EP1431225B1 - Ascenseur à entrainement hydraulique - Google Patents

Ascenseur à entrainement hydraulique Download PDF

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Publication number
EP1431225B1
EP1431225B1 EP03028882A EP03028882A EP1431225B1 EP 1431225 B1 EP1431225 B1 EP 1431225B1 EP 03028882 A EP03028882 A EP 03028882A EP 03028882 A EP03028882 A EP 03028882A EP 1431225 B1 EP1431225 B1 EP 1431225B1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
drive
lift
elevator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03028882A
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German (de)
English (en)
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EP1431225A1 (fr
Inventor
Sebode Georg
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.)
Hydro Space GmbH
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Individual
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Publication date
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Publication of EP1431225A1 publication Critical patent/EP1431225A1/fr
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Anticipated expiration legal-status Critical
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B1/00—Control systems of elevators in general
    • B66B1/24—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration

Definitions

  • the invention relates to a lift with a hydraulic drive, measuring signal pickups for detecting system states and at least one electronically controllable valve with a controller having a device for returning at least the measurement signals of the hydraulic pressure and the valve piston position.
  • Hydraulic lifts are known in different configurations.
  • DE 36 29 032 A1 describes a hoist which uses a hydraulic motor to drive a flexible drive means different from the carrying cable of the elevator and thus to move the elevator. Both hydraulic cylinders and hydraulic rotary motors are used as hydraulic drive.
  • Hydraulic lifts sometimes use hydraulic control valves.
  • a system size is measured and fed to a controller, which calculates possible disturbances and compensates the hydraulic flow by changing the hydraulic valve position to compensate for the disturbances.
  • a regulation as a function of the elevator position is realized.
  • an electrohydraulic control valve which controls the flow rate and / or pressure to a hydraulic load as a function of the detected valve position, the detected pressures and other measured states and a control signal.
  • an integrated control circuit By an integrated control circuit, a fast and accurate control of the fluid is achieved.
  • the second 2/2-way valve the down valve
  • the down valve is fully opened and hydraulic fluid is released from the cylinder, resulting in the downward movement.
  • this arrangement is disadvantageous.
  • the oil temperature and other system parameters also have an influence on the system behavior. As a result, for example, stops can not approach exactly. Due to the long dead time of the system and the generally poor controllability oscillations occur in the oil column, which must be damped by very complex control and regulation techniques.
  • the invention has the object to improve a hydraulic elevator of this type.
  • the valve delivers exactly the hydraulic flow that is necessary to achieve a specific target-driving behavior.
  • a change of pressure in the pressure supply can be compensated automatically.
  • the same applies to a change of the load state which can be compensated so directly on the valve and not by a long dead time afflicted feedback, such as a position signal, the elevator car must be considered in the controller. It is such a quick precise control of the hydraulic volume flow directly on the valve possible, resulting in a significant improvement in the overall system behavior.
  • Plant data and any operating parameters can thus already be taken into account in the regulator of the valve and are easily modifiable in order to take into account, for example, aging phenomena of the components.
  • a preferred embodiment of the invention is characterized in that the drive is designed as a hydraulic rotary motor or as a hydraulic linear drive. Depending on the application, one of the two embodiments of the drive can be advantageous. Thus, rotary engines at high delivery and high speed of the elevator make sense. A hydraulic linear drive is able to handle particularly high loads move, with both the maximum head and the maximum travel speed are limited.
  • a preferred embodiment of the invention is characterized in that in each case a 3/3-way valve is provided for the inlet and the outlet of the hydraulic rotary motor.
  • a 3/3-way valve is provided for the inlet and the outlet of the hydraulic rotary motor.
  • the use of a separate valve for both connections of the drive offers a number of advantages over the conventional design with a combined inlet and outlet valve.
  • any leakage in the drive can be fully compensated.
  • On a change in the load state which in a four-quadrant operation of the elevator causes the motor depending on the direction and load state once used as a drive and once as a brake, so can react very quickly and gently.
  • the drive is preferably equipped with a mechanical holding device, in particular a brake or a holding valve.
  • the at least one control valve is provided spatially directly on the drive, possibly in Flanschbauweise.
  • Such attachment to the drive possible with particularly rigid connections ensures that no vibrations can occur in this part of the hydraulic circuit.
  • the pressure medium flows set by the control valve directly reach the drive, without vibrations being able to form in long supply lines which impair the stability of the overall system. Overall, the control properties are thereby significantly improved.
  • a further embodiment of the invention is characterized in that the drive is arranged in the shaft head or shaft bottom.
  • the drive is arranged in the shaft head or shaft bottom.
  • An embodiment of the invention is characterized in that the counterweight has the same mass as the elevator plus its half maximum load.
  • a weighted counterweight is a four-quadrant operation of the elevator possible.
  • the motor is used both as a drive and as a brake depending on the load of the elevator car. Overall, such an interpretation of the elevator system has the advantage that the drive can be built very small and the system has good energy efficiency.
  • measuring signal pickups are provided for detecting hydraulic fluid temperature and / or elevator position and / or optionally further system states.
  • a constant speed and accurate positioning of the elevator can be achieved at the breakpoints.
  • the system security is increased because pressure medium leaks or other emergency conditions can be detected and compensated if possible.
  • the controller has in this case cascade structure, in which the regulation of valve piston position and hydraulic pressure in the inner control loop occurs and occurring control errors are compensated on the basis of further measured system conditions in an outer slow control loop to ensure, for example, an accurate entrance to the stops.
  • cascade-like control structure can be vibrations due to the low Effectively prevent damping and long dead time of such a hydraulic elevator system and still achieve a high dynamic and stationary control accuracy.
  • the valve has a device for compensating the hydraulic fluid temperature.
  • the integration of automatic temperature compensation into the valve simplifies the system design and improves the system's behavior, as the different viscosities of the hydraulic fluid due to temperature changes are immediately taken into account and no longer have negative effects on system performance. So a trouble-free operation of the elevator is guaranteed at low as well as high stress.
  • At least one electronic processor unit is provided with the regulator and / or for controlling the valve and / or the holding device.
  • the use of electronic processor units for example in the form of plug-in cards or other such components, allows precise control of the elevator in all operating areas. The connection to higher-level system controls is easily possible. By adapting the operating programs, wide ranges of systems and system configurations can be covered and quickly adapted to changing circumstances.
  • the invention also relates to a method for controlling a hydraulically driven elevator.
  • An advantageous development of the method is characterized in that the measurement signals are recorded by other system states, in particular the elevator position, the controller thus determines a control error by comparing the actual state with the desired state of the elevator and with the valve of this control error Adjustment of the hydraulic flow to achieve the desired state compensated.
  • a generally designated 1 elevator consists of an elevator car 2, which is connected via a flexible support cable 3 with a counterweight 4.
  • the weight 4 is guided vertically displaceable in existing in the elevator shaft rails 5.
  • the elevator car 2 is slidably mounted in guide rails 6.
  • a flat belt with steel wire inserts can be used.
  • the flexible support cable 3 is guided over a plurality of deflection rollers 7 and fastened with its two ends in the shaft head. Between elevator car and counterweight it runs via the traction sheave 8, which is driven by a hydraulic rotary motor 9.
  • the drive 9 is an electronic valve 10, which is connected via two rigid lines 11 to the drive motor 9.
  • a pressure medium supply 12, which provides both the high and the low pressure for the operation of the engine is connected via leads 13 to the control valve.
  • FIG. 1 An alternative embodiment with a hydraulic linear drive is shown in more detail in FIG.
  • the elevator car 2 is slidably mounted again in guide rails 6 and vertically displaced by a plunger hydraulic cylinder 9a.
  • the hydraulic valve 10 is arranged in spatial proximity to the pressure medium supply 12 and connected via a single pressure medium line 11a to the hydraulic cylinder 9a.
  • valve 10 is driven by a valve processor 26, which receives its control signals from a system processor 27.
  • a higher-level system controller 28 coordinates the overall control of the system.
  • a hydraulic linear drive 9a is used to drive the elevator.
  • the hydraulic supply 12 consists of a hydraulic reservoir 14 and a load-sensing pump 16, which is driven by a motor 15 and provides the operating pressure of the system at the high-pressure connection 17.
  • a working pressure limiting valve 18 ensures that the operating pressure of the system available at the connection 17 is kept constant.
  • a maximum pressure limiting valve 19 is still available, which protects the system against dangerous overpressure conditions.
  • the returning oil is returned from the low pressure port 20 in the hydraulic reservoir 14.
  • the electronically controllable valve 10 is in its simple design for a linear drive from a 3/3-way valve 21, which is adjusted via an electronically controllable 4/3-way pilot valve 22.
  • a Wegmesssensor 23 for measuring the control piston position.
  • a pressure sensor 24 for measuring the drive-side pressure and a temperature measuring member 25 for determining the hydraulic fluid temperature is present.
  • the measuring signals of the sensors are directed into a valve processor 26 which contains the regulator and to whose control output the electrical control input 27 of the pilot valve 22 is connected.
  • the setpoint sizes for the piston position and the various system pressures are specified by the system processor 27, which calculates the necessary control variables in dependence on user preferences and by the system controller 28 not shown here, and transfers the necessary control variables to the valve processor 26.
  • the valve processor 26 calculates a manipulated variable for the pilot valve 22, which is set by the electric valve processor 27.
  • the control piston is moved in the main valve 21 and its position is measured by the distance measuring sensor 23.
  • a closed-loop control of the control piston can be achieved.
  • the hydraulic pressure can also be controlled to the desired target value.
  • the manifold occurring disturbances are compensated by a superimposed position control of the elevator.
  • a displacement sensor 34a on the elevator which receives its position in the shaft.
  • the actual position is compared with the desired position and corresponding control errors by changing the desired values balanced on the valve processor 26. This allows an accurate positioning of the linear drive and thus reach the elevator car.
  • a pilot-operated check valve 29 is provided, which can be actuated by an electrically operated control valve 30. Furthermore, a stopcock 31 for maintenance and the like. Is provided.
  • a hydraulically actuated brake 32 is provided for holding the elevator at a certain position on the drive roller 8, which is operated by an electrically operated control valve 33.
  • the brake is used to protect the elevator from falling in case of faults in the drive and is also used to hold the elevator at a standstill.
  • the structure of the hydraulic circuit is similar to that shown in Fig. 3.
  • two main control valves 21a and 21b are provided, which are each controlled by a separate electronically actuated pilot valve 22a and 22b.
  • the Wegmesssensoren 23a and 23b, the pressure measuring sensors 24a and 24b and the temperature measuring elements 25a and 25b are also for each of the two control valves 21a and 21b available.
  • the valves are connected on the input side to the high-pressure connection 20 and to the low-pressure connection 17 of the hydraulic supply 12.
  • the control valves 21a and 21b are coupled to the hydraulic motor 9 via two shut-off valves 31a and 31b by means of two short rigid pipes 11.
  • a valve 21a is connected to the inlet and a valve to the outlet of the hydraulic motor 9.
  • the measurement signals of the sensors in the hydraulic circuit are again supplied to the valve processor 26, which calculates therefrom the control variables for the control inputs 27a and 27b of the pilot valves 22a and 22b as a function of the measured variables.
  • the system processor 27 calculates analogous to above depending on other system sizes, the necessary hydraulic flows to and from the engine 9.
  • the hydraulic motor 9 additionally has a sensor 34, the signal from the system computer 27 to control the elevator position and Speed is used.

Landscapes

  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Types And Forms Of Lifts (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Elevator Control (AREA)
  • Actuator (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (12)

  1. Ascenseur avec un entraînement hydraulique, des capteurs de signaux de mesure (23-25) pour détecter des états du système et au moins une électrovanne (10) avec un régulateur (26, 22) qui présente un dispositif pour renvoyer au moins les signaux de mesure de la pression hydraulique et de la position du piston de la vanne,
    caractérisé en ce que l'électrovanne (10) présente au moins une vanne 3/3 voies (21, 21a) pour commander l'entraînement.
  2. Ascenseur selon la revendication 1,
    caractérisé en ce que l'entraînement est formé comme un moteur à cylindres rotatifs hydraulique (9) ou comme un entraînement linéaire hydraulique (9a).
  3. Ascenseur selon la revendication 2,
    caractérisé en ce qu'une vanne 3/3 voies (21, 21a) est prévue respectivement pour l'admission et la sortie du moteur à cylindres rotatifs hydraulique (9).
  4. Ascenseur selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que l'entraînement est muni d'un dispositif d'arrêt mécanique, en particulier d'un frein (8) ou d'une vanne d'arrêt (29).
  5. Ascenseur selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'au moins une vanne (10) est prévue au niveau spatial directement sur l'entraînement (9, 9a), le cas échéant en montage en bride.
  6. Ascenseur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que l'entraînement (9, 9a) est placé dans la tête de la cage ou au fond de la cage.
  7. Ascenseur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le contre-poids (4) présente la même masse que l'ascenseur (2) plus la moitié de sa charge maximale.
  8. Ascenseur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que des capteurs de signaux de mesure (23, 24, 25, 34, 34a) sont prévus pour détecter la température du fluide hydraulique et/ou la position de l'ascenseur et/ou le cas échéant d'autres états du système.
  9. Ascenseur selon l'une quelconque des revendications précédentes,
    caractérisé en ce que la vanne (10) présente un dispositif de compensation de la température du fluide hydraulique.
  10. Ascenseur selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'au moins une unité de processeur électronique est prévue avec le régulateur et/ou pour commander la vanne et/ou le dispositif d'arrêt (26, 27, 28).
  11. Procédé de commande d'un ascenseur à entraînement hydraulique selon la revendication 1 ou l'une quelconque des revendications suivantes,
    caractérisé en ce que les signaux de mesure de la pression hydraulique et de la position du piston de la vanne sont enregistrés dans et/ou sur l'électrovanne (10) et qu'ainsi le régulateur commande la vanne, de manière à ce qu'un écoulement hydraulique nécessaire pour obtenir un état du système de consigne de l'ascenseur (2) se règle.
  12. Procédé selon la revendication 11,
    caractérisé en ce que les signaux de mesure d'autres états du système, en particulier de la position de l'ascenseur, sont enregistrés, le régulateur définissant avec cela une erreur de réglage en comparant l'état réel à l'état de consigne de l'ascenseur et compensant avec la vanne (10) cette erreur de réglage en adaptant l'écoulement hydraulique pour obtenir l'état de consigne.
EP03028882A 2002-12-18 2003-12-16 Ascenseur à entrainement hydraulique Expired - Lifetime EP1431225B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10259146 2002-12-18
DE10259146A DE10259146A1 (de) 2002-12-18 2002-12-18 Aufzug mit einem hydraulischen Antrieb

Publications (2)

Publication Number Publication Date
EP1431225A1 EP1431225A1 (fr) 2004-06-23
EP1431225B1 true EP1431225B1 (fr) 2007-02-14

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ID=32336428

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03028882A Expired - Lifetime EP1431225B1 (fr) 2002-12-18 2003-12-16 Ascenseur à entrainement hydraulique

Country Status (3)

Country Link
EP (1) EP1431225B1 (fr)
AT (1) ATE353847T1 (fr)
DE (2) DE10259146A1 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2646294C2 (de) * 1976-10-14 1987-02-26 C. Haushahn GmbH & Co, 7000 Stuttgart Hydraulische Antriebsvorrichtung für einen Aufzug
DE2658928A1 (de) * 1976-12-24 1978-07-06 Beringer Hydraulik Gmbh Hydraulische steuerung
DE3629032C2 (de) * 1986-08-27 1994-02-03 Haushahn C Gmbh Co Hebezeug, insbesondere Aufzug
GB9503854D0 (en) * 1995-02-25 1995-04-19 Ultra Hydraulics Ltd Electrohydraulic proportional control valve assemblies

Also Published As

Publication number Publication date
EP1431225A1 (fr) 2004-06-23
DE10259146A1 (de) 2004-07-15
ATE353847T1 (de) 2007-03-15
DE50306487D1 (de) 2007-03-29

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