EP0815361B1 - Clapet d'arret automatique - Google Patents

Clapet d'arret automatique Download PDF

Info

Publication number
EP0815361B1
EP0815361B1 EP96902996A EP96902996A EP0815361B1 EP 0815361 B1 EP0815361 B1 EP 0815361B1 EP 96902996 A EP96902996 A EP 96902996A EP 96902996 A EP96902996 A EP 96902996A EP 0815361 B1 EP0815361 B1 EP 0815361B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
consumer
piston
chamber
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
EP96902996A
Other languages
German (de)
English (en)
Other versions
EP0815361A1 (fr
Inventor
Edmund Kraft
Günter FERTIG
Walter Kirsch
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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 Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP0815361A1 publication Critical patent/EP0815361A1/fr
Application granted granted Critical
Publication of EP0815361B1 publication Critical patent/EP0815361B1/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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • 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
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86759—Reciprocating
    • Y10T137/86767—Spool

Definitions

  • the present invention relates to a pipe rupture safety valve in particular a brake check valve according to the Preamble of claim 1.
  • Valves of this type are used, for example, as counterbalance check valves to regulate the discharge current by an external
  • loads of a consumer cylinder of a lifting cylinder used to lead the consumer ahead to prevent the feed flow.
  • these valves take over at the same time these valves in the event that they are designed as seat pistons are, the function of a leak-free, shutting off the consumer controlled clamping in the respective position Check valve.
  • a Brake check valve known which in a particular embodiment with a positive check valve is trained.
  • This known brake / check valve has one first hollow valve piston with an inner valve seat, the by means of a valve plunger preloaded in the closed position is closable.
  • the inner valve seat has a Valve piston provided first radial bore connection with a first pump-side valve pressure connection.
  • One behind the second radial bore arranged over the valve seat an annular channel with a further valve seat of the check valve connected, which is a second consumer side Valve pressure connection blocks.
  • the above Valve piston also has additional small diameters Radial holes immediately before the inner one Valve seat on and is in a spring Biased position in which a connection between the Ring channel and the small-diameter radial holes interrupted is.
  • Hydraulic fluid flows from the first to lift a load Valve pressure connection through the valve piston, the inner valve seat, the ring channel, the valve seat of the check valve to the second valve pressure connection and becomes a consumer from there headed.
  • the load should be in a certain position will be held when the pump pressure decreases the check valve is pressed onto the valve seat by a spring, whereby the hydraulic pressure at the second valve pressure connection and thus clamped in the consumer.
  • valve piston In this embodiment and the piston of the check valve through the Pressure in a control pressure line against the respective preload springs moves, with a fluid connection between the second valve pressure connection via the now positively opened Check valve seat, the rink channel and the small-diameter radial bores and the first valve pressure connection is produced, which in this case has a external directional valve is connected to a tank.
  • This valve has a hollow valve piston which is biased against a valve seat connecting two valve pressure connections by means of a spring which is located in a spring chamber.
  • a spring which is located in a spring chamber.
  • the valve piston there is also an internal pilot seat valve which can be positively opened by means of a control piston which can be actuated by control pressure.
  • the brake / shut-off valve is connected in parallel to a check valve arranged in a pressure line leading to the consumer with its two connections, the spring space being permanently subjected to the load pressure.
  • the pressure connection located upstream of the check valve is acted upon by a pump pressure which is increased in relation to the load pressure prevailing in the connection downstream downstream of the check valve in accordance with the force of the spring in the check valve, the valve piston being affected by both the piston spring and by the load pressure prevailing in the spring chamber is pressed onto the valve seat. If the load is to be held in one position, the external non-return valve closes, while the valve piston of the brake / shut-off valve continues to be held in the closed position and the pump-side valve connection is essentially depressurized. To lower the load, the control piston is actuated to open the internal pilot seat valve, which relaxes the pressure in the spring chamber.
  • the valve piston When the actuating piston is actuated further, the valve piston is lifted off the valve seat and the consumer pressure is thus released into a tank. It has been shown that with this valve design, the varying level of pressure at the pump-side valve connection has an adverse effect on the control of the valve piston.
  • the housing of the brake / check valve, in particular the spring chamber must be solid and particularly fluid-tight, since it is permanently exposed to the load pressure and must therefore withstand it.
  • a brake / check valve preferably as a pipe rupture safety valve create which is a simpler and cheaper Has structure.
  • Pipe rupture safety valve with the in claim 1 specified features solved.
  • it has Pipe burst safety valve according to the invention, a servo valve, that at least two internal work connections and one Has valve piston, which by a bias spring in a first position separating the work connections is biased.
  • the valve piston is with a formed first control edge, by means of which one of the Pressure connections can be closed.
  • an annular collar provided which the biasing spring against the Seals pressure connections.
  • Valve seat formed by a sleeve which in one in the Pipe rupture valve housing drilled Location hole is inserted. This construction enables quasi a complete and therefore inexpensive Pre-assemble the servo valve before putting it in the Pipe burst safety valve is used.
  • the development according to claim 5 further provides that the pipe rupture safety valve, optionally with a pump or a tank connectable valve connection, as well as a Has consumer connection with a pressure supply channel an intermediate pressure / feed valve with each other are connected to which a return channel is connected in parallel in which the servo valve is interposed.
  • the integral arrangement of the combined pressure / feed valve not only simplifies the channel routing within the Pipe burst safety valve but also its assembly, so that this also saves costs.
  • the further measure is specified on a the biasing spring opposite side of the valve piston form a cavity by one on the valve piston Additional ring collar arranged in one piece against the working pressure leading consumer chamber is separated.
  • the Cavity according to claim 10 preferably through the additional ring collar trained throttle point with the consumer chamber connected, wherein according to claim 11, the cavity Leakage line is connected via a channel in which the Pilot seat valve sits.
  • the brake / check valve as a pipe rupture safety valve in its basic structure an integrated Servo valve 1 with at least two internal pressure connections 2, 3 and a valve piston 4, which by a Preload spring 5 in a first, the two pressure connections 2, 3rd separating position is biased.
  • the valve piston 4 is for this with a provided as a cone section valve plate 6, the pressed on a valve seat 7 via the biasing spring 5 becomes.
  • the valve piston 4 is at an axial distance to the cone section closing the first pressure connection 2 6 a seal, in this case in the form of an annular collar 8 provided that the biasing spring 5 relative to the seals two pressure connections 2, 3.
  • a the bias spring 5 receiving and thus pressure-free spring chamber 9 is there via an additional leak oil line 10 with a separate one Tank connection L connected.
  • the servo valve 1 is interposed in a return channel 11 formed in the brake / check valve, which connects a consumer-side valve connection V with a further valve connection A, which in turn can be optionally connected via an external directional valve, not shown a pump or a tank can be connected.
  • the servo valve 1 is designed for actuation by means of a control pressure which can be applied to the brake / shut-off valve via an external control connection P st .
  • a servo valve 1 in particular bypassing or bridging its pressure connection 2, is also formed, in which, according to the invention, a combined, pilot-controlled pressure / feed valve 13 is interposed, as described, for example, by the applicant under the designation "MHDBN 22K "is distributed and therefore belongs to the state of the art.
  • a measuring port M is also provided for a pressure sensor, which is connected directly to the port V or can be used as a connection for a compensating line in double cylinders.
  • the measuring connection M is connected via a first channel 14 to a consumer chamber 15 formed in a valve housing, from which a bore 16 leads to the consumer connection V according to FIG. 2.
  • the consumer chamber 15 or the bore 16 is penetrated essentially at right angles by a further valve housing bore for receiving the servo valve 1, which runs through the entire valve housing and is thereby divided into two parts by the consumer chamber 15.
  • a sleeve 17 is fitted in a fluid-tight manner in the right-hand part of the bore according to FIG. As can be seen from FIG.
  • this sleeve 17 is pressed against a shoulder in the valve housing bore by means of a bush 18 screwed into the valve housing with an inner bore diameter larger than the sleeve 17, as a result of which the sleeve 17 is axially fixed.
  • the bushing 18 forms the spring chamber 9 mentioned at the beginning, which is closed to the outside by an end wall of the bushing 18.
  • the control pressure connection P st is designed for a control pressure line, via which an actuating piston 19, which is mounted in the bushing 18, can be actuated via the control pressure.
  • FIG. 2 In the left part of the bore according to FIG. 2 there is also one Sleeve 20 with an inner diameter equal to the right sleeve 17 screwed in and countered by a hollow screw 21, the left-hand bore part by means of an as Adjusting screw trained, screwed into the hollow screw Blind plug (not shown) opposite the Environment is closed.
  • the valve piston 4 is through the Consumer chamber 15 into the left-hand sleeve 20 extended and is there within the sleeve 20 via a Valve piston 4 formed collar 22 slide-bearing, wherein a cavity 23 between the sleeve 20 Blind plug and the left-hand collar 22 forms.
  • valve piston 4 furthermore also in the right sleeve 17 according to FIG. 2 plain bearing, here the support points on the one hand by the ring collar 8 serving as a seal and a further, ring collar 25 directly adjacent to the conical section 6 of the valve piston 4 are formed.
  • This second, on the cone section 6 arranged collar 25 has on it Shell surface axial notches 26 which in the direction of Sealing ring collar 8 are open and as so-called fine control grooves serve.
  • the position the drain hole 29 is selected such that in each position of the valve piston 4 a separation of the drain hole 29 from the return duct leading to valve connection A. 11 through the sealing collar 8 and at the same time one permanent connection of the drain hole 29 to the spring chamber 9 guaranteed is.
  • valve piston extension 30 extended into the spring space 9 of the sleeve 18, the one on the right outer end of the extension into an annular collar Spring seat 31 is radially expanded, on which the Valve piston extension 30 arranged bias spring 5 on her supports one end.
  • the other end of the spring 5 is on supported the right end of the sleeve 17 itself, whereby the valve piston 4 with respect to the sleeve 17 according to FIG. 2 biased to the right and thus the cone section 6 below Support of the one in the left-hand cavity 23 Pressure is pressed on the valve seat 7.
  • the valve piston 4 and the extension 30 is provided with an inner axial through hole 32 provided which the left-hand side Cavity 23 connects to the spring chamber 9.
  • this through hole 32 is at the left end portion of the valve piston extension 30, i.e. between valve piston 4 and extension 30 a pilot valve 33 in seat design with a closing element 34 arranged, supported by a spring by the pressure in the left-hand cavity 23, on an inner Valve seat is pressed and by means of the adjusting piston 19th via two in the through bore 32 of the valve piston extension 30 additionally stored spacer pins 35 in an open position is feasible.
  • the valve seat of the pilot valve 33 is attached via a valve piston extension 30 Radial bore connected to the spring chamber 9.
  • valve housing Location hole there is another one in FIG. 2 in the valve housing Location hole, not shown, for the commercially available combined Pressure / feed valve 13 formed, which from For the sake of clarity, only as a symbol is shown.
  • the pilot operated pressure / feed valve 13 accordingly forms a to the consumer chamber 15 opening check valve, which on a Control side held in the closed position by a preload spring and through one introduced via valve port A. Pump pressure can be brought into the open position.
  • a lifting cylinder for lifting a load When pressure is supplied to a consumer, not shown for example, a lifting cylinder for lifting a load Appropriate actuation of an upstream of the brake / check valve conventional directional valve (not shown) flows Hydraulic fluid through pressure port A, opens the check valve of the combined pressure / feed valve 13 against the force of the biasing spring and passes through the pressure supply channel 12 and the inner consumer chamber 15 of the brake / check valve to the consumer connection V, at which one is not shown consumer line is connected.
  • the pump pressure simply reduced, which causes the check valve of the combined pressure feed valve 13 in the closed position emotional.
  • the connection channel 24 acting as a throttle the consumer pressure built from de consumer chamber 15
  • pressurizing area on the cone section 6 is substantially identical to the left-hand collar 22, so that each one on it mutually acting pressure forces from the consumer chamber 15 almost cancel.
  • the actuating piston moves further to the left, it lays the right-hand end face of the valve piston 4 or extension 30 and moves the valve piston 4 against the now acting biasing force of the biasing spring 5.
  • This causes the cone section 6 of its Valve seat 7 lifted off, so that in the consumer and thus in the pressure prevailing in the consumer chamber 15 via the return duct 11 to the valve connection A and from there to the not shown Tank can be relaxed.
  • the maximum displacement of the valve piston 4 in the left-hand direction limits the blind plug designed as an adjusting screw becomes. Furthermore, the dosing of the flowing can Determine or adjust hydraulic fluids exactly because the force to move the valve piston 4 as described above Independently of consumer pressure, only proportional to the spring force of the biasing spring 9. This dosing accuracy is additionally determined by the arrangement of the Fine control grooves 26 improved, the greater displacement tolerance allow.
  • the formation of the cavity 23 on the 2 left end of the valve piston 4 (on the valve piston side opposite the spring chamber) furthermore the guarantee of the functional maintenance of the Brake / check valve also in the event that the bias spring 5 of the valve piston 4 is broken.
  • pilot seat valve 33 in this embodiment according to the invention at the left end portion of the valve piston 4 within the Consumer chamber 15, wherein for actuating valve 33 through the adjusting piston 18 a push rod 36 in the inner Through bore 32 of the valve piston 4 retracted and according Fig. 3 is spring biased to the right.
  • the pilot seat valve 33 here consists of the biased on a valve seat Closing element 34, which by means of the push rod 36 an interposed spacer pin 37 in the opening direction is movable.
  • the closing element 34 is stored in a outer sleeve 38 forming the valve seat, which in turn axially displaceably mounted in the valve piston 4 and immediately can be operated by the push rod 36.
  • the sleeve 38 has an outer shoulder, which with a corresponding Heel in the through bore 32 of the valve piston 4 for an axial displacement limitation in the spring preload direction comes into engagement.
  • the sleeve 38 by a bias spring of the closing element 34 over the valve seat against the shoulder in the through hole 32 pressed and can by an axial displacement the push rod 36 are lifted off.
  • the valve piston 4 is in the area of the outer sleeve 38 provided with radial bores 39 which connect between the consumer chamber 15 and the inner through hole 32 of the valve piston 4.
  • the closing element 34 of the pilot seat valve 33 in the closed position held in the connection between the left cavity 23 and the spring chamber 9 is interrupted.
  • Closing element 34 acting bias also becomes the outer Sleeve 38 on the paragraph in the inner through hole 32 pressed, the radial bores 39 from the sleeve wall be closed.
  • this annulus 40 lead a number of obliquely outwards extending holes 41, which in the inner through hole 32 of the valve piston 4 open and in closed State of the cone section 6 or the pilot seat valve 33 from the outer sleeve 38 of the pilot seat valve 33 as well be closed.
  • This outer sleeve 38 has on its outer surface a recess 42 of a width according to the axial distance between the radial and oblique holes 39, 41 of the valve piston 4, but with the screwing 42 is arranged such that in the above closed position of the pilot seat valve 33 between the radial bores 39 and the oblique bores 41 there is no fluid connection.
  • a control pressure is applied to the actuating piston 18 via the control pressure connection P st at a regulated pressure voltage, whereby the push rod 36 within the valve piston 4 according to FIG. 3 is shifted to the left.
  • the closing element 34 of the pilot control valve 33 is first lifted from its valve seat, as a result of which the hydraulic pressure in the left-hand cavity 23 is released via the valve seat, the inner through bore 32 of the valve piston 4 and the spring chamber 9 into the leakage oil line 10.
  • the relevant pressure application area of the cone section 6 pointing towards the consumer chamber 15 is also larger than the corresponding contact area of the left-hand annular collar 22 formed on the valve piston 4, so that a resulting residual pressure force is dependent on the consumer pressure the cone section 6 acts in the closing direction.
  • valve piston 4 no internal pilot seat valve, whereas the left-hand one Cavity 23 through the through hole 32 in the valve piston 4 permanently connected to the spring chamber on the right 9 Has.
  • the reason for this is that the left side Cavity 23 is kept depressurized, the contact pressure between the cone section 6 and the valve seat 7 exclusively from the spring force of the biasing spring 5 of the Valve piston 4 determined.
  • valve piston 4 points according to its Fig. 4 left end portion with a first collar 43 an outer spiral groove 44 in one in the valve housing fixed sleeve 45 is slidably mounted.
  • This sleeve 45 is at its end facing away from the consumer chamber 15 closed by a hollow truncated cone 46, which by a sleeve 47 screwed into the valve housing in a fluid-tight manner is and which is penetrated by the valve piston 4.
  • valve piston 4 If the valve piston 4 is used to open the valve seat 7 4 now moved to the left, the left side bumps first ring collar 43 already after a small displacement against the truncated cone 46 and lifts it off the left-hand sleeve 45. This can cause hydraulic fluid through the annular groove 44 on the lateral surface of the first ring collar 43 flow directly into the sleeve 47 surrounding the truncated cone 46, which increases the leakage slightly. Emotional meanwhile the valve piston 4 according to FIG the truncated cone 46 gradually comes to the right in the closed position again in contact with the left-hand sleeve 45 to complete this and thus reduce leakage losses again.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)

Claims (14)

  1. Clapet d'arrêt automatique pour tuyauterie, destiné à la protection d'un utilisateur hydraulique, comprenant une servo-valve (1), qui possède au moins deux raccords de travail internes (2, 3), dont un premier (2) est ouvert en direction d'un raccord d'utilisateur (V), ainsi qu'un piston de valve (4), lequel est précontraint par un ressort de précontrainte (5) dans une position de fermeture qui isole les raccords de travail (2, 3) et qui repose dans cette position de fermeture par un opercule de valve (6) sur un siège de valve (7), et susceptible d'être sollicité en outre par la pression de l'utilisateur dans la direction de la position de fermeture, ladite pression d'utilisateur apparaissant dans une chambre de commande (23), laquelle est raccordée sur le plan hydraulique au premier raccord de travail (2) via un étranglement (24), et susceptible d'être déchargée de la pression via un canal (32) qui mène axialement à travers le piston de valve (4) et via une valve pilote (33) réalisée sous forme de valve à siège, et dans lequel le piston de valve (4) est susceptible d'être amené en engagement, pour son déplacement axial en direction d'ouverture, avec un piston de positionnement (19), lequel ouvre la valve pilote (33) agencée dans le piston de valve (4) un instant avant venue en engagement avec le piston de valve (4) afin de décharger la chambre de commande (23) de la pression d'utilisateur,
    caractérisé en ce que le ressort de précontrainte (5) est logé dans une chambre à ressort (9) située à l'opposé de la chambre de commande (23) par rapport au piston de valve (4), ladite chambre à ressort étant sans pression,
    en ce que sur le piston de valve (4) et à distance axiale de l'opercule de valve (6) est réalisée une collerette annulaire (8), au moyen de laquelle est formée une chambre annulaire située entre la collerette et l'opercule de valve et ouverte en direction du deuxième raccord de travail (3), et laquelle (8) étanche la chambre à ressort (9) vis-à-vis du deuxième raccord de travail (3) et fait office de portée coulissante pour le piston de valve (4),
    et en ce que la chambre de commande (23) est susceptible d'être déchargée de la pression vers la chambre à ressort (9).
  2. Clapet d'arrêt automatique pour tuyauterie selon la revendication 1, caractérisé en ce que le siège de valve (7) est réalisé par une douille (17), laquelle est mise en place dans un perçage de réception percé dans le boítier du clapet d'arrêt automatique.
  3. Clapet d'arrêt automatique pour tuyauterie selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu, entre l'opercule de valve (6) et la portée coulissante, une autre collerette annulaire (25) immédiatement adjacente à l'opercule de valve (6), qui fait également office de guidage coulissant pour le piston de valve (4).
  4. Clapet d'arrêt automatique pour tuyauterie selon l'une des revendications précédentes, caractérisé en ce que la chambre à ressort (9) est en permanence en communication avec un raccord de fuite (L) du clapet d'arrêt automatique.
  5. Clapet d'arrêt automatique pour tuyauterie selon l'une des revendications précédentes, caractérisé par un raccord de valve (A) susceptible d'être relié au choix avec une pompe ou un réservoir, ledit raccord de valve étant relié au raccord d'utilisateur (V) via un canal d'admission de pression (12) avec interposition d'une valve de pression/admission (13), avec un canal de retour (11) branché en parallèle et dans lequel est interposée la servo-valve (1).
  6. Clapet d'arrêt automatique pour tuyauterie selon l'une ou l'autre des revendications 1 et 2, caractérisé en ce que le piston de valve (4) est pourvu, sur un tronçon terminal opposé au clapet de valve (6), d'une collerette annulaire additionnelle (22), dont le diamètre extérieur correspond sensiblement à celui de l'opercule de valve (6), et qui est montée en coulissement dans le perçage de réception du boítier du clapet d'arrêt automatique.
  7. Clapet d'arrêt automatique pour tuyauterie selon la revendication 6, caractérisé par une douille coulissante (20), agencée entre la collerette annulaire additionnelle (22) et le boítier, et fixée dans le perçage de réception dans le boítier de valve.
  8. Clapet d'arrêt automatique pour tuyauterie selon l'une ou l'autre des revendications 6 et 7, caractérisé en ce que le piston de valve (4) traverse une chambre d'utilisateur (15) qui mène une pression d'utilisateur, à l'intérieur du clapet d'arrêt automatique, et en ce qu'un emplacement d'entrée à travers l'opercule de valve (6) et un emplacement de sortie à travers la collerette annulaire additionnelle (22) sont susceptibles d'être obturés.
  9. Clapet d'arrêt automatique pour tuyauterie selon la revendication 8, caractérisé en ce que, à l'intérieur du perçage de réception et sur un côté du piston de valve (4) opposé au ressort de précontrainte (5), est réalisée une cavité, qui est séparée de la chambre d'utilisateur (15) par la collerette annulaire additionnelle (22) et qui forme la chambre de commande (23).
  10. Clapet d'arrêt automatique pour tuyauterie selon la revendication 9, caractérisé en ce que l'étranglement est réalisé par la collerette additionnelle annulaire additionnelle (22), et en ce qu'il est relié directement avec la chambre d'utilisateur (15) dans laquelle débouche le premier raccord de travail (2).
  11. Clapet d'arrêt automatique pour tuyauterie selon l'une ou l'autre des revendications 9 et 10, caractérisé en ce que la cavité (23) est reliée à une conduite de fuite (10) par l'intermédiaire du canal (32) dans lequel est agencée la valve pilote (33).
  12. Clapet d'arrêt automatique pour tuyauterie selon la revendication 11, caractérisé en ce que l'opercule de valve (6) est réalisé par un tronc de cône, tel que la collerette annulaire (25) de forme cylindrique se raccorde à sa face frontale de petit diamètre, et en ce que le siège de valve (7) va en s'élargissant radialement quant à son diamètre par rapport à la collerette annulaire (25), de sorte que se forme la chambre annulaire fermée (40) entre l'opercule de valve (6), le siège de valve (7), et la collerette annulaire (25) dans l'état fermé du raccord de pression (2).
  13. Clapet d'arrêt automatique pour tuyauterie selon l'une ou l'autre des revendications 11 et 12, caractérisé en ce que la valve pilote (33) comporte un siège de valve susceptible d'être fermé par un élément de fermeture (34), lequel est réalisé dans une douille (38) susceptible de se déplacer axialement dans le canal (32).
  14. Clapet d'arrêt automatique pour tuyauterie selon la revendication 13, caractérisé en ce que la douille (38) susceptible de se déplacer est actionnée par le piston de positionnement (18) au moyen d'une barre de poussée (36), et en ce qu'elle ferme, un instant après la fermeture du siège de valve (7) par l'opercule de valve (6), un canal de liaison (39, 41) entre la chambre utilisateur (15) et la chambre annulaire (40).
EP96902996A 1995-03-23 1996-02-23 Clapet d'arret automatique Expired - Lifetime EP0815361B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19510586 1995-03-23
DE1995110586 DE19510586A1 (de) 1995-03-23 1995-03-23 Rohrbruchsicherungsventil
PCT/EP1996/000755 WO1996029517A1 (fr) 1995-03-23 1996-02-23 Clapet d'arret automatique
US08/935,736 US6027095A (en) 1995-03-23 1997-09-23 Pipe breakage safety valve

Publications (2)

Publication Number Publication Date
EP0815361A1 EP0815361A1 (fr) 1998-01-07
EP0815361B1 true EP0815361B1 (fr) 2000-08-09

Family

ID=26013642

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96902996A Expired - Lifetime EP0815361B1 (fr) 1995-03-23 1996-02-23 Clapet d'arret automatique

Country Status (5)

Country Link
US (1) US6027095A (fr)
EP (1) EP0815361B1 (fr)
JP (1) JPH11505592A (fr)
DE (1) DE19510586A1 (fr)
WO (1) WO1996029517A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19642567C1 (de) * 1996-10-15 1997-08-21 Brueninghaus Hydromatik Gmbh Kombiniertes Hydraulikventil mit einer Schalt- und einer Druckminderfunktion
DE102009038780B4 (de) * 2009-08-25 2011-12-01 Airbus Operations Gmbh Vorrichtung zur Rohrbruchsicherung
CN102889261B (zh) * 2012-10-15 2015-02-04 常德中联重科液压有限公司 平衡阀、液压缸伸缩控制回路以及液压设备
DE102015225927A1 (de) * 2015-12-18 2017-06-22 Robert Bosch Gmbh Ventilkolben und Schieberventil mit einem Ventilkolben

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2187086A5 (fr) * 1972-05-31 1974-01-11 Poclain Sa
DE2536106A1 (de) * 1975-08-13 1977-02-24 Hubert Odenthal Lastabsicherungsventil
US4187870A (en) * 1977-05-06 1980-02-12 Baker International Corporation Valve actuator and pilot assembly therefor
GB2091383B (en) * 1979-11-09 1985-07-24 Bennes Marrel Braking valve
DE3239930A1 (de) * 1982-10-28 1984-05-10 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulisch steuerbares sperrventil, insbesondere fuer die rohrbruchsicherung
DE3319810C1 (de) * 1983-06-01 1984-10-25 Montan-Hydraulik GmbH, 4755 Holzwickede Einrichtung zum Steuern von Hydroantrieben
EP0197467B1 (fr) * 1985-04-11 1992-01-29 Beringer-Hydraulik AG Soupape de descente freinée et maintenu sans fuites.
DE4032420C2 (de) * 1990-10-12 1994-04-14 Wessel Hydraulik Hydraulisches Sicherheitsventil
US5381822A (en) * 1993-11-26 1995-01-17 Dana Corporation Relief valve with hydraulic fuse

Also Published As

Publication number Publication date
WO1996029517A1 (fr) 1996-09-26
DE19510586A1 (de) 1996-09-26
US6027095A (en) 2000-02-22
EP0815361A1 (fr) 1998-01-07
JPH11505592A (ja) 1999-05-21

Similar Documents

Publication Publication Date Title
DE3413866A1 (de) Hydrostatisches antriebssystem
EP0279315B1 (fr) Dispositif de commande hydraulique
EP3101283B1 (fr) Cylindre de verrouillage a double action et son procede de fonctionnement
EP2239470A2 (fr) Vérin de verrouillage et procédé de verrouillage et de déverrouillage d'un vérin de verrouillage
DE4032078C2 (de) Steuervorrichtung für einen hydraulischen Arbeitszylinder
EP0815361B1 (fr) Clapet d'arret automatique
EP2241763B1 (fr) Dispositif de commande hydraulique et balance de pression pour ledit dispositif
EP0505349B2 (fr) Vérin hydraulique
DE3225132A1 (de) Hydraulisches sicherheitsbremsventil
DE3011196C2 (fr)
WO2003102427A1 (fr) Cylindre hydraulique dote d'un ensemble soupapes
WO1998021486A1 (fr) Systeme de valve anti-retour
EP2241764B1 (fr) Soupape à siège dotée d'une fonction de soupape de dérivation et de compensateur de pression
EP0491155B1 (fr) Distributeur pour commande d'un moteur hydraulique
EP0967028B1 (fr) Presse hydraulique
DE3039002A1 (de) Druckregelventil
DE4304117C2 (de) Druckminderventil in Kolbenschieber-Bauweise
EP1204823B1 (fr) Dispositif de surveillance electrohydraulique d'un cylindre hydraulique a double effet
DE19510588B4 (de) Ventilsitzkonstruktion
DE102012218450A1 (de) Ventilvorrichtung, insbesondere zur Ansteuerung eines Druckabschneidventils
AT524662B1 (de) Längenverstellbare Pleuelstange mit Schraubbund
DE102005052692B3 (de) Elektrohydraulische Überwachungseinrichtung
DE102008019743A1 (de) Druckreduzier-Sitzventil und Spannschaltung
DE19536725A1 (de) Vorgesteuertes Druckabschaltventil
DE19605173C2 (de) Hydraulische Sicherheitsventilanordnung

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

17P Request for examination filed

Effective date: 19970922

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17Q First examination report despatched

Effective date: 19981112

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MANNESMANN REXROTH AG

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REF Corresponds to:

Ref document number: 59605719

Country of ref document: DE

Date of ref document: 20000914

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

Effective date: 20000824

ITF It: translation for a ep patent filed

Owner name: RACHELI & C. S.R.L.

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

Free format text: ORIGINAL CODE: 0009261

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: FR

Payment date: 20050216

Year of fee payment: 10

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

Ref country code: SE

Payment date: 20050221

Year of fee payment: 10

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

Ref country code: SE

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

Effective date: 20060224

EUG Se: european patent has lapsed
REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20061031

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: 20060228

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

Ref country code: IT

Payment date: 20150225

Year of fee payment: 20

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

Ref country code: GB

Payment date: 20150223

Year of fee payment: 20

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

Ref country code: DE

Payment date: 20150424

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59605719

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20160222

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 EXPIRATION OF PROTECTION

Effective date: 20160222