EP1987255A1 - Systeme pneumatique d'entrainement - Google Patents

Systeme pneumatique d'entrainement

Info

Publication number
EP1987255A1
EP1987255A1 EP06707116A EP06707116A EP1987255A1 EP 1987255 A1 EP1987255 A1 EP 1987255A1 EP 06707116 A EP06707116 A EP 06707116A EP 06707116 A EP06707116 A EP 06707116A EP 1987255 A1 EP1987255 A1 EP 1987255A1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve means
drive system
switching
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.)
Granted
Application number
EP06707116A
Other languages
German (de)
English (en)
Other versions
EP1987255B1 (fr
Inventor
Ulrich Hirling
Ute Casimir
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 EP1987255A1 publication Critical patent/EP1987255A1/fr
Application granted granted Critical
Publication of EP1987255B1 publication Critical patent/EP1987255B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F15B11/02—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, which has a drive housing and a driven in this regard by compressed air driven output unit, wherein the output unit includes a driven piston, which divides in the drive housing two working chambers of which one or both controlled to Serving compressed air serving control valve means are connected, which are switchable between a plurality of switching positions, among which there is a one NEN throttle section predetermining air-saving.
  • a known from WO 02/14698 Al pneumatic drive system of this type is used for crust crusher applications in aluminum processing. It contains a pneumatic drive designed as a crusher cylinder, whose output unit can be driven to perform oscillating working movements in which it is temporarily immersed in an aluminum melt bath while puncturing a possibly constructed material crust.
  • a directional presetting valve which controls the supply and discharge of compressed air in two working chambers divided by the output piston of the output unit.
  • the control of the compressed air supply also has doubly existing control valve means, which are connected in the connection between the directional specification valve and a respective working chamber. are turned on. These control valve means can assume different switching positions, wherein a switching position is responsible for causing the working movement by releasing an air passage.
  • 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 meets an aluminum crust and is therefore opposed to increased resistance to movement, progressively higher actuating pressure gradually builds up in the connected working chamber over the throttle cross section until the required penetration force has been achieved.
  • 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.
  • An essential object of the present invention is to propose measures which allow a reduction in the allow no excessive consumption of compressed air.
  • control valve means as a further switching position have a comparatively s to the throttle cross-section larger Strömungsguerquaint predetermining high power position, and that the control valve means are assigned actuating means, the switching of connected to this working chamber control valve means during the compressed air supply into a working chamber as a function of the air pressure prevailing in at least one working chamber, such that switching takes place from the normally assumed air-saving position into the high-force position, if and at least as long as the drive unit is exposed to an increased resistance to 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, the degree of filling of the connected
  • the at least one linear drive is preferably a pneumatic cylinder with a piston rod which can be used as a crust breaker cylinder.
  • the use is not limited to the range of crust crusher applications 5.
  • 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 lo. 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 assumed position of a control valve member of this 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 Häkam-
  • the switching takes place in the high-force position. If the actuating force of the spring means can be set variably, it is possible to individually set the switching threshold.
  • Control valve means in the depressurized state the high pressure take up. If the operating pressure is switched on, in particular through the intermediary of an upstream directional specification valve, a delayed build-up of the actuating force resulting from the outlet pressure can be caused by a throttling point connected to the outlet pressure, so that the control valve means immediately assume the air-saving position.
  • a further advantage can be achieved if the control valve means have a third switching position, in which the compressed air is made available in comparison with the throttle cross-section smaller flow cross-section.
  • This switching position is referred to as a holding position, because it 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 switching can be caused mechanically, for example due to a cooperating with the output unit ram actuated actuator, but also electrically, using suitable position sensor means.
  • the reduced flow cross-section available in the stop position prevents too much filling of the connected working chamber and at the same time compensates for possible leakage losses, so that the drive unit is held constant and does not perform any 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.
  • Figure 1 shows the pneumatic drive system as a simplified circuit diagram in a preferred embodiment which is particularly, but not exclusively, suitable for crust crusher applications.
  • the pneumatic drive system designated in its entirety by reference numeral 1 comprises at least one pneumatic drive 2, which is expediently a linear drive. Associated with 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 contains a housing designated as a drive housing 5, having a certain longitudinal extent, in the interior of which there is a linearly displaceable output piston 6 which is combined with the already mentioned piston rod 4 to form a movement unit designated as output unit 7.
  • 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.
  • 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 are connected with their pneumatic drive 2 opposite ends.
  • 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 provides pressurized air under a certain operating pressure.
  • the directional specification valve is exemplified by a 5/2 way valve. It is biased by a spring device 22 in an apparent from Figure 1 basic 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 can also consist of several functionally linked individual valves, for example, two 3/2 way valves.
  • the pneumatic drive 2 is designed as Krustenbrecherzylinder.
  • an impact element 24 which is suitable for penetrating 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.
  • the driven unit 7 When the driven unit 7 is retracted - this condition is evident from FIG. 1 - the push element 24 occupies a position at a distance above the material 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.
  • the first and second control valve means 25, 26 operating independently of one another are connected to the two working chambers 12, 13.
  • 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 specification valve 16, a particularly controlled pressurized air admission of the respectively connected working chamber 12, 13.
  • 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 stop 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 are in the air-saving position.
  • 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.
  • the flow cross-section released in the air-saving division 30 is referred to as the 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 unhindered, thus at the valve output 28 is compared to the operating pressure fed lower output pressure, which is present as the instantaneous working pressure in the connected working chamber 12, 13.
  • the flow cross section released in the high force position 29 is greater 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 operation takes place irrespective of whether the control valve means 25, 26 had previously taken up the high-force position 29 or the air-saving division 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 fed working chamber 12, 13 prevails and which in this case coincides with the prevailing at the valve outlet 28 outlet pressure.
  • the design is expediently such that normally, when the output unit 7 can move without interruption, the air-purging 30 is present and that, starting therefrom, a switch to the high-power position 29 is caused when the output unit 7 during its working movement 8a, 8b is exposed to an increased resistance to movement and thereby increases in the currently supplied with compressed air working chamber 12, 13 prevailing working pressure 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 Heilbeetzleyungs 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 air admission surface 43 is acted upon by the outlet pressure prevailing at the valve outlet 28.
  • 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 pedestrian means 46 is expediently adjustable, which is illustrated symbolically 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 compressed air which has been ejected from the second working chamber 13 by the output piston 6 passes through the high-force position which is also enabled by the spring means 46 in the likewise full passage. Since the control line 15 is at 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 the operating pressure hitherto prevailing in the entire first control line 14 can act on the first air-admission surface 42 without restriction, but due to the intermediate throttle restriction 47, an initially only low activation pressure is applied to the second air-admission surface 43.
  • the design is such that the 42 imposed on the first air i5 impact surface, in the direction of
  • Air-pressure acting pressure force is greater than the sum of the pressure applied to the second Heilbeierschungs composition 43 and the force of the spring means 46th
  • 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 Querterrorismsgr ⁇ ße of the released in the air-saving throttle area. Since the working pressure increasing in the applied working chamber 12 or 13 also acts on the control valve member 32 via the second admission passage 45, the operating force 5 acting in the direction of the high force position eventually exceeds the opposite operating force effective over the first air impingement face 42.
  • 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 restoring force lo of the spring means 46.
  • an operating pressure of 6 bar is applied, from which a working chamber pressure of 2 bar results in the air-purging, wherein the switching threshold value for switching to the high-force position is at a working chamber pressure of approximately 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 occurs when an increased resistance to movement occurs. In many cases, this will not be the case, so that then a operation under full utilization of the air-saving function is possible.
  • control valve means 25, 26 allow the already mentioned additional switchover to a holding position 31.
  • the further actuation means 38, 39 are designed such that they bring about the holding position currently enabling compressed air to be fed into a working chamber 12 or 13 into the holding flow which enables an only greatly reduced flow throughput, if the output unit 7 reached a stroke end position or a position just before the Hubendlage.
  • 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 permitted flow corresponds at least substantially to the leakage occurring in the pneumatic drive 2.
  • the permitted flow rate is at least equal to or slightly greater than the 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 expediently on or in the drive housing 5, wherein they 5 are formed in the embodiment in order to produce a purely mechanical switching of the control valve means 25, 26.
  • each comprise at least one stelike actuator 0 48a, 49a, which protrudes into the stroke of the output unit 7, that it is acted upon by these on reaching the desired switching position and relocated.
  • the response means 48, 49 are direct components of the control valve means 25, 26.
  • the control valve means 25, 26 to install directly on or in the drive housing 5, as indicated by dash-dotted lines in Figure 1.
  • the control valve means 25, 26 are shown separately in FIG. 1 from the drive housing 5 and it is made clear by respectively assigning the reference numerals 48, 49 which response means 48, 49 belong to which control valve means 25, 26.
  • a purely mechanical switching has the advantage that can be dispensed with an electrical equipment.
  • responsive sensors 48, 49 without contact with the position of the output unit 7 to be detected, which output an electrical sensor signal upon activation, by means of which electrical switching of the control valves 25, 26 into the Haltment 31 is caused.
  • the switching between the high-force position 29 and the air-purging position 30 can also be caused by electrical signals when the relevant pressure parameters are picked up by pressure switches or pressure sensors.
  • At least the two control valves 5, 25 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 just a pneumatic drive 2, in which case each pneumatic drive 20 is expediently assigned its own first and second control valve means 25, 26.
  • the directional specification valve 16 in contrast, can in principle serve for the simultaneous control of several parallel-connected pneumatic drives 2.
  • the pneumatic kantrieb 2 associated control valve means 25, 26 may be present only simply. 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un système pneumatique d'entraînement (1) dans lequel le déplacement d'une unité entraînée (7) d'un entraînement pneumatique (2) est contrôlé par des moyens (25, 26) à soupape de commande raccordés aux chambres de travail (12, 13) de l'entraînement pneumatique (2). Les moyens (25, 26) à soupape de commande présentent au moins une position (30) d'économie d'air qui définit une section transversale étranglée et une position (29) à force élevée qui définit une section transversale d'écoulement plus grande que la précédente. Des moyens d'actionnement (36, 37) permettent de déplacer les moyens (25, 26) à soupape de commande depuis la position (30) d'économie d'air normalement prise jusque dans la position (29) à force élevée en fonction de la pression d'air qui règne dans au moins l'une des chambres de travail (12, 13) lorsque l'unité d'entraînement (7) subit une plus grande résistance au déplacement.
EP06707116A 2006-02-21 2006-02-21 Systeme pneumatique d'entrainement Expired - Lifetime EP1987255B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2006/001538 WO2007095964A1 (fr) 2006-02-21 2006-02-21 Systeme pneumatique d'entrainement

Publications (2)

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

Family

ID=37079506

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06707116A Expired - Lifetime EP1987255B1 (fr) 2006-02-21 2006-02-21 Systeme pneumatique d'entrainement

Country Status (7)

Country Link
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)

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DE102011088979A1 (de) * 2011-12-19 2013-06-20 Robert Bosch Gmbh Pneumatische Werkzeugvorrichtung
DE102011088972A1 (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
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Publication number Publication date
EP1987255B1 (fr) 2012-06-06
CA2640774A1 (fr) 2007-08-30
CA2640774C (fr) 2013-04-02
NO20083999L (no) 2008-11-19
CN101384825B (zh) 2011-11-16
AU2006338713A1 (en) 2007-08-30
US20100276171A1 (en) 2010-11-04
WO2007095964A1 (fr) 2007-08-30
NO334223B1 (no) 2014-01-13
AU2006338713B2 (en) 2011-05-12
US7896102B2 (en) 2011-03-01
CN101384825A (zh) 2009-03-11

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