EP3695125B1 - Système de soupapes et procédé de commande - Google Patents

Système de soupapes et procédé de commande Download PDF

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Publication number
EP3695125B1
EP3695125B1 EP18812035.6A EP18812035A EP3695125B1 EP 3695125 B1 EP3695125 B1 EP 3695125B1 EP 18812035 A EP18812035 A EP 18812035A EP 3695125 B1 EP3695125 B1 EP 3695125B1
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EP
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Prior art keywords
valve
directional valve
directional
compressed air
rest position
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EP18812035.6A
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German (de)
English (en)
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EP3695125A1 (fr
Inventor
Stefan Tadje
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Aventics GmbH
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Aventics GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/008—Valve failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/068—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam with valves for gradually putting pneumatic systems under 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
    • 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
    • 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
    • F15B13/043—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 electrically-controlled pilot valves
    • F15B13/0435—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 electrically-controlled pilot valves the pilot valves being sliding 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
    • F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
    • F15B19/005—Fault detection or monitoring
    • 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
    • F15B2013/041—Valve members; Fluid interconnections therefor with two positions
    • 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
    • F15B2013/0412—Valve members; Fluid interconnections therefor with three positions
    • 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
    • F15B2211/3138—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/322—Directional control characterised by the type of actuation mechanically actuated by biasing means, e.g. spring-actuated
    • 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
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8636—Circuit failure, e.g. valve or hose failure
    • 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
    • F15B2211/865—Prevention of failures
    • 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
    • F15B2211/87—Detection of failures
    • 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
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8757—Control measures for coping with failures using redundant components or assemblies
    • 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 valve arrangement and a control method for the safe control of pneumatic drives.
  • pneumatically pilot-operated valves with an electrically directly operated preliminary stage (pilot valve, pilot valve) and a main stage (main valve) that is pneumatically operated indirectly via the preliminary stage is known in the prior art.
  • Such pneumatically piloted valves are also referred to as multi-stage valves and include, for example, as a preliminary stage an electrically operated 3/2-way pilot solenoid valve in seat valve design (also referred to as a "pilot solenoid valve") with a mechanical spring return and, as the main stage, a 5 pneumatically operated against a mechanical spring / 2-way slide valve in longitudinal or piston valve design.
  • the electrically operated 3/2-way solenoid pilot valve switches the control air present at its inlet to the likewise spring-loaded longitudinal or piston slide of the main stage.
  • the control air can be drawn from the pilot valve either internally via the compressed air connection of the multi-stage valve (i.e. the compressed air supply switched from the main stage to the working connections of the drive) or externally via a separate control air connection.
  • An external supply of the control air is used, for example, when the main stage is only to switch very low pressures that are not sufficient to actuate the drive piston itself.
  • pilot-operated valves of this kind When used in safety-related applications, pilot-operated valves of this kind have the disadvantage that a possible break in the spring of the pilot-control valve reduces its closing force and the applied air pressure pushes the pilot-control valve open and thus control air can reach the drive spool or piston of the main stage. This can switch the main stage and unexpectedly act on the pneumatic drive automatically.
  • the 5/2-way valve 101 designed as an electro-pneumatically piloted valve is arranged directly upstream of the working connections 103 and 104, which it connects in an idle and a switching position alternately in opposite directions with the compressed air connection 105 and one of the compressed air outlets 106 or 107 (also referred to as exhaust air connections) .
  • the two chambers of a double-acting pneumatic drive connected to the working connections 103 and 104 are alternating via the valve 101 in its two switching states (rest position on the one hand and switching position on the other hand) acted upon and vented in opposite directions.
  • the control air supply of the pilot valve 108 which provides the control air required to act on the main stage 109 of the valve 101, is preceded by the valve 102, which is designed as an electropneumatically piloted 3/2-way valve 102 with the pilot valve 110.
  • the pilot valve 110 draws the control air it has switched internally via the compressed air connection 111.
  • the valve 102 releases the compressed air supply for the pilot valve 108 of the valve 101 in its switching state and blocks it in its rest position. Both valves 101 and 102 must therefore always switch at the same time in order to be able to bring about a change of state at the working connections 103 and 104.
  • Such a circuit has the advantage that a spring break in one of the two pilot valves 108 or 110 without an input signal alone cannot lead to a change of state at the working connections 103 and 104.
  • a spring break in the pilot valve 110 can possibly lead to the switching of the main stage 112 of the valve 102, which would result in the provision of a control pressure at the pilot valve 108.
  • the valve 101 does not change its switching state.
  • a spring break in the pilot valve 108 alone cannot switch the valve 101 because there is no control pressure at the pilot valve 108, since the valve 102 does not switch due to the lack of an electrical control signal.
  • a disadvantage of such a circuit is that a spring break in only one of the two pilot valves 108 or 110 cannot be detected during operation. In these two cases, the two valves 101 and 102 would switch when an electrical control signal is applied, because the pilot valves 108 and 110 are electromagnetically direct switching and change their position in each case even without a counterforce.
  • a valve arrangement with two series-connected, automatically resetting main valves and their respective associated pilot valves is known, which can be used, for example, to control a double-acting pneumatic cylinder.
  • the main valves are arranged in a rest position and a switching position for alternately opposing loading and venting of the two chambers of the working cylinder, with both main valves having to switch to take up the switching position.
  • the main valves are each designed to operate switches which enable the electrically operated pilot valves to be electrically operated via external relays. Electrical actuation only takes place when both main valves are in their rest position and the switches are closed.
  • the DE 10 2007 041 583 A1 discloses a valve arrangement with a first main valve controlled by a first pilot valve and a second main valve controlled by a second pilot valve, which are interconnected in this way are that with simultaneous activation of the two main valves by means of the pilot valves, a switching process takes place from a basic position to a working position, whereby two working connections are alternately acted upon and vented in opposite directions in the basic and in the working position.
  • a pneumatic circuit with two changeover valves upstream of the pilot valves, each with three connections, is provided, which is relatively complex and a relatively complex pneumatic ducting and interconnection with one requires correspondingly large installation space.
  • the DE 10 2009 037 120 A1 discloses a pneumatic safety valve device with two bistable main valves, each of which can be actuated by a pilot valve in order to be able to be switched into a working position in which they cause a pneumatic pressure to be applied to two working connections.
  • the structural design of the safety valve device causes the main valves to switch to the working position only when the two pilot valves are actuated essentially synchronously. If only one of the main valves is switched to the working position with only asynchronous actuation, this error state remains stored until a reset takes place by means of a separate reset valve device.
  • the pneumatic interconnection of the safety valve device is relatively complex due to its purpose of providing pneumatic error storage and requires a relatively complex pneumatic channel routing and interconnection with a correspondingly large installation space.
  • the invention is based on the object of avoiding the disadvantages presented.
  • a structurally simple valve arrangement for the safe control of pneumatic drives is to be created, which offers protection against a sudden automatic change in the initial switching position without an input signal in the event of an error in a reset device of a preliminary stage and, in this case, enables effective error detection by purely pneumatic means.
  • the core of the invention is formed by a valve arrangement comprising a first and a second working connection that can be connected to a pneumatic drive and a first and a second, each electro-pneumatically piloted directional valve, in which one or both directional valves is or are upstream of the working connections to act on and vent them , whereby the preliminary stages of both directional valves are designed to be automatically resetting and the second directional valve is designed to alternately assume a rest position and a switching position and the preliminary stage of the first directional valve has an external control connection which can be acted upon via the second directional valve in its switching position and vented in its rest position is, wherein the second directional valve as a return device for the main stage has an externally pressurized and ventable air spring via the first directional valve and a change of state between pressurization or venting of the air spring of the two iten directional valve after the first directional valve has assumed a switching position only takes place as a function of the change in the switching state of the first directional valve,
  • valve arrangement a structurally simple control for a double-acting pneumatic drive is provided, which offers effective protection against a sudden automatic change in the initial switching position without an input signal in the event of an error in a reset device of a preliminary stage and which in this case also provides effective error detection purely pneumatic means made possible.
  • the valve arrangement effects the alternating loading and venting of the working connections and thus the control of a double-acting pneumatic drive connected to the working connections in its two directions of movement. Due to the redundant arrangement of the two directional control valves, the basic fault exclusion is initially ensured that there is a fault in the reset device one of the two preliminary stages (e.g.
  • a spring break in a pilot valve does not lead to an unintentional change of state at the working connections.
  • Both directional control valves must always switch in order to be able to bring about a change of state at the working connections (venting / admission in opposite directions).
  • a fault in the preliminary stage of the second directional valve in the non-actuated (de-energized) rest position can indeed lead to the switching of its main stage, which would result in the provision of a control pressure at the control connection of the first directional valve.
  • the first directional control valve does not change its switching state.
  • the valve arrangement has the further advantage that an error in one of the two preliminary stages of the two directional control valves is reliably detected from the outside during operation. For example, when electrical control signals are applied, the two directional control valves initially switch normally in one of the two pilot control valves, even in the event of a fault in the reset device, because the electrically actuated (for example, by means of switching magnets) pre-stages their position in each case without the counterforce of an automatic reset device (e.g. a mechanical Spring) change.
  • an automatic reset device e.g. a mechanical Spring
  • the main stage of the second directional valve cannot return to its rest position, even when the air spring is acted upon by the first directional valve, because Due to the defective pilot valve, which cannot switch back, there is still a control pressure that counteracts the return movement of the main stage (which, in contrast to the functionality of the first directional valve, is not controlled externally).
  • the state of a chamber of the pneumatic drive connected to the working connection concerned cannot change from loading to venting or vice versa, the movement of the pneumatic drive is blocked.
  • the pneumatic drive cannot retract, the error is recognized.
  • neither the first nor the second directional control valve return to their rest position because they block each other.
  • the main stage of the first directional valve cannot switch back as long as the second directional valve has not switched back because a control pressure that counteracts the return movement of its main stage is still present via the control connection and the defective preliminary stage of the first directional valve.
  • the main stage of the second directional valve in turn, cannot switch back as long as the main stage of the first directional valve has not switched back because the air spring, which is externally applied via the first directional valve in its rest position, does not build up any pressure. Since there is no new change in status at the working connections and thus no new status change (reversed, opposite pressure / venting) occurs on a connected pneumatic drive, a pneumatic drive connected to the working connections cannot retract and the error is recognized. A pneumatic drive connected to the working connections can therefore not change its state in both fault cases. Both error cases can therefore be recognized from the outside based on the unchanged position of the drive after switching.
  • the main stages of the two directional valves are designed in slide and / or the preliminary stages of the two directional valves in seat design.
  • the first directional valve is designed to alternate between a rest position and a switching position with an automatically resetting main stage
  • the second directional valve connects the external control connection of the first directional valve in its switching position via a control line with a compressed air source and in its rest position with a compressed air outlet and its air spring is acted upon via the first directional valve in its rest position and vented in its switching position
  • the first directional valve upstream of the two working connections is and in the switching position connects the first working connection with a compressed air source and the second working connection with a compressed air outlet and in the rest position the second working connection with a compressed air q uelle and the first working connection connects to the control line via a connecting line, a non-return valve blocking in the opposite direction being
  • valve arrangement a structurally simple control for a double-acting pneumatic drive is provided, which offers effective protection against a sudden automatic change in the initial switching position without an input signal in the event of an error in a reset device of a preliminary stage and which in this case also provides effective error detection made possible by purely pneumatic means.
  • the valve arrangement in the parallel rest and switching positions of the two directional control valves causes alternating opposing loading and venting of the working connections and thus the control of a double-acting pneumatic drive connected to the working connections in its two directions of movement. Due to the redundant arrangement of the two directional control valves, the basic fault exclusion is first ensured that a fault in the reset device of one of the two preliminary stages (e.g.
  • a spring break in a pilot valve does not lead to an unintentional change in the status of the working connections.
  • Both directional control valves must always switch together in order to be able to bring about a change of state at the working connections (opposing loading / venting).
  • An error in the resetting device of the preliminary stage of the second directional control valve in its unactuated The (de-energized) rest position can lead to the switching of its main stage, which would result in the provision of a control pressure at the control connection of the first directional valve.
  • the first directional control valve does not change its switching state.
  • the check valve or the throttle device prevent or delay the application of the first working connection via the control line, the connecting line and the first directional valve, which is in the rest position, either completely, or at least in such a way that this does not result in a dangerous - sudden - movement of one the working connection connected to the pneumatic drive.
  • valve arrangement is designed exclusively with a throttle device upstream of the compressed air connection of the second directional valve instead of a check valve, in the event of a fault in the resetting device of the preliminary stage of the second directional valve in the unactuated rest position - depending on the nature of a pneumatic drive connected to the working connections - a change of state occurs (Loading) of the first working connection is not completely prevented in every case.
  • the second working connection is acted upon at the same time via the first directional control valve and the compressed air source, there is basically a counter-pressure that counteracts the unintentional change in position of a pneumatic drive connected to the working connections.
  • the throttle device ensures that a change in position can at best occur at a significantly reduced speed, which as a rule satisfies existing practical requirements for operational safety and at the same time also ensures recognizability of the error.
  • a fault in the resetting device of the preliminary stage of the first directional valve in the unactuated (de-energized) rest position cannot switch its main stage because there is no control pressure at its preliminary stage because the second directional valve does not switch without an electrical control signal.
  • the valve arrangement has the further advantage that a fault in the resetting device of one of the two preliminary stages (for example a spring break in a pilot valve) of the two directional control valves is reliably detected during operation.
  • the two directional control valves initially switch normally when electrical control signals are applied, because the electrical actuated preliminary stages change their position in each case even without counterforce of the restoring devices (for example mechanical springs).
  • the first directional valve connects the first working connection to the compressed air source and the second working connection to a compressed air outlet, and a pneumatic drive connected to the working connections changes its position.
  • a pneumatic drive connected to the working connections would not retract again in these error cases when the electrical control signals were removed.
  • the main stage of the second directional control valve cannot return to its rest position despite the action of the air spring, because a control pressure that counteracts the return movement of its main stage is still present via the defective preliminary stage (which, in contrast to the functionality of the first directional control valve, is not controlled externally).
  • the valve arrangement is designed exclusively with a throttle device upstream of the compressed air connection of the second directional valve instead of a non-return valve, there is also no new change in status at the connected cylinder because the first working connection and the associated chamber of the pneumatic drive are still acted upon via the second directional valve and not be vented. Basically, there is a counter-pressure that counteracts the change in position of a pneumatic drive connected to the work connections.
  • the main stage of the first directional valve cannot switch back as long as the second directional valve has not switched back because a control pressure that counteracts the return movement of its main stage is still present via the external control connection.
  • the main stage of the second directional valve in turn cannot switch back as long as the main stage of the first directional valve has not switched back because the air spring, which is only acted upon externally via the first directional valve in its rest position, does not build up any pressure. Since there is no new change in status at the work connections, a pneumatic drive connected to the work connections cannot retract and the error is recognized.
  • the second directional valve is designed as a 3/2-way valve and designed as a return device for the main stage with an air spring that can be acted upon and vented externally via the first directional valve.
  • the second directional valve is designed as a 4/2-way valve and designed as a return device for the main stage with an air spring that can be externally acted upon and vented via the first directional valve.
  • the first directional control valve is designed to alternately assume a rest position and a switching position with an automatically resetting main stage, whereby the second directional valve with the external control connection of the first directional valve in its switching position via a control line a compressed air source and in a rest position with a compressed air outlet and its air spring is acted upon via the first directional valve in its rest position and is vented in its switching position, and wherein the first directional valve is upstream of the first working connection and this in the switching position with a compressed air source and in the rest position connects to a compressed air outlet and wherein the second directional control valve is arranged upstream of the second working connection and connects it in the rest position to a compressed air source and in the switching position to a compressed air outlet.
  • the arrangement of a check valve or a throttle device upstream of the compressed air connection of the second directional control valve is unnecessary due to the changed channel routing while maintaining the desired safety features. Due to the redundant arrangement, both the preliminary stage of the first directional valve, which is formed with the external control connection, and the preliminary stage of the second directional valve must switch in order to be able to bring about a change of state (opposing venting / admission) at the two working connections. In the event of a fault in the resetting device of the preliminary stage of the second directional valve, there is no change of state at the two working connections (venting / loading in opposite directions) because the preliminary stage of the first directional valve does not switch without an electrical control signal.
  • the error in the resetting device of the preliminary stage of the second directional control valve can lead to the switching of its main stage, but this only leads to additional venting of the second working connection as well.
  • the first working connection remains vented via the first directional valve that remains in its rest position.
  • a pneumatic drive connected to the two working connections remains in its position.
  • Even in the event of a fault in the resetting device of the preliminary stage of the first directional valve there is no change of state at the two working connections (venting / loading in opposite directions) because there is no control pressure at its preliminary stage because the second directional valve does not switch without an electrical control signal.
  • the first working connection remains vented via the first directional control valve, the second is pressurized via the second directional control valve.
  • valve arrangement also has the further advantage in this embodiment that a fault in the resetting device of one of the two preliminary stages of the two directional control valves is reliably detected during operation.
  • the connected pneumatic drive would not retract again in these error cases when the electrical control signals were removed. Because due to the cross-connection, both directional control valves must always switch back so that a new change of state can occur on the connected cylinder (reversed, opposing loading / venting of the working connections).
  • the connected cylinder does not change state again because the second working connection is still vented via the second directional control valve .
  • the first working connection is also vented via the first directional control valve that has returned to its rest position.
  • a pneumatic drive connected to the two working connections remains in its last position.
  • neither the first nor the second directional control valve return to their rest position because they block each other.
  • the main stage of the first directional valve cannot switch back as long as the second directional valve has not switched back because a control pressure that counteracts the return movement of its main stage is still present via the external control connection.
  • the main stage of the second directional valve in turn cannot switch back as long as the main stage of the first directional valve has not switched back because the air spring, which is only acted upon externally via the first directional valve in its rest position, does not build up any pressure.
  • the first working connection remains pressurized via the first directional valve and the second working connection is vented via the second directional valve. Since there is no new change in status at the working connections (venting / admission in opposite directions), a pneumatic drive connected to the working connections cannot retract and the error is recognized.
  • the first directional valve is designed as a 5/2-way valve.
  • the first directional control valve is electropneumatic on both sides Pilot-operated 5/3-way valve designed with an automatically resetting main stage on both sides and designed to take up a vented middle position as the rest position, as well as a first and a second switch position, the first switch position being taken when the pre-stage formed with the external control connection is actuated and acted upon , and wherein the second directional valve connects the external control connection of the first directional valve in its switching position via a control line with a compressed air source and in a rest position with a compressed air outlet and its air spring is acted upon via the first directional valve in its second switching position and vented in its first switching position and rest position , and wherein the first directional control valve is arranged upstream of the first working connection and connects it to a compressed air source in the first switching position and to a compressed air outlet in the second switching position and the rest position t and wherein the second directional control valve is arranged upstream of the second working
  • the arrangement of a check valve or a throttle device upstream of the compressed air connection of the second directional control valve is unnecessary due to the changed channel routing while maintaining the desired safety features. Due to the redundant arrangement, both the preliminary stage of the first directional valve, which is formed with the external control connection, and the preliminary stage of the second directional valve must switch in order to be able to bring about a change of state (opposing venting / admission) at the two working connections. In the event of a fault in the resetting device of the preliminary stage of the second directional valve, there is no change of state at the two working connections (venting / loading in opposite directions) because the preliminary stage of the first directional valve does not switch without an electrical control signal.
  • the error in the resetting device of the preliminary stage of the second directional control valve can lead to the switching of its main stage, but this only leads to additional venting of the second working connection as well.
  • the first working connection remains vented via the first directional valve that remains in its rest position.
  • a pneumatic drive connected to the two working connections remains in its position.
  • Even in the event of an error in the resetting device of the preliminary stage of the first directional valve there is no change of state at the two working connections in the starting position (opposite venting / admission) because there is no control pressure at its preliminary stage, since the second directional valve does not switch without an electrical control signal.
  • the first working connection remains vented via the first directional control valve, the second is pressurized via the second directional control valve.
  • a pneumatic drive connected to the two working connections remains in its position.
  • the valve arrangement also has the further advantage in this embodiment that a fault in the resetting device of one of the two preliminary stages of the two directional control valves is reliably detected during operation.
  • a pneumatic drive connected to the working connections would not retract again in these error cases when the electrical control signals were removed. Because of the cross-connection, both directional control valves always have to change their previously assumed switching state so that a new change in state (reversed, opposing loading / venting of the working connections) can take place on a connected pneumatic drive and the drive can move back again.
  • the second directional control valve is designed as a 5/2-way valve and designed as a return device for the main stage with an air spring that can be externally acted upon and vented via the first directional control valve, unless it is designed as a 3 / 2- or 4/2 -Way valve is provided.
  • the return device of the main stage of the first directional valve is designed in parallel with a mechanical spring and an air spring, the air spring being acted upon externally via the second directional valve in its rest position and its switching position being vented, provided that the first directional valve is used as a directional valve Assumption of two switching states (a rest position and a switching position) is formed.
  • the second directional valve is a 5/2-way valve designed.
  • the first directional control valve for alternately taking a rest position and a switching position is designed with an automatically resetting main stage and designed as a 5/2-way valve, and is arranged upstream of the two working connections and in the switching position with the first working connection a compressed air source and the second working connection with a compressed air outlet and in the rest position connects the second working connection with a compressed air source and the first working connection via a connecting line to the control line, the compressed air connection of the second directional valve being preceded by a throttle device and no check valve being arranged in the connecting line , an additional valve function is achieved through a special control method in which the preliminary stages of the two directional valves can be electrically switched both together and individually.
  • valve arrangement can thereby be controlled overall as a 5/3-way valve with an open middle position (both working connections acted upon).
  • the control position corresponding to a 5/3-way valve in its open central position corresponds to the switching position of only the second directional valve (while the first directional valve is in the rest position).
  • the first directional valve is designed to alternate between a rest position and a switching position with an automatically resetting main stage and is configured as a 5/2-way valve, and is upstream of the first working connection and this is in the switching position with a compressed air source and connects to a compressed air outlet in the rest position
  • the second directional control valve is arranged upstream of the second working connection and connects it in the rest position to a compressed air source and in the switched position to a compressed air outlet
  • the valve arrangement can be controlled as a total of 5/3-way valve with a vented middle position (both working connections vented).
  • the 5/3-way valve in The control position corresponding to its vented middle position corresponds to the switching position of the second directional valve only (while the first directional valve is in the rest position).
  • Fig. 1 shows an embodiment of a valve arrangement according to the invention in the unactuated (de-energized) starting position with all valves in their rest position.
  • the valve arrangement comprises a first working connection 1 and a second working connection 2, which are connected to a pneumatic drive designed as a double-acting pneumatic working cylinder 3.
  • the valve arrangement comprises a first electro-pneumatically pilot-operated directional valve, which is designed as a pilot-operated 5/2-way valve 4 and has a mechanical spring 5 as a restoring device, which automatically switches the main stage 6 of the 5/2-way valve 4, which is spring-loaded by it, into a non-energized state Shifts back to rest position.
  • the 5/2-way valve 4 is designed as a pilot control device with an electromagnetically actuated, automatically resetting pilot valve 7, which switches the main stage 6 of the 5/2-way valve 4 from the rest position to a switching position when a control pressure is actuated and a control pressure is applied to the control port 8.
  • the 5/2-way valve 4 is arranged upstream of the two work connections 1 and 2 and, in the rest position, connects the work connection 1 with the connecting line 9 and the work connection 2 with the compressed air source 10. In the switching position, the 5/2-way valve 4 connects the work connection 1 with the Compressed air source 10 and the working connection 2 with the compressed air outlet 11.
  • a second electro-pneumatically pilot-operated directional control valve which is also designed as a pilot-operated 5/2-way valve 12, is arranged upstream of the control connection 8.
  • the 5/2-way valve 12 is also designed with an electromagnetically actuated, automatically resetting pilot valve 13, which switches the main stage 14 of the 5/2-way valve 12 from the rest position to a switching position when a control pressure is actuated and a control pressure is applied, the pilot valve 13 internally transfers the control pressure required to operate the actuator of main stage 14 refers to the compressed air connection 15.
  • the 5/2-way valve 12 connects the control line 16 and the control connection 8 in the switching position with the compressed air source 10 and in the rest position with the compressed air outlet 17, the non-return valve 18 arranged in the connecting line 9 when the control line 16 is acted upon by the 5 / 2- Directional valve 12 blocks.
  • the left chamber of the pneumatic drive is simultaneously connected to the compressed air outlet 17 via the 5/2-way valve 4, the connecting line 9 and the 5/2-way valve 12 and is therefore vented because the check valve 18 only blocks in the opposite direction.
  • the 5/2-way valve 12 has an air spring 19, which switches the main stage 14 of the 5/2-way valve 12, which is spring-loaded by it, back into a rest position in the de-energized state when a control pressure is applied to the air spring 19.
  • the air spring 19 is acted upon externally via the 5/2-way valve 4 in its rest position via the supply line 20 arranged parallel to the working connection 2.
  • a spring break does not lead to an unintentional movement of one the working connections 1 and 2 leads to the connected pneumatic drive.
  • Both 5/2-way valves 4 and 12 must always switch together in order to be able to bring about a change of state at the working connections 1 and 2 (opposite of the pressurization / venting).
  • a spring break in the pilot valve 13 in the de-energized rest position can lead to the switching of the main stage 14 of the 5/2-way valve 12, which would result in the provision of a control pressure at the pilot valve 7.
  • this does not switch due to the lack of an electrical control signal, the 5/2-way valve 4 does not change its switching state.
  • the check valve 18 prevents the left chamber of the pneumatic working cylinder 3 from being acted upon via the control line 16 and the 5/2-way valve 4, which is in the rest position.
  • Lead 2-way valve 4 because there is no control pressure at the pilot valve 7, since the 5/2-way valve 12 does not switch due to the lack of an electrical control signal.
  • the valve arrangement has the further advantage that a fault, such as a spring break, in one of the two pilot valves 7 or 13 is reliably detected during operation. In both of these cases The two 5/2-way valves 4 and 12 initially switch normally when electrical control signals are applied, because the electromagnetically controlled pilot valves 7 and 13 change their position by a mechanical spring even without a counterforce.
  • the 5/2-way valve 4 connects the working connection 1 with the compressed air source 10 and the working connection 2 with the compressed air outlet 11; the pneumatic working cylinder 3 extends.
  • the pneumatic working cylinder 3 does not retract when the control signals are removed. Because of the cross connection of the two 5/2-way valves 4 and 12, both pilot valves 7 and 13 must always switch back so that a new change in status (opposite venting / admission) can occur at the working connections 1 and 2.
  • the main stage 6 of the 5/2-way valve 4 cannot switch back as long as the 5/2-way valve 12 has not switched back because a control pressure counteracting the spring-loaded main stage 6 is still present via the defective pilot valve 7.
  • the main stage 14 of the 5/2-way valve 12 cannot switch back as long as the main stage 6 of the 5/2-way valve 4 has not switched back because the air spring 19 does not build up any pressure. Since there is no new change of state at the working connections 1 and 2, the working cylinder 3 remains extended and the error is recognized.
  • Fig. 2 shows an alternative embodiment of the valve arrangement according to the invention in the unactuated (de-energized) starting position with all valves in their rest position. Otherwise with the valve arrangement according to Fig. 1 identical valve arrangement is in contrast to the valve arrangement according to Fig. 1 no Check valve arranged in the connecting line 9. Instead, the compressed air connection 15 in the valve arrangement is shown in FIG Fig. 2 upstream of a throttle device, which is designed as a constant cross-sectional constriction 22 in the supply line 21 to the compressed air connection 15 of the 5/2-way valve 12. Furthermore, instead of being a constant cross-sectional constriction 22, the throttle device can also be designed as a variable cross-sectional constriction, for example as a throttle valve.
  • the design as a constant cross-sectional constriction 22 offers a high level of failure safety, since it does not contain any moving parts, but is only a constriction of the respective line cross-section, which can be implemented either when the line is formed or as a subsequently inserted, cross-section narrowing aperture.
  • the valve arrangement is designed as a modular unit with a common base plate for the lines (air ducts and electrical conductors) and connections and valve modules or valve bodies placed on the base plate, as is the case, for example, from the EP 0 463 394 B1 or the DE 39 27 637 C1 disclosed prior art
  • the cross-sectional constriction 22 can further be designed in a structurally simple manner as a section with a smaller diameter in the course of the corresponding channel bore or opening in the base plate.
  • the 5/2-way valve 12 acts - as in the valve arrangement according to FIG Fig. 1 the control connection 8 of the 5/2-way valve 12 by connecting the control line 16 to the compressed air source 10.
  • a spring break in the pilot valve 13 in the de-energized rest position can also occur in this embodiment of the valve arrangement (according to FIG Fig. 2 ) lead to the switching of the main stage 14 of the 5/2-way valve 12, which would result in the provision of a control pressure at the pilot valve 7.
  • the 5/2-way valve 4 does not change its switching state.
  • no non-return valve is arranged in the connecting line 9, this simultaneously leads to an actuation of the valve connection 23 of the 5/2-way valve 4 (which does not switch) in the de-energized rest position and thereby to an actuation of the left chamber of the working cylinder 3 via the control line 16 and the connecting line 9.
  • valve arrangement according to FIG Fig. 1 in the event of a simultaneous spring break in the pilot valve 13 and an error (failure) of the check valve 18. Since in this state the right chamber of the pneumatic drive 3 via the 5/2-way valve 4 is acted upon by the compressed air source 10, in this case of failure there is basically a counter-pressure which counteracts the unintentional extension of the pneumatic drive 3. If the valve arrangement is used to control a pneumatic drive without a piston rod, it is pressure-balanced and does not move if both chambers are acted upon at the same time. However - according to the embodiments according to Fig.
  • the cross-sectional constriction 22 is arranged upstream of the compressed air connection 15 of the 5/2-way valve 12, in the event of such a fault it is ensured that the piston rod not only has a reduced force (compared to normal operation) (corresponding to the force difference applied), but also a reduced force Speed extends. If the extension of the working cylinder 3 is not completely prevented in this error case, however, the execution of a dangerous - sudden - movement is prevented, which as a rule satisfies the practical requirements for the operational safety of such pneumatic drives.
  • Fig. 3 shows an alternative embodiment of the valve arrangement according to the invention in the unactuated (de-energized) starting position with all valves in their rest position.
  • the identical valve arrangement is the compressed air connection 15 of the 5/2-way valve 12 in the valve arrangement Fig. 3 additionally arranged upstream of a throttle device, which is designed as a constant cross-sectional constriction 22 arranged in the supply line 21 to the compressed air connection 15 of the 5/2-way valve 12.
  • This embodiment of the valve arrangement according to the invention therefore offers combined protection against various possible faults in connection with a spring break in the pilot control valve 13 as well as a simultaneous failure of the check valve 18.
  • the check valve 18 prevents the left chamber of the pneumatic working cylinder 3 from being acted upon via the control line 16 and the 5/2-way valve 4, which is in the rest position
  • the activation of a piston rod cylinder ensures that the piston rod only extends at a reduced speed because the cross-sectional constriction 22 is arranged upstream of the compressed air connection 15 of the 5/2-way valve 12.
  • Fig. 4 shows an alternative embodiment of the valve arrangement according to the invention in the unactuated (de-energized) starting position with all valves in their rest position.
  • identical valve arrangement is in contrast to the valve arrangement according to Fig. 1
  • the resetting device of the 5/2-way valve 4 is not designed as a mechanical spring, but rather as an air spring 24, which is constantly acted upon externally by the pressure medium source 10. In this design, the risk of a spring break in the reset device of the main stage 6 is also excluded.
  • the pilot valve 13 receives the control pressure required to actuate the actuator of the main stage 14, in contrast to the valve arrangements according to FIG Figs.
  • valve assembly with two identically designed valve types is possible.
  • the external control air supply to the pilot valve 13 is also not switched in this case, but is constantly connected externally to the compressed air source 13. This is not relevant for the functioning of the valve arrangement, but leads to the possibility of using the same parts (here the valves 4 and 12) during manufacture.
  • the functionality of the valve arrangement that is relevant for the purposes of the application Fig. 4 is, moreover, according to the mode of operation of the valve arrangement Fig. 1 identical.
  • Fig. 5 shows an alternative embodiment of the valve arrangement according to the invention in the (non-actuated) de-energized starting position with all valves in their rest position.
  • identical valve arrangement is in contrast to the valve arrangement according to Fig. 1
  • the resetting device of the 5/2-way valve 4 is also formed parallel to the mechanical spring 5 with the air spring 24, which is externally applied via the 5/2-way valve 12 in its rest position and whose switching position is vented via the compressed air outlet 25.
  • This embodiment serves to increase the vibration and operational stability of the valve arrangement in that the restoring force exerted on the 5/2-way valve 4 is increased by the two restoring devices that are implemented in parallel.
  • this embodiment offers additional security in the event of a break in the spring 5 of the main stage 6, in which the return is still guaranteed by the air spring 24.
  • the functionality of the valve arrangement that is relevant for the purposes of the application Fig. 5 is, moreover, according to the mode of operation of the valve arrangement Fig. 1 identical.
  • Fig. 6 shows an alternative embodiment of the valve arrangement according to the invention in the unactuated (de-energized) starting position with all valves in their rest position.
  • the valve arrangement has one compared to the valve arrangement according to FIG Fig. 1 changed channel routing.
  • the first electro-pneumatically piloted 5/2-way valve 4 is arranged upstream of the first working port 1 and connects it in the rest position to the compressed air outlet 26 and in the switching position to the compressed air source 10.
  • the second electro-pneumatically piloted 5/2-way valve 12 is arranged upstream of the second working port 2 and connects this via the supply line 27 in the rest position with the compressed air source 10 and in the switching position with the compressed air outlet 25.
  • the air spring 19 is external via the 5/2-way valve 4 is applied via the supply line 28 in its rest position.
  • both the arrangement of a check valve in the connecting line 9 and a throttle device upstream of the compressed air connection 15 of the second 5/2-way valve 12 are dispensable. Due to the redundant arrangement, both the pilot valve 7 of the first 5/2-way valve 4, which is configured with the external control port 8, and the pilot valve 13 of the second 5/2-way valve 12 must switch so that a change of state at the two working ports 1 and 2 ( opposing venting / admission) occurs.
  • a fault in the resetting device of one of the two pilot control valves 7 or 13 cannot lead to an unintentional movement of a pneumatic drive connected to the working connections 1 and 2.
  • a spring break in the pilot valve 13 there is no change of state at the two working connections 1 and 2 (venting / loading in opposite directions) because the pilot valve 7 does not switch without an electrical control signal.
  • a spring break in the pilot valve 13 can lead to the switching of its main stage 14, but this only leads to additional venting of the second working connection 2 via the compressed air outlet 25.
  • the first working connection 1 remains vented via the first 5/2-way valve 4, which remains in its rest position.
  • the working cylinder 3 connected to the two working connections 1 and 2 remains in its position.
  • the valve arrangement also has the further advantage in this embodiment that a fault in the resetting device of one of the two pilot control valves 7 or 13 (for example a spring break) is reliably detected during operation.
  • the main stage 14 of the 5/2-way valve 12 cannot switch back despite the action of the air spring 19 because a control pressure counteracting the main stage 14 is still present via the defective pilot valve 13, which receives the control pressure internally via the compressed air connection 15.
  • the first working connection 1 is also vented via the 5/2-way valve 4 that has returned to its rest position.
  • the pneumatic working cylinder 3 remains extended.
  • neither the 5/2-way valve 4 nor the 5/2-way valve 12 switch because they block each other.
  • the main stage 6 of the 5/2-way valve 4 cannot switch back as long as the 5/2-way valve 12 has not switched back because a control pressure counteracting the spring-loaded main stage 6 is still present via the defective pilot valve 7.
  • the main stage 14 of the 5/2-way valve 12 cannot switch back as long as the main stage 6 of the 5/2-way valve 4 has not switched back because the air spring 19 does not build up any pressure. Since there is no new change in status at the working connections 1 and 2, the pneumatic working cylinder 3 remains extended and the error is recognized.
  • the first working connection 1 remains pressurized via the first 5/2-way valve 4 and the second working connection is vented via the second 5/2-way valve 12. Since there is consequently no new change in status (venting / loading in the opposite direction) at the working connections 1 and 2, the pneumatic working cylinder 3 cannot retract and the error is recognized.
  • the resetting device of the main stage 6 of the 5/2-way valve 4 can additionally be parallel to the mechanical spring 5 with an air spring in accordance with the embodiment according to FIG Fig. 5 be formed.
  • This air spring is connected to the supply line 27 via a branch and also externally via the 5/2-way valve 12 in its rest position is applied and its switching position is vented via the compressed air outlet 25.
  • Fig. 7 shows an alternative embodiment of the valve arrangement according to the invention in the unactuated (de-energized) starting position with all valves in their rest position.
  • identical valve arrangement is in contrast to the valve arrangement according to Fig. 6 the first electro-pneumatically pilot-operated valve designed as a bilaterally electropneumatically pilot-operated 5/3-way valve 29 with an automatically resetting main stage on both sides and designed to assume a vented middle position as the rest position, as well as a first and a second switching position, the assumption of the first switching position when actuating and The pilot valve 7 'formed with the external control connection 8' is acted upon.
  • the 5/3-way valve 29 is arranged upstream of the first working connection 1 and connects it in the first switching position (switching of the pilot valve 7 ') to the compressed air source 10 and in the second switching position (switching of the pilot valve 30) and the rest position to the compressed air outlet 26.
  • the electro-pneumatically piloted 5/2-way valve 12 is arranged upstream of the second working connection 2 and connects it via the supply line 27 in the rest position to the compressed air source 10 and in the switching position to the compressed air outlet 25.
  • the air spring 19 of the 5/2-way valve 12 is external via the 5/3-way valve 29 is acted upon in its second switching position (switching the pilot valve 30) via the supply line 28 and vented in its first switching position (switching the pilot valve 7 ') and rest position.
  • switching the pilot valve 30 switching the pilot valve 30
  • first switching position switching the pilot valve 7 '
  • both the pilot valve 7 'of the 5/3-way valve 29, which is formed with the external control connection 8', and the pilot valve 13 of the second 5/2-way valve 12 must switch so that a change of state occurs at the two working connections 1 and 2 (opposite ventilation / admission) occurs.
  • a fault in the resetting device of one of the two pilot control valves 7 'or 13 can occur in the starting position do not lead to unintentional movement of a pneumatic drive connected to working connections 1 and 2.
  • a spring break in the pilot valve 13 there is no change of state at the two working connections 1 and 2 (venting / loading in opposite directions) because the pilot valve 7 'does not switch without an electrical control signal.
  • a spring break in the pilot valve 13 can lead to the switching of its main stage 14, but this only leads to additional venting of the second working connection 2 via the compressed air outlet 25.
  • the first working connection 1 remains vented via the 5/3-way valve 29 that remains in its rest position.
  • the working cylinder 3 connected to the two working connections 1 and 2 remains in its position. Even in the event of a spring break in the pilot valve 7 ', there is no change of state at the two working connections 1 and 2 in the initial position (opposite venting / loading), because there is no control pressure at the pilot valve 7' because the second 5/2-way valve 12 has no electrical control signal does not switch.
  • the first working connection 1 remains vented via the 5/3-way valve 29, which remains in its rest position, and the second working connection 2 is acted upon via the second 5/2-way valve 12.
  • the working cylinder 3 connected to the two working connections 1 and 2 remains in its position.
  • the valve arrangement in this embodiment also has the further advantage that a fault in the resetting device of one of the two pilot control valves 7 'or 13 (for example a spring break) is reliably detected during operation. A pneumatic drive connected to the working connections 1 and 2 would not retract again in these error cases when the electrical control signals were removed.
  • the main stage 14 of the 5/2-way valve 12 cannot switch back despite the action of the air spring 19, because via the defective pilot valve 13, which draws the control pressure internally via the compressed air connection 15, a control pressure that counteracts the main stage 14 is still present.
  • the first working connection 1 is also vented via the 5/3-way valve 29 that has returned to its rest position (the vented central position).
  • the pneumatic working cylinder 3 remains extended.
  • neither the 5/3-way valve 29 nor the 5/2-way valve 12 switch because they block each other.
  • the main stage 6 'of the 5/3-way valve 29 cannot switch back as long as the 5/2-way valve 12 has not switched back, because a control pressure counteracting the spring-loaded main stage 6' is still present via the defective pilot valve 7 '.
  • the main stage 14 of the 5/2-way valve 12 cannot switch back as long as the main stage 6 'of the 5/3-way valve 29 does not switch to its second switching position (switching of the pilot valve 30) because the air spring 19 does not build up any pressure. Since there is no new change in status at the working connections 1 and 2, the pneumatic working cylinder 3 remains extended and the error is recognized.
  • the first working connection 1 remains pressurized via the first 5/3-way valve 29 and the second working connection is vented via the second 5/2-way valve 12.
  • valve arrangements of the Fig. 6 and Fig. 7 can be manufactured as a modular unit with a base plate and valve modules or valve bodies with the same base plate placed on them due to the identical channel routing in the design. This makes it possible to use the same parts for the base plate in the manufacture of both valve assemblies in FIG Fig. 6 and 7th .
  • the different valve functions result only from the different design of the first directional valve, which can be changed by exchanging on the same base plate.
  • Fig. 8 shows a tabular representation of switching positions of the valve arrangement according to FIG Fig. 2 in comparison with the switching positions of a commercially available 5/3-way valve 29 ', which is electro-pneumatically piloted on both sides, with an open middle position (both working connections acted upon).
  • the pilot valves 7 and 13 of the valve arrangement according to Fig. 2 both together and individually electrically are designed to be switchable, an additional valve function is achieved with the control positions made possible by this.
  • the possible control positions are in the rows of the table Fig. 8
  • the information in the first column denotes the respective switching positions of the pilot valve 7 and the information in the second column denotes the respective switching positions of the pilot valve 13, both in each case based on the design of the valve arrangement according to FIG. Fig.
  • the indication "On” denotes the actuation of the corresponding pilot valve, whereby the directional valve pneumatically piloted by it assumes its switching position.
  • the indication “Off” denotes the non-actuation of the corresponding pilot valve, as a result of which the directional valve pneumatically piloted by it assumes its rest position.
  • the valve arrangement is shown in FIG Fig. 2 can be controlled with these control positions overall in accordance with the mode of operation of a commercially available 5/3-way valve 29 'with an open middle position (both working connections acted upon).
  • the in Fig. 8 specified control positions of the valve assembly according to. Fig.
  • Fig. 9 shows a tabular representation of switching positions of the valve arrangement according to FIG Fig. 6 in comparison with the switching positions of a commercially available 5/3-way valve 29 ′′ which is electro-pneumatically piloted on both sides and has a vented middle position Fig. 6 are designed to be electrically switchable both jointly and individually, an additional valve function is achieved with the control positions made possible by this.
  • the possible control positions are in the rows of the table Fig. 9 shown, the information in the first column designating the respective switching positions of the pilot valve 7 and the information in the second column the respective switching positions of the Designate pilot valve 13, both based on the design of the valve assembly according to FIG. Fig. 6 .
  • the indication "On” denotes the actuation of the corresponding pilot valve, whereby the directional valve pneumatically piloted by it assumes its switching position.
  • the indication “Off” denotes the non-actuation of the corresponding pilot valve, as a result of which the directional valve pneumatically piloted by it assumes its rest position.
  • the valve arrangement is shown in FIG Fig. 6 with these control positions can be controlled overall in accordance with the mode of operation of a commercially available 5/3-way valve 29 ′′ with a vented middle position (both working connections vented)
  • Fig. 9 specified control positions of the valve assembly according to. Fig.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)

Claims (12)

  1. Agencement de vannes, comprenant un premier et un second raccords de travail (1; 2) qui peuvent être reliés à un entraînement pneumatique et une première et une seconde vannes directionnelles à commande électropneumatique (4, 29 ; 12) respectives, une ou les deux vannes directionnelles (4, 29; 12) étant disposées en amont des raccords de travail (1; 2) pour leur sollicitation et leur désaération, les étages préliminaires (7; 13) des deux vannes directionnelles (4, 29; 12) étant conçus pour se réarmer automatiquement et la seconde vanne directionnelle (12) étant conçue pour alterner entre une position de repos et une position de commutation et l'étage préliminaire (7,7') de la première vanne directionnelle (4, 29) présentant un raccord de commande externe (8; 8'), lequel peut être sollicité par l'intermédiaire de la seconde vanne directionnelle (12) dans sa position de commutation et être désaéré dans sa position de repos, caractérisé en ce que la seconde vanne directionnelle (12) présente , en tant que dispositif de retour pour un étage principal (14), un ressort pneumatique (19) qui peut être sollicité et désaéré de l'extérieur par l'intermédiaire de la première vanne directionnelle (4, 29), et un changement d'état entre la sollicitation ou la désaération du ressort pneumatique (19) de la seconde vanne directionnelle (12) après la prise d'une position de commutation par la première vanne directionnelle (4, 29) n'a lieu seulement qu'en fonction du changement de l'état de commutation de la première vanne directionnelle (4, 29), et un changement d'état entre la sollicitation ou la désaération au niveau de l'un ou des deux raccords de travail (1; 2) après une sollicitation ou une désaération qui a lieu préalablement à la prise de la position de commutation par la seconde vanne directionnelle (12) n'a lieu qu'en fonction de la prise de la position de repos par la seconde vanne directionnelle (12).
  2. Agencement de vannes selon la revendication 1, caractérisé en ce que les étages principaux (6, 6'; 14) des deux vannes directionnelles sont réalisés sous forme de coulisseaux et/ou les étages préliminaires des deux vannes directionnelles sont réalisés sous forme de construction de siège.
  3. Agencement de vannes selon la revendication 1 ou 2, dans lequel la première vanne directionnelle est conçue pour prendre de manière alternative une position de repos et une position de commutation comportant un étage principal (6) à réarmement automatique, caractérisé en ce que la seconde vanne directionnelle relie le raccord de commande externe (8) de la première vanne directionnelle, dans sa position de commutation, à une source d'air comprimé (10) et, dans sa position de repos, à une sortie d'air comprimé (17) par l'intermédiaire d'une conduite de commande (16), et son ressort pneumatique (19) est sollicité par l'intermédiaire de la première vanne directionnelle dans sa position de repos et désaéré dans sa position de commutation, et dans lequel la première vanne directionnelle est disposée en amont des deux raccords de travail (1; 2) et, dans la position de commutation, relie le premier raccord de travail (1) à une source d'air comprimé (10) et le second raccord de travail (2) à une sortie d'air comprimé (11) et, dans la position de repos, relie le second raccord de travail à une source d'air comprimé (10) et le premier raccord de travail (1) à la conduite de commande (16) par l'intermédiaire d'une conduite de liaison (9), dans lequel une vanne anti-retour (18) à verrouillage dans le sens inverse est disposée dans la conduite de liaison (9) et/ou un dispositif d'étranglement est disposé en amont du raccord d'air comprimé (15) de la seconde valve directionnelle.
  4. Agencement de vannes selon l'une des revendications 1 à 3, caractérisé en ce que la seconde vanne directionnelle est réalisée en tant que vanne directionnelle à 3/2 voies.
  5. Agencement de vannes selon l'une des revendications 1 à 3, caractérisé en ce que la seconde vanne directionnelle est réalisée en tant que vanne directionnelle à 4/2 voies.
  6. Agencement de vannes selon la revendication 1 ou 2, dans lequel la première vanne directionnelle est conçu pour prendre de manière alternative une position de repos et une position de commutation comportant un étage principal (6) à réarmement automatique, caractérisé en ce que la seconde vanne directionnelle relie le raccord de commande externe (8) de la première vanne directionnelle, dans sa position de commutation, à une source d'air comprimé (10) par l'intermédiaire d'une conduite de commande (16) et, dans une position de repos, à une sortie d'air comprimé (17), et son ressort pneumatique (19) est sollicité par l'intermédiaire de la première vanne directionnelle dans sa position de repos et désaéré dans sa position de commutation, et dans lequel la première vanne directionnelle est disposée en amont du premier raccord de travail (1) et le relie, dans la position de commutation, à une source d'air comprimé (10) et, dans la position de repos, à une sortie d'air comprimé (11), et dans lequel la seconde vanne directionnelle est disposée en amont du second raccord de travail (2) et le relie, dans la position de repos, à une source d'air comprimé (10) et, dans la position de commutation, à une sortie d'air comprimé (25).
  7. Agencement de vannes selon l'une des revendications 1 à 6, caractérisé en ce que la première vanne directionnelle est réalisée en tant que vanne directionnelle à 5/2 voies (4).
  8. Agencement de vannes selon la revendication 1 ou 2, dans lequel la première vanne directionnelle est réalisée en tant que vanne directionnelle (29) à 5/3 voies à commande électropneumatique des deux côtés comportant un étage principal (6') à réarmement automatique des deux côtés et est conçue pour prendre une position médiane désaérée en tant que position de repos, ainsi qu'une première et une seconde positions de commutation, dans lequel la prise de la première position de commutation a lieu lors de l'actionnement et de la sollicitation de l'étage préliminaire conçu avec le raccord de commande externe (8'), caractérisé en ce que la seconde vanne directionnelle relie le raccord de commande externe (8') de la première vanne directionnelle, dans sa position de commutation, à une source d'air comprimé (10) par l'intermédiaire d'une conduite de commande (16) et, dans une position de repos, à une sortie d'air comprimé (17), et son ressort pneumatique (19) est sollicité par l'intermédiaire de la première vanne directionnelle dans sa seconde position de commutation, et est désaéré dans sa première position de commutation et position de repos, et dans lequel la première vanne directionnelle est disposée en amont du premier raccord de travail (1) et le relie, dans la première position de commutation, à une source d'air comprimé (10) et, dans la seconde position de commutation et la position de repos, à une sortie d'air comprimé (26), et dans lequel la seconde vanne directionnelle est disposée en amont du second raccord de travail (2) et le relie, dans la position de repos, à une source d'air comprimé (10) et, dans la position de commutation, à une sortie d'air comprimé (25).
  9. Agencement de vannes selon l'une des revendications 1 à 3, 6 ou 8, ou l'une des revendications 1 à 3 ou 6 en combinaison avec la revendication 7, caractérisé en ce que la seconde vanne directionnelle est réalisée en tant que vanne directionnelle à 5/2 voies (12).
  10. Agencement de vannes selon l'une des revendications 1 à 3, 6 ou 7 en combinaison avec la revendication 9, caractérisé en ce que le dispositif de rappel de l'étage principal (6) de la première vanne directionnelle est conçu parallèlement à un ressort mécanique (5) et un ressort pneumatique (24), dans lequel le ressort pneumatique (24) est sollicité de l'extérieur par l'intermédiaire de la seconde vanne directionnelle dans sa position de repos et est désaéré dans sa position de commutation.
  11. Procédé de commande pour un agencement de vannes selon les revendications 3 et 7 ou les revendications 3 et 7 en combinaison avec l'une des revendications 4, 5 ou 9, ou les revendications 3 et 7 et la revendication 10, ou les revendications 3, 7, 9 et 10, dans lequel le raccord d'air comprimé (15) de la seconde vanne directionnelle est disposé en amont d'un dispositif d'étranglement et aucune vanne anti-retour n'est disposée dans la conduite de liaison (9), caractérisé en ce que les étages préliminaires des deux vannes directionnelles sont conçus pour être commutables électriquement à la fois conjointement et individuellement.
  12. Procédé de commande pour un agencement de vannes selon les revendications 6 et 7, ou les revendications 6, 7 et 9, ou les revendications 6, 7, 9 et 10, caractérisé en ce que les étages préliminaires des deux vannes directionnelles sont commutables électriquement à la fois conjointement et individuellement.
EP18812035.6A 2017-10-10 2018-10-03 Système de soupapes et procédé de commande Active EP3695125B1 (fr)

Applications Claiming Priority (2)

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DE102017009374.1A DE102017009374B4 (de) 2017-10-10 2017-10-10 Ventilanordnung und Steuerungsverfahren
PCT/DE2018/000282 WO2019072328A1 (fr) 2017-10-10 2018-10-03 Système de soupapes et procédé de commande

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EP (1) EP3695125B1 (fr)
CN (1) CN111656021B (fr)
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Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA3129682A1 (fr) * 2019-02-07 2020-08-13 Equalaire System, Inc. Systeme de commande d'essieu relevable
DE102019113640B3 (de) * 2019-05-22 2020-09-17 Heraeus Medical Gmbh Differenzdruckmotor und Verfahren zum Betreiben eines Differenzdruckmotors
CN110529449B (zh) * 2019-09-24 2021-03-09 中国航空工业集团公司沈阳飞机设计研究所 一种液压伺服阀高可靠性卸压装置及方法
US11572901B2 (en) * 2020-03-16 2023-02-07 Woodward, Inc. Redundant electrohydraulic positioning control system
DE102020213812B3 (de) 2020-11-03 2022-02-10 Festo Se & Co. Kg Ventilanordnung
WO2022107230A1 (fr) * 2020-11-18 2022-05-27 Smc株式会社 Circuit de commande pneumatique équipé de caractéristique de sécurité
DE102021118895A1 (de) * 2021-07-21 2023-01-26 Zf Cv Systems Global Gmbh Elektropneumatische Feststellbremseinheit mit Selbsthaltung im Fehlerfall
EP4212741A1 (fr) 2022-01-18 2023-07-19 Asco Numatics GmbH Dispositif et procédé de commande et de régulation de flux de fluide
DE102022001747B3 (de) * 2022-05-18 2023-07-20 Günther Zimmer Pneumatische Bestätigungsvorrichtung und Einheit

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3712481A1 (de) 1987-04-13 1988-10-27 Herion Werke Kg Ventilanordnung mit sicherheitsfunktion
DE3927637C1 (fr) 1989-08-22 1990-03-01 Robert Bosch Gmbh, 7000 Stuttgart, De
DE4020024A1 (de) 1990-06-23 1992-01-02 Bosch Gmbh Robert Elektromagnetisch betaetigbares wegeventil
DE4221756C2 (de) * 1992-07-02 2003-06-12 Bosch Rexroth Ag Sicherheitsschaltung für hydraulische Verbraucher
JPH10169805A (ja) 1996-12-05 1998-06-26 Smc Corp パイロット式切換弁
DE19909920A1 (de) * 1999-03-06 2000-09-07 Bosch Gmbh Robert Sicherheitsschaltung für einen pneumatischen Motor
DE19948747C2 (de) 1999-10-09 2003-10-02 Bar Pneumatische Steuerungssys Einrichtung zur Sicherheitsrückstellung einer pneumatischen Betätigungsvorrichtung
DE10006367A1 (de) * 2000-02-12 2001-08-16 Festo Ag & Co Fluidtechnisches System mit Sicherheitsfunktion
AUPR616101A0 (en) 2001-07-02 2001-08-02 Hodges, Murray Andrew Safety device for fluid operated machines
DE10310314B4 (de) * 2003-03-10 2006-04-27 Sauer-Danfoss Aps Antriebsanordnung, insbesondere Hebevorrichtung eines Arbeitsfahrzeugs
DE102007041583B4 (de) 2007-09-01 2012-05-24 Festo Ag & Co. Kg Ventileinrichtung
DE102009037120B4 (de) 2009-08-11 2012-12-06 Festo Ag & Co. Kg Pneumatische Sicherheitsventileinrichtung
EP2644904B1 (fr) * 2012-03-26 2014-11-12 Festo AG & Co. KG Procédé de commande d'un système de travail à actionnement fluidique
US20180073524A1 (en) * 2016-08-12 2018-03-15 Hydraforce, Inc. Hydraulic actuator control system
CN107166081B (zh) * 2017-06-19 2019-03-29 北京航天发射技术研究所 一种用于火箭发射喷水的蝶阀气动冗余系统及其控制方法
US11313391B2 (en) * 2018-05-11 2022-04-26 Sikorsky Aircraft Corporation Actuator system for a fly-by-wire aircraft

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DE102017009374A1 (de) 2019-04-11
EP3695125A1 (fr) 2020-08-19
DE102017009374B4 (de) 2019-08-22
CN111656021A (zh) 2020-09-11
CN111656021B (zh) 2023-02-21
US11359650B2 (en) 2022-06-14
US20200240444A1 (en) 2020-07-30
WO2019072328A1 (fr) 2019-04-18

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