EP1987257B1 - Systeme d'entrainement pneumatique - Google Patents

Systeme d'entrainement pneumatique Download PDF

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Publication number
EP1987257B1
EP1987257B1 EP07702849A EP07702849A EP1987257B1 EP 1987257 B1 EP1987257 B1 EP 1987257B1 EP 07702849 A EP07702849 A EP 07702849A EP 07702849 A EP07702849 A EP 07702849A EP 1987257 B1 EP1987257 B1 EP 1987257B1
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EP
European Patent Office
Prior art keywords
control valve
valve means
output unit
drive system
pneumatic
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.)
Not-in-force
Application number
EP07702849A
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German (de)
English (en)
Other versions
EP1987257A1 (fr
Inventor
Dieter Waldmann
Jan-Peter Bender
José ARANA
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 SE and Co KG
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Festo SE and Co KG
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Publication date
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Publication of EP1987257A1 publication Critical patent/EP1987257A1/fr
Application granted granted Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/064—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam with devices for saving the compressible medium
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/202—Externally-operated valves mounted in or on the actuator
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/225—Other 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
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/421—Flow control characterised by the type of actuation mechanically
    • F15B2211/424—Flow control characterised by the type of actuation mechanically actuated by an output member of the circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • 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 Druck Kunststoffbeetzschung 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 Lucasspar too 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.
  • 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.
  • 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.
  • 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.
  • a throttle effective with respect to injected fluid is used to build up a backpressure for braking a piston.
  • control valve means are designed so that the air-saving is compared to the open position a smaller flow cross-section releasing throttle position.
  • 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.
  • a saving in compressed air is thus not possible to the same extent as in the prior art discussed above.
  • 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 Beernachströmung 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.
  • 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.
  • 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.
  • 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 Gutnachbuch 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.
  • 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.
  • 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.
  • 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.
  • control valve means 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.
  • mechanical response means comprise at least one plunger member projecting in the stroke of the output unit and displaceably mounted.
  • control valve means have adjustment means that allow a variable specification of the released in the throttle position flow cross-section.
  • the flow rate occurring in the throttle position can be adjusted as needed.
  • FIG. 1 shows a circuit diagram of a particularly advantageous equipped pneumatic drive system.
  • 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.
  • 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.
  • the pneumatic drive 2 could also be a rodless linear drive.
  • 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.
  • 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.
  • 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.
  • first control valve means 22 are turned on.
  • 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.
  • 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.
  • 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.
  • 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.
  • the released flow cross-section may in particular correspond to the nominal cross-section of the respectively assigned control line 17, 18.
  • 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.
  • 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.
  • 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.
  • 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 Beauftschungsstoff 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 Anschbig 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a new duty cycle begins with the renewed switching of the directional specification valve 11.
  • 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.
  • 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.
  • 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
  • control valve means can also be switched on in the course of only one of the two control lines 17, 18.
  • control valve means can also be switched on in the course of only one of the two control lines 17, 18.
  • the first control line 17 could in this case be a simple line without valve means turned on.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Actuator (AREA)

Claims (13)

  1. Système d'entraînement pneumatique avec au moins un entraînement pneumatique (2) qui présente un boîtier d'entraînement (4) et une unité de sortie de mouvement (6) mobile par rapport à celui-ci par sollicitation par air comprimé, dans lequel l'unité de sortie de mouvement (6) contient un piston de sortie (8) qui sépare dans le boîtier d'entraînement (4) deux chambres de travail (12, 13) l'une de l'autre, dont l'une ou les deux sont raccordées à une conduite de pilotage (17, 18) pneumatique, dans le parcours de laquelle sont insérés des moyens formant distributeur de commande (22, 23) pouvant commuter entre une position d'économie d'air et une position ouverte (24) libérant par rapport à celle-ci une section d'écoulement plus grande, auxquels sont associés des moyens d'actionnement (32) activables en fonction de la position de l'unité de sortie de mouvement (6), lesquels peuvent susciter une commutation des moyens formant distributeur de commande (22, 23) dans la position d'économie d'air si l'unité de sortie de mouvement (6) a atteint en raison de l'air comprimé affluant par ces moyens formant distributeur de commande (22, 23), dans l'entraînement pneumatique (2), une position de fin de course ou une position se trouvant juste avant, caractérisé en ce que la position d'économie d'air est une position d'étranglement (25) libérant par rapport à la position ouverte (24) une section d'écoulement plus petite.
  2. Système d'entraînement selon la revendication 1, caractérisé en ce que l'un entraînement pneumatique (2) au nombre d'au moins un est un entraînement linéaire.
  3. Système d'entraînement selon la revendication 1 ou 2, caractérisé en ce que l'un entraînement pneumatique (2) au nombre d'au moins un est un vérin pneumatique, dont l'unité de sortie de mouvement (6) contient une tige de piston (7) dépassant côté frontal hors du boîtier d'entraînement (4).
  4. Système d'entraînement selon la revendication 3, caractérisé en ce que le vérin pneumatique est un cylindre broyeur de croûte, sur la tige de piston (7) duquel un élément de butée (14) approprié au perçage de la croûte d'un bain de métal liquide est disposé côté frontal.
  5. Système d'entraînement selon l'une des revendications 1 à 4, caractérisé en ce qu'une soupape de prescription de sens (11) reliée ou pouvant être reliée à une source d'air comprimé (15) est montée en amont des moyens formant distributeur de commande (22, 23) côté entrée, laquelle est en mesure d'alimenter ou de vidanger les deux conduites de pilotage (17, 18) en alternance et en sens contraires en air comprimé se trouvant sous une pression de service.
  6. Système d'entraînement selon la revendication 5, caractérisé en ce que la soupape de prescription de sens (11) est réalisée comme une soupape à 5/2 voies.
  7. Système d'entraînement selon l'une des revendications 1 à 6, caractérisé en ce qu'au moins les moyens formant distributeur de commande (22, 23) et l'entraînement pneumatique (2) sont réunis en une unité de construction.
  8. Système d'entraînement selon l'une quelconque des revendications 1 à 7, caractérisé en ce que les moyens d'actionnement (32) contiennent, à partir ou dans une certaine position de l'unité de sortie de mouvement (6), des moyens de réponse (33) répondant à celle-ci et suscitant par là-même la commutation des moyens formant distributeur de commande (22, 23) associés dans la position d'étranglement (25).
  9. Système d'entraînement selon la revendication 8, caractérisé par des moyens d'actionnement (32) conformés pour la commutation mécanique des moyens formant distributeur de commande (22, 23), dont les moyens de réponse (33) s'avancent dans la trajectoire de l'unité de sortie de mouvement (6) et peuvent être déplacés par celle-ci.
  10. Système d'entraînement selon la revendication 9, caractérisé en ce que les moyens de réponse (33) mécaniques contiennent au moins un élément à poussoir monté coulissant.
  11. Système d'entraînement selon l'une des revendications 8 à 10, caractérisé en ce que les moyens d'actionnement (32) sont réalisés de sorte qu'ils recommutent les moyens formant distributeur de commande (22, 23) associés dans la position ouverte (24) si l'unité de sortie de mouvement (6) quitte de nouveau la zone de réponse des moyens de réponse (33).
  12. Système d'entraînement selon l'une des revendications 1 à 11, caractérisé en ce que la section d'écoulement libérée dans la position d'étranglement (25) présente une dimension qui prescrit, en tenant compte de la pression d'air régnante côté entrée, sur les moyens formant distributeur de commande (22, 23), un débit qui se trouve dans la zone du débit de fuite survenant de manière autorisée dans la partie de système disposée en aval des moyens formant distributeur de commande (22, 23) et correspond de manière avantageuse au moins à la valeur de ce débit de fuite autorisé.
  13. Système d'entraînement selon l'une des revendications 1 à 12, caractérisé en ce que les moyens formant distributeur de commande (22, 23) disposent de moyens de réglage (28) pour la prescription variable de la section d'écoulement libérée en position d'étranglement (25).
EP07702849A 2006-02-21 2007-01-18 Systeme d'entrainement pneumatique Not-in-force EP1987257B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202006002727U DE202006002727U1 (de) 2006-02-21 2006-02-21 Pneumatisches Antriebssystem
PCT/EP2007/000398 WO2007096031A1 (fr) 2006-02-21 2007-01-18 Systeme d'entrainement pneumatique

Publications (2)

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EP1987257A1 EP1987257A1 (fr) 2008-11-05
EP1987257B1 true EP1987257B1 (fr) 2009-07-22

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US (1) US20090078110A1 (fr)
EP (1) EP1987257B1 (fr)
AT (1) ATE437309T1 (fr)
AU (1) AU2007218273A1 (fr)
CA (1) CA2611208C (fr)
DE (2) DE202006002727U1 (fr)
WO (1) WO2007096031A1 (fr)

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WO2007096031A1 (fr) 2007-08-30
DE202006002727U1 (de) 2006-04-20
ATE437309T1 (de) 2009-08-15
DE502007001127D1 (de) 2009-09-03
CA2611208A1 (fr) 2007-08-30
AU2007218273A1 (en) 2007-08-30
US20090078110A1 (en) 2009-03-26
EP1987257A1 (fr) 2008-11-05
CA2611208C (fr) 2014-02-25

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