EP1987255B1 - Systeme pneumatique d'entrainement - Google Patents

Systeme pneumatique d'entrainement Download PDF

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Publication number
EP1987255B1
EP1987255B1 EP06707116A EP06707116A EP1987255B1 EP 1987255 B1 EP1987255 B1 EP 1987255B1 EP 06707116 A EP06707116 A EP 06707116A EP 06707116 A EP06707116 A EP 06707116A EP 1987255 B1 EP1987255 B1 EP 1987255B1
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EP
European Patent Office
Prior art keywords
control valve
valve means
drive system
output unit
air
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.)
Expired - Lifetime
Application number
EP06707116A
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German (de)
English (en)
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EP1987255A1 (fr
Inventor
Ulrich Hirling
Ute Casimir
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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 EP1987255A1 publication Critical patent/EP1987255A1/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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/40—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

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 in the drive housing from each other, one or both serving for the controlled application of compressed air Control valve means are connected, which are switchable between a plurality of switching positions, among which a throttle cross-section predetermining air-saving, and which have a further switching position a larger compared to the throttle cross-sectional flow area high-power position, wherein the control valve means are assigned actuating means which during the compressed air supply in a working chamber, the switching of the control valve means connected to this working chamber in dependence on the in at least one Arb Control chamber prevailing air pressure such that a switch from the normally assumed air saving takes place in the high force position, if and at least as long as the output unit is exposed to increased resistance to movement.
  • a pneumatic drive designed as a crust-breaking cylinder, the output unit of which is drivable for oscillating working movements in which it is temporarily immersed in a molten aluminum bath while puncturing a possibly constructed material crust.
  • a directional specification valve which controls the supply and discharge of compressed air in two of the output piston of the output unit divided working chambers.
  • double control valve means which are turned on in the connection between the directional control valve and a respective working chamber.
  • this switching position is designed as air-saving, in that the fluid passage has a throttle cross section, which allows only a limited flow.
  • the degree of filling of the connected working chamber remains at the lowest possible level. If the output unit strikes an aluminum crust and is therefore opposed to increased resistance to movement, progressively higher actuating pressure builds up in the connected working chamber over the throttle cross section until the required puncture force has been reached.
  • the control valve means Upon arrival in a stroke end position causes the output unit finally switching the control valve means in a blocking position to prevent further compressed air supply to the pneumatic drive.
  • the DE 31 18 764 A1 describes a pneumatic door operating system, which is equipped with a pneumatic drive system comparable to the aforementioned type. After the system has been vented by operating an emergency valve, a throttling function prevents a sudden venting of the system until the throttle is deliberately switched off again.
  • An essential object of the present invention is to propose measures that allow a reduction in cycle times without excessive consumption of compressed air.
  • control valve means have as a further switching position a smaller compared to the throttle cross-section flow cross-holding position and that the control valve means are assigned depending on the position of the output unit activatable further actuating means which can cause the switching to the holding position , if the Output unit reaches a stroke end position or a position shortly before the stroke end position during their working movement.
  • the output unit moves so long in the air saving mode, as it is not exposed to increased resistance to movement. Due to the effective throttle cross-section here, the degree of filling of the connected working chamber is limited to a minimum, and consequently also the air consumption.
  • the control valve means responsible for the pressure feed into the respective working chamber switch to the high force position due to the pressure change occurring in the pneumatic drive and, with an enlarged flow cross section, enable a faster air inflow and thus a rapid pressure increase in the connected working chamber , This leads to an increase in the force and an overcoming of the output unit opposite motion resistance. After reducing the resistance to movement, the control valve means may eventually switch back to air-saving.
  • control valve means have a third switching position, in which the compressed air is provided in comparison to the throttle cross section smaller flow cross-section available.
  • This switch position is referred to as a holding position, because they is effective to securely hold the output unit in its Hubendlage.
  • the holding position of the control valve means becomes effective as a function of the position of the output unit when the latter approaches or has reached the stroke end position.
  • the described advantages are particularly noteworthy when the pneumatic drive system is used as a crust breaker system in aluminum production or processing. Due to the short operating cycle times, the air saving proves to be immense. At the same time, if necessary, an increased actuating force is available with only a short time delay in order, for example, to break through an aluminum crust or strip off solidified aluminum material adhering to the output unit. Due to the pressure-controlled actuation also has the advantage that the pressure build-up in the working chamber responsible for the current working movement takes place variably, taking into account the height of the movement resistance to be overcome. It can thus be achieved that only as much compressed air is fed into the pneumatic drive in the high-power phase, as is required to overcome the movement resistance that is just occurring.
  • the at least one linear drive is preferably a pneumatic cylinder with a piston rod which can be used as Krustenbrecherzylinder.
  • the use is not limited to the field of crust crusher applications.
  • the actuating means for the control valve means are in particular designed so that they control the switching operation in dependence on that air pressure prevailing in the working chamber connected to the control valve means. When a resistance to movement of this air pressure increases and causes the switch from the air-saving position in the high-power position.
  • the switching position of the control valve means is expediently predetermined by the currently occupied position of a control valve member of the control valve means. This is expediently switched in the direction of the air-saving of the input side to the control valve means pending input pressure.
  • the output side of the control valve means ie on the side of the connected working chamber, prevailing output pressure acts on the control valve member opposite in the direction of the high force position.
  • effective spring means are available in this direction. If the force of the spring means and the force resulting from the output pressure are altogether greater than the force resulting from the inlet pressure, the switching to the high force position takes place. If the actuating force of the spring means can be set variably, it is possible to individually set the switching threshold.
  • the spring means expediently ensure that the control valve means occupy the high force position in the pressureless state. Is - especially under the mediation of an upstream directional specification valve - the operating pressure connected, can be caused by an in the pressure acting on the output pressure seizure passage throttling a delayed build-up of the resulting from the output pressure force, so that the control valve means immediately occupy the air-saving.
  • the switching to the holding position can be caused mechanically, for example due to a cooperating with the output unit ram-shaped actuator, but also electrically, using suitable position sensor means.
  • the existing in the holding position reduced flow cross-section prevents excessive filling of the connected working chamber and compensates at the same time any leakage losses, so that the output unit is held constant and performs no oscillatory movements.
  • a design is considered to be optimal in which the flow cross-section released in the holding position has a dimension which, taking into account the pending operating pressure, predetermines a flow which at least substantially corresponds to the leakage occurring in the pneumatic drive. In this way, the degree of air filling in the connected working chamber does not increase or only slightly, although the air connection is not shut off as required by the prior art.
  • FIG. 1 shows the pneumatic drive system as a simplified circuit diagram in a preferred embodiment which is particularly, but not exclusively, suitable for crusher crusher applications.
  • pneumatic drive system comprises at least one pneumatic actuator 2, which is expediently a linear drive. Assigned to it is a control device serving its operational control, designated overall by reference numeral 3.
  • pneumatic drive 2 is in principle arbitrary.
  • it could be a rodless linear drive.
  • it is designed as equipped with a piston rod 4 pneumatic cylinder.
  • the pneumatic drive 2 comprises a drive housing 5 referred to, a certain longitudinal extension exhibiting housing in the interior of which a linearly displaceable driven piston 6 is located, which is summarized with the already mentioned piston rod 4 to a drive unit 7 designated as the movement unit.
  • This output unit 7 is under the execution of either an extending or a retracting working movement 8a, 8b relative to the drive housing 5 linearly movable.
  • the first working chamber 12 is connected to a first fluidic control line 14, the second working chamber 13 to a second fluidic control line 15.
  • These two control lines 14, 15 are also part of the control device 3 as a directional default valve 16, to which the two control lines 14, 15 with their ends opposite the pneumatic drive 2 are connected.
  • the directional default valve 16 may connect either one (14) or the other (15) control line to a compressed air source 17, while simultaneously bleeding the other control line 15, 14 to the atmosphere 18, depending on the switch position taken by it.
  • the compressed air source 17 is provided under a certain operating pressure compressed air available.
  • the directional specification valve is an example of a 5/2-way valve. It is characterized by a spring device 22 in a FIG. 1 biased initial position, in which the second control line 15 is connected to the compressed air source 17 and the first control line 14 is vented. By an electric or electromagnetic actuator 23, the directional specification valve 16 can be switched to the opposite switching position.
  • the directional default valve 11 may be a directly actuated or pilot operated valve. to Realization of the desired functionality, it can also be composed of several functionally linked individual valves, for example, from two 3/2-way valves.
  • the pneumatic drive 2 is designed as Krustenbrecherzylinder.
  • an impact element 24, which is suitable for piercing the crust formed on the surface of an aluminum melt bath or of another molten metal bath, is arranged on the end region of the piston rod 4 located outside the drive housing 5.
  • the pneumatic drive 2 is typically installed with a vertical longitudinal direction and downwardly projecting piston rod 4. With retracted output unit 7 - this state goes out FIG. 1 As shown, the impact element 24 occupies a position at a distance above the material crust. To pierce the crust, the output unit 7 is driven to its extending working movement 8a, wherein it dives with the shock element 24 ahead, piercing the possibly existing crust in the molten aluminum bath.
  • first and second control valve means 25, 26 are connected to the two working chambers 12, 13 independently operating first and second control valve means 25, 26 .
  • the first control valve means 25 are turned on in the course of the first control line 14, the second control valve means 26 in the course of the second control line 15. They allow, in addition to the directional default valve 16, a controlled in a special way Druck Kunststoffbeetzschlagung each connected working chamber 12, 13th
  • the control valve means 25, 26 each have a valve inlet 27 connected to the directional specification valve 16 and a valve outlet 28 connected to the working chamber 12, 13 to be controlled.
  • Both control valve means 25, 26 are switchable between different switching positions. In this case, both control valve means 25, 26 alternatively occupy a high force position 29, an air-saving position 30 and a holding position 31. Shown is an operating state in which the first control valve means 25 are in the high-force position and the second control valve means 26 in the air-saving.
  • control valve means 25, 26 each formed by a control valve which has an optionally positionable in one of three positions control valve member 32, which is illustrated purely symbolically in the drawing.
  • the control valve member 32 may be, for example, a piston valve.
  • throttle cross-section The released in the air-saving 30 flow cross section is referred to as throttle cross-section. It is less than the nominal cross section of the respectively connected control line 14, 15 and causes a throttling of the flowing compressed air. If the output unit 7 can move freely, is thus at the valve outlet 28 against the fed operating pressure lower output pressure, which is present as the instantaneous working pressure in the connected working chamber 12, 13.
  • the released in the high force position 29 flow cross-section is larger than the throttle cross-section. He allows in particular an unthrottled air passage and suitably corresponds to the nominal cross section of the control lines 14, 15th
  • the smallest flow cross section is provided in the holding position 31. This is even much smaller than the effective in the air-saving 30 throttle area, which will be discussed later.
  • Both control valve means 25, 26 are assigned independently operating first and second actuating means 36, 37. These are responsible for whether the associated control valve means 25, 26 occupy the high-force position 29 or 30 Heilpargna. Switching to the holding position 31, however, they can not cause.
  • first and second further actuating means 38, 39 are responsible, which unlike the purely pressure-dependent first and second operating means 36, 37 are activated or deactivated expediently purely as a function of the linear position of the output unit 7, with respect to the first and second actuating means 36, 37 have priority. If the output unit 7 reaches a position relevant for switching to the holding position 31, the switching process takes place irrespective of whether the control valve means 25, 26 had previously occupied the high-force position 29 or the air-saving position 30.
  • the first and second actuation means 36, 37 are capable of controlling the switching of the associated control valve means 25, 26 in response to the air pressure prevailing in at least one working chamber.
  • the control is based in particular on the pressure that is currently in the Compressed air supplied working chamber 12, 13 prevails and which in the present case coincides with the prevailing at the valve output 28 output pressure.
  • the design is expediently such that normally, when the output unit 7 can move undisturbed, the air-saving 30 is present and that from this switching to the high force position 29 is caused when the output unit 7 exposed in their working movement 8a, 8b increased resistance to movement is and thereby in the currently supplied with compressed air working chamber 12, 13 prevailing working pressure increases up to a predetermined switching threshold.
  • a respective control valve member 32 in the embodiment two oppositely oriented first and second shipsbeetzungs vom 42, 43 assigned. Actuation of the first air-admission surface 42 leads to a restoring force in the direction of the air-saving position 30, an admission of the second air-admission surface 43 has an effective in the direction of the high-force position 29 actuating force.
  • the first Lsymmetricbeetzschlagungs character 42 is supplied via a first supply passage 44 of the pending on the valve inlet 27 inlet pressure. Via a second admission channel 45, the second Heilbeaufschlagungs composition 43 is acted upon by the pressure prevailing at the valve outlet 28 output pressure.
  • spring means 46 are present, which exert a force acting also in the direction of the high force position on the control valve member 32.
  • the actuating force of the spring means 46 is suitably adjustable, which is symbolically illustrated by an oblique arrow.
  • a throttle point 47 is suitably turned on, which causes a time-delayed pressure force build-up on the second Heilbeetzungs composition 43.
  • the directional specification valve 16 is switched with the compressed air source 17 in the second switching position, not shown, so that the first control line 14 supplied under operating pressure compressed air and at the same time the second control line 15 is vented.
  • the compressed air flowing in via the first control line 14 flows through the first control valve means 25 located in the high force position and acts on the output unit 7 in the direction of extension, so that it is driven to the extending working movement 8a.
  • the case pushed by the output piston 6 from the second working chamber 13 compressed air passes through the held by the spring means 46 in the likewise a full passage enabling high power position second control valve means 26 and the subsequent directional presetting valve 16 to the atmosphere 18. Since in the control line 15 there is atmospheric pressure, the switching position of the second control valve means 26 is not affected during the venting phase.
  • the first control valve means 25 switch to the air-saving position 30. This is due to the fact that while the operating pressure prevailing in the entire first control line 14 can act on the first air admission surface 42 without restriction, an initially only low activation pressure is present at the second air admission surface 43 because of the intermediate throttle restriction 47.
  • the design is such that the pressure force applied in the direction of air-saving via the first air-impingement surface 42 is greater than the sum of the pressure force impinging on the second air-impingement surface 43 and the actuating force of the spring means 46.
  • the operating behavior changes, however, if the output unit 7 is opposed to an increased resistance to movement during one or the other working movement 8a, 8b. During extension, this may be due to the output unit 7 impinging with its impact element 24 on a material crust to be pierced. During retraction, such a resistance can be caused for example by solidified materials from the melting pot, which are deposited on the extended end portion of the piston rod 4.
  • the working pressure prevailing in the working chamber 12 or 13 which is currently pressurized with compressed air increases.
  • the speed of the pressure increase depends on the cross-sectional size of the released in the air-saving throttle area.
  • the relevant for the changeover switching threshold can be influenced and set by mutual coordination of the surface dimensions of the two Heilbeetzungs vom 42, 43 and the force of the spring means 46.
  • an operating pressure of 6 bar is applied, resulting in the air-saving a working chamber pressure of 2 bar, the switching threshold for switching to the high force position at a working chamber pressure of about 2.5 bar.
  • control valve means 25, 26 can not switch back to the air saving after switching to the high power position during the ongoing work movement due to the dynamics of the system, a significant air consumption advantage remains, because switching to the high power position in the individual working movements always only takes place when an increased resistance to movement occurs. In many cases, this will not be the case, so that then operation is possible with the full use of the air save function.
  • control valve means 25, 26 allow the already mentioned additional switchover to a holding position 31.
  • the further actuating means 38, 39 are designed such that they bring about the momentarily with the supply of compressed air in a working chamber 12 or 13 concerned control valve means 25 or 26 in the only greatly reduced flow rate enabling stop position when the output unit 7 is a stroke end or reached a position just before the stroke end position.
  • This position-dependent switching ensures that in the Hubendlagen when the output unit 7 can not move on, the compressed air can flow with a further reduced flow rate in the connected working chamber 12 or 13, as long as the directional specification valve 16 is not switched.
  • the released in the holding position 31 flow cross-section of the control valve means 25, 26 such that based on the pending operating pressure of the approved flow at least substantially corresponds to the occurring in the pneumatic drive 2 leakage.
  • the permitted flow is at least equal to or slightly greater than the occurring leakage flow, which occurs for example between the output piston 6 and the drive housing 5.
  • the further actuating means 38, 39 are equipped with suitable response means 48, 49.
  • These response means 48, 49 are located conveniently on or in the drive housing 5, wherein they are formed in the embodiment, to cause a purely mechanical switching of the control valve means 25, 26.
  • the response means 48, 49 are direct components of the control valve means 25, 26.
  • the control valve means 25, 26 directly on or in the drive housing 5 to install, as in FIG. 1 indicated by dash-dotted lines.
  • the control valve means 25, 26 in the FIG. 1 shown separately from the drive housing 5 and it is made clear by two assigning the reference numerals 48, 49, which responsive means 48, 49 to which control valve means 25, 26 belong.
  • the switching between the high-force position 29 and the air-saving position 30 can also be caused by electrical signals when the relevant pressure parameters are picked up by pressure switches or pressure sensors.
  • the associated control valve means 25, 26 occupy the holding position 31 irrespective of the working pressures prevailing in the working chambers 12, 13.
  • the switching position is specified here depending on the position of the output unit 7. Only outside this response range, the switching position of the control valve means 25, 26 is controlled pressure-dependent between the air-saving position 30 and the high-force position 29.
  • At least the two control valve means 25, 26 can be designed as a structural unit with the pneumatic drive 2.
  • the directional specification valve 16 may also be a component of this structural unit.
  • the pneumatic drive system 1 may comprise more than the only one pneumatic drive 2, wherein then each pneumatic drive 2 expediently own first and second control valve means 25, 26 are assigned.
  • the directional specification valve 16 in contrast, can in principle serve for the simultaneous control of several parallel-connected pneumatic drives 2.
  • control valve means 25, 26 associated with a pneumatic drive 2 may also be present only in a simple manner. They are then suitably switched on either in the first control line 14 or in the second control line 15, depending on which stroke direction the associated functionality is desired.

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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)

Claims (14)

  1. Système d'entraînement pneumatique, comportant au moins un mécanisme d'entraînement pneumatique (2), qui présente un boîtier d'entraînement (5) et une unité de sortie (7) pouvant être déplacée du fait de son exposition à de l'air comprimé, sachant que l'unité de sortie (7) contient un piston de sortie (6), qui sépare dans le boîtier d'entraînement (5) deux chambres de travail (12, 13) entre elles, une des chambres de travail ou les deux chambres de travail étant raccordées à des moyens à soupape de commande (25, 26) du système d'entraînement pneumatique, servant à commander l'exposition à l'air comprimé, lesquels moyens à soupape de commande peuvent être commutés entre plusieurs positions de commutation, parmi lesquelles se trouve une position à économie d'air (30) prédéfinissant une section transversale d'étranglement, et lesquels moyens à soupape de commande présentent comme autre position de commutation, une position à force élevée (29) prédéfinissant une section transversale d'écoulement plus grande en comparaison avec la section transversale d'étranglement, sachant que des moyens d'actionnement (36, 37) appartenant au système d'entraînement pneumatique sont associés aux moyens à soupape de commande (25, 26), lesquels moyens d'actionnement commandent au cours de l'amenée d'air comprimé dans une chambre de travail (12, 13) la commutation des moyens à soupape de commande (25, 26) raccordés à cette chambre de travail (12, 13) en fonction de l'air comprimé régnant dans au moins une chambre de travail (12, 13) de telle manière qu'une commutation d'une position à économie d'air (30) prise dans les conditions normales dans une position à force élevée (29) a lieu, lorsque et au moins aussi longtemps que l'unité de sortie (7) est exposée à une résistance de déplacement élevée, caractérisé en ce que les moyens à soupape de commande (25, 26) présentent comme autre position de commutation une position d'arrêt (31) prédéfinissant une section transversale d'écoulement plus petite en comparaison avec la section transversale d'étranglement, et en ce que d'autres moyens d'actionnement (38, 39) pouvant être activés en fonction de la position de l'unité d'entraînement (7) sont associés aux moyens à soupape de commande (25, 26), lesquels moyens d'actionnement peuvent entraîner la commutation dans une position d'arrêt (31), lorsque l'unité de sortie (7) atteint lors de son déplacement en service, une position de fin de course ou une position un peu juste avant la position de fin de course.
  2. Système d'entraînement selon la revendication 1, caractérisé en ce que le mécanisme d'entraînement pneumatique (2) au moins au nombre de un est un mécanisme d'entraînement linéaire.
  3. Système d'entraînement selon la revendication 1 ou 2, caractérisé en ce que le mécanisme d'entraînement pneumatique (2) au moins au nombre de un est un cylindre pneumatique, dont l'unité de sortie (7) contient une tige de piston (4) faisant saillie côté frontal du boîtier d'entraînement (5).
  4. Système d'entraînement selon la revendication 3, caractérisé en ce que le cylindre pneumatique est un cylindre briseur de croûte, au niveau de la tige de piston (4) duquel est disposé côté frontal un élément tamponneur (24) approprié pour passer à travers la croûte d'un bain de fusion métallique.
  5. Système d'entraînement selon l'une quelconque des revendications 1 à 4, caractérisé en ce que les moyens d'actionnement (36, 37) sont réalisés de telle manière qu'ils commandent la commutation des moyens à soupape de commande (25, 26) en fonction de l'air comprimé régnant dans la chambre de travail (12, 13) raccordée aux moyens à soupape de commande (25, 26).
  6. Système d'entraînement selon la revendication 5, caractérisé en ce que les moyens d'actionnement (36, 37) sont réalisés de telle manière qu'ils commutent les moyens à soupape de commande (25, 26) de la position à économie d'air (30) prise jusqu'à présent dans la position à force élevée (29), lorsque l'air comprimé régnant dans la chambre de travail (12, 13) raccordée à ces moyens à soupape de commande (25, 26) est élevé à une valeur seuil de commutation prédéterminée.
  7. Système d'entraînement selon la revendication 5 ou 6, caractérisé en ce que les moyens à soupape de commande (25, 26) contiennent un organe à soupape de commande (32) définissant par la position qu'il prend à ce moment la position de commutation des moyens à soupape de commande (25, 26), dans lequel organe à soupape de commande la pression d'entrée est commutée en agissant en direction de la position à économie d'air (30), et la pression de sortie des moyens à soupape de commande (25, 26) est commutée en agissant en direction de la position à force élevée (29), et lequel organe à soupape de commande est soumis à l'action de moyens à ressort (46) en plus dans la direction de la position à force élevée.
  8. Système d'entraînement selon la revendication 7, caractérisé en ce que les moyens à ressort (46) sont réalisés de manière à pouvoir être ajustés dans leur force de réglage.
  9. Système d'entraînement selon la revendication 7 ou 8, caractérisé en ce qu'un emplacement d'étranglement (47) entraînant sur l'organe à soupape de commande (32) l'établissement décalé dans le temps d'une force de pression est inséré dans le canal d'alimentation (45) commutant la pression de sortie dans l'organe à soupape de commande (32).
  10. Système d'entraînement selon l'une quelconque des revendications 1 à 9, caractérisé en ce qu'est commutée en amont des moyens à soupape de commande (25, 26) côté entrée, une soupape spécifiant la direction (16) réalisée de manière à pouvoir être reliée à une source d'air comprimé (17) ou de manière reliée à cette dernière, réalisée en particulier comme une soupape 5/2 voies, laquelle soupape est en mesure d'alimenter les deux chambres de travail (12, 13) en alternance, à contre-sens en air comprimé ou de les ventiler.
  11. Système d'entraînement selon l'une quelconque des revendications 1 à 10, caractérisé en ce que les autres moyens d'actionnement (38, 39) contiennent des moyens de réponse (48, 49) réagissant à une position prédéterminée de l'unité de sortie (7) et provoquant ainsi la commutation dans la position d'arrêt (31).
  12. Système d'entraînement selon la revendication 11, caractérisé en ce que les moyens de réponse (48, 49) comportent au moins un organe d'ajustage (48a, 49a) dépassant sur le trajet de course de l'unité de sortie (7), de préférence présentant une forme de coulisseau.
  13. Système d'entraînement selon l'une quelconque des revendications 1 à 12, caractérisé en ce que les moyens à soupape de commande (25, 26) servant à prescrire leurs positions de commutation contiennent un organe à soupape de commande (32) pouvant être positionné au choix dans l'une des trois positions.
  14. Système d'entraînement selon l'une quelconque des revendications 1 à 13, caractérisé en ce que la section transversale d'écoulement libérée dans la position d'arrêt (31) des moyens à soupape de commande (25, 26) présente une mesure qui prescrit un débit, qui correspond au moins à la fuite survenant dans le mécanisme d'entraînement pneumatique et se trouve de manière opportune dans la zone de cette fuite.
EP06707116A 2006-02-21 2006-02-21 Systeme pneumatique d'entrainement Expired - Lifetime EP1987255B1 (fr)

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PCT/EP2006/001538 WO2007095964A1 (fr) 2006-02-21 2006-02-21 Systeme pneumatique d'entrainement

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EP1987255A1 EP1987255A1 (fr) 2008-11-05
EP1987255B1 true EP1987255B1 (fr) 2012-06-06

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US (1) US7896102B2 (fr)
EP (1) EP1987255B1 (fr)
CN (1) CN101384825B (fr)
AU (1) AU2006338713B2 (fr)
CA (1) CA2640774C (fr)
NO (1) NO334223B1 (fr)
WO (1) WO2007095964A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2948426B1 (fr) * 2009-07-21 2011-09-02 Asco Joucomatic Sa Dispositif de commande d'un verin pneumatique
DE102011088972A1 (de) * 2011-12-19 2013-06-20 Robert Bosch Gmbh Pneumatische Werkzeugvorrichtung
DE102011088979A1 (de) * 2011-12-19 2013-06-20 Robert Bosch Gmbh Pneumatische Werkzeugvorrichtung
DE102012208891A1 (de) * 2012-05-25 2013-11-28 Robert Bosch Gmbh Pneumatische Schlagwerkvorrichtung
CN103738854A (zh) * 2013-12-24 2014-04-23 安徽山河矿业装备股份有限公司 一种气动单轨吊驱动控制系统
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system
US11092170B2 (en) 2017-02-15 2021-08-17 Nikon Corporation Dual valve fluid actuator assembly
DE102018217337A1 (de) * 2018-10-10 2020-04-16 Festo Se & Co. Kg Bewegungsvorrichtung, Reifenhandhabungsvorrichtung und Verfahren zum Betrieb eines fluidischen Aktors
WO2020095775A1 (fr) * 2018-11-09 2020-05-14 Smc株式会社 Dispositif de commande de débit et dispositif d'entraînement le comprenant
DE102019104283A1 (de) * 2019-02-20 2020-08-20 Saurer Technologies GmbH & Co. KG Steuereinheit zur pneumatischen Ansteuerung eines aktiven Spulengatters

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3118764A1 (de) * 1981-05-12 1983-03-17 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover Pneumatische tuerbetaetigungsanlage
IL78698A (en) * 1986-05-06 1990-11-05 Goldman Giora Hydraulic-pneumatic actuator for impact cutter
US5163353A (en) * 1991-12-12 1992-11-17 Ross Operating Valve Company Energy saving and monitoring pneumatic control valve system
JPH07127607A (ja) * 1993-09-07 1995-05-16 Yutani Heavy Ind Ltd 作業機械の油圧装置
ATE230824T1 (de) 1994-07-15 2003-01-15 Tyco Flow Control Pacific Pty Aktuator
JP3817617B2 (ja) * 1999-05-10 2006-09-06 新日本製鐵株式会社 さく孔装置
DE10013270A1 (de) * 2000-03-17 2001-09-20 Krupp Berco Bautechnik Gmbh Fluidbetriebenes Schlagwerk
US6557647B2 (en) * 2000-05-30 2003-05-06 American Piledriving Equipment, Inc. Impact hammer systems and methods
SE517901C2 (sv) 2000-08-15 2002-07-30 Parker Hannifin Ab Styrsystem för pneumatiska drivanordningar
US6981558B2 (en) * 2001-05-02 2006-01-03 Wacker Construction Equipment Ag Controller for an unbalanced mass adjusting unit of a soil compacting device
DE10123202A1 (de) * 2001-05-12 2002-11-14 Krupp Berco Bautechnik Gmbh Verfahren und Vorrichtung zur Absicherung eines fluidbetriebenen Schlagwerks gegen Leerschläge

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CA2640774A1 (fr) 2007-08-30
EP1987255A1 (fr) 2008-11-05
CN101384825A (zh) 2009-03-11
US20100276171A1 (en) 2010-11-04
US7896102B2 (en) 2011-03-01
NO20083999L (no) 2008-11-19
CA2640774C (fr) 2013-04-02
NO334223B1 (no) 2014-01-13
AU2006338713A1 (en) 2007-08-30
WO2007095964A1 (fr) 2007-08-30
AU2006338713B2 (en) 2011-05-12
CN101384825B (zh) 2011-11-16

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