EP0328933B1 - Ferme-porte avec un dispositif d'arrêt hydraulique - Google Patents

Ferme-porte avec un dispositif d'arrêt hydraulique Download PDF

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Publication number
EP0328933B1
EP0328933B1 EP89101666A EP89101666A EP0328933B1 EP 0328933 B1 EP0328933 B1 EP 0328933B1 EP 89101666 A EP89101666 A EP 89101666A EP 89101666 A EP89101666 A EP 89101666A EP 0328933 B1 EP0328933 B1 EP 0328933B1
Authority
EP
European Patent Office
Prior art keywords
door
piston
door closer
overflow valve
valve
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
EP89101666A
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German (de)
English (en)
Other versions
EP0328933A1 (fr
Inventor
Peter Kubelka
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.)
Gretsch Unitas GmbH Baubeschlaege
Original Assignee
Gretsch Unitas GmbH Baubeschlaege
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Publication date
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Publication of EP0328933A1 publication Critical patent/EP0328933A1/fr
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Publication of EP0328933B1 publication Critical patent/EP0328933B1/fr
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Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
    • E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
    • E05F3/223—Hydraulic power-locks, e.g. with electrically operated hydraulic valves
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
    • E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
    • E05F3/12—Special devices controlling the circulation of the liquid, e.g. valve arrangement
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/10—Application of doors, windows, wings or fittings thereof for buildings or parts thereof
    • E05Y2900/13—Type of wing
    • E05Y2900/132—Doors

Definitions

  • the invention relates to a door closer with a hydraulic locking device for the at least partially opened door according to the preamble of claim 1. If a door equipped with such a door closer is opened by a predetermined angle, for example at 80 ° to 90 °, it closes at Let go automatically. If, however, the opening angle mentioned, for example, is exceeded, the door remains open when the closure element of the overflow valve is in Closed position is maintained. If you release the closing element of the overflow valve, the piston load spring also causes the wide-open door to close slowly.
  • a predetermined angle for example at 80 ° to 90 °
  • a door closer with a hydraulic locking device is known, which can be used in any desired manner due to the use of several throttle valves as well as auxiliary and pressure relief valves.
  • the sash By closing the second throttle valve completely, the sash can be locked in any open position over approx. 80 ° to 90 °.
  • a hand force acting on it and acting in the closing direction is necessary.
  • the wing is reset in a known manner with the aid of a return spring.
  • This door closer has the disadvantage that a hand force is necessary to close the door leaf and only slowed movements are possible.
  • a door closing and holding device which contains a cylinder with a piston which responds to the pivoting movement of a door leaf in a door frame.
  • a spring is tensioned and presses on a piston to close the door.
  • Various channels opening into the cylinders are provided with valves which control the speed (s) of the closing and opening movement of the door leaf.
  • One of the valves is electrically operated and allows the door leaf to be closed from an open position.
  • the object of the invention is to develop a door closer of the type mentioned in such a way that it automatically releases the piston which is held hydraulically when the door is open in the event of smoke or the like and thereby closes the door, but on the other hand the door is braked from this open position and can be quickly closed by hand and opened again.
  • This door closer works in a known and preferred manner with a smoke detector. Instead of the smoke detector, it is of course also possible to use another monitoring device, which should also release the piston when the event to be monitored occurs.
  • the invention proposes that the door closer is designed according to the preamble of claim 1 in accordance with the characterizing part of this claim.
  • the locking member of this door closer can be operated by a controllable assistant.
  • This assistant preferably holds which is controllable, for example, by the smoke detector mentioned, the closure member of the overflow valve by means of the blocking member in its closed position. With this door closer there is no blocking of the overflow valve closing element as soon as the assistant is reversed due to a corresponding control command, for example a smoke detector, or is omitted. If the other requirements, in particular a corresponding pressure difference in the hydraulic system of the door closer, are now present, the overflow valve can be opened hydraulically.
  • the inflow side of the overflow valve is only released from an opening angle of the door of, for example, approximately 80 ° to 90 °. It is previously closed indirectly by the piston, in particular by an element of a hydraulic valve unit which is displaceably mounted on the piston.
  • this door closer works quite normally, ie closes the released door, the medium flowing back from the rear cylinder space into the front cylinder space via at least one throttle channel with at least one throttle valve inserted therein. If the open door is locked and the closing element of the overflow valve is blocked by the blocking element, the door can still be closed by hand like a normal door without a door closer and subsequently opened and closed as desired. According to the requirements, no hydraulic medium flows through the throttle channels, rather the piston remains with the associated, in particular one-piece, piston-side part of the piston rod in the sliding position reached when the locked door is open. As usual, the return spring of the door closer is tensioned.
  • the drive-side section can be displaced relative to the stationary piston-side section. Because the drive-side section of the piston rod is coupled to the door, the turning of the latter only has a relative displacement of the drive-side piston rod section with respect to the piston side.
  • the door closer closes the door from any open position because the force of the load spring of the piston can then have an effect and the overflow valve on Opening is not prevented by the hydraulic overpressure.
  • the closure member of the overflow valve can be prevented from moving into the open position by the blocking member which can be brought into its displacement area, one could also speak of a hydraulic mechanical locking device.
  • the locking member can be controlled by means of an auxiliary force, which can be an electrical or magnetic auxiliary force, for example. In this case, the term electro-hydraulic locking device could also be used will. The same applies accordingly when using another assistant.
  • a particularly preferred embodiment of the invention provides that the closure member of the overflow valve can be locked by means of a locking member that can be adjusted by an electromagnet.
  • the arrangement can, for example, be such that the electromagnet holds the locking member in the locking position as long as it is excited. If, for example, a smoke detector then interrupts the current to the electromagnet, the magnet that has now become de-energized releases the blocking element and then in turn allows the closing element of the overflow valve to open when the pressure in the rear cylinder chamber is large enough to close the loading spring of the overflow valve closing element overcome.
  • the blocking member can also be held in its blocking position against the resistance of a return spring, so that when the control force is switched, that is to say, for example when the electromagnetic force is removed from its return spring, it is brought into a non-obstructing displacement position which prevents the overflow valve closure member from opening.
  • the arrangement mentioned can of course also work in exactly the opposite way.
  • a preferred variant of the invention is characterized in that the drive-side section of the piston rod is guided in a central bore of the piston-side section and that a thickened head. or the like.
  • the drive-side section engages behind a narrow point of the central bore, the thickened head or the like. Is located between the constriction and the piston of the piston rod and the part of the central bore receiving the thickened head is longer than the head height by approximately the displacement distance of the telescopic connection.
  • Other telescopic connections are of course also conceivable, in which, for example, the piston-side section engages with a shaft in a bore in the drive-side.
  • the door can be transferred from the closed position into a partially or fully open position, the opening taking place as far as possible without lost motion and that with the door open to the maximum and the piston-side section determined the lock side can be moved so far compared to the piston side that the door can take its closed position.
  • the lost motion distance must therefore correspond to the distance that the drive-side section must be able to cover up to the maximum opening of the door.
  • the thickened head is formed by a screw head, in particular an Allen screw which is screwed into the free end of the piston rod section on the drive side. Due to the use of this screw, one could also speak of a two-part drive-side section of the piston rod.
  • the screw is particularly important in terms of simplifying assembly. Your head must be arranged and dimensioned that he does not hinder the hydraulic flow, which can also take place through the aforementioned central bore in the piston-side section of the piston rod in any displacement position.
  • the constriction of the piston rod section is advantageously formed by an inner collar and this contributes to inexpensive manufacture of the piston section.
  • the piston 1 When opening the door, not shown, which is rotatably connected in a known manner to the rotary member 9 of the door closer, the piston 1 is moved in the cylinder 2 in the direction of arrow 3.
  • the cylinder 2 is located in the housing of the door closer or forms part of the same.
  • the rotary movement of the rotary member is preferably transmitted via an eccentric mechanism to the piston rod 4 and thus also to the piston 1 firmly connected to it.
  • the rotary member is assigned to the end of the piston rod remote from the piston.
  • the latter is concentrically surrounded by at least one strong return spring 5, the right end of which in the drawing is supported on the piston 1 and the left end of which is indirectly supported on a housing wall.
  • the return spring When the piston is moved in the direction of arrow 3, i.e. when the door is opened, the return spring is tensioned.
  • the front cylinder space 6 receiving the piston rod and the spring like the rear cylinder space 7, is filled with a suitable hydraulic fluid.
  • a cylinder transverse bore 10 Via a cylinder transverse bore 10, it enters a longitudinal channel 11 and from there reaches a first adjustable throttle valve 12. A further short transverse bore 13 creates the connection to the front cylinder chamber 6. The channels 10, 11 and 13 together form a first channel 14 of the door closer.
  • a second channel 16 opens into the bore 15 of the first throttle valve 12. It consists of the short connecting piece 17 between the first throttle valve 12 and a second throttle valve 18 and a transverse bore 19 which runs parallel to the transverse bore 13 and also opens into the front cylinder chamber 6 .
  • the two throttle valves 12 and 18 are located on a housing or cylinder wall 20.
  • a third throttle valve 22 and a fourth throttle valve 23 are likewise offset in the longitudinal direction on an opposite wall 21 of the housing or of the cylinder.
  • the third throttle valve 22 includes a third Channel 24. It consists of the transverse channel 25, which opens approximately opposite from the transverse channel 10 into the rear cylinder chamber 7 and the longitudinal channel 26 and another transverse channel 27 opening into the front cylinder chamber 6.
  • the piston 1 has a two-part piston ring 28.
  • the transverse channel 27 is arranged so that it is in the starting position of the piston (FIG. 2) is released from the piston ring 28.
  • the play between the piston and the cylinder wall 29 is large enough to allow the medium to enter the transverse bore 27 from the front cylinder space 6 as soon as its mouth in the cylinder interior is at least partially released by the piston ring.
  • the fourth channel 37 consists of the transverse bore 30 opening into the front cylinder chamber, the adjoining longitudinal bore 31 and a further transverse bore 32, 33, which leads to an overflow valve 34 designed as a first pressure relief valve and an annular groove 35 connected between its parts 32 and 33 is.
  • the transverse bore 33 also forms the outlet bore of the first pressure relief valve or overflow valve 34. Its inlet bore is denoted by 36 and it opens into the rear cylinder chamber 7. However, it is not released in the starting position of the piston 1, as will be explained below.
  • the inlet 36 of the overflow valve 34 is closed by a spring-loaded (38) closure member 39 of an auxiliary valve 40 attached to the piston 1.
  • Both the closure member 39 and the housing 41 of the auxiliary valve 40 have a cup-shaped shape.
  • the pot shell of the housing encompasses that of the closure member and the Pot bases are separated from each other.
  • the loading spring 38 for the closure member 39 It is supported on the two pot bases.
  • the pot bottom of the housing 41 has a central hole 42.
  • a sealing ring 43 Outside on the pot bottom of the closure member 39 there is a sealing ring 43, in particular an O-ring, which in the starting position and, as will be explained later, also has part of the door opening movement, the inlet bore 36 of the Overflow valve 34 keeps closed.
  • the closure member 39 is slidably mounted in the housing 41 in the longitudinal direction of the piston axis.
  • a second pressure relief valve 47 is installed in the piston 1 and is closed when the door is closed.
  • Its locking member 48 has, for example, the shape of a bolt with an outer collar 49 at its end assigned to the rear cylinder space 7. Both the bolt and the collar 49 can be designed in a star shape on the outer circumference in a manner not shown on the one hand to achieve good guidance in the piston 1 and on the other hand to ensure that the medium flows past.
  • the housing of this second pressure relief valve is formed by the piston 1. Accordingly, there is also the annular valve seat surface 50.
  • the loading spring 51 holding the closure member in the closed position can be centered by a tubular extension and is supported with one end on the outside of the closure member and with its other end on a plate in the housing 41 of the auxiliary valve 40 from.
  • the housing 48 of the second pressure relief valve 47 also forms a housing of a third, oppositely opening pressure relief valve 53 which is closed when the door is closed.
  • Its closure member 54 preferably consists of a ball, and its load spring 55, like the other valve springs, is a helical compression spring.
  • the closure member 56 of the overflow valve 34 has a cup-shaped shape.
  • a loading spring 57 normally keeps the valve closed.
  • the closure member 56 does not act directly with the housing valve seat at the right end of the inlet channel 36 in FIG. 2 together, rather a laterally well-guided ball 62 is interposed.
  • a particularly central bore 63 is made on the bottom of the closure member 56.
  • the closure members 56, 48, 54, 39 of the overflow valve and the second and third pressure relief valves 34, 47, 53 and the auxiliary valve 40 and thus also these valves themselves are arranged concentrically with the geometric axis of the cylinder or the piston 1. This makes production particularly easy.
  • the separately manufactured bottom 44 At the end of the cylinder facing away from the rotary member there is the separately manufactured bottom 44 mentioned. It receives the overflow valve 34 and its transverse bore 33. In addition, an outer groove forms the aforementioned ring groove 35. On each side of the latter there is an O-ring 58 and 59, respectively. The bottom 44 is held on the outside by a spring ring 60 or the like. The separate production of this cylinder bottom has the advantage that it can be easily exchanged for another.
  • the door valves are located on the piston. They are arranged centrally to its axis, the closure members 39 and 54 of the auxiliary valve 40 and the third pressure relief valve 53 against the rotary member and those 56 and 48 of the overflow and the second pressure relief valve 34 and 47 are directed in the opposite direction.
  • the axes of the valve bodies of the throttle valves 12, 18, 22 and 23 run perpendicular to the floor in the position of use of the door closer, and their actuating ends. (eg 61) are therefore easily accessible from above.
  • the housing or the cylinder for the piston 1 is located in an outer housing 64, for example a floor box, which can be closed by means of a cover, not shown, so that, in particular, the throttle valves are not accessible to unauthorized persons. It remains to be added that the second pressure relief valve 47 opens at a higher pressure than the overflow valve 34.
  • An electromagnet 65 is installed in the cylinder base 44, in particular concentrically to the overflow valve 34. It receives a spring-loaded locking member 66 for the closure member 56 of the overflow valve 34.
  • the loading spring 57 of the closure member 56 is also a loading spring for the locking member 66.
  • the latter has an essentially sleeve-like shape and it is in direct extension from the pot wall of the cup-shaped locking member 56, with its free edge facing the locking member, both of which are approximately the same Have outside and inside diameters.
  • the locking member-side end of the load spring 56 of the relief valve 34 and the locking member 66 abuts a screw member 67 which can be screwed into a thread 68 of the locking member 66.
  • a screw member 67 which can be screwed into a thread 68 of the locking member 66.
  • it is sealed against a cylindrical inner wall of the locking member 66 by means of a sealing ring 69, in particular an O-ring.
  • the screw member has an extension 70 for an actuating tool, for example a screwdriver slot, at its outwardly projecting end.
  • the electromagnet is designed as a ring magnet.
  • the piston rod consists of two telescopically collapsible sections.
  • the piston-side section 71 has the aforementioned T-shaped channel 8, the central bore in FIG. 1 being extended to the left. More precisely, it is a continuous central bore 74 with a constriction 72.
  • the part 73 of the central bore 74 located on the left of the constriction in FIG. 1 receives the end of the drive-side section 75 of the piston rod 4.
  • a screw 76 with head 77 is screwed into a central bore at the free end of this section 75. The head is located to the right of the constriction 72 in the bore part 78 of the central bore 74.
  • the height of the head 77 and the length of the bore part 78 are determined so that the telescopic piston rod 4 can be shortened by an amount which corresponds at least approximately to the displacement distance, around which a one-piece piston rod with maximum opening of the door is moved. This is explained in more detail below.
  • this door closer is as follows, with two cases to be distinguished. In the first case, the throttle valve 18 is open. This means that the door is not hydraulically locked.
  • the rotary member of the door closer and the conversion mechanism for the rotary movement move the piston 1 in the direction of the arrow 3 (FIG. 1).
  • the outer ring of the two-part piston ring 28 slides first over the transverse bore 27 of the third throttle valve 22 and then over the transverse bore 13 of the first throttle valve 12.
  • the piston movement ends before the piston ring 28 cross-bores 19 and 30 of the second throttle valve 18 and the fourth Throttle valve 23 reached.
  • the second throttle valve 18 with its transverse bore 19 need not necessarily be present. If this throttle valve is missing, the freewheeling function in such a door closer always occurs when the electromagnet is switched on when the door is opened over approximately 80 ° to 90 °.
  • the medium can also flow into the front cylinder chamber 6 via the first channel. If the first throttle valve is opened further than the second, at least the majority of the back-flowing liquid will flow via the first throttle valve 12. When the first channel 14 or its transverse bore 13 is released, the door is in an open position of approximately 80 ° to 90 °.
  • the third channel or its transverse channel 27 is finally released, so that in the final phase of the door closing, the medium can also flow back into the front cylinder chamber 6 via the third channel and the third throttle valve. This causes an accelerated closing in the final phase and a strong decrease in the throttling effect, so that the door closer provides sufficient torque to actuate a lock latch on the door.
  • the second throttle valve 18 is closed. If, for example, the door is only opened by an angle of approximately 80 ° to 90 °, then the first channel or its transverse bore 13 is still released by the piston or piston ring 28, and the door therefore closes only after the actuation force ceases to exist the force of the return spring 5.
  • the opening angle of the door exceeds approximately 80 ° to 90 °, not only are the third and first channels closed, but also the second channel due to the closed second throttle valve. This means that no oil or the like can flow back through these channels from the rear into the front cylinder space 6.
  • the door remains hydraulically secured in an open position. Now there is still a hydraulic connection between the front and rear cylinder space via the fourth throttle valve 23 and the fourth channel 37.
  • the overflow valve 34 in the fourth channel 37.
  • the spring 5 can also close the wide open door. Locking the closure member 56 of the overflow valve 34 in its closed position with the aid of the locking member 66, the flow path through the fourth channel 37 is blocked by the overflow valve 34 and therefore the loading spring 5 cannot push the piston 1 back from the left to the right, because that Medium from the rear cylinder space 7 can not flow into the front cylinder space 6.
  • the door connected to this door closer would be now after the first opening over an angle of, for example, approximately 80 ° to 90 ° permanently blocked if the piston rod 4 would not be telescopically collapsible due to its two sections 71 and 75.
  • the closure member 56 of the overflow valve 34 can now be locked via a controllable auxiliary force, namely, for example, via the force of the electromagnet 65, by the locking member 66 being pressed onto the closure member 56 when the magnet is excited.
  • the electromagnet can be controlled, for example, by a smoke detector. The latter represents the appearance of smoke firmly, so he interrupts the current to the electromagnet 65. This consequently releases the blocking member 66 and it is shifted from the left to the right by the loading spring 57 in FIG. 2, ie removed from the closure member 56 of the overflow valve 34, the blocking thereof being released .
  • the force of the return spring 5 can now have an effect.
  • the auxiliary valve and the pressure relief valves work, as said, in the manner of check valves, ie they open when the prevailing pressure exerts a greater force on their closure member than the closing spring acting in the opposite direction.
  • the piston movement creates an overpressure in the front cylinder chamber, while when the door is closed, the rear cylinder chamber 7 comes under overpressure.
  • this overpressure acts on the closure member 56 of the overflow valve 34.
  • it also acts on the closure member 54 of the third pressure relief valve 53.
  • the hydraulic path goes via the radial slot or the like or the like and the opening of the tubular extension for centering the loading spring 51.
  • the loading spring 55 of the third pressure relief valve 53 and that 57 of the Overflow valve 34 are now coordinated so that the third pressure relief valve 53 opens at a significantly higher pressure than the overflow valve 34, which can be seen from the dimensioning of the springs in the drawing.
  • the pressure in the rear cylinder space 7 becomes high enough to also open the third pressure relief valve 53.
  • a sufficiently large return flow cross-section is available, which is the set one severe throttling mitigates or cancels.
  • the third pressure relief valve 53 can of course be effective from any piston position, in contrast to the overflow valve 34, which is only released from a position of the piston 1 that an opening angle of the door z. B. from 80 ° to 90 °.
  • the overflow valve 34 Because the pressure in the rear cylinder chamber 7 is sufficient to open the overflow valve 34, the latter has a stable open position. Its inlet bore 36 has a small cross section, so that the force when the valve is closed is relatively small. However, as soon as the ball 62 of the valve 34 has lifted off, the liquid also acts against the larger surface of the pot bottom of the closure member 56, as a result of which a lower force is sufficient to keep it open. After a counter pressure prevails in the fourth channel through the fourth throttle valve 23, the overflow valve 34 only closes again when the hydraulic fluid can flow out in another way. It is particularly advantageous that the closing speed of the door leaf can be set in the range above approximately 80 ° to 90 ° due to the use of the fourth throttle valve 23.
  • valves the flow channels and the transverse bores of the embodiment described in more detail may only be understood as examples.
  • some of the valves can be omitted without impairing the invention.
  • the control elements can also be at least partially replaced by other known ones.
  • the invention can also be used in a known type of overhead door closer.

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  • Closing And Opening Devices For Wings, And Checks For Wings (AREA)

Claims (12)

  1. Ferme-porte avec un dispositif d'arrêt hydraulique pour immobiliser la porte au moins partiellement ouverte, comprenant une chambre arrière (7) d'un cylindre, située côté porte d'un piston chargé par ressort et déplaçable en translation par la rotation de la porte, qui est reliée hydrauliquement par un canal d'écoulement (37), disposé fixe dans le boîtier, à une chambre avant (6) du cylindre, canal d'écoulement dans lequel sont situées une soupape d'étranglement (23) ainsi que, entre celle-ci et la chambre arrière du cylindre, une soupape de décharge (34), possédant un obturateur (56) chargé par ressort, qui peut être traversée par le fluide s'écoulant de la chambre arrière vers la chambre avant du cylindre et dont le côté arrivée du fluide (36) est découvert par le piston (1) à partir d'un angle d'ouverture prédéterminé de la porte, en particulier à partir d'environ 80° à 90°, caractérisé en ce que l'obturateur (56) de la soupape de décharge (34) peut être bloqué mécaniquement à sa position de fermeture au moyen d'un élément de verrouillage (66) manoeuvrable par une force auxiliaire pouvant être commandée, et la tige de piston (4) est constituée de deux tronçons (71 et 75) reliés télescopiquement, qui sont couplés dans la direction d'ouverture par coopération de profils quand la porte est fermée et qui peuvent être amenés à coulisser l'un vers l'autre, lorsque la porte est ouverte, d'une quantité correspondant au moins à la course de coulissement de la tige de piston (4) coordonnée à l'angle d'ouverture maximale de la porte.
  2. Ferme-porte selon la revendication 1, caractérisé en ce que l'obturateur (56) de la soupape de décharge (34) est blocable au moyen d'un élément de verrouillage (66) déplaçable par un électroaimant (65).
  3. Ferme-porte selon la revendication 2, caractérisé en ce que l'obturateur (56) de la soupape de décharge (34) est à peu près en forme de godet et l'élément de verrouillage (66) est essentiellement en forme de douille, le fond du godet étant coordonné au siège de la soupape de décharge (34), et l'obturateur (56) et l'élément de verrouillage (66) sont disposés dans le prolongement l'un de l'autre et présentent des extrémités dirigées l'une vers l'autre.
  4. Ferme-porte selon la revendication 3, caractérisé en ce qu'un ressort de charge commun (57), en particulier un ressort hélicoïdal de compression, est interposé entre l'obturateur (56) de la soupape de décharge (34) et l'élément de verrouillage (66), ressort qui est de préférence centré extérieurement par ces deux pièces.
  5. Ferme-porte selon la revendication 4, caractérisé en ce que l'extrémité côté élément de verrouillage du ressort de charge (56) de la soupape de décharge (34) est appliquée contre une pièce filetée (67) de l'élément de verrouillage (66).
  6. Ferme-porte selon la revendication 5, caractérisé en ce que la pièce filetée (67) est étanchée vis-à-vis d'une paroi intérieure cylindrique de l'élément de verrouillage (66) au moyen d'une bague d'étanchéité (69), en particulier d'un joint torique.
  7. Ferme-porte selon la revendication 6, caractérisé en ce que la pièce filetée (67) présente, sur son extrémité faisant saillie à l'extérieur ou dirigée vers l'extérieur, un prolongement (70) pour l'application d'un outil pour manoeuvrer cette pièce.
  8. Ferme-porte selon au moins une des revendications 2 à 7, caractérisé en ce que l'élément de verrouillage (66) est disposé de façon centrée dans un aimant annulaire (65) commandé électriquement.
  9. Ferme-porte selon au moins une des revendications 3 à 8, caractérisé en ce que le fond du godet formant l'obturateur (56) de la soupape de décharge (34) présente un orifice (63), en particulier un orifice centré, et est appliqué, lorsque la soupape de décharge (34) est fermée, contre une bille (62) pressée de façon étanche contre le siège de la soupape.
  10. Ferme-porte selon au moins l'une des revendications précédentes, caractérisé en ce que le tronçon (75) côté entraînement de la tige de piston (4) est guidé dans un alésage central (74) du tronçon (71) côté piston, et qu'une tête (77) plus épaisse ou analogue du tronçon (75) côté entraînement est accrochée derrière un rétrécissement (72) de l'alésage central (74), la tête plus épaisse ou analogue étant situé entre le rétrécissement (72) et le piston (1) relié à la tige de piston (4), la partie (78) de l'alésage central (74) recevant la tête plus épaisse étant plus longue que la hauteur de la tête d'une quantité correspondant à peu près à la course de coulissement de la liaison télescopique.
  11. Ferme-porte selon la revendication 10, caractérisé en ce que la tête (77) plus épaisse est formée par la tête d'une vis, en particulier d'une vis (76) à six pans creux, qui est vissée dans l'extrémité libre du tronçon (75) côté entraînement de la tige de piston.
  12. Ferme-porte selon la revendication 10 ou 11, caractérisé en ce que le rétrécissement (72) du tronçon (71) côté piston de la tige de piston est formé par un collet intérieur.
EP89101666A 1988-02-13 1989-02-01 Ferme-porte avec un dispositif d'arrêt hydraulique Expired - Lifetime EP0328933B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8801895U 1988-02-13
DE8801895U DE8801895U1 (de) 1988-02-13 1988-02-13 Türschließer mit hydraulischer Feststellvorrichtung

Publications (2)

Publication Number Publication Date
EP0328933A1 EP0328933A1 (fr) 1989-08-23
EP0328933B1 true EP0328933B1 (fr) 1993-06-23

Family

ID=6820664

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89101666A Expired - Lifetime EP0328933B1 (fr) 1988-02-13 1989-02-01 Ferme-porte avec un dispositif d'arrêt hydraulique

Country Status (2)

Country Link
EP (1) EP0328933B1 (fr)
DE (2) DE8801895U1 (fr)

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2611607A1 (de) * 1976-03-19 1977-09-29 Eaton Gmbh Feststellvorrichtung fuer tuer-, tor- o.dgl. fluegel
DE3331783A1 (de) * 1983-09-02 1985-03-21 Schlage Lock Co., San Francisco, Calif. Tuerschliess- und -haltevorrichtung
DE8526660U1 (de) * 1985-09-18 1987-01-22 Gretsch-Unitas GmbH Baubeschläge, 7257 Ditzingen Türschließer

Also Published As

Publication number Publication date
DE8801895U1 (de) 1988-03-24
DE58904758D1 (de) 1993-07-29
EP0328933A1 (fr) 1989-08-23

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