EP1987257B1 - Pneumatic drive system - Google Patents

Pneumatic drive system Download PDF

Info

Publication number
EP1987257B1
EP1987257B1 EP20070702849 EP07702849A EP1987257B1 EP 1987257 B1 EP1987257 B1 EP 1987257B1 EP 20070702849 EP20070702849 EP 20070702849 EP 07702849 A EP07702849 A EP 07702849A EP 1987257 B1 EP1987257 B1 EP 1987257B1
Authority
EP
European Patent Office
Prior art keywords
position
control valve
output unit
valve means
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20070702849
Other languages
German (de)
French (fr)
Other versions
EP1987257A1 (en
Inventor
José ARANA
Jan-Peter Bender
Dieter Waldmann
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.)
Festo AG and Co KG
Original Assignee
Festo AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE200620002727 priority Critical patent/DE202006002727U1/en
Application filed by Festo AG and Co KG filed Critical Festo AG and Co KG
Priority to PCT/EP2007/000398 priority patent/WO2007096031A1/en
Publication of EP1987257A1 publication Critical patent/EP1987257A1/en
Application granted granted Critical
Publication of EP1987257B1 publication Critical patent/EP1987257B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/064Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam with devices for saving the compressible medium
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20Other details, e.g. assembly with regulating devices
    • F15B15/202Externally-operated valves mounted in or on the actuator
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20Other details, e.g. assembly with regulating devices
    • F15B15/22Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/225Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke with valve stems operated by contact with the piston end face or with the cylinder wall
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30525Directional control valves, e.g. 4/3-directional control valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/32Directional control characterised by the type of actuation
    • F15B2211/327Directional control characterised by the type of actuation electrically or electronically
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/405Flow control characterised by the type of flow control means or valve
    • F15B2211/40515Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/415Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/42Flow control characterised by the type of actuation
    • F15B2211/421Flow control characterised by the type of actuation mechanically
    • F15B2211/424Flow control characterised by the type of actuation mechanically actuated by an output member of the circuit
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/46Control of flow in the return line, i.e. meter-out control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051Linear output members
    • F15B2211/7053Double-acting output members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/80Other types of control related to particular problems or conditions
    • F15B2211/88Control measures for saving energy

Abstract

The invention relates to a pneumatic drive system, having at least one pneumatic drive (2) which has a drive housing (4) and a drive output unit (6) which is moveable relative to said drive housing (4) under pressure loading. The drive output unit (6) comprises a drive output piston (8) which, in the drive housing (4), separates two working chambers (12, 13) from one another, one or both of which chambers (12, 13) are connected to a pneumatic control line (17, 18), in the course of which are connected control valve means (22, 23) which are switchable between an air-saving position and an open position (24) which releases a larger flow cross section than said air-saving position, which control valve means (22, 23) are assigned actuating means (32) which can be activated as a function of the position of the drive output unit (6) and which can bring about a switch of the control valve means (22, 23) into the air-saving position when the drive output unit (6), on account of the compressed air flowing through said control valve means (22, 23) into the pneumatic drive (2), has reached a stroke end position or a position situated a short distance before said stoke end position. The air-saving position has the peculiarity that it is a throttle position (25) which releases a smaller flow cross section than the open position (24).

Description

  • The invention relates to a pneumatic drive system, comprising at least one pneumatic drive having a drive housing and a driven in this regard by Druckluftbeaufschlagung output unit, wherein the output unit includes a driven piston which divides two working chambers of the drive housing from each other, one or both connected to a pneumatic control line are switchable in the course between an air-saving and in this respect a larger flow cross-section openable control valve means which are assigned depending on the position of the output unit activatable actuating means which can cause a switching of the control valve means in the Luftsparstellung when the output unit due to the Through this control valve means in the pneumatic drive incoming compressed air has reached a stroke end position or a short before lying position.
  • One from the EP 0771396 B1 known pneumatic drive system of this type includes a pneumatic crusher designed as Krustenbrecherzylinder which is vertically aligned in the usual position of use and includes a controlled by pressurized pressurized optionally lowerable or liftable output unit whose task is to immerse in a predetermined cycle in a molten aluminum bath, in order to break up a material crust possibly formed on its surface. The direction of movement of the output unit is predetermined by a directional specification valve. In the course of the connected to the lower working chamber of the pneumatic cylinder control line formed by a plunger valve control valve means are switched, which can be switched between a maximum flow enabling open position and the air flow completely shut-off air saving. During most of the lifting movement of the output unit, the control valve means are in the open position, so that a high actuating force can be provided. Shortly before reaching the maximum retracted stroke end position, however, the output unit switches the control valve means into the air-saving position so that no further compressed air can flow in. This prevents excessive filling of the associated working chamber and brings about an air consumption saving. If a pressure drop occurs due to systemic leakage in the clogged air volume, the output unit drops so far until the control valve means switch back to the open position, so that compressed air is pumped and the output unit is moved back into the retracted stroke end position.
  • As advantageous as the known air-saving measure is, it nevertheless has the disadvantage that a considerable wear can occur due to the frequent opening and closing of the control valve means in connection with the pumping-back of the compressed air. Furthermore, the adjustment movements of the output unit caused by the cyclic Nachpumpen may lead to vibrations that are responsible for the operation of the pneumatic Drive system or the system equipped with it can be disturbing or even damaging.
  • The same problem occurs also in the in the WO 02/14698 A1 described pneumatic drive system. This differs from the above-cited essentially only in that the open position is designed as throttle position in order to reduce the filling intensity of the pneumatic drive in favor of a further reduced air consumption. Upon reaching the stroke end position of the output unit, the control valve means are in turn switched to a closed position.
  • The DE 10 2004 029 990 A1 describes a pneumatic cylinder with cushioning, the piston shuts off an exhaust passage when reaching its end position, so that the fluid can only flow through a throttle channel. In case of DE 101 38 026 C2 For example, a throttle effective with respect to injected fluid is used to build up a backpressure for braking a piston.
  • It is the object of the present invention to provide a pneumatic drive system of the type mentioned, which undergoes a reduced mechanical stress during operation.
  • To solve this problem, the control valve means are designed so that the air-saving is compared to the open position a smaller flow cross-section releasing throttle position.
  • Deviating from the prior art, the air-saving is thus no longer formed as the air flow completely occlusive shut-off, but as a throttle position, the continue to allow - albeit reduced compared to the open position - air flow. Although a saving in compressed air is thus not possible to the same extent as in the prior art discussed above. However, since the flow is reduced compared to the open position, the pressure prevailing in the working chamber increases only slowly, so that an increase in the working chamber pressure can be avoided in particular at short operating cycle times to the operating pressure also denominated as supply pressure. The particular advantage of the embodiment according to the invention lies in the at least largely avoiding oscillating movements of the output unit relative to the drive housing in the Hubendlagen. Due to the constant Luftnachströmung in the working chamber, the output unit can be reliably held in its stroke end position, so that frequent switching of the control valve means with resulting wear does not occur and also ongoing disturbing vibrations of the pneumatic drive can be largely excluded.
  • In particular, it is possible to design the control valve means in such a way that the flow cross-section released in the throttle position has a dimension which, taking into account the air pressure present on the input side of the control valve means, determines a flow which lies in the region of the leakage discharge occurring in the system section arranged downstream of the control valve means. The resulting flow should expediently correspond at least to the leakage discharge. As a result, the output unit is reliably held. Without causing excessive pressure increase in the powered working chamber.
  • Particularly expedient is a pertinent interpretation that the predetermined flow in the area of interpretation permissible leakage flow is. As long as the leakage occurring, for example, between the output unit and the drive housing or in the region of fluid line connection points is within the permissible range, this is constantly compensated and the retracted output unit remains fixed in its stroke end position. Only when the leakage occurring in the system exceeds the permissible value, occur due to the low Luftnachfuhr on the aforementioned position instabilities of the output unit, which is practically synonymous with an advantageous wear indicator, because of the optionally occurring in the region of the stroke end position reciprocating movements of the Output unit can be concluded that one or more of the components of the drive system has exceeded its reliable wear limit and should be replaced.
  • In the dependent claims, further advantageous embodiments of the drive system according to the invention are defined.
  • The inventive measures can be implemented particularly advantageous in a trained as a linear actuator pneumatic drive. Nevertheless, they can be realized, for example, in rotary actuators or rotary actuators.
  • The pneumatic drive designed as a linear drive is preferably a pneumatic cylinder, the output unit of which has a piston rod protruding from the drive housing. In an advantageous embodiment as Krustenbrecherzylinder the piston rod may be provided on the front side with a shock element, which is particularly suitable to pierce the crust of a molten aluminum bath.
  • Depending on the application, control valve means of the type described can be switched on in both control lines or in only one control line. Accordingly, the effect explained in both or only at a stroke end position of the output unit.
  • In any case, it is advantageous for the control valve means to be preceded on the input side by a directional specification valve which is connected or connectable to a compressed air source supplying the operating pressure and by means of whose switching position the stroke direction of the output unit can be predetermined. The directional specification valve is in particular a 5/2-way valve.
  • A particularly compact arrangement results when at least the control valve means and the pneumatic drive are combined to form a structural unit. The optional directional control valve may also be part of this structural unit.
  • The actuating means associated with the control valve means expediently contain response means arranged directly on or in the drive housing which respond to them at or above a certain position of the output unit and cause the switching of the control valve means from the open position into the throttle position. The response means may be designed for purely mechanical or for the electrical actuation of the control valve means. Advantageously, mechanical response means comprise at least one plunger member projecting in the stroke of the output unit and displaceably mounted.
  • In particular, to enable use with different operating pressures, it is advantageous if the control valve means have adjustment means that allow a variable specification of the released in the throttle position flow cross-section. Thus, the flow rate occurring in the throttle position can be adjusted as needed.
  • The invention will be explained in more detail with reference to the accompanying drawings. The only figure ( FIG. 1 ) shows a circuit diagram of a particularly advantageous equipped pneumatic drive system.
  • The designated in its entirety by reference numeral 1 pneumatic drive system includes a preferably designed as a linear actuator pneumatic drive 2 and its operating mode controlling, designated overall by reference numeral 3 control device. If required, these components can be combined to form a compact unit.
  • The pneumatic drive 2 includes a housing having a longitudinal shape, designated as a drive housing 4, and a movable output unit 6 in this respect, with the execution of mutually opposite linear working movements 5a, 5b.
  • Preferably, the pneumatic drive 2 is designed as equipped with a piston rod 7 pneumatic cylinder. The piston rod 7 is part of the output unit 6 and at one end attached to a displaceably arranged in the interior of the drive housing 4 output piston 8.
  • The output piston 8 divides the interior of the drive housing 4 in a rear-side first working chamber 12 and a front, displaced by the piston rod 7 displaceable second working chamber 13. The end face of the drive housing 4 outstanding end portion of the piston rod 7 is the force tap.
  • In principle, the pneumatic drive 2 could also be a rodless linear drive. In place of the piston rod 7 would then occur another Kraftabgriffsglied, for example, a longitudinal slot of the drive housing 4 enforcing driver.
  • The pneumatic drive system 1 is suitable for any application. In a particularly advantageous manner, it can be used in the production and / or processing of aluminum, wherein the pneumatic drive 2 then forms a so-called Krustenbrecherzylinder. The further description should be based on this application, but also applies to other applications.
  • When used as Krustenbrecherzylinder the pneumatic drive 2, deviating from the drawing representation, with vertical alignment of its longitudinal axis at a distance above a molten aluminum bath installed. The drive housing 4 is fixedly fixed to a frame and the piston rod 7 protrudes downwards. At maximum in the drive housing 4 retracted output unit 6 - hereinafter referred to as "retracted stroke end position", the in FIG. 1 dash-dotted lines is indicated - the output unit 6 is moved out completely from the top of the melt. A front end arranged on the outer end of the piston rod 7 shock element 14 is spaced from the surface of the metal melt bath not shown in detail. By controlled pressurization, the output unit 6 can be driven to the aüsfahrenden work movement 5a, wherein it dives after covering a certain distance in the molten metal, while piercing the possibly formed on the surface of the melt material crust by means of the impact element 14. The material crust is characterized broken up. The output unit 6 then moves up to her retracted Hubendlage opposite, not shown extended Hubendlage. Both stroke end positions are expediently predetermined by the output unit 6 striking in a manner not shown on a housing-fixed stop surface, which may be provided in particular on the associated end-side end wall 2a, 2b of the drive housing 4.
  • By reversing the application of compressed air, the extended output unit 6 can be driven to its retracting working movement 5b, where it is pulled back completely out of the molten metal until it is finally back in the retracted Hubendlage.
  • The pressurization which causes the desired working movement 5a, 5b is determined by a directional specification valve 11 of the control device 3. This is on the one hand to a standing under the desired operating pressure compressed air available compressed air source 15 and connected to the atmosphere 16. On the other hand, it is connected to the first working chamber 12 via a first fluidic control line 17 and to the second working chamber 13 via a second fluidic control line 18. It can be selectively positioned in one of two switching positions, wherein in each case a working chamber 12 or 13 compressed air is supplied, while at the same time the respective other working chamber 13 or 12 is vented. The easiest way to realize this functionality is through a 5/2-way valve as shown.
  • The actuation of the directional specification valve 11 is preferably carried out electrically or electromagnetically. It may be a directly actuated or a pilot operated valve. To realize the desired functionality it can Also composed of several functionally linked individual valves, for example, from two 3/2-way valves.
  • In the course of the first control line 17 first control valve means 22 are turned on. In a comparable manner, in the course of the second control line 18, second control valve means 23 can be used. Both control valve means 22, 23 can optionally assume the open position 24 shown in the drawing or a throttle position 25 which functions, inter alia, as an air-saving function. Conveniently, the control valve means 22, 23 are each designed as a two-position valve and contain only a symbolically indicated control valve member 26 which defined by its currently occupied position either the open position 24 or the throttle position 25.
  • By control means 27, in particular formed by spring means, the control valve means 22, 23 are constantly acted upon in the direction of the open position. The basic position of the control valve means 22, 23 is thus the open position 24.
  • In the open position 24 of the compressed air is provided a maximum flow area available. This is preferably chosen so that the compressed air when flowing through the control valve means 22, 23 experiences no or at least no appreciable throttling. In this case, the released flow cross-section may in particular correspond to the nominal cross-section of the respectively assigned control line 17, 18.
  • Also in the throttle position 25 of the compressed air is a free flow cross section for the passage into the connected working chamber 12 or 13 are available. The released in the throttle position 25 flow cross-section is, however, less than that of the open position, so that the flowing therethrough Compressed air is throttled. As long as compressed air flows through the control valve means located in the throttle position 22 or 23 into the respectively connected working chamber 12 or 13, there is a lower air pressure at the valve outlet of the control valve means 22, 23 than at the direction input valve 11 associated with the valve inlet. The input pressure normally corresponds to the operating pressure provided by the compressed air source 15, unless a throttling point serving to reduce the pressure is switched on between the compressed air source 15 and the control valve means 22, 23 (not shown).
  • The flow cross-section released in the throttle position 25 preferably has a size such that in the throttle position 25, taking into account the air pressure present on the input side of the control valve means 22, 23, a flow rate is established which is located in the region of the airflow occurring due to leakage, which is located in the control valve means 22, 23 downstream system section permissibly occurs due to tolerance.
  • A certain leakage flow is unavoidable due to not completely excludable system leaks. Small amounts of compressed air can occur in particular at line connection points or in the dynamically sealed areas between the output unit 6 and the drive housing 4. If the throttle position is present, compressed air is always fed into the connected working chamber 12 or 13 to the extent that it escapes at the same time as a result of leakage. Even if this flow rate is not exactly adjustable, it should at least be within the range of permissible leakage throughput, and as a precaution, you can choose a preset compared to the permissible one Leakage throughput has a slightly larger inflow rate.
  • In order to allow an exact, application-specific adjustment, the control valve means 22, 23 may have symbolically indicated by an arrow adjustment means 28 which allow a variable and in particular stepless specification of the released in the throttle position 25 flow cross-section.
  • The two control valve means 22, 23 are each associated with actuating means 32 which enable a position-dependent activation and preferably also deactivation of the control valve means 22, 23 from the axial position of the output unit 6.
  • In the particularly robust design of the embodiment, the actuating means 32 for a mechanical actuation of the control valve means 22, 23 are formed. They contain response means 33, which are embodied here in the form of a displaceably mounted in the longitudinal direction of the output unit 6 ram member and the starting from one of the two end walls 2a, 2b axially into the interior of the drive housing 4 and thereby protrude the output piston 8:
  • The response means 33 are coupled for movement with the control valve member 26 and therefore take in the basic position of the control valve means 22, 23 a due to the action of the actuating means 32 belonging to Beaufschlagungsmittel 27 as far as possible axially into the interior of the drive housing 4 projecting response position.
  • The output unit 6 approaching a Hubendlange meets with its output piston 8 before reaching the Hubendlage on the located in their Ansprechstellung response 33. These include 33 such as the associated actuating means 32 to those control valve means 22 or 23, for the compressed air supply to the each other working chamber 12, 13 are responsible. In other words, the output unit 6 cooperates in the region of the retracted stroke end position with those actuating means 32 which are associated with the second control valve means 23 responsible for the compressed air supply into the second working chamber 13. In the extended stroke end position, the output unit 6 cooperates with the first control valve means 22 responsible for supplying the first working chamber 12.
  • The arrangement is such that the output unit 6 first acts on the response means 33 when it has approached a distance "S" of the associated stroke end position. When covering this remaining distance "S", which practically defines the response range of the response means 33, the response means 33 are pushed back by the output unit 6, which with simultaneous compression of the resilient urging means 27, a switching of the associated control valve means 22 or 23 from the previously occupied open position in the throttle position causes.
  • If the direction of movement of the output unit 6 subsequently reverses again, the control valve means 22 or 23 previously switched into the throttle position are switched back into the open position by the actuating means 27 belonging to the actuating means 32. The response means 33 practically follow the rejecting output unit 6, until they are back to the initial response position.
  • A typical duty cycle of the exemplary pneumatic drive system 1 is as follows.
  • The starting point is the retracted stroke end position of the output unit 6 indicated by the dot-dash line. Here, the second control valve means 23 are in the throttle position due to the activated actuating means 32, while the first control valve means 22 assume the open position.
  • In order to now cause the extending working movement 5a, 11 compressed air is fed into the first control line 17 by the directional setting valve engaging the illustrated switching position, while at the same time the second control line 18 is vented. Initially, the extension speed of the output unit 6 is still somewhat reduced, because the compressed air can only flow throttled out of the second working chamber 13. However, as soon as the output unit 6 has left the response range of the response means 33 assigned to the second control valve means 23, the complete outflow cross-section defined by the open position 24 of the second control valve means 23 is available. The output unit 6 now moves at high speed in the direction of its extended stroke end position, being able to pierce a possibly located in the travel path metal crust of a molten metal bath.
  • Starting shortly before reaching the extended stroke end position, the output unit 6 cooperates with the actuating means 32 of the first control valve means 22 and switches them into the throttle position 25, so that the per unit of time further inflowing amount of compressed air is reduced.
  • Subsequently, the directional specification valve 11 is switched to the second switching position by, for example, time-controlled or position-dependent controlled actuation. It then takes place the same sequence of movements as just described, but now the output unit 6 executes the retracting output movement 5b and leaves the molten metal again. As soon as the output unit 6 encounters the response means 33 of the second control valve means 23, the switchover of the latter into the throttle position 25 begins, so that the air flow flowing in from then into the second working chamber 13 is reduced.
  • Due to the above-described dimensions of the released in the throttle position 25 flow cross-section is here in the second working chamber 13 continuously replenished compressed air at least to an extent that the leakage occurring is compensated. As a result, the output unit 6 normally remains immobile in the retracted stroke end position. The entire system is therefore at rest and there are no mechanical stress.
  • A new duty cycle begins with the renewed switching of the directional specification valve 11.
  • Occurs with increasing operating time of the pneumatic drive system 1 increased wear, which leads to an increase in the leakage flow, the fed in the throttle position 25 compressed air is no longer sufficient to fix the output unit 6 in the retracted Hubendlage. Especially with vertical installation, the output unit 6 therefore has a tendency to move away from the retracted stroke end position. However, once it has left the response range of the response means 33 - in the embodiment, this is the case when the output unit 6 to the Distance "S" has moved out of the retracted Hubendlage - compressed air is fed into the second working chamber 13 by temporarily switching the second control valve means 23 in the open position 24 until the output unit 6 returns to the retracted end position and then the second control valve means 23 again take the throttle position 25.
  • This recognizable from the outside oscillation movement with a slight stroke of the output unit 6 acts as a wear indicator. It is an expression of a system leak above the permissible value and thus a sign of wear on one or more system components. This provides the opportunity to replace worn components early in order to constantly ensure reliable operation of the drive system 1.
  • The described wear indicator also works, of course, with respect to the first control valve means 22, when the output unit 6 is exposed in the extended stroke end position of a counter-force acting in the retraction direction, for example when the pneumatic drive 2 is used with a different orientation than described above.
  • Instead of mechanical response means 33, non-contact response means can also be used, in particular so-called reed switches or other position sensors. In this case, the switching of the control valve means 22, 23 would take place by means of electrical signals.
  • In the exemplary embodiment, the control valve means 22, 23 are combined with the pneumatic drive 2 to form a compact structural unit. If necessary, even the directional specification valve 11 incorporated into this unit, together with the existing control lines 17, 18th
  • Deviating from the exemplary embodiment, control valve means can also be switched on in the course of only one of the two control lines 17, 18. In particular, when used as Krustenbrecherzylinder it would be sufficient in principle, only the second control line 18 communicating with the second working chamber to associate the control valve means 23 according to the invention. The first control line 17 could in this case be a simple line without valve means turned on.
  • Instead of only a single pneumatic drive 2, a plurality of pneumatic actuators may also be contained in the pneumatic drive system 1. Each pneumatic drive 2 are preferably assigned their own control valve means 22, 23. The directional specification valve 11 can then be used as needed for the simultaneous control of several pneumatic drives 2.

Claims (13)

  1. Pneumatic drive system with at least one pneumatic drive (2) which has a drive housing (4) and an output unit (6) movable relative to the former by means of compressed air pressurisation, wherein the output unit (6) contains an output piston (8) dividing two operating chambers (12, 13) in the drive housing (4) from one another and with one or both operating chambers connected to a pneumatic control line (17, 18), in the course of which are inserted control valve means (22, 23) switchable between an air economy position and an open position (24) allowing in this respect a larger flow cross-section, and which are assigned actuating means (32) which may be activated depending on the position of the output unit (6) and are able to generate a switch of the control valve means (22, 23) into the air economy position when the output unit (6), due to the compressed air flowing through these control valve means (22, 23) into the pneumatic drive (2), has reached an end-of-stroke position or a position lying shortly before it, characterised in that the air economy position is a restrictor position (25) allowing a smaller flow cross-section than the open position (24).
  2. Drive system according to claim 1, characterised in that the pneumatic drive or drives (2) is or are a linear drive(s).
  3. Drive system according to claim 1 or 2, characterised in that pneumatic drive or drives (2) is or are a pneumatic cylinder(s), with an output unit (6) containing a piston rod (7) extending out of the end face of the drive housing (4).
  4. Drive system according to claim 3, characterised in that the pneumatic cylinder is a crust-breaking cylinder, carrying on the end face of its piston rod (7) a ram element (14) suitable for piercing the crust of a metal melting bath.
  5. Drive system according to any of claims 1 to 4, characterised in that upstream of the control valve means (22, 23) on the inlet side is a direction setting valve (11) connectable or connected to a compressed air source (15) and able to feed the two control lines (17, 18) with compressed air under operating pressure, or to vent them, alternately in opposite directions.
  6. Drive system according to claim 5, characterised in that the direction setting valve (11) is in the form of a 5/2-way valve.
  7. Drive system according to any of claims 1 to 6, characterised in that at least the control valve means (22, 23) and the pneumatic drive (2) may be combined to form a unit.
  8. Drive system according to any of claims 1 to 7, characterised in that the actuating means (32) contain response means (33) which operate from or at a specific position of the output unit (6), thereby generating the switching of the assigned control valve means (22, 23) into the restrictor position (25).
  9. Drive system according to claim 8, characterised by actuating means (32) designed for the mechanical switching of the control valve means (22, 23), with response means (33) extending into the path of the stroke of the output unit (6) and able to be moved by the latter.
  10. Drive system according to claim 9, characterised in that the mechanical response means (33) contain at least one slidably mounted punch member.
  11. Drive system according to any of claims 8 to 10, characterised in that the actuating means (32) are so designed that they reset the assigned control valve means (22, 23) to the open position (24) when the output unit (6) once again leaves the response range of the response means (33).
  12. Drive system according to any of claims 1 to 11, characterised in that the flow cross-section provided in the restrictor position (25) is of a size which, allowing for the air pressure at the control valve means (22, 23) on the inlet side, presets a flow lying in the range of the acceptable leakage occurring in the system section downstream of the control valve means (22, 23), and expediently corresponding at least to the level of this acceptable leakage outflow.
  13. Drive system according to any of claims 1 to 12, characterised in that the control valve means (22, 23) have setting means (28) for variable presetting of the flow cross-section provided in the restrictor position (25).
EP20070702849 2006-02-21 2007-01-18 Pneumatic drive system Active EP1987257B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE200620002727 DE202006002727U1 (en) 2006-02-21 2006-02-21 Pneumatic drive system
PCT/EP2007/000398 WO2007096031A1 (en) 2006-02-21 2007-01-18 Pneumatic drive system

Publications (2)

Publication Number Publication Date
EP1987257A1 EP1987257A1 (en) 2008-11-05
EP1987257B1 true EP1987257B1 (en) 2009-07-22

Family

ID=36314415

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070702849 Active EP1987257B1 (en) 2006-02-21 2007-01-18 Pneumatic drive system

Country Status (7)

Country Link
US (1) US20090078110A1 (en)
EP (1) EP1987257B1 (en)
AT (1) AT437309T (en)
AU (1) AU2007218273A1 (en)
CA (1) CA2611208C (en)
DE (2) DE202006002727U1 (en)
WO (1) WO2007096031A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2562128C1 (en) * 2014-10-22 2015-09-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Тульский государственный университет" (ТулГУ) Gas drive with efficient selector valve

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2007346492B2 (en) * 2007-02-07 2011-08-25 Festo Ag And Co. Kg Crust breaker for breaking through a crust formed on a metal molten pool
MX2009010974A (en) 2007-04-10 2009-11-02 Wabtec Holding Corp Cushioning system for pneumatic cylinder of differential engine.
DE102009052286A1 (en) 2009-11-21 2011-05-26 Robert Bosch Gmbh Crust breaking device
RU2457368C1 (en) * 2010-12-16 2012-07-27 Государственное образовательное учреждение высшего профессионального образования "Тульский государственный университет" (ТулГУ) Gas drive with efficient selector valve
DE102011050941A1 (en) * 2011-06-09 2012-12-13 Bar-Pneumatische Steuerungssysteme Gmbh Method for operating a pneumatic drive
US8932515B2 (en) 2011-06-13 2015-01-13 La-Z-Boy Incorporated Crust breaker aluminum bath detection system
US8910562B2 (en) * 2011-06-13 2014-12-16 Mac Valves, Inc. Pneumatic system for controlling aluminum bath crust breaker
US8753564B2 (en) * 2011-06-13 2014-06-17 Mac Valves, Inc. Piston rod and cylinder seal device for aluminum bath crust breaker
US8906291B2 (en) 2011-06-13 2014-12-09 Mac Valves, Inc. Piston rod and cylinder seal device for aluminum bath crust breaker
DE102012101459A1 (en) 2012-02-23 2013-08-29 Zwick Gmbh & Co. Kg Fluidic control, in particular pneumatic control for testing machines
CA2888028A1 (en) * 2014-04-16 2015-10-16 Bp Corporation North America, Inc. Reciprocating pumps for downhole deliquification systems and pistons for reciprocating pumps
DE102016008818A1 (en) * 2016-07-19 2018-01-25 Liebherr-Aerospace Lindenberg Gmbh Hydraulic flight control actuator with double seal device and defined leakage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3530766A (en) * 1969-01-09 1970-09-29 Ware Machine Works Inc Control mechanism for automatically restricting the flow of fluid in a conduit leading to hydraulically actuated means
US4189983A (en) * 1977-01-04 1980-02-26 Zahnradfabrik Friedrichshafen Ag Servomotor pressure control responsive to piston travel
JPS58134203A (en) * 1982-02-05 1983-08-10 Hitachi Constr Mach Co Ltd Cushion device of cylinder
DE3506180C2 (en) * 1985-02-22 1992-10-01 Festo Kg, 7300 Esslingen, De
CA2192563C (en) * 1994-07-15 2003-03-25 Peter Jones Actuator
DE10138026C2 (en) * 2001-08-08 2003-09-25 Helmut Baumgartner Pneumatic drive control for controlling the movement of pneumatic drives

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2562128C1 (en) * 2014-10-22 2015-09-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Тульский государственный университет" (ТулГУ) Gas drive with efficient selector valve

Also Published As

Publication number Publication date
AT437309T (en) 2009-08-15
DE502007001127D1 (en) 2009-09-03
CA2611208A1 (en) 2007-08-30
US20090078110A1 (en) 2009-03-26
EP1987257A1 (en) 2008-11-05
WO2007096031A1 (en) 2007-08-30
AU2007218273A1 (en) 2007-08-30
CA2611208C (en) 2014-02-25
DE202006002727U1 (en) 2006-04-20

Similar Documents

Publication Publication Date Title
US9669533B2 (en) Multi-operational valve
US7739941B2 (en) Hydraulic drive system and method of operating a hydraulic drive system
AT413234B (en) Piston compressor and method for the stage-free delivery rate control thereof
JP3811501B2 (en) Hydraulically operated valve device
US6799501B2 (en) High speed driving method and apparatus of pressure cylinder
US6701823B2 (en) Method and device for controlling a lift cylinder, especially of working machines
EP0318671B1 (en) Pneumatic shock absorber
DE10013194B4 (en) driving device
KR100518767B1 (en) flow control device of construction heavy equipment actuator
US6722257B2 (en) Workpiece high-speed pressurizing method and mechanism by using cylinder with cushioning mechanism
EP2171334B1 (en) Method for controlling or regulating a vacuum valve
US7387061B2 (en) Control apparatus for hydraulic cylinder
DE3410309C2 (en)
JP2013024345A (en) Energy saving valve
KR100946689B1 (en) Positioning control mechanism for double-acting air cylinder
US7011192B2 (en) Air cylinder with high frequency shock absorber and accelerator
US20090025947A1 (en) Method, arrangement and valve for controlling rock drilling
EP2171335B1 (en) Method for controlling or regulating a vacuum valve
RU2008112210A (en) System and method of control of independent dosing valve
US20070186763A1 (en) Inlet monitor and latch for a crust breaking system
GB2403029A (en) Circuit for controlling hydraulic pump discharge
EP1860328A1 (en) Control device for a double-acting pneumatic actuator
US20100126339A1 (en) Actuator control device
JP2012513568A (en) Valve assembly
EP0760908B1 (en) Control arrangement for at least two hydraulic consumers

Legal Events

Date Code Title Description
17P Request for examination filed

Effective date: 20070927

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (to any country) (deleted)
REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

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

REF Corresponds to:

Ref document number: 502007001127

Country of ref document: DE

Date of ref document: 20090903

Kind code of ref document: P

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced from national office to epo]

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: 20091122

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: 20090722

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: 20090722

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: 20090722

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: 20091102

PG25 Lapsed in a contracting state [announced 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: 20090722

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: 20090722

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: 20090722

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: 20090722

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

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: 20091022

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: 20091122

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

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: 20090722

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: 20090722

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: 20090722

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: 20090722

Ref country code: IE

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

Effective date: 20090722

PG25 Lapsed in a contracting state [announced 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: 20090722

26N No opposition filed

Effective date: 20100423

BERE Be: lapsed

Owner name: FESTO A.G. & CO. KG

Effective date: 20100131

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

Ref country code: MC

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

Effective date: 20100131

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

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: 20091023

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

Ref country code: BE

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

Effective date: 20100131

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20110501

PGRI Patent reinstated in contracting state [announced from national office to epo]

Ref country code: IT

Effective date: 20110501

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: LI

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

Effective date: 20110131

Ref country code: CH

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

Effective date: 20110131

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

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: 20090722

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

Ref country code: LU

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

Effective date: 20100118

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

Effective date: 20100123

PG25 Lapsed in a contracting state [announced 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: 20090722

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 437309

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120118

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

Ref country code: AT

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

Effective date: 20120118

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

Ref country code: GB

Payment date: 20141218

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

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

Effective date: 20160118

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

Ref country code: GB

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

Effective date: 20160118

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

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

Ref country code: FR

Payment date: 20170124

Year of fee payment: 11

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

Ref country code: IT

Payment date: 20170125

Year of fee payment: 11

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

Ref country code: FR

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

Effective date: 20180131

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180928

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

Ref country code: IT

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

Effective date: 20180118

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

Ref country code: DE

Payment date: 20190125

Year of fee payment: 13

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

Ref country code: DE

Payment date: 20190125

Year of fee payment: 13