EP1724226B1 - Elevator - Google Patents

Abstract

Lift comprising a drive unit that drives a lift car by means of a drive belt running over a pulley comprises a drive belt (12.1) that has parallel longitudinal ribs (20.1) of wedge-shaped or trapezoidal cross-section on the side facing the pulley and cables (22) distributed over the width of the belt so that there is the same number of cables for each rib, the outer cable of each rib being located within the perpendicular projection (P) of a flank of the rib.

Description

The subject of the invention is an elevator installation as defined in the patent claims.

Elevator systems of the type according to the invention usually have an elevator car and a counterweight, which are movable in an elevator shaft or along free-standing guide devices. To generate the movement, the elevator installation has at least one drive with at least one traction sheave each, which carries the elevator car and the counterweight via supporting and / or drive means and transmits the required driving forces thereto.

An elevator installation according to the preamble of claim 1 is eg in EP-A-1396458 disclosed.

In the following, the carrying and / or drive means will only be referred to as suspension means for the sake of simplicity.

Out WO 03/043926 is a machine room elevator system known in which are used as a support means for the elevator car V-ribbed belt. These comprise a flat belt-like belt body produced from an elastic material (rubber, elastomers), which has a plurality of ribs extending in the longitudinal direction of the belt on its running surface facing the traction sheave. These ribs cooperate with complementary shaped grooves in the periphery of driving or deflecting pulleys (hereinafter referred to as pulleys) in order to guide the V-ribbed belt on the pulleys and to increase the traction between the traction sheave and the suspension element. The ribs and grooves have triangular or trapezoidal, ie wedge-shaped cross-sections. In the belt body of the V-ribbed belts are oriented in the belt longitudinal direction, consisting of metallic or non-metallic strands Tensile beams embedded, which give the support means the required tensile strength and longitudinal stiffness.

From WO 03/043926 known V-ribbed belts have certain disadvantages, ie, they are not optimally adapted to the requirements of a suspension means for elevator cars. Such a suspension should have the smallest possible dimensions and the lowest possible weight own high load capacity and low longitudinal elasticity and can be performed on driving and deflecting discs with the smallest possible diameters.

The according to WO 03/043926 V-ribbed belts used as suspension means show relatively large cross sections of the belt bodies in relation to the cross sections of the tension members, ie the thickness of the belt bodies is large with respect to the diameters of the tension members, and the edge portions of the belt bodies facing the pulleys and rollers, in particular the tips of the wedge-shaped ribs are relatively far away from the tension members. When given by the required load capacity cross-section of the tension members, this means that the disclosed V-ribbed belt on the one hand have more than the amount of material required for the belt body and thus are too heavy and too expensive. On the other hand, the material of the relatively high in the bending direction belt body is unnecessarily strongly stressed by bending alternating voltages when the support means rotates a traction sheave or a pulley of small diameter, which can lead to cracking and premature failure of the suspension element. Strong bending alternating voltages are in particular the areas of the belt body remote from the tension members, ie the tips of the wedge-shaped ribs.

The present invention has for its object to provide an elevator installation of the type described above, in which the said disadvantages are not present, ie, that the elevator installation comprises a flat belt-like support means with ribs, which has minimal dimensions and minimum weight when used with minimum pulley diameters and for a given load capacity, wherein the tension members and the belt body are exposed to the lowest possible loads, so that for the suspension means an optimal life is guaranteed.

According to the invention, this object is achieved by the measures and features specified in patent claim 1.

The proposed solution consists essentially in that in a lift system, a flat belt-like support means is used, which comprises at least on one of the traction sheave facing tread a plurality of belt longitudinally parallel ribs, wherein per rib at least two oriented in the belt longitudinal direction of tensile carriers are present and the sum of the cross-sectional areas of all tensile carriers is 30% to 40% of the total cross-sectional area of the suspension element. To determine the total cross-sectional area of the tension members, the cross-section defined by their outer diameter must be taken into account.

By dividing the load on two tensile members (with the required cross-section) per rib, it is achieved that the traction means are subjected to lower alternating bending stresses when the support means travel over small diameter pulleys than if a single tensile member with a correspondingly larger diameter is used per rib would.

With the specified ratio between the sum of the cross-sectional areas of all tensile carriers and the cross-sectional area of the suspension element, a suspension element is defined which has optimally small dimensions and material quantities. The Optimal small dimensions also have correspondingly low alternating bending stresses in the material of the belt body result. For the production of the belt body therefore materials (rubber, elastomers) can be selected, which have a lower allowable bending stress, but bear higher surface pressures between tension members and belt body.

Advantageous embodiments and modifications of the invention will become apparent from the independent claims 2 to 7.

According to a preferred embodiment of the invention, tension members with a substantially round cross-section are used in the suspension element, the outside diameter of which is at least 30%, preferably 35% to 40%, of the rib spacing. The distance between ribs is to be understood as meaning the distance between adjacent ribs of a suspension element, which is usually the same between all the ribs of a particular suspension element. In a designed according to this rule support means ensures that distributed by the tension members on the belt body to a traction sheave or a pulley forces optimally distributed in the belt body and occurring between tension members and belt body surface pressures are optimally low. This minimizes the risk that a loaded tension member cuts through the belt body.

Advantageously, the ribs have a wedge-shaped cross section with a flank angle of 60 ° to 120 °, wherein the range of 80 ° to 100 ° is preferable. The flank angle is the angle existing between both side surfaces (flanks) of a wedge-shaped rib. With flank angles of 60 ° to 120 ° on the one hand ensures that when running the suspension means pulleys no jamming between the ribs and to them complementarily shaped grooves of the pulleys occurs. This reduces running noise as well as the excitation of vibrations of the V-ribbed belt. On the other hand, with such flank angles sufficient guidance of the support means on the pulleys can be achieved, which prevents lateral displacement of the support means relative to the pulleys.

An ideal distribution of the forces introduced by the belt body into the tension members is achieved, inter alia, by the distances between the centers of tension carriers assigned to a particular rib being at most 20% smaller than the distances between centers of adjacent tension members associated with adjacent ribs.

Optimal small dimensions and low weight of the suspension element can be achieved if the minimum distance of the outer contour of a tension member to a surface of a rib is at most 20% of the total thickness of the suspension element. The total thickness is understood to mean the entire thickness of the belt body with the grooves.

According to the invention, the tensile carriers assigned to a rib are arranged such that in each case an external tensile carrier lies substantially in the region of the vertical projection of one respective flank of the wedge-shaped rib.
As a vertical projection, a directed perpendicular to the plane of the flat side of the support means projection is designated, and by "largely" is to be understood that at least 90% of the cross-sectional area of the respective tension member are within said projection.

In a particularly advantageous embodiment, in each case an outer tension member is arranged completely in the region of the vertical projection (P) of in each case one flank of a wedge-shaped rib.

With the two above-defined arrangements of the tension members in the flank area it is ensured that during the rotation of a pulley, no tension member has to be supported by that point of the belt body having the deepest notch formed by the grooves lying between the ribs.

In order to obtain a suspension, which have the lowest possible elongation at a given tensile load, tensile steel wire ropes are used. Steel wire ropes are stretched less at the same load as, for example, tensile carriers with the same cross section of conventional synthetic fibers.

A support means with a particularly low allowable bending radius, which is suitable for use in combination with pulleys of small diameter, can be achieved in that the steel wire ropes have outer diameter of less than 2 mm and are stranded from several strands, the total of more than 50 individual wires contain.

Embodiments of the invention are explained with reference to the accompanying drawings.

Fig. 1

einen zu einer Aufzugskabinenfront parallelen Schnitt durch eine erfindungsgemässe Aufzugsanlage.

Fig. 2

eine isometrische Ansicht der Rippenseite eines Tragmittels gemäss Erfindung in Form eines Keilrippenriemens.

Fig. 3

einen Schnitt durch einen ersten, das Tragmittel der Aufzugsanlage bildenden Keilrippenriemen.

Fig. 4

einen Schnitt durch einen zweiten, das Tragmittel der Aufzugsanlage bildenden Keilrippenriemen.

Fig. 5

einen Querschnitt durch einen Stahldraht-Zugträger des Keilrippenriemens.

Show it:

Fig. 1

a parallel to an elevator car front section through an inventive elevator system.

Fig. 2

an isometric view of the rib side of a support means according to the invention in the form of a V-ribbed belt.

Fig. 3

a section through a first, the support means of the elevator system forming V-ribbed belt.

Fig. 4

a section through a second, the support means of the elevator system forming V-ribbed belt.

Fig. 5

a cross section through a steel wire tension member of the V-ribbed belt.

• eine im Aufzugsschacht 1 fixierte Antriebseinheit 2 mit einer Treibscheibe 4.1
• eine an Kabinenführungsschienen 5 geführte Aufzugskabine 3 mit unterhalb des Kabinenbodens 6 angebrachten Kabinentragrollen 4.2
• ein an Gegengewichtsführungsschienen 7 geführtes Gegengewicht 8 mit einer Gegengewichtstragrolle 4.3
• ein als Keilrippenriemen 12 ausgebildetes Tragmittel für die Aufzugskabine 3 und das Gegengewicht 8, welches Tragmittel die Antriebskraft von der Treibscheibe 4.1 der Antriebseinheit 2 auf die Aufzugskabine und das Gegengewicht überträgt.
  (Bei einer realen Aufzugsanlage sind mindestens zwei parallel angeordnete Keilrippenriemen vorhanden)

Fig. 1 shows a section through an installed in an elevator shaft 1 inventive elevator system.
Shown are essentially:

• a fixed in the elevator shaft 1 drive unit 2 with a traction sheave 4.1
• a guided to cabin guide rails 5 elevator car 3 with mounted below the cabin floor 6 cab support rollers 4.2
• a guided on counterweight guide rails 7 counterweight 8 with a counterweight roller 4.3
• a designed as a V-ribbed belt 12 support means for the elevator car 3 and the counterweight 8, which suspension means transmits the driving force from the traction sheave 4.1 of the drive unit 2 to the elevator car and the counterweight.
  (In a real elevator installation there are at least two parallel V-ribbed belts)

Serving as a support means V-ribbed belt 12 is attached at one of its ends below the traction sheave 4.1 at a first support means fixed point 10. From this, it extends down to the counterweight carrying roller 4.3, wraps around this and extends from this to the traction sheave 4.1, wraps around it and runs along the gegengewichtsseitigen cabin wall down, wraps on both sides of the elevator car depending mounted below the elevator car 3 cabin roll 4.2 by 90 ° and extends along the counterweight 8 facing away from the cabin wall up to a second support means fixed point eleventh

The plane of the traction sheave 4.1 is arranged at right angles to the counterweight-side cabin wall and its vertical projection is outside the vertical projection of the elevator car 3. It is therefore important that the traction sheave 4.1 has a small diameter, so that the distance between the left-hand cabin wall and the opposite wall of the Elevator shaft 1 can be as small as possible. In addition, a small pulley diameter allows the use of a gearless drive motor with relatively low drive torque as the drive unit. 2

The traction sheave 4.1 and the counterweight trailing roller 4.3 are provided at their periphery with grooves which are formed complementary to the ribs of the V-ribbed belt 12. Where the V-ribbed belt 12 wraps around one of the pulleys 4.1 and 4.3, its ribs lie in corresponding grooves of the pulley, thus ensuring perfect guidance of the V-ribbed belt on these pulleys. In addition, by a serving between the grooves of the pulley 4.1 and the ribs of the pulley V-ribbed belt 12 improves the traction ability.

In the support means unterschlingung below the elevator car 3 is no lateral guidance between the Kabinentragrollen 4.2 and the V-ribbed belt 12 given because the ribs of the V-ribbed belt are located on its side facing away from the Kabinentragrollen 4.2 page. In order to ensure the lateral guidance of the V-ribbed belt, however, two groove-mounted guide rollers 4.4 are mounted on the cabin floor 6, the grooves of which interact with the ribs of the V-ribbed belt 12 as a lateral guide.

Fig. 2 shows a portion of serving as a support means V-ribbed belt 12.1 of an elevator system according to the invention. The belt body 15.1, the wedge-shaped ribs 20.1 and the tension members 22 embedded in the belt body can be seen.

Fig. 3 shows a cross section through a V-ribbed belt 12.1 according to the present invention, which includes a belt body 15.1 and a plurality of traction carriers 22 embedded therein. The belt body 15.1 is made of an elastic material. For example, natural rubber or a variety of synthetic elastomers can be used. The flat side 17 of the belt body 15.1 may be provided with an additional cover layer or an incorporated fabric layer. The at least with the traction sheave 4.1 of the drive unit 2 cooperating traction side of the belt body 15.1 has a plurality of wedge-shaped ribs 20.1, which extend in the longitudinal direction of the V-ribbed belt 12.1. By means of phantom lines, a pulley 4 is indicated, in the periphery of which complementary grooves are incorporated into the ribs 20.1 of the V-ribbed belt 12.1.

Each of the wedge-shaped ribs 20.1 of the V-ribbed belt 12.1 is associated with two round tension members 22, which are dimensioned so that they can jointly transmit the belt loads occurring in the V-ribbed belt per rib. These belt loads are on the one hand the transmission of pure tensile forces in the belt longitudinal direction. On the other hand, when a belt pulley 4.1 - 4.4 is wrapped, forces are transmitted radially from the tension members to the belt pulley via the belt body. The cross sections of the tension members 22 are dimensioned so that these radial forces do not cut through the belt body 15.1. In the case of wrap around a pulley, additional bending stresses occur in the tension members due to the curvature of the V-ribbed belt resting on the pulley. In order to keep these additional bending stresses in the tension members 22 as low as possible, the forces to be transmitted per rib 20.1 are distributed over two tension members, although a single tension member arranged in the center of the rib would allow a slightly smaller total thickness of the V-ribbed belt.

Extensive testing has determined an arrangement of belt body 15.1 and tension members 22 which, for a given pulley diameter D of about 90 mm, a given tensile load and given allowable alternating bending stress of the tension members and belt body material, provides the lowest possible total cross section with the least weight of the V-ribbed belt , As an important criterion for a V-ribbed belt having the properties mentioned, it has been found that the proportion of the total cross-sectional area of all tensile carriers on the cross-sectional area of the V-ribbed belt should be at least 25%, preferably 30% to 40%.

The in Fig. 2 shown V-ribbed belt meets this criterion. For the determination of the total cross-sectional area of all tension members is the by the in Fig. 5 shown external diameter DA defined cross section of the wire ropes to be considered.

In the case of a V-ribbed belt 12.1 with two tension members per rib 20.1, the abovementioned properties are achieved particularly optimally if the outer diameter of a tension member is at least 30% of the rib spacing. The rib spacing is the regular pitch T of the ribs.

Fig. 4 shows a variant 12.2 of the V-ribbed belt, in which the wedge-shaped ribs 20.2 wider than in in Fig. 2 variant 12.1 are shown and each having three associated tension members. All others in connection with the variant according to Fig. 2 mentioned properties are also present in this variant. Such a V-ribbed belt has the advantage that the corresponding pulleys 4.1, 4.3, 4.4 are somewhat easier to produce.

In the 3 and 4 illustrated, serving as a support means V-ribbed belt have a preferred flank angle β of about 90 °. The flank angle is the angle between two flanks of a wedge-shaped rib of the belt body. As already explained in the description of advantages, experiments have shown that the flank angle has a decisive influence on the development of noise and the generation of vibrations, and that for a lift-carrying means provided V-ribbed belt β of 80 ° to 100 ° optimally and 60 ° are applicable up to 120 °.

In 3 and 4 It can also be seen that the distances A between centers of the tensile carriers 22 associated with a particular rib are slightly smaller than the distances B between centers of adjacent tensile carriers of adjacent ribs. This is due to the maintenance of a minimum required distance of the tension members 22 to the edges of the ribs 20.1, 20.2. By keeping the differences in these distances as small as possible, a homogeneous distribution of the forces introduced by the belt body in the tension members is ensured. It has proved to be advantageous if the distances A are not more than 20% smaller than the distances B.

The 3 and 4 It can also be seen that small dimensions and low weight of the V-ribbed belt are achieved by making the distances X between the outer contours of the tension members and the surfaces of the ribs as low as possible. Optimal properties have been found in the tests for V-ribbed belts in which these distances X are at most 20% of the total thickness s of the suspension element or at most 17% of the spacing T between the ribs 20.1, 20.2. The total thickness s is the entire thickness of the belt body 15.1, 15.2 with the ribs 20.1, 20.2 to understand.

Particularly small dimensions and good running properties have shown for V-ribbed belts 12.1, 12.2, when the ribs 20.1, 20.2 associated tensile carrier 22 are arranged so that in each case an outer tensile carrier largely or completely in the region of the vertical projection P of each flank of the wedge-shaped rib 20.1, 20.2 lies.

Fig. 5 shows an enlarged view of a cross section through a preferred embodiment of a tension member 22, which is ideal for a V-ribbed belt for use in an elevator system according to the invention. The tension member 22 is a steel wire rope, which are stranded from a total of 75 individual wires 23 with extremely small diameters.

To achieve a long service life of the suspension element in elevator systems with pulleys of small diameter, it is of considerable advantage if the steel wire ropes used as tension members 22 consist of at least 50 individual wires.

Claims (7)

1. Lift installation with a drive engine (2), which drives at least one support means (12.1) of flat belt form, which carries a lift cage (3), by way of a drive pulley (4.1), wherein the support means has, at least on a running surface facing the drive pulley (4.1), several ribs (20.1; 20.2), which extend parallelly in the longitudinal direction of the support means (12.1; 12.2), with wedge-shaped or trapezium-shaped cross-section, and several tensile carriers (22) oriented in the longitudinal direction of the support means, wherein exactly two or three tensile carriers (22) are associated with each of the ribs (20.1; 20.2) and the total cross-sectional area of the tensile carriers (22) amounts to 30% to 40% of the a cross-sectional area of the support means (12.1, 12.2), characterised in that the tensile carriers (22) are arranged to be so distributed over the width of the support means (12.1; 12.2) that at least 90% of the cross-sectional area of each tensile carrier lies in the region of a perpendicular projection (P) of a flank of the wedge-shaped ribs (20.1; 20.2).
2. Lift installation according to claim 1, characterised in that each tensile carrier (22) lies entirely within the perpendicular projection (P) of a flank of the wedge-shaped ribs (20.1; 20.2).
3. Lift installation according to any one of claims 1 or 2, characterised in that the spacings (A) between the centres of two tensile carriers (22) associated with one of the ribs (20.1; 20.2) is at most 20% smaller than the spacings (B) between the centres of mutually adjacent tensile carriers (22) which are associated with two adjacent ribs.
4. Lift installation according to any one of claims 1 to 3, characterised in that an outer diameter of a tensile carrier amounts to at least 30% of a rib spacing (T).
5. Lift installation according to any one of claims 1 to 4, characterised in that the ribs (20.1, 20.2) have a wedge-shaped cross-section with a flank angle (β) of 60° to 120°.
6. Lift installation according to any one of claims 1 to 5, characterised in that a minimum spacing (X) between an outer contour of a tensile carrier (22) and a surface of a rib (20.1, 20.2) amounts to at most 20% of the total thickness (s) of the support means (12.1, 12.2).
7. Lift installation according to any one of claims 1 to 6, characterised in that the tensile carriers (22) consist of steel wire cables, which are twisted from several stands which in total contain more than 50 individual wires (23).

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