EP1222416A2 - Unite soupape de commande pour un ascenseur hydraulique - Google Patents

Unite soupape de commande pour un ascenseur hydraulique

Info

Publication number
EP1222416A2
EP1222416A2 EP01962699A EP01962699A EP1222416A2 EP 1222416 A2 EP1222416 A2 EP 1222416A2 EP 01962699 A EP01962699 A EP 01962699A EP 01962699 A EP01962699 A EP 01962699A EP 1222416 A2 EP1222416 A2 EP 1222416A2
Authority
EP
European Patent Office
Prior art keywords
control valve
control
valve
valve unit
piston
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.)
Granted
Application number
EP01962699A
Other languages
German (de)
English (en)
Other versions
EP1222416B1 (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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from 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

Links

Classifications

    • 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 to influence 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 of the type mentioned in the preamble of claim 1 is known from US-A-5,040,639. It includes three pilot operated control valves and a check valve, in which the position of the opening is monitored with a position transmitter. In addition to fixed throttles, there are also some adjustment elements.
  • a similar control valve unit is known from EP-A2-0 964 163, which is constructed in a considerably more complex manner and, in addition to four main control valves and three pilot control valves, contains a whole series of mechanical setting elements.
  • the invention has for its object to provide a control valve unit which is simple in construction and does not require any adjustment elements. This results in lower manufacturing costs and time-consuming settings are not necessary during commissioning.
  • FIG. 1 shows a diagram of the hydraulic elevator including the device for controlling it
  • Fig. 13 shows a special design of an opening on the throttle body.
  • 1 means an elevator car of a hydraulic elevator, which can be moved by a reciprocating piston 2.
  • the reciprocating piston 2 forms, together with a lifting cylinder 3, a known hydraulic drive.
  • a cylinder line 4 is connected to this hydraulic drive, through which hydraulic coils can be conveyed.
  • 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 like a proportional valve or like a check valve, which depends on how the control valve 5 is controlled, what is still discussed.
  • the proportional valve function can be achieved in a known manner with a main valve and a pilot valve, the pilot valve being actuated by an electric drive, for example a proportional magnet.
  • the closed check valve holds the elevator car 1 in the respective position.
  • the control valve 5 is connected to a pump 10 via a pump line 8, in which a pressure pulsation damper 9 can be arranged, by means of which pump hydraulic pumps can be conveyed from a tank 11 for hydraulic drive.
  • the pump 10 is driven by an electric motor 12 to which a power supply part 13 is assigned.
  • a pressure P P prevails in the pump line 8.
  • a second control valve 15 is arranged between the control valve 5 and the tank 11 between the control valve 5 and the tank 11 there is a further line leading to hydraulic piston, namely a return line 14, in which a second control valve 15 is arranged.
  • This control valve 15 allows the hydraulic oil to flow back almost without resistance from the pump 10 into the tank 11 when the pressure P P has exceeded a certain threshold value. As a result, the pressure P P cannot substantially exceed 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 take over a pressure control function in a manner similar to a known proportional valve.
  • a main valve and a pilot valve can be used in a known manner, which is actuated by a proportional magnet which can be controlled electrically.
  • a load pressure sensor 18 is located in the cylinder line 4, preferably directly at the corresponding connection of the control valve 5 or on the control valve 5 itself, and is connected to a control unit 20 via a first measuring line 19.
  • the control device 20 serving to operate the hydraulic elevator is thus able to recognize the pressure P z prevailing in the cylinder line 4.
  • this pressure P z reflects the load on the elevator car 1.
  • control and regulating processes can be influenced and operating states can be determined.
  • the control unit 20 can also consist of several control and regulator units.
  • a further pressure sensor namely a pump pressure sensor 23, is advantageously present, which detects the pressure P P in the pump line 8 and is advantageously arranged directly at the corresponding connection of the pump line 8 on the control valve 5.
  • the pump pressure sensor 23 also transmits its measured value to the control unit 20 via a further measuring line 24.
  • a first control line 25 leads from the control unit 20 to the control valve 5.
  • this control valve 5 can be electrically controlled from the control unit 20.
  • a second control line 26 leads to the control valve 15, so that this can also be controlled by the control unit 20.
  • 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 possibly also the speed of the motor 12 and thus the delivery rate of the pump 10 can be influenced by the control unit 20.
  • both control valves 5 and 15 basically behave like a check valve that can be preloaded differently. If the control valves 5 and 15 are actuated by the control device 20 by means of 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. This has the advantage that the assembly effort on the construction site of the hydraulic elevator is reduced. According to the general idea of the invention, the two control valves 5 and 15 are similar and constructed using the same parts, which has different advantages, which will be discussed below.
  • the electrically not controlled control valve 5 closes automatically due to the effect of the pressure P z which the elevator car 1 generates 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. The effective load of the elevator car 1 is determined and transmitted to the control unit 20. The control device 20 can thus recognize whether the elevator car 1 is empty or loaded and the size of the load is thus also known. If the elevator car 1 is to move in the upward direction, the control unit 20 first activates the power supply part 13 via the control line 27 and thus sets the electric motor 12 in rotation, as a result of which the pump 10 starts to run and promotes hydraulic power. As a result, the pressure P P in the pump line 8 rises.
  • 2 shows a basic state without any control of the control valves 5 and 15 contained in the control valve unit 28.
  • FIG. 3 shows a state during the upward movement of the elevator car 1 (FIG. 1), while FIG. 4 shows the state during the downward movement.
  • 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] shows the connection to the pump line 8 and with [14] the connection to the return line 14.
  • the pressures P z and P P prevailing in the connection spaces are drawn in, which were 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 actuated by a proportional magnet.
  • the control valve unit 28 consists of two housing parts, namely a first housing part 30, which contains the main valves of the control valves 5 and 15, and a second housing part 31, in which the associated pilot valves, which are denoted by 5 V and 15 V , are accommodated.
  • the housing part 31 itself can be in two parts, in that each of the pilot valves 5 V and 15 V has its own housing part.
  • a proportional magnet is assigned to each of the pilot valves 5 V and 15 v , namely the pilot valve 5 V the proportional magnet 5 M and the pilot valve 15 v the proportional magnet 15 M.
  • These proportional magnets 5 M and 15 M can be controlled by control unit 20 (FIG. 1) via control lines 25 and 26, respectively.
  • the first housing part 30 contains several chambers.
  • a first chamber is referred to as a cylinder chamber 32.
  • the cylinder line 4 (FIG. 1) connects to this, which is why the corresponding connection is designated by [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 symbol [8].
  • Another chamber is referred to as the return chamber 34, to which the return line 14 connects, which is correspondingly designated by the reference symbol [14].
  • a first throttle body 35 is arranged in an opening between the cylinder chamber 32 and the pump chamber 33 and, together with a first valve seat 36 formed in the housing part 30, forms the main valve of the control valve 5.
  • this main valve of the control valve 5 is the essential element which directly influences the flow of hydraulic fluid to and from the lifting cylinder 3 (FIG. 1).
  • the main valve of the control valve 5 contains the function of a check valve and at the same time the function of a proportional valve, which is 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 actuated on the one hand by a return spring 37.
  • the main valve is kept closed by this return spring 37 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, when the pump 10 (FIG. 1) is not running and the elevator car 1 (FIG. 1) is at a standstill.
  • control elements act on the throttle body 35 and are moved by the control of the pilot valve 5 V.
  • These adjusting elements comprise a counter-piston 38 with an adjusting rod 39 fastened thereon.
  • 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 can be actuated by the pilot valve 5 V as follows.
  • the proportional magnet 5 M acts on a pilot piston 43 in a known manner via a plunger plunger 41 against a pilot control spring 42.
  • the movement of the pilot piston 43 results in the build-up 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 therefore also determined by the pilot control spring 42.
  • pilot valve 5 V detects the pressure P z in the cylinder chamber 32 via a first connecting duct 45 and also detects the pressure prevailing in the return chamber 34 via a second connecting duct 46, no adjustment elements are required in order to obtain the correct control pressure Px to reach.
  • the pilot valve 5 V regulates the control pressure P ⁇ 5 , the control pressure P x being a function of the pressures in the cylinder chamber 32 and the 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.
  • the control pressure P acts on a piston 48 which is displaceable in a control chamber 47.
  • the piston 48 is supported by a main valve control spring 49 against the gel part 30.
  • the movement of the piston 48 is transmitted to the counter-piston 38 by means of a control rod 50.
  • the main valve control spring 49 thus acts on the one hand as a return spring for the piston 48, but on the other hand also acts as a control spring for the main valve of the control valve 5. According to the invention, no adjustment elements are required here either.
  • the second control valve 15 is designed according to the same basic principle.
  • a second throttle body 55 is arranged in an opening between the pump chamber 33 and the return chamber 34 and, together with a second valve seat 56 formed in the housing part 30, forms the main valve of the control valve 15.
  • 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 is explained below.
  • the throttle body 55 is actuated on the one hand by a return spring 57.
  • This return spring 57 keeps the main valve 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 (Fig. 1) is not running.
  • control elements act on the throttle body 55 and are moved by the control of the pilot valve 15 v .
  • control valve 5 is acted M 15 without the interposition of a counter-piston to the throttle body 55 when control valve 15 by the proportional solenoid.
  • the throttle body 55 can also be actuated by the pilot valve 15 v as follows.
  • the proportional magnet 15 M acts in a known manner on a pilot piston 63 via a plunger plunger 61 against a pilot control spring 62.
  • the movement of the pilot piston 63 results in the build-up of a control pressure Py in a control pressure chamber 64.
  • This control pressure P ⁇ depends on the movement of the pilot piston 63 and is therefore also determined by the pilot control spring 62.
  • the pilot valve 15 v detects the pressure P P in the pump chamber 33 via a further connection duct 65 and also detects the pressure prevailing in the return chamber 34 via the connection duct 46 mentioned above, no adjustment elements are required to determine the correct one To reach control pressure Py.
  • the connecting channel 65 is shown in dashed lines because it lies in a different plane so that it can make the connection from the pilot valve 15 v to the pump chamber 33 bypassing the return chamber 34.
  • the pilot valve 15 v regulates the control pressure P ⁇ , the control pressure P ⁇ being a function of the pressures in the pump chamber 33 and the return chamber 34 and the stroke of the pilot piston 63, which in turn is determined by the actuation of the pilot valve 15 v .
  • the control pressure P ⁇ acts on a piston 68 which is displaceable in a control chamber 67.
  • the piston 68 is supported by 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, but on the other hand also as a control spring for the main valve of the control valve 15.
  • no adjustment elements are required according to the invention.
  • the proportional valve function of the control valve 15 is activated, as mentioned at the beginning. This is done by actuating the proportional magnet 15 M via the control line 26.
  • FIG. 3 also shows that, as a result of the increased pressure P P , the throttle body 35 of the main valve of the first control valve 5 has also been moved against the return spring 37. This movement can then occur as soon as the pressure P P is so much greater than the pressure P z that the force of the return spring 37 is also overcome.
  • hydraulic piston is thus conveyed through the cylinder line 4 into the lifting cylinder 3, which causes the elevator car 1 to move upwards.
  • the opening of the main valve of the control valve 5 takes place without the control of the proportional magnet 5 M , that is to say without the involvement of the pilot valve 5 V, solely because of the positive pressure difference P P -P Z.
  • the upward travel of the elevator car 1 is thus achieved solely by actuating the proportional magnet 15 M and the main valve of the control valve 5 has only the check valve function.
  • the control valve 15 also has a counter body 58 and an actuating rod 59.
  • the actuating rod 39 is fixedly attached to the counter-piston 38
  • the throttle body 35 is a separate part in the control valve 15 counter body 58, adjusting rod 59 and throttle body 55 a single part.
  • the counter body 58 has regard to The effect of force has no influence on the main valve of the control valve 15 formed from the throttle body 55 and the valve seat 56.
  • Guide ribs with which the counter body 58 is guided can advantageously be arranged in the recess 60.
  • the counter bodies 38 and 58 have the following different meanings.
  • the pressure in the pump chamber 33 acts on the counter-bodies 38 and 58 in the same way as on the throttle bodies 35 and 55. If the diameters of the counter-bodies 38 and 58 are advantageously the same size as the diameters of the throttle bodies 35 and 55, this results a balance of forces.
  • the first control valve 5 in which the throttle body 35 on the one hand and the counter body 38 with the actuating rod 39 on the other hand are separate parts, the same force acting on the throttle body 35 as is caused by the pressure P P acts on the throttle body 35.
  • the force which the pilot valve 5 M exerts must in order to move the piston 48 and the control rod 50 against the counter-piston 38 and the throttle body 35 is not changed by differential forces.
  • the rigid connection of the counter-piston 58 to the throttle body 55 is necessary because here the counter-piston 58 lies on the side of the main valve facing away from the pilot valve 15 M , so that the force is not transmitted via the counter-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 counter-piston 58, and therefore 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 cabin 1 (FIG. 1) moves downward.
  • the pump 10 (FIG. 1) then does not run. Accordingly, the pressure P P is small.
  • the main valve of the control valve 5 formed from the throttle body 35 and seat 36 is closed.
  • the pro- portionalmagnet 5 M driven. This acts via the plunger plunger 41 on the pilot valve 5 V , which builds up the control pressure P x in the control chamber 47.
  • the size of the control pressure P x is determined by the control of the proportional magnet 5M and the pilot control spring 42 and is of course also influenced by the pressure P z in the cylinder chamber 32 and by 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 in the direction of the counter-piston 38 against the force of the main valve control spring 49. This movement is transmitted to the counter-piston 38 via the control rod 50.
  • Whose movement is transmitted to the throttle body 35 via the adjusting rod 39.
  • the main valve of the control valve 5 thus opens.
  • the main valve of the control valve 15 formed from the throttle body 55 and the valve seat 56 thus acts as a check valve when traveling downward, which is opened solely by the pressure P P.
  • the proportional solenoid 15M is therefore not actuated and therefore the pilot valve 15 v is also without function.
  • control valves 5 and 15 are required according to the invention, each of which functions of check valve and proportional valve combine.
  • the check valve functions of control valves 5 and 15 also 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 unnecessary.
  • the control valve unit 28 according to the invention thus has a particularly simple structure and can be produced inexpensively. If the throttle bodies 35 and 55 are identical according to an advantageous embodiment of the invention, this also means an advantage in terms of production costs because different throttle bodies do not have to be manufactured.
  • FIG. 5 shows the closing body 55 together with the counter body 58 and the connecting rod 59 connecting these two parts.
  • the surface facing the closing body 55 has the shape of a truncated cone 80.
  • the surface of the truncated cone 80 advantageously forms an angle Winkel of approximately 15 to 25 degrees with respect to a surface perpendicular to the longitudinal axis. It is thereby achieved that dynamic forces generated by the main valve of the control valve 15 at a high flow rate have no adverse repercussions on the pilot valve 15 v .
  • the counter body 58 of the control valve 15 has the same shape and size as the counter body 38 of the control valve 5. If the counter bodies 38 and 58 are identical, this has the advantage that fewer different parts have to be manufactured and kept in stock the production lot size is twice as large, which has a favorable effect on production costs. This is also important with regard to service work on site.
  • a counter body 58 is shown in FIG. 6, the shape and size of which corresponds to the counter body 38 (FIG. 4). The angle a is also present here.
  • FIG. 7 shows the counter body again, which can be used as a counter body 38 for the control valve 5 and as a counter body 58 for the control valve 15, with the angle a again occurring.
  • the size of the recess 60 is in each case adapted to the size of the counter body 58. If the counter body 58 is designed according to FIG. 5, the depth of the recess 60 is small. If, however, the size of the counter body 58 is designed according to FIG. 6, the depth of the recess 60 is correspondingly greater, so that the counter body 58 can be accommodated in the recess 60 when the main valve of the second control valve 15 is closed.
  • FIGS. 8a to 8d Details of the throttle bodies 35, 55 are shown in FIGS. 8a to 8d, namely different design variants.
  • a cylinder 91 connects to a base 90, the lateral surface of which is designated by the reference number 92. Openings 93 are milled into the cylinder 91, through which the hydraulic piston can pass. For example, six evenly distributed openings 93 are advantageously milled into the circumference of the cylinder 91.
  • the openings 93 can have different shapes.
  • the openings 93 in the part adjoining the base 90 are V-shaped and in the part adjoining them are of constant width. It follows from this that the effective passage cross section for the hydraulic piston initially increases progressively with increasing stroke of throttle body 35, 55 and then increases linearly with increasing stroke.
  • the openings 92 in the part adjoining the base have a cup-shaped shape instead of the V-shaped one.
  • the effective passage cross-section for the hydraulic piston is non-linear. Starting from the closed state of the control valves 5 and 15, the effective passage cross-section for the hydraulic piston initially increases only slightly when actuated in the opening direction, then becomes increasingly larger with increasing stroke and then later decreases with increasing stroke. Then it remains constant.
  • FIG. 8c shows an example in which 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 cross-section for the hydraulic piston initially increases slightly and then changes abruptly to a maximum value at which the cross-section is then independent of the further stroke.
  • FIG. 8d Another example is shown in FIG. 8d, in which the openings 93 are only stepped. In the first stroke range, the opening 93 has a small width and then abruptly goes into one Rectangular shape greater width. This means that the effective passage cross-section for the hydraulic piston initially has a first value and then changes abruptly to a maximum value at which the passage cross-section is then independent of the further stroke.
  • the shape of the throttle bodies 35, 55 means that the flow characteristics of the control valves 5 and 15 can be adapted within wide limits to the respective elevator system and the type of control.
  • the examples shown above give an idea of the possibilities that are available. By different designs of the throttle bodies 35 and 55, the control valves 5 and 15 can thus be adapted to different tasks and systems. In the known prior art, different types and sizes exist for the different applications. It is thus achieved by the invention that both small and large elevator systems can be controlled with only a single control valve unit 28 by slight modifications.
  • a further advantageous embodiment consists in providing a stroke limitation.
  • Such a stroke limitation can advantageously be achieved in that the possible path of the pistons 48 and 68 within the control chamber 47 and 67 is limited. Suitable variants are shown in FIGS. 9a and 9b.
  • FIG. 9 a shows a detail from FIGS. 2 to 4, namely the control chamber 47 or 67 with the piston 48 or 68 which can be displaced therein.
  • a number of annular grooves 95 are pierced into the cylindrical inner wall of the control chamber 47 and 67. Snap rings 96 can be inserted into these ring grooves 95. Depending on the desired stroke limitation, a snap ring 96 is inserted into one of the ring grooves 95.
  • the stroke that the piston 48 or 68 can make is thus limited.
  • the stroke of the throttle bodies 35 and 55 of the control valves 5 and 15 (FIGS. 2 to 4) is also limited accordingly. In this way, it is possible to determine during the assembly of the control valve unit 28 for which maximum nominal flow rate the control valve unit 28 is to be designed. Different sizes of control valve units 28 are therefore unnecessary.
  • FIG. 9b An advantageous variant of the stroke limitation is shown in FIG. 9b.
  • the ring grooves 95 (FIG. 9a), which are problematic in terms of production technology, are not necessary here. Instead, a spacer ring 97 is inserted into the control chamber 47 or 67. Its outer diameter is slightly smaller than the diameter of the control chamber 47 or 67.
  • the length of the cylindrical spacer ring determines the stroke limitation.
  • the possible stroke limits namely, for example, 5, 8, 11 and 14 mm, depend on the positions of the individual annular grooves 95, there is the possibility of providing any desired stroke limits.
  • FIG. 2 A detail of the pistons 48, 68 is shown in FIG. They have a groove 98 on their outer circumference, in which an annular elastic seal 99 is inserted.
  • This seal 99 largely fills the gap between the cylindrical outer surface of the pistons 48, 68 and the inner wall of the control chamber 47, 67 (FIG. 2).
  • the seal 99 advantageously fulfills the task of reducing the leakage, because it decisively reduces the leakage of hydraulic fluid from the control chamber 47, 67 in the direction of the main valve of the control valves 5, 15.
  • FIG. 11 shows the outer surface of a throttle body 35 (FIG. 2).
  • the opening 93 of FIG. 11 begins at a distance d from the base 90 (FIGS. 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.
  • This different size of the individual openings 93 advantageously achieves the fact that the flow characteristic dependent on the valve lift can be defined as desired by defining the individual distances d, d ', d "etc., so that the flow characteristic can be optimally adapted to the respective needs.
  • FIG. 12a and 12b show further possible details of openings 93.
  • An opening 93 is shown in FIG. 12a, the root 93 w of which begins analogously to FIG. 11 at a certain distance from the base 90.
  • the depth of such an opening, but also the width advantageously follow a dimensioning rule, which is 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. 12 b shows a section to FIG. 12 a at a distance y from the root 93 w.
  • all openings 93 begin with their roots 93 w (FIG. 12 a) at the same distance from the base 90, but it is also conceivable that this solution is combined with that of FIG. 11 what is indicated in FIG. 12 b by the fact that one of the openings is deeper with a broken line, because its root 93 w begins at a smaller distance from the base 90.
  • this opening 93 shows a boundary line of an opening 93 in a particularly advantageous shape.
  • this opening 93 has a radius of, for example, 1 mm.
  • a 180-degree arc is followed by curved boundary lines.
  • the special measures described above for the design of the openings 93 serve the purpose of ensuring that a sufficiently large pressure control range is available for all flow rates.
  • control valve unit 28 was initially described in connection with FIG. 1.
  • the pressure sensors 18 and 23 required for this type of control have not been shown in the other figures because the prior art already provides models for this. The same applies to the temperature sensor.
  • control valve unit 28 according to the invention is not only intended to be used in connection with a system shown in FIG. 1 in the operating mode mentioned in the description for FIG. 1.
  • control valve unit 28 according to the invention can also be used with any other type of construction, with for example, even if the pump 10 is speed-controlled, which also entails another control principle for the control valve unit 28.

Landscapes

  • 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.
EP01962699A 2000-07-03 2001-06-01 Unite soupape de commande pour un ascenseur hydraulique Expired - Lifetime EP1222416B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
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

Publications (2)

Publication Number Publication Date
EP1222416A2 true EP1222416A2 (fr) 2002-07-17
EP1222416B1 EP1222416B1 (fr) 2006-10-18

Family

ID=25738978

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01962699A Expired - Lifetime EP1222416B1 (fr) 2000-07-03 2001-06-01 Unite soupape de commande pour un ascenseur hydraulique

Country Status (12)

Country Link
US (1) US6742629B2 (fr)
EP (1) EP1222416B1 (fr)
JP (1) JP2004502114A (fr)
KR (1) KR20020030792A (fr)
AU (1) AU770145B2 (fr)
BR (1) BR0106900A (fr)
CA (1) CA2383190A1 (fr)
DE (1) DE50111267D1 (fr)
HR (1) HRP20020191A2 (fr)
MX (1) MXPA01013142A (fr)
PL (1) PL357194A1 (fr)
WO (1) WO2002002974A2 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2383190A1 (fr) 2000-07-03 2002-01-10 Wittur Ag Unite soupape de commande pour un ascenseur hydraulique
AT503040B1 (de) * 2005-12-12 2007-07-15 Lcm Gmbh Verfahren und vorrichtung zur steuerung eines hydraulischen aufzugs
DE102007005070B4 (de) 2007-02-01 2010-05-27 Klippel, Wolfgang, Dr. Anordnung und Verfahren zur optimalen Schätzung der linearen Parameter und der nichtlinearen Parameter eines Modells, das einen Wandler beschreibt
US8191689B2 (en) * 2009-06-19 2012-06-05 Tower Elevator Systems, Inc. Elevator safety rescue system
ITMO20110330A1 (it) * 2011-12-22 2013-06-23 Brevini Fluid Power S P A Dispositivo di comando
DE102013014671A1 (de) 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
EP3280669A4 (fr) * 2015-04-08 2019-03-20 W2W 777 Operations LLC Fosse intelligente pour ascenseurs hydrauliques et d'autres produits utilisant des fluides hydrauliques sous pression
CN105402468B (zh) * 2015-09-16 2018-06-29 中国船舶重工集团公司第七0七研究所九江分部 一种电磁阀箱油路切换装置
EP3444213A1 (fr) * 2017-08-17 2019-02-20 Blain Hydraulics GmbH Ascenseur hydraulique
US11198585B2 (en) * 2019-02-18 2021-12-14 Tk Elevator Corporation Systems and methods for controlling working fluid in hydraulic elevators
EP3778298B1 (fr) * 2019-08-13 2024-06-26 Rotex Automation Limited Soupape de commande de cabine intégrée dotée d'une soupape de commande de direction de solénoïde
CN110748520B (zh) * 2019-09-19 2021-03-30 山东科技大学 一种针规节流器
US11845633B2 (en) * 2020-06-02 2023-12-19 Killakathu Ramanathan Babu Overload valve assembly for a pneumatic vacuum elevator

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5138136B2 (fr) * 1971-09-17 1976-10-20
DE2358057C2 (de) * 1973-02-15 1984-09-06 Maxton Manufacturing Co., Los Angeles, Calif. Hydraulische Steueranlage
US4438831A (en) * 1980-01-07 1984-03-27 Westinghouse Electric Corp. Elevator system
US4368805A (en) * 1980-12-15 1983-01-18 Elevator Equipment Company Hydraulic control unit for elevators
US4637495A (en) * 1985-10-09 1987-01-20 Blain Roy W Pressure/viscosity compensated up travel for a hydraulic elevator
JPS63199969A (ja) * 1987-02-13 1988-08-18 Hitachi Ltd 流体制御弁
US5040639A (en) 1990-01-31 1991-08-20 Kawasaki Jukogyo Kabushiki Kaisha Elevator valve apparatus
JP2893978B2 (ja) * 1991-02-28 1999-05-24 株式会社日立製作所 流体圧エレベータ及びその制御方法
US5232070A (en) * 1991-08-15 1993-08-03 Blain Roy W Up leveling control system for small elevators
US5289901A (en) * 1992-08-03 1994-03-01 Otis Elevator Company Hydraulic elevator pressure relief valve
KR960010228B1 (ko) * 1993-10-25 1996-07-26 이희종 유압엘리베이터용 제어밸브장치
US5636652A (en) * 1995-02-28 1997-06-10 Otis Elevator Company Valve for a hydraulic elevator
US5593004A (en) * 1995-03-28 1997-01-14 Blain Roy W Servo control for hydraulic elevator
JPH09124256A (ja) * 1995-10-31 1997-05-13 Hitachi Ltd 油圧式エレベータの油圧制御弁
JP3421495B2 (ja) * 1996-02-02 2003-06-30 豊興工業株式会社 エレベータ弁装置
JP2000508614A (ja) * 1997-02-06 2000-07-11 ベーリンガー―ヒィドラウリク・アクチェンゲゼルシャフト 液圧式昇降機を制御する方法および装置
IT1299508B1 (it) 1998-06-10 2000-03-16 Otis Elevator Co Valvola perfezionata per centralina idraulica, in particolare per ascensori, montacarichi e simili
CA2383190A1 (fr) 2000-07-03 2002-01-10 Wittur Ag Unite soupape de commande pour un ascenseur hydraulique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0202974A2 *

Also Published As

Publication number Publication date
PL357194A1 (en) 2004-07-26
AU770145B2 (en) 2004-02-12
KR20020030792A (ko) 2002-04-25
AU8383101A (en) 2002-01-14
US6742629B2 (en) 2004-06-01
BR0106900A (pt) 2002-07-16
JP2004502114A (ja) 2004-01-22
EP1222416B1 (fr) 2006-10-18
US20020153204A1 (en) 2002-10-24
MXPA01013142A (es) 2003-08-20
HRP20020191A2 (en) 2004-02-29
WO2002002974A3 (fr) 2002-05-23
CA2383190A1 (fr) 2002-01-10
WO2002002974A2 (fr) 2002-01-10
DE50111267D1 (de) 2006-11-30

Similar Documents

Publication Publication Date Title
DE2925268C2 (fr)
DE3688321T2 (de) Entspannungsventil.
EP2307726B1 (fr) Pompe à cylindrée variable
DE3910030C2 (de) Radaufhängung für Fahrzeuge
EP1222416B1 (fr) Unite soupape de commande pour un ascenseur hydraulique
DE3149026C2 (fr)
EP1065379B1 (fr) Alimentation en pression avec pompe à capacité variable et motorisation électrique réglable
DE2065423B2 (de) Steuervorrichtung fuer ein hydrostatisches getriebe mit veraenderlichem uebersetzungsverhaeltnis fuer fahrzeuge
DE3437217A1 (de) Fahrzeug-hoehenverstellsystem mit gleichfoermiger hoehensteuerung
WO1985004455A1 (fr) Systeme hydraulique pour vehicules
EP1446349A1 (fr) Ascenseur hydraulique equipe d'un accumulateur de pression et son procede de commande et de reglage
DE3247004A1 (de) Hydrostatisches getriebe, insbesondere fuer den fahrzeugantrieb
DE102009005768B4 (de) Druckregelung einer hydraulischen Antriebseinheit
DE2108202C3 (de) Hubfahrsteuereinrichtung für einen hydraulischen Aufzug
DE3210445A1 (de) Elektrohydraulisches proportionalsteuerventil
EP3464908B1 (fr) Système de vannes
DE1630105C3 (de) Hydrostatisches Getriebe für Kraftfahrzeuge
DE2537957A1 (de) Steuer- bzw. regelanordnung fuer pumpen mit variabler verdraengung
EP2126370A1 (fr) Dispositif de commande pour des consommateurs hydrauliques
EP0561153A1 (fr) Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable
DE4120489A1 (de) Niveauregeleinrichtung fuer fahrzeuge
DE2352622B2 (de) Hydraulisches Steuersystem für ein automatisches Getriebe
EP0574737B1 (fr) Véhicule à propulsion électrique à alimentation par accumulateurs, en particulier Chariot-élévateur
CH694763A5 (de) Steuerventileinheit für einen hydraulischen Aufzug.
DE19541190A1 (de) Hydraulische Anordnung zur Steuerung des Hubwerks einer mobilen Arbeitsmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20011129

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

EL Fr: translation of claims filed
REG Reference to a national code

Ref country code: GR

Ref legal event code: PP

Ref document number: 20020300048

Country of ref document: GR

GBC Gb: translation of claims filed (gb section 78(7)/1977)
17Q First examination report despatched

Effective date: 20050622

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20061018

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061018

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061018

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50111267

Country of ref document: DE

Date of ref document: 20061130

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070118

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070118

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20070201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070319

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2177480

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070719

BERE Be: lapsed

Owner name: WITTUR A.G.

Effective date: 20070630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20080101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080101

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070630

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070601

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20090629

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070601

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061018

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20090522

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20090618

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20090825

Year of fee payment: 9

Ref country code: GB

Payment date: 20090623

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20090627

Year of fee payment: 9

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20100601

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100601

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100630

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20110714

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100601

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110704

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100602

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100601