EP3746662A1 - Control valve assembly for an indirect pneumatic control, and method for controlling a working fluid pressure - Google Patents

Control valve assembly for an indirect pneumatic control, and method for controlling a working fluid pressure

Info

Publication number
EP3746662A1
EP3746662A1 EP19704558.6A EP19704558A EP3746662A1 EP 3746662 A1 EP3746662 A1 EP 3746662A1 EP 19704558 A EP19704558 A EP 19704558A EP 3746662 A1 EP3746662 A1 EP 3746662A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
working fluid
pressure
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
EP19704558.6A
Other languages
German (de)
French (fr)
Other versions
EP3746662B1 (en
EP3746662C0 (en
Inventor
Piotr KRUPNIK
Simon Brose
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.)
J D Neuhaus Holding & Co KG GmbH
Original Assignee
J D Neuhaus Holding & Co KG GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by J D Neuhaus Holding & Co KG GmbH filed Critical J D Neuhaus Holding & Co KG GmbH
Priority to HRP20230778TT priority Critical patent/HRP20230778T1/en
Priority to RS20230633A priority patent/RS64404B1/en
Publication of EP3746662A1 publication Critical patent/EP3746662A1/en
Application granted granted Critical
Publication of EP3746662B1 publication Critical patent/EP3746662B1/en
Publication of EP3746662C0 publication Critical patent/EP3746662C0/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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 assembly for indirect pneumatic control is
  • Control valve arrangements for pneumatic control in a variety of configurations from the prior art are known from the prior art and are used in particular for controlling pneumatic actuators.
  • a special field here concerns the pneumatic control of pneumatically operated motors of hoists.
  • the pressure of the working fluid is directly controlled before the supply line to the pneumatically operated engine.
  • the compressed air provided for the drive is typically passed 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 endure the full working pressure of the working fluid, are relatively thick and heavy, making them difficult to handle and complicating operation.
  • Wei terhin leads a correspondingly long hose between the hand control and hoist to the hose length increasingly greater power losses and to a control delay, whereby a precise and sensitive control of a load on the hoist is no longer possible.
  • indirect controls are known from the prior art, in which the Working fluid is connected directly to a control valve assembly on the engine, wherein the control by means of a control fluid, usually also compressed air at a lower pressure than the pressure of the working fluid, takes place. It is common that by means of applied to a manual control fluid control only switching on and Ausschal th of the working fluid by means of the control valve assembly on the pneumatic motor, while the working pressure and thus the speed of the hoist are fixed and adjustable by means of a screw on the control valve assembly. This, however, has the disadvantage that a change in the speed of the hoist is not readily possible and thus only a slow start and sensitive lifting or alternatively a rapid lifting of loads is possible, please include. In particular, when transporting heavy loads over high altitudes but both a high lifting speed, as well as a sensitive control for lifting and stopping the load is necessary.
  • Each of the two valve units is provided with a valve piston which is arranged within a valve cylinder and which is displaceable between an open and a closed position, with each of the two valve pistons being preloaded toward the closed position of the valve unit.
  • spring element acts.
  • Both valve units furthermore each have a control pressure chamber connected to the control fluid inlet for acting on the respective valve piston with a control pressure counteracting the bias of the spring element in order to move the valve piston against the force of the spring element into an at least partially open position.
  • the first valve unit is formed such that upon application of any control pressure greater than o bar in the control pressure chamber, the valve piston is moved from the closed to a fully open position.
  • the second valve unit in a blocking and control range of the working fluid channel, two opposing, mutually angled valve surfaces on the surface of the Ven tilzylinders and the valve piston extending along the direction of displacement are arranged to each other such that the valve surfaces when moving the Ventilkol bens due to applied control pressure in dependence of the control pressure associated displacement position of the valve piston in the valve cylinder a difference Lich wide open valve opening form and according to the valve opening of the Ar beits horr depending on the control pressure is finely adjustable.
  • the invention also relates to a hoist with a pneumatically operated Lamel lenmotor and arranged in front, control valve arrangement according to the invention.
  • a working pressure is applied to a working fluid inlet by means of a working fluid and a control pressure in a control fluid, in particular by means of a sensitive valve of a manual control, set as well as a control fluid inlet loaded with the control pressure.
  • the ste is under the control pressure rising control fluid is introduced into a respective control fluid chamber of two pneumatic valve units, wherein the control fluid can move a biased by a spring element to a closed position, disposed within a valve cylinder valve piston to an open position.
  • the first valve piston by applying any control pressure in the first control pressure chamber, the first valve piston 29o ben from the closed to the open position, whereby the working fluid can flow through a connected to the working fluid inlet working fluid passage 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 Fe derelements in a control pressure associated position of the valve piston in the valve cylinder between the closed and the open position, whereby the working fluid through the working fluid channel in the second Valve unit between two opposing, mutually angled and on the surface of the Ventilzy Linders and the valve piston along the direction of displacement extending Ventilflä chen flows through, wherein a formed between the valve surfaces valve opening in the working fluid passage in accordance with the control pressure is correspondingly finely adjustable.
  • control valve arrangement according to the invention and the inventive method allow in a particularly simple manner a precise, sensitive and stepless Steue tion, wherein the pressure of the working fluid can be controlled at the outlet, for example, over a wide range proportional to the pressure of the control fluid.
  • a variation of the pressure of the working fluid in operation is made possible by a pressure adjustment of the control fluid in a simple manner, whereby, for example, the speed of a powered by the working fluid motor of a hoist is continuously and sensitively variable.
  • indirect control by means of a control fluid dependent on the hoist altitude and the distance to the manual control power loss is avoided.
  • control valve arrangement is an assembly within which the pressure of a working fluid which has passed through and possibly is blocked can be controlled by means of the pressure of a control fluid.
  • the control valve arrangement is fiction, according to a device for indirect control.
  • the Steuerventilan Regulation an independent device, and in particular in a supply line for a working fluid to an actuator, in particular a pneumatic motor, be arranged.
  • the control valve arrangement can also be part of a further device and in particular be integrated in a hoist.
  • the control valve arrangement is preferably an exclusively pneumatically operated device, ie no further operating medium and / or electricity is necessary for operation.
  • Each of the pneumatic valve units comprises at least one, preferably exactly one valve, which can be switched or controlled by means of a fluid, in particular a gas pressure.
  • each valve unit is formed by a valve which is operated exclusively pneumatically, which preferably excludes no spring elements in the interior of the valve unit, but particularly before given kart only on the operation from the outside.
  • the first and second valve unit are, preferably immediately adjacent to each other, in a common housing is arranged, more preferably, the two valve cylinders are arranged parallel to each other and / or side by side and very particularly preferably with respect to length and / or diameter identical to each other.
  • the Venti lein spur are functionally arranged one behind the other, that is, that the Steuerventilanord tion supplied working fluid first to the first valve unit and then, preferably with the first valve unit in an open position, enters the second valve unit.
  • the working fluid and / or the control fluid it may in principle be any liquid or any gas. Although an operation with a hydraulic working and / or control fluid is conceivable, however, a purely pneumatic operation is preferred. Particularly preferably, the pressurized fluids are each compressed air.
  • the pressure of the working and / or control fluid can be chosen as desired. Preferably, the pressure of the working or operating fluid provided is between 0 bar and 10 bar, more preferably at most 6 bar and most preferably exactly 6 bar, so that a constant pressure of about 6 bar is applied to 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, the control pressure FITS preferred between 1 bar and 6 bar by means of a control valve, in particular in a manual control, is variable. Accordingly, the control fluid is also preferably Inlass the control valve assembly, a pressure of at most 6 bar and preferably between 1 bar and 6 bar.
  • the working fluid channel has in principle the task of connecting the working fluid inlet to the outlet for the working fluid within the control valve assembly and thereby to guide the control fluid through both valve units such that the flow rate or the volume flow of the working fluid by means of both valve units is changed derbar.
  • the working fluid channel preferably extends through in each case a blocking and control region of the two valve units and in particular by the respective valve opening, which is formed by the two valve surfaces of the valve cylinder and the Ventilkol ben.
  • the working fluid channel connects the first and second valve units with each other such that the working fluid can flow directly from the first to 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 may in principle be any component or any construction group which is suitable to bias the valve piston within the valve cylinder to a closed position of the valve unit.
  • the Federele element is a compression spring, more preferably a coil spring, and / or integrally formed.
  • one side of the spring element is supported against a front or end side of the valve cylinder and / or the other side of the spring element at one end or an end face of the valve piston.
  • one end of the spring element is arranged at least in sections in a bore of the Ventilkol bens.
  • the bore is arranged at the end or on the end face of the valve piston and / or in particular has a depth selected so that the spring element are completely pressed into the bore and then the end face of the valve piston come into abutment with an end face of the valve cylinder can, which is determined in a particularly simple manner, the maximum displaceability of the valve piston with respect to the valve cylinder in this direction.
  • the strength of the first spring element is selected such that the Ventilkol ben reliably closes the working fluid channel without applied pressure of the control fluid and particularly preferably at the same time such that upon reaching a predetermined minimum pressure of the control fluid, preferably from 1.2 bar to 1.3 bar, the valve piston against the force of the spring element is pressed so far in the direction of the open position in the valve cylinder, that a complete opening means the increasing pressure of the working fluid in the first valve unit is made possible.
  • the minimum pressure for opening the valve piston can also be chosen differently.
  • the strength of the second spring element is selected such that a displacement of the valve piston to a desired extent at a predetermined control pressure, in particular a complete displacement exactly within the posi chen pressure limits of the control pressure, for example between 1 bar and 6 bar.
  • a control of the pressure of the working fluid by means of the control valve arrangement is possible, at least the second control pressure chamber must be completely separated from the Häfluidka channel.
  • the first control fluid chamber is also completely separated from the working fluid channel.
  • an arbitrarily strong control pressure or any control pressure above half a minimum pressure in the first control pressure chamber is sufficient to open the first Ventilein unit completely.
  • the first valve unit is thus operated upstream as a check valve of the second valve unit and provides u.a.
  • no permanent pressure is applied to the second valve unit when no control pressure acts on the control valve assembly.
  • the first valve unit forms a safety valve to provide a double safety next to the second valve unit against an unwanted desired release of working pressure at the outlet.
  • the first valve unit can only be switched between a closed and an open state, that is, it is a two-state valve.
  • the second valve unit is preferably formed such that it can completely block the working fluid.
  • the second valve unit has a valve opening which can be adjusted by displacing the valve piston in the valve cylinder.
  • the valve opening is formed on one side by a valve surface of the valve piston and on an opposite side by a valve surface of the valve cylinder.
  • the two valve surfaces are arranged angled to each other, so that the ex-position of both valve surfaces in a displacement of the piston increases or verklei nert.
  • each of the Ventilflä chen extends on a surface of the valve piston and the valve cylinder at least from sections along the direction of displacement.
  • At least one of the two valve surfaces of the second valve unit has at least two, preferably exactly two consecutive sections, wherein particularly preferably the angle between the valve surfaces in the first, the closed position following section is smaller than the angle of the valve surfaces in the second, adjacent to the open position area, whereby a particularly sensitive start and slow lifting and lowering is possible with a hoist.
  • one of the two valve surfaces preferably has a changing angle between the first and the second section, and particularly preferably the other valve surface is formed without changing the angle.
  • the two sections of a valve surface are clearly separated from each other, ie, the angle between the sections does not change continuously, but suddenly or at a position.
  • the angle of the valve surfaces 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 surfaces in the first section.
  • the diameter of the valve piston or the distance of the two opposing valve surfaces at least twice, more preferably at least five times and most preferably at least ten times as large as in the first section.
  • both sections are formed such that they allow control of the flow rate of the working fluid between a fully locked state and a fully open state, initially a slow and sensitive Anfah ren and higher control pressure a rapid lifting of a load by means of a hoist is possible.
  • the two sections in addition to the ge closed and the open state can be controlled.
  • the two valve surfaces in the first and / or second section at least in relation to each other, preferably each formed linearly extending, wherein the angle between the two valve surfaces of the first section preferably between o, i ° and 15 0 , more preferably between i ° and io ° and most preferably between 2 ° and 7 ° and the angle of the second section between 5 0 and 85 °, more preferably between 10 ° and 75 0 and most preferably between 20 ° and 6 ° ,
  • both valve surfaces extend in the first and / or second portion at a constant angle to each other along the surface of the valve cylinder or the valve piston, so that the distance between the two valve surfaces continuously increases, in particular from the closed position to the open position.
  • An embodiment of the control valve arrangement provides that at least one of the two valve surfaces in the first and / or second portion is formed non-linearly extending, wherein the angle between the two opposite valve surfaces of the Ventilkol ben and the valve cylinder preferably increases between the closed and the geöff Neten position and while the angle of the first portion continues to be given between o, i ° and 15 0 , more preferably between i ° and io ° and very FITS preferred between 2 0 and 7 0 and the angle of the second section between 5 0 and 85 ° , more preferably between io ° and 75 0 and most preferably between 20 ° and 6s °.
  • one of the valve surfaces of the valve piston or the valve cylinder is formed non-linearly extending in one or both sections, while the opposite valve surface of the valve cylinder or the valve piston is linear.
  • a profile of the valve surfaces in relation to one another is preferred with a valve opening which increases toward the open position of the valve piston. It is also generally preferred that in at least one section and more preferably in both portions of the valve surface of the valve piston or the valve cylinder is arranged parallel to the displacement 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. Particularly preferred 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.
  • the first section and / or the second section of the valve surfaces extends over at least 15%, preferably at least 25%, more preferably at least 30% and most preferably over at least 40% of the maximum displacement of the valve piston with respect to the valve cylinder, whereby a particularly sensitive control tion can be achieved.
  • the first section extends over a maximum of 80%, preferably 60%, more preferably 50% and most preferably before given 40% of the maximum adjustment.
  • both sections together extend over at least 50%, more preferably at least 75%, and most 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 rotationally symmetrical about an axis along the adjustment and the corresponding 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 cylindrical or conical.
  • control valve arrangement in which the first and / or second control pressure chamber in the region of the spring element pridelie ing end of the respective valve piston is arranged and / or the Facultyfluidka channel in the first and / or in the second valve unit between the region of the spring element and the region of the control pressure chamber is arranged.
  • the working fluid channel surrounds the respective valve piston within the Valve cylinder sections on all sides. Further preferably, the working fluid channel is formed in sections by the valve cylinder.
  • a hand control unit is arranged in front of the control fluid inlet, which has a hand controller, by means of which the control pressure of the control fluid is infinitely adjustable, the hand controller particularly preferably comprises a handbetätigbares gas valve by means of which the control pressure is infinitely and sensitively adjustable.
  • control valve arrangement preferably has precisely one single control fluid discharge, which is connected to the two control pressure chambers in the interior of the control valve arrangement, so that the control pressure is always the same in both control pressure chambers.
  • control valve arrangement also has only exactly one working fluid inlet and / or one working fluid outlet.
  • FIG. 2 is an enlarged sectional view of a blocking portion of the second valve unit of the control valve assembly shown in Fig. L,
  • FIG. 3 shows a sectional view of the control valve arrangement shown in FIG. 1 with an opened first valve unit and a closed second valve unit
  • FIG. 4 shows a sectional view of the control valve arrangement shown in FIG. 1 with a fully opened first valve unit and a partially opened second valve unit,
  • Fig. 5 is a sectional view of the control valve assembly shown in Fig. L with two open valve units.
  • control valve assembly l for indirect pneumatic control of the working pressure for a pneumatic vane motor of a hoist are a first and a second valve unit 2, 3 arranged parallel to each other in a common seed housing.
  • Each of the two valve units 2, 3 is formed as a spring-biased, pneumatically operated valve. Accordingly, in each of the valve units 2, 3 a displaceable valve piston 9, 10 arranged in a valve cylinder 7, 8 such that a guided through the valve unit 2, 3 pressure fluid, in particular compressed air, by means of a Oberflä chenabterrorisms the valve cylinder 7,8 and the valve piston 9, 10 can be locked or regulated.
  • the valve piston 9, 10 is biased on one side with a coil spring 11, 12 to a closed position, with one end of the coil spring 11, 12 against a round end face of the valve cylinder 7, 8 is supported, while the other end 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 Steuerdruckkam numbers 13, 14 of both valve units 2, 3 are connected together with an inlet for a control compressed air flow, so that in the control pressure chamber 13, 14, a pressure can be established, which counteracts the spring tension of the coil spring 11, 12 and by an application of the end face of the Valve piston 9, 10 with the control pressure a displacement of the valve piston 9, 10 allows.
  • the control valve unit 1 has a working air inlet 4 and a corresponding outlet 5, which provides a pressure-controlled compressed air flow for the vane motor of the hoist.
  • the outlet 5 is connected via a working compressed air duct 6 to the working air inlet 4, wherein the working compressed air duct 6 in succession through both valve units 2, 3 and in each case by means of the valve units 2, 3 in a blocking and control range 15 can be blocked and regulated.
  • valve surface 16, 17 is arranged in each case, which abut each other in the closed state of the valve unit 2, 3. Both valve surfaces 16, 17 are arranged so bent to each other that when displacing the valve piston 10 in the valve cylinder 8 with increasing displacement, a magnifying valve opening in the form of a Ringspalts forms.
  • control valve assembly 1 shows a control valve arrangement 1 with both valve units 2, 3 in the closed position, so that the first valve unit 2 shuts off the working compressed air flow already shortly after the working compressed air inlet 4 and at the second valve unit 3 no pressure in the area of the working compressed air duct 6 is applied.
  • the control valve assembly 1 is also no control pressure or the control pressure of the control compressed air in the control pressure chambers 13, 14 is below a predetermined threshold value of about 1.2 bar to open the valve units 2, 3rd
  • a control valve assembly 1 is shown in a state which only nearbyfris tig or exactly when a threshold value of the control pressure for opening the valve units 2, 3 occurs.
  • the first valve unit 2 is fully open, while the second valve unit 3 is still closed.
  • the control pressure applied in the first control air pressure chamber 13 counteracts the first spiral spring 11 so far 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 out of contact.
  • the second valve piston 10 of the second valve unit 3 is shifted against the spring force of the coil spring 12 to the open position, wherein the spring force is selected such that in a predefined pressure range, preferably between 1 bar and 6 bar, the Valve piston 10 is moved over the maximum adjustment path W.
  • the Ventilflä surfaces 16, 17 of the second valve unit 3 with a within the control surface 17 of the valve piston 10 changing angle a, b formed (see FIG 2).
  • the valve surface 16 of the valve cylinder 8 as a linearly extending cylindrical surface as part of the Wan PHg of the valve cylinder 8 is formed.
  • the valve surface 17 of the valve piston 10 has two mutually angled sections A, B, which are each 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 Overlying valve surface 16 is 5 0
  • the corresponding angle b of the second section B 45 is 0 .
  • the two sections A, B extend over 85% of the maximum adjustment path W of the valve piston 10 in the valve cylinder 8. In Fig.
  • valve 4 is a control valve assembly 1 with the first valve unit 2 in the completeness dig open position and the second valve unit 3 in a partially open Position shown, wherein the working pressure air is passed 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 pressure air duct 6 from the working air pressure inlet 4 to the outlet 5 of the control valve assembly.
  • FIG. 5 shows a control valve arrangement 1 with both valve units 2, 3 in the fully open position, wherein the working compressed air through the control surfaces 16, 17 of the two valve units 2, 3 passes unhindered through the working compressed air duct 6 from the working air pressure inlet 4 to the outlet 5 of the control valve arrangement can flow.

Abstract

The invention relates to a control valve assembly (1) for an indirect pneumatic control and to a method for controlling a working fluid pressure. The aim of the invention is to provide a control valve assembly (1) and a method for controlling a working fluid pressure using a control fluid, said assembly and method allowing a precise, sensitive, speed-variable control without large output losses and control delays. This is achieved in that the control valve assembly (1) has two pneumatic valve units (2, 3) which are arranged one behind the other; a working fluid inlet (4); a control fluid inlet; a working fluid channel (6) which connects the working fluid inlet (4) to an outlet (5) by means of the two valve units (2, 3); a respective valve piston (9, 10) which is arranged within each valve cylinder (7, 8) of the first and second valve unit (2, 3) and which can be moved between an open position and a closed position; a respective spring element (11, 12) which biases the first and second valve piston (9, 10) towards the closed position; and a respective control pressure chamber (13, 14) which is connected to the control fluid inlet for applying a control pressure to each valve piston (9, 10), said control pressure counteracting the bias of the spring element (11, 12); wherein the first valve unit (2) is produced such that the first valve piston (9) is moved from the closed position to the open position when a control pressure is applied in the first control pressure chamber (13), and two opposite valve surfaces (16, 17) which are angled relative to each other are arranged on the surface of the valve cylinder (8) and the valve piston (10) so as to extend along the movement direction (V) in the second valve unit (3) in a blocking and control region (15) of the working fluid channel (6) such that the valve surfaces (16, 17) form a valve opening that is opened to varying widths when the valve piston (10) is moved in the valve cylinder (8) as a result of a changing control pressure, and the working pressure can be finely adjusted on the basis of the control pressure according to the valve opening.

Description

Beschreibung  description
STEUERVENTILANORDNUNG ZUR INDIREKTEN PNEUMATISCHEN STEUERUNG UND VERFAHREN ZUM STEUERN EINES ARBEITS- CONTROL VALVE ASSEMBLY FOR INDIRECT PNEUMATIC CONTROL AND METHOD FOR CONTROLLING WORKING
FLUIDDRUCKS FLUID PRESSURE
Die Erfindung betrifft eine Steuerventilanordnung zur indirekten pneumatischen Steuerung sowie ein Verfahren zum Steuern eines Arbeitsfluiddrucks mittels einesThe invention relates to a control valve arrangement for indirect pneumatic control and a method for controlling a working fluid pressure by means of a
Steuerfluids in einer Steuerventilanordnung zur indirekten pneumatischen Steuerung. Control fluid in a control valve assembly for indirect pneumatic control.
Aus dem Stand der Technik sind Steuerventilanordnungen zur pneumatischen Steue rung in vielfältiger Ausgestaltung aus dem Stand der Technik bekannt und werden dabei insbesondere zur Steuerung pneumatischer Aktuatoren verwendet. Ein spezielles Gebiet hierbei betrifft die pneumatische Steuerung pneumatisch betriebener Motoren von Hebezeugen. Control valve arrangements for pneumatic control in a variety of configurations from the prior art are known from the prior art and are used in particular for controlling pneumatic actuators. A special field here concerns the pneumatic control of pneumatically operated motors of hoists.
Dabei ist zunächst bekannt, den Motor, insbesondere einen Lamellenmotor, eines Hebezeugs direkt zu steuern, wobei der Druck des Arbeitsfluids, zumeist Druckluft, vor der Zuleitung zum pneumatisch betriebenen Motor direkt geregelt wird. Dazu wird typischerweise die zum Antrieb vorgesehene Druckluft von einem zentralen Anschluss über einen Schlauch zu einer Handsteuereinheit geleitet und von dort zur Position des Motors des Hebezeugs, der zumeist im Bereich einer Hallendecke positioniert ist. Dies macht einen langen Druckluftschlauch wenigstens von der Handsteuerung zum an der Hallendecke angeordneten Hebezeug notwendig. Diese Schläuche, die durchgehend den vollen Arbeitsdruck des Arbeitsfluids aushalten müssen, sind jedoch relativ dick und schwer, wodurch diese schlecht handhabbar sind und die Bedienung erschweren. Wei terhin führt ein entsprechend langer Schlauch zwischen Handsteuerung und Hebezeug zu mit der Schlauchlänge zunehmend größeren Leistungsverlusten sowie zu einer Steuerverzögerung, wodurch eine präzise und feinfühlige Steuerung einer Last am Hebezeug nicht mehr möglich ist. It is initially known to control the engine, in particular a vane motor, a hoist directly, the pressure of the working fluid, usually compressed air, is directly controlled before the supply line to the pneumatically operated engine. For this purpose, the compressed air provided for the drive is typically passed 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. This makes a long compressed air hose at least from the manual control to hoist arranged at the hall ceiling necessary. However, these hoses, which must endure the full working pressure of the working fluid, are relatively thick and heavy, making them difficult to handle and complicating operation. Wei terhin leads a correspondingly long hose between the hand control and hoist to the hose length increasingly greater power losses and to a control delay, whereby a precise and sensitive control of a load on the hoist is no longer possible.
Zudem sind aus dem Stand der Technik indirekte Steuerungen bekannt, bei denen das Arbeitsfluid direkt an eine Steuerventilanordnung am Motor angeschlossen wird, wobei die Steuerung mittels eines Steuerfluids, zumeist auch Druckluft mit einem geringeren Druck als der Druck des Arbeitsfluids, erfolgt. Dabei ist es üblich, dass mittels des an einer Handsteuerung anliegenden Steuerfluids lediglich ein Einschalten und Ausschal ten des Arbeitsfluids mittels der Steuerventilanordnung am pneumatischen Motor erfolgt, während der Arbeitsdruck und somit die Geschwindigkeit des Hebezeugs fest vorgegeben und mittels einer Stellschraube an der Steuerventilanordnung einstellbar sind. Daraus ergibt sich jedoch der Nachteil, dass eine Veränderung der Geschwindigkeit des Hebezeugs nicht ohne weiteres möglich ist und somit nur entweder ein langsames Anfahren sowie feinfühliges Heben oder alternativ ein zügiges Heben von Lasten mög lich ist. Insbesondere beim Transport schwerer Lasten über große Höhen ist aber sowohl eine große Hebegeschwindigkeit, als auch eine feinfühlige Steuerung zum Abheben und Absetzen der Last notwendig. In addition, indirect controls are known from the prior art, in which the Working fluid is connected directly to a control valve assembly on the engine, wherein the control by means of a control fluid, usually also compressed air at a lower pressure than the pressure of the working fluid, takes place. It is common that by means of applied to a manual control fluid control only switching on and Ausschal th of the working fluid by means of the control valve assembly on the pneumatic motor, while the working pressure and thus the speed of the hoist are fixed and adjustable by means of a screw on the control valve assembly. This, however, has the disadvantage that a change in the speed of the hoist is not readily possible and thus only a slow start and sensitive lifting or alternatively a rapid lifting of loads is possible, please include. In particular, when transporting heavy loads over high altitudes but both a high lifting speed, as well as a sensitive control for lifting and stopping the load is necessary.
Es kann daher als Aufgabe der Erfindung angesehen werden, eine Steuerventilanord nung sowie ein Verfahren zum Steuern eines Arbeitsfluiddrucks mittels eines Steuer fluids bereitzustellen, die eine präzise, feinfühlige und geschwindigkeitsvariable Steue rung ohne große Leistungsverluste und Steuerverzögerungen ermöglichen. It may therefore be regarded as an object of the invention to provide a Steuerventilanord tion and a method for controlling a working fluid pressure by means of a control fluids that allow a precise, sensitive and variable speed Steue tion without large power losses and control delays.
Die Aufgabe wird erfindungsgemäß durch eine Steuerventilanordnung gemäß An spruch l sowie ein Verfahren gemäß Anspruch io gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den abhängigen Ansprüchen angegeben. The object is achieved by a control valve arrangement according to claim 1 and a method according to claim io solved. Advantageous developments of the invention are specified in the dependent claims.
Die erfindungsgemäße Steuerventilanordnung zur indirekten pneumatischen Steuerung, insbesondere eines pneumatisch betriebenen Lamellenmotors eines Hebezeugs, umfasst zwei pneumatische, funktional hintereinander angeordnete Ventileinheiten, einen Arbeitsfluideinlass und einen Steuerfluideinlass sowie einen den Arbeitsfluideinlass durch beide Ventileinheiten hindurch mit einem Auslass verbindenden Arbeits fluidkanal, wobei der Auslass insbesondere zum Zuleiten des Arbeitsfluids zu einem Lamellenmotor eines Hebezeugs vorgesehen ist. An jeder der beiden Ventileinheiten ist jeweils ein innerhalb eines Ventilzylinders angeordneter, zwischen einer geöffneten und einer geschlossenen Stellung verschiebbarer Ventilkolben vorgesehen, wobei auf jeden der beiden Ventilkolben ein auf die geschlossene Stellung der Ventileinheit hin vorspan- nendes Federelement wirkt. Beide Ventileinheiten weisen weiterhin jeweils eine mit dem Steuerfluideinlass verbundene Steuerdruckkammer zum Beaufschlagen des jeweiligen Ventilkolbens mit einem der Vorspannung des Federelements entgegenwirkenden Steuerdruck auf, um den Ventilkolben entgegen der Kraft des Federelements in eine zumindest abschnittsweise geöffnete Stellung zu bewegen. The control valve arrangement according to the invention for indirect pneumatic control, in particular a pneumatically operated multi-disk motor of a hoist comprises two pneumatic, functionally successively arranged valve units, a working fluid inlet and a control fluid inlet and the working fluid inlet through both valve units through with an outlet connecting working fluid channel, the outlet in particular for Supplying the working fluid is provided to a vane motor of a hoist. Each of the two valve units is provided with a valve piston which is arranged within a valve cylinder and which is displaceable between an open and a closed position, with each of the two valve pistons being preloaded toward the closed position of the valve unit. nendes spring element acts. Both valve units furthermore each have a control pressure chamber connected to the control fluid inlet for acting on the respective valve piston with a control pressure counteracting the bias of the spring element in order to move the valve piston against the force of the spring element into an at least partially open position.
Dabei ist die erste Ventileinheit derart gebildet, dass beim Anlegen eines beliebigen Steuerdrucks größer als o bar in der Steuerdruckkammer der Ventilkolben von der geschlossenen in eine vollständig geöffnete Stellung verschoben wird. In der zweiten Ventileinheit, in einem Sperr- und Regelbereich des Arbeitsfluidkanals, sind zwei sich gegenüberliegende, zueinander verwinkelte Ventilflächen auf der Oberfläche des Ven tilzylinders und des Ventilkolbens sich entlang der Verschieberichtung erstreckend derart zueinander angeordnet, dass die Ventilflächen beim Verschieben des Ventilkol bens aufgrund des angelegten Steuerdrucks in Abhängigkeit der dem Steuerdruck zugeordneten Verschiebeposition des Ventilkolbens im Ventilzylinder eine unterschied lich weit geöffnete Ventilöffnung bilden und entsprechend der Ventilöffnung der Ar beitsdruck in Abhängigkeit des Steuerdrucks feinstufig einstellbar ist. In this case, the first valve unit is formed such that upon application of any control pressure greater than o bar in the control pressure chamber, the valve piston is moved from the closed to a fully open position. In the second valve unit, in a blocking and control range of the working fluid channel, two opposing, mutually angled valve surfaces on the surface of the Ven tilzylinders and the valve piston extending along the direction of displacement are arranged to each other such that the valve surfaces when moving the Ventilkol bens due to applied control pressure in dependence of the control pressure associated displacement position of the valve piston in the valve cylinder a difference Lich wide open valve opening form and according to the valve opening of the Ar beitsdruck depending on the control pressure is finely adjustable.
Die Erfindung betrifft auch ein Hebezeug mit einem pneumatisch betriebenen Lamel lenmotor und einer davor angeordneten, erfindungsgemäßen Steuerventilanordnung. The invention also relates to a hoist with a pneumatically operated Lamel lenmotor and arranged in front, control valve arrangement according to the invention.
Bei dem erfindungsgemäßen Verfahren zum Steuern eines Arbeitsfluiddrucks mittels eines Steuerfluids, insbesondere in einer erfindungsgemäßen Steuerventilanordnung zur indirekten pneumatischen Steuerung, bevorzugt für einen pneumatisch betriebenen Lamellenmotor eines Hebezeugs, wird zunächst ein Arbeitsdruck mittels eines Arbeits fluids auf einen Arbeitsfluideinlass angelegt und ein Steuerdruck in einem Steuerfluid, insbesondere mittels eines feinfühligen Ventils einer Handsteuerung, eingestellt sowie ein Steuerfluideinlass mit dem Steuerdruck belastet. Das unter dem Steuerdruck ste hende Steuerfluid wird in jeweils eine Steuerfluidkammer von zwei pneumatischen Ventileinheiten eingeleitet, wobei das Steuerfluid einen durch ein Federelement auf eine geschlossene Stellung vorgespannten, innerhalb eines Ventilzylinders angeordneten Ventilkolben auf eine geöffnete Stellung hin verschieben kann. Dabei wird durch das Anlegen eines beliebigen Steuerdrucks in der ersten Steuerdruck kammer der erste Ventilkolben von der geschlossenen in die geöffnete Stellung verscho ben, wodurch das Arbeitsfluid durch einen mit dem Arbeitsfluideinlass verbundenen Arbeitsfluidkanal durch die erste, geöffnete Ventileinheit zur zweiten Ventileinheit strömen kann. Dabei führt das Anlegen des Steuerdrucks in der zweiten Steuerdruck kammer zu einem Verschieben des zweiten Ventilkolbens entgegen der Kraft des Fe derelements in eine dem Steuerdruck zugeordneten Position des Ventilkolbens im Ventilzylinder zwischen der geschlossenen und der geöffneten Stellung, wodurch das Arbeitsfluid durch den Arbeitsfluidkanal in der zweiten Ventileinheit zwischen zwei sich gegenüberliegenden, zueinander verwinkelten und sich auf der Oberfläche des Ventilzy linders und des Ventilkolbens entlang der Verschieberichtung erstreckenden Ventilflä chen hindurchströmt, wobei eine zwischen den Ventilflächen gebildete Ventilöffnung im Arbeitsfluidkanal in Abhängigkeit des Steuerdrucks entsprechend feinstufig einstellbar ist. In the method according to the invention for controlling 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 driven vane motor of a hoist, first a working pressure is applied to a working fluid inlet by means of a working fluid and a control pressure in a control fluid, in particular by means of a sensitive valve of a manual control, set as well as a control fluid inlet loaded with the control pressure. The ste is under the control pressure rising control fluid is introduced into a respective control fluid chamber of two pneumatic valve units, wherein the control fluid can move a biased by a spring element to a closed position, disposed within a valve cylinder valve piston to an open position. In this case, by applying any control pressure in the first control pressure chamber, the first valve piston verscho ben from the closed to the open position, whereby the working fluid can flow through a connected to the working fluid inlet working fluid passage through the first, open valve unit to the second valve unit. In this case, 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 Fe derelements in a control pressure associated position of the valve piston in the valve cylinder between the closed and the open position, whereby the working fluid through the working fluid channel in the second Valve unit between two opposing, mutually angled and on the surface of the Ventilzy Linders and the valve piston along the direction of displacement extending Ventilflä chen flows through, wherein a formed between the valve surfaces valve opening in the working fluid passage in accordance with the control pressure is correspondingly finely adjustable.
Die erfindungsgemäße Steuerventilanordnung sowie das erfindungsgemäße Verfahren ermöglichen in besonders einfacher Weise eine präzise, feinfühlig und stufenlose Steue rung, wobei der Druck des Arbeitsfluids am Auslass beispielsweise über einen weiten Bereich proportional zum Druck des Steuerfluids gesteuert werden kann. Zudem wird in einfacher Weise eine Variation des Drucks des Arbeitsfluids im Betrieb durch eine Druckeinstellung des Steuerfluids ermöglicht, wodurch beispielsweise die Geschwindig keit eines mittels des Arbeitsfluids betriebenen Motors eines Hebezeugs stufenlos und feinfühlig variierbar ist. Weiterhin wird durch die indirekte Ansteuerung mittels eines Steuerfluids ein von der Hebezeughöhe bzw. von dem Abstand zur Handsteuerung abhängiger Leistungsverlust vermieden. Schließlich kommt es auch zu keinen Steuerver zögerungen aufgrund einer direkten Steuerung des Arbeitsfluiddrucks mit einem nach folgenden großen Arbeitsfluidvolumen in einem langen Schlauch oder dergleichen. The control valve arrangement according to the invention and the inventive method allow in a particularly simple manner a precise, sensitive and stepless Steue tion, wherein the pressure of the working fluid can be controlled at the outlet, for example, over a wide range proportional to the pressure of the control fluid. In addition, a variation of the pressure of the working fluid in operation is made possible by a pressure adjustment of the control fluid in a simple manner, whereby, for example, the speed of a powered by the working fluid motor of a hoist is continuously and sensitively variable. Furthermore, by the indirect control by means of a control fluid dependent on the hoist altitude and the distance to the manual control power loss is avoided. Finally, there are also no Steuerver delays due to a direct control of the working fluid pressure with a subsequent large working fluid volume in a long hose or the like.
Bei der Steuerventilanordnung handelt es sich grundsätzlich um eine Baueinheit, innerhalb der der Druck eines durchgeleiteten und ggf. gesperrten Arbeitsfluids mittels des Drucks eines Steuerfluids gesteuert werden kann. Somit handelt es sich erfindungs gemäß um eine Vorrichtung zur indirekten Steuerung. Dabei kann die Steuerventilan ordnung eine eigenständige Vorrichtung und dabei insbesondere in einer Zuleitung für ein Arbeitsfluid zu einem Aktuator, insbesondere einem pneumatischen Motor, ange ordnet sein. Alternativ kann die Steuerventilanordnung aber auch Teil einer weiteren Vorrichtung und dabei insbesondere in einem Hebezeug integriert sein. Bevorzugt ist die Steuerventilanordnung eine ausschließlich pneumatisch betriebene Vorrichtung, d.h., zum Betrieb ist kein weiteres Betriebsmedium und/oder keine Elektrizität notwendig. In principle, the control valve arrangement is an assembly within which the pressure of a working fluid which has passed through and possibly is blocked can be controlled by means of the pressure of a control fluid. Thus, it is fiction, according to a device for indirect control. In this case, the Steuerventilan Regulation an independent device, and in particular in a supply line for a working fluid to an actuator, in particular a pneumatic motor, be arranged. Alternatively, however, the control valve arrangement can also be part of a further device and in particular be integrated in a hoist. The control valve arrangement is preferably an exclusively pneumatically operated device, ie no further operating medium and / or electricity is necessary for operation.
Jede der pneumatischen Ventileinheiten umfasst jeweils wenigstens ein, bevorzugt genau ein Ventil, das mittels eines Fluid-, insbesondere eines Gasdrucks umgeschaltet bzw. gesteuert werden kann. Besonders bevorzugt ist jede Ventileinheit durch ein Ventil gebildet, das ausschließlich pneumatisch betrieben wird, wobei dies bevorzugt keine Federelemente im Inneren der Ventileinheit ausschließt, sondern sich besonders bevor zugt lediglich auf den Betrieb von außen bezieht. Die erste und zweite Ventileinheit sind, bevorzugt unmittelbar aneinander angrenzend, in einem gemeinsamen Gehäuse ange ordnet, wobei besonders bevorzugt die beiden Ventilzylinder parallel zueinander und/oder nebeneinander angeordnet sind und ganz besonders bevorzugt bezüglich Länge und/oder Durchmesser identisch zueinander gebildet sind. Dabei sind die Venti leinheiten funktional hintereinander angeordnet, d.h., dass das der Steuerventilanord nung zugeleitete Arbeitsfluid erst zur ersten Ventileinheit und anschließend, bevorzugt mit der ersten Ventileinheit in einer geöffneten Stellung, in die zweite Ventileinheit gelangt. Each of the pneumatic valve units comprises at least one, preferably exactly one valve, which can be switched or controlled by means of a fluid, in particular a gas pressure. Particularly preferably, each valve unit is formed by a valve which is operated exclusively pneumatically, which preferably excludes no spring elements in the interior of the valve unit, but particularly before given zugt only on the operation from the outside. The first and second valve unit are, preferably immediately adjacent to each other, in a common housing is arranged, more preferably, the two valve cylinders are arranged parallel to each other and / or side by side and very particularly preferably with respect to length and / or diameter identical to each other. The Venti leinheiten are functionally arranged one behind the other, that is, that the Steuerventilanord tion supplied working fluid first to the first valve unit and then, preferably with the first valve unit in an open position, enters the second valve unit.
Bei den Druckfluiden, dem Arbeitsfluid und/oder dem Steuerfluid, kann es sich grund sätzlich um eine beliebige Flüssigkeit oder ein beliebiges Gas handeln. Zwar ist ein Betrieb mit einem hydraulischen Arbeits- und/oder Steuerfluid denkbar, jedoch wird ein rein pneumatischer Betrieb bevorzugt. Besonders bevorzugt sind die Druckfluide jeweils Druckluft. Grundsätzlich kann dabei der Druck des Arbeits- und/oder Steuerfluids beliebig gewählt sein. Bevorzugt beträgt der Druck des bereitgestellten Arbeits- bzw. Betriebsfluids zwischen o bar und io bar, besonders bevorzugt maximal 6 bar und ganz besonders bevorzugt genau 6 bar, sodass am Arbeitsfluideinlass der Steuerventilanord nung ein konstanter Druck von etwa 6 bar anliegt. Der maximale Steuerdruck, d.h., der Druck des Steuerfluids, beträgt bevorzugt ebenfalls 6 bar, wobei der Steuerdruck beson ders bevorzugt zwischen l bar und 6 bar mittels eines Steuerventils, insbesondere in einer Handsteuerung, variierbar ist. Entsprechend liegt bevorzugt auch am Steuerfluide- inlass der Steuerventilanordnung ein Druck von maximal 6 bar und bevorzugt zwischen l bar und 6 bar an. In the pressurized fluids, the working fluid and / or the control fluid, it may in principle be any liquid or any gas. Although an operation with a hydraulic working and / or control fluid is conceivable, however, a purely pneumatic operation is preferred. Particularly preferably, the pressurized fluids are each compressed air. In principle, the pressure of the working and / or control fluid can be chosen as desired. Preferably, the pressure of the working or operating fluid provided is between 0 bar and 10 bar, more preferably at most 6 bar and most preferably exactly 6 bar, so that a constant pressure of about 6 bar is applied to 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, the control pressure FITS preferred between 1 bar and 6 bar by means of a control valve, in particular in a manual control, is variable. Accordingly, the control fluid is also preferably Inlass the control valve assembly, a pressure of at most 6 bar and preferably between 1 bar and 6 bar.
Der Arbeitsfluidkanal hat grundsätzlich die Aufgabe, den Arbeitsfluideinlass mit dem Auslass für das Arbeitsfluid innerhalb der Steuerventilanordnung zu verbinden und dabei das Steuerfluid durch beide Ventileinheiten derart zu leiten, dass die Durchfluss menge bzw. der Volumenstrom des Arbeitsfluids mittels beider Ventileinheiten verän derbar ist. Dazu verläuft der Arbeitsfluidkanal bevorzugt durch jeweils einen Sperr- und Regelbereich der beiden Ventileinheiten und dabei insbesondere durch die jeweilige Ventilöffnung, die durch die beiden Ventilflächen des Ventilzylinders und des Ventilkol bens gebildet wird. Bevorzugt verbindet der Arbeitsfluidkanal die erste und zweite Ventileinheit derart miteinander, dass das Arbeitsfluid unmittelbar von der ersten in die zweite Ventileinheit strömen kann. Besonders bevorzugt sind im Arbeitsfluidkanal zwischen der ersten und der zweiten Ventileinheit keine weiteren Bauteile, insbesondere keine Ventile und/oder Verzweigungen angeordnet. The working fluid channel has in principle the task of connecting the working fluid inlet to the outlet for the working fluid within the control valve assembly and thereby to guide the control fluid through both valve units such that the flow rate or the volume flow of the working fluid by means of both valve units is changed derbar. For this purpose, the working fluid channel preferably extends through in each case a blocking and control region of the two valve units and in particular by the respective valve opening, which is formed by the two valve surfaces of the valve cylinder and the Ventilkol ben. Preferably, the working fluid channel connects the first and second valve units with each other such that the working fluid can flow directly from the first to the second valve unit. Particularly preferably, 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.
Das Federelement kann grundsätzlich ein beliebiges Bauteil oder eine beliebige Bau gruppe sein, die geeignet ist, den Ventilkolben innerhalb des Ventilzylinders auf eine geschlossene Stellung der Ventileinheit hin vorzuspannen. Bevorzugt ist das Federele ment dabei eine Druckfeder, besonders bevorzugt eine Spiralfeder, und/oder einstückig gebildet. Weiterhin bevorzugt ist eine Seite des Federelements gegen eine Stirn- bzw. Endseite des Ventilzylinders und/oder die andere Seite des Federelements an einem Ende bzw. einer Stirnseite des Ventilkolbens abgestützt. Ganz besonders bevorzugt ist ein Ende des Federelements zumindest abschnittsweise in einer Bohrung des Ventilkol bens angeordnet. Ebenfalls bevorzugt ist die Bohrung am Ende bzw. an der Stirnseite des Ventilkolbens derart angeordnet und/oder weist insbesondere eine so gewählte Tiefe auf, dass das Federelement vollständig in die Bohrung eingedrückt werden und dann die Stirnseite des Ventilkolbens mit einer Stirnseite des Ventilzylinders in Anlage kommen kann, wodurch in besonders einfacher Weise die maximale Verschiebbarkeit des Ventil kolbens in Bezug zum Ventilzylinder in diese Richtung festgelegt wird. The spring element may in principle be any component or any construction group which is suitable to bias the valve piston within the valve cylinder to a closed position of the valve unit. Preferably, the Federele element is a compression spring, more preferably a coil spring, and / or integrally formed. Further preferably, one side of the spring element is supported against a front or end side of the valve cylinder and / or the other side of the spring element at one end or an end face of the valve piston. Most preferably, one end of the spring element is arranged at least in sections in a bore of the Ventilkol bens. Also preferably, the bore is arranged at the end or on the end face of the valve piston and / or in particular has a depth selected so that the spring element are completely pressed into the bore and then the end face of the valve piston come into abutment with an end face of the valve cylinder can, which is determined in a particularly simple manner, the maximum displaceability of the valve piston with respect to the valve cylinder in this direction.
Bevorzugt wird die Stärke des ersten Federelements derart gewählt, dass der Ventilkol ben den Arbeitsfluidkanal ohne anliegenden Druck des Steuerfluids zuverlässig schließt und besonders bevorzugt zugleich derart, dass beim Erreichen eines vorbestimmten Mindestdrucks des Steuerfluids, bevorzugt von 1,2 bar bis 1,3 bar, der Ventilkolben entgegen der Kraft des Federelements soweit in Richtung der geöffneten Stellung im Ventilzylinder gedrückt wird, dass ein vollständiges Öffnen mittels des ansteigenden Drucks des Arbeitsfluids in der ersten Ventileinheit ermöglicht wird. Grundsätzlich kann der Mindestdruck zum Öffnen des Ventilkolbens jedoch auch beliebig anders gewählt werden. Bevorzugt wird die Stärke des zweiten Federelements derart gewählt, dass eine Verschiebung des Ventilkolbens in gewünschtem Maße bei einem vorgegebenen Steuer druck erfolgt, insbesondere eine vollständige Verschiebung genau innerhalb der mögli chen Druckgrenzen des Steuerdrucks, beispielsweise zwischen 1 bar und 6 bar. Damit eine Steuerung des Drucks des Arbeitsfluids mittels der Steuerventilanordnung möglich ist, muss wenigstens die zweite Steuerdruckkammer vollständig von dem Arbeitsfluidka nal getrennt sein. Bevorzugt ist auch die erste Steuerfluidkammer vollständig vom Arbeitsfluidkanal getrennt. Preferably, the strength of the first spring element is selected such that the Ventilkol ben reliably closes the working fluid channel without applied pressure of the control fluid and particularly preferably at the same time such that upon reaching a predetermined minimum pressure of the control fluid, preferably from 1.2 bar to 1.3 bar, the valve piston against the force of the spring element is pressed so far in the direction of the open position in the valve cylinder, that a complete opening means the increasing pressure of the working fluid in the first valve unit is made possible. In principle, however, the minimum pressure for opening the valve piston can also be chosen differently. Preferably, the strength of the second spring element is selected such that a displacement of the valve piston to a desired extent at a predetermined control pressure, in particular a complete displacement exactly within the posi chen pressure limits of the control pressure, for example between 1 bar and 6 bar. In order for a control of the pressure of the working fluid by means of the control valve arrangement is possible, at least the second control pressure chamber must be completely separated from the Arbeitsfluidka channel. Preferably, the first control fluid chamber is also completely separated from the working fluid channel.
Bevorzugt reicht ein beliebig starker Steuerdruck bzw. ein beliebiger Steuerdruck ober halb eines Mindestdrucks in der ersten Steuerdruckkammer aus, um die erste Ventilein heit vollständig zu öffnen. Die erste Ventileinheit wird somit als Sperrventil der zweiten Ventileinheit vorgeschaltet betrieben und sorgt u.a. in vorteilhafter Weise dafür, dass kein dauerhafter Druck an der zweiten Ventileinheit anliegt, wenn kein Steuerdruck auf die Steuerventilanordnung wirkt. Zudem bildet die erste Ventileinheit ein Sicherheits ventil, um eine doppelte Sicherheit neben der zweiten Ventileinheit gegen eine uner wünschte Freigabe von Arbeitsdruck am Auslass zu bieten. Bevorzugt kann die erste Ventileinheit dazu nur zwischen einem geschlossenen und einem offenen Zustand geschaltet werden, d.h., es handelt sich um ein Zweizustandsventil. Preferably, an arbitrarily strong control pressure or any control pressure above half a minimum pressure in the first control pressure chamber is sufficient to open the first Ventilein unit completely. The first valve unit is thus operated upstream as a check valve of the second valve unit and provides u.a. Advantageously, that no permanent pressure is applied to the second valve unit when no control pressure acts on the control valve assembly. In addition, the first valve unit forms a safety valve to provide a double safety next to the second valve unit against an unwanted desired release of working pressure at the outlet. Preferably, the first valve unit can only be switched between a closed and an open state, that is, it is a two-state valve.
Auch die zweite Ventileinheit ist bevorzugt derart gebildet, dass diese das Arbeitsfluid vollständig sperren kann. Um das Arbeitsfluid in gewünschtem Umfang durchlassen zu können, weist die zweite Ventileinheit eine durch Verschieben des Ventilkolbens in dem Ventilzylinder einstellbare Ventilöffnung auf. Dabei wird die Ventilöffnung an einer Seite durch eine Ventilfläche des Ventilkolbens und an einer gegenüberliegenden Seite durch eine Ventilfläche des Ventilzylinders gebildet. Um mit einer Verschiebung des Ventilkolbens eine Veränderung der Größe der Ventilöffnung ermöglichen zu können, sind die beiden Ventilflächen verwinkelt zueinander angeordnet, sodass sich der Ab stand beider Ventilflächen bei einem Verschieben des Kolbens vergrößert bzw. verklei nert. Um eine feinfühlige Verstellung zu ermöglichen, erstreckt sich jeder der Ventilflä chen auf einer Oberfläche des Ventilkolbens bzw. des Ventilzylinders zumindest ab schnittsweise entlang der Verschieberichtung. Bei einer geeigneten Auswahl der Feder stärke der Ventileinheit ist es so möglich, für jeden möglichen Steuerdruck eine spezifi sche Position des Ventilkobens im Ventilzylinder zwischen der geschlossenen und der geöffneten Stellung vorzusehen, sodass entsprechend der Ventilöffnung der Arbeits druck in Abhängigkeit des Steuerdrucks entsprechend feinstufig einstellbar ist. Also, the second valve unit is preferably formed such that it can completely block the working fluid. In order to allow the working fluid to pass through to the desired extent, the second valve unit has a valve opening which can be adjusted by displacing the valve piston in the valve cylinder. In this case, the valve opening is formed on one side by a valve surface of the valve piston and on an opposite side by a valve surface of the valve cylinder. In order to enable a change in the size of the valve opening with a displacement of the valve piston, the two valve surfaces are arranged angled to each other, so that the ex-position of both valve surfaces in a displacement of the piston increases or verklei nert. In order to allow a sensitive adjustment, each of the Ventilflä chen extends on a surface of the valve piston and the valve cylinder at least from sections along the direction of displacement. With a suitable selection of the spring strength of the valve unit, it is possible to provide a specifi cal position of the Ventilkobens in the valve cylinder between the closed and the open position for each possible control pressure, so according to the valve opening of the working pressure in accordance with the control pressure according to fine-scale adjustable ,
Bei einer vorteilhaften Weiterbildung der erfindungsgemäßen Steuerventilanordnung weist wenigstens eine der beiden Ventilflächen der zweiten Ventileinheit wenigstens zwei, bevorzugt genau zwei aufeinander folgende Abschnitte auf, wobei besonders bevorzugt der Winkel zwischen den Ventilflächen im ersten, der geschlossenen Stellung folgenden Abschnitt kleiner ist als der Winkel der Ventilflächen im zweiten, an die geöffnete Stellung angrenzenden Bereich, wodurch ein besonders feinfühliges Anfahren sowie langsames Heben und Senken bei einem Hebezeugs möglich ist. Bevorzugt weist eine der beiden Ventilflächen dabei einen sich ändernden Winkel zwischen dem ersten und dem zweiten Abschnitt auf und besonders bevorzugt ist die andere Ventilfläche dabei ohne Winkeländerung gebildet. Weiterhin bevorzugt sind die beiden Abschnitte einer Ventilfläche deutlich voneinander abgegrenzt, d.h., der Winkel zwischen den Abschnitten ändert sich nicht kontinuierlich, sondern sprunghaft bzw. an einer Position. Ebenfalls bevorzugt ist der Winkel der Ventilflächen im zweiten Abschnitt wenigstens doppelt so groß, besonders bevorzugt wenigstens fünfmal so groß und ganz besonders bevorzugt wenigstens zehnmal so groß wie der Winkel der Ventilflächen im ersten Abschnitt. Entsprechend ist im zweiten Abschnitt der Ventilflächen bevorzugt der Durchmesser des Ventilkolbens bzw. der Abstand der beiden sich gegenüberliegenden Ventilflächen wenigstens doppelt, besonders bevorzugt wenigstens fünfmal und ganz besonders bevorzugt wenigstens zehnmal so groß wie im ersten Abschnitt. Besonders bevorzugt sind beide Abschnitte derart gebildet, dass diese eine Steuerung der Durch flussmenge des Arbeitsfluids zwischen einem voll gesperrten Zustand und einem voll geöffneten Zustand ermöglichen, wobei zunächst ein langsames und feinfühliges Anfah ren und mit höherem Steuerdruck ein zügiges Heben einer Last mittels eines Hebezeugs möglich ist. Ganz besonders bevorzugt sind die beiden Abschnitte zusätzlich zum ge schlossenen und zum geöffneten Zustand ansteuerbar. In an advantageous development of the control valve arrangement according to the invention, at least one of the two valve surfaces of the second valve unit has at least two, preferably exactly two consecutive sections, wherein particularly preferably the angle between the valve surfaces in the first, the closed position following section is smaller than the angle of the valve surfaces in the second, adjacent to the open position area, whereby a particularly sensitive start and slow lifting and lowering is possible with a hoist. In this case, one of the two valve surfaces preferably has a changing angle between the first and the second section, and particularly preferably the other valve surface is formed without changing the angle. Further preferably, the two sections of a valve surface are clearly separated from each other, ie, the angle between the sections does not change continuously, but suddenly or at a position. Also preferably, the angle of the valve surfaces 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 surfaces in the first section. Accordingly, in the second section of the valve surfaces preferably the diameter of the valve piston or the distance of the two opposing valve surfaces at least twice, more preferably at least five times and most preferably at least ten times as large as in the first section. Particularly preferably, both sections are formed such that they allow control of the flow rate of the working fluid between a fully locked state and a fully open state, initially a slow and sensitive Anfah ren and higher control pressure a rapid lifting of a load by means of a hoist is possible. Most preferably, the two sections in addition to the ge closed and the open state can be controlled.
Gemäß einer bevorzugten Ausgestaltung der erfindungsgemäßen Steuerventilanordnung sind die beiden Ventilflächen im ersten und/oder zweiten Abschnitt, wenigstens in Bezug zueinander, bevorzugt jeweils linear verlaufend gebildet, wobei der Winkel zwischen den beiden Ventilflächen des ersten Abschnitts bevorzugt zwischen o,i° und 150, besonders bevorzugt zwischen i° und io° und ganz besonders bevorzugt zwischen 2° und 7° und der Winkel des zweiten Abschnitts zwischen 50 und 85°, besonders bevorzugt zwischen io° und 750 und ganz besonders bevorzugt zwischen 20° und 6s°beträgt. According to a preferred embodiment of the control valve arrangement according to the invention, the two valve surfaces in the first and / or second section, at least in relation to each other, preferably each formed linearly extending, wherein the angle between the two valve surfaces of the first section preferably between o, i ° and 15 0 , more preferably between i ° and io ° and most preferably between 2 ° and 7 ° and the angle of the second section between 5 0 and 85 °, more preferably between 10 ° and 75 0 and most preferably between 20 ° and 6 ° ,
Insbesondere bevorzugt beträgt der Winkel im ersten Abschnitt 20 und/oder der Winkel im zweiten Abschnitt 450. Weiterhin bevorzugt erstrecken sich beide Ventilflächen im ersten und/oder zweiten Abschnitt mit gleichbleibendem Winkel zueinander entlang der Oberfläche des Ventilzylinders bzw. des Ventilkolbens, sodass sich der Abstand beider Ventilflächen zueinander kontinuierlich, insbesondere von der geschlossenen Position zur geöffneten Position hin, vergrößert. Particularly preferably, the angle in the first section 2 0 and / or the angle in the second section 45 0 . Further preferably, both valve surfaces extend in the first and / or second portion at a constant angle to each other along the surface of the valve cylinder or the valve piston, so that the distance between the two valve surfaces continuously increases, in particular from the closed position to the open position.
Eine Ausführung der Steuerventilanordnung sieht vor, dass wenigstens eine der beiden Ventilflächen im ersten und/oder zweiten Abschnitt nichtlinear verlaufend gebildet ist, wobei der Winkel zwischen den beiden gegenüberliegenden Ventilflächen des Ventilkol bens und des Ventilzylinders sich bevorzugt zwischen der geschlossenen und der geöff neten Position vergrößert und dabei der Winkel des ersten Abschnitts weiterhin bevor zugt zwischen o,i° und 150, besonders bevorzugt zwischen i° und io° und ganz beson ders bevorzugt zwischen 20 und 70 und der Winkel des zweiten Abschnitts zwischen 50 und 85°, besonders bevorzugt zwischen io° und 750 und ganz besonders bevorzugt zwischen 20° und 6s°beträgt. Ganz besonders bevorzugt ist eine der Ventilflächen des Ventilkolbens oder des Ventilzylinders in einem oder beiden Abschnitten nichtlinear verlaufend gebildet, während die gegenüberliegende Ventilfläche des Ventilzylinders oder des Ventilkolbens linear verläuft. An embodiment of the control valve arrangement provides that at least one of the two valve surfaces in the first and / or second portion is formed non-linearly extending, wherein the angle between the two opposite valve surfaces of the Ventilkol ben and the valve cylinder preferably increases between the closed and the geöff Neten position and while the angle of the first portion continues to be given between o, i ° and 15 0 , more preferably between i ° and io ° and very FITS preferred between 2 0 and 7 0 and the angle of the second section between 5 0 and 85 ° , more preferably between io ° and 75 0 and most preferably between 20 ° and 6s °. Most preferably, one of the valve surfaces of the valve piston or the valve cylinder is formed non-linearly extending in one or both sections, while the opposite valve surface of the valve cylinder or the valve piston is linear.
Generell wird ein Verlauf der Ventilflächen in Bezug zueinander mit einer zur geöffneten Position des Ventilkolbens hin sich vergrößernden Ventilöffnung bevorzugt. Ebenfalls wird generell bevorzugt, dass in wenigstens einem Abschnitt und besonders bevorzugt in beiden Abschnitten die Ventilfläche des Ventilkolbens oder des Ventilzylinders parallel zur Verstellrichtung des Ventilkolbens im Ventilzylinder angeordnet ist, während die andere, gegenüberliegende Ventilfläche in einem Winkel dazu mit einem linearen oder nichtlinearen Verlauf angeordnet ist. Besonders bevorzugt wird eine Ausführung mit einem Verlauf der Ventilfläche mit einem ersten linearen Abschnitt mit kleinem Winkel und einem zweiten linearen Abschnitt mit einem größeren Winkel. In general, a profile of the valve surfaces in relation to one another is preferred with a valve opening which increases toward the open position of the valve piston. It is also generally preferred that in at least one section and more preferably in both portions of the valve surface of the valve piston or the valve cylinder is arranged parallel to the displacement 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. Particularly preferred 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.
Bei einer bevorzugten Ausführung der erfindungsgemäßen Steuerventilanordnung erstreckt sich der erste Abschnitt und/oder der zweite Abschnitt der Ventilflächen über wenigstens 15 %, bevorzugt wenigstens 25 %, besonders bevorzugt wenigstens 30 % und ganz besonders bevorzugt über wenigstens 40 % des maximalen Verstellweges des Ventilkolbens in Bezug zum Ventilzylinder, wodurch eine besonders feinfühlige Steue rung erreicht werden kann. Ebenfalls bevorzugt erstreckt sich der erste Abschnitt über maximal 80 %, bevorzugt 60 %, besonders bevorzugt 50 % und ganz besonders bevor zugt 40 % des maximalen Verstellweges. Weiterhin bevorzugt erstrecken sich beide Abschnitte zusammen über wenigstens 50 %, besonders bevorzugt wenigstens 75 % und ganz besonders bevorzugt wenigstens 80 % der maximalen Verstelllänge des Ventilkol bens. In a preferred embodiment of the control valve arrangement according to the invention, the first section and / or the second section of the valve surfaces extends over at least 15%, preferably at least 25%, more preferably at least 30% and most preferably over at least 40% of the maximum displacement of the valve piston with respect to the valve cylinder, whereby a particularly sensitive control tion can be achieved. Also preferably, the first section extends over a maximum of 80%, preferably 60%, more preferably 50% and most preferably before given 40% of the maximum adjustment. Further preferably, both sections together extend over at least 50%, more preferably at least 75%, and most preferably at least 80% of the maximum adjustment length of the valve piston.
Weiterhin ist eine Ausführung der Steuerventilanordnung bevorzugt bei der wenigstens der zweite Ventilkolben, bevorzugt auch der erste Ventilkolben, rotationssymmetrisch um eine Achse entlang der Verstellrichtung gebildet ist und der korrespondierende Ventilzylinder einen runden Querschnitt aufweist, sodass die Ventilöffnung die Form eines Ringspalts hat. Entsprechend weist wenigstens eine Ventilfläche bevorzugt eine konische Form auf, während die zweite Ventilfläche ebenfalls bevorzugt zylindrisch oder auch konisch gebildet ist. Furthermore, an embodiment of the control valve arrangement is preferred in which at least the second valve piston, preferably also the first valve piston, is rotationally symmetrical about an axis along the adjustment and the corresponding valve cylinder has a round cross section, so that the valve opening has the shape of an annular gap. Accordingly, at least one valve surface preferably has a conical shape, while the second valve surface is also preferably cylindrical or conical.
Ebenfalls bevorzugt ist eine Ausführung der Steuerventilanordnung bei der die erste und/oder zweite Steuerdruckkammer im Bereich des dem Federelement gegenüberlie genden Endes des jeweiligen Ventilkolbens angeordnet ist und/oder der Arbeitsfluidka nal in der ersten und/oder in der zweiten Ventileinheit zwischen dem Bereich des Federelements und dem Bereich der Steuerdruckkammer angeordnet ist. Besonders bevorzugt umgibt der Arbeitsfluidkanal den jeweiligen Ventilkolben innerhalb des Ventilzylinders abschnittsweise allseitig. Weiterhin bevorzugt ist der Arbeitsfluidkanal abschnittsweise durch den Ventilzylinder gebildet. Also preferred is an embodiment of the control valve arrangement in which the first and / or second control pressure chamber in the region of the spring element gegenüberlie ing end of the respective valve piston is arranged and / or the Arbeitsfluidka channel in the first and / or in the second valve unit between the region of the spring element and the region of the control pressure chamber is arranged. Particularly preferably, the working fluid channel surrounds the respective valve piston within the Valve cylinder sections on all sides. Further preferably, the working fluid channel is formed in sections by the valve cylinder.
Bei einer vorteilhaften Weiterbildung der erfindungsgemäßen Steuerventilanordnung ist eine Handsteuereinheit vor dem Steuerfluideinlass angeordnet, die einen Handregler aufweist, mittels dem der Steuerdruck des Steuerfluids stufenlos regulierbar ist, wobei der Handregler besonders bevorzugt ein handbetätigbares Gasventil umfasst, mittels dem der Steuerdruck stufenlos und feinfühlig einstellbar ist. In an advantageous development of the control valve arrangement according to the invention a hand control unit is arranged in front of the control fluid inlet, which has a hand controller, by means of which the control pressure of the control fluid is infinitely adjustable, the hand controller particularly preferably comprises a handbetätigbares gas valve by means of which the control pressure is infinitely and sensitively adjustable.
Schließlich weist die Steuerventilanordnung bevorzugt genau einen einzigen Steuerflui deinlass auf, der im Inneren der Steuerventilanordnung mit den beiden Steuerdruck kammern verbunden ist, sodass der Steuerdruck stets in beiden Steuerdruckkammern gleich ist. Insbesondere bevorzugt weist die Steuerventilanordnung auch nur genau einen Arbeitsfluideinlass und/oder einen Arbeitsfluidauslass auf. Finally, the control valve arrangement preferably has precisely one single control fluid discharge, which is connected to the two control pressure chambers in the interior of the control valve arrangement, so that the control pressure is always the same in both control pressure chambers. Particularly preferably, the control valve arrangement also has only exactly one working fluid inlet and / or one working fluid outlet.
Ein Ausführungsbeispiel der erfindungsgemäßen Steuerventilanordnung wird nachste hend mit Bezug auf die Zeichnungen näher erläutert. In den Figuren zeigen: An embodiment of the control valve assembly according to the invention is explained in more detail below with reference to the drawings. In the figures show:
Fig. l eine Schnittansicht einer Steuerventilanordnung mit zwei geschlossenen Venti leinheiten, 1 is a sectional view of a control valve assembly with two closed Venti leinheiten,
Fig. 2 eine vergrößerte Schnittansicht eines Sperrbereichs der zweiten Ventileinheit der in Fig. l dargestellten Steuerventilanordnung,  2 is an enlarged sectional view of a blocking portion of the second valve unit of the control valve assembly shown in Fig. L,
Fig. 3 eine Schnittansicht der in Fig. l dargestellten Steuerventilanordnung mit einer geöffneten ersten Ventileinheit und einer geschlossenen zweiten Ventileinheit, und  3 shows a sectional view of the control valve arrangement shown in FIG. 1 with an opened first valve unit and a closed second valve unit, and FIG
Fig. 4 eine Schnittansicht der in Fig. l dargestellten Steuerventilanordnung mit einer voll geöffneten ersten Ventileinheit und einer teilweise geöffneten zweiten Venti leinheit,  4 shows a sectional view of the control valve arrangement shown in FIG. 1 with a fully opened first valve unit and a partially opened second valve unit,
Fig. 5 eine Schnittansicht der in Fig. l dargestellten Steuerventilanordnung mit zwei geöffneten Ventileinheiten.  Fig. 5 is a sectional view of the control valve assembly shown in Fig. L with two open valve units.
Bei einer in Figur l dargestellten Steuerventilanordnung l zur indirekten pneumatischen Steuerung des Arbeitsdrucks für einen pneumatischen Lamellenmotor eines Hebezeugs sind eine erste und eine zweite Ventileinheit 2, 3 parallel zueinander in einem gemein samen Gehäuse angeordnet. In an illustrated in Figure l control valve assembly l for indirect pneumatic control of the working pressure for a pneumatic vane motor of a hoist are a first and a second valve unit 2, 3 arranged parallel to each other in a common seed housing.
Jede der beiden Ventileinheiten 2, 3 ist als federvorgespanntes, pneumatisch betriebenes Ventil gebildet. Entsprechend ist in jeder der Ventileinheiten 2, 3 ein verschieblicher Ventilkolben 9, 10 in einem Ventilzylinder 7, 8 derart angeordnet, dass ein durch die Ventileinheit 2, 3 geleitetes Druckfluid, insbesondere Druckluft, mittels eines Oberflä chenabschnitts des Ventilzylinders 7,8 und des Ventilkolbens 9, 10 gesperrt bzw. geregelt werden kann. Each of the two valve units 2, 3 is formed as a spring-biased, pneumatically operated valve. Accordingly, in each of the valve units 2, 3 a displaceable valve piston 9, 10 arranged in a valve cylinder 7, 8 such that a guided through the valve unit 2, 3 pressure fluid, in particular compressed air, by means of a Oberflä chenabschnitts the valve cylinder 7,8 and the valve piston 9, 10 can be locked or regulated.
Der Ventilkolben 9, 10 ist an einer Seite mit einer Spiralfeder 11, 12 auf eine geschlossene Stellung hin vorgespannt, wobei ein Ende der Spiralfeder 11, 12 gegen eine runde Stirn fläche des Ventilzylinders 7, 8 abgestützt ist, während das andere Ende innerhalb einer Bohrung im Ventilkolben 9, 10 festgelegt ist. Am anderen Ende E des Ventilkolbens 9,10 ist im Ventilzylinder 7, 8 eine Steuerdruckkammer 13, 14 gebildet. Die Steuerdruckkam mern 13, 14 beider Ventileinheiten 2, 3 sind gemeinsam mit einem Einlass für einen Steuerdruckluftstrom verbunden, sodass in der Steuerdruckkammer 13, 14 ein Druck aufgebaut werden kann, der der Federspannung der Spiralfeder 11, 12 entgegenwirkt und durch eine Beaufschlagung der Stirnfläche des Ventilkolbens 9, 10 mit dem Steuer druck ein Verschieben des Ventilkolbens 9, 10 ermöglicht. The valve piston 9, 10 is biased on one side with a coil spring 11, 12 to a closed position, with one end of the coil spring 11, 12 against a round end face of the valve cylinder 7, 8 is supported, while the other end within a bore in the valve piston 9, 10 is fixed. At the other end E of the valve piston 9, 10 a control pressure chamber 13, 14 is formed in the valve cylinder 7, 8. The Steuerdruckkam numbers 13, 14 of both valve units 2, 3 are connected together with an inlet for a control compressed air flow, so that in the control pressure chamber 13, 14, a pressure can be established, which counteracts the spring tension of the coil spring 11, 12 and by an application of the end face of the Valve piston 9, 10 with the control pressure a displacement of the valve piston 9, 10 allows.
Die Steuerventileinheit 1 weist einen Arbeitsdrucklufteinlass 4 sowie einen entsprechen den Auslass 5 auf, der einen druckgesteuerten Druckluftstrom für den Lamellenmotor des Hebezeugs bereitstellt. Der Auslass 5 ist über einen Arbeitsdruckluftkanal 6 mit dem Arbeitsdrucklufteinlass 4 verbunden, wobei der Arbeitsdruckluftkanal 6 hintereinander durch beide Ventileinheiten 2, 3 führt und dabei jeweils mittels der Ventileinheiten 2, 3 in einem Sperr- und Regelbereich 15 sperr- und regelbar ist. The control valve unit 1 has a working air inlet 4 and a corresponding outlet 5, which provides a pressure-controlled compressed air flow for the vane motor of the hoist. The outlet 5 is connected via a working compressed air duct 6 to the working air inlet 4, wherein the working compressed air duct 6 in succession through both valve units 2, 3 and in each case by means of the valve units 2, 3 in a blocking and control range 15 can be blocked and regulated.
An dem zweiten Ventilkolben 10 sowie dem zugehörigen Ventilzylinder 8 ist jeweils eine Ventilfläche 16, 17 angeordnet, die im geschlossenen Zustand der Ventileinheit 2, 3 aneinander anliegen. Beide Ventilflächen 16, 17 sind derart verwinkelt zueinander angeordnet, dass bei einem Verschieben des Ventilkolbens 10 im Ventilzylinder 8 mit zunehmender Verschiebung sich eine vergrößernde Ventilöffnung in Form eines Ringspalts bildet. On the second valve piston 10 and the associated valve cylinder 8, a valve surface 16, 17 is arranged in each case, which abut each other in the closed state of the valve unit 2, 3. Both valve surfaces 16, 17 are arranged so bent to each other that when displacing the valve piston 10 in the valve cylinder 8 with increasing displacement, a magnifying valve opening in the form of a Ringspalts forms.
In Fig. l ist eine Steuerventilanordnung l mit beiden Ventileinheiten 2, 3 in der ge schlossenen Position dargestellt, sodass die erste Ventileinheit 2 den Arbeitsdruckluft- strom bereits kurz hinter dem Arbeitsdrucklufteinlass 4 absperrt und an der zweiten Ventileinheit 3 kein Druck im Bereich des Arbeitsdruckluftkanals 6 anliegt. In diesem Zustand der Steuerventilanordnung 1 liegt ebenfalls kein Steuerdruck an bzw. der Steuerdruck der Steuerdruckluft in den Steuerdruckkammern 13, 14 liegt unterhalb eines festgelegten Schwellenwerts von etwa 1,2 bar zum Öffnen der Ventileinheiten 2, 3. 1 shows a control valve arrangement 1 with both valve units 2, 3 in the closed position, so that the first valve unit 2 shuts off the working compressed air flow already shortly after the working compressed air inlet 4 and at the second valve unit 3 no pressure in the area of the working compressed air duct 6 is applied. In this state, the control valve assembly 1 is also no control pressure or the control pressure of the control compressed air in the control pressure chambers 13, 14 is below a predetermined threshold value of about 1.2 bar to open the valve units 2, 3rd
In Fig. 3 ist eine Steuerventilanordnung 1 in einem Zustand dargestellt, der nur kurzfris tig bzw. exakt beim Erreichen eines Schwellenwerts des Steuerdrucks zum Öffnen der Ventileinheiten 2, 3 auftritt. Die erste Ventileinheit 2 ist voll geöffnet, während die zweite Ventileinheit 3 noch geschlossen ist. Der in der ersten Steuerluftdruckkammer 13 anliegende Steuerdruck wirkt der ersten Spiralfeder 11 soweit entgegen, dass die Ventil öffnung der ersten Ventileinheit 2 gerade geöffnet wird, indem die beiden Ventilflächen 16, 17 der ersten Ventileinheit 2 außer Kontakt geraten. In Fig. 3, a control valve assembly 1 is shown in a state which only kurzfris tig or exactly when a threshold value of the control pressure for opening the valve units 2, 3 occurs. The first valve unit 2 is fully open, while the second valve unit 3 is still closed. The control pressure applied in the first control air pressure chamber 13 counteracts the first spiral spring 11 so far 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 out of contact.
Mit steigendem Steuerdruck wird nun auch der zweite Ventilkolben 10 der zweiten Ventileinheit 3 gegen die Federkraft der Spiralfeder 12 auf die geöffnete Stellung hin verschoben, wobei die Federkraft derart gewählt ist, dass in einem vordefinierten Druck bereich, bevorzugt zwischen 1 bar und 6 bar, der Ventilkolben 10 über den maximalen Verstellweg W verschoben wird. Um zunächst eine feinfühlige Steuerung und mit steigendem Steuerdruck dann eine zügige und kraftvolle Freigabe des Arbeitsluftdrucks zu ermöglichen, sind die Ventilflä chen 16, 17 der zweiten Ventileinheit 3 mit einem sich innerhalb der Steuerfläche 17 des Ventilkolbens 10 verändernden Winkel a, b gebildet (siehe Fig. 2). Dabei ist die Ventil fläche 16 des Ventilzylinders 8 als linear verlaufende Zylinderfläche als Teil der Wan- düng des Ventilzylinders 8 gebildet. Die Ventilfläche 17 des Ventilkolbens 10 weist zwei zueinander verwinkelte Abschnitte A, B auf, die jeweils auch in einem Winkel a, b zur gegenüberliegenden Ventilfläche 16 angeordnet sind. Beide Abschnitte A, B weisen einen linearen Verlauf auf. Der Winkel a des ersten Abschnitts der Ventilfläche 17 zur gegen- überliegenden Ventilfläche 16 beträgt 50, während der entsprechende Winkel b des zweiten Abschnitts B 450 beträgt. Die beiden Abschnitte A, B erstrecken sich über 85 % des maximalen Verstellweges W des Ventilkolbens 10 im Ventilzylinder 8. In Fig. 4 ist eine Steuerventilanordnung 1 mit der ersten Ventileinheit 2 in der vollstän dig geöffneten Position und der zweiten Ventileinheit 3 in einer teilweise geöffneten Position dargestellt, wobei die Arbeitsdruckluft durch einen durch die Steuerflächen 16, 17 der zweiten Ventileinheit 3 gebildeten Ringspalt geleitet wird und ein reduzierter Volumenstrom durch diesen Ringspalt durch den Arbeitsdruckluftkanal 6 von dem Arbeitsluftdruckeinlass 4 zum Auslass 5 der Steuerventilanordnung strömen kann. With increasing control pressure now the second valve piston 10 of the second valve unit 3 is shifted against the spring force of the coil spring 12 to the open position, wherein the spring force is selected such that in a predefined pressure range, preferably between 1 bar and 6 bar, the Valve piston 10 is moved over the maximum adjustment path W. In order first to allow a sensitive control and with increasing control pressure then a rapid and powerful release of the working air pressure, the Ventilflä surfaces 16, 17 of the second valve unit 3 with a within the control surface 17 of the valve piston 10 changing angle a, b formed (see FIG 2). In this case, the valve surface 16 of the valve cylinder 8 as a linearly extending cylindrical surface as part of the Wan düng of the valve cylinder 8 is formed. The valve surface 17 of the valve piston 10 has two mutually angled sections A, B, which are each 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 Overlying valve surface 16 is 5 0 , while the corresponding angle b of the second section B 45 is 0 . The two sections A, B extend over 85% of the maximum adjustment path W of the valve piston 10 in the valve cylinder 8. In Fig. 4 is a control valve assembly 1 with the first valve unit 2 in the completeness dig open position and the second valve unit 3 in a partially open Position shown, wherein the working pressure air is passed 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 pressure air duct 6 from the working air pressure inlet 4 to the outlet 5 of the control valve assembly.
In Fig. 5 ist schließlich eine Steuerventilanordnung 1 mit beiden Ventileinheiten 2, 3 in der vollständig geöffneten Position dargestellt, wobei die Arbeitsdruckluft durch die Steuerflächen 16, 17 der beiden Ventileinheiten 2, 3 ungehindert durch den Arbeits- druckluftkanal 6 von dem Arbeitsluftdruckeinlass 4 zum Auslass 5 der Steuerventilan ordnung strömen kann. Finally, FIG. 5 shows a control valve arrangement 1 with both valve units 2, 3 in the fully open position, wherein the working compressed air through the control surfaces 16, 17 of the two valve units 2, 3 passes unhindered through the working compressed air duct 6 from the working air pressure inlet 4 to the outlet 5 of the control valve arrangement can flow.
Bezugszeichenliste LIST OF REFERENCE NUMBERS
1 Steuerventilanordnung 1 control valve arrangement
2 erste Ventileinheit  2 first valve unit
3 zweite Ventileinheit  3 second valve unit
4 Arbeitsfluideinlass  4 working fluid inlet
5 Auslass  5 outlet
6 Arbeitsfluidkanal  6 working fluid channel
7 erster Ventilzylinder  7 first valve cylinder
8 zweiter Ventilzylinder  8 second valve cylinder
9 ersten Ventilkolben  9 first valve piston
10 zweiter Ventilkolben  10 second valve piston
11 erstes Federelement  11 first spring element
12 zweites Federelement  12 second spring element
13 erste Steuerdruckkammer  13 first control pressure chamber
14 zweite Steuerdruckkammer  14 second control pressure chamber
15 Sperr- und Regelbereich  15 blocking and control range
16 erste Ventilfläche  16 first valve surface
17 zweite Ventilfläche  17 second valve surface
A erster Abschnitt  A first section
B zweiter Abschnitt  B second section
E Ende des Ventilkolbens  E end of the valve piston
F Bereich des Federelements  F range of the spring element
S Bereich der Steuerdruckkammer  S range of the control pressure chamber
V Verstellrichtung  V adjustment direction
W maximaler Verstellweg  W maximum adjustment
a Winkel des ersten Abschnitts a Angle of the first section
b Winkel des zweiten Abschnitts b angle of the second section

Claims

Ansprüche claims
1. Steuerventilanordnung (l) zur indirekten pneumatischen Steuerung, insbesonde re eines pneumatisch betriebenen Lamellenmotors eines Hebezeugs, mit1. control valve assembly (l) for indirect pneumatic control, insbesonde a pneumatically operated multi-disk motor of a hoist, with
- zwei pneumatischen, hintereinander angeordneten Ventileinheiten (2, 3),two pneumatic valve units (2, 3) arranged one behind the other,
- einem Arbeitsfluideinlass (4) und einem Steuerfluideinlass, a working fluid inlet (4) and a control fluid inlet,
- einem den Arbeitsfluideinlass (4) durch beide Ventileinheiten (2, 3) hin durch mit einem Auslass (5) verbindenden Arbeitsfluidkanal (6), a working fluid channel (6) connecting the working fluid inlet (4) through both valve units (2, 3) through an outlet (5),
- jeweils einem innerhalb eines Ventilzylinders (7, 8) der ersten und zweiten Ventileinheit (2, 3) angeordneten, zwischen einer geöffneten und einer ge schlossenen Stellung verschiebbaren Ventilkolben (9, 10), each one within a valve cylinder (7, 8) of the first and second valve unit (2, 3) arranged between an open and a closed position ge slidable valve piston (9, 10),
- jeweils einem den ersten und den zweiten Ventilkolben (9, 10) auf die ge schlossene Stellung hin vorspannenden Federelement (11, 12),  - Each one the first and the second valve piston (9, 10) to the ge closed position biasing spring element (11, 12),
- jeweils einer mit dem Steuerfluideinlass verbundenen Steuerdruckkam  - Each one connected to the control fluid inlet Steuerdruckkam
mer (13, 14) zum Beaufschlagen des jeweiligen Ventilkolbens (9, 10) mit ei nem der Vorspannung des Federelements (11, 12) entgegenwirkenden Steu erdruck, wobei  Mer (13, 14) for applying the respective valve piston (9, 10) with egg NEM of the bias of the spring element (11, 12) counteracting STEU erdruck, wherein
- die erste Ventileinheit (2) derart gebildet ist, dass beim Anlegen eines Steu erdrucks in der ersten Steuerdruckkammer (13) der erste Ventilkolben (9) von der geschlossenen in die geöffnete Stellung verschoben wird, und wobei - The first valve unit (2) is formed such that when creating a STEU erdrucks in the first control pressure chamber (13) of the first valve piston (9) is moved from the closed to the open position, and wherein
- in der zweiten Ventileinheit (3) in einem Sperr- und Regelbereich (15) des Arbeitsfluidkanals (6) zwei sich gegenüberliegende, zueinander verwinkelte Ventilflächen (16, 17) am Ventilzylinder (8) und am Ventilkolben (10) derart sich entlang der Verschieberichtung (V) erstreckend angeordnet sind, dass die Ventilflächen (16, 17) beim Verschieben des Ventilkolbens (10) im Ven tilzylinder (8) aufgrund eines sich ändernden Steuerdrucks eine unterschied lich weit geöffnete Ventilöffnung bilden und entsprechend der Ventilöff nungsweite der Arbeitsdruck in Abhängigkeit des Steuerdrucks feinstufig ein stellbar ist. - In the second valve unit (3) in a blocking and control region (15) of the working fluid channel (6) two opposing, mutually angled valve surfaces (16, 17) on the valve cylinder (8) and the valve piston (10) so along the direction of displacement (V) are arranged extending extending that the valve surfaces (16, 17) when moving the valve piston (10) in Ven tilzylinder (8) due to a changing control pressure a difference Lich wide open valve opening and according to the Ventilöff tion width of the working pressure in dependence of Control pressure is finely adjustable.
2. Steuerventilanordnung nach Anspruch l, dadurch gekennzeichnet, dass wenigs tens eine der beiden Ventilflächen (16, 17) der zweiten Ventileinheit (3) zwei auf einander folgende Abschnitte (A, B) aufweist, wobei der Winkel (a) zwischen den Ventilflächen (16, 17) im ersten, der geschlossenen Stellung folgenden Ab schnitt (A) kleiner ist als der Winkel (b) der Ventilflächen (16, 17) im zweiten, an die geöffnete Stellung angrenzenden Bereich (B). 2. control valve arrangement according to claim l, characterized in that wenigs least one of the two valve surfaces (16, 17) of the second valve unit (3) has two successive sections (A, B), wherein the angle (a) between the valve surfaces ( 16, 17) in the first, the closed position following from section (A) is smaller than the angle (b) of the valve surfaces (16, 17) in the second, adjacent to the open position region (B).
3. Steuerventilanordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die beiden Ventilflächen (16, 17) im ersten und/oder zweiten Abschnitt (A, B) li near verlaufend gebildet sind, wobei der Winkel (a, b) zwischen den beiden Ven tilflächen (16, 17) zwischen o,i° und io° beträgt. 3. Control valve arrangement according to claim 1 or 2, characterized in that the two valve surfaces (16, 17) in the first and / or second portion (A, B) are formed li near extending, wherein the angle (a, b) between the two Ven tilflächen (16, 17) between o, i ° and io °.
4. Steuerventilanordnung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass wenigstens eine der beiden Ventilflächen (16, 17) im ersten und/oder zweiten Abschnitt (A, B) nichtlinear verlaufend gebildet ist, wobei der Winkel (a, b) zwischen den beiden Ventilflächen (16, 17) sich zwischen der ge schlossenen und der geöffneten Position vergrößert und dabei zwischen o,i° und 450 beträgt. 4. control valve arrangement according to one of the preceding claims, characterized in that at least one of the two valve surfaces (16, 17) in the first and / or second portion (A, B) is formed non-linearly extending, wherein the angle (a, b) between the two valve surfaces (16, 17) increases between the ge closed and the open position and thereby between o, i ° and 45 0 .
5. Steuerventilanordnung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sich der erste Abschnitt (A) und/oder der zweite Ab schnitt (B) der Ventilflächen (16, 17) jeweils über wenigstens 25 % des maximalen Verstellweges (W) des Ventilkolbens (10) in Bezug zum Ventilzylinder (8) er streckt. 5. Control valve arrangement according to one of the preceding claims, characterized in that the first section (A) and / or the second section from (B) of the valve surfaces (16, 17) respectively over at least 25% of the maximum adjustment path (W) of the valve piston (10) in relation to the valve cylinder (8) he stretches.
6. Steuerventilanordnung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass wenigstens der zweite Ventilkolben (10) rotationssymmet risch gebildet ist und der korrespondierende Ventilzylinder (8, 7) einen runden Querschnitt aufweist, sodass die Ventilöffnung die Form eines Ringspalts hat. 6. Control valve arrangement according to one of the preceding claims, characterized in that at least the second valve piston (10) is formed rotationally symmetrical and the corresponding valve cylinder (8, 7) has a round cross section, so that the valve opening has the shape of an annular gap.
7. Steuerventilanordnung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die erste und/oder zweite Steuerdruckkammer (13, 14) im Bereich des dem Federelement (11, 12) gegenüberliegenden Endes (E) des jewei- ligen Ventilkolbens (9, 10) angeordnet ist und/oder der Arbeitsfluidkanal (6) in der ersten und/oder in der zweiten Ventileinheit (2, 3) zwischen dem Bereich (F) des Federelements (11, 12) und dem Bereich (S) der Steuerdruckkammer (13, 14) angeordnet ist. 7. Control valve arrangement according to one of the preceding claims, characterized in that the first and / or second control pressure chamber (13, 14) in the region of the spring element (11, 12) opposite end (E) of jewei- The working fluid channel (6) in the first and / or in the second valve unit (2, 3) between the region (F) of the spring element (11, 12) and the region (S ) of the control pressure chamber (13, 14) is arranged.
Steuerventilanordnung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass eine Handsteuereinheit vor dem Steuerfluideinlass ange ordnet ist, die einen Handregler aufweist, mittels dem der Steuerdruck des Steu erfluids stufenlos regulierbar ist. Control valve arrangement according to one of the preceding claims, characterized in that a manual control unit is arranged in front of the control fluid inlet, which has a hand controller, by means of which the control pressure of the STEU is continuously adjustable.
Steuerventilanordnung nach einem der vorhergehenden Ansprüche, gekenn zeichnet durch einen einzigen Steuerfluideinlass, der im Inneren der Steuerven tilanordnung (1) mit beiden Steuerdruckkammern verbunden ist. Control valve arrangement according to one of the preceding claims, characterized by a single control fluid inlet, which is connected inside the control valve arrangement (1) with both control pressure chambers.
Verfahren zum Steuern eines Arbeitsfluiddrucks mittels eines Steuerfluids in einer Steuerventilanordnung (1) zur indirekten pneumatischen Steuerung, mit den Schritten: Method for controlling a working fluid pressure by means of a control fluid in a control valve arrangement (1) for indirect pneumatic control, comprising the steps of:
- Anlegen eines Arbeitsdrucks mittels eines Arbeitsfluids an einem Arbeits fluideinlass (4),  Applying a working pressure by means of a working fluid at a working fluid inlet (4),
- Steuerung des Drucks in einem Steuerfluid, insbesondere mittels eines feinfühligen Ventils einer Handsteuerung, und Belasten eines Steuerfluide inlasses mit dem Steuerdruck,  Controlling the pressure in a control fluid, in particular by means of a sensitive valve of a manual control, and loading a control fluid inlet with the control pressure,
- Einleiten von Steuerfluid in jeweils eine Steuerfluidkammer (13, 14) einer pneumatischen Ventileinheit (2, 3), wobei das Steuerfluid einen durch ein Federelement (11, 12) auf eine geschlossene Stellung vorgespannten, inner halb eines Ventilzylinders (7, 8) angeordneten Ventilkolben (9, 10) auf eine geöffnete Stellung hin verschieben kann, wobei  - Introducing control fluid in each case a control fluid chamber (13, 14) of a pneumatic valve unit (2, 3), wherein the control fluid by a spring element (11, 12) biased to a closed position, inner half of a valve cylinder (7, 8) Valve piston (9, 10) can move to an open position, wherein
- das Anlegen eines Steuerdrucks in der ersten Steuerdruckkammer (13) den ersten Ventilkolben (9) von der geschlossenen in die geöffnete Stellung ver schiebt, wodurch das Arbeitsfluid durch einen mit dem Arbeitsfluidein lass (4) verbundenen Arbeitsfluidkanal (6) durch die erste, geöffnete Venti leinheit (2) zur zweiten Ventileinheit (3) strömen kann, wobei  - The application of a control pressure in the first control pressure chamber (13) ver pushes the first valve piston (9) from the closed to the open position, whereby the working fluid through a with the Arbeitsfluidein let (4) connected working fluid channel (6) through the first, open Venti leinheit (2) to the second valve unit (3) can flow, wherein
- das Anlegen des Steuerdrucks in der zweiten Steuerdruckkammer (14) zu einem Verschieben des zweiten Ventilkolbens (10) entgegen der Kraft des Federelements (12) in eine dem Steuerdruck zugeordneten Position des Ventilkolbens (10) im Ventilzylinder (8) zwischen der geschlossenen und der geöffneten Stellung führt, wodurch das Arbeitsfluid durch den Arbeits- fluidkanal (6) in der zweiten Ventileinheit (3) zwischen zwei sich gegen überliegenden, zueinander verwinkelten und sich auf der Oberfläche des Ventilzylinders (8) und des Ventilkolbens (10) entlang der Verschieberich tung (V) erstreckenden Ventilflächen (16, 17) hindurchströmt, wobei eine zwischen den Ventilflächen (16, 17) gebildete Ventilöffnung im Arbeitsflu- idkanal (6) in Abhängigkeit des Steuerdrucks entsprechend feinstufig ein stellbar ist und den am Auslass (5) anliegenden Druck des Arbeitsfluids re gelt. - Applying the control pressure in the second control pressure chamber (14) a displacement of the second valve piston (10) against the force of the spring element (12) in a control pressure associated position of the valve piston (10) in the valve cylinder (8) between the closed and the open position, whereby the working fluid through the working fluid channel ( 6) in the second valve unit (3) between two opposing, mutually angled and on the surface of the valve cylinder (8) and the valve piston (10) along the direction Verschieberich (V) extending valve surfaces (16, 17) flows through, said a valve opening formed between the valve surfaces (16, 17) in Arbeitsflu- idkanal (6) in accordance with the control pressure in accordance with a finely adjustable and adjustable at the outlet (5) applied pressure of the working fluid re gelt.
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US20200392972A1 (en) 2020-12-17
RS64404B1 (en) 2023-08-31
EP3746662B1 (en) 2023-06-07
ES2954844T3 (en) 2023-11-27
DE102018102397A1 (en) 2019-08-08
EP3746662C0 (en) 2023-06-07
US11493061B2 (en) 2022-11-08
HRP20230778T1 (en) 2023-10-27
PL3746662T3 (en) 2023-10-30
HUE063189T2 (en) 2023-12-28
CA3089166A1 (en) 2019-08-08
CN111742151A (en) 2020-10-02

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