EP2229333A1 - Ascenseur doté de deux cabines d'ascenseur et d'un contrepoids commun - Google Patents

Ascenseur doté de deux cabines d'ascenseur et d'un contrepoids commun

Info

Publication number
EP2229333A1
EP2229333A1 EP08865484A EP08865484A EP2229333A1 EP 2229333 A1 EP2229333 A1 EP 2229333A1 EP 08865484 A EP08865484 A EP 08865484A EP 08865484 A EP08865484 A EP 08865484A EP 2229333 A1 EP2229333 A1 EP 2229333A1
Authority
EP
European Patent Office
Prior art keywords
elevator
braking device
elevator car
counterweight
deflection roller
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Withdrawn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
EP08865484A
Other languages
German (de)
English (en)
Inventor
Bjarne Lindberg
Marius STÜCHELI
Josef Husmann
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.)
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
Application filed by Inventio AG filed Critical Inventio AG
Priority to EP08865484A priority Critical patent/EP2229333A1/fr
Publication of EP2229333A1 publication Critical patent/EP2229333A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B9/00—Kinds or types of lifts in, or associated with, buildings or other structures
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B11/00—Main component parts of lifts in, or associated with, buildings or other structures
    • B66B11/0065—Roping
    • B66B11/008—Roping with hoisting rope or cable operated by frictional engagement with a winding drum or sheave
    • B66B11/0095—Roping with hoisting rope or cable operated by frictional engagement with a winding drum or sheave where multiple cars drive in the same hoist way

Definitions

  • the present invention relates to an elevator comprising a first elevator car, a second elevator car and a counterweight, wherein the counterweight, the first and the second elevator cars are coupled to each other via a lifting means and a method for damping vibrations in such elevator.
  • Lifts with two elevator cars and common counterweight are known, for example, from US Pat. No. 1,837,643, in which the counterweight is arranged in the suspension element line between the first and the second elevator car and moves in the opposite direction to the two elevator cars.
  • the counterweight, the first and the second elevator car are additionally coupled to each other via a compensating means also described in EP 0 619 263 B1, which in US 1, 837,643 has three inertially arranged in a shaft pit and two arranged on the counterweight Pulleys running.
  • the compensating means transmits fluctuations in the traction force of the suspension elements when the other elevator car is moved onto the stationary elevator car. Due to the elastic suspension of the stationary elevator car on the suspension element and the elasticity of the suspension element, this leads to unwanted vibrations which impair the ride comfort and adversely affect the components of the elevator, in particular the suspension element, in its fastenings and the suspensions of the elevator cars.
  • Object of the present invention is therefore to reduce such loads.
  • a lift according to the preamble of claim 1 is further developed by its characterizing features.
  • Claim 16 protects a corresponding method.
  • the dependent claims relate to advantageous development.
  • An elevator comprises at least a first and a second elevator car and at least one counterweight, which are coupled to one another via a lifting and holding means.
  • the counterweight may in particular be arranged in the suspension element line between the first and the second elevator car and moved in opposite directions to the sum of the signed speeds of the two elevator cars. For example, it lowers when one of the first and second elevator cars is raised and the other one of the first and second elevator cars is also raised or standing.
  • the counterweight is raised, for example, when one of the first and second elevator cars is lowered faster than the other one is lifted by the first and second elevator cars.
  • the first and second elevator cars can preferably travel in the same elevator shaft next to each other or one above the other, wherein in the latter case an elevator control advantageously prevents a collision of the two elevator cars.
  • the counterweight, the first and the second elevator car are additionally coupled to each other via a compensation means.
  • the supporting and / or compensating means may comprise, for example, one or more metal or synthetic fiber ropes with optional sheaths, straps with wrapped tension members made of metal or plastic fibers or the like, and runs over at least one deflection roller in order to advantageously provide an inertial connection, a joint use of the counterweight and to allow a flaschenzugieri distribution of tensile forces.
  • the elevator further comprises at least one braking device for applying a braking torque to the deflection roller, which counteracts a rotational movement of the deflection roller and dissipatively dissipates the rotational energy transmitted by the compensation means to the deflection roller.
  • the tensile force now fluctuates in the suspension element, for example during acceleration or deceleration of one elevator car, while the other elevator car is stationary, this imparts tensile force fluctuations and micro-movements in the compensation device which, in particular in conjunction with an elastic suspension, cause oscillations of the elevator cars and the counterweight.
  • the braking torque, braking acting on the deflection roller over which the compensation means runs, has a damping effect on such vibrations, which advantageously reduces vibration-induced loads on the elevator components.
  • the braking device is selectively adjustable between a released position in which it applies little or no braking torque to the diverting pulley and a closed position in which it applies a greater braking torque.
  • the braking device may be designed such that it applies a dissipative braking torque to the at least one deflection roller when one of the first or second elevator car is stationary and the other moves from the first or second elevator car, since in this case changes in the tensile force on the traveling elevator cab particularly lead to vibrations. If, on the other hand, the first and second elevator cars both negotiate or stand, the braking device is advantageously ventilated, since in this case fewer vibrations are induced.
  • the braking torque applied by the braking device to the deflection roller is adjustable, in particular controllable.
  • the braking device can be controlled or regulated, for example, by an elevator control.
  • the applied braking torque can be optimally adapted and increased, for example, at higher vibrations in order to dampen them more.
  • such an adjustable braking device can also support an emergency stop of an elevator car, for example a catching of the car by catch brakes in the event of a failure of the suspension element.
  • the individual braking devices can advantageously be controlled or regulated differently.
  • the deflection roller may be closed on a stationary elevator car and there counteracting incoming tensile force fluctuations in a damping manner, while at the same time a deflection roller on a traveling elevator car and / or a consequently moved counterweight is not to hinder the required rotation of the pulleys.
  • the total speed of the compensating means, with which it passes over a deflection roller is composed of a basic component, which results from the process of the elevator car or counterweight, and a superimposed sign-changing component, which results from the generally higher-frequency vibrations.
  • the braking device is therefore designed so that the braking torque applied by it to the deflection roller is dependent on the rotational speed of the deflection roller, in particular increases with increasing rotational speed, for example substantially proportionally.
  • velocity-proportional forces or torques which counteract a movement damp vibrations particularly efficiently and stably, since the higher velocity components resulting from vibrations are more strongly damped, while a uniform ground speed is only slightly influenced by the braking device acting as a low-pass filter.
  • the braking device may comprise a, in particular hydraulic, pneumatic, mechanical or magnetic damper.
  • the braking device may comprise a fluid roller damper, which is connected directly, via a gear and / or a coupling with the axis of the deflection roller.
  • a roller damper generally comprises a fluid pump driven by the diverting pulley and a fluid, for example, in a hydraulic roller damper, pumping a hydraulic fluid, such as oil, through a circuit in which a valve is disposed.
  • a fluid can also be used a gas and so a pneumatic damper can be formed.
  • the fluid circuit is advantageously designed with low friction.
  • the valve can be adjusted, for example, continuously or in discrete stages, whereby the throttle losses and thus the dissipated energy can be adjusted. If the valve is closed more strongly, the fluid pump circulating fluid counteracts a higher flow resistance. This increases at higher speeds of the pulley and the associated pump and the circulating through this fluid, so that an adjustable damping constant of a speed proportional damping can be realized by an adjustable valve, which advantageously to different types of lifts or operating conditions, such as payloads and / or positions the elevator cabins is customizable. For example, in heavier elevator cabins with lower natural frequencies, the damping constant can be reduced.
  • the braking device can advantageously act as an (additional) holding or parking brake.
  • the braking device may for example comprise a fluid rotation brake, which is connected directly, via a gear and / or a coupling with the axis of the deflection roller.
  • a rotary brake works according to the above-described principle, wherein instead of the valve, a throttle device is arranged in the fluid circuit, which results due to their flow resistance with the speed of the fluid pump and thus the rotational speed of the pulley connected to it, speed-dependent braking torque.
  • a throttle requires no external energy for actuation, but can work autonomously and automatically.
  • the braking device may for example comprise a centrifugal brake, which is connected directly, via a gear and / or a coupling with the axis of the deflection roller.
  • a centrifugal brake for example, act mechanically and for this purpose comprises one or more friction linings, which move radially outwardly under a centrifugal force acting on them and exert a braking torque on a brake bell.
  • a centrifugal brake advantageously operates without external power supply and provides a speed-dependent brake torque for vibration damping.
  • a breakaway speed, at the first time brake torque is built up, and the dependence of the braking torque of the rotational speed of the deflection roller, for example, on the spring stiffness and / or bias of acting against the centrifugal force return springs, the masses of friction linings or the like can be adjusted.
  • a designed as a fluid roller damper braking device can be preferably ventilated by opening the valve, this can be used in a fluid-rotation brake or centrifugal brake, which operate automatically speed-dependent, the braking device advantageously be separated via a coupling of the pulley, for example, if both elevator cabins method and the braking device should not apply any braking torque to the deflection roller. As a result, the deflection roller then rotates advantageous low friction.
  • the braking device comprises a vibration damper.
  • This generally includes a damper mass coupled to the diverting pulley via a spring-damper assembly.
  • a vibration damper can be separated as described above in a preferred embodiment via a coupling of the deflection roller.
  • the braking device may also include a controllable or controllable brake, the braking torque of which can be controlled or controlled substantially independently of the rotational speed, for example a mechanical friction brake such as a drum or jaw brake, but also an electromagnetic eddy current brake. By selectively closing and releasing such a brake vibrations can also be damped, but also a low-friction operation can be realized.
  • a controllable or controllable brake the braking torque of which can be controlled or controlled substantially independently of the rotational speed
  • a mechanical friction brake such as a drum or jaw brake
  • an electromagnetic eddy current brake By selectively closing and releasing such a brake vibrations can also be damped, but also a low-friction operation can be realized.
  • Such brakes can be actuated, for example, by an elevator control, in particular an elevator car control system.
  • the braking device can be coupled directly to the deflection pulley via a transmission and / or a clutch, so that the braking device operates in favorable speed ranges or can be decoupled to reduce losses.
  • the compensation means can run over several pulleys. For example, it can run over one or more deflection rollers arranged on the counterweight, one or more deflection rollers inertially fixed in a shaft of the elevator, in particular in a shaft pit, and / or one or more deflection rollers connected to a tensioning device, in particular a tension weight.
  • the first and / or second elevator car with a 1: 1 ratio and / or the counterweight are suspended in a 2: 1 ratio of the compensation means, so that the counterweight moves in relation to an elevator car by half the distance.
  • the first and / or second elevator car with a 1: 1 ratio and / or the counterweight with a 2: 1 ratio be suspended on the support means, so that the suspension to support and compensation means advantageously correspond to each other.
  • the compensating means runs over a plurality of deflection rollers, preferably two or more deflection rollers can cooperate with a braking device designed to apply a dissipative braking torque acting on this deflection roller, as described above, the individual braking devices being the same or extending from one another Dimension, vote or principle of action can differ.
  • a braking device which cooperates with a deflection roller on the counterweight, which rotates both when the first first and traversing second elevator car and when moving the first and stationary second elevator car, be designed particularly low friction
  • a braking device with a deflection roller on an elevator car cooperates, with an additional hold function.
  • such braking devices can advantageously be controlled differently. For example, by at least partially closing a valve of a fluid roll damper, coupling a rotary or centrifugal brake, or closing a controllable mechanical brake, a braking torque may be applied to a diverting pulley connected to an elevator car when that elevator car is stationary To dampen vibrations that are conveyed by another, traveling elevator car on the compensation means and the pulley to the standing elevator car. Conversely, as by at least partially opening a valve of a fluid roll damper, uncoupling a rotary or centrifugal brake, or ventilating a controllable mechanical brake, the energy dissipated in this pulley can be reduced when this elevator car moves.
  • FIG. 1 shows in lateral cross-section an elevator according to an embodiment of the present invention with a first elevator car 1 and a second elevator car 2.
  • the two elevator cars are coupled to each other via a suspension element in the form of a belt 4, which runs in the same direction over a first traction sheave of a first drive 7.1 for the first elevator car and a second traction sheave of a second drive 7.2 for the second elevator car.
  • a first or second electric motor of the first and second drive 7.1 and 7.2 can apply a torque to the first and second traction sheave to raise the first and second elevator car 1 and 2, to hold or lower.
  • the elevator cars 1, 2 arranged side by side in an elevator shaft 9 can move independently of one another.
  • the support means 4 runs between the two drives 7.1, 7.2 in opposite directions around a deflection roller 5.4, on which a counterweight 3 is suspended, so that the first and second elevator car 1, 2 in a 1: 1 ratio and the counterweight 3 in a 2: 1 - are suspended on the suspension means 4, i. e. the suspension element decreases in a ratio of 1: 2, when the first or second elevator car 1 or 2 is raised and vice versa.
  • a compensation means in the form of a belt 5 is struck. This runs, starting from the first elevator car 1, around a first inertially mounted in the pit of the elevator shaft 9 pulley 5.1, then wraps in the opposite direction a fixed to the underside of the counterweight 3 third guide pulley 5.3, again runs in opposite directions about a second guide pulley 5.2, on which a compensating means clamping device in the form of a tension weight 8 is suspended, and is attached at its other end to the underside of the second elevator car 2.
  • the suspension means suspension the elevator cars 1, 2 are suspended in a 1: 1 ratio, and the counterweight 3 is suspended in a 2: 1 ratio on the compensation means 5.
  • the second elevator car 2 is held on a floor by the second drive 7.2 blocks a rotation of the second traction sheave while at the same time the first drive 7.1 raises the first elevator car 1, simultaneously lowers the counterweight 3 by half the distance.
  • the compensation means 5 is drawn in by the lifting first elevator car 1 and in this case runs over the co-rotating first and third deflection rollers 5.1, 5.3.
  • Torque fluctuations of the first drive 7.1, adhesion-sliding transitions of the first elevator car 1, inertia and elasticity-induced tensile force fluctuations in the suspension means 4 and the like cause the first elevator car 1 to exert a non-uniform tensile force on the compensating means 5, due to the elastic suspension of the second Elevator car 2 on the elastic support means 4 to undesirable vibrations, in particular the stationary second elevator car 2 leads.
  • a second braking device in the form of a hydraulically adjustable roller damper 6.2 is provided, which is connected via a pinion with the second guide roller 5.2 and driven by the guide pulley 5.2 hydraulic pump and actuatable by an elevator control valve includes (not shown). Is the second elevator car 2, the valve of the hydraulically adjustable roller damper 6.2 is partially closed. The thus induced flow resistance of the circulated by the hydraulic pump in a hydraulic circuit oil causes a dissipative braking torque to the second guide roller 5.2, which counteracts their rotation. This braking torque is proportional to the speed and thus attenuates vibrations transmitted by the compensating means 5 running over the second deflection roller 5.2.
  • the damping coefficient can be advantageously adapted to different environmental conditions, for example, different weights of the elevator cars, the compensation means or the like.
  • the elevator control system lifts the second brake device 6.2 by completely opening the valve.
  • the flow resistance and thus acting on the second pulley 5.2 brake torque is greatly reduced, so that only little energy is dissipated while driving.
  • the first deflection roller 5.1 is connected to a first brake device 6.1, which is formed analogously to the second brake device 6.2 described above.
  • the free running with the tension weight 8 second braking device 6.2 is designed as a mechanical centrifugal brake, automatically, ie without external power supply or actuation, with increasing rotational speed of the second guide pulley 5.2 growing, the rotation counteracting braking torque on the second pulley 5.2 exerts.
  • the first braking device 6.1 which interacts with the inertially mounted in the hoistway 9 first guide pulley 5.1 and therefore easy to power with external energy and is controlled by the elevator control is designed as a controllable brake, the at least 1 closed grinding when the first elevator car 1, in traversing first elevator car 1 is ventilated, and so dissipative vibrations of the compensation means 5 attenuates the standing first elevator car 1.
  • the counterweight 3 travels both when the first and the second elevator car are moving and when the first and second elevator car are stationary. Therefore, with the arranged at the bottom of the counterweight 3 third guide pulley 5.3, a third braking device 6.3 is connected in the form of a vibration absorber.
  • a damping mass via a rotary spring-damper assembly (not shown) with the third guide roller 5.3 is connected.
  • the spring or damper constant and the Tilger loftmasse are tuned so that vibrations occurring during operation in the compensation means 5 are preferably damped.
  • this vibration damper dissipates no energy with uniform, vibration-free running and attenuates occurring on the other side vibrations in the compensation means 5 without external power supply or actuation.
  • Autonomous or controllable or brake devices can be arranged on one or more deflection rollers over which the compensating means 5 runs, which can apply a preferably speed-dependent and / or adjustable braking torque to the respective deflection roller so as to damp vibrations in the compensation means.
  • Different or identical brake devices can be provided at different pulleys, which are preferably individually controlled, in particular llite- or closable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Cage And Drive Apparatuses For Elevators (AREA)
  • Elevator Control (AREA)
  • Lift-Guide Devices, And Elevator Ropes And Cables (AREA)

Abstract

L'invention concerne un ascenseur qui comprend une première cabine d'ascenseur, une deuxième cabine d'ascenseur et un contrepoids, le contrepoids, la première et la deuxième cabine d'ascenseur étant accouplés les uns aux autres par l'intermédiaire d'un moyen de support pour le relèvement et la retenue. Le contrepoids, la première et la deuxième cabine d'ascenseur sont en outre accouplés les uns aux autres par l'intermédiaire d'un moyen de compensation, le moyen de compensation passant sur au moins un galet de renvoi. L'ascenseur comprend en outre un système de freinage qui exerce sur le galet de renvoi un couple de rotation de freinage dissipatif qui s'oppose à sa rotation.
EP08865484A 2007-12-21 2008-12-10 Ascenseur doté de deux cabines d'ascenseur et d'un contrepoids commun Withdrawn EP2229333A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08865484A EP2229333A1 (fr) 2007-12-21 2008-12-10 Ascenseur doté de deux cabines d'ascenseur et d'un contrepoids commun

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP07123998 2007-12-21
EP08865484A EP2229333A1 (fr) 2007-12-21 2008-12-10 Ascenseur doté de deux cabines d'ascenseur et d'un contrepoids commun
PCT/EP2008/067178 WO2009080503A1 (fr) 2007-12-21 2008-12-10 Ascenseur doté de deux cabines d'ascenseur et d'un contrepoids commun

Publications (1)

Publication Number Publication Date
EP2229333A1 true EP2229333A1 (fr) 2010-09-22

Family

ID=39433851

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08865484A Withdrawn EP2229333A1 (fr) 2007-12-21 2008-12-10 Ascenseur doté de deux cabines d'ascenseur et d'un contrepoids commun

Country Status (7)

Country Link
US (1) US20110017552A1 (fr)
EP (1) EP2229333A1 (fr)
CN (1) CN101903279B (fr)
AU (1) AU2008340488A1 (fr)
BR (1) BRPI0821212A2 (fr)
TW (1) TW200936485A (fr)
WO (1) WO2009080503A1 (fr)

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US8430210B2 (en) * 2011-01-19 2013-04-30 Smart Lifts, Llc System having multiple cabs in an elevator shaft
EP2670695B1 (fr) 2011-02-04 2022-09-07 Otis Elevator Company Système permettant de séquencer l'arrêt d'un dispositif de freinage
KR20140020998A (ko) * 2011-04-06 2014-02-19 오티스 엘리베이터 컴파니 4:1 로핑 구성부를 포함하는 엘리베이터 시스템
JP5808189B2 (ja) * 2011-08-04 2015-11-10 日本ケーブル株式会社 索条牽引式輸送設備
EP2711324B1 (fr) * 2012-09-20 2019-03-20 KONE Corporation Ensemble d'ascenseur et procédé
FI125336B (fi) * 2012-10-31 2015-08-31 Kone Corp Hissijärjestely
RU2518458C1 (ru) * 2012-12-27 2014-06-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Национальный минерально-сырьевой университет "Горный" Пассажирский лифт для многоэтажных зданий
AU2014211373B2 (en) * 2013-02-04 2017-04-27 Inventio Ag Compensation element with blocking device
FI125200B (fi) * 2013-07-04 2015-06-30 Kone Oyj Järjestely kuormituksen muutoksen aiheuttaman hissikorin siirtymän pienentämiseksi
DE102014105003A1 (de) * 2014-04-08 2015-10-08 Thyssenkrupp Elevator Ag Aufzugsystem
CN104860175B (zh) * 2015-05-19 2018-01-12 上海德圣米高电梯有限公司 一种双主机同步驱动电梯
CN104860174B (zh) * 2015-05-19 2018-01-12 上海德圣米高电梯有限公司 一种四主机同步驱动电梯
CN109156063A (zh) * 2015-08-27 2019-01-04 沙特基础工业全球技术公司 具有电致发光量子点的设备
CN108466904A (zh) * 2018-06-12 2018-08-31 叶荣伟 一种节能型共用对重电梯系统

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Also Published As

Publication number Publication date
WO2009080503A1 (fr) 2009-07-02
TW200936485A (en) 2009-09-01
AU2008340488A1 (en) 2009-07-02
CN101903279A (zh) 2010-12-01
US20110017552A1 (en) 2011-01-27
BRPI0821212A2 (pt) 2015-06-16
CN101903279B (zh) 2012-12-26

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