EP1555234B1 - Elevator - Google Patents

Elevator Download PDF

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Publication number
EP1555234B1
EP1555234B1 EP04405008A EP04405008A EP1555234B1 EP 1555234 B1 EP1555234 B1 EP 1555234B1 EP 04405008 A EP04405008 A EP 04405008A EP 04405008 A EP04405008 A EP 04405008A EP 1555234 B1 EP1555234 B1 EP 1555234B1
Authority
EP
European Patent Office
Prior art keywords
support means
ribs
rib
tensile
installation according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP04405008A
Other languages
German (de)
French (fr)
Other versions
EP1555234A1 (en
Inventor
Ernst Dipl.-Ing. Ach
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Inventio AG
Original Assignee
Inventio AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to ES04405008T priority Critical patent/ES2264105T3/en
Application filed by Inventio AG filed Critical Inventio AG
Priority to EP04405008A priority patent/EP1555234B1/en
Priority to DK04405008T priority patent/DK1555234T3/en
Priority to PT04405008T priority patent/PT1555234E/en
Priority to DE502004000538T priority patent/DE502004000538D1/en
Priority to AT04405008T priority patent/ATE325771T1/en
Priority to ES06118333T priority patent/ES2341276T3/en
Priority to US10/585,563 priority patent/US7757817B2/en
Priority to NZ548565A priority patent/NZ548565A/en
Priority to PL06118333T priority patent/PL1724226T3/en
Priority to BRPI0418358-4A priority patent/BRPI0418358A/en
Priority to DK06118333.1T priority patent/DK1724226T3/en
Priority to DE502004010825T priority patent/DE502004010825D1/en
Priority to CN2004800399904A priority patent/CN1902119B/en
Priority to EP04804313A priority patent/EP1706346B1/en
Priority to AU2004312154A priority patent/AU2004312154B2/en
Priority to MXPA06007700A priority patent/MXPA06007700A/en
Priority to CA2552202A priority patent/CA2552202C/en
Priority to SI200431417T priority patent/SI1724226T1/en
Priority to AT06118333T priority patent/ATE458692T1/en
Priority to EP06118333A priority patent/EP1724226B1/en
Priority to PCT/EP2004/014723 priority patent/WO2005066060A1/en
Priority to JP2006548169A priority patent/JP4896738B2/en
Priority to PT06118333T priority patent/PT1724226E/en
Publication of EP1555234A1 publication Critical patent/EP1555234A1/en
Application granted granted Critical
Publication of EP1555234B1 publication Critical patent/EP1555234B1/en
Priority to ZA2006/06452A priority patent/ZA200606452B/en
Priority to NO20063575A priority patent/NO334078B1/en
Priority to US12/403,026 priority patent/US8550216B2/en
Priority to CY20101100460T priority patent/CY1110542T1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B7/00—Other common features of elevators
    • B66B7/06—Arrangements of ropes or cables
    • B66B7/062—Belts
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B1/00—Constructional features of ropes or cables
    • D07B1/22—Flat or flat-sided ropes; Sets of ropes consisting of a series of parallel ropes
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B2201/00—Ropes or cables
    • D07B2201/20—Rope or cable components
    • D07B2201/2083—Jackets or coverings
    • D07B2201/2087—Jackets or coverings being of the coated type
    • D—TEXTILES; PAPER
    • D07—ROPES; CABLES OTHER THAN ELECTRIC
    • D07B—ROPES OR CABLES IN GENERAL
    • D07B2501/00—Application field
    • D07B2501/20—Application field related to ropes or cables
    • D07B2501/2007—Elevators

Definitions

  • 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.
  • 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.
  • suspension means for the sake of simplicity.
  • WO 03/043926 discloses a machine room-less elevator system in which V-ribbed belts are used as the suspension means for the elevator car.
  • V-ribbed belts 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 ten
  • the V-ribbed belts known from WO 03/043926 have certain disadvantages, ie they are not optimally adapted to the requirements for 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 V-ribbed belts used as suspension elements according to WO 03/043926 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 areas 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 in each case one flank of the wedge-shaped rib.
  • 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.
  • 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.
  • 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.
  • 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 gegenimportants districten 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 support 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 improved wedge effect improves traction.
  • FIG. 2 shows a section of a V-ribbed belt 12.1 serving as a suspension element of an elevator installation 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 comprises a belt body 15. 1 and a plurality of tension members 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.
  • 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.
  • 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 .
  • 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 V-ribbed belt shown in Fig. 2 fulfills this criterion.
  • the cross-section of the wire ropes defined by the outer diameter DA shown in FIG. 5 must be taken into account.
  • 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.
  • V-ribbed belt shows a variant 12.2 of a V-ribbed belt, in which the wedge-shaped ribs 20.2 are wider than in the variant 12.1 shown in FIG. 2 and each have three associated tensile carriers. All other properties mentioned in connection with the variant according to FIG. 2 are likewise 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.
  • the V-ribbed belts shown in FIGS. 3 and 4 which serve as suspension elements, have a preferred flank angle ⁇ of approximately 90 °.
  • the flank angle is the angle between two flanks of a wedge-shaped rib of the belt body.
  • 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 ⁇ of 80 ° to 100 ° optimally and 60 ° are applicable up to 120 °.
  • the distances A between centers of the tensile carriers 22 assigned to a specific 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.
  • FIGS. 3 and 4 also show 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 small as possible. Optimum properties have been found for the V-ribbed belt tests, where these distances X are at most 20% of the total thickness s of the suspension element or at most 17% of the spacing T present 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.
  • 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. In order 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.

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

Gegenstand der Erfindung ist eine Aufzugsanlage, wie in den Patentansprüchen definiert.The subject of the invention is an elevator installation as defined in the patent claims.

Aufzugsanlagen der erfindungsgemässen Art weisen üblicherweise eine Aufzugskabine und ein Gegengewicht auf, die in einem Aufzugsschacht oder entlang freistehender Führungseinrichtungen bewegbar sind. Zum Erzeugen der Bewegung weist die Aufzugsanlage mindestens einen Antrieb mit mindestens je einer Treibscheibe auf, die über Trag- und/oder Antriebsmittel die Aufzugkabine und das Gegengewicht tragen und die erforderlichen Antriebskräfte auf diese übertragen.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.

Im Folgenden werden der Einfachheit halber die Trag- und/oder Antriebsmittel nur noch als Tragmittel bezeichnet.In the following, the carrying and / or drive means will only be referred to as suspension means for the sake of simplicity.

Aus WO 03/043926 ist ein maschinenraumloses Aufzugssystem bekannt, bei welchem als Tragmittel für die Aufzugskabine Keilrippenriemen verwendet werden. Diese umfassen einen aus einem elastischen Material (Gummi, Elastomere) hergestellten flachriemenartigen Riemenkörper, der auf seiner der Treibscheibe zugewandten Lauffläche mehrere in Riemenlängsrichtung verlaufende Rippen aufweist. Diese Rippen wirken mit zu ihnen komplementär geformten Rillen in der Peripherie von Treib- oder Umlenkscheiben (im Folgenden als Riemenscheiben bezeichnet) zusammen, um einerseits den Keilrippenriemen auf den Riemenscheiben zu führen und andererseits die Traktionsfähigkeit zwischen der Treibscheibe und dem Tragmittel zu erhöhen. Die Rippen und Rillen haben dreieck- oder trapezförmige, d. h. keilförmige Querschnitte. In die Riemenkörper der Keilrippenriemen sind in Riemenlängsrichtung orientierte, aus metallischen oder nichtmetallischen Litzen bestehende Zugträger eingebettet, die dem Tragmittel die erforderliche Zugfestigkeit und Längssteifigkeit verleihen.WO 03/043926 discloses a machine room-less elevator system in which V-ribbed belts are used as the suspension means for the elevator car. 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.

Die aus WO 03/043926 bekannten Keilrippenriemen weisen gewisse Nachteile auf, d. h., sie sind den Anforderungen an ein Tragmittel für Aufzugskabinen nicht optimal angepasst. Ein solches Tragmittel soll bei kleinstmöglichen Abmessungen und geringstmöglichem Eigengewicht eine hohe Tragfähigkeit und eine geringe Längselastizität aufweisen und dabei über Treib- und Umlenkscheiben mit möglichst geringen Durchmessern geführt werden können.
Die gemäss WO 03/043926 als Tragmittel verwendeten Keilrippenriemen zeigen im Verhältnis zu den Querschnitten der Zugträger relativ grosse Querschnitte der Riemenkörper, d. h. die Dicke der Riemenkörper ist gross in Bezug auf die Durchmesser der Zugträger, und die den Scheiben und Rollen zugewandten Randbereiche der Riemenkörper, insbesondere die Spitzen der keilförmigen Rippen sind verhältnismässig weit von den Zugträgern entfernt. Bei durch die erforderliche Tragkraft gegebenem Querschnitt der Zugträger bedeutet dies, dass die offenbarten Keilrippenriemen einerseits mehr als die unbedingt erforderliche Materialmenge für den Riemenkörper aufweisen und damit zu schwer und zu teuer sind. Andererseits wird das Material des in Biegerichtung relativ hohen Riemenkörpers unnötig stark durch Biege-Wechselspannungen beansprucht, wenn das Tragmittel eine Treibscheibe oder eine Umlenkrolle von geringem Durchmesser umläuft, was zu Rissbildungen und vorzeitigem Ausfall des Tragmittels führen kann. Starken Biege-Wechselspannungen sind insbesondere die weit von den Zugträgern entfernten Bereiche des Riemenkörpers, d. h. die Spitzen der keilförmigen Rippen ausgesetzt.The V-ribbed belts known from WO 03/043926 have certain disadvantages, ie they are not optimally adapted to the requirements for 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 V-ribbed belts used as suspension elements according to WO 03/043926 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 areas 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.

Eine Aufzugsaulage gemäβ dem Oberbegriff des Anspruchs ist aus US 2003/0 121 129 bekannt.An elevator installation according to the preamble of the claim is known from US 2003/0121 129.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Aufzugsanlage der vorstehend beschriebenen Art zu schaffen, bei der die genannten Nachteile nicht vorhanden sind, d. h., dass die Aufzugsanlage ein flachriemenartiges Tragmittel mit Rippen umfasst, welches beim Einsatz mit minimalen Riemenscheibendurchmessern und bei vorgegebener Tragfähigkeit minimale Abmessungen und minimales Gewicht aufweist, wobei die Zugträger und der Riemenkörper geringstmöglichen Belastungen ausgesetzt sind, so dass für das Tragmittel eine optimale Lebensdauer gewährleistet ist.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.

Erfindungsgemäss wird diese Aufgabe durch die im Patentanspruch 1 angegebenen Massnahmen und Merkmale gelöst.According to the invention, this object is achieved by the measures and features specified in patent claim 1.

Durch die Aufteilung der Belastung auf zwei Zugträger (mit dem erforderlichen Querschnitt) pro Rippe wird erreicht, dass die Zugmittel beim Lauf des Tragmittels über Riemenscheiben mit kleinen Durchmessern geringeren Wechsel-Biegespannungen ausgesetzt sind, als wenn pro Rippe ein einziger Zugträger mit entsprechend grösserem Durchmesser verwendet würde.
Mit dem angegebenen Verhältnis zwischen der Summe der Querschnittsflächen aller Zugträger und der Querschnittsfläche des Tragmittels wird ein Tragmittel definiert, das optimal geringe Abmessungen und Materialmengen aufweist. Die optimal geringen Abmessungen haben auch entsprechend geringe Wechsel-Biegespannungen im Material des Riemenkörpers zur Folge. Für die Herstellung des Riemenkörpers können daher Materialien (Gummi, Elastomere) gewählt werden, die eine geringere zulässige Biegebeanspruchung aufweisen, jedoch höhere Flächenpressungen zwischen Zugträgern und Riemenkörper ertragen.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.

Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung gehen aus den unabhängigen Ansprüchen 2 bis 8 hervor.Advantageous embodiments and further developments of the invention will become apparent from the independent claims 2 to 8.

Gemäss einer bevorzugten Ausgestaltung der Erfindung werden im Tragmittel Zugträger mit im Wesentlichen rundem Querschnitt verwendet, deren Aussendurchmesser mindestens 30%, vorzugsweise 35% bis 40% des Rippenabstands beträgt. Als Rippenabstand ist der Abstand zwischen benachbarten Rippen eines Tragmittels zu verstehen, der üblicherweise zwischen allen Rippen eines bestimmten Tragmittels derselbe ist. Bei einem nach dieser Regel ausgebildeten Tragmittel ist gewährleistet, dass die von den Zugträgern über den Riemenkörper auf eine Treibscheibe oder eine Umlenkrolle zu übertragenden Kräfte optimal im Riemenkörper verteilt und die zwischen Zugträgern und Riemenkörper auftretenden Flächenpressungen optimal gering sind. Damit wird das Risiko minimiert, dass ein belasteter Zugträger den Riemenkörper durchschneidet.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.

Vorteilhafterweise weisen die Rippen einen keilförmigen Querschnitt mit einem Flankenwinkel von 60° bis 120° auf, wobei der Bereich von 80° bis 100° zu bevorzugen ist.
Als Flankenwinkel ist der zwischen beiden Seitenflächen (Flanken) einer keilförmigen Rippe vorhandene Winkel bezeichnet. Mit Flankenwinkeln von 60° bis 120° ist einerseits gewährleistet, dass beim Lauf des Tragmittels über Riemenscheiben kein Klemmen zwischen den Rippen und den zu ihnen komplementär geformten Rillen der Riemenscheiben auftritt. Dadurch werden Laufgeräusche wie auch die Anregung von Vibrationen des Keilrippenriemens reduziert. Andererseits kann mit solchen Flankenwinkeln eine ausreichende Führung des Tragmittels auf den Riemenscheiben erzielt werden, welche eine Seitwärtsverschiebung des Tragmittels gegenüber den Riemenscheiben verhindert.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.

Eine ideale Verteilung der vom Riemenkörper in die Zugträger eingeleiteten Kräfte wird unter anderem dadurch erreicht, dass die Abstände zwischen den Zentren von einer bestimmten Rippe zugeordneten Zugträgern höchstens 20% kleiner sind, als die Abstände zwischen Zentren benachbarter Zugträger, die nebeneinander liegenden Rippen zugeordnet sind.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 geringe Abmessungen und geringes Gewicht des Tragmittels sind erreichbar, wenn der minimale Abstand der Aussenkontur eines Zugträgers zu einer Oberfläche einer Rippe höchstens 20% der Gesamtdicke des Tragmittels beträgt. Als Gesamtdicke ist die gesamte Dicke des Riemenkörpers mit den Rillen zu verstehen.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.

Nach einer bevorzugten Ausgestaltung der Erfindung sind die einer Rippe zugeordneten Zugträger so angeordnet, dass jeweils ein äusserer Zugträger weitgehend im Bereich der senkrechten Projektion von jeweils einer Flanke der keilförmigen Rippe liegt.
Als senkrechte Projektion ist eine senkrecht auf die Ebene der Flachseite des Tragmittels gerichtete Projektion bezeichnet, und unter "weitgehend" ist zu verstehen, dass mindestens 90% der Querschnittsfläche des jeweiligen Zugträgers innerhalb der genannten Projektion liegen.According to a preferred embodiment of 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 in each case one 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.

Bei einer besonders vorteilhaften Ausführungsform ist jeweils ein äusserer Zugträger vollständig im Bereich der senkrechten Projektion (P) von jeweils einer Flanke einer keilförmigen Rippe angeordnet.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.

Mit den beiden vorstehend definierten Anordnungen der Zugträger im Flankenbereich ist gewährleistet, dass beim Umlaufen einer Riemenscheibe kein Zugträger durch diejenige Stelle des Riemenkörpers abgestützt werden muss, welche die tiefste Einkerbung aufweist, die durch die zwischen den Rippen liegenden Rillen gebildet wird.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.

Um ein Tragmittel zu erhalten, das bei gegebener Zugbelastung eine möglichst geringe Längsdehnung aufweisen, werden Zugträger aus Stahldrahtseilen verwendet. Stahldrahtseile werden bei gleicher Belastung weniger gedehnt als beispielsweise Zugträger mit gleichem Querschnitt aus üblichen Kunstfasern.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.

Ein Tragmittel mit besonders geringen zulässigen Biegeradien, welches für die Anwendung in Kombination mit Riemenscheiben von geringem Durchmesser geeignet ist, kann dadurch erreicht werden, dass die Stahldrahtseile Aussendurchmesser von weniger als 2 mm aufweisen und aus mehreren Litzen verseilt sind, die insgesamt mehr als 50 Einzeldrähte enthalten.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.

Ausführungsbeispiele der Erfindung sind anhand der beigefügten Zeichnungen erläutert.Embodiments of the invention are explained with reference to the accompanying drawings.

Es zeigen:

Fig. 1
einen zu einer Aufzugskabinenfront parallelen Schnitt durch eine erfindungsgemässe Aufzugs- anlage.
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, der nicht Teil der Erfindung ist.
Fig. 5
einen Querschnitt durch einen Stahldraht-Zugträger des Keilrippenriemens.
Show it:
Fig. 1
a section parallel to an elevator car front through an elevator according to the invention; investment.
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, which is not part of the invention.
Fig. 5
a cross section through a steel wire tension member of the V-ribbed belt.

Fig. 1 zeigt einen Schnitt durch ein in einem Aufzugsschacht 1 installiertes erfindungsgemässes Aufzugssystem. Dargestellt sind im Wesentlichen:

  • 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.
1 shows a section through an elevator system according to the invention installed in an elevator shaft 1. 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.

(Bei einer realen Aufzugsanlage sind mindestens zwei parallel angeordnete Keilrippenriemen vorhanden)(In a real elevator installation there are at least two parallel V-ribbed belts)

Der als Tragmittel dienende Keilrippenriemen 12 ist an einem seiner Enden unterhalb der Treibscheibe 4.1 an einem ersten Tragmittelfixpunkt 10 befestigt. Von diesem aus erstreckt er sich abwärts bis zu der Gegengewichtstragrolle 4.3, umschlingt diese und erstreckt sich von dieser aus zur Treibscheibe 4.1, umschlingt diese und verläuft entlang der gegengewichtsseitigen Kabinenwand abwärts, umschlingt auf beiden Seiten der Aufzugskabine je eine unterhalb der Aufzugskabine 3 angebrachte Kabinentragrolle 4.2 um je 90° und verläuft entlang der dem Gegengewicht 8 abgewandten Kabinenwand aufwärts zu einem zweiten Tragmittelfixpunkt 11.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

Die Ebene der Treibscheibe 4.1 ist rechtwinklig zur gegengewichtsseitigen Kabinenwand angeordnet und ihre Vertikalprojektion liegt ausserhalb der Vertikalprojektion der Aufzugskabine 3. Es ist daher wichtig, dass die Treibscheibe 4.1 einen geringen Durchmesser aufweist, damit der Abstand zwischen der linksseitigen Kabinenwand und der dieser gegenüber liegenden Wand des Aufzugsschachts 1 möglichst klein sein kann. Ausserdem ermöglicht ein geringer Treibscheibendurchmesser die Verwendung eines getriebelosen Antriebsmotors mit relativ geringem Antriebsdrehmoment als Antriebseinheit 2.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

Die Treibscheibe 4.1 und die Gegengewichtstragrolle 4.3 sind an ihrer Peripherie mit Rillen versehen, die komplementär zu den Rippen des Keilrippenriemens 12 geformt sind. Wo der Keilrippenriemen 12 eine der Riemenscheiben 4.1 und 4.3 umschlingt, liegen seine Rippen in korrespondierenden Rillen der Riemenscheibe, wodurch eine perfekte Führung des Keilrippenriemens auf diesen Riemenscheiben gewährleistet ist. Ausserdem wird durch eine zwischen den Rillen der als Treibscheibe dienenden Riemenscheibe 4.1 und den Rippen des Keilrippenriemens 12 entstehende Keilwirkung die Traktionsfähigkeit verbessert.The traction sheave 4.1 and the counterweight support 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 improved wedge effect improves traction.

Bei der Tragmittel-Unterschlingung unterhalb der Aufzugskabine 3 ist keine seitliche Führung zwischen den Kabinentragrollen 4.2 und dem Keilrippenriemen 12 gegeben, da die Rippen des Keilrippenriemens sich auf seiner von den Kabinentragrollen 4.2 abgewandten Seite befinden. Um die Seitenführung des Keilrippenriemens dennoch zu gewährleisten, sind am Kabinenboden 6 zwei mit Rillen versehene Führungsrollen 4.4 angebracht, deren Rillen mit den Rippen des Keilrippenriemens 12 als Seitenführung zusammenwirken.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 zeigt einen Abschnitt eines als Tragmittel dienenden Keilrippenriemens 12.1 einer erfindungsgemässen Aufzugsanlage. Zu erkennen sind der Riemenkörper 15.1, die keilförmigen Rippen 20.1 sowie die im Riemenkörper eingebetteten Zugträger 22.FIG. 2 shows a section of a V-ribbed belt 12.1 serving as a suspension element of an elevator installation 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 zeigt einen Querschnitt durch einen Keilrippenriemen 12.1 gemäss vorliegender Erfindung, der einen Riemenkörper 15.1 und mehrere darin eingebettete Zugträger 22 umfasst. Der Riemenkörper 15.1 ist aus einem elastischen Material hergestellt. Verwendbar sind beispielsweise Naturgummi oder eine Vielzahl von synthetischen Elastomeren. Die Flachseite 17 des Riemenkörpers 15.1 kann mit einer zusätzlichen Deckschicht oder einer eingearbeiteten Gewebeschicht versehen sein. Die mindestens mit der Treibscheibe 4.1 der Antriebseinheit 2 zusammenwirkende Traktionsseite des Riemenkörpers 15.1 weist mehrere keilförmige Rippen 20.1 auf, die sich in Längsrichtung des Keilrippenriemens 12.1 erstrecken. Mittels Phantomlinien ist eine Riemenscheibe 4 angedeutet, in deren Peripherie zu den Rippen 20.1 des Keilrippenriemens 12.1 komplementäre Rillen eingearbeitet sind.FIG. 3 shows a cross section through a V-ribbed belt 12. 1 according to the present invention, which comprises a belt body 15. 1 and a plurality of tension members 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.

Jeder der keilförmigen Rippen 20.1 des Keilrippenriemens 12.1 sind zwei runde Zugträger 22 zugeordnet, die so dimensioniert sind, dass sie gemeinsam die im Keilrippenriemen pro Rippe auftretenden Riemenbelastungen übertragen können. Es handelt sich bei diesen Riemenbelastungen einerseits um die Übertragung reiner Zugkräfte in Riemenlängsrichtung. Andererseits werden bei der Umschlingung einer Riemenscheibe 4.1 - 4.4 von den Zugträgern Kräfte in radialer Richtung über den Riemenkörper auf die Riemenscheibe übertragen. Die Querschnitte der Zugträger 22 sind so dimensioniert, dass diese radialen Kräfte nicht den Riemenkörper 15.1 durchschneiden. Im Falle der Umschlingung einer Riemenscheibe treten in den Zugträgern zusätzliche Biegespannungen infolge der Krümmung des auf der Riemenscheibe aufliegenden Keilrippenriemens auf. Um diese zusätzlichen Biegespannungen in den Zugträgern 22 so gering wie möglich zu halten, werden die pro Rippe 20.1 zu übertragenden Kräfte auf zwei Zugträger verteilt, obwohl ein im Zentrum der Rippe angeordneter einziger Zugträger eine etwas geringere Gesamtdicke des Keilrippenriemens ermöglichen würde.
Durch umfangreiche Tests wurde eine Anordnung von Riemenkörper 15.1 und Zugträgern 22 ermittelt, die bei einem gegebenem Riemenscheibendurchmesser D von etwa 90 mm, einer gegebenen Zugbelastung und gegebener zulässiger Wechsel-Biegebeanspruchung der Zugträger und des Riemenkörper-Materials einen geringstmöglichen Gesamtquerschnitt bei geringstmöglichem Gewicht des Keilrippenriemens ergibt. Als wichtiges Kriterium für einen Keilrippenriemen mit den genannten Eigenschaften hat sich dabei ergeben, dass der Anteil der Gesamt-Querschnittsfläche aller Zugträger an der Querschnittsfläche des Keilrippenriemens mindestens 25%, vorzugsweise 30% bis 40% betragen soll.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%.

Der in Fig. 2 dargestellte Keilrippenriemen erfüllt dieses Kriterium. Für die Ermittlung der Gesamt-Querschnittsfläche aller Zugträger ist der durch den in Fig. 5 gezeigten Aussendurchmesser DA definierte Querschnitt der Drahtseile zu berücksichtigen.The V-ribbed belt shown in Fig. 2 fulfills this criterion. To determine the total cross-sectional area of all tension members, the cross-section of the wire ropes defined by the outer diameter DA shown in FIG. 5 must be taken into account.

Bei einem Keilrippenriemen 12.1 mit zwei Zugträgern pro Rippe 20.1 werden vorstehend genannte Eigenschaften besonders optimal erreicht, wenn der Aussendurchmesser eines Zugträgers mindestens 30% des Rippenabstands beträgt. Als Rippenabstand wird der regelmässige Teilungsabstand T der Rippen bezeichnet.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 zeigt eine Variante 12.2 eines Keilrippenriemens, bei der die keilförmigen Rippen 20.2 breiter als bei der in Fig. 2 dargestellten Variante 12.1 sind und jeweils drei zugeordnete Zugträger aufweisen. Alle andern im Zusammenhang mit der Variante gemäss Fig. 2 genannten Eigenschaften sind bei dieser Variante ebenfalls vorhanden. Ein solcher Keilrippenriemen hat den Vorteil, dass die korrespondierenden Riemenscheiben 4.1, 4.3, 4.4 etwas einfacher herzustellen sind.4 shows a variant 12.2 of a V-ribbed belt, in which the wedge-shaped ribs 20.2 are wider than in the variant 12.1 shown in FIG. 2 and each have three associated tensile carriers. All other properties mentioned in connection with the variant according to FIG. 2 are likewise 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.

Die in Fig. 3 und 4 dargestellten, als Tragmittel dienenden Keilrippenriemen weisen einen bevorzugten Flankenwinkel β von etwa 90° auf. Als Flankenwinkel wird der zwischen beiden Flanken einer keilförmigen Rippe des Riemenkörpers vorhandene Winkel bezeichnet. Wie bereits in der Vorteilsbeschreibung erläutert, haben Versuche ergeben, dass der Flankenwinkel einen entscheidenden Einfluss auf die Geräuschentwicklung und die Entstehung von Vibrationen hat, und dass für einen als Aufzugs-Tragmittel vorgesehenen Keilrippenriemen Flankenwinkel β von 80° bis 100° optimal und von 60° bis 120° anwendbar sind.The V-ribbed belts shown in FIGS. 3 and 4, which serve as suspension elements, have a preferred flank angle β of approximately 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 Fig. 3 und 4 ist auch erkennbar, dass die Abstände A zwischen Zentren der einer bestimmten Rippe zugeordneten Zugträger 22 geringfügig kleiner sind als die Abstände B zwischen Zentren von benachbarten Zugträgern nebeneinander liegender Rippen. Dies ist durch die Einhaltung eines minimal erforderlichen Abstands der Zugträger 22 zu den Rändern der Rippen 20.1, 20.2 bedingt. Indem die Unterschiede in diesen Abständen so geringfügig wie möglich gehalten sind, wird eine homogene Verteilung der vom Riemenkörper in die Zugträger eingeleiteten Kräfte gewährleistet. Als vorteilhaft hat sich erwiesen, wenn die Abstände A nicht mehr als 20% kleiner als die Abstände B sind.It can also be seen in FIGS. 3 and 4 that the distances A between centers of the tensile carriers 22 assigned to a specific 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.

Den Fig. 3 und 4 ist ausserdem zu entnehmen, dass geringe Abmessungen und geringes Gewicht des Keilrippenriemens dadurch erreicht werden, dass die Abstände X zwischen den Aussenkonturen der Zugträger und den Oberflächen der Rippen so gering wie möglich ausgeführt sind. Optimale Eigenschaften haben die Versuchen für Keilrippenriemen ergeben, bei denen diese Abstände X höchstens 20% der Gesamtdicke s des Tragmittels oder höchstens 17% des zwischen den Rippen 20.1, 20.2 vorhandenen Teilungsabstands T betragen. Als Gesamtdicke s ist die gesamte Dicke des Riemenkörpers 15.1, 15.2 mit den Rippen 20.1, 20.2 zu verstehen.FIGS. 3 and 4 also show 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 small as possible. Optimum properties have been found for the V-ribbed belt tests, where these distances X are at most 20% of the total thickness s of the suspension element or at most 17% of the spacing T present 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.

Besonders geringe Abmessungen und gute Laufeigenschaften haben sich für Keilrippenriemen 12.1, 12.2 ergeben, wenn die einer Rippe 20.1, 20.2 zugeordneten Zugträger 22 so angeordnet sind, dass jeweils ein äusserer Zugträger weitgehend oder vollständig im Bereich der senkrechten Projektion P von jeweils einer Flanke der keilförmigen Rippe 20.1, 20.2 liegt.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 zeigt in vergrösserter Darstellung einen Querschnitt durch eine bevorzugte Ausführungsform eines Zugträgers 22, der sich hervorragend für einen Keilrippenriemen zur Anwendung in einer erfindungsgemässen Aufzugsanlage eignet. Der Zugträger 22 ist ein Stahldrahtseil, das aus insgesamt 75 Einzeldrähten 23 mit extrem geringen Durchmessern verseilt sind.
Um eine lange Lebensdauer des Tragmittels in Aufzugsanlagen mit Riemenscheiben von geringem Durchmesser zu erreichen, ist es von wesentlichem Vorteil, wenn die als Zugträger 22 verwendeten Stahldrahtseile aus mindestens 50 Einzeldrähten bestehen.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.
In order 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 (8)

  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) of wedge-shaped cross-section which extend parallelly in the longitudinal direction of the support means and which has several tensile carriers (22) oriented in the longitudinal direction of the support means, characterised in that the tensile carriers (22) are so distributed in transverse direction of the support means (12.1) that exactly two tensile carriers (22) are associated with each of the ribs (20.1), wherein the two tensile carriers (22) are arranged symmetrically to the axis of symmetry of the respective rib (20.1).
  2. Lift installation according to claim 1, characterised in that all tensile carriers (22) are so arranged in transverse direction of the support means (12.1) that in each instance at least 90% of their cross-sectional area lies within the perpendicular projection (P) of a respective inclined flank of one of the ribs (20.1).
  3. Lift installation according to claim 1 or 2, characterised in that the spacings (A) between the centres of two tensile carriers (22) associated with a rib are smaller than the spacings (B) between the centres of adjacent tensile carriers (22) associated with two adjoining ribs.
  4. Lift installation according to one of claims 1 to 3, characterised in that the total cross-sectional area of all tensile carriers (22) amounts to 30% to 40% of the cross-sectional area of the support means (12.1, 12.2).
  5. Lift installation according to one of claims 1 or 4, characterised in that an outer diameter of a tensile carrier amounts to at least 30% of a rib spacing (T).
  6. Lift installation according to one of claims 1 to 5, characterised in that the ribs (20.1, 20.2) have a wedge-shaped cross-section with a flank angle (β) of 60° to 120°.
  7. Lift installation according to one of claims 1 to 6, 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).
  8. Lift installation according to one of claims 1 to 7, characterised in that the tensile carriers (22) consist of steel wire cables, which are twisted from several stands in total containing more than 50 individual wires (23).
EP04405008A 2004-01-06 2004-01-06 Elevator Expired - Lifetime EP1555234B1 (en)

Priority Applications (28)

Application Number Priority Date Filing Date Title
EP04405008A EP1555234B1 (en) 2004-01-06 2004-01-06 Elevator
DK04405008T DK1555234T3 (en) 2004-01-06 2004-01-06 Elevator
PT04405008T PT1555234E (en) 2004-01-06 2004-01-06 ELEVATOR SYSTEM
DE502004000538T DE502004000538D1 (en) 2004-01-06 2004-01-06 elevator system
AT04405008T ATE325771T1 (en) 2004-01-06 2004-01-06 ELEVATOR SYSTEM
ES04405008T ES2264105T3 (en) 2004-01-06 2004-01-06 ELEVATOR INSTALLATION.
AT06118333T ATE458692T1 (en) 2004-01-06 2004-12-27 ELEVATOR SYSTEM
NZ548565A NZ548565A (en) 2004-01-06 2004-12-27 Lift installation having elevator belt with wedge shaped ribs and embedded tensile carriers
PL06118333T PL1724226T3 (en) 2004-01-06 2004-12-27 Elevator
BRPI0418358-4A BRPI0418358A (en) 2004-01-06 2004-12-27 lift installation
DK06118333.1T DK1724226T3 (en) 2004-01-06 2004-12-27 Elevator Plant
DE502004010825T DE502004010825D1 (en) 2004-01-06 2004-12-27 elevator system
CN2004800399904A CN1902119B (en) 2004-01-06 2004-12-27 Elevator
EP04804313A EP1706346B1 (en) 2004-01-06 2004-12-27 Lift system
ES06118333T ES2341276T3 (en) 2004-01-06 2004-12-27 ELEVATOR INSTALLATION.
MXPA06007700A MXPA06007700A (en) 2004-01-06 2004-12-27 Lift system.
CA2552202A CA2552202C (en) 2004-01-06 2004-12-27 Lift system
SI200431417T SI1724226T1 (en) 2004-01-06 2004-12-27 Elevator
US10/585,563 US7757817B2 (en) 2004-01-06 2004-12-27 Elevator system having a flat belt with wedge-shaped ribs
EP06118333A EP1724226B1 (en) 2004-01-06 2004-12-27 Elevator
PCT/EP2004/014723 WO2005066060A1 (en) 2004-01-06 2004-12-27 Lift system
JP2006548169A JP4896738B2 (en) 2004-01-06 2004-12-27 Elevator equipment
PT06118333T PT1724226E (en) 2004-01-06 2004-12-27 Elevator
AU2004312154A AU2004312154B2 (en) 2004-01-06 2004-12-27 Lift system
ZA2006/06452A ZA200606452B (en) 2004-01-06 2006-08-03 Lift system
NO20063575A NO334078B1 (en) 2004-01-06 2006-08-07 Elevator Construction
US12/403,026 US8550216B2 (en) 2004-01-06 2009-03-12 Elevator system having a flat belt with wedge-shaped ribs
CY20101100460T CY1110542T1 (en) 2004-01-06 2010-05-21 ELEVATOR INSTALLATION

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04405008A EP1555234B1 (en) 2004-01-06 2004-01-06 Elevator

Publications (2)

Publication Number Publication Date
EP1555234A1 EP1555234A1 (en) 2005-07-20
EP1555234B1 true EP1555234B1 (en) 2006-05-10

Family

ID=34610248

Family Applications (3)

Application Number Title Priority Date Filing Date
EP04405008A Expired - Lifetime EP1555234B1 (en) 2004-01-06 2004-01-06 Elevator
EP04804313A Active EP1706346B1 (en) 2004-01-06 2004-12-27 Lift system
EP06118333A Active EP1724226B1 (en) 2004-01-06 2004-12-27 Elevator

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP04804313A Active EP1706346B1 (en) 2004-01-06 2004-12-27 Lift system
EP06118333A Active EP1724226B1 (en) 2004-01-06 2004-12-27 Elevator

Country Status (20)

Country Link
US (2) US7757817B2 (en)
EP (3) EP1555234B1 (en)
JP (1) JP4896738B2 (en)
CN (1) CN1902119B (en)
AT (2) ATE325771T1 (en)
AU (1) AU2004312154B2 (en)
BR (1) BRPI0418358A (en)
CA (1) CA2552202C (en)
CY (1) CY1110542T1 (en)
DE (2) DE502004000538D1 (en)
DK (2) DK1555234T3 (en)
ES (2) ES2264105T3 (en)
MX (1) MXPA06007700A (en)
NO (1) NO334078B1 (en)
NZ (1) NZ548565A (en)
PL (1) PL1724226T3 (en)
PT (2) PT1555234E (en)
SI (1) SI1724226T1 (en)
WO (1) WO2005066060A1 (en)
ZA (1) ZA200606452B (en)

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DE102008037537B4 (en) * 2008-11-10 2020-11-05 Contitech Antriebssysteme Gmbh Traction drive and elevator system with this traction drive
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Also Published As

Publication number Publication date
CN1902119A (en) 2007-01-24
DK1724226T3 (en) 2010-06-14
US20070084671A1 (en) 2007-04-19
NZ548565A (en) 2009-09-25
CN1902119B (en) 2010-05-26
PL1724226T3 (en) 2010-07-30
JP2007517747A (en) 2007-07-05
US20090166132A1 (en) 2009-07-02
EP1555234A1 (en) 2005-07-20
DK1555234T3 (en) 2006-08-21
MXPA06007700A (en) 2006-09-01
PT1724226E (en) 2010-05-21
JP4896738B2 (en) 2012-03-14
NO20063575L (en) 2006-10-06
ZA200606452B (en) 2008-01-08
US7757817B2 (en) 2010-07-20
US8550216B2 (en) 2013-10-08
WO2005066060A1 (en) 2005-07-21
EP1706346B1 (en) 2012-10-10
SI1724226T1 (en) 2010-07-30
AU2004312154B2 (en) 2010-03-04
BRPI0418358A (en) 2007-05-08
ATE325771T1 (en) 2006-06-15
CY1110542T1 (en) 2015-04-29
EP1706346A1 (en) 2006-10-04
EP1724226B1 (en) 2010-02-24
ES2264105T3 (en) 2006-12-16
ES2341276T3 (en) 2010-06-17
DE502004000538D1 (en) 2006-06-14
PT1555234E (en) 2006-08-31
ATE458692T1 (en) 2010-03-15
EP1724226A1 (en) 2006-11-22
AU2004312154A1 (en) 2005-07-21
DE502004010825D1 (en) 2010-04-08
NO334078B1 (en) 2013-12-02
CA2552202C (en) 2012-03-20
CA2552202A1 (en) 2005-07-21

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