provide compensation for deterioration in the guidance on a deflecting wheel due to a smaller angle of wrap. A ratio of at least 1.75, for example, can be advantageous to provide compensation for deterioration in the guidance on a deflecting wheel due to the intrinsic weight which does not return the elevator support means to its position on the deflecting wheel or even sets it away from this. A ratio of at least 2.0, for example, can be advantageous to make possible a greater diagonal tension.
The above-explained advantages of a greater flank height or flank width of the guide rib by comparison with the drive rib are already self-evident. For preference, however, the two features are combined together so that the higher and wider guide rib can further displace not only in radial direction, but also in axial direction and nevertheless is guided, especially centered, by the guide rib on the deflecting wheel. A greater diagonal tension can thereby be realized at the deflecting wheel, whilst at the same time the more homogenous distribution of force arises due to the lower, narrower drive ribs.
According to a second embodiment of the present invention, additionally or alternatively to the ratio of the flank height and/or flank width of at least one guide rib to at least one drive rib it is provided that the ratio of the flank height of at least one, preferably each, guide rib to the width of the elevator support means is at least 0.4, preferably at least 0.45 and particularly preferably at least 0.5.
The wider the elevator support means is formed, the more inertial mass pushes away from the deflecting wheel when microscopic or macroscopic slackening occurs. Wider elevator support means also permit, due to the geometrical moment of inertia thereof, stronger transverse forces or a stronger diagonal tension, which equally requires better guidance on a deflecting wheel. It has now proved in tests that with the above-mentioned ratios between guide rib height and elevator support means width it is possible to achieve a very good guidance of the elevator support means on a deflecting wheel. In that case a ratio of at least 0.4, for example, can be sufficient to provide compensation for deterioration in the guidance on a deflecting wheel due to a smaller angle of wrap. A ratio of at least 0.45, for example, can be advantageous in order to provide compensation for deterioration in the guidance on a deflecting wheel due to the intrinsic weight which does not return the elevator support means to its position on the deflecting wheel or sets it away from this. A ratio of at least 0.5, for example, can be advantageous in order to make possible a greater diagonal tension.
The ratio of the flank height of at least one guide rib to the width of the elevator support means according to the second embodiment of the present invention can be realized independently of the ratio of the flank height or flank width of the guide rib by comparison with a drive rib in accordance with the first embodiment. For example, the above-explained advantages can result even with high and wide drive ribs in which flank height and/or flank width of drive and guide ribs are substantially the same. However, the two embodiments are preferably combined together so that not only the more homogenous distribution of force in the shorter and/or narrower drive ribs, but also the better guidance characteristics of the high and/or wide guide ribs are achieved, wherein the guide ribs are adapted to the width of the elevator support means.
According to a third embodiment of the present invention, additionally or alternatively to the ratio of the flank height and/or flank width of a guide rib to a drive rib according to the first embodiment and/or additionally or alternatively to the ratio of the flank height of a guide rib to the width of the elevator support means according to the second embodiment at least one, preferably each, drive rib and at least one, preferably each, guide rib is constructed as a wedge rib with a flank angle, wherein the flank angle of at least one, preferably each, drive rib is greater than the flank angle of at least one, preferably each, guide rib.
More acute guide ribs improve the transverse guidance of the elevator support means at the deflecting side thereof and can thus better provide compensation for, for example, the above-explained effects due to the intrinsic weight, a smaller angle of wrap and/or the greater diagonal tension. In particular, greater penetration depths are thus provided by comparison with rib base area without having to widen the elevator support means overall. On the other hand, more obtuse drive ribs lead to a more homogenous distribution of force in the elevator support means, since the spacing of the individual tensile carriers from the drive side is more uniform and also the maximum spacing reduces.
The ratio of the flank angle according to a third embodiment of the present invention can be realized independently of the features of the first or second embodiment. For example, the above-explained advantages can result even with shorter or narrower guide ribs in which the penetration depth is, nevertheless, increased relative to its base area by the more acute flank angle. The third embodiment is, however, preferably combined with the first and/or second embodiment so that the advantageous greater flank height of the guide rib results due to the more acute flank angle.
A flank angle between 60° and 120°, preferably between 80° and 100° and particularly preferably substantially equal to 90° has proved advantageous for a drive rib constructed as a wedge rib so as to on the one hand achieve a sufficient wedge effect and thus increase in the normal force and on the other hand prevent excessive area pressure, material loading and noise output connected therewith and a jamming of the elevator support means.
A flank angle between 60° and 100°, preferably between 70° and 90° and particularly preferably substantially equal to 80° has proved advantageous for a guide rib constructed as a wedge rib so as on the one hand to ensure a sufficient guidance in a groove of a deflecting wheel and on the other hand to avoid excessive area pressures and the loading of the elevator support means connected therewith as well as output of noise which occurs.
According to a fourth embodiment of the present invention it is provided, additionally or alternatively to the flank height and/or flank width of the guide rib according to the first and/or second embodiment and/or additionally or alternatively to the flank angle of the guide rib according to the third embodiment that a respective guide rib is associated with one, two or three guide ribs.
The transverse guidance on a deflecting wheel is particularly advantageous in order to prevent migration of the elevator support means due to diagonal tension, which can result, for example, due to diagonal running of the elevator support means between a drive wheel and a deflecting wheel. The diagonal tension possible between a drive wheel and a deflecting wheel is limited, inter alia, by the number of drive ribs guiding the elevator support means on the drive wheel. It has proved in tests that with one guide rib for at most three, preferably at most two, drive ribs and particularly preferably one drive rib a particularly reliable guidance of the elevator support means can be ensured. In addition, the lever arm between outer drive ribs and the associated guide rib advantageously reduces and thus the torque which acts on the elevator support means and which results from the components of the forces, which act on the inclined flanks, perpendicularly to the flank width.
Advantageously the fourth embodiment is combined with the first, second and/or third embodiment of the present invention. In particular, if in accordance with the first or second embodiment a guide rib is constructed which is high and/or wide by comparison with the drive rib or the elevator support means width and in accordance with the third embodiment a guide rib is constructed which is acute, advantageous guidance and lever conditions occur with a drive-to-guide rib ratio of at most 3:1.
A guide rib is preferably centered between two adjacent drive ribs. The resultant of the area load on a flank of the guide rib is then applied in statically stable manner between the two points of action of the resultant of the area loads on the flanks of the drive ribs. In addition, the elevator support means can in this manner be constructed to be particularly slender.
According to an embodiment of the present invention the ratio of the width of the elevator support means to the height of the elevator support means is at most 0.95, preferably at most 0.93 and particularly preferably at most 0.91.
Thus, in particular, relatively acute and/or high guide ribs can be provided, which due to their flank height ensure good transverse guidance of the elevator support means.
Advantageously, such a slender elevator support means also has a greater geometrical moment of inertia in transverse direction and thus is stiffer than flat belts with respect to bending about the transverse axis. Such an elevator support means therefore experiences a higher degree of biasing back into the straight, undeformed position when deflected around a drive or deflecting wheel. This biasing counteracts jamming of drive or guide ribs of the elevator support means in associated grooves on a drive or deflecting wheel and thus advantageously reduces the risk of jamming.
A further advantage resides in the additional volume of the elevator support means in the direction of its height. This additional volume advantageously damps vibrations and diminishes shocks, which makes the running of such a belt more consistent.
The transmission of the circumferential force between tensile carriers and drive wheel takes place with transient deformation of the elevator support means in shear. The thus-occurring alternating deformations lead, over the long term, to destruction of the elevator support means and thus limit the service life thereof. Here, too, the additional volume of the elevator support means in the direction of its height can advantageously on the one hand reduce the deformations in shear and on the other hand better dissipate the then-created heat over the greater volume and, in particular, over the greater surface area.
The drive side of the elevator support means according to the present invention preferably has at most three, preferably exactly two, drive ribs and the deflecting side exactly one guide rib. Such an elevator support means can be of slender construction and thus realize the advantages explained in the foregoing.
As explained above, it is advantageous to associate one or two flanks of a drive rib with each tensile carrier so as to achieve a more homogenous distribution of force. For this purpose it is thus advantageous to associate one or two tensile carriers with a drive rib. If the drive side has only two or three drive ribs, then a tensile carrier arrangement of two (two drive ribs each with an associated tensile carrier) up to a maximum of six (three drive ribs each with two associated tensile carriers) tensile carriers thus results. If now for fulfillment of different tensile force requirements several elevator support means are connected in parallel, then elevator support means with only two or three drive ribs therefore significantly increase the modularity, because the tensile force transmissible by the combination of parallel elevator support means can thus be graduated significantly more finely and be adapted to the respective requirements.
The flanks of at least one, preferably each, drive rib and/or at least one, preferably each, guide rib can be formed to be planar. This facilitates production and advantageously produces a self-centering of the rib in an associated groove due to the inclination. Equally, the flanks of, for example, at least one, preferably each, guide rib can also be formed to be concave so as to save material and at the same time achieve a large flank height and/or flank width. The flanks of, for example, at least one, preferably each, guide rib can just as well be formed to be convex so as to make available sacrificial material and thus increase the service life of the elevator support means.
According to an embodiment of the present invention the minimum width of one or more drive ribs is greater than the minimum width of the associated grooves of a drive wheel. It can thereby be ensured that the distal flank regions of the drive ribs always completely rest on corresponding counter-flanks of the associated grooves, which still further taper below the completely penetrated drive rib. These counter-flanks thus do not exert, in their groove base, any notch effect on the drive ribs.
A groove with a radius is preferably formed between two adjacent drive ribs, wherein the ratio of this radius to a radius formed at the tip of an associated rib of the drive wheel of the elevator system is less than one, preferably less than 0.75 and particularly preferably less than 0.5. It can thereby be ensured that the rib, which engages between the two adjacent drive ribs, of the drive wheel exerts no or only a small notch effect on the proximal flank regions of the drive ribs.
The base body, one or more drive ribs and/or one or more guide ribs can be of unitary or multi-part construction from an elastomer, particularly polyurethane (PU), polychloroprene (CR), natural rubber and/or ethelene-propylene-diene rubber (EPDM). These materials are particularly suitable for conversion of the friction forces acting on the drive side into tension forces in the tensile carriers and in addition advantageously damp vibrations of the elevator support means. The drive and/or deflecting side can have one or more casings, for example of textile fabric, for protection against abrasion and dynamic destruction.
A unitary construction gives a particularly compact and homogenous elevator support means. If, conversely, a group of one or more drive ribs is of multi-part construction with a group of one or more guide ribs, in that the elevator support means, for example, is of two-part construction from a part comprising the drive ribs and a part connected therewith and comprising the guide ribs, different material characteristics can be provided on the drive side and deflecting side. For example, the drive side can have a lesser hardness, particularly a lesser Shore hardness, and/or a greater coefficient of friction than the deflecting side so as to achieve better drive capability, whereas conversely the lower coefficient of friction of the deflecting side reduces the energy loss during deflection.
For this purpose, in particular, the drive side and/or the deflecting side can additionally or alternatively have a coating of which the coefficient of friction, hardness and/or abrasion resistance differs or differ from the base body. Alternatively to the coating, a vapor deposition or a flocking can also be provided.
Through the multi-part construction of drive and guide rib and/or the coating of drive and/or deflecting side a elevator support means according to the present invention can preferably have coefficients of friction of μ=0.2 to 0.6 on the drive side and/or μ less than or equal to 0.3 on the deflecting side.
As explained in the foregoing, it can be advantageous for the spacing of the tensile carrier arrangement from the drive side to be less than from the deflecting side. A more homogenous distribution of force in the drive rib and at the same time a better guidance of the elevator support means at the deflecting side can thereby be combined. In that case, for example, there can be defined as spacing the maximum spacing of a tensile carrier from a flank, the mean spacing thereof and/or the spacing of the tensile carrier from the point of force action of the resultant of the area load on the flank.
The diameter of the tensile carriers is preferably in the region of 1.5 to 4 millimeters. Such tensile carriers have a sufficient capability of bending around drive and deflecting wheels and on the other hand have a sufficient strength and can be readily embedded in the base body.
According to an embodiment of the present invention each tensile carrier of the tensile carrier arrangement comprises a double-ply core strand with a core wire and two wire layers wrapped about this, and single-ply outer strands, which are arranged around the core strand, with a core wire, and a wire layer wrapped around this. Such a tensile carrier construction, which can have, for example, one core strand with 1+6+12 steel wires and eight outer strands with 1+6 steel wires, has in tests proved advantageous with respect to strength, ease of production and capability of bending.
Advantageously, in that case the two wire layers of the core strand have the same angle of wrap, whilst the one wire layer of the outer strands is wrapped against the wrap direction of the core strand, and the outer strands are wrapped around the core strand opposite to the wrap direction of their own wire layer. The tensile carrier thus has the order SSZS or ZZSZ. This reduces stretching of the strands.
As mentioned in the foregoing, a modular construction of an elevator support means composite of several elevator support means according to the present invention is advantageous in order to provide different tensile force requirements. In that case the elevator support means are guided parallel to the drive wheel and deflecting wheel.
In this connection, two elevator support means can be spaced apart by a gap. This simplifies mounting and allows slight deformations of the individual elevator support means without these rubbing against one another or mutually working out of the grooves of the drive wheel or deflecting wheel. Advantageously for this purpose the gap is at least 3%, preferably at least 4% and particularly preferably at least 5% of the width of the elevator support means.
For mounting, the elevator support means can be produced from a pre-product, wherein the pre-product consists of two or more elevator support means with a one-piece base body. The pre-product is partly divided between drive ribs and guide ribs so that elevator support means substantially separated in that manner remain connected by way of at least one thin base body web before they are mounted in the elevator system. This facilitates handling thereof and positionally correct arrangement on drive wheel and deflecting wheel. Alternatively, it is possible for mounting to permanently or detachably connect two or more elevator support means with an assembly band before they are mounted in the elevator system.
A drive wheel and/or a deflecting wheel of a elevator system according to an embodiment of the present invention has or have for each drive or guide rib an associated groove in such a manner that when the elevator support means is laid in place the flanks of the drive or guide rib contact corresponding counter-flanks of the associated groove. In this connection the grooves are preferably formed in correspondence with the ribs of the elevator support means: if the guide rib or drive rib has a specific flank height, flank width and/or a specific flank angle, then advantageously the counter-flanks of the associated groove have substantially the same flank height and/or flank width and/or substantially the same flank angle. In particular it is preferred for the penetration depth by which at least one, preferably each, guide rib of a elevator support means according to the present invention penetrates into a groove in a deflecting wheel to be greater than the penetration depth by which the at least one, preferably each, drive rib penetrates into a groove in a drive wheel. In other words, preferably at least one, preferably each, groove in a deflecting wheel is so formed that the projection of the contact surface between a flank of a guide rib arranged in this groove and the corresponding counter-flank of this groove is greater in axial and/or radial direction than the corresponding projection of the contact surface between a flank of at least one, preferably each, drive rib and the corresponding counter-flank of a groove, which is associated with this drive rib, in the drive wheel.
The drive wheel or the drive wheels can have several drive zones which are looped around at least partly by the elevator support means. Advantageously, an elevator support means loops around a drive wheel with an angle of wrap of 180°, preferably less than 180°, preferably less than 150°, particularly preferably less than 120° and especially 90°.
Due to the small bending radii, which are possible, of the elevator support means it is possible to connect the drive with a separate drive pulley or, however, to integrate drive zones in a drive output shaft with a drive. Drive pulleys and drive shafts provided with drive zones are therefore uniformly referred to as drive wheel. Advantageously, the diameter of a drive wheel is less than or equal to 220 millimeters, preferably less than 180 millimeters, preferably less than 140 millimeters, preferably less than 100 millimeters, preferably less than 90 millimeters and preferably less than 80 millimeters. The tension forces are introduced into the belts by the drive wheel in friction-coupling and/or shape-coupling manner.
An elevator support means can be constructed as an endless belt, the ends of which are fastened to belt locks. The belt can, particularly in the case of difficult deflecting conditions, for example be led through openings or placed on belt wheels mounted so as to be non-aligned.
The above, as well as other advantages of the present invention, will become readily apparent to those skilled in the art from the following detailed description of a preferred embodiment when considered in the light of the accompanying drawings in which:
The U.S. provisional patent application Ser. No. 60/822,118 filed Aug. 11, 2006 and U.S. provisional patent application Ser. No. 60/871,869 filed Dec. 22, 2006 are hereby incorporated herein by reference.
The following detailed description and appended drawings describe and illustrate various exemplary embodiments of the invention. The description and drawings serve to enable one skilled in the art to make and use the invention, and are not intended to limit the scope of the invention in any manner. In respect of the methods disclosed, the steps presented are exemplary in nature, and thus, the order of the steps is not necessary or critical.
Each wedge-ribbed belt 1 is fastened at one of its ends below the drive wheel 20 at a first belt fixing point 14.1. From this it extends downwardly to the counterweight support roller 21.1, loops around this and extends out from this to the drive wheel 20, loops around this and runs downwardly along the car wall of the counterweight side, loops on either side of the elevator car around car support rollers 21.2 and 21.3—which are respectively mounted below the elevator car 10—each time through approximately 90° and runs upwardly along the car wall remote from the counterweight 13 to a second belt fixing point 14.2.
The plane of the drive wheel 20 can be arranged at right angles to the car wall at the counterweight side and its vertical projection can lie outside the vertical projection of the elevator car 10. It is therefore preferred that the drive wheel has a small diameter of less than or equal to 220 millimeters, preferably less than 180 millimeters, preferably less than 140 millimeters, preferably less than 100 millimeters, preferably less than 90 millimeters, and preferably less than 80 millimeters, so that the spacing between the car wall at the counterweight side and the wall of the elevator shaft 12 opposite thereto can be as small as possible. Moreover, a small diameter of the drive wheel 20 enables use of a gearless drive motor with a relatively low drive torque as drive unit. The belt fixing points 14.1, 14.2 are devices which are known to the expert and in which the wedge-ribbed belt 1 is clamped between a wedge and a housing.
A drive side (at the bottom in
A deflecting side (at the top in
The dimensional sizes of the elevator support means 1 are schematically shown in
The flank width t3 or t4 of a drive rib 3 or of the guide rib 4 corresponds with the projection of the rib on the base body 2 of the elevator support means 1, i.e. perpendicularly to the flank height (horizontal in
The flank angle α4 of the guide rib 4 is the internal angle between the two flanks of the guide rib 4 and in the example of embodiment is 80°. The correspondingly defined flank angle α3 of the drive ribs 3 is, in the example of embodiment, 90°.
As recognizable in
As similarly recognizable in
This is particularly advantageous, since, due to mounting tolerances with the deflecting wheels 21.2, 21.3 as well as the small spacing thereof from one another, a more pronounced diagonal tension can occur, which opposes the improved guidance at the deflecting side. In addition, greater tolerances can be accepted between the deflecting wheel 21.3 and the belt fixing point 14.2, since the wider and higher guide rib 4 allows a greater diagonal tension.
Partial compensation can be provided between the drive wheel 20 and the deflecting wheel 21.2 for such diagonal tension by deformation of the elevator support means, so that the shorter and narrower drive ribs 3 run into the drive wheel 20 with smaller diagonal tension.
A guide rib 4 which extends over substantially the entire width w of the elevator support means 1 and is thus approximately twice as wide as the two drive ribs 3 is associated with the two drive ribs 3. In order to further increase the depth of penetration the flank angle α4 of the guide rib 4 is formed, at 80°, to be more acute than the flank angle α3 of the drive ribs 3.
Overall, the guide rib 4 thus has a significantly larger flank area f4=√(t42+h42) than the drive ribs 3 at f3=√(t32+h32), which significantly improves the guidance at the deflecting side. On the other hand, the tensile carriers 5 are arranged near the drive side, wherein due to the flatter flank angle α3 the spacing from the drive side varies only a little. Since, in addition, two tensile carriers 5 are associated with each drive rib 3, friction forces can be transferred from the drive wheel 20 substantially by way of each flank drive of a drive rib 3 to an associated tensile carrier 5, which has the effect of a particularly homogenous distribution of force in the drive ribs.
As mentioned above, a group of one or more drive ribs can be of multi-part construction with a group of one or more guide ribs. As shown in
As schematically indicated in
On the other hand, the counter-flanks of adjacent grooves 20.1 of the drive wheel go over into one another by a radius R20 which is greater than a radius R3 by which mutually facing flanks of the adjacent drive ribs 3 go over into one another. The contact between the flanks of the drive ribs 3 and the counter-flanks of the grooves 20.1 thus takes place smoothly and without large notch effects.
The drive side can have at least in the regions of its wedge ribs 3, which come into friction couple with the flanks of the drive wheel 20, a covering 6 (
As indicated in
For mounting such an elevator support means combination the elevator support means 1 can be made, as shown in
Alternatively, for mounting such an elevator support means composite it is also possible, as shown in
In accordance with the provisions of the patent statutes, the present invention has been described in what is considered to represent its preferred embodiment. However, it should be noted that the invention can be practiced otherwise than as specifically illustrated and described without departing from its spirit or scope.
| Number | Date | Country | Kind |
|---|---|---|---|
| 06118824.9 | Aug 2006 | EP | regional |
| 06127168.0 | Dec 2006 | EP | regional |
This application claims the benefit of U.S. provisional patent application Ser. No. 60/822,118 filed Aug. 11, 2006 and U.S. provisional patent application Ser. No. 60/871,869 filed Dec. 22, 2006.
| Number | Date | Country | |
|---|---|---|---|
| 60822118 | Aug 2006 | US | |
| 60871869 | Dec 2006 | US |
