EP2471736A1 - escalier mécanique - Google Patents

escalier mécanique Download PDF

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Publication number
EP2471736A1
EP2471736A1 EP12162122A EP12162122A EP2471736A1 EP 2471736 A1 EP2471736 A1 EP 2471736A1 EP 12162122 A EP12162122 A EP 12162122A EP 12162122 A EP12162122 A EP 12162122A EP 2471736 A1 EP2471736 A1 EP 2471736A1
Authority
EP
European Patent Office
Prior art keywords
sprocket
chain
escalator
escalator according
lever arm
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.)
Withdrawn
Application number
EP12162122A
Other languages
German (de)
English (en)
Inventor
Burkhard Grobbel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ketten Wulf Betriebs GmbH
Original Assignee
Ketten Wulf Betriebs GmbH
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 claimed from DE102006036353A external-priority patent/DE102006036353A1/de
Application filed by Ketten Wulf Betriebs GmbH filed Critical Ketten Wulf Betriebs GmbH
Publication of EP2471736A1 publication Critical patent/EP2471736A1/fr
Withdrawn legal-status Critical Current

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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 deflecting 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 inlet 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 is lifted off the sprocket R, the instantaneous wrap angle ⁇ will suddenly decrease, because at different entry angles ⁇ above and below, for example, a chain link K lifts on the top, but at the same time the next chain link K does not yet rest on the underside. Therefore, in the following, a mean wrap angle ⁇ is assumed that is greater than or equal to the minimum wrap angle and less than or equal to the maximum wrap angle.
  • 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 movement of the articulated chain due to the joint 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 over the upper strand driven sprocket around which partially runs a link 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 lower strand is also afflicted with masses, such as the masses of the chains, rollers, axles and steps or pallets, arise from this non-uniformity forces that are 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 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, for example, designed on the upper strand polygon compensation that not only the upper run runs at a constant speed, but also the lower strand.
  • the solution according to the invention makes it possible to use step or pallet chains with significantly increased pitch, namely, for example, chain pitch equal to half step spacing or chain pitch equal step spacing, and / or to reduce the required installation space.
  • the first sprocket and the second sprocket are offset from each other operated in such a way that at minimum effective lever arm on the first sprocket in the same strand the effective lever arm on the second sprocket is not minimal, preferably at most ⁇ 20% of 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 escalator comprises at least one guide which can influence the entry angle of the chain on the first and / or the second sprocket, wherein the at least one guide is arranged such that the entry angle is smaller with a minimum effective lever arm is than at maximum effective lever arm.
  • the at least one guide causes the oscillating movement of the deflection station is almost zero when the machine is running, which has absolutely positive effects in terms of smoothness.
  • the at least one guide the rollers only very low burden. It is therefore possible to use relatively inexpensive rollers.
  • 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 ).
  • a deflection arc 20 is provided.
  • the radius is chosen so that even at the deflection arc 20 of the effective lever arm (not shown) in the upper run 5 is equal to the effective lever arm in the lower strand 6.
  • the guides 18, 19 lead the chain 1 in such a way in the deflection arc, that the lead-in angle with a minimum effective lever arm is significantly smaller than the lead-in angle with the maximum effective lever arm.
  • the circulating arc 20, the first sprocket 2 and the chain 1 can be designed and arranged such that just when the chain 1 acts on the first sprocket 2 with a minimum effective lever arm 16, 16 ', the chain 1 on the deflection arc 20 attacks with a maximum effective lever arm, and vice versa.
  • 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. It is crucial that the effective lever arm on the side of the upper run is always substantially identical to the effective 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 same law as with the driven sprocket 2 also applies to the non-driven diverter (in escalators usually the lower landing station).
  • the consideration of identical effective lever arms is also important here. This also applies to the case that a sprocket 3 is not used for the deflection, but a non-toothed, fixed mounted or resilient / elastic mounted deflecting bow 20 is used.
  • the radii or diameter of the deflection arc must be designed taking into account the diameter of the chain rollers so that the joint centers of the chain 1 on a corresponding circle, which corresponds to that of a sprocket with a corresponding number of teeth, expire.
  • the sprockets 2, 3 run at a 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.
  • 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.
  • the guides would result in a large oscillating movement of the deflection station with corresponding disadvantages as already 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. Also, this one Arrangement of the guides the rollers loaded only very low. 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.

Landscapes

  • Escalators And Moving Walkways (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
EP12162122A 2006-08-02 2007-07-27 escalier mécanique Withdrawn EP2471736A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006036353A DE102006036353A1 (de) 2006-08-02 2006-08-02 Fahrtreppe
DE102007034628 2007-07-23
EP07786388A EP2049428B1 (fr) 2006-08-02 2007-07-27 Escalier mécanique

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP07786388.4 Division 2007-07-27

Publications (1)

Publication Number Publication Date
EP2471736A1 true EP2471736A1 (fr) 2012-07-04

Family

ID=38996898

Family Applications (3)

Application Number Title Priority Date Filing Date
EP12162123A Withdrawn EP2471737A1 (fr) 2006-08-02 2007-07-27 escalier mécanique
EP12162122A Withdrawn EP2471736A1 (fr) 2006-08-02 2007-07-27 escalier mécanique
EP07786388A Not-in-force EP2049428B1 (fr) 2006-08-02 2007-07-27 Escalier mécanique

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP12162123A Withdrawn EP2471737A1 (fr) 2006-08-02 2007-07-27 escalier mécanique

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP07786388A Not-in-force EP2049428B1 (fr) 2006-08-02 2007-07-27 Escalier mécanique

Country Status (8)

Country Link
US (3) US8286778B2 (fr)
EP (3) EP2471737A1 (fr)
JP (3) JP5461182B2 (fr)
CN (1) CN102249141B (fr)
ES (1) ES2402824T3 (fr)
PL (1) PL2049428T3 (fr)
RU (1) RU2412896C2 (fr)
WO (1) WO2008014938A1 (fr)

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FI20090265A (fi) * 2009-07-03 2011-01-04 Kone Corp Henkilökuljetin ja menetelmä
US8430210B2 (en) 2011-01-19 2013-04-30 Smart Lifts, Llc System having multiple cabs in an elevator shaft
US9365392B2 (en) 2011-01-19 2016-06-14 Smart Lifts, Llc System having multiple cabs in an elevator shaft and control method thereof
US8925689B2 (en) 2011-01-19 2015-01-06 Smart Lifts, Llc System having a plurality of elevator cabs and counterweights that move independently in different sections of a hoistway
WO2012161691A1 (fr) * 2011-05-23 2012-11-29 Otis Elevator Company Accouplement à compensation de polygone pour des systèmes entraînés par chaîne et pignon
WO2013092238A1 (fr) 2011-12-22 2013-06-27 Ketten-Wulf Betriebs-Gmbh Transmission par moyen de traction
TWI612241B (zh) * 2012-12-07 2018-01-21 伊文修股份有限公司 具有梯級帶之升降梯及具有板帶之移動步道
DE102013103323A1 (de) 2013-04-03 2014-10-23 Ketten-Wulf Betriebs-Gmbh Zugmitteltrieb
DE102014103045A1 (de) 2014-03-07 2015-09-10 Ketten-Wulf Betriebs-Gmbh Fahrgeschäft, insbesondere Achterbahn
RU2682693C1 (ru) * 2014-05-28 2019-03-20 Инвенцио Аг Шарнирная цепь траволатора или эскалатора
EP3227221A1 (fr) 2014-12-02 2017-10-11 Otis Elevator Company Chaîne d'entraînement et mécanisme de chaîne d'entraînement et transporteur comprenant un tel mécanisme de chaîne d'entraînement
CN104843424A (zh) * 2015-05-20 2015-08-19 江苏比微曼智能科技有限公司 一种工件贴合机构及其所用的链式传送机构
EP3243788B1 (fr) 2016-05-10 2020-03-04 Otis Elevator Company Transporteur de passagers
CN105730711B (zh) * 2016-05-11 2017-11-24 亳州沃野知识产权服务有限公司 一种飞机用自动电梯
JP6382425B1 (ja) * 2017-10-13 2018-08-29 三菱重工機械システム株式会社 垂直循環式駐車装置及びその改造方法
CN112499450B (zh) * 2020-11-27 2022-12-06 中铁第四勘察设计院集团有限公司 一种监测自动扶梯主驱动电机是否稳定的系统及方法

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WO2003036129A1 (fr) 2001-10-26 2003-05-01 Burkhard Grobbel Entrainement de chaine articulee
EP1344740A1 (fr) 2002-03-13 2003-09-17 Thyssen Fahrtreppen GmbH Escalier mécanique ou trottoir roulant
DE10218374A1 (de) * 2002-04-25 2003-11-13 Kone Corp Antriebssystem zur Reduzierung des Polygoneffektes bei umlaufenden Antriebsketten von Rolltreppen und Rollsteigen
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Publication number Priority date Publication date Assignee Title
US4498890A (en) * 1982-12-20 1985-02-12 General Electric Company Fixed track chain drive
GB2243430A (en) * 1990-04-18 1991-10-30 Hitachi Ltd Power transmission apparatus, sprocket means used therein, and passenger conveyer using the same
WO2003036129A1 (fr) 2001-10-26 2003-05-01 Burkhard Grobbel Entrainement de chaine articulee
EP1344740A1 (fr) 2002-03-13 2003-09-17 Thyssen Fahrtreppen GmbH Escalier mécanique ou trottoir roulant
DE10218374A1 (de) * 2002-04-25 2003-11-13 Kone Corp Antriebssystem zur Reduzierung des Polygoneffektes bei umlaufenden Antriebsketten von Rolltreppen und Rollsteigen
WO2005090221A1 (fr) * 2004-03-23 2005-09-29 Toshiba Elevator Kabushiki Kaisha Dispositif transporteur

Also Published As

Publication number Publication date
WO2008014938A8 (fr) 2008-03-20
JP5461182B2 (ja) 2014-04-02
US20090308712A1 (en) 2009-12-17
US20110220457A1 (en) 2011-09-15
PL2049428T3 (pl) 2013-06-28
CN102249141A (zh) 2011-11-23
US8292059B2 (en) 2012-10-23
RU2009107222A (ru) 2010-09-10
EP2049428A1 (fr) 2009-04-22
CN102249141B (zh) 2013-03-27
JP2013063854A (ja) 2013-04-11
US20110220456A1 (en) 2011-09-15
US8286778B2 (en) 2012-10-16
RU2412896C2 (ru) 2011-02-27
JP2009545501A (ja) 2009-12-24
WO2008014938A1 (fr) 2008-02-07
ES2402824T3 (es) 2013-05-09
JP5996757B2 (ja) 2016-09-21
EP2471737A1 (fr) 2012-07-04
JP2016027993A (ja) 2016-02-25
EP2049428B1 (fr) 2013-01-09
US8292058B2 (en) 2012-10-23

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