EP3746662B1 - Steuerventilanordnung zur indirekten pneumatischen steuerung und verfahren zum steuern eines arbeitsfluiddrucks - Google Patents

Steuerventilanordnung zur indirekten pneumatischen steuerung und verfahren zum steuern eines arbeitsfluiddrucks Download PDF

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Publication number
EP3746662B1
EP3746662B1 EP19704558.6A EP19704558A EP3746662B1 EP 3746662 B1 EP3746662 B1 EP 3746662B1 EP 19704558 A EP19704558 A EP 19704558A EP 3746662 B1 EP3746662 B1 EP 3746662B1
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EP
European Patent Office
Prior art keywords
valve
control
working fluid
piston
pressure
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.)
Active
Application number
EP19704558.6A
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German (de)
English (en)
French (fr)
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EP3746662C0 (de
EP3746662A1 (de
Inventor
Piotr KRUPNIK
Simon Brose
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J D Neuhaus Holding & Co KG GmbH
Original Assignee
J D Neuhaus Holding & Co Kg GmbH
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Priority to HRP20230778TT priority Critical patent/HRP20230778T1/hr
Priority to RS20230633A priority patent/RS64404B1/sr
Publication of EP3746662A1 publication Critical patent/EP3746662A1/de
Application granted granted Critical
Publication of EP3746662C0 publication Critical patent/EP3746662C0/de
Publication of EP3746662B1 publication Critical patent/EP3746662B1/de
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Anticipated expiration legal-status Critical

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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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/0422—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with manually-operated pilot valves, e.g. joysticks
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated 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
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-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
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in 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
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and 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
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/411—Flow control characterised by the positions of the valve element the positions being discrete
    • 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
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control 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
    • F15B2211/42—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
    • F15B2211/70—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
    • F15B2211/7058—Rotary 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/885—Control specific to the type of fluid, e.g. specific to magnetorheological fluid
    • F15B2211/8855—Compressible fluids, e.g. specific to pneumatics

Definitions

  • the invention relates to a control valve arrangement for indirect pneumatic control and a method for controlling a working fluid pressure by means of a control fluid in a control valve arrangement for indirect pneumatic control.
  • Control valve arrangements for pneumatic control are known from the prior art in a variety of configurations from the prior art and are used in particular for controlling pneumatic actuators.
  • a special area here relates to the pneumatic control of pneumatically operated motors of hoists.
  • the motor in particular a vane motor, of a hoist directly
  • the pressure of the working fluid usually compressed air
  • the compressed air provided for the drive is typically routed from a central connection via a hose to a manual control unit and from there to the position of the motor of the hoist, which is usually positioned in the area of a hall ceiling.
  • these hoses which must continuously withstand the full working pressure of the working fluid, are relatively thick and heavy, making them difficult to handle and difficult to operate.
  • a correspondingly long hose between the manual control and the hoist leads to power losses that increase with the length of the hose and to a control delay, which means that precise and sensitive control of a load on the hoist is no longer possible.
  • a control valve for a hydraulic motor is already known, the control valve being designed as a directional control valve in which a control slide is arranged to be displaceable in a longitudinal bore of a valve body in order to control the flow of hydraulic oil between two working connection bores, a pump connection bore and a tank connection bore.
  • a non-return valve which is prestressed by means of a prestressing spring and is connected on the one hand to an auxiliary control groove via a first transverse bore and on the other hand to the B-tank groove via a second transverse bore.
  • the control valve arrangement according to the invention for indirect pneumatic control in particular a pneumatically operated vane motor of a hoist, comprises two pneumatic valve units arranged functionally one behind the other, a working fluid inlet and a control fluid inlet as well as a working fluid channel connecting the working fluid inlet through both valve units to an outlet, the outlet being provided in particular for supplying the working fluid to a vane motor of a hoist is.
  • a valve piston which is arranged within a valve cylinder and can be displaced between an open and a closed position, with each of the two valve pistons being acted upon by a spring element which prestresses towards the closed position of the valve unit.
  • Both valve units also each have a control pressure chamber connected to the control fluid inlet for applying a control pressure counteracting the preload of the spring element to the respective valve piston in order to move the valve piston into an at least partially open position against the force of the spring element.
  • the first valve unit is formed in such a way that when any control pressure greater than 0 bar is applied in the control pressure chamber, the valve piston is shifted from the closed to a fully open position.
  • two opposing valve surfaces which are angled towards one another, are arranged on the surface of the valve cylinder and the valve piston, extending along the direction of displacement in such a way that the valve surfaces close when the valve piston is displaced due to the applied control pressure depending on the displacement position of the valve piston in the valve cylinder associated with the control pressure, form a valve opening that is open to different extents and, corresponding to the valve opening, the working pressure can be finely adjusted as a function of the control pressure.
  • a working fluid pressure by means of a control fluid in particular in a control valve arrangement according to the invention for indirect pneumatic control, preferably for a pneumatically operated vane motor of a hoist, but at least by means of a control valve arrangement with two pneumatic valve units arranged one behind the other, each with one arranged inside a valve cylinder Valve piston, is initially a Working pressure is applied to a working fluid inlet of the control valve arrangement by means of a working fluid and a control pressure is set in a control fluid, in particular by means of a sensitive valve of a manual control, and a control fluid inlet of the control valve arrangement is loaded with the control pressure.
  • the control fluid which is under the control pressure, is introduced into a respective control pressure chamber of a first and a second pneumatic valve unit, with the control fluid being able to move a valve piston, which is pretensioned to a closed position by a spring element and is arranged inside a valve cylinder, to an open position.
  • the first valve piston By applying any desired control pressure in the first control pressure chamber, the first valve piston is shifted from the closed to the open position, as a result of which the working fluid can flow through a working fluid channel connected to the working fluid inlet through the first, open valve unit to the second valve unit.
  • the application of the control pressure in the second control pressure chamber leads to a displacement of the second valve piston against the force of the spring element into a position of the valve piston in the valve cylinder associated with the control pressure between the closed and the open position, as a result of which the working fluid flows through the working fluid channel in the second valve unit between flows through two opposing valve faces that are angled relative to one another and extend along the displacement direction on the surface of the valve cylinder and the valve piston, with a valve opening formed between the valve faces in the working fluid channel being adjustable in fine steps as a function of the control pressure.
  • control valve arrangement according to the invention and the method according to the invention enable precise, sensitive and stepless control in a particularly simple manner, with the pressure of the working fluid at the outlet being able to be controlled proportionally to the pressure of the control fluid over a wide range, for example.
  • a variation of the pressure of the working fluid during operation is made possible in a simple manner by adjusting the pressure of the control fluid, whereby, for example, the speed of a motor of a hoist operated by the working fluid can be varied continuously and sensitively.
  • the height of the hoist or the distance to the manual control dependent power loss avoided.
  • the control valve arrangement is basically a structural unit within which the pressure of a working fluid that is passed through and possibly blocked can be controlled by means of the pressure of a control fluid.
  • the control valve arrangement can be an independent device and can be arranged in particular in a supply line for a working fluid to an actuator, in particular a pneumatic motor.
  • the control valve arrangement can also be part of a further device and, in particular, can be integrated in a hoist.
  • the control valve arrangement is an exclusively pneumatically operated device, i.e. no further operating medium and/or no electricity is required for operation.
  • Each of the pneumatic valve units comprises at least one valve, preferably exactly one valve, which can be switched over or controlled by means of a fluid pressure, in particular a gas pressure.
  • Each valve unit is particularly preferably formed by a valve that is operated exclusively pneumatically, with this preferably not excluding any spring elements inside the valve unit, but particularly preferably only relating to operation from the outside.
  • the first and second valve units are arranged, preferably directly adjacent to one another, in a common housing, with the two valve cylinders particularly preferably being arranged parallel to one another and/or next to one another and very particularly preferably being identical to one another in terms of length and/or diameter.
  • the valve units are arranged functionally one behind the other, i.e. the working fluid fed to the control valve arrangement first reaches the first valve unit and then, preferably with the first valve unit in an open position, reaches the second valve unit.
  • the pressure fluids, the working fluid and/or the control fluid can in principle be any liquid or any gas. Although operation with a hydraulic working and / or control fluid is conceivable, but a purely pneumatic operation is preferred.
  • the pressurized fluids are particularly preferably compressed air.
  • the pressure of the working and/or control fluid can be selected as desired.
  • the pressure of the working or operating fluid provided is preferably between 0 bar and 10 bar, particularly preferably a maximum of 6 bar and very particularly preferably exactly 6 bar, so that a constant pressure of about 6 bar is present at the working fluid inlet of the control valve arrangement.
  • the maximum control pressure ie the pressure of the control fluid, is preferably also 6 bar, with the control pressure being particularly preferably variable between 1 bar and 6 bar by means of a control valve, in particular in a manual control.
  • a pressure of at most 6 bar and preferably between 1 bar and 6 bar is also present at the control fluid inlet of the control valve arrangement.
  • the basic task of the working fluid channel is to connect the working fluid inlet to the outlet for the working fluid within the control valve arrangement and to direct the control fluid through both valve units in such a way that the flow rate or the volume flow of the working fluid can be changed by means of both valve units.
  • the working fluid channel preferably runs through a blocking and control area of the two valve units and in particular through the respective valve opening, which is formed by the two valve surfaces of the valve cylinder and the valve piston.
  • the working fluid channel preferably connects the first and second valve units to one another in such a way that the working fluid can flow directly from the first into the second valve unit.
  • no further components, in particular no valves and/or branches, are arranged in the working fluid channel between the first and the second valve unit.
  • the spring element can be any desired component or any desired subassembly which is suitable for prestressing the valve piston within the valve cylinder towards a closed position of the valve unit.
  • the spring element is preferably a compression spring, particularly preferably a spiral spring, and/or is formed in one piece.
  • one side of the spring element is preferably supported against an end face or end face of the valve cylinder and/or the other side of the spring element is supported on one end or an end face of the valve piston.
  • One end of the spring element is very particularly preferably at least partially in a bore of the valve piston arranged.
  • the borehole is also preferably arranged at the end or on the end face of the valve piston and/or has, in particular, a depth selected in such a way that the spring element is pressed completely into the borehole and the end face of the valve piston then comes into contact with an end face of the valve cylinder can, whereby the maximum displaceability of the valve piston in relation to the valve cylinder is set in this direction in a particularly simple manner.
  • the strength of the first spring element is preferably selected in such a way that the valve piston reliably closes the working fluid channel when there is no pressure from the control fluid and particularly preferably at the same time in such a way that when a predetermined minimum pressure of the control fluid is reached, preferably from 1.2 bar to 1.3 bar, the Valve piston is pressed against the force of the spring element in the direction of the open position in the valve cylinder, that full opening is made possible by means of the increasing pressure of the working fluid in the first valve unit.
  • the minimum pressure for opening the valve piston can also be selected in any other way.
  • the strength of the second spring element is preferably chosen such that the valve piston is displaced to the desired extent at a predetermined control pressure, in particular a complete displacement exactly within the possible pressure limits of the control pressure, for example between 1 bar and 6 bar. So that the pressure of the working fluid can be controlled by means of the control valve arrangement, at least the second control pressure chamber must be completely separated from the working fluid channel.
  • the first control pressure chamber is preferably also completely separated from the working fluid channel.
  • any control pressure or any control pressure above a minimum pressure in the first control pressure chamber is sufficient to fully open the first valve unit.
  • the first valve unit is thus operated upstream of the second valve unit as a check valve and advantageously ensures, among other things, that no permanent pressure is applied to the second valve unit when no control pressure is acting on the control valve arrangement.
  • the first valve unit forms a safety valve in order to offer double security alongside the second valve unit against an undesired release of working pressure at the outlet.
  • the first valve unit can preferably only switch between a closed and an open state switched, ie it is a two-state valve.
  • the second valve unit is also preferably formed in such a way that it can completely block the working fluid.
  • the second valve unit has a valve opening that can be adjusted by moving the valve piston in the valve cylinder.
  • the valve opening is formed on one side by a valve face of the valve piston and on an opposite side by a valve face of the valve cylinder.
  • the two valve surfaces are arranged at an angle to one another, so that the distance between the two valve surfaces increases or decreases when the piston is displaced.
  • each of the valve surfaces extends at least in sections along the direction of displacement on a surface of the valve piston or valve cylinder.
  • valve unit With a suitable selection of the spring strength of the valve unit, it is possible to provide a specific position of the valve piston in the valve cylinder between the closed and the open position for every possible control pressure, so that the working pressure can be finely adjusted in accordance with the valve opening as a function of the control pressure.
  • At least one of the two valve surfaces of the second valve unit in particular the valve surface of the valve piston, has at least two, preferably exactly two, consecutive sections, with the angle between the valve surface of the valve piston and the opposite valve surface of the valve cylinder being particularly preferably first section following the closed position is smaller than the angle of the valve surface of the valve piston and the opposite valve surface of the valve cylinder in the second section adjoining the open position, as a result of which particularly sensitive starting and slow lifting and lowering of a hoist is possible.
  • One of the two valve surfaces preferably has a changing angle between the first and the second section, and the other valve surface is particularly preferably formed without a change in angle.
  • the two sections of a valve surface are preferably clearly separated from one another, ie the angle between the sections does not change continuously, but rather abruptly or at a position.
  • the angle of the valve faces in the second section is at least twice as large, more preferably at least five times as large, and most preferably at least ten times as large as the angle of the valve faces in the first section.
  • the diameter of the valve piston or the distance between the two opposing valve surfaces is preferably at least twice, particularly preferably at least five times and very particularly preferably at least ten times as large as in the first section.
  • both sections are formed in such a way that they allow the flow rate of the working fluid to be controlled between a fully blocked state and a fully opened state, with a slow and sensitive start-up initially being possible and, with a higher control pressure, a load being lifted quickly using a hoist.
  • the two sections can also be controlled to the closed and to the open state.
  • the two valve surfaces in the first and/or second section are preferably formed so as to run linearly, at least in relation to one another, with the angle between the two valve surfaces of the first section preferably being between 0.1° and 15°. more preferably between 1° and 10° and most preferably between 2° and 7° and the angle of the second section is between 5° and 85°, more preferably between 10° and 75° and most preferably between 20° and 65° .
  • the angle in the first section is particularly preferably 2° and/or the angle in the second section is 45°.
  • both valve surfaces preferably extend in the first and/or second section at a constant angle to one another along the surface of the valve cylinder or the valve piston, so that the distance between the two valve surfaces increases continuously, in particular from the closed position to the open position.
  • One embodiment of the control valve arrangement provides that at least one of the two valve surfaces in the first and/or second section is designed to run non-linearly, with the angle between the two opposite valve surfaces of the valve piston and the valve cylinder preferably increasing between the closed and the open position and thereby increasing the angle of the first section is still preferred between 0.1° and 15°, more preferably between 1° and 10° and most preferably between 2° and 7° and the angle of the second section between 5° and 85°, more preferably between 10° and 75° and entirely more preferably between 20° and 65°.
  • one of the valve surfaces of the valve piston or of the valve cylinder is designed to run non-linearly in one or both sections, while the opposite valve surface of the valve cylinder or of the valve piston runs linearly.
  • valve surface of the valve piston or of the valve cylinder is arranged parallel to the adjustment direction of the valve piston in the valve cylinder, while the other, opposite valve surface is arranged at an angle thereto with a linear or non-linear course is.
  • An embodiment with a profile of the valve surface with a first linear section with a small angle and a second linear section with a larger angle is particularly preferred.
  • the first section and/or the second section of the valve surfaces extends over at least 15%, preferably at least 25%, particularly preferably at least 30% and very particularly preferably over at least 40% of the maximum adjustment path of the valve piston in relation to the valve cylinder, whereby a particularly sensitive control can be achieved.
  • the first section also preferably extends over a maximum of 80%, preferably 60%, particularly preferably 50% and very particularly preferably 40% of the maximum adjustment path.
  • both sections preferably extend together over at least 50%, particularly preferably at least 75% and very particularly preferably at least 80% of the maximum adjustment length of the valve piston.
  • control valve arrangement is preferred in which at least the second valve piston, preferably also the first valve piston, is formed rotationally symmetrically about an axis along the adjustment direction and the corresponding one Valve cylinder has a round cross section, so that the valve opening has the shape of an annular gap.
  • at least one valve surface preferably has a conical shape, while the second valve surface is also preferably formed cylindrically or else conically.
  • control valve arrangement in which the first and/or second control pressure chamber is arranged in the area of the end of the respective valve piston opposite the spring element and/or the working fluid channel in the first and/or in the second valve unit is located between the area of the spring element and the Area of the control pressure chamber is arranged.
  • the working fluid channel particularly preferably surrounds the respective valve piston within the valve cylinder on all sides in sections. Furthermore, the working fluid channel is preferably formed in sections by the valve cylinder.
  • a manual control unit is arranged in front of the control fluid inlet, which has a manual regulator, by means of which the control pressure of the control fluid can be continuously regulated, the manual regulator particularly preferably comprising a manually operated gas valve, by means of which the control pressure can be continuously and sensitively adjusted.
  • control valve arrangement preferably has exactly one single control fluid inlet, which is connected to the two control pressure chambers inside the control valve arrangement, so that the control pressure is always the same in both control pressure chambers.
  • control valve arrangement also has exactly one working fluid inlet and/or one working fluid outlet.
  • a first and a second valve unit 2, 3 are arranged parallel to each other in a common housing.
  • Each of the two valve units 2, 3 is designed as a spring-loaded, pneumatically operated valve.
  • a displaceable valve piston 9, 10 is arranged in a valve cylinder 7, 8 in each of the valve units 2, 3 in such a way that a pressure fluid, in particular compressed air, conducted through the valve unit 2, 3 can be , 10 can be blocked or regulated.
  • valve piston 9, 10 is biased towards a closed position on one side by a spiral spring 11, 12, one end of the spiral spring 11, 12 being supported against a round end face of the valve cylinder 7, 8, while the other end is within a bore in the Valve piston 9, 10 is fixed.
  • a control pressure chamber 13, 14 is formed in the valve cylinder 7, 8.
  • the control pressure chambers 13, 14 of both valve units 2, 3 are jointly connected to an inlet for a control compressed air flow, so that a pressure can be built up in the control pressure chamber 13, 14, which counteracts the spring tension of the spiral spring 11, 12 and by acting on the end face of the valve piston 9, 10 allows the valve piston 9, 10 to be displaced with the control pressure.
  • the control valve unit 1 has a working compressed air inlet 4 and a corresponding one Outlet 5, which provides a pressure-controlled flow of compressed air for the vane motor of the hoist.
  • the outlet 5 is connected to the working compressed air inlet 4 via a working compressed air duct 6, with the working compressed air duct 6 leading one behind the other through both valve units 2, 3 and being able to be blocked and regulated in each case by means of the valve units 2, 3 in a blocking and control area 15.
  • a valve face 16, 17 is arranged on the second valve piston 10 and the associated valve cylinder 8, which face one another in the closed state of the valve unit 2, 3. Both valve surfaces 16, 17 are arranged at an angle to one another in such a way that when the valve piston 10 is displaced in the valve cylinder 8 with increasing displacement, an enlarging valve opening is formed in the form of an annular gap.
  • a control valve arrangement 1 is shown with both valve units 2, 3 in the closed position, so that the first valve unit 2 already shuts off the working compressed air flow shortly after the working compressed air inlet 4 and no pressure is applied to the second valve unit 3 in the area of the working compressed air channel 6.
  • this state of the control valve arrangement 1 there is also no control pressure or the control pressure of the control compressed air in the control pressure chambers 13, 14 is below a specified threshold value of approximately 1.2 bar for opening the valve units 2, 3.
  • a control valve arrangement 1 is shown in a state that occurs only briefly or exactly when a threshold value of the control pressure for opening the valve units 2, 3 is reached.
  • the first valve unit 2 is fully open while the second valve unit 3 is still closed.
  • the control pressure present in the first control air pressure chamber 13 counteracts the first spiral spring 11 to such an extent that the valve opening of the first valve unit 2 is just opened by the two valve surfaces 16, 17 of the first valve unit 2 coming out of contact.
  • the second valve piston 10 of the second valve unit 3 is now also pushed towards the open position against the spring force of the spiral spring 12, the spring force being selected such that in a predefined pressure range, preferably between 1 bar and 6 bar, the valve piston 10 over the max Adjustment path W is shifted.
  • valve surfaces 16, 17 of the second valve unit 3 are formed with an angle a, b that changes within the control surface 17 of the valve piston 10 (see Fig 2 ).
  • the valve surface 16 of the valve cylinder 8 is formed as a linearly extending cylinder surface as part of the wall of the valve cylinder 8 .
  • the valve surface 17 of the valve piston 10 has two mutually angled sections A, B, which are each also arranged at an angle a, b to the opposite valve surface 16 . Both sections A, B have a linear course.
  • the angle a of the first section of the valve surface 17 to the opposite valve surface 16 is 5°, while the corresponding angle b of the second section B is 45°.
  • the two sections A, B extend over 85% of the maximum adjustment path W of the valve piston 10 in the valve cylinder 8.
  • a control valve arrangement 1 is shown with the first valve unit 2 in the fully open position and the second valve unit 3 in a partially open position, the working compressed air being guided through an annular gap formed by the control surfaces 16, 17 of the second valve unit 3 and a reduced volume flow through this annular gap can flow through the working compressed air channel 6 from the working compressed air inlet 4 to the outlet 5 of the control valve arrangement.
  • FIG 5 Finally, a control valve arrangement 1 is shown with both valve units 2, 3 in the fully open position, the working compressed air being able to flow unhindered through the control surfaces 16, 17 of the two valve units 2, 3 through the working compressed air channel 6 from the working compressed air inlet 4 to the outlet 5 of the control valve arrangement.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Fluid Pressure (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
EP19704558.6A 2018-02-02 2019-01-30 Steuerventilanordnung zur indirekten pneumatischen steuerung und verfahren zum steuern eines arbeitsfluiddrucks Active EP3746662B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
HRP20230778TT HRP20230778T1 (hr) 2018-02-02 2019-01-30 Sklop kontrolnog ventila za neizravnu pneumatsku kontrolu i postupak za kontrolu tlaka radne tekućine
RS20230633A RS64404B1 (sr) 2018-02-02 2019-01-30 Sklop upravljačkog ventila za indirektno pneumatsko upravljanje i postupak za upravljanje pritiskom radnog fluida

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018102397.9A DE102018102397A1 (de) 2018-02-02 2018-02-02 Steuerventilanordnung zur indirekten pneumatischen Steuerung
PCT/EP2019/052247 WO2019149751A1 (de) 2018-02-02 2019-01-30 Steuerventilanordnung zur indirekten pneumatischen steuerung und verfahren zum steuern eines arbeitsfluiddrucks

Publications (3)

Publication Number Publication Date
EP3746662A1 EP3746662A1 (de) 2020-12-09
EP3746662C0 EP3746662C0 (de) 2023-06-07
EP3746662B1 true EP3746662B1 (de) 2023-06-07

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EP19704558.6A Active EP3746662B1 (de) 2018-02-02 2019-01-30 Steuerventilanordnung zur indirekten pneumatischen steuerung und verfahren zum steuern eines arbeitsfluiddrucks

Country Status (13)

Country Link
US (1) US11493061B2 (zh)
EP (1) EP3746662B1 (zh)
CN (1) CN111742151B (zh)
AU (1) AU2019216277B2 (zh)
CA (1) CA3089166A1 (zh)
DE (1) DE102018102397A1 (zh)
ES (1) ES2954844T3 (zh)
HR (1) HRP20230778T1 (zh)
HU (1) HUE063189T2 (zh)
PL (1) PL3746662T3 (zh)
RS (1) RS64404B1 (zh)
RU (1) RU2020128699A (zh)
WO (1) WO2019149751A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021121466A1 (de) * 2021-08-18 2023-02-23 J.D. Neuhaus Holding Gmbh & Co. Kg Handsteuerung zur indirekten Steuerung eines fluidbetriebenen Hebezeugs sowie fluidbetriebenes Hebezeug

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Also Published As

Publication number Publication date
AU2019216277A1 (en) 2020-08-06
AU2019216277B2 (en) 2024-05-09
CA3089166A1 (en) 2019-08-08
US20200392972A1 (en) 2020-12-17
EP3746662C0 (de) 2023-06-07
RS64404B1 (sr) 2023-08-31
PL3746662T3 (pl) 2023-10-30
CN111742151A (zh) 2020-10-02
DE102018102397A1 (de) 2019-08-08
CN111742151B (zh) 2023-02-03
EP3746662A1 (de) 2020-12-09
US11493061B2 (en) 2022-11-08
WO2019149751A1 (de) 2019-08-08
HRP20230778T1 (hr) 2023-10-27
ES2954844T3 (es) 2023-11-27
RU2020128699A (ru) 2022-03-02
HUE063189T2 (hu) 2023-12-28

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