EP1222416B1 - Unite soupape de commande pour un ascenseur hydraulique - Google Patents

Unite soupape de commande pour un ascenseur hydraulique Download PDF

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Publication number
EP1222416B1
EP1222416B1 EP01962699A EP01962699A EP1222416B1 EP 1222416 B1 EP1222416 B1 EP 1222416B1 EP 01962699 A EP01962699 A EP 01962699A EP 01962699 A EP01962699 A EP 01962699A EP 1222416 B1 EP1222416 B1 EP 1222416B1
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EP
European Patent Office
Prior art keywords
control valve
control
valve
throttle body
valve unit
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
EP01962699A
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German (de)
English (en)
Other versions
EP1222416A2 (fr
Inventor
Sead Veletovac
Luigi Del Re
Andreas Schrempf
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.)
Wittur AG
Original Assignee
Wittur AG
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Filing date
Publication date
Priority claimed from CH01312/00A external-priority patent/CH694763A5/de
Application filed by Wittur AG filed Critical Wittur AG
Publication of EP1222416A2 publication Critical patent/EP1222416A2/fr
Application granted granted Critical
Publication of EP1222416B1 publication Critical patent/EP1222416B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • 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
    • 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
    • B66B9/04—Kinds or types of lifts in, or associated with, buildings or other structures actuated pneumatically or hydraulically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/008—Throttling member profiles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/26—Power control functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8613—Control during or prevention of abnormal conditions the abnormal condition being oscillations

Definitions

  • the invention relates to a control valve unit for a hydraulic elevator according to the preamble of claim 1.
  • Such control valve units are used for influencing the flow of hydraulic oil between a pump or a tank and a drive cylinder for the direct or indirect drive of an elevator car.
  • a control valve unit referred to in the preamble of claim 1 is known from US-A-5,040,639. It includes three pilot operated control valves and a non-return valve in which the position of the opening is monitored with a position transmitter. In addition to fixed chokes also some adjustment elements are available.
  • a control valve unit for a hydraulic elevator for controlling the upward travel has a control valve in the main flow of hydraulic fluid between the pump and the elevator cylinder and a bypass valve between supply line and return line.
  • the control valve is designed as a spring-loaded check valve.
  • the bypass valve is moved by a piston and hydraulically controls the opening of the control valve.
  • the flow rate of the bypass valve can be adjusted to the operating conditions with a setting device.
  • a control of the downward drive make further modules necessary.
  • US-A-4,153,074 discloses a control valve unit for controlling an elevator in which there is a pilot-operated control valve each for controlling the upward and downward travel, each acting both as a check valve and as a proportional valve.
  • the invention has for its object to provide a control valve unit, which is simple and manages without adjustment. This results in lower production costs and time-consuming adjustments are not necessary during commissioning.
  • 1 denotes an elevator car of a hydraulic elevator which can be moved by a reciprocating piston 2.
  • the reciprocating piston 2 forms a known hydraulic drive together with a lifting cylinder 3.
  • a cylinder line 4 is connected to this hydraulic drive.
  • the cylinder line 4, is connected to a first control valve 5, which combines at least the functions of a proportional valve and a check valve, so that it behaves either as a proportional valve or as a check valve, which depends on how the control valve 5 is actuated, which will be discussed.
  • the proportional valve function can be achieved in a known manner with a main valve and a pilot valve, wherein the pilot valve is actuated by an electric drive, for example a proportional solenoid.
  • the closed check valve keeps the elevator car 1 in the respective position.
  • the control valve 5 is connected via a pump line 8, in which a pressure pulsation damper 9 can be arranged, with a pump 10, by means of the hydraulic oil from a tank 11 to the hydraulic drive can be conveyed.
  • the pump 10 is driven by an electric motor 12, which is associated with a power supply part 13.
  • P P In the pump line 8 there is a pressure P P.
  • a further hydraulic oil-carrying line namely a return line 14, in which a second control valve 15 is arranged.
  • This control valve 15 allows the almost resistance return of the hydraulic oil from the pump 10 into the tank 11 when the pressure P P has exceeded a certain threshold. As a result, the pressure P P can not significantly exceed the said threshold value. It is now the case that this threshold value can be changed by an electrical signal, so that the control valve 15 can assume a pressure regulating function in a manner similar to a known proportional valve. Also, to achieve this function can, as in a proportional valve, resort in a known manner to a main valve and a pilot valve, which is actuated by a proportioning magnet, which is electrically controlled.
  • a load pressure sensor 18 which is connected via a first measuring line 19 to a control unit 20.
  • the operation of the hydraulic elevator serving controller 20 is thus able to detect which pressure P Z prevails in the cylinder line 4.
  • This pressure P Z is at standstill elevator car 1, the load of the elevator car 1 again.
  • control and regulating operations can be influenced and operating conditions can be determined.
  • the controller 20 may also consist of several control and regulator units.
  • a temperature sensor 21 which is connected to the control unit 20 via a second measuring line 22, is arranged on the cylinder line 4, again preferably directly on the corresponding connection of the control valve 5 or on the control valve 5 itself. Because hydraulic oil has a viscosity that varies significantly with its temperature, the control and regulation of the hydraulic elevator can be significantly improved if the temperature of the hydraulic oil is included as a parameter in the control processes.
  • a first control line 25 leads to the control valve 5.
  • this control valve 5 from the control unit 20 is electrically controlled.
  • a second control line 26 leads to the control valve 15, so that it is controllable by the control unit 20 ago.
  • a third control line 27 leads from the control unit 20 to the power supply part 13, whereby the motor 12 can be switched on and off, but optionally also the speed of the motor 12 and thus the flow rate of the pump 10 from the controller 20 can be influenced.
  • control valves 5 and 15 By controlling the control valves 5 and 15 from the controller 20 ago it is determined how the control valves 5 and 15 behave functionally. If the control valves 5 and 15 are not actuated by the control unit 20, both control valves 5 and 15 basically behave like a differently biasable check valve. If the control valves 5 and 15 are actuated by the control unit 20 by a control signal, they act as proportional valves.
  • the two control valves 5 and 15 are combined in a control valve unit 28, which is indicated in the figure by a dashed line comprising the two control valves 5 and 15.
  • a control valve unit 28 which is indicated in the figure by a dashed line comprising the two control valves 5 and 15.
  • This has the advantage that the assembly work on the construction site of the hydraulic elevator is reduced.
  • the two control valves 5 and 15 are similar and constructed using the same parts, which has various advantages, which will be discussed.
  • the electrically non-controlled control valve 5 closes automatically by the action of the pressure P Z , which generates the elevator car 1, when this pressure P Z is greater than the pressure P P. It has already been mentioned that in this state the load pressure sensor 18 indicates the load caused by the elevator car 1. In this case, the effective load of the elevator car 1 is determined and transmitted to the control unit 20. The controller 20 can thus detect whether the elevator car 1 is empty or loaded and the size of the load is thus known.
  • the power supply part 13 is first activated by the control unit 20 via the control line 27, and thus the electric motor 12 is rotated, whereby the pump 10 starts to run and pumps hydraulic oil.
  • the pressure P P in the pump line 8 increases.
  • this pressure P P exceeds a value correlated with the bias of the check valve of the control valve 15
  • the check valve of the control valve 15 opens, so that the pressure P P can not initially exceed this value. If this pressure value, which is usually the case, is lower than the pressure P Z in the cylinder line 4, the control valve 5 remains closed and no hydraulic oil flows into the cylinder line 4.
  • the switching on of the pump 10 does not cause any movement of the elevator car 1, because the entire amount of hydraulic oil delivered by the pump 10 is in this case fed back into the tank 11 via the control valve 15.
  • the control unit 20 can now control the proportional valve function of the control valve 15 via the signal line 26, so that a greater hydraulic resistance is set on the control valve 15. This allows now to increase the pressure P P until the necessary amount of hydraulic oil can flow into the cylinder line 4 through the control valve 5. In this case, part of the flow of hydraulic oil conveyed by the pump 10 flows back into the tank 11 via the control valve 15.
  • the pump 10 need only be designed so that it can supply a sufficient for the maximum speed of the elevator car 1 flow of hydraulic oil at the maximum expected back pressure at the rated speed, taking into account the usual reserve factors and other margins.
  • FIGS. 2 to 4 A first embodiment of the control valve unit 28 according to the invention is shown in FIGS. 2 to 4.
  • FIG. 2 shows a basic state without any activation of the control valves 5 and 15 contained in the control valve unit 28.
  • FIG. 3 shows a state during the upward travel of the elevator car 1 (FIG. 1), while FIG. 4 shows the state during the downward travel.
  • FIGS. 2 to 4 show the control valve unit 28, which represents a combination of the control valves 5 and 15.
  • the upper part represents the control valve 5
  • the lower part the control valve 15.
  • [4] shows the connection of the control valve unit 28 to the cylinder line 4 (FIG. 1)
  • [8] the connection to the pump line 8
  • [14] the connection to the return line 14.
  • the prevailing pressures P Z and P P are drawn there, which have been mentioned in the description above and which can be detected with the pressure sensors not shown here.
  • Each of the control valves 5 and 15 consists of a main valve and a pilot valve, which in turn is each actuated by a proportional solenoid.
  • the control valve unit 28 consists of two housing parts, namely a first housing part 30, which includes the main valves of the control valves 5 and 15, and a second housing part 31, in which the associated pilot valves are located, which are designated 5 V and 15 V.
  • the housing part 31 itself may be in two parts, by each of the pilot valves 5 V and 15 V has its own housing part.
  • Each of the pilot valves 5 V and 15 V is assigned a proportional solenoid, namely the pilot valve 5 V, the proportional solenoid 5 M and the pilot valve 15 V, the proportional solenoid 15 M.
  • These proportional solenoids 5 M and 15 M can be actuated by the control unit 20 (FIG. 1) via the control lines 25 and 26, respectively.
  • the first housing part 30 contains a plurality of chambers.
  • a first chamber is referred to as a cylinder chamber 32. This is followed by the cylinder line 4 (FIG. 1), which is why the corresponding connection is designated [4].
  • a second chamber is referred to as a pump chamber 33 to which the pump line 8 connects, which is represented by the reference numeral [8].
  • Another chamber is referred to as return chamber 34, to which the return line 14 connects, which is designated by the reference numeral [14].
  • a first throttle body 35 is arranged, which forms the main valve of the control valve 5 together with a first valve seat 36 formed in the housing part 30.
  • this main valve of the control valve 5 is the essential element which directly influences the flow of hydraulic oil from and to the lifting cylinder 3 ( Figure 1).
  • the main valve of the control valve 5 includes the function of a check valve and at the same time the function of a proportional valve, which will be explained below.
  • the check valve fulfills the requirements set out in EN safety standards, so that an additional safety valve is not required.
  • the throttle body 35 is on the one hand actuated by a return spring 37.
  • the return spring 37 By this return spring 37, the main valve is kept closed as long as the pressure P P in the pump chamber 33 is not greater than the pressure P Z in the cylinder chamber 32. This is the case, for example the pump 10 ( Figure 1) is not running and the elevator car 1 ( Figure 1) is stationary.
  • actuators act, which are moved by the control of the pilot valve 5 V.
  • These adjusting elements comprise an opposed piston 38 with an actuating rod 39 fastened thereto.
  • the counter-piston 38 is displaceable in a guide space 40, which is arranged in the housing part 30.
  • the counter-piston 38 in turn is actuated by the pilot valve 5 V and that as follows. From the proportional solenoid 5 M is acted in a known manner via a plunger plunger 41 against a pilot control spring 42 to a pilot piston 43. From the movement of the pilot piston 43 follows the structure of a control pressure P X in a control pressure chamber 44.
  • This control pressure P X depends on the movement of the pilot piston 43 and is thus determined by the pilot control spring 42. Characterized in that the pilot valve 5 V detects the pressure P Z in the cylinder chamber 32 via a first connecting channel 45 and also detects the pressure prevailing in the return chamber 34 via a second connecting channel 46, no adjusting elements are required to the correct control pressure P X to reach.
  • the pilot valve 5 V controls the control pressure P X , wherein the control pressure P X is a function of the pressures in cylinder chamber 32 and return chamber 34 and the stroke of the pilot piston 43, which in turn is determined by the control of the pilot valve 5 V.
  • control pressure P X is acted on a displaceable in a control chamber 47 piston 48.
  • the piston 48 is supported via a main valve control spring 49 against the housing part 30.
  • the movement of the piston 48 is transmitted by means of a control rod 50 to the counter-piston 38.
  • the main valve control spring 49 thus acts on the one hand as a return spring for the piston 48, on the other hand just as a control spring for the main valve of the control valve 5. Again, according to the invention no adjustment is required.
  • the second control valve 15 is designed.
  • a second throttle body 55 is arranged, which forms the main valve of the control valve 15 together with a second valve seat 56 formed in the housing part 30.
  • This main valve of the control valve 15 also includes the function of a check valve and at the same time the function of a proportional valve, which will be explained below.
  • the throttle body 55 is on the one hand actuated by a return spring 57.
  • the return spring 57 By this return spring 57, the main valve is kept closed as long as the pressure P P in the pump chamber 33 is not greater than the pressure in the return chamber 34. This is the case, for example, when the pump 10 ( Figure 1) is not running.
  • actuators act, which are moved by the control of the pilot valve 15 V.
  • the throttle body 55 is actuated by the pilot valve 15 V , namely as follows. From the proportional solenoid 15 M is acted in a known manner via a plunger tang 61 against a pilot control spring 62 to a pilot piston 63. From the movement of the pilot piston 63 follows the structure of a control pressure P Y in a control pressure chamber 64. This control pressure P Y depends on the movement of the pilot piston 63 and is thus determined by the pilot control spring 62.
  • the pilot valve 15 V controls the control pressure P Y
  • the control pressure P Y is a function of the pressures in the pump chamber 33 and return chamber 34 and the stroke of the pilot piston 63, which in turn is determined by the control of the pilot valve 15 V.
  • the control pressure P Y is acted on a displaceable in a control chamber 67 piston 68.
  • the piston 68 is supported via a main valve control spring 69 against the housing part 30.
  • the movement of the piston 68 is transmitted to the throttle body 55 by means of a control rod 70.
  • the main valve control spring 69 thus acts on the one hand as a return spring for the piston 68, on the other hand just as a control spring for the main valve of the control valve 15. Again, no adjustment elements are required according to the invention.
  • the proportional valve function of the control valve 15 is activated. This is done by driving the proportional solenoid 15 M via the control line 26.
  • the control valve 15 has a counter-body 58 and an actuating rod 59.
  • the control valve 15 in which the adjusting rod 39 is fixedly mounted on the counter-piston 38, while the throttle body 35 is a separate part form the control valve 15 counter-body 58, control rod 59 and throttle body 55 a single part.
  • the counter body 58 is then, when the control valve 15 is closed, in a recess 60 in the first housing part 30.
  • the diameter of the recess 60 may be significantly larger than the diameter of the counter body 58.
  • the counter body 58 has regard Force effect has no effect on the formed from the throttle body 55 and the valve seat 56 main valve of the control valve 15.
  • Advantageously 60 guide ribs can be arranged in the recess, with which the counter body 58 is guided.
  • the mating bodies 38 and 58 have the following different meanings.
  • the pressure in the pump chamber 33 acts in the same manner as on the throttle body 35 and 55. If now advantageously the diameter of the counter-body 38 and 58 are equal to the diameter of the throttle body 35 and 55, this causes a force balance.
  • the first control valve 5 in which the throttle body 35 on the one hand and counter body 38 with control rod 39 on the other hand are separate parts acts on the counter body 38, the same caused by the pressure P P force as on the throttle body 35.
  • the force applied by the pilot valve 5 M. must to move the piston 48 and the control rod 50 against the opposed piston 38 and the throttle body 35, so is not changed by differential forces.
  • the rigid connection of the counter-piston 58 with the throttle body 55 is necessary because here the counter-piston 58 is on the pilot valve 15 M side facing away from the main valve, so that the power is not transmitted via the opposed piston 58. Because the diameter of the recess 60 is significantly larger than the diameter of the counter-piston 58, the pressure P P acts on all sides in the case of the counter-piston 58, ie it does not develop any counterforce on the throttle body 55.
  • FIG. 4 shows a position of the control valve unit 28 when the pull-out booth 1 is moved downwards (FIG. 1).
  • the pump 10 Figure 1 will not run. Accordingly, the pressure P P is small.
  • the main valve of the control valve 5 formed from throttle body 35 and seat 36 is closed.
  • the proportional solenoid 5 M activated. This acts on the plunger rod 41 on the pilot valve 5 V , which builds up the control pressure P X in the control chamber 47.
  • the magnitude of the control pressure P X is determined by the control of the proportional solenoid 5 M and the pilot control spring 42 and is of course also influenced by the pressure P Z in the cylinder chamber 32 and the pressure in the return chamber 34.
  • the control pressure P X in the control pressure chamber 44 increases, as a result of which the piston 48 is moved against the force of the main valve control spring 49 in the direction of the counter-piston 38. In this case, this movement is transmitted via the control rod 50 to the counter-piston 38.
  • Whose movement is transmitted via the control rod 39 to the throttle body 35.
  • the main valve of the control valve 5 opens.
  • the main valve of the control valve 15 formed from throttle body 55 and valve seat 56 thus acts as a check valve when traveling downwards, which valve is opened solely by the pressure P P.
  • a control of the proportional solenoid 15 M thus does not take place and thus the pilot valve 15 V without function.
  • control valves 5 and 15 are required, each having the functions of non-return valve and proportional valve.
  • the check valve functions of the control valves 5 and 15 simultaneously meet the requirements of EN safety standards.
  • the control valve 5 fulfills the function of the safety valve, while the control valve 15 makes an additional pump pressure relief valve dispensable.
  • the inventive control valve unit 28 thus has a particularly simple structure and is inexpensive to produce. If the throttle body 35 and 55 are identical according to an advantageous embodiment of the invention, this also means an advantage in terms of manufacturing costs, because not different throttle body must be fabricated.
  • FIG. 5 shows the closing body 55 together with the counterbody 58 and the actuating rod 59 connecting these two parts.
  • the surface facing the truncated cone 55 has the shape of a truncated cone 80.
  • the surface of the truncated cone 80 forms an angle a of approximately 15 to 25 degrees against a surface perpendicular to the longitudinal axis. This ensures that at high flow rate through the main valve of the control valve 15 resulting dynamic forces have no adverse effects on the pilot valve 15 V.
  • FIG. 6 shows a counterbody 58 whose shape and size correspond to the counterbody 38 (FIG. 4).
  • the angle a is also present here.
  • the counter-body is again shown, which is usable as a counter-body 38 for the control valve 5 and as a counter-body 58 for the control valve 15, in turn, the angle á occurs.
  • the size of the recess 60 is in each case adapted to the size of the counter body 58.
  • the depth of the recess 60 is small.
  • the size of the counter body 58 is designed in accordance with FIG. 6, then the depth of the recess 60 is correspondingly greater, so that the counter body 58 fits into the recess 60 when the main valve of the second control valve 15 is closed.
  • FIGS. 8a to 8d Details of the throttle body 35, 55 are shown in FIGS. 8a to 8d, namely different variants of the embodiment.
  • a base 90 To a base 90 is followed in each case a cylinder 91, whose lateral surface is designated by the reference numeral 92.
  • openings 93 are milled through which the hydraulic oil can pass.
  • six uniformly distributed openings 93 are milled into the circumference of the cylinder 91.
  • the openings 93 may have different shapes.
  • the openings 93 in the part adjoining the base 90 are V-shaped and in the adjoining part of constant width.
  • the openings 93 are clearly stepped.
  • the opening 93 is V-shaped and then abruptly changes into a rectangular shape. This means that the effective passage cross section for the hydraulic oil initially increases slightly and then changes abruptly to a maximum value, in which case the passage cross section is independent of the further stroke.
  • FIG. 8d shows a further example in which the openings 93 are only stepped. In the first stroke range, the opening 93 has a small width and then goes abruptly into one
  • a further advantageous embodiment is to provide a stroke limitation.
  • Such a stroke limitation can advantageously be achieved by limiting the possible travel of the pistons 48 and 68 within the control chamber 47 and 67, respectively. Suitable variants are shown in FIGS. 9a and 9b.
  • FIG. 9a shows a detail from FIGS. 2 to 4, namely the control chamber 47 or 67 with the piston 48 or 68 displaceable in it.
  • Numerous annular grooves 95 are inserted into the cylindrical inner wall of the control chamber 47 or 67.
  • snap rings 96 can be used.
  • a snap ring 96 is inserted into one of the annular grooves 95.
  • FIG. 9b An advantageous variant of the stroke limitation is shown in FIG. 9b.
  • the production-technically problematic annular grooves 95 (FIG. 9a) are not necessary.
  • a spacer ring 97 is inserted into the control chamber 47 and 67, respectively. Its outer diameter is slightly smaller than the diameter of the control chamber 47 and 67, respectively.
  • the length of the cylindrical spacer determines the stroke limit.
  • FIG. 10 shows a detail of the pistons 48, 68. They have on their outer periphery a groove 98 in which an annular elastic seal 99 is inserted.
  • an annular elastic seal 99 is inserted.
  • the seal 99 advantageously fulfills the task of reducing the leakage, because by it the leakage flow of hydraulic oil from the control chamber 47, 67 in the direction of the main valve of the control valves 5, 15 is decisively reduced.
  • FIG. 11 shows the lateral surface of a throttle body 35 (FIG. 2).
  • the opening 93 of Figure 11 begins at a distance d from the base 90 ( Figure 8a-d), while another opening 93 'begins at a distance d' and another opening 93 "at a distance d".
  • the smallest distance d is, for example, 1 mm.
  • valve-dependent flow characteristic is arbitrarily fixed, so as to make the flow characteristics optimally adaptable to the needs.
  • openings 93 are shown in FIGS. 12a and 12b.
  • an opening 93 is shown, the root 93 w of which, analogous to FIG. 11, begins at a specific distance from the base 90.
  • the depth of such opening, as well as the width, advantageously follows a design rule characterized in that the effective area A of the opening 93 is a function of a distance y from the root 93w.
  • k is a proportionality factor
  • FIG. 12b shows a section to FIG. 12a at a distance y from the root 93w.
  • all openings 93 begin with their root 93w (FIG. 12a) at the same distance from the base 90, but it is also conceivable that this solution would be co-ordinated with that of FIG 12b is indicated by the fact that one of the openings is deeper with a dashed line, because its root 93w begins at a smaller distance from the base 90.
  • FIG. 13 shows a boundary line of an opening 93 in a particularly advantageous form.
  • this opening 93 has a radius of, for example, 1 mm.
  • a 180-degree arch is followed by curved boundary lines. The design of these boundary lines can achieve special flow characteristics.
  • the above-described special measures of the design of the openings 93 serve the purpose of achieving that a sufficiently large pressure control range is available at all flow rates.
  • the inventive control valve unit 28 has initially been described in connection with FIG.
  • the pressure sensors 18 and 23 required in this type of control were not shown in the further figures because the prior art already provides examples for this. The same applies to the temperature sensor.
  • control valve unit 28 is not only intended to be used in connection with a system shown in FIG. 1 in the mode of operation mentioned according to the description of FIG.
  • inventive control valve unit 28 can also be used in any other design variants, for example even if the pump 10 is speed-controlled, which also entails another control principle for the control valve unit 28.

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  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Types And Forms Of Lifts (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Elevator Control (AREA)

Abstract

Unité soupape de commande (28) pour un ascenseur hydraulique, qui comporte deux soupapes de commande (5, 15) à l'aide desquelles le flux d'huile hydraulique peut être dirigé d'un réservoir à un vérin hydraulique entraînant la cabine de l'ascenseur et dudit vérin au réservoir. En cas de déplacement ascendant de la cabine, l'huile hydraulique est refoulée à l'aide d'une pompe entraînée par un moteur électrique du réservoir au vérin hydraulique via l'unité soupapes de commande (28), tandis que lors du déplacement descendant de la cabine, l'huile hydraulique s'écoule vers le réservoir via l'unité soupapes de commande (28) sans que la pompe soit actionnée. Selon la présente invention, pour commander le déplacement ascendant et le déplacement descendant de la cabine d'ascenseur, l'unité soupapes de commande (28) comporte deux soupapes de commande (5, 15) pilotes dont chacune fonctionne tant comme soupape de non-retour que comme soupape proportionnelle. Chacune des soupapes de commande (5, 15) possède un seul corps d'étranglement (35 ; 55) qui peut coulisser par rapport à un siège (36 ; 56). Sur le corps d'étranglement (35 ; 55) agissent d'une part un ressort de rappel (37 ; 57) et d'autre part une soupape de commande pilote (5V ; 15V), chacun de ces éléments étant actionné par un aimant proportionnel (5M ; 15M) à commande électrique. Ladite unité soupapes de commande (28) présente ainsi une construction très simple et peut donc être fabriquée à faible coût. Elle possède en outre le grand avantage de ne pas nécessiter d'éléments de réglage.

Claims (16)

  1. Unité de valves de commande (28) pour un ascenseur hydraulique, qui comprend des valves de commande (5, 15) et des valves pilotes (5V, 15V), par lesquelles le flux de l'huile hydraulique peut être commandé depuis un réservoir (11) vers un vérin de levée (3) entraînant une cabine d'ascenseur (1) ou depuis le vérin de levée (3) vers le réservoir (11), dans laquelle, pour un déplacement montant de la cabine d'ascenseur (1), l'huile hydraulique peut être convoyée depuis le réservoir (11) via l'unité de valves de commande (28) jusqu'au vérin de levée (3) au moyen d'une pompe (10) entraînée par un moteur électrique (12), et pour un déplacement descendant de la cabine d'ascenseur (1), l'huile hydraulique peut être convoyée vers le réservoir (11) via l'unité de valves de commande (28), et, dans laquelle, pour commander le déplacement montant et le déplacement descendant de la cabine d'ascenseur (1), il est prévu une valve pilote respective unique (5, 15) dont chacune fait office aussi bien de clapet anti-retour que de valve proportionnelle, caractérisée en ce que
    dans la valve de commande (5) commandant le déplacement descendant, la transmission des forces s'effectue depuis sa valve pilote (5V) au moyen d'un piston (48) agissant à l'encontre d'un ressort de régulation de valve principale (49) via une tige de commande (50) sur un piston antagoniste (38) qui déplace, via une tige de positionnement (39) fixée sur celui-ci, un corps d'étranglement (35), le diamètre du piston antagoniste (38) étant égal au diamètre du corps d'étranglement (35), et
    dans la valve de commande (15) commandant le déplacement montant, la transmission des forces s'effectue depuis sa valve pilote (15V) au moyen d'un piston (68) agissant à l'encontre d'un ressort de régulation de valve principale (69) via une tige de commande (70) sur un corps d'étranglement (55), et en ce que le corps d'étranglement (55) est relié fermement à un piston antagoniste (58) via une tige de positionnement (59), le diamètre du piston antagoniste (58) étant égal au diamètre du corps d'étranglement (55).
  2. Unité de valves de commande (28) selon la revendication 1, caractérisée en ce que dans chacune des valves de commande (5, 15) est prévu un corps d'étranglement unique (35 ; 55) qui est mobile en translation par rapport à un siège (36 ; 56).
  3. Unité de valves de commande (28) selon la revendication 2, caractérisée en ce que sur le corps d'étranglement (35 ; 55) agissent d'une part un ressort de rappel (37 ; 57) et d'autre part une valve pilote (5V ; 15V), dont chacune est susceptible d'être commandée au moyen d'un aimant proportionnel (5M ; 15M) à pilotage électrique.
  4. Unité de valves de commande (28) selon la revendication 3, caractérisée en ce que dans la valve de commande (15) commandant le déplacement montant, son ressort de rappel (57) et sa valve pilote (15V) agissent dans le même sens sur son corps d'étranglement (55) en direction de fermeture.
  5. Unité de valves de commande (28) selon la revendication 3, caractérisée en ce que dans la valve de commande (5) commandant le déplacement descendant, son ressort de rappel (37) agit sur son corps d'étranglement (35) en direction de fermeture, tandis que sa valve pilote (5V) agit en direction d'ouverture.
  6. Unité de valves de commande (28) selon les revendications 4 et 5, caractérisée en ce que le corps d'étranglement (35) de la valve de commande (5) commandant le déplacement descendant et le corps d'étranglement (55) de la valve de commande (15) commandant le déplacement montant présentent la même forme et les mêmes dimensions.
  7. Unité de valves de commande (28) selon la revendication 1, caractérisée en ce que le piston (48 ; 68) présente à sa périphérie extérieure une gorge (98) dans laquelle est mis en place un joint élastique (99).
  8. Unité de valves de commande (28) selon la revendication 1, caractérisée en ce que la surface du corps antagoniste (38 ; 58) tournée vers le corps d'étranglement (35 ; 55) présente la forme d'un tronc de cône.
  9. Unité de valves de commande (28) selon la revendication 8, caractérisée en ce que la surface enveloppe du tronc de cône (80) forme un angle a d'environ 15 à 25° par rapport à une surface dressée verticalement sur l'axe longitudinal.
  10. Unité de valves de commande (28) selon l'une des revendications 1 à 9, caractérisée en ce que les corps d'étranglement (35 ; 55) sont formés par une base (90) et par un cylindre (91) qui s'y raccorde, dans la surface enveloppe (92) duquel sont fraisées des ouvertures (93).
  11. Unité de valves de commande (28) selon la revendication 10, caractérisée en ce que les ouvertures (93) sont au moins en partie en forme de V.
  12. Unité de valves de commande (28) selon la revendication 10, caractérisée en ce que les ouvertures (93) présentent une forme de coupe.
  13. Unité de valves de commande (28) selon la revendication 10, caractérisée en ce que les ouvertures (93) sont en gradins.
  14. Unité de valves de commande (28) selon l'une des revendications 1 à 13, caractérisée en ce qu'il est prévu des moyens (95, 96 ; 97) par lesquels la course du piston (48 ; 68) peut être limitée.
  15. Unité de valves de commande (28) selon la revendication 14, caractérisée en ce que la limitation de la course s'effectue par un circlips (96) qui peut être mis en place dans l'une parmi plusieurs gorges annulaires (95) ménagées dans la paroi intérieure cylindrique de chambres de commande (47 ; 67).
  16. Unité de valves de commande (28) selon la revendication 14, caractérisée en ce qu'un anneau écarteur cylindrique (97) peut être mis en place dans la chambre de commande (47 ; 67), anneau dont le diamètre extérieur est légèrement inférieur au diamètre de la chambre de commande (47 ; 67) et par la longueur duquel peut être déterminée la limitation de course.
EP01962699A 2000-07-03 2001-06-01 Unite soupape de commande pour un ascenseur hydraulique Expired - Lifetime EP1222416B1 (fr)

Applications Claiming Priority (3)

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CH131200 2000-07-03
CH01312/00A CH694763A5 (de) 2000-07-03 2000-07-03 Steuerventileinheit für einen hydraulischen Aufzug.
PCT/EP2001/006273 WO2002002974A2 (fr) 2000-07-03 2001-06-01 Unite soupape de commande pour un ascenseur hydraulique

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PL357194A1 (en) 2004-07-26
EP1222416A2 (fr) 2002-07-17
US20020153204A1 (en) 2002-10-24
KR20020030792A (ko) 2002-04-25
US6742629B2 (en) 2004-06-01
HRP20020191A2 (en) 2004-02-29
WO2002002974A2 (fr) 2002-01-10
AU8383101A (en) 2002-01-14
WO2002002974A3 (fr) 2002-05-23
MXPA01013142A (es) 2003-08-20
BR0106900A (pt) 2002-07-16
CA2383190A1 (fr) 2002-01-10
JP2004502114A (ja) 2004-01-22
AU770145B2 (en) 2004-02-12

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