EP1130272B1 - Distributeur - Google Patents

Distributeur Download PDF

Info

Publication number
EP1130272B1
EP1130272B1 EP01102432A EP01102432A EP1130272B1 EP 1130272 B1 EP1130272 B1 EP 1130272B1 EP 01102432 A EP01102432 A EP 01102432A EP 01102432 A EP01102432 A EP 01102432A EP 1130272 B1 EP1130272 B1 EP 1130272B1
Authority
EP
European Patent Office
Prior art keywords
valve
switching
spring means
valve according
control unit
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
EP01102432A
Other languages
German (de)
English (en)
Other versions
EP1130272A2 (fr
EP1130272A3 (fr
Inventor
Grzegorz Bogdanowicz
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 EP1130272A2 publication Critical patent/EP1130272A2/fr
Publication of EP1130272A3 publication Critical patent/EP1130272A3/fr
Application granted granted Critical
Publication of EP1130272B1 publication Critical patent/EP1130272B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor

Definitions

  • the invention relates to a valve having a control device which has a valve slide for controlling fluid flows and which can be driven by applying adjusting forces relative to the valve housing to a first switching movement following a first switching direction and a second switching movement following an opposite second switching direction and thereby positionable in different switching positions wherein it is displaceable in the first switching movement while covering a switching path from a first switching position in a predetermined by housing stop means final switching position, wherein at only one end portion of the control device, a drive means is provided at the first switching movement under tension settable spring means and wherein the control device can be held by acting in the first switching direction first actuating forces in the end-switching position, from which they by Aufb Ringing of acting in the opposite second switching direction second actuating forces in the context of the second switching movement is moved out, and wherein the valve is designed as a two-position valve, which is switchable without an intermediate switching position only between the first switching position and the end switching position.
  • the valve in turn is connected to a working piston, the piston chamber is acted upon depending on the switching position of the valve with hydraulic fluid or emptied.
  • the valve has a valve housing defining a valve space in which a valve piston is arranged axially movable.
  • the valve piston divides the valve chamber into a first and second piston chamber, which can be acted upon by hydraulic fluid, in order to move the valve piston in one or the other direction.
  • the valve piston also has at its opposite end faces lying recesses, in each of which a spring element is integrated, wherein the spring elements hold the valve piston in a central position, provided that the piston chambers are not acted upon by hydraulic fluid.
  • valve piston moves from its central position to one of its end positions, wherein it abuts against the rear wall of the piston chamber which is not fluid-stressed. At the same time the projecting into the non-fluid-loaded piston chamber spring is tensioned. As soon as the pressure escapes from the fluid-loaded piston chamber, the valve piston moves from its end position back into its middle position due to the spring force of the preloaded spring.
  • a multi-way valve is apparent, for example, from EP 0 678 676 B1.
  • the control device is formed by a piston-like valve slide with axially upstream actuating piston and can be positioned by applying a control fluid in two opposite end switching positions. Depending on the switching position while the valve channels of the valve are fluidly linked with different configuration.
  • a problem with all valves of this type is that with prolonged whereabouts of the control device in one of the end switching positions, the static friction between the valve spool and the enclosing seals this greatly increases. This behavior is particularly typical for standstill periods of 2 hours or more. The consequence of this is that the forces required to move out of the control device from the respective end shift position and to switch to a different shift position increase. This, in turn, causes the switching resistance opposed to the available fluidic actuating forces to be increased, so that the switching times increase, which can cause malfunctions in the loads connected to the valve. Particularly critical is the behavior in monostable two-position valves.
  • first actuating forces acting in the first switching direction are caused by an air spring, by which the control device is held in the final switching position
  • drive means is designed such that the spring means at the beginning of the final Switching position directed first switching movement are still ineffective and are set only during the end portion of the first switching movement by the kinetic energy of the controller under tension, the clamping force of the spring means at the beginning of the second switching movement in addition to the actuating forces generated by the compressed air supply contributes to the generation of the second actuating forces.
  • At least one drive device may also be provided on the control device, so that it is supported by this and moved along with the switching movements.
  • this type of construction can be implemented considerably more simply than integration into the valve housing.
  • the drive device is integrated into an actuating piston of the control device, which constitutes a separate part with respect to the valve slide, so that it can be used very simply instead of a conventional actuating piston.
  • the tensioning of the spring means is expediently effected in that the spring means is compressed between the moving control device and housing-fixed support means when the control device approaches its final switching position.
  • the necessary for tensioning the spring means distance can be very low and in particular significantly less than the remaining distance of the switching path, in which the spring means are still out of function and not yet compressed. As a result, the control device remains sufficient time during the switching movement for the construction of the kinetic energy required for tensioning the spring means.
  • the applied at the beginning of the clamping process and the spring means associated impact surface is suitably located on a displaceably guided drive ram of the drive means, which can be added directly adjustable in the valve housing or in the control device.
  • the spring means are under a certain pretension even in the unbiased state.
  • adjusting means may be provided which allow a variable specification of the bias of the spring means.
  • Such adjustment means also allow a tolerance compensation with respect to the length of the spring means, in particular if they are formed by at least one mechanical spring.
  • the spring means may also be formed by a gas spring and preferably by an air spring.
  • the drive device is expediently assigned to an axial end region of the control device. It is possible, in the case of a control device having two end switch positions, to assign a drive device to both end shift positions, specifically expediently in the region of the two axial ends of the control device.
  • the first actuating forces are formed by an air spring, for example to realize a monostable two-position valve.
  • the first actuating forces at befindlichem in the end switching position control device can be substantially balanced by the clamping force, so that the applied by a control fluid actuating forces must overcome only the static friction of the sealing measures to the control device again from the final switching position to switch to another switch position.
  • valve 1 shown in the drawing is a multi-way valve
  • the concrete example shows a 5/2-way valve.
  • the valve 1 has a valve housing 2, which in the present case contains a main body 3, at whose two axial end sides in each case a closure body 4, 5 is arranged.
  • Suitable fastening means for fixing the terminal body 4, 5 on the main body 3 are indicated by dash-dotted lines at 6, which are, for example, fixing screws.
  • valve housing 2 In the interior of the valve housing 2 extends in the longitudinal direction of an elongated receiving space 7, in which a likewise elongate control device 8 is housed.
  • the control device 8 includes a piston-like elongated valve spool 12 and two adjusting pistons 13, 14, which are upstream of the valve spool 12 at its two axial end faces.
  • valve channels 15 In the receiving space 7 open laterally, at longitudinally spaced locations, a plurality of valve channels 15, wherein the communicating with the individual valve channels 15 receiving space portions are axially flanked on both sides each of an annular sealing means 16.
  • the valve spool 12 has in the longitudinal direction alternately over areas of larger and smaller cross-section, depending on the instantaneous axial position of the valve spool 12 with each of the fixed housing fixed in the embodiment sealing means 16 or not work together. If there is a sealing contact, the receiving space sections located on both sides of the respective sealing device 16 are separated from each other in a fluid-tight manner.
  • valve spool 12 there is an area smaller diameter of the valve spool 12 at the same height with a sealing device 16, there is a gap through which the adjacent receiving space sections are interconnected, so that a fluid pressure medium between the thus communicating with each other valve channels 15 can flow.
  • one of the valve channels 15 is a feed channel P, via which the pressure medium to be distributed through the valve, in particular compressed air, is fed.
  • a feed channel P via which the pressure medium to be distributed through the valve, in particular compressed air, is fed.
  • On both sides adjacent to the feed P each opens a working channel A, B in the receiving space 7, wherein these working channels A, B are connected to a consumer, for example with a pneumatic cylinder.
  • At each working channel A, B closes axially outward still a vent channel R, S on.
  • the sealing devices 16 surround the control device 8 coaxially, wherein they each contain an existing of suitable sealing material annular sealing body 17, for example, an elastomeric body.
  • the sealing body 17 is held in the embodiment of an annular, radially inwardly open seal housing 18, via which the sealing means 16 is fixed to the inner surface of the receiving space 7, for example by pressing.
  • the sealing contact between a sealing device 16 and the control device 8 is brought about in that the sealing body 17 encloses a portion of larger diameter of the valve spool 12 with sealing contact.
  • the control device 1 is switchable in the embodiment between two switching positions.
  • the first possible switching position is shown in Figure 1 below the longitudinal axis 22 of the receiving space 7, while the second switching position - hereinafter referred to as the end switching position - is shown above the longitudinal axis 22.
  • the valve channel assignment such that the feed channel P is in communication with a working channel B, while the other working channel A communicates with the one vent channel R.
  • the second venting channel S is shut off here.
  • the feed channel P is in communication with the previously vented working channel A, while at the same time the other working channel B is vented via the previously still closed vent channel S.
  • the remaining remaining vent channel R is shut off.
  • the movement taking place for shifting the control device 8 from the first switching position into the final switching position is referred to as the first switching movement and proceeds in a first switching direction indicated by an arrow.
  • the shifting of the control device 8 out of the end switching position into the first switching position be referred to as a second switching movement and takes place in a first switching direction 23 opposite, also marked by an arrow second switching direction 24.
  • the switching directions are rectified with the longitudinal axis 22.
  • the valve of the exemplary embodiment is a monostable valve which has a preferred switching position in the form of the end switching position. This is called forth by the fact that the one, in Figure 1 right-most actuator piston 13 is acted upon at its the valve spool 12 opposite first loading surface 25 constantly by a standing under a certain operating pressure fluidic pressure medium in the form of compressed air.
  • compressed air is branched off from the feed channel P through a first actuating channel 26 in the interior of the valve housing 2 and fed into a first admission chamber 27 formed by the associated end region of the receiving chamber 7, which is delimited by the movable actuating piston 13 or its first loading surface 25.
  • the term "fluid" or "pressure medium” is understood in the following compressed air.
  • control device 8 By the force acting on the first loading surface 25 pressure medium, the control device 8 undergoes first actuating forces Si, which are effective in the first switching direction 23.
  • the second actuating piston 14 assigned to the opposite axial end region of the valve slide 12 is, like the other, the first actuating piston 13 guided so as to be displaceable in the associated end section of the receiving space 7.
  • an annular sealing device 28 may be provided be seated in an annular groove of the respective actuating piston 13, 14 and is in sliding sealing contact with the radially facing inner peripheral surface 32 of the receiving space 7.
  • the second actuating piston 14 delimits a second admission area 34 formed by the associated end section of the receiving space 7 with a second admission area 33 which is axially remote from the valve slide 12.
  • the latter is connected to the feed channel P via a second actuation channel 35 like the first admission area 27 However, it is a controlled connection.
  • a pilot valve 36 is turned on, which has an electrically activatable actuator 37 - for example, an electromagnet or a piezoelectric device - through which the fluid passage through the second actuation channel 35 through selectively released or blocked can.
  • blocked second actuating channel 35 of the second admission chamber 34 is vented by a channel guide, not shown, for example, within the actuator 37.
  • control fluid could be supplied instead of a branch from the feed channel P by a separate control channel, which also applies to the serving for acting on the first actuating piston 13 pressure medium.
  • the receiving space 7 preferably extends in the longitudinal direction through the entire main body 3 and into the two closing bodies 4, 5. At least the major part of their travel, the adjusting piston 13, 14 while within the respective associated closure body 4, 5 back, to obtain an optimum sliding surface, a guide sleeve 38 can be coaxially inserted into the respective end portion of the receiving space 7.
  • the actuating device 37 is expediently also provided on one of the closure body 4.
  • control device 8 If the supply of control fluid into the second admission chamber 34 is prevented by the actuating device 37 and the latter is vented, the control device 8 is displaced in the first switching direction 23 starting from the first switching position until finally the first end switching position is defined, characterized in that the control device 8 comes into abutment with second stop means 39 fixed to the housing on the first stop means 38 provided on it.
  • the latter are formed in the embodiment of the control device 8 axially facing end face 41 of the receiving space 7.
  • the provided on the control device 8 stop means 38 are in the embodiment of the control piston 14 and are preferably of which the end surface 41 axially facing end face 42 is formed.
  • An essential core of the present invention resides in the provision of the aforementioned clamping force F S by means of a drive device 43 shown enlarged in FIG. 2, which is preferably integrated in the actuating piston 14 as shown, and is thus supported by the control device 8 ,
  • the drive device 43 is equipped with spring means 44, which are set during the course of the first switching movement for generating the clamping force F S under tension.
  • the arrangement is such that the spring means 44 ineffective at the beginning of the first switching movement and preferably during most of the switching path are and are set only during the end portion of the first switching movement, ie during the covering of the end switching position immediately upstream portion of the switching path under tension. The latter is done by the kinetic energy of the control device 8, which builds this when passing through the spring means 44 unrestrained portion of the first switching movement. As long as the control device 8 is held by the first actuating forces S 1 in the final switching position, the clamping force F S is stored in the spring means 44.
  • the control device 8 shifts due to the excess of force in the second switching direction 24, wherein the spring means 44 deliver the stored energy in the form of the clamping force F S to the control device 8 and for optimum initial acceleration behavior of the control device 8 to care.
  • the drive means 43 includes a formed in the one base body 45 actuating piston 14 formed drive chamber 46 which is open to the axial end face 42 out.
  • a drive rod 47 is mounted axially adjustable in the direction of Umschaltschien according to double arrow 48.
  • spring means 44 supported on the one hand on the base body 45 and on the other hand on the drive plunger 47 and apply this in a rectified with the first switching direction 23 extension direction 49.
  • the basic position of the drive plunger 47 is predetermined by mutually cooperating and facing each other first and second stop surfaces 53, 54 on the drive plunger 47 and on the actuating piston 14.
  • the drive plunger 47 is stepped in the longitudinal direction and has an end face provided with the impact surface 52 impact portion 56, to which a stop portion 55 of larger diameter connects axially.
  • the first abutment surface 53 is provided on the end face of the abutment portion 55 which is oriented in the extension direction 49 and projects radially beyond the impact portion 56, while the second abutment surface 54 is provided on a sleeve body 57 coaxially surrounding the impact portion 56 and projecting into the drive space 46.
  • the spring means 44 are based on the one hand on the first stop surface 53 opposite oriented back of the abutment portion 55 and on the other hand at this distance by far inner boundary surface 58 of the drive chamber 46th
  • the impact surface 52 in the first switching direction 23 opposite a valve housing fixed counter-impact surface 61 is provided.
  • both the first and second stop means 38, 39 and the impact surface 52 and the counter-impact surface 61 are arranged at a relatively large distance from each other.
  • the drive plunger 47 assumes the basic position.
  • the final switching position is thus characterized Characterized that both the impact surface 52 and the counter-impact surface 61 and the two stop means 38, 39 abut each other, wherein the spring means 44 are stretched to the clamping path h.
  • the conditions of the final switching position are indicated in dash-dotted lines.
  • the clamping of the spring means 44 takes place in the embodiment by compressing the same.
  • This is one or more mechanical springs, preferably compression springs.
  • other types of springs would also be possible and one could resort in particular to a gas spring, preferably in the form of an air spring, wherein the air cushion could be generated for example by branching off compressed air from the channels extending in the valve 1.
  • the clamping force F S acts only during the initial phase of the second switching movement, via a proportion of the switching path corresponding to the clamping path h. Even if this clamping travel h is very small - it can, for example, on the order of 5/10 mm move - the stored spring energy is sufficient to help overcome the initially high static friction forces F H and move the control device 8 in motion. As soon as the control device 8 moves, the actuation forces F B are sufficient to move the control device 8 back into the first switching position and to hold it there for as long as desired, despite constant fluid admission of the first admission space 27.
  • the design of the valve 1 is such that on the basis of identical fluid pressures in the two Beauftschungshack 27, 34, the clamping force F S of the tensioned spring means 44 is equal to or slightly less than the caused by an air spring effect first actuating forces S 1st Despite matching forces, the spring means 44 can be stretched here, because the impact surface 52 by the unimpeded movement of the control device 8 hits the counter-impact surface 61 with force and by the kinetic energy compression of the spring means 44 is possible. That the control device 8 then remains in the final switching position depends on the static friction forces F H caused by the sealing devices 16. If a switching of the control device 8 is then to take place, the control pressure fed in via the second actuating channel 35 must first only be the static friction F H overcome, which is readily possible, so that the control device 8 switches almost instantaneously.
  • the bias voltage can be variable by selecting a corresponding axial mounting depth of the sleeve body 57 with respect to the drive space 46 pretend.
  • the sleeve body 57 thus forms here setting means 62 for variably setting the bias of the spring means 44, wherein in the present case the different mounting depths are realized by varying the width of the sleeve body 57 into the drive chamber 46.
  • the drive device 43 could also be located elsewhere than in the present case at an axial end region of the control device 8.
  • a control device 8 which can be displaced between two end shift positions, with a plurality of drive devices, which, starting from both end shift positions, provide support for the return movement.
  • a drive device could be provided in particular at both axial end regions of the control device 8.
  • At least one drive device is alternatively or additionally on the valve housing.
  • the arrangement can then be imagined, for example, such that the base body 45 is arranged on the housing side and the movable impact surface 52 projects beyond the counter-impact surface 61 provided on the control device 8.
  • the valve housing 2 directly as a basic body for supporting the spring means 44 and optionally for supporting the drive tappet 47.
  • One or both adjusting pistons 13, 14 could well be so firmly connected to the valve spool 12 that they can transmit tensile and compressive forces on the valve spool 12 respectively.
  • an actuator piston drive means 43 is a separate with respect to the valve slide 12 embodiment, because this allows easy retrofitting conventional valves by simply in place of a conventional actuator piston equipped with a drive means 43 actuator piston is used.

Landscapes

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

Claims (16)

  1. Soupape, avec un dispositif de commande (8) comportant un coulisseau de soupape (12) destiné à contrôler des écoulements de fluide, qui par application de forces de réglage (S1, S2) par rapport au corps de soupape (2) peut être entraîné dans un premier déplacement de commutation suivant un premier sens de commutation (23) et dans un deuxième déplacement de commutation suivant un deuxième sens de commutation (24) opposé et peut être positionné de ce fait dans différentes positions de commutation, et pouvant être déplacé lors du premier déplacement de commutation en parcourant un trajet de commutation d'une première position de commutation jusque dans une position de commutation finale prédéfinie par des éléments de butée (39) solidaires du corps, sur seulement une zone d'extrémité du dispositif de commande (8) un dispositif d'entraînement (43) étant prévu, avec des moyens à ressort (44) pouvant être mis en tension lors du premier déplacement de commutation et le dispositif de commande (8) pouvant être maintenu par des premières forces de réglage (S1) agissant dans le premier sens de commutation (23) dans la position de commutation finale, à partir de laquelle il peut être déplacé par des forces de réglage (S2) agissant dans le deuxième sens de commutation opposé (24), dans le cadre du deuxième déplacement de commutation et la soupape étant conçue en tant que soupape à deux positions (1), qui sans position de commutation intermédiaire peut exclusivement commuter entre la première position de commutation et la position de commutation finale, caractérisée en ce que les forces de réglages (S1) agissant dans le premier sens de commutation sont générées par un coussin d'air, qui maintient le dispositif de commande (8) dans la position de commutation finale, en ce que le dispositif d'entraînement (43) est conçu de façon à ce qu'au début du premier déplacement de commutation en direction de la position de commutation finale, les moyens à ressort (44) soient encore inactifs et qu'il ne soient mis en tension que pendant la partie finale du premier déplacement de commutation, par l'énergie cinétique du dispositif de commande (8), l'effort de tension (FS) des moyens à ressort (44) contribuant, en supplément à des forces d'actionnement (FB) générées par l'application d'air comprimé, à la génération des deuxièmes forces de réglage (S2), au début du deuxième déplacement de commutation.
  2. Soupape selon la revendication 1, caractérisée en ce qu'il est prévu au moins un dispositif d'entraînement (43) sur le corps de soupape (2) et ce que celui-ci comprend une surface de collision qui est en interaction avec les moyens à ressort (44), sur laquelle le dispositif de commande (8) peut rebondir par une contre-surface opposée pour assurer la mise en tension des moyens à ressort (44).
  3. Soupape selon la revendication 1 ou 2, caractérisée en ce qu'au moins un dispositif d'entraînement (43) est porté par le dispositif de commande (8) et comprend une surface de collision (52) qui est en interaction avec les moyens à ressort (44), qui pour assurer la mise en tension des moyens à ressort (44) peut rebondir sur une contre-surface de collision (61) opposées , stationnaire sur le corps.
  4. Soupape selon la revendication 2 ou 3, caractérisée en ce que la surface de collision (52) sur laquelle agissent les éléments à ressort (44) qui s'appuient sur le corps de base (45) est prévue sur une tige d'entraînement (47) mobile par rapport à un élément de base (45) du dispositif d'entraînement (43) dans les sens de commutation (23, 24).
  5. Soupape selon la revendication 4, caractérisée en ce que le corps de base (45) est conçu en conséquence du placement du dispositif d'entraînement (43) du corps de soupape (2) ou du dispositif de commande (8).
  6. Soupape selon l'une des revendications 3 à 5, caractérisée en ce que le dispositif d'entraînement (43) est prévu sur ou dans un piston de réglage (14) du dispositif de commande (8) qui est en interaction avec le coulisseau de soupape (12).
  7. Soupape selon la revendication 6, caractérisée en ce que le piston de réglage (14) et le coulisseau de soupape (12) sont conçus comme des éléments mutuellement séparés.
  8. Soupape selon l'une des revendications 1 à 7, caractérisée en ce qu'au moins un dispositif d'entraînement (43) se trouve sur une zone d'extrémité axiale du dispositif de commande (8).
  9. Soupape selon l'une des revendications 1 à 8, caractérisée en ce que le dispositif de commande (8) peut se déplacer entre deux positions de commutation finales, au moins chaque fois un dispositif d'entraînement (43) agissant dans les deux positions de commutation finales.
  10. Soupape selon la revendication 9, en association avec la revendication 8, caractérisée en ce que chaque fois un dispositif d'entraînement (43) est prévu sur les deux zones d'extrémités axiales du dispositif de commande (8).
  11. Soupape selon l'une des revendications 1 à 10, caractérisée en ce que les moyens à ressort (44) sont constamment sous précontrainte.
  12. Soupape selon la revendication 11, caractérisée en ce que sont prévus des moyens de réglage (62) pour la prédéfinition variable de la précontrainte des éléments à ressort (44).
  13. Soupape selon l'une des revendications 1 à 12, caractérisé en ce que les moyens à ressort (44) comprennent au moins un ressort mécanique.
  14. Soupape selon l'une des revendications 1 à 13, caractérisée en ce que les moyens à ressort (44) comprennent au moins un ressort à gaz et à cet effet de préférence un coussin d'air.
  15. Soupape selon l'une des revendications 1 à 14, caractérisé par au moins un dispositif de manoeuvre (37) pour le contrôle de l'application sur le dispositif de commande (8) d'un fluide de commande générant la force d'actionnement (FB) agissant dans le deuxième sens de commutation (24).
  16. Soupape selon l'une des revendications 1 à 15, caractérisée en ce que la force de tension (FS) des moyens à ressort (44) est au moins sensiblement égale ou légèrement inférieure aux premières forces de réglage.
EP01102432A 2000-03-04 2001-02-03 Distributeur Expired - Lifetime EP1130272B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10010690A DE10010690B4 (de) 2000-03-04 2000-03-04 Ventil
DE10010690 2000-03-04

Publications (3)

Publication Number Publication Date
EP1130272A2 EP1130272A2 (fr) 2001-09-05
EP1130272A3 EP1130272A3 (fr) 2003-10-29
EP1130272B1 true EP1130272B1 (fr) 2006-10-25

Family

ID=7633565

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01102432A Expired - Lifetime EP1130272B1 (fr) 2000-03-04 2001-02-03 Distributeur

Country Status (4)

Country Link
US (1) US6450202B2 (fr)
EP (1) EP1130272B1 (fr)
DE (2) DE10010690B4 (fr)
ES (1) ES2269235T3 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6776192B2 (en) 2002-04-12 2004-08-17 Mead Fluid Dynamics, Inc. Pneumatic valve and manifold mounting system
DE102004046976B4 (de) * 2004-09-28 2007-11-08 Festo Ag & Co. Mehrwegeventil
US7465177B2 (en) * 2006-10-10 2008-12-16 Tyco Electronics Corporation Electrical connector having a fluid coupling
DE102008060650A1 (de) 2008-12-05 2010-06-10 Festo Ag & Co. Kg Ventil mit Endlagen-Dämpfungseinrichtung
US8555096B2 (en) * 2009-08-07 2013-10-08 Advanced Processor Architectures, Llc Method and apparatus for selectively placing components into a sleep mode in response to loss of one or more clock signals or receiving a command to enter sleep mode
EP3514394A1 (fr) 2010-05-11 2019-07-24 Parker Hannifin Corp. Système hydraulique à compensation de pression doté d'une commande de la pression différentielle
DE102010044632B4 (de) 2010-09-07 2012-08-16 Festo Ag & Co. Kg Vorgesteuertes Mehrwegeventil
CN106527621B (zh) * 2015-09-10 2019-08-23 讯凯国际股份有限公司 电子系统及其外接式辅助散热装置
DE102016223685A1 (de) * 2016-11-29 2018-05-30 Festo Ag & Co. Kg Ventilanordnung

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US137A (en) * 1837-03-03 Register and air-box for grates and fireplaces
US2870789A (en) * 1956-01-11 1959-01-27 Bilaisis Viktoras Pneumatically operated control valve for hydraulic actuators
US2916879A (en) * 1956-04-04 1959-12-15 John T Gondek Combination hydraulic power unit
NL104412C (fr) * 1956-05-07 1900-01-01
US3060688A (en) * 1959-09-18 1962-10-30 John T Gondek Hydraulic systems
US3267965A (en) * 1963-03-28 1966-08-23 Airmatic Valve Inc Pilot operated spool valve
FR2236132B1 (fr) * 1973-07-03 1983-11-18 Messier Hispano Sa
US4197878A (en) * 1978-03-30 1980-04-15 Ideus, Inc. Hydraulic valve
DE2906258A1 (de) * 1979-02-19 1980-08-28 Reinhard Ing Grad Kucharzyk Servohydraulische einrichtung zur lasteingespannten und lastunabhaengigen steuerung und regelung der druckmittel- beaufschlagung eines druckmittelmotores in abhaengigkeit einer elektrischen sig- nalgroesse
US4267862A (en) * 1979-02-21 1981-05-19 Mac Valves, Inc. Directional control valve with flow path through valve spool
FR2453306B1 (fr) * 1979-04-06 1986-03-14 Dba Dispositif d'actionnement hydraulique a cinq positions
DE8107889U1 (de) * 1981-03-18 1981-10-22 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Pneumatische ventilanordnung
DE4244080A1 (en) * 1992-03-13 1993-09-16 Festo Kg Spring loaded fluid flow switching device - uses return mechanism comprising two pressure elements having axially overlapping sections.
US5490441A (en) * 1994-01-24 1996-02-13 Hallstrom; Olof A. Automatic reciprocation of a reversible fluid pressure unit and switching valve therefor
DE4413657C1 (de) 1994-04-20 1995-11-02 Festo Kg Ventilanordnung
GB2303881B (en) * 1995-07-31 1999-06-23 Honda Motor Co Ltd Inchworm type of actuator

Also Published As

Publication number Publication date
DE50111295D1 (de) 2006-12-07
EP1130272A2 (fr) 2001-09-05
US20010032677A1 (en) 2001-10-25
ES2269235T3 (es) 2007-04-01
US6450202B2 (en) 2002-09-17
DE10010690B4 (de) 2004-03-25
DE10010690A1 (de) 2001-09-13
EP1130272A3 (fr) 2003-10-29

Similar Documents

Publication Publication Date Title
DE102012013284B4 (de) Energiesparventil
EP0829668B1 (fr) Vanne électromagnétique
DE19621951C1 (de) Hydraulische Venbtilsteuervorrichtung
DE2952237A1 (de) Drucksteuerventil
EP1130272B1 (fr) Distributeur
DE19716042C1 (de) Hydraulische Steuervorrichtung für wenigstens ein Hubventil
DE29704758U1 (de) Hydraulische Schalteinheit
EP1302958B1 (fr) Soupape à siège pour vérin différentiel pour sectionneur
DE102016205722B3 (de) Mehrwegeventil
EP0341597A2 (fr) Amortisseurs de chocs à caractéristique d'amortissement variable
DE102004046976B4 (de) Mehrwegeventil
DE19632368A1 (de) Elektrohydraulisches Regelwegeventil
DE29610911U1 (de) Mehrstufige fluidbetätigte Arbeitszylinderanordnung
DE102016224525B4 (de) Mehrwegeventil und Verfahren zu seinem Betreiben
DE102008006777A1 (de) Ventiltrieb mit einem pneumatischen Rückstellsystem
DE19509578B4 (de) Pneumatisches Wegeventil
DE19702948C2 (de) Ventilanordnung
EP1225343A1 (fr) Dispositif d'entrainement par vérin à pression fluidique
EP1369596B1 (fr) Agencement de distributeur hydraulique
DE19529072C2 (de) Schwingungsdämpfer mit verstellbarer Dämpfkraft
DE19709593A1 (de) Vorrichtung zur Verzögerung einer bewegten Masse
EP2426388B1 (fr) Soupape à plusieurs voies précommandée
DE102010032118B4 (de) Bistabiles Mehrwegeventil
DE2647151A1 (de) Gesteuertes verbundventil
DE20119470U1 (de) Differenzdruck-Proportionalventil

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17P Request for examination filed

Effective date: 20031024

17Q First examination report despatched

Effective date: 20040325

AKX Designation fees paid

Designated state(s): DE ES FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20061025

REF Corresponds to:

Ref document number: 50111295

Country of ref document: DE

Date of ref document: 20061207

Kind code of ref document: P

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2269235

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070726

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

Ref country code: GB

Payment date: 20120119

Year of fee payment: 12

Ref country code: IT

Payment date: 20120228

Year of fee payment: 12

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

Ref country code: FR

Payment date: 20130315

Year of fee payment: 13

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

Ref country code: ES

Payment date: 20120123

Year of fee payment: 12

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

Effective date: 20130203

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

Ref country code: IT

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

Effective date: 20130203

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

Ref country code: GB

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

Effective date: 20130203

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20140716

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20141031

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

Ref country code: ES

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

Effective date: 20130204

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

Ref country code: FR

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

Effective date: 20140228

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

Ref country code: DE

Payment date: 20141126

Year of fee payment: 15

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50111295

Country of ref document: DE

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

Ref country code: DE

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

Effective date: 20160901