EP1987257A1 - Systeme d'entrainement pneumatique - Google Patents

Systeme d'entrainement pneumatique

Info

Publication number
EP1987257A1
EP1987257A1 EP07702849A EP07702849A EP1987257A1 EP 1987257 A1 EP1987257 A1 EP 1987257A1 EP 07702849 A EP07702849 A EP 07702849A EP 07702849 A EP07702849 A EP 07702849A EP 1987257 A1 EP1987257 A1 EP 1987257A1
Authority
EP
European Patent Office
Prior art keywords
control valve
drive
valve means
output unit
drive system
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
EP07702849A
Other languages
German (de)
English (en)
Other versions
EP1987257B1 (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
Original Assignee
Festo SE 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
Application filed by Festo SE and Co KG filed Critical Festo SE and Co KG
Publication of EP1987257A1 publication Critical patent/EP1987257A1/fr
Application granted granted Critical
Publication of EP1987257B1 publication Critical patent/EP1987257B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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 unit which can be moved by the application of compressed air, wherein the output unit includes a driven piston dividing two working chambers from one another in the drive housing, one or both of which is connected to a pneumatic control line in the course of which switchable control valve means are interposed between an air-purging position and a larger flow cross-sectional opening, to which activatable actuating means are assigned in dependence on the position of the output unit, which can cause the control valve means to change over to air-purging, if the output unit due to the compressed air flowing through this control valve means into the pneumatic drive compressed air reached a stroke end position or a short position before ha t.
  • a known from EP 0771396 Bl pneumatic drive system of this type contains a designed as Krustenbrecherzylinder pneumatic drive, which in the usual
  • Position of use is vertically aligned and includes a controlled by pressurized air supply optionally lowerable or liftable output unit whose task is, according to a predetermined cycle in a molten aluminum bath dive to break a possibly formed on the surface material crust.
  • the direction of movement of the drive unit is specified by a directional specification valve.
  • a plunger valve control valve means 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.
  • the control valve means are in the open position, so that a high actuating force can be provided.
  • the output unit Shortly before reaching the maximum retracted stroke end position, however, the output unit switches the control valve means to 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.
  • DE 10 2004 029 990 A1 describes a pneumatic cylinder with end position damping, wherein the piston shuts off an outlet channel when its end position is reached, so that the fluid can only flow away via a throttle channel.
  • an effective throttle with respect to the injected fluid is used to build up a backpressure serving for braking a piston.
  • control valve means are designed such that the air-saving position is a throttle position which releases a smaller flow cross-section compared to the open 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 at the beginning.
  • the pressure prevailing in the working chamber increases only slowly, so that an increase of the working chamber pressure to the operating pressure, which can also be indicated as supply pressure, can be avoided, especially with short operating cycle times.
  • 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 Gutnachströmung 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, predetermines a flow occurring in the region of the leakage discharge occurring in the system section downstream of the control valve means lies.
  • the resulting flow should expediently correspond at least to the leakage discharge.
  • 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.
  • the measures according to the invention can be implemented particularly advantageously in a pneumatic drive designed as a linear 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 for piercing the crust of a Aluminiumschmelzba- to.
  • 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 results in both or only at a hub 5 endlage 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 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 if at least the control valve means and the pneumatic drive are combined to form a building unit.
  • the optional directional control valve may also be part of this structural unit.
  • the actuating means associated with the control valve means expediently comprise directly on or in the drive housing arranged response means which respond to or at a certain position of the output unit to this and cause the switching of the control valve means from the open position to the throttle position.
  • the response means can be designed for purely mechanical or else 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.
  • Figure 1 shows a circuit diagram of a particularly advantageous equipped pneumatic drive system.
  • the pneumatic drive system designated in its entirety by reference numeral 1 contains a pneumatic drive 2, preferably designed as a linear drive, and a control device which controls its operation and is designated as a whole by reference number 3. 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 preferably designed as a pneumatic cylinder equipped with a piston rod 7.
  • Piston rod 7 is part of the output unit 6 and one nenends attached to a displaceably arranged in the interior of the drive housing 4 output piston 8.
  • the output piston 8 subdivides the interior of the drive housing 4 into a rear-side first working chamber 12 and a front second working chamber 13 displaceably penetrated by the piston rod 7.
  • the end section of the piston rod 7 projecting from the end face of the drive housing 4 is used for power tapping.
  • 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 5 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, the pneumatic drive 2 then forms a so-called lo Krustenbrecherzylinder. The further description should be based on this application, but also applies to other applications.
  • the output unit 6 has moved completely upwards out of the melt, and an impact element 14 arranged at the outer end of the piston rod 7 is at a distance from the surface of the metal melt bath (not shown)
  • the output unit 6 can be driven to the extending working movement 5a, wherein it dives after covering a certain distance in the molten metal, namely by piercing the possibly formed on the surface of the melt 0 material crust by means of
  • Push element 14 The material crust is thereby broken.
  • 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, whereby it is pulled out again completely upwards out of the molten metal until finally it is again in the retracted stroke end position.
  • 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 can be a directly actuated valve 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 in the course of the second control line 18.
  • Both control valve means 22, 23 can optionally assume the open position 24 o shown in the drawing or a throttle position 25 functioning 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.
  • 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 flow cross-section released in throttle position 25, however, is less than that of the open position, so that the passage through flowing compressed air is throttled.
  • compressed air flows through the throttle valve located in the control valve means 22 o- 23 into the respectively connected working chamber 12 or 13 prevails at the valve output of the control valve 5 tilstoff 22, 23, a lower air pressure than at the directional control valve 11 associated valve inlet.
  • the inlet 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 valves 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 input side, the control valve means 22, 23 are present
  • Air pressure a flow rate which is located in the area of the air outlet occurring due to leakage, which in the system section downstream of the control valve means 22, 23 is permissibly tolerated due to tolerances.
  • 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 regions 5 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 value can not be set exactly, it should at least be within the range of the permissible leakage throughput, whereby for safety's sake one can choose a preset which, in comparison to the casual leakage rate 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 which, 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 Beauftschungsffen 27 as far as possible axially into the interior of the drive housing 4 projecting response position.
  • the output unit 6 approximating a stroke length strikes with its output piston 8 before reaching the stroke end position on the response means 33 located in its response position.
  • the response means 33 and 5 also include the associated actuating means 32
  • Control valve means 22 or 23, which are responsible for the compressed air supply to the respective other-side working chamber 12, 13.
  • the output unit 6 cooperates in the region of the retracted stroke end position with those lo actuating means 32 which are associated with the second control valve means 23 responsible for the supply of compressed air into the second working chamber 13.
  • the output unit 6 cooperates with the first control valve means 22 responsible for feeding 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
  • control valve means 22 or 23 previously switched into the throttle position are switched back to the open position by the apply means 27 belonging to the actuation 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 dot-dash lines.
  • 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 now moves at high speed in the direction of its extended stroke end position, being capable of a metal crust possibly located in the travel path
  • the output unit 6 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 compressed air quantity flowing further per unit time 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. The same course of motion then takes place 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 changeover of the latter into the throttle position 25 begins, so that the air flow flowing into the second working chamber 13 from then on is reduced.
  • a new duty cycle begins with the renewed switching of the directional specification valve 11.
  • This oscillation movement which can be recognized from the outside, 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 creates the possibility of early replacement of worn components in order to constantly ensure reliable operation of the drive system 1.
  • the described wear indicator also works with respect to the first control valve means 22 when the output unit 6 is subjected to an opposing force acting in the retracted direction in the extended stroke end position, for example when the pneumatic drive 2 is used with a different orientation than that 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 over 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, the directional beventil 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 23 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.

Landscapes

  • 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)

Abstract

L'invention concerne un système d'entraînement pneumatique qui présente au moins un entraînement pneumatique (2) muni d'un boîtier d'entraînement (4) et d'une unité entraînée (6) qui peut être déplacée par rapport au boîtier lorsqu'elle est sollicitée par de l'air comprimé. L'unité entraînée (6) contient un piston entraîné (8) qui sépare l'une de l'autre deux chambres de travail (12, 13) dans le boîtier d'entraînement (4), l'une des chambres ou les deux étant raccordées à un conduit (17, 18) de commande pneumatique dans le parcours duquel des moyens inversibles (22, 23) à soupape de commande sont déplacés entre une position d'économie d'air et une position d'ouverture (24) qui libère une section transversale d'écoulement plus grande que dans la première position. Des moyens d'actionnement (32) qui peuvent être activés en fonction de la position de l'unité entraînée (6) et qui peuvent amener les moyens (22, 23) à soupape de commande dans la position d'économie d'air lorsque l'unité entraînée (6) a atteint une position de fin de course ou une position située un peu en avant de celle-ci suite à la pénétration de l'air comprimé dans l'entraînement pneumatique (2) à travers ces moyens (22, 23) à soupape de commande sont associés à ces derniers. La position d'économie d'air présente la particularité d'être une position d'étranglement (25) qui libère une plus petite section transversale d'écoulement que la position d'ouverture (24).
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)

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

Family

ID=36314415

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07702849A Not-in-force EP1987257B1 (fr) 2006-02-21 2007-01-18 Systeme d'entrainement pneumatique

Country Status (7)

Country Link
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)

Families Citing this family (14)

* 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
WO2008124816A1 (fr) 2007-04-10 2008-10-16 Wabtec Holding Corp. Système d'amortissement pour cylindre pneumatique de moteur différentiel
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US20090078110A1 (en) 2009-03-26
EP1987257B1 (fr) 2009-07-22
ATE437309T1 (de) 2009-08-15
CA2611208A1 (fr) 2007-08-30
AU2007218273A1 (en) 2007-08-30
WO2007096031A1 (fr) 2007-08-30
DE202006002727U1 (de) 2006-04-20
DE502007001127D1 (de) 2009-09-03
CA2611208C (fr) 2014-02-25

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