EP2049428B1 - Escalator - Google Patents
Escalator Download PDFInfo
- Publication number
- EP2049428B1 EP2049428B1 EP07786388A EP07786388A EP2049428B1 EP 2049428 B1 EP2049428 B1 EP 2049428B1 EP 07786388 A EP07786388 A EP 07786388A EP 07786388 A EP07786388 A EP 07786388A EP 2049428 B1 EP2049428 B1 EP 2049428B1
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- EP
- European Patent Office
- Prior art keywords
- chain wheel
- chain
- lever arm
- effective lever
- escalator
- 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.)
- Not-in-force
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- 230000000694 effects Effects 0.000 description 8
- 230000008092 positive effect Effects 0.000 description 2
- 206010038743 Restlessness Diseases 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B23/00—Component parts of escalators or moving walkways
- B66B23/02—Driving gear
- B66B23/022—Driving gear with polygon effect reduction means
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
- B66B23/00—Component parts of escalators or moving walkways
- B66B23/02—Driving gear
- B66B23/026—Driving gear with a drive or carrying sprocket wheel located at end portions
Definitions
- the present invention relates to an escalator according to the preamble of claim 1.
- escalator should include both escalators with stairs, as they are used for example in department stores, as well as moving walks with pallets, such as those used at airports.
- Fig. 1 schematically illustrated a link chain G and a partially wrapped by this sprocket R to define some terms in advance.
- the joint chain G comprises hingedly interconnected chain links K, which are connected via a pivot point P hinged together.
- the exemplified sprocket K has 8 teeth Z, between which tooth spaces are arranged, in which the pivot points P can engage.
- the pitch angle ⁇ between two teeth or two tooth gaps is 45 ° in the example shown.
- Fig. 1 on the lower side of the sprocket an entry angle ⁇ located, which can be caused for example by a joint chain G lowering guide.
- the lead-in angle ⁇ is measured between the actual output direction of the link chain G and the perpendicular S on the connecting line between the detachment point A of the link chain G from the sprocket R and the rotational axis D of the sprocket R.
- the entry angle ⁇ is about 11 ° in the example shown.
- Fig. 1 an instantaneous angle of wrap ⁇ is shown, which corresponds to the circumferential angle between two detachment points A of the articulated chain G from the sprocket R and is equal to 180 ° in the illustrated case. If a chain link K lifts off the sprocket R, the instantaneous wrap angle u will suddenly decrease, because at different entry angle ⁇ above and below, for example, lifts a chain link K on top, at the same time on the bottom of the next chain link K but not yet rests. Therefore, in the following, a mean wrap angle u is assumed which is greater than or equal to the minimum wrap angle and less than or equal to the maximum wrap angle u.
- an effective lever arm H eff is located on the upper side of the sprocket R, which corresponds to the vertical distance between the line of action W of the force, in particular tensile force of the link chain G and the axis of rotation D of the sprocket R.
- the effective lever arm H eff also fluctuates around the sprocket during articulation movement due to ligamentous detachment of the articulated chain, in particular due to the polygonal (polygonal support) of the chain.
- the effective lever arm H eff ' is slightly smaller, because due to the slightly tilted action line W of the force of the link chain G, the effective lever arm H eff ' no longer passes through the detachment point A.
- conveyor chains which are designed as so-called step chains or pallet chains, driven and also attached to these.
- the conveyor chains have three or four divisions, including three or four joints, per level.
- the sprockets used have about 16 to 25 teeth. This relatively high number is chosen to minimize the so-called polygon effect.
- the polygon effect is created by the fluctuating effective lever arm H eff (see Fig. 1 ).
- Sprockets are usually driven at a constant angular velocity. Due to fluctuating effective lever arms, the speed of the step chains fluctuates, as a result of constant acceleration and deceleration of the moving masses (chains, axes, steps), mass forces are generated which are introduced as disturbing forces or torques in the step / pallet chains or in the drive and partially there lead shortened life or represent an order of magnitude, which must be considered in the design of the particular drive components.
- the moving parts in an escalator together with the surrounding steel structure represent a vibratory spring-mass system.
- this spring-mass system can have very unfavorable operating points as a function of the number of teeth of the sprockets, the driving speed and the load.
- guides have been installed in the area of the sprockets, which cause a tangential inlet of the chain on the sprockets.
- the primary objective of this measure is to reduce the inlet noise of the chain to the sprockets.
- the polygon effect is reduced, but not compensated.
- step / pallet chain there are the high costs for the step / pallet chain. The more divisions it has, the more joints per step or per meter, the higher their costs. In addition, there are then per stage / pallet a larger number of bodies that are subject to wear. Over the operating period of the escalator, keeping the maximum permissible gap between the steps / pallets as long as possible is a very important criterion.
- An escalator of the type mentioned is from the European patent application EP 1 344 740 A1 known.
- the escalator described therein has a polygon compensated driven over the upper strand sprocket around which partially runs a joint chain.
- the sprocket has an odd number of teeth. Due to the odd number of teeth of Untertrum runs not polygonkompensiert, but on the contrary extremely non-uniform. Since the bottom strand Also, with masses such as the masses of chains, rollers, axles and steps or pallets, this non-uniformity gives rise to forces transmitted to the steps or pallets in the upper run.
- Such an escalator may run comparatively quiet in the heavily laden state due to the large quotient between the mass in the upper strand to the mass in the lower strand. In the unloaded or only a few persons occupied condition, she will also run in the upper strand very restless.
- the problem underlying the present invention is to provide a device of the type mentioned, which runs comparatively quiet even with a relatively small number of teeth of the at least one sprocket.
- the first sprocket and the second sprocket are offset from each other operated so that at minimum effective lever arm on the first sprocket in the same strand of the effective lever arm on the second sprocket is not minimal, preferably at most ⁇ 20% of the difference between maximum and minimum value deviates from the maximum value, in particular maximum.
- the angular position of the first sprocket may be different from that of the second sprocket by at least ⁇ 30%, preferably by at least ⁇ 40% of a pitch angle, in particular by half a pitch angle. Due to this antiphase of the two sprockets, a reciprocating motion of the second sprocket formed, for example, as a deflection wheel is reduced.
- the effective lever arm of the chain on the at least one sprocket in the upper run is substantially equal to the effective lever arm of the chain on the at least one sprocket in the lower run.
- this causes not only the upper run to run at a constant speed, but also the lower run.
- the solution according to the invention makes it possible to use stepped or pallet chains of substantially increased pitch, namely, for example, chain pitch equal to half step pitch or chain pitch equal to step pitch, and / or to reduce the required installation space.
- the escalator comprises at least one guide that can influence the angle of entry of the chain on the first and / or the second sprocket, wherein the at least one guide is arranged such that the entry angle with minimal effective Lever arm is smaller than at maximum effective lever arm.
- the at least one guide causes that when the machine is running, the oscillating movement of the deflection station is almost zero, which has absolutely positive effects in terms of smoothness.
- the at least one guide the rollers only very lightly loaded. It is therefore possible to use relatively inexpensive rollers.
- escalator comprises a chain 1 designed as a chain, which rotates about a first, driven sprocket 2 and a second, serving as a reversing sprocket 3.
- Each of the sprockets 2, 3 has six, only schematically indicated teeth.
- the chain 1 With the chain 1, the non-illustrated steps or pallets of the escalator are connected.
- Fig. 2 and Fig. 3 only a circumferential handrail 4 is indicated, which can be used by a user during the movement of the escalator.
- the chain 1 forms between the sprockets 2, 3 in each case above in Fig. 2 to Fig. 4 a top strand 5 and below in each case Fig. 2 to Fig. 4 a sub-tower 6.
- the first sprocket 2 is driven by a drive motor 7 via a drive chain 8 polygon fürso or polygonkompensiert. This can be achieved for example in the illustrated embodiment by engaging in the drive chain 8, non-circular wheel 9.
- Other possibilities of a polygon compensated drive are from the WO 03/036129 A1 which is explicitly made a part of the present disclosure.
- the polygonal-compensated drive allows the first sprocket 2 to be driven at a non-constant angular velocity in such a way that the driven chain 1 runs at a constant or almost constant speed.
- the handrail 4 is driven by the drive motor 7, the handrail 4 is driven at a constant angular velocity.
- the second sprocket 3 is slidably supported by means of a movable attachment 10.
- Fig. 4 shows that the second sprocket 3 is offset relative to the first sprocket 2 in terms of its angular position.
- the angular positions of the sprockets 2, 3 thus differ by 30 °, which corresponds to half a pitch angle of the six teeth having sprockets 2, 3, because the pitch angle is equal to 360 ° by the number of teeth.
- Fig. 4 are guides 18, 19 can be seen, which can specify the entry angle ⁇ 1 , ⁇ 2 of the chain 1 on the sprockets.
- the guide 18 so far down in Fig. 4 or the guide 19 as far as in Fig. 4 arranged that the entry angle ⁇ 1 at minimum effective lever arm 16, 16 '(see first sprocket 2 in Fig. 4 ) is significantly smaller than the entry angle ⁇ 2 at maximum effective lever arm 17, 17 '(see second sprocket 3 in FIG Fig. 4 ).
- the number of teeth of the sprockets 2, 3 used is straight. This applies to the case that the wrap angle of the chain 1 is about 180 °, which is the normal case for escalators / moving walks. What matters is that the effective lever arm on the side of the upper run is always essentially identical to the effective one Lever arm on the side of the lower run. This causes, when designed on the upper strand polygon compensation that not only the upper strand runs at a constant speed but also the lower strand (in the case of odd number of teeth at 180 ° wrap the bottom strand would run with about twice as high unevenness as a conventional, so not polygonkompensierter drive ).
- the wrap angle can also be performed deviating from 180 ° under the condition that the effective lever arms are identical in the upper and lower run. This means that the number of teeth and the wrap angle must then be adjusted for this case. In compliance with this condition, uniform chain speeds are set in the upper and in the lower run, which are necessary for the smooth running of the escalator / moving walk.
- the sprockets 2, 3 run at non-constant angular velocity and this effect with a smaller number of teeth is greater, it must be noted that they are as light as possible, so running with little moment of inertia, so that the forces exerted by you on the chains / stages / pallets disturbing forces are possible low. In particular, at the farther from the fulcrum point points to ensure weight optimization and, where appropriate, appropriate relief recesses or the like are provided.
- polygonal support of the particular large-scale chain 1 on the sprockets 2, 3 usually varies from meshing to meshing the center distance between the sprockets 2, 3.
- the chain 1 has, apart from elastic elongation, always a constant length.
- the drive sprockets are usually fixed in place and the deflection sprockets resiliently and linearly movable on the attachment 10. The deflection sprockets thus always make from pitch to pitch a linear movement. This is the larger the larger the chain pitch and the smaller the sprocket teeth number.
- the division can be very large, namely 1/1 or 1 ⁇ 2 of the step / pallet pitch and the number of teeth very small, namely up to 6 or 4, here can such a large linear movement of the second, as sprocket serving sprocket 3 and the deflection arc 20 come about that this is a disturbing for the smoothness of the escalator / moving walk component. It arise from this large linear movement of the Umlenkstation disturbing mass forces and it can also cause disturbing noises. Particularly unfavorable is the constellation when drive and Umlenkkettenrad have the same angular position (measured for example by the angle ⁇ or ⁇ of a sprocket corner relative to the horizontal).
- first and the second sprocket 2, 3 should preferably have the same number of teeth. Deviations from the same number of teeth in the range ⁇ 30% are tolerable.
- the guides 18, 19 used in an embodiment of the escalator according to the invention cause a run-in of the chain 1 on the sprockets 2, 3 just above the minimum effective lever arm. Furthermore, they are optionally curved at their ends, which causes the chains 1 is given a speed component in the radial direction shortly before hitting the sprockets 2, 3 or after their expiration of the sprockets 2, 3 on the guides.
- the impact component of the chain link points in the tooth gaps of the sprockets or on the guides 18, 19 is thus significantly reduced, which leads to much lower noise and more favorable running properties.
- Chain guides which cause a tangential entry of the chains on the sprockets and thus reduce inlet noise (chain - sprocket), can not be used in an escalator according to the invention, because at the realized there low numbers of sprockets and the resulting angle ratios, the burden on the Rollers are much too large or the rollers for these loads would be dimensioned, which would make this much more expensive. In addition, would be in this arrangement of the guides a large oscillating movement of the deflection arise with corresponding disadvantages as mentioned above.
- the correct height of the guide 18, 19 between minimum and maximum effective lever arm in the vicinity of the minimum lever arm causes the oscillating movement of the deflection station to become almost zero when the machine is running, which has absolutely positive effects on the smooth running.
- the rollers are loaded only very slightly in this arrangement of the guides. So you can use relatively inexpensive rollers.
- the optimal height of the chain guide is determined as follows:
- the chain links buckle at a certain angle as they leave the guides 18, 19.
- trigonometric functions all dimensions can be calculated.
- a pitch angle of, for example, 60 ° is thus subdivided, for example, into 20 steps of 3 ° each.
- the height of the guides will now be changed until the sum of the horizontal catheters on the different angular positions gives a value as constant as possible. Where these deviations have reached their minimum, the linear movement of the Umlenkkettengan / the deflection has its minimum.
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- Escalators And Moving Walkways (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
Description
Die vorliegende Erfindung betrifft eine Fahrtreppe gemäß dem Oberbegriff des Anspruchs 1.The present invention relates to an escalator according to the preamble of
Der Begriff Fahrtreppe soll sowohl Fahrtreppen mit Treppenstufen umfassen, wie sie beispielsweise in Kaufhäusern Verwendung finden, als auch Fahrsteige mit Paletten, wie sie beispielsweise auf Flughäfen Verwendung finden.The term escalator should include both escalators with stairs, as they are used for example in department stores, as well as moving walks with pallets, such as those used at airports.
In
Weiterhin ist in
In
Weiterhin ist an der oberen Seite des Kettenrades R ein effektiver Hebelarm Heff eingezeichnet, der dem senkrechten Abstand zwischen der Wirklinie W der Kraft, insbesondere Zugkraft der Gelenkkette G und der Drehachse D des Kettenrades R entspricht. Wie der momentane Umschlingungswinkel u schwankt auch der effektive Hebelarm Heff während der Bewegung der Gelenkkette aufgrund des gliedweisen Ablösens der Gelenkkette, insbesondere aufgrund der polygonalen (vieleckförmigen Auflage) der Kette um das Kettenrad. An der unteren Seite des Kettenrades R ist der effektive Hebelarm Heff' etwas kleiner, weil aufgrund der etwas verkippten Wirklinie W der Kraft der Gelenkkette G der effektive Hebelarm Heff' nicht mehr durch den Ablösepunkt A verläuft.Furthermore, an effective lever arm H eff is located on the upper side of the sprocket R, which corresponds to the vertical distance between the line of action W of the force, in particular tensile force of the link chain G and the axis of rotation D of the sprocket R. Like the instantaneous wrap angle u, the effective lever arm H eff also fluctuates around the sprocket during articulation movement due to ligamentous detachment of the articulated chain, in particular due to the polygonal (polygonal support) of the chain. On the lower side of the sprocket R, the effective lever arm H eff 'is slightly smaller, because due to the slightly tilted action line W of the force of the link chain G, the effective lever arm H eff ' no longer passes through the detachment point A.
Bei Fahrtreppen beziehungsweise Fahrsteigen werden in der Regel deren Stufen oder Paletten, insbesondere beidseitig, durch Förderketten, die als sogenannte Stufenketten oder Palettenketten ausgebildet sind, angetrieben und auch an diesen befestigt.In escalators or moving walks usually their steps or pallets, in particular on both sides, by conveyor chains, which are designed as so-called step chains or pallet chains, driven and also attached to these.
Üblicherweise haben die Förderketten drei oder vier Teilungen, also auch drei oder vier Gelenke, pro Stufe. Die verwendeten Kettenräder haben etwa 16 bis 25 Zähne. Diese verhältnismäßig hohe Zahl wird gewählt, um den sogenannten Polygoneffekt zu minimieren.Usually, the conveyor chains have three or four divisions, including three or four joints, per level. The sprockets used have about 16 to 25 teeth. This relatively high number is chosen to minimize the so-called polygon effect.
Der Polygoneffekt entsteht durch den schwankenden effektiven Hebelarm Heff (siehe
In der Praxis begegnet man diesem Sachverhalt üblicherweise durch Reduzierung der Kettenteilung und Erhöhung der Zähnezahl. Mit sinkender Teilung und steigender Zähnezahl wird der Polygoneffekt geringer, bis schließlich ein Maß erreicht wird, bei dem der Polygoneffekt in der Praxis so gering ist, also die Bewegung der Ketten / Stufen / Paletten so gleichmäßig ist, dass der Polygoneffekt praktisch nicht mehr stört, jedoch immer noch vorhanden ist.In practice, this situation is usually encountered by reducing the chain pitch and increasing the number of teeth. With decreasing pitch and increasing number of teeth, the polygon effect is reduced, until finally a level is reached at which the polygon effect in practice is so low, so the movement of the chains / stages / pallets is so uniform that the polygon effect practically no longer bothers but still exists.
Auch wurden Führungen im Bereich der Kettenräder installiert, die einen tangentialen Einlauf der Kette auf die Kettenräder bewirken. Das primäre Ziel dieser Maßnahme ist, das Einlaufgeräusch der Kette auf die Kettenräder zu reduzieren. Auch der Polygoneffekt wird hierbei reduziert, jedoch nicht kompensiert.Also, guides have been installed in the area of the sprockets, which cause a tangential inlet of the chain on the sprockets. The primary objective of this measure is to reduce the inlet noise of the chain to the sprockets. The polygon effect is reduced, but not compensated.
Die konventionelle Bauweise mit relativ geringer Kettenteilung und relativ großer Kettenrad-Zähnezahl hat jedoch entscheidende Nachteile.However, the conventional construction with relatively low chain pitch and relatively large sprocket teeth number has significant disadvantages.
Zuerst sind die hohen Kosten für die Stufen- / Palettenkette zu nennen. Je mehr Teilungen diese hat, desto mehr Gelenke pro Stufe oder pro Meter, umso höher ihre Kosten. Außerdem existieren dann pro Stufe / Palette eine größere Anzahl von Stellen, die einem Verschleiß unterliegen. Über den Betriebszeitraum der Fahrtreppe ist die möglichst lange Einhaltung des maximal zulässigen Spaltmaßes zwischen den Stufen / Paletten ein sehr wichtiges Kriterium.First of all, there are the high costs for the step / pallet chain. The more divisions it has, the more joints per step or per meter, the higher their costs. In addition, there are then per stage / pallet a larger number of bodies that are subject to wear. Over the operating period of the escalator, keeping the maximum permissible gap between the steps / pallets as long as possible is a very important criterion.
Bedingt durch hohe Zähnezahlen der Kettenräder haben diese relativ große Durchmesser und benötigen viel Bauraum, insbesondere für die Antriebsstation. Dadurch geht in Gebäuden kostbarer Raum verloren. Bedingt durch große Durchmesser werden hohe Antriebsmomente erforderlich, was entsprechende Kosten für die Antriebe mit sich bringt.Due to high numbers of teeth sprockets have relatively large diameter and require a lot of space, especially for the drive station. As a result, valuable space is lost in buildings. Due to large diameters, high drive torques are required, which entails corresponding costs for the drives.
Eine Fahrtreppe der eingangs genannten Art ist aus der europäischen Patentanmeldung
Auch aus der
Das der vorliegenden Erfindung zugrunde liegende Problem ist die Schaffung einer Vorrichtung der eingangs genannten Art, die auch bei vergleichsweise geringer Zähnezahl des mindestens einen Kettenrades vergleichsweise ruhig läuft.The problem underlying the present invention is to provide a device of the type mentioned, which runs comparatively quiet even with a relatively small number of teeth of the at least one sprocket.
Dies wird erfindungsgemäß durch die Fahrtreppe der eingangs genannten Art mit den kennzeichnenden Merkmalen des Anspruchs 1 erreicht. Die Unteransprüche betreffen bevorzugte Ausgestaltungen der Erfindung.This is inventively achieved by the escalator of the type mentioned above with the characterizing features of
Gemäß Anspruch 1 ist vorgesehen, dass das erste Kettenrad und das zweite Kettenrad derart versetzt gegeneinander betrieben werden, dass bei minimalem wirksamem Hebelarm am ersten Kettenrad im gleichen Trum der wirksame Hebelarm am zweiten Kettenrad nicht minimal ist, vorzugsweise höchstens um ± 20% der Differenz zwischen maximalem und minimalem Wert von dem maximalen Wert abweicht, insbesondere maximal ist. Dazu kann beispielsweise die Winkelstellung des ersten Kettenrades von der des zweiten Kettenrades um mindestens ± 30%, vorzugsweise um mindestens ± 40% eines Teilungswinkels, insbesondere um einen halben Teilungswinkel verschieden sein. Durch diese Gegenphasigkeit der beiden Kettenräder wird eine Hin- und Herbewegung des beispielsweise als Umlenkrad ausgebildeten zweiten Kettenrades verkleinert.According to
Gemäß einer bevorzugten Weiterbildung der erfindungsgemäßen Fahrtreppe ist vorgesehen, dass der wirksame Hebelarm der Kette an dem mindestens einen Kettenrad im Obertrum im wesentlichen gleich dem wirksamen Hebelarm der Kette an dem mindestens einen Kettenrad im Untertrum ist. Dies bewirkt bei beispielsweise auf den Obertrum ausgelegter Polygonkompensation, dass nicht nur der Obertrum mit konstanter Geschwindigkeit läuft, sondern auch der Untertrum. Die erfindungsgemäße Lösung erlaubt es, Stufenbeziehungsweise Palettenketten mit wesentlich vergrößerter Teilung, nämlich beispielsweise Kettenteilung gleich halber Stufenteilung oder Kettenteilung gleich Stufenteilung zu verwenden und/oder den benötigten Bauraum zu reduzieren.According to a preferred development of the escalator according to the invention, it is provided that the effective lever arm of the chain on the at least one sprocket in the upper run is substantially equal to the effective lever arm of the chain on the at least one sprocket in the lower run. For polygon compensation designed, for example, on the upper run, this causes not only the upper run to run at a constant speed, but also the lower run. The solution according to the invention makes it possible to use stepped or pallet chains of substantially increased pitch, namely, for example, chain pitch equal to half step pitch or chain pitch equal to step pitch, and / or to reduce the required installation space.
Gemäß einer bevorzugten Weiterbildung der erfindungsgemäßen Fahrtreppe ist vorgesehen, dass die Fahrtreppe mindestens eine Führung umfasst, die den Einlaufwinkel der Kette auf das erste und/oder das zweite Kettenrad beeinflussen kann, wobei die mindestens eine Führung derart angeordnet ist, das der Einlaufwinkel bei minimalem wirksamem Hebelarm kleiner ist als bei maximalem wirksamem Hebelarm. Eine derartige Anordnung der Führung bewirkt, dass bei laufender Maschine die oszillierende Bewegung der Umlenkstation nahezu Null wird, was sich hinsichtlich der Laufruhe absolut positiv auswirkt. Außerdem sind bei dieser Anordnung der mindestens einen Führung die Laufrollen nur sehr gering belastet. Es besteht also die Möglichkeit, relativ kostengünstige Laufrollen zu verwenden.According to a preferred embodiment of the escalator according to the invention it is provided that the escalator comprises at least one guide that can influence the angle of entry of the chain on the first and / or the second sprocket, wherein the at least one guide is arranged such that the entry angle with minimal effective Lever arm is smaller than at maximum effective lever arm. Such an arrangement of the guide causes that when the machine is running, the oscillating movement of the deflection station is almost zero, which has absolutely positive effects in terms of smoothness. In addition, in this arrangement, the at least one guide, the rollers only very lightly loaded. It is therefore possible to use relatively inexpensive rollers.
Weitere Merkmale und Vorteile der vorliegenden Erfindung werden deutlich anhand der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele unter Bezugnahme auf die beiliegenden Abbildungen. Darin zeigen
- Fig. 1
- schematisch ein Kettenrad und eine Gelenkkette zur Verdeutlichung verwendeter Begriffe;
- Fig. 2
- eine schematische Seitenansicht einer erfindungsgemäßen Fahrtreppe mit einem Umlenkkettenrad;
- Fig. 3
- eine schematische Seitenansicht einer erfindungsgemäßen Fahrtreppe mit einem Umlenkbogen anstelle eines Umlenkkettenrades, wobei der Umlenkbogen jedoch nicht zu der vorgeschlagenen Erfindung gehört;
- Fig. 4
- eine schematische vergrößerte Ansicht mehrerer für die Funktion der Fahrtreppe gemäß
Fig. 2 wesentlicher Komponenten.
- Fig. 1
- schematically a sprocket and a link chain for clarity of terms used;
- Fig. 2
- a schematic side view of an escalator according to the invention with a Umlenkkettenrad;
- Fig. 3
- a schematic side view of an escalator according to the invention with a Umlenkbogen instead of a Umlenkkettenrades, the deflection arc, however, does not belong to the proposed invention;
- Fig. 4
- a schematic enlarged view of several for the function of the escalator according to
Fig. 2 essential components.
Die aus
Das erste Kettenrad 2 wird von einem Antriebsmotor 7 über eine Antriebskette 8 polygonwirkungsfrei beziehungsweise polygonkompensiert angetrieben. Dies kann beispielsweise in dem abgebildeten Ausführungsbeispiel durch ein in die Antriebskette 8 eingreifendes, unrundes Rad 9 erreicht werden. Weitere Möglichkeiten eines polygonkompensierten Antriebs sind aus der
Der Handlauf 4 wird von dem Antriebsmotor 7 angetrieben, wobei der Handlauf 4 mit konstanter Winkelgeschwindigkeit angetrieben wird. Das zweite Kettenrad 3 ist mittels einer beweglichen Befestigung 10 verschieblich gehaltert.The
Bei der Darstellung gemäß
Dieser Unterschied in den Winkelstellungen der Kettenräder 2, 3 bewirkt, dass genau dann, wenn an dem ersten Kettenrad 2 die Kette 1 mit einem minimalen effektiven Hebelarm 16, 16' angreift, die Kette 1 an dem zweiten Kettenrad 3 mit einem maximalen effektiven Hebelarm 17, 17' angreift (siehe
Weiterhin ist aus
Aus
Eine weitere teilweise funktionale Beschreibung der Ausführungsbeispiele ergibt sich auch aus dem folgenden.A further partially functional description of the embodiments will also be apparent from the following.
Die Zähnezahl der verwendeten Kettenräder 2, 3 ist gerade. Dies gilt für den Fall, dass der Umschlingungswinkel der Kette 1 etwa 180° beträgt, was bei Fahrtreppen / Fahrsteigen der Normalfall ist. Entscheidend ist, dass der wirksame Hebelarm auf der Seite des Obertrums immer im Wesentlichen identisch ist mit dem wirksamen Hebelarm auf der Seite des Untertrums. Dies bewirkt, bei auf den Obertrum ausgelegter Polygonkompensation, dass nicht nur der Obertrum mit konstanter Geschwindigkeit läuft sondern auch der Untertrum (im Falle ungerader Zähnezahl bei 180° Umschlingungswinkel liefe der Untertrum mit ungefähr doppelt so hoher Ungleichmäßigkeit wie ein konventioneller, also nicht polygonkompensierter, Antrieb).The number of teeth of the
Der Umschlingungswinkel kann auch von 180° abweichend ausgeführt werden unter der Bedingung, dass die wirksamen Hebelarme bei Ober- und Untertrum identisch sind. Das bedeutet, dass Zähnezahl und Umschlingungswinkel dann für diesen Fall angepasst werden müssen. Unter Beachtung dieser Bedingung werden sich im Ober- und im Untertrum gleichmäßige Kettengeschwindigkeiten einstellen, die für den ruhigen Lauf der Fahrtreppe / des Fahrsteigs erforderlich sind.The wrap angle can also be performed deviating from 180 ° under the condition that the effective lever arms are identical in the upper and lower run. This means that the number of teeth and the wrap angle must then be adjusted for this case. In compliance with this condition, uniform chain speeds are set in the upper and in the lower run, which are necessary for the smooth running of the escalator / moving walk.
Die gleiche Gesetzmäßigkeit wie bei dem angetriebenen Kettenrad 2 gilt auch für die nicht angetriebene Umlenkstation (bei Fahrtreppen in der Regel die untere Landestation). Die Beachtung identischer wirksamer Hebelarme ist auch hier wichtig.The same law as with the driven
Da die Kettenräder 2, 3 mit nicht konstanter Winkelgeschwindigkeit laufen und dieser Effekt bei geringerer Zähnezahl umso größer wird, muß beachtet werden, dass diese möglichst leicht, also mit wenig Trägheitsmoment ausgeführt werden, damit die von Ihnen auf die Ketten/Stufen/Paletten ausgeübten Störkräfte möglicht gering sind. Insbesondere ist bei den weiter vom Drehpunkt entfernt liegenden Punkten auf Gewichtsoptimierung zu achten und gegebenenfalls sind entsprechende Erleichterungs-Aussparungen oder ähnliches vorzusehen.Since the
Durch polygonale Auflage der insbesondere großgliedrigen Kette 1 auf den Kettenrädern 2, 3 verändert sich üblicherweise von Zahneingriff zu Zahneingriff der Achsabstand zwischen den Kettenrädern 2, 3. Die Kette 1 hat, abgesehen von elastischer Längung, stets eine konstante Länge. Die Antriebs-Kettenräder sind normalerweise ortsfest angebracht und die Umlenk-Kettenräder federnd elastisch und linear beweglich an der Befestigung 10. Die Umlenk-Kettenräder machen also stets von Teilung zu Teilung eine lineare Bewegung. Diese ist umso größer je größer die Kettenteilung ist und je kleiner die Kettenrad-Zähnezahl ist.By polygonal support of the particular large-
Bei konventionellen Fahrtreppen mit relativ kleiner Kettenteilung und relativ großen Zähnezahlen muß dieser Sachverhalt gegebenenfalls nicht beachtet werden.In conventional escalators with relatively small chain pitch and relatively large numbers of teeth, this issue may not be considered.
Da bei einer erfindungsgemäßen Fahrtreppe (beziehungsweise Fahrsteig) die Teilung sehr groß sein kann, nämlich 1/1 oder ½ der Stufen-/Palettenteilung und die Zähnezahl sehr klein, nämlich bis zu 6 oder 4, kann hier eine so große lineare Bewegung des zweiten, als Umlenkrad dienenden Kettenrades 3 beziehungsweise des Umlenkbogens 20 zustande kommen, dass hieraus eine für die Laufruhe der Fahrtreppe / des Fahrsteiges störende Komponente wird. Es entstehen aus dieser großen linearen Bewegung der Umlenkstation störende Massenkräfte und es können auch störende Geräusche entstehen. Besonders ungünstig ist die Konstellation wenn Antriebs- und Umlenkkettenrad die gleiche Winkelstellung haben (gemessen beispielsweise durch den Winkel α beziehungsweise β einer Kettenrad-Ecke relativ zur Horizontalen).Since in an escalator according to the invention (or moving walk), the division can be very large, namely 1/1 or ½ of the step / pallet pitch and the number of teeth very small, namely up to 6 or 4, here can such a large linear movement of the second, as
Daher muss die relative Winkelstellung α, β der Kettenräder 2, 3 beachtet werden, das heißt, sie sollte gegenphasig sein: Zwischen der Winkelstellung des ersten Kettenrades 2 und der des zweiten - Kettenrades 3 muß etwa ein halber Teilungswinkel (± 20%) liegen (Teilungswinkel = 360° geteilt durch Zähnezahl). Das heißt, Achsabstand, Förderhöhe und Länge der Ketten müssen aufeinander abgestimmt sein.Therefore, the relative angular position α, β of the
Ferner sollten das erste und das zweite Kettenrad 2, 3 möglichst die gleiche Zähnezahl haben. Abweichungen von gleicher Zähnezahl im Bereich ± 30% sind dabei tolerierbar.Furthermore, the first and the
Des weiteren kommt der Führung der Ketten Bedeutung zu. Die bei einem Ausführungsbeispiel der erfindungsgemäßen Fahrtreppe verwendeten Führungen 18, 19 bewirken ein Einlaufen der Kette 1 auf die Kettenräder 2, 3 kurz über dem minimalen wirksamen Hebelarm. Des weiteren sind sie optional an ihren Enden gekrümmt, was bewirkt daß den Ketten 1 kurz vor Auftreffen auf die Kettenräder 2, 3 beziehungsweise nach deren Ablaufen von den Kettenrädern 2, 3 auf die Führungen eine Geschwindigkeitskomponente in radialer Richtung gegeben wird. Die Aufschlagkomponente der Kettengelenkpunkte in die Zahnlücken der Kettenräder beziehungsweise auf die Führungen 18, 19 wird also deutlich reduziert, was zu wesentlich geringeren Geräuschen und günstigeren Laufeigenschaften führt.Furthermore, the leadership of the chains is important. The
Kettenführungen, die einen tangentialen Einlauf der Ketten auf die Kettenräder herbeiführen und somit Einlaufgeräusche (Kette - Kettenrad) reduzieren, können bei einer erfindungsgemäßen Fahrtreppe nicht verwendet werden, weil bei den dort realisierten geringen Zähnezahlen der Kettenräder und den sich daraus ergebenden Winkelverhältnissen die Belastung für die Laufrollen viel zu groß werden beziehungsweise die Rollen für diese Belastungen zu dimensionieren wären, was diese stark verteuern würde. Außerdem würde sich bei dieser Anordnung der Führungen eine große oszillierende Bewegung der Umlenkstation ergeben mit entsprechenden Nachteilen wie oben bereits erwähnt.Chain guides, which cause a tangential entry of the chains on the sprockets and thus reduce inlet noise (chain - sprocket), can not be used in an escalator according to the invention, because at the realized there low numbers of sprockets and the resulting angle ratios, the burden on the Rollers are much too large or the rollers for these loads would be dimensioned, which would make this much more expensive. In addition, would be in this arrangement of the guides a large oscillating movement of the deflection arise with corresponding disadvantages as mentioned above.
Bei einer erfindungsgemäßen Fahrtreppe ist die richtige Höhe der Führung 18, 19 zwischen minimalem und maximalem wirksamem Hebelarm in der Nähe des minimalen Hebelarmes. Bringt man sie in der richtigen Höhe an, bewirkt dies, dass bei laufender Maschine die oszillierende Bewegung der Umlenkstation nahezu Null wird, was sich für die Laufruhe absolut positiv auswirkt. Außerdem sind bei dieser Anordnung der Führungen die Laufrollen nur sehr gering belastet. Man kann also relativ kostengünstige Laufrollen verwenden.In an escalator according to the invention, the correct height of the
Die optimale Höhe der Kettenführung wird wie folgt ermittelt: Die Kettengelenke knicken um einen bestimmten Winkel ab, wenn sie die Führungen 18, 19 verlassen. Man kann dort zeichnerisch oder auch gedanklich kleine rechtwinklige Dreiecke bilden, deren Hypotenuse das betrachtete Kettenglied ist, wobei eine der Katheten durch die Horizontale gebildet wird. Mithilfe der Winkelfunktionen lassen sich sämtliche Maße auch berechnen. Man bildet nun die Summe der waagerechten Katheten und ermittelt diese für verschiedene Winkelstellungen der Kettenräder innerhalb eines Teilungswinkels. Man lässt also gedanklich die Ketten immer wieder ein kleines Stück weiter laufen und die Kettenräder weiter drehen bis sich diese um einen Teilungswinkel weiter gedreht haben. Ein Teilungswinkel von beispielsweise 60° wird also beispielsweise in 20 Schritte von je 3° unterteilt. Die Höhe der Führungen wird nun solange verändert bis die Summe der waagerechten Katheten über die verschiedenen Winkelstellungen einen möglichst konstanten Wert ergibt. Dort wo diese Abweichungen ihr Minimum erreicht haben, hat auch die lineare Bewegung der Umlenkkettenräder / der Umlenkstation ihr Minimum.The optimal height of the chain guide is determined as follows: The chain links buckle at a certain angle as they leave the
Bei realen Fahrtreppen wären gegebenenfalls noch die Polygonwirkungen zu berücksichtigen, die sich beim Durchlaufen der Ketten durch die Kettenführungen in den Übergängen waagerechte /ansteigende Teile (Umlenkradien) ergeben.In the case of real escalators, the polygonal effects which, when passing through the chains by the chain guides in the transitions, would also result in horizontal / rising parts (deflection radii), would possibly have to be taken into account.
Claims (15)
- Escalator, comprising- a plurality of steps or panels;- at least one chain (1) for driving the steps or panels;- at least one chain wheel (2, 3) about which the chain (1) partially circulates, wherein the chain (1) forms an upper strand (5) and a lower strand (6) starting from the chain wheel (2, 3);- means for polygon compensation of the movement of the at least one chain wheel (2, 3);- wherein the escalator comprises a second chain wheel (3) about which the chain (1) partially circulates,characterized in that the first chain wheel (2) and the second chain wheel (3) are operated in an offset manner with respect to one another such that, with a minimum effective lever arm (16, 16') at the first chain wheel (2) in the same strand (5, 6), the effective lever arm (17, 17') at the second chain wheel (3) is not at a minimum.
- Escalator according to Claim 1, characterized in that the first chain wheel (2) and the second chain wheel (3) are operated in an offset manner with respect to one another such that, with a minimum effective lever arm (16, 16') at the first chain wheel (2) in the same strand (5, 6), the effective lever arm (17, 17') at the second chain wheel (3) deviates from the maximum value at most by 20% of the difference between the maximum and minimum value.
- Escalator according to Claim 1 or 2, characterized in that the first chain wheel (2) and the second chain wheel (3) are operated in an offset manner with respect to one another such that, with a minimum effective lever arm (16, 16') at the first chain wheel (2) in the same strand (5, 6), the effective lever arm (17, 17') at the second chain wheel (3) is at a maximum.
- Escalator according to one of Claims 1 to 3, characterized in that the effective lever arm (16, 17) of the chain (1) at the at least one chain wheel (2, 3) in the upper strand (5) is substantially equal to the effective lever arm (16', 17') of the chain (1) at the at least one chain wheel (2, 3) in the lower strand (6).
- Escalator according to one of Claims 1 to 4, characterized in that the escalator comprises at least one guide (18, 19) which can influence the run-in angle (φ1, φ2) of the chain (1) onto the first and/or the second chain wheel (2, 3), wherein the at least one guide (18, 19) is arranged such that the run-in angle (φ1, φ2) is smaller with a minimum effective lever arm (16, 16') than with a maximum effective lever arm (17, 17').
- Escalator according to one of Claims 1 to 5, characterized in that the first chain wheel (2) is a driven chain wheel.
- Escalator according to one of Claims 1 to 6, characterized in that the second chain wheel (3) is a deflecting wheel.
- Escalator according to one of Claims 1 to 7, characterized in that the number of teeth of the first and/or second chain wheel (2, 3) is even.
- Escalator according to one of Claims 1 to 8, characterized in that the number of teeth of the first chain wheel (2) is less than or equal to 12, in particular 4 or 6.
- Escalator according to one of Claims 1 to 9, characterized in that the number of teeth of the second chain wheel (3) is less than or equal to 12, in particular 4 or 6.
- Escalator according to one of Claims 1 to 10, characterized in that the number of teeth of the first chain wheel (2) is not equal to or is approximately equal to or is equal to the number of teeth on the second chain wheel (3).
- Escalator according to one of Claims 1 to 11, characterized in that the average wrap angle (v) of the first and/or of the second chain wheel (2, 3) deviates from an integer multiple of the pitch angle (τ) by at most ±20% of the pitch angle (τ).
- Escalator according to Claim 12, characterized in that the average wrap angle (ν) of the first and/or of the second chain wheel (2, 3) is an integer multiple of the pitch angle (τ).
- Escalator according to one of Claims 1 to 13, characterized in that the angular position of the first chain wheel (2) differs from that of the second chain wheel (3) by at least ±30% of a pitch angle (τ).
- Escalator according to Claim 14, characterized in that the angular position of the first chain wheel (2) differs from that of the second chain wheel (3) by at least ±40% of a pitch angle (τ), in particular by half a pitch angle (τ).
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP12162123A EP2471737A1 (en) | 2006-08-02 | 2007-07-27 | escalator |
PL07786388T PL2049428T3 (en) | 2006-08-02 | 2007-07-27 | Escalator |
EP12162122A EP2471736A1 (en) | 2006-08-02 | 2007-07-27 | escalator |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006036353A DE102006036353A1 (en) | 2006-08-02 | 2006-08-02 | Escalator, has steps driven by chain conveyor, which is driven by driving wheel, where driving wheel is driven in polygon-offset manner to drive driving wheel with non-constant angular speed and conveyor is operated with constant speed |
DE102007034628 | 2007-07-23 | ||
PCT/EP2007/006676 WO2008014938A1 (en) | 2006-08-02 | 2007-07-27 | Escalator |
Related Child Applications (2)
Application Number | Title | Priority Date | Filing Date |
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EP12162122.1 Division-Into | 2012-03-29 | ||
EP12162123.9 Division-Into | 2012-03-29 |
Publications (2)
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EP2049428A1 EP2049428A1 (en) | 2009-04-22 |
EP2049428B1 true EP2049428B1 (en) | 2013-01-09 |
Family
ID=38996898
Family Applications (3)
Application Number | Title | Priority Date | Filing Date |
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EP12162123A Withdrawn EP2471737A1 (en) | 2006-08-02 | 2007-07-27 | escalator |
EP07786388A Not-in-force EP2049428B1 (en) | 2006-08-02 | 2007-07-27 | Escalator |
EP12162122A Withdrawn EP2471736A1 (en) | 2006-08-02 | 2007-07-27 | escalator |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
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EP12162123A Withdrawn EP2471737A1 (en) | 2006-08-02 | 2007-07-27 | escalator |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
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EP12162122A Withdrawn EP2471736A1 (en) | 2006-08-02 | 2007-07-27 | escalator |
Country Status (8)
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US (3) | US8286778B2 (en) |
EP (3) | EP2471737A1 (en) |
JP (3) | JP5461182B2 (en) |
CN (1) | CN102249141B (en) |
ES (1) | ES2402824T3 (en) |
PL (1) | PL2049428T3 (en) |
RU (1) | RU2412896C2 (en) |
WO (1) | WO2008014938A1 (en) |
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-
2007
- 2007-07-27 JP JP2009522151A patent/JP5461182B2/en not_active Expired - Fee Related
- 2007-07-27 EP EP12162123A patent/EP2471737A1/en not_active Withdrawn
- 2007-07-27 US US12/376,018 patent/US8286778B2/en not_active Expired - Fee Related
- 2007-07-27 EP EP07786388A patent/EP2049428B1/en not_active Not-in-force
- 2007-07-27 EP EP12162122A patent/EP2471736A1/en not_active Withdrawn
- 2007-07-27 CN CN2011101550486A patent/CN102249141B/en not_active Expired - Fee Related
- 2007-07-27 PL PL07786388T patent/PL2049428T3/en unknown
- 2007-07-27 WO PCT/EP2007/006676 patent/WO2008014938A1/en active Application Filing
- 2007-07-27 ES ES07786388T patent/ES2402824T3/en active Active
- 2007-07-27 RU RU2009107222/11A patent/RU2412896C2/en not_active IP Right Cessation
-
2011
- 2011-05-26 US US13/116,070 patent/US8292058B2/en not_active Expired - Fee Related
- 2011-05-26 US US13/116,075 patent/US8292059B2/en not_active Expired - Fee Related
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2012
- 2012-10-24 JP JP2012234934A patent/JP2013063854A/en active Pending
-
2015
- 2015-10-16 JP JP2015205097A patent/JP5996757B2/en not_active Expired - Fee Related
Also Published As
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US8286778B2 (en) | 2012-10-16 |
US20090308712A1 (en) | 2009-12-17 |
JP2009545501A (en) | 2009-12-24 |
RU2412896C2 (en) | 2011-02-27 |
EP2049428A1 (en) | 2009-04-22 |
WO2008014938A8 (en) | 2008-03-20 |
EP2471737A1 (en) | 2012-07-04 |
JP5461182B2 (en) | 2014-04-02 |
US20110220456A1 (en) | 2011-09-15 |
ES2402824T3 (en) | 2013-05-09 |
EP2471736A1 (en) | 2012-07-04 |
PL2049428T3 (en) | 2013-06-28 |
JP2013063854A (en) | 2013-04-11 |
US8292059B2 (en) | 2012-10-23 |
JP5996757B2 (en) | 2016-09-21 |
JP2016027993A (en) | 2016-02-25 |
CN102249141B (en) | 2013-03-27 |
RU2009107222A (en) | 2010-09-10 |
US20110220457A1 (en) | 2011-09-15 |
WO2008014938A1 (en) | 2008-02-07 |
CN102249141A (en) | 2011-11-23 |
US8292058B2 (en) | 2012-10-23 |
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