EP2799722A1 - Commande hydraulique et élément logique - Google Patents

Commande hydraulique et élément logique Download PDF

Info

Publication number
EP2799722A1
EP2799722A1 EP13166438.5A EP13166438A EP2799722A1 EP 2799722 A1 EP2799722 A1 EP 2799722A1 EP 13166438 A EP13166438 A EP 13166438A EP 2799722 A1 EP2799722 A1 EP 2799722A1
Authority
EP
European Patent Office
Prior art keywords
control
hydraulic
logic element
load
control pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13166438.5A
Other languages
German (de)
English (en)
Other versions
EP2799722B1 (fr
Inventor
Martin Ascherl
Daniel Burmeister
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
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 Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP13166438.5A priority Critical patent/EP2799722B1/fr
Publication of EP2799722A1 publication Critical patent/EP2799722A1/fr
Application granted granted Critical
Publication of EP2799722B1 publication Critical patent/EP2799722B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B13/027—Check 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
    • F15B13/029—Counterbalance 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance 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
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control

Definitions

  • the invention relates to a hydraulic control according to the preamble of claim 1 and a hydraulic logic element according to the preamble of claim 8.
  • a generic hydraulic control according to EP 24 66 153 A1 provides for the hydraulic consumer in an open neutral position of the three-position proportional directional slide a floating position in which the load-holding valves are acted upon at their Auf Kunststoffen simultaneously with the same control pressures that are tapped by Druckvor Kunststoffungen the directional slide when both proportional magnets are energized simultaneously and the same.
  • the hydraulic consumer is hydraulically blocked in the open neutral position of the directional slide, that the Auf Kunststoffenstra the load-holding valves remain pressure-relieved and shut off the load-holding valves, the proportional solenoids are not energized.
  • the hydraulic consumer is controlled in one direction or the other, only a load-holding valve is acted upon on its control side with a control pressure, which is tapped from the pressurized working line and relatively high.
  • the simultaneously acting control pressures from the pressure pilot controls of the directional slide should also be relatively high, for example about 60 bar, ie, for which both proportional magnets must be energized at the same time and at the same time relatively strong to maximum. This can lead to inappropriate floatation due to improper heating by the proportional solenoids.
  • EP 12 81 872 A and EP 20 31 256 A known hydraulic controls that can be set in addition to the direction control of the hydraulic consumer whose hydraulic blocking but also a floating position, require a structurally complex and expensive four-position proportional directional slide.
  • the directional slide In the floating position, the directional slide, which is switched into an open neutral position, directly connects a control pressure supply with the control sides the two load-holding valves to réellesteuem together.
  • the hydraulic blocking is controlled in a closed neutral position.
  • the invention has for its object to provide a hydraulic control and a logic element for a hydraulic control, which are inexpensive and reliable.
  • the hydraulic control should allow the floating position and the hydraulic blocking of the hydraulic consumer with a cost-effective and small-sized three-position proportional directional slide and simple load-holding valves.
  • the logic element is intended to provide a reliable safety function and only release a pressure-transmitting connection when two at least approximately equal control pressures are present at the same time.
  • the logic element interrupts a pressure transmission between the control pressure supply and the control sides of the load-holding valves.
  • the and logic element is structurally simple and reliable and can be easily integrated in the control pressure circuit of the hydraulic control integrate. Simple load-holding valves can be used. The control behavior is stable and yet sensitive.
  • the logic element is not only useful for those hydraulic controls in which a floating position of a double-acting hydraulic consumer is adjusted via the logic element with a three-position proportional directional valve, but can generally be used in safety-related applications, if necessary, a pressure-transmitting connection only open when two approximately equal pressure signals are applied simultaneously.
  • the logic element adds these two pressure signals across the two series-connected actuating pistons, which only unlock the check valve when the two control pressure signals are approximately equal and simultaneous.
  • the and-logic element responds purely pressure-dependent, i. it does not require a switching magnet or switching operation.
  • the same control pressures are set on the control sides of the two load-holding valves and thus the load-holding valves are opened in the same way.
  • unequal control pressures are set on the control sides of the load-holding valves in order to control the load-holding valves differently and / or differently from one another, if appropriate also in the direction control of the hydraulic consumer, and not only in the floating position.
  • This is preferably accomplished via different nozzle populations in the connections and optionally also in discharge lines connected to the connections to the tank.
  • the responsive logic element first receives the high control pressure from the control pressure supply, e.g. about 60 bar, releases, but this control pressure is modulated or reduced on the way to Aufberichtseite.
  • the nozzle assembly for example, a user-specific adjustment of the Auf Kunststoff s and / or maximum Auf Kunststoffrargues each load-holding valve can make.
  • the and logic element is associated with a discharge relief to the tank comprehensive pressure relief at least for the connections to the Auf Kunststoffen the load-holding valves.
  • a discharge relief to the tank comprehensive pressure relief at least for the connections to the Auf Kunststoffe the load-holding valves.
  • About this pressure relief at least the Auf Kunststoffhestra the load-holding valves are relieved, for example, when the hydraulic consumer must be hydraulically blocked, i. the load-holding valves or one must reliably hold a load.
  • the pressure relief is even incorporated into the logic element and so that the logic element in the control pressure circuit fulfills a further function, in which it is also for the pressure relief, if required by the operating situation.
  • This is effected particularly advantageously by means of a discharge function monitoring, derived from the response of the logic element on the two simultaneously applied control pressure signals slide function in the logic element. For example, if the float position is set, the discharge line is automatically disconnected from the tank.
  • the pressure relief could also take place in another way and separated from the logic element, for example with a nozzle in the discharge line and / or with a relief switching valve, which is deliberately actuated to relieve.
  • a particularly cost-effective and simple limitation has, for example, a screw-adjustable limit stop for the opening stroke of the load-holding valve, which is optionally adjustable from the outside, or a replaceable but built-in limit stop, such as a spacer or a spacer.
  • hydraulic And logic element of the plunger is loaded by spring force in the closing direction of the check valve, and is provided between the actuating piston a relative idle stroke between these limiting coupling. To unlock the check valve, this idle stroke must first be overcome by the other actuating piston.
  • the one actuating piston is a pot piston movable in a first control pressure chamber over a limited stroke, which receives the other, preferably as a solid piston, actuating piston axially displaceable in a limited between the actuating piston second control chamber and as coupling a Leerhubanschlag for the other actuating piston contains.
  • the other actuating piston ultimately actuates the plunger to unlock the check valve, but only if both actuation pistons are simultaneously subjected to a respective control pressure signal in the first and second control pressure chambers.
  • the series arrangement of the actuating piston ensures that when only applying a control pressure, the check valve is not unlocked.
  • a particularly expedient embodiment is characterized by a 2/2-way slide function, which is incorporated for the one actuating piston in the and logic element.
  • This slide function is used to release a pressure relief to the tank when the check valve is not or no longer unlocked.
  • Pressure medium from control pressure lines which must be relieved of pressure in this phase of operation, takes the path via the open slide function through the logic element to the tank.
  • the first control pressure chamber may be provided with a spool bore portion for a spool end of the one actuating piston.
  • the spool bore portion may be bounded by a sealing ring in the axial direction.
  • At this slide bore section of the tank and a discharge relief required for discharge or one side of the check valve are connected. Via the slide function, the discharge line and the tank can be connected or disconnected. In this way, the logic element in a hydraulic control assumes another function.
  • the check valve is acted upon in the reverse direction with control pressure from a control pressure supply to a hydraulic control.
  • the non-return valve is unlocked via both actuating pistons, it connects the control pressure supply with at least one connection to a pressure-dependent operable valve, preferably a load-holding valve openable against spring force in the hydraulic control.
  • a pressure-dependent operable valve preferably a load-holding valve openable against spring force in the hydraulic control.
  • the logic element is designed as Einschraubventil that can be used in a block bore.
  • the logic element can of course also be designed in block construction as a separate assembly.
  • this And logic element in a hydraulic control of a double-acting hydraulic consumer, which is controlled by a three-position proportional directional slide, which not only direction control positions for the hydraulic consumer can be set, but also a hydraulically locked position and a floating position.
  • the floating position is set by simultaneously energizing both proportional solenoids of the directional slide.
  • the proportional solenoids actuate pressure feedforward controls of the directional valve. From these pressure pilot control, a proportional to the energization control pressure signal is derived.
  • both proportional solenoids are energized simultaneously, the simultaneously applied control pressure signals are processed in the logic element in an addition, in order to finally establish a connection from the control pressure supply to the control sides of load-holding valves in the working lines of the hydraulic consumer.
  • the proportional magnets need to be little energized so that they do not experience inappropriate heating even over a long period of floating position.
  • the control pressure signals from the pressure pilot valves of the proportional directional spool may be relatively weak, since the logic element is only required to abut simultaneously and at approximately the same height, and the actuating pistons, like the closing spring of the check valve, may be designed for relatively moderate control pressure signals from the outset ,
  • Fig. 1 In the block diagram of Fig. 1 is of a hydraulic control H, which optionally has a plurality of sections and for the sections together a pump line P, a return line R (to a pump / tank assembly) and to a control pressure supply (not shown) connected control pressure line Z, a section for controlling a double-acting hydraulic consumer V, eg a hydraulic cylinder shown.
  • the control pressure line Z is for example from a (not shown) control pressure pump or via a (not shown) Pressure reducing valve supplied by the pump line P with a substantially constant control pressure of eg about 60 bar, with which a control pressure circuit 10 is fed.
  • the hydraulic consumer V can be connected to at least P, R via working lines A, B and a three-position-way proportional slide W (4/3 slide valve).
  • the directional slide W has two proportional magnets 4, 6, each of which actuate a pressure feedforward control 5, 6 for adjusting a piston slide between three control positions or from a neutral position into two control positions and against the force of a spring arrangement fixing the piston slide in the middle neutral position.
  • pressure feedforward controls 5, 7, for example pressure reducing valves (not shown) are included, which set in accordance with the energization of the respective proportional solenoid 4, 6 on the spool a certain control pressure, which is regulated for example between 0 and about 60 bar.
  • the control pressure acting on the piston slide can be lower than that of the control pressure supply Z even at maximum current supply.
  • the pressure pilot controls 5, 7 are connected via a control line 8 to the control pressure supply.
  • a feed regulator 3 may be provided between the pump line P and the directional slide W.
  • a load-holding valve 11 and 12 is arranged, which is bypassable in the flow direction to the hydraulic consumer V by a check valve 13 and 14 respectively.
  • Each load-holding valve 11, 12 is pressure-controlled upstream and downstream, acted upon by a spring 35 in the reverse direction, and connected to the control pressure circuit 10 at a control side 47 and 48, respectively.
  • B leads between the load-holding valve 11, 12 and the directional slide W a control line 15 and 16 to a shuttle valve 17 and 18, from which control lines 19 and 20 lead to the Aufberichtier 47, 48.
  • control lines 23, 24 are further connected, which are connected together via a control line 25 to the logic element L and in which a pilot-operated check valve 26 is included.
  • a pressure relief D is provided, which includes a leading to the tank R control line 21, 22 respectively to the control lines 15, 16 and a discharge line 49 to or from the and-logic element L.
  • each nozzle can be arranged.
  • the hydraulic consumer V is controllable in both directions of movement with adjustable speed.
  • either the proportional solenoid 4 or the proportional solenoid 6 is energized.
  • the movement speed is proportional to the current supply.
  • the proportional solenoid 6 is energized, via the pressure feedforward 7, the spool up from the in Fig. 1 adjusted neutral position, so that the working line A with P and the working line B is connected to R.
  • the opening check valve 13 the left admission space of the hydraulic consumer V is pressurized.
  • the direction control of the hydraulic consumer V in FIG. 1 to the left is effected by energizing the other proportional magnet 4, so that the load-holding valve 11 is opened by control pressure in the control line 16 tapped off from the working line B.
  • the AND logic element L does not respond, because then only the control line 2 control pressure leads, while the control line 1 is depressurized.
  • the hydraulic control H of Fig. 1 (and Fig. 3 ) is used, for example, in a piste grooming vehicle, a winter utility vehicle, an agricultural vehicle, or the like, to adjust, for example, by means of the hydraulic consumer V an attachment such as a shield, a roller, a plow, or the like.
  • a floating position is required for the hydraulic consumer V or the implement operated by it, ie, both admission chambers of the hydraulic consumer V are to be connected to the tank R.
  • the hydraulic control H contains only a three-position directional slide W, this fourth position is still adjustable as a floating position on the open neutral position by both load-holding valves 11, 12 are turned on. This is done by the and logic element L.
  • both proportional magnets 4, 6 are energized simultaneously and at least approximately equal, for example with at most half maximum current intensity or less, so that in both control lines 1, 2 control pressure is present, which is lower than the control pressure of the control pressure supply Z, For example, in the control line 9.
  • Only at the same time and in about the same control pressure signals in the control lines 1, 2 adds the And logic element L this control pressure signals and unlocks the check valve 26 so that the control pressure from the control line 9 from the logic element L on the Control line 25, the control lines 23, 24, which then switching switching shuttle valves 17, 18 and the control lines 19, 20 is brought to the Aufberichtbloquest 47, 48, and the load-holding valves 11, 12 als mortt (floating position).
  • the control pressure of the control pressure supply Z can be about the same as the direction control of the hydraulic consumer V from the working line A or B for controlling a load-holding valve 11 or 12 tapped control pressure in the lines 15 or 16, the load-holding valves 11, 12 at least largely fully open.
  • the mechanical limitations 27 of the load-holding valves 11, 12 are preferably effective, as well as in the direction control of the hydraulic consumer. That is, the load-holding valves 11, 12 are only turned on as far as the limitations allow 27. there For example, the limits 27 on the load-holding valves 11, 12 can be set the same or different.
  • Fig. 2 shows in section an embodiment of a load-holding valve 11 (12) with, optionally, integrated mechanical limit 27, as symbolically in FIG Fig. 1 indicated.
  • the load-holding valve 11 (12) has a valve cone 28, which here has a conical sealing surface 29 for cooperation with a seat 30 in a ring insert 33.
  • the ring insert is penetrated by axial bores 32, which are part of the check valve 13 (14), which is equipped with a spring-loaded lock plate 31.
  • the seat 30 is disposed in the working line A or B between the side of the hydraulic consumer V and the side of the pump / tank assembly P, R.
  • a spring abutment 34 cooperates, which is acted upon by the spring 35 and presses the valve plug 28 in the shut-off position shown.
  • the bias of the spring 35 is adjusted for example by a replaceable insert 36.
  • a screw-adjustable spring abutment could be provided here.
  • the integrated into the load-holding valve 11 (12) mechanical limit 27 comprises a lock nut 40 securable bolt 38 which forms a stop 39 for the spring abutment 34 with its end and limits the opening stroke or opening cross-section of the valve plug 28 in the seat 30.
  • the stop can thus be adjusted from the outside.
  • a built-in disk or the like could serve as a stop 39.
  • FIG. 3 shown embodiment of the hydraulic control H differs from that of Fig. 1 in just a few details, which will be discussed below.
  • the load-holding valves 11, 12 are in Fig. 3 , optionally, designed without mechanical limitations 27. Further lead from the control lines 23 and 24 control lines 43 and 44 to the tank in which nozzles 45, 46 are included. Furthermore, between the control line 25 and the branches of the control lines 43, 44 of the control lines 23, 24 nozzles 41 and 42 are used.
  • the other functions of the hydraulic control H in Fig. 3 match the basis Fig. 1 described.
  • the floating position is also set by simultaneous moderate energizing of both proportional magnets 4, 6 of the three-position-way proportional directional slider W with the participation of the and logic element L.
  • Fig. 4 shows an embodiment of the And logic element L, the example in the hydraulic controls H of Fig. 1 and 3 is usable, but also in other hydraulic controls, to provide there a safety aspect such that only in the presence of two simultaneous pressure signals with approximately the same pressure values, a pressure transmission path for another possibly higher pressure is released.
  • the and-logic element L in Fig. 4 is designed as Einschraubventil and screwed into a block 52 in a first control pressure chamber 53, which is closed by a screw plug 55.
  • the control line 1 (see Fig. 1 and 3 ) connected to the first control pressure chamber 53.
  • an actuating piston 54 is sealingly displaceable via a stroke X limited by a valve insert 60 (slide fitting).
  • the one actuating piston 54 is designed as a pot piston and contains in the interior in a second control pressure chamber 57, a further actuating piston 56 (eg, a solid piston), which is axially adjustable only over a Leerhub Y due to a arranged in an actuating piston 54 coupling 66 (eg a locking ring) ,
  • the second control pressure chamber 57 is connected through the wall of the one actuating piston 54 between the bottom of the one actuating piston 54 and the further actuating piston 56 to the control line 2 (FIG. Fig. 1 and 3 ) connected.
  • the check valve 26 In the lower end of the bore in the block 52 is the check valve 26, which can be unlocked, for example, by a displaceable in the valve insert 60 plunger 58.
  • the ram 58 becomes acted upon by a spring 59 in the reverse direction of the check valve 26 and faces the underside of the further actuating piston 56.
  • the one actuating piston 54 for example, by a return spring 62 for in Fig. 4 shown exposed position.
  • a 2/2-way slider function F which is part of the basis of the Fig. 1 and 3 explained pressure relief D is.
  • the control line 9 is connected to the control pressure supply Z, while the space containing the spring 59 is connected to the line 25 to the control pressure circuit 10.
  • From the line 25 branches off the discharge line 49, which leads to an opening provided in the first control pressure chamber 53 above the valve insert 60 annular space, is connected to the via a channel 61 in the valve insert 60 of the tank R.
  • the lower end of the further actuating piston 54 has a slide end 64, and below the annular space to which the discharge line 49 leads, a slide bore section 65 is provided whose inner diameter corresponds approximately to the outer diameter of the slide end 64.
  • control lines 1, 2 control pressure, take the actuating piston 54, 56, for example, in Fig. 4 drawn layers.
  • the check valve 26 is in the blocking position.
  • the control lines 25 and the discharge line 49 are depressurized to the tank R.
  • the one actuating piston 54 moves downwards over its stroke X until it optionally engages on an elastic sealing ring 63 arranged in the valve insert 60. Since the control line 2 carries no control pressure, the other actuating piston 56 remains passive, so that the plunger 58 is not acted upon. Does the control line 2 control pressure, however, the control line 1 no control pressure, then moves the other actuating piston 56 via its idle stroke Y up against the coupling 66 at which it is intercepted. The one actuating piston 54 remains in the in Fig. 4 shown position so that the plunger 58 is not acted upon. The check valve 26 holds its blocking position.
  • both control lines 1, 2 at the same time (or optionally with a slight time offset), for example by simultaneous energization of the two proportional magnets 4, 6 in the Fig. 1 and 3 are subjected to control pressure
  • the actuating forces exerted by the two actuating pistons 54, 56 add up and displace the plunger 58 downwards, so that the check valve 26 is hydraulically unlocked and feeds the control pressure from the control line 9 into the control line 25.
  • the slider function F then the discharge line 49 is separated from the tank R, since the slider end 64 is retracted into the slide bore portion 65 and shut off. This way, in the Fig. 1 and 3 set the floating position.
  • control pressures up to about 60 bar, as provided by the control pressure supply Z although the control pressure signals in the control lines 1, 2 can be weaker, eg only 20 to 40 bar to exclude heating problems of the proportional solenoid 4, 6 at a longer duration of the floating position.
  • the proportional solenoids 4, 6 are used, so to speak, only to simultaneously apply two control pressure signals in the control lines 1, 2 with a relatively moderate height to make the AND logic element L to respond and to unlock the check valve 26, thus the higher control pressure from the control pressure supply Z for controlling the load-holding valves 11, 12 is usable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP13166438.5A 2013-05-03 2013-05-03 Commande hydraulique Active EP2799722B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13166438.5A EP2799722B1 (fr) 2013-05-03 2013-05-03 Commande hydraulique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13166438.5A EP2799722B1 (fr) 2013-05-03 2013-05-03 Commande hydraulique

Publications (2)

Publication Number Publication Date
EP2799722A1 true EP2799722A1 (fr) 2014-11-05
EP2799722B1 EP2799722B1 (fr) 2017-07-19

Family

ID=48288872

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13166438.5A Active EP2799722B1 (fr) 2013-05-03 2013-05-03 Commande hydraulique

Country Status (1)

Country Link
EP (1) EP2799722B1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120298892A1 (en) * 2009-11-18 2012-11-29 Knorr-Bremse Systeme Fur Schienenfahrzeuge Gmbh Multi-stage switchable pilot-controlled valve arrangement
CN111442008A (zh) * 2020-04-24 2020-07-24 徐州徐工随车起重机有限公司 一种用于控制高空作业车伸臂的差动平衡阀
CN113227588A (zh) * 2019-02-06 2021-08-06 克斯美库股份有限公司 带保持阀的空气压力缸装置
CN115962175A (zh) * 2023-01-04 2023-04-14 广东实密智能装备有限公司 液压调节阀及阀通量调节方法

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE656144A (fr) *
FR1500028A (fr) * 1966-06-10 1967-11-03 Neyrpic Ets Perfectionnement aux organes pneumatiques de commutation
US3547156A (en) * 1968-06-14 1970-12-15 Towler Hydraulics Ltd Fluid control amplifiers
EP1106840A2 (fr) * 1999-12-10 2001-06-13 Karmann Wilhelm GmbH Circuit hydraulique
EP1281872A1 (fr) 2001-08-04 2003-02-05 Robert Bosch Gmbh Dispositif electro-hydraulique pour le contrôle d'un moteur à double effet
US20050242312A1 (en) * 2004-04-30 2005-11-03 Smc Corporation Two-port valve for vacuum operation
WO2009003500A1 (fr) * 2007-06-30 2009-01-08 Festo Ag & Co. Kg Soupape à fonction et
EP2031256A2 (fr) 2007-08-29 2009-03-04 Robert Bosch GmbH Dispositif de levage et procédé de commande d'un dispositif de levage
EP2466153A1 (fr) 2010-12-17 2012-06-20 HAWE Hydraulik SE Dispositif de commande hydroélectrique

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE656144A (fr) *
FR1500028A (fr) * 1966-06-10 1967-11-03 Neyrpic Ets Perfectionnement aux organes pneumatiques de commutation
US3547156A (en) * 1968-06-14 1970-12-15 Towler Hydraulics Ltd Fluid control amplifiers
EP1106840A2 (fr) * 1999-12-10 2001-06-13 Karmann Wilhelm GmbH Circuit hydraulique
EP1281872A1 (fr) 2001-08-04 2003-02-05 Robert Bosch Gmbh Dispositif electro-hydraulique pour le contrôle d'un moteur à double effet
US20050242312A1 (en) * 2004-04-30 2005-11-03 Smc Corporation Two-port valve for vacuum operation
WO2009003500A1 (fr) * 2007-06-30 2009-01-08 Festo Ag & Co. Kg Soupape à fonction et
EP2031256A2 (fr) 2007-08-29 2009-03-04 Robert Bosch GmbH Dispositif de levage et procédé de commande d'un dispositif de levage
EP2466153A1 (fr) 2010-12-17 2012-06-20 HAWE Hydraulik SE Dispositif de commande hydroélectrique

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120298892A1 (en) * 2009-11-18 2012-11-29 Knorr-Bremse Systeme Fur Schienenfahrzeuge Gmbh Multi-stage switchable pilot-controlled valve arrangement
US9487197B2 (en) * 2009-11-18 2016-11-08 Knorr-Bremse Systme Fur Schienenfahrzeuge Gmbh Multi-stage switchable pilot-controlled valve arrangement
CN113227588A (zh) * 2019-02-06 2021-08-06 克斯美库股份有限公司 带保持阀的空气压力缸装置
CN113227588B (zh) * 2019-02-06 2024-02-06 克斯美库股份有限公司 带保持阀的空气压力缸装置
CN111442008A (zh) * 2020-04-24 2020-07-24 徐州徐工随车起重机有限公司 一种用于控制高空作业车伸臂的差动平衡阀
CN115962175A (zh) * 2023-01-04 2023-04-14 广东实密智能装备有限公司 液压调节阀及阀通量调节方法

Also Published As

Publication number Publication date
EP2799722B1 (fr) 2017-07-19

Similar Documents

Publication Publication Date Title
DE10344480B3 (de) Hydraulische Ventilanordnung
DE102004063044B4 (de) Hydraulische Steuerung
EP2772373B1 (fr) Distributeur proportionnel, circuit hydraulique et système de suspension hydropneumatique doté d'un tel distributeur
EP2294331B1 (fr) Dispositif de vanne hydraulique
EP0279315B1 (fr) Dispositif de commande hydraulique
EP0777829A1 (fr) Dispositif de commande electro-hydraulique pour un consommateur a double action
EP2799722B1 (fr) Commande hydraulique
EP2835540B1 (fr) Entraînement hydraulique
EP4196687A1 (fr) Soupape
EP2157320B1 (fr) Commande hydraulique pour un moteur hydraulique
EP2642132A2 (fr) Agencement de soupape pilote hydraulique et agencement de soupape hydraulique en étant équipé
DE19632368A1 (de) Elektrohydraulisches Regelwegeventil
DE19548943B4 (de) Ventilanordnung
DE3733679C2 (fr)
WO2003087585A1 (fr) Systeme de commande hydraulique faisant appel au principe de la sensibilite de charge
EP1611358B1 (fr) Soupape de distribution a variation continue
EP2157319B1 (fr) Commande hydraulique pour un moteur hydraulique
DE102006004423A1 (de) Ventilanordnung zur Ansteuerung eines Hubwerkes oder Anbaugerätes
DE4418881A1 (de) Hubwerkregelsystem mit Regelventil
DE19702948C2 (de) Ventilanordnung
DE102023204654B4 (de) Ventilbaugruppe zur Betätigung eines Hubwerks
DE3910895A1 (de) Lastunabhaengige steuereinrichtung fuer hydraulische verbraucher
CH653417A5 (de) Hydraulische steuervorrichtung.
DE2926547A1 (de) Regel- und fernsteuerbares hydraulisches servoventil mit mechanischer rueckfuehrung und nothandbetaetigung
EP2047108A1 (fr) Ensemble de soupape à ouverture en fondu (soft start)

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20131217

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F16K 15/18 20060101ALI20170209BHEP

Ipc: F15B 13/02 20060101ALI20170209BHEP

Ipc: F15C 3/06 20060101ALI20170209BHEP

Ipc: F15B 11/024 20060101ALI20170209BHEP

Ipc: F16K 31/122 20060101ALI20170209BHEP

Ipc: F15B 11/00 20060101AFI20170209BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170317

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 910679

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170815

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013007788

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: TROESCH SCHEIDEGGER WERNER AG, CH

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20170719

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: LT

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

Effective date: 20170719

Ref country code: NL

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

Effective date: 20170719

Ref country code: NO

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

Effective date: 20171019

Ref country code: HR

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

Effective date: 20170719

Ref country code: SE

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

Effective date: 20170719

Ref country code: FI

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

Effective date: 20170719

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

Ref country code: LV

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

Effective date: 20170719

Ref country code: ES

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

Effective date: 20170719

Ref country code: RS

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

Effective date: 20170719

Ref country code: PL

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

Effective date: 20170719

Ref country code: BG

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

Effective date: 20171019

Ref country code: IS

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

Effective date: 20171119

Ref country code: GR

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

Effective date: 20171020

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: HAWE HYDRAULIK SE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PCOW

Free format text: NEW ADDRESS: EINSTEINRING 17, 85609 ASCHHEIM (DE)

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013007788

Country of ref document: DE

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

Ref country code: CZ

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

Effective date: 20170719

Ref country code: DK

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

Effective date: 20170719

Ref country code: RO

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

Effective date: 20170719

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502013007788

Country of ref document: DE

Representative=s name: GROSSE, SCHUMACHER, KNAUER, VON HIRSCHHAUSEN, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 502013007788

Country of ref document: DE

Owner name: HAWE HYDRAULIK SE, DE

Free format text: FORMER OWNER: HAWE HYDRAULIK SE, 81673 MUENCHEN, DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

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

Ref country code: SK

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

Effective date: 20170719

Ref country code: SM

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

Effective date: 20170719

Ref country code: EE

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

Effective date: 20170719

Ref country code: IT

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

Effective date: 20170719

26N No opposition filed

Effective date: 20180420

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

Ref country code: SI

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

Effective date: 20170719

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

Ref country code: MT

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

Effective date: 20170719

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20180503

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20180531

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

Ref country code: MC

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

Effective date: 20170719

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: LI

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

Effective date: 20180531

Ref country code: CH

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

Effective date: 20180531

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

Ref country code: LU

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

Effective date: 20180503

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

Ref country code: FR

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

Effective date: 20180531

Ref country code: IE

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

Effective date: 20180503

Ref country code: GB

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

Effective date: 20180503

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

Ref country code: BE

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

Effective date: 20180531

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 910679

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180503

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

Ref country code: AT

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

Effective date: 20180503

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

Ref country code: TR

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

Effective date: 20170719

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

Ref country code: HU

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

Effective date: 20130503

Ref country code: PT

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

Effective date: 20170719

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

Ref country code: MK

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

Effective date: 20170719

Ref country code: CY

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

Effective date: 20170719

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

Ref country code: AL

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

Effective date: 20170719

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230523

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

Ref country code: DE

Payment date: 20250521

Year of fee payment: 13