EP0328912B1 - Ferme-porte avec un dispositif d'arrêt hydraulique - Google Patents

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

Info

Publication number
EP0328912B1
EP0328912B1 EP89101324A EP89101324A EP0328912B1 EP 0328912 B1 EP0328912 B1 EP 0328912B1 EP 89101324 A EP89101324 A EP 89101324A EP 89101324 A EP89101324 A EP 89101324A EP 0328912 B1 EP0328912 B1 EP 0328912B1
Authority
EP
European Patent Office
Prior art keywords
housing
valve
door closer
door
spring
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
EP89101324A
Other languages
German (de)
English (en)
Other versions
EP0328912A1 (fr
Inventor
Gerhard Schröder
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
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 Gretsch Unitas GmbH Baubeschlaege filed Critical Gretsch Unitas GmbH Baubeschlaege
Publication of EP0328912A1 publication Critical patent/EP0328912A1/fr
Application granted granted Critical
Publication of EP0328912B1 publication Critical patent/EP0328912B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
    • E05F3/225—Additional arrangements for closers, e.g. for holding the wing in opened or other position mounted at the bottom of wings, e.g. details related to seals, covers, connections to the wings, embedding in the floor
    • E05F3/226—Additional arrangements for closers, e.g. for holding the wing in opened or other position mounted at the bottom of wings, e.g. details related to seals, covers, connections to the wings, embedding in the floor with means to adjust the closed position of the wing
    • 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 open door, wherein a rear cylinder space located on this side of a spring-loaded piston which can be displaced by rotating the door is hydraulically connected to a front cylinder space via a housing-fixed flow channel and enters this flow channel Throttle valve and between this and the rear Cylinder chamber are an overflow valve with a spring-loaded closure member, which can be flowed through from the rear to the front cylinder chamber and is released by the piston on its inflow side from a predetermined opening angle of the door, in particular from about 80 ° to 90 °.
  • a door closer has become known from DE-GM 85 26 660.
  • a door closer with a locking device is known from DE-A-26 11 607.
  • a door leaf to be opened is stopped in any position between 85 ° and 180 ° and inevitably remains at this opening angle.
  • the door is closed either by pressing hard or by remote control using an electromagnet.
  • a pressure relief valve releases the flow path for the hydraulic medium when there is a corresponding pressure load or when the spring load is controlled by a magnet, thus enabling the closing spring of the door closer to close the door.
  • the valve ball of the pressure relief valve is loaded in the closing direction by a spring.
  • the spring is supported at one end on this valve ball and at the other end on an adjusting screw from, which is screwed into a thread of a bearing part. The further the set screw is screwed into the thread, the greater the closing force.
  • the known door closer does not offer the possibility of individually adjusting or adjusting the closing force at the installation site.
  • projections of an armature reach through the set screw in the known door closer and subsequent turning of this set screw is therefore no longer possible. If the closing force is to be adjusted or changed, the magnet must be removed.
  • the locking device is not housed in the actual door closer, but in the linkage of the door closer.
  • the object of the invention is to develop a door closer of the type described in the opening paragraph in such a way that, when the door closer is in the installed state, the closing torque can be changed and thus an adjustment to the door weights can be brought about.
  • the door closer is designed according to the preamble of claim 1 in accordance with the characterizing part of this claim.
  • the closure element of the overflow valve is loaded by spring force.
  • the loading spring is supported on the closure member on the one hand and on the valve housing of the overflow valve on the other. If you now the spring housing of the overflow valve in the direction of displacement of the valve closure member can adjust, so it is relatively easy to change the spring force with which the closure member is pressed against its valve seat.
  • the adjustment mechanism must be designed in such a way that every setting is retained safely.
  • the load spring of the overflow valve is maximally tensioned by the fact that the spring housing assumes its position closest to the valve seat, the maximum pressure is required to open the overflow valve. This means that in this one end position of the spring housing the valve has its maximum holding force. Conversely, the minimum holding force and thus the smallest holding torque for the locked door is achieved when the spring housing is in its setting position furthest from the valve seat or the piston of the door closer. Corresponding intermediate positions of the spring housing result in corresponding values of the holding force or the closing torque. This makes it possible to adapt this door closer within its setting range to the respective door weight with relatively little effort and in particular without changing the other hydraulic control system.
  • a further development of the invention provides that the spring housing of the overflow valve is connected to the cylinder base by means of a thread, the thread connection being located between the rear cylinder space and a sealing ring sealing the spring housing against the cylinder base, in particular an O-ring.
  • This cylinder base is expediently a separately manufactured, sealingly inserted part.
  • a threaded connection is relatively easy to manufacture and is therefore particularly inexpensive. In addition, it allows a very sensitive adjustment, especially when using a fine thread.
  • threaded connections are generally not liquid-tight, which is why the spring housing in an area outside the threaded connection must be sealed off from the door closer housing, in particular the cylinder base, so that the hydraulic medium in the door closer, which has penetrated to the outside beyond the threaded connection, is stopped at the location of the sealing ring. The friction in the thread is sufficient to secure the respective setting against unintentional adjustment.
  • the spring housing of the overflow valve has in its outer end a receptacle for a turning tool, in particular a slot, cross recess or hexagon socket.
  • a turning tool used in it, for example a screwdriver or an Allen key, can now be used to easily and precisely adjust the holding torque of this door closer within the intended setting range. without having to open the door closer housing.
  • the screw-in depth of the spring housing of the overflow valve is limited by a stop, in particular a stop surface of the cylinder base.
  • the housing of the overflow valve requires a counter stop surface. This can be formed by enlarging the housing like a paragraph or by providing an outer collar.
  • the incremental enlargement of the spring housing offers itself, which is preferably circular in cross-section already with regard to the sealing ring mentioned. So that the stop surface of the cylinder base is an annular surface, which arises, for example, that a corresponding bore made from the outside inwards in the cylinder base in front of the threaded area is narrowed.
  • the setting range is limited in that the free outer end of the spring housing of the overflow valve can be placed against an external stop in a further embodiment of the invention.
  • a particularly preferred embodiment of the invention provides that the outer stop for the spring housing is formed by a clamping piece of a fastening device for the adjustable holding of the door closer housing in an outer housing, in particular a floor box or the like is.
  • floor door closers In the case of overhead door closers, for which this invention is of course also suitable, the outer stop is located on the door closer housing or on the cylinder base. For example, the use of a snap ring is conceivable.
  • a further embodiment of the invention provides that this clamping piece has an opening which is aligned with the receptacle of the spring housing for the turning tool. The reason is that the turning tool cannot normally be inserted between the clamping piece and the spring housing because the clamping piece is relatively close to the cylinder end or cylinder base.
  • the closing element of the overflow valve closes off the relatively narrow inlet bore with a part that is smaller in cross section. In addition, however, it also has a part with a larger cross section, which becomes effective when the medium can flow through the valve seat of the overflow valve, that is to say when a small opening movement has taken place.
  • the hydraulic pressure now has the option of engaging a larger area and thereby opposing the load spring with a greater force. As a result, the valve remains open at the corresponding hydraulic pressure. It is easy to see that, especially with the small size of the valve parts, precision parts must be involved, which is reflected in the costs and on the other hand leads to a relatively high tolerance sensitivity. For this reason, efforts are being made to improve this.
  • the closure member of the overflow valve is formed by two balls of different sizes, the smaller ball being in contact with the valve seat when the valve is closed and the larger one being inserted between the smaller and the loading spring.
  • the load spring is therefore supported both on the larger ball and on a corresponding support surface in the interior of the closure member. It presses the larger ball against the smaller one, which in turn rests on the valve seat.
  • the balls which theoretically only have a point-like contact, must be secured against lateral deflection in that they can each be displaced in a hole of a corresponding diameter.
  • the displacement distances in such an overflow valve are relatively small. Balls can be manufactured and obtained with high precision, so that the construction is simplified by using balls instead of a turned part and the tolerance sensitivity is reduced.
  • the piston 1 When opening the door, not shown, which is rotatably connected in a known manner to the rotary member 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 supported indirectly 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 one that holds the piston rod and spring Cylinder chamber 6, like the rear cylinder chamber 7, is filled with a suitable hydraulic fluid.
  • 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 the cylinder.
  • the third throttle valve 22 is not must necessarily be present, a third channel 24 belongs. It consists of the transverse channel 25, which opens approximately opposite from the transverse channel 10 into the rear cylinder space 7 and the longitudinal channel 26 and another transverse channel 27 opening into the front cylinder space 6.
  • the piston 1 has a two-part piston ring 28.
  • the transverse channel 27 is arranged such that it is released from the piston ring 28 in the starting position of the piston (FIG. 1).
  • the play between the piston and the cylinder wall 29 is large enough to allow the medium to enter the transverse channel 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 between the parts 32 and 33 thereof 35 is switched.
  • the transverse bore 33 also forms the outlet bore of the first pressure relief 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 first pressure relief valve or 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 casing of the housing encompasses that of the closure member and the pot bases are separated from one another.
  • 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.
  • 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 the shape of a bolt with an outer collar 49 at its end associated with 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, in order to achieve good guidance in the piston 1 on the one hand and flow of the medium on the other hand.
  • the housing of the 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 is centered by a tubular extension, and it is supported with one end on the outside of the closure member and with its other end at a point 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, counter-opening, when closed Door closed pressure relief valve 53.
  • Its closure member 54 is preferably made of a ball, and its load spring 55, like the other valve springs, is a helical compression spring.
  • the closure member of the first pressure relief valve 34 is formed by a small ball 52 and a larger ball 56 resting thereon.
  • the loading spring is designated 57. It normally keeps the valve closed.
  • the small ball 52 of the closure member cooperates with the housing valve seat at the right end of the inlet channel 36 in FIG. 2.
  • the closure members 52 with 56, 48, 54, 39 of the first, 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 piston 1. This makes production particularly easy.
  • the separately manufactured bottom 44 At the end of the cylinder facing away from the rotating member there is the separately manufactured bottom 44 mentioned. It receives the first pressure relief valve 34 and its transverse bore 33, which can also run in the direct extension of the transverse bore 32. In addition, an outer groove forms the aforementioned annular 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 snap ring 60 or the like. The separate production of this cylinder bottom has the advantage that it can be easily exchanged for another.
  • valve bodies of the throttle valves 12, 18, 22 and 23 run perpendicular to the floor when the door closer is in use, and their actuating ends (e.g. 61) are therefore easily accessible from above.
  • the housing or the cylinder for the piston 1 is located in an outer housing 62, 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 substantially higher pressure than the first pressure relief valve 34.
  • the essentially rotationally symmetrical cylinder base 44 has a central bore, the smallest portion of which in diameter forms the inlet bore 36 for the first overflow valve 34.
  • the valve seat 66 of the first overflow valve 34 is formed on the basis of a first shoulder-like extension 65.
  • the diameter of the first extension 65 corresponds approximately to the diameter of the small ball 52 including a small radial play. Viewed in the axial direction, the length is the first paragraph-like expansion approximately equal to the diameter of the small ball 52.
  • the subsequent second step-like extension 67 accommodates the larger ball 56. Accordingly, their diameter corresponds to the diameter of this ball in addition to a small game.
  • the second shoulder-like extension can be enlarged by a cone 69. The largest diameter of which merges into a nut thread 70.
  • this creates an annular stop surface 71 for the spring housing 72 of the first overflow valve 34 and a cylindrical inner surface for engaging the O-ring 74 inserted in a groove 73 of the spring housing 72.
  • the spring housing 72 has the shape of a screw plug with a thickened head. In addition to the mentioned external groove 75 for the O-ring 74, it has a central blind bore for receiving and centering the load spring 57 and on its outside preferably an internal hexagon 77 for screwing in and unscrewing or for adjusting the first overflow valve 34 the transverse bore 33 adjoins the cone 69, the bore 33. Seen in the axial direction, the length of the second shoulder-like extension 67 and the cone 69 together are somewhat less than the diameter of the large ball 56. However, it need not necessarily be so.
  • a stop counter surface 80 is formed, which together with the annular stop surface 71 determines the lowest screw-in position of the spring housing and thus the highest tension of the load spring 57.
  • the unscrewing of the spring housing ends when its outer surface 81 meets an outer stop 82.
  • this is a surface of a clamping piece 83 of a fastening device 84 which points against the cylinder base 44 and by means of which the door closer can be aligned and locked relative to the outer housing 62. It remains to be added that the bolt thread of the spring housing 72 is designated 85.
  • 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 return spring 5 presses the piston 1 and all parts coupled with it in terms of movement back into the starting position shown in FIG. 1. This reduces the volume of the rear cylinder space 7. This requires the amount of liquid that previously occurred when the door was opened to flow back. However, it does not take the path via the second pressure relief valve 47 because it works as a check valve, but via the second throttle valve 18 and the second channel 16. As soon as the piston has run back far enough and the piston ring 28 the transverse bore 13 of the first channel 14 at least partially released, the medium can also flow into the front cylinder space 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 sharp 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 °, the first channel or its transverse bore 13 is still released by the piston or piston ring 28, and therefore the door closes after the actuation force ceases to exist solely on account of 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 through the 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 first pressure relief valve or overflow valve 34 is also located in the fourth channel 37.
  • the transverse bore 13 of the first channel 14 is released for this purpose, so that the back-flowing medium is now through the first channel 14 and the first throttle valve 12 can flow to the front cylinder space 6.
  • the third channel 24 is finally released.
  • 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 works also on the closure member 54 of the third pressure relief valve 53.
  • the hydraulic path goes through the radial slot or the like or the like and the opening of the tubular extension for centering the load spring 51.
  • the load spring 55 of the third pressure relief valve 53 and that of the overflow valve 34 are now matched to one another so that the third pressure relief valve 53 opens at a substantially 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 large enough to also open the third pressure relief valve 53.
  • a sufficiently large return flow cross-section is available which mitigates or eliminates the strong throttling set.
  • the third pressure relief valve 53 can of course be effective from any opening position of the door, in contrast to the overflow valve 34, which is only "released" from an opening angle of the door of, for example, approximately 80 ° to 90 °.
  • the overflow valve 34 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 valve 34 opens, that is to say the balls lift off, the liquid also acts against the larger ball 56, as a result of which a lower force is required to keep it open. After in the fourth channel A back pressure prevails through the fourth throttle valve 23, the overflow valve 34 only closes again when the hydraulic fluid can flow out in another way or when the door is stopped in an intermediate position before the transverse bore 13 of the first throttle valve 12 is released. 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.

Landscapes

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

Claims (8)

  1. Ferme-porte à dispositif d'arrêt hydraulique pour la porte au moins partiellement ouverte, une chambre cylindrique postérieure (7), située en deçà d'un piston (1) chargé élastiquement et pouvant coulisser par rotation de la porte, étant en liaison hydraulique avec une chambre cylindrique antérieure (6) par l'intermédiaire d'un canal d'écoulement (37) ménagé solidairement dans le carter, ce canal d'écoulement renfermant une soupape d'étranglement (23) ainsi que, entre cette dernière et la chambre cylindrique postérieure, une soupape de décharge (34) qui est munie d'un organe obturateur (52, 56) chargé élastiquement, peut être parcourue par un flux de la chambre cylindrique postérieure à la chambre cylindrique antérieure, et dont le côté afflux (36) est dégagé par le piston (1) à partir d'un angle d'ouverture prédéterminé de la porte, notamment à partir d'environ 80° à 90°, caractérisé par le fait que la soupape de décharge (34) présente un boîtier (72) de ressort mobile dans le carter du ferme-porte, en particulier dans le fond cylindrique (44), dans la direction du coulissement de l'organe obturateur (52, 56) de cette soupape, sans devoir ouvrir le carter du ferme-porte.
  2. Ferme-porte selon la revendication 1, caractérisé par le fait que le boîtier (72) de ressort de la soupape de décharge (34) est relié au fond cylindrique (44) par l'intermédiaire d'un filetage, la solidarisation filetée (70, 85) étant située entre la chambre cylindrique postérieure (7) et une garniture annulaire d'étanchement (74), notamment un joint torique, assurant l'étanchéité du boîtier (72) de ressort par rapport au fond cylindrique (44).
  3. Ferme-porte selon la revendication 1 ou 2, caractérisé par le fait que le boîtier (72) de ressort de la soupape de décharge (34) comporte, à son extrémité externe, un logement (77) pour un outil rotatif, en particulier une fente, une fente cruciforme ou une configuration hexagonale creuse.
  4. Ferme-porte selon la revendication 2 ou 3, caractérisé par le fait que la profondeur de vissage du boîtier (72) de ressort de la soupape de décharge (34) est limitée par une butée, notamment une surface de butée (71) du fond cylindrique (44).
  5. Ferme-porte selon au moins l'une des revendications 2 à 4, caractérisé par le fait que l'extrémité externe libre (81) du boîtier (72) de ressort de la soupape de décharge (34) peut être appliquée contre une butée extérieure (82).
  6. Ferme-porte selon la revendication 5, caractérisé par le fait que la butée extérieure (82) destinée au boîtier (72) de ressort est formée par une pièce de coincement (83) d'un dispositif de fixation (84) assurant le verrouillage à demeure réglable du carter (2) du ferme-porte dans un carter extérieur (62), par exemple un caisson d'encastrement au sol.
  7. Ferme-porte selon la revendication 6, caractérisé par le fait que la pièce de coincement (83) présente un évidement qui coïncide avec le logement (77) du carter (2, respectivement 44) de soupape, destiné à l'outil rotatif.
  8. Ferme-porte selon au moins l'une des revendications précédentes, caractérisé par le fait que l'organe obturateur de la soupape de décharge (34) est formé de deux billes de tailles différentes, la bille (52) plus petite étant appliquée contre le siège obturateur (66) lorsque la soupape est fermée, et la bille (56) plus grande étant engagée entre la bille (52) plus petite et le ressort de sollicitation (57).
EP89101324A 1988-02-13 1989-01-26 Ferme-porte avec un dispositif d'arrêt hydraulique Expired - Lifetime EP0328912B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8801894U DE8801894U1 (de) 1988-02-13 1988-02-13 Türschließer mit einer hydraulischen Feststellvorrichtung
DE8801894U 1988-02-13

Publications (2)

Publication Number Publication Date
EP0328912A1 EP0328912A1 (fr) 1989-08-23
EP0328912B1 true EP0328912B1 (fr) 1992-10-14

Family

ID=6820663

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89101324A Expired - Lifetime EP0328912B1 (fr) 1988-02-13 1989-01-26 Ferme-porte avec un dispositif d'arrêt hydraulique

Country Status (2)

Country Link
EP (1) EP0328912B1 (fr)
DE (2) DE8801894U1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4241701C1 (de) * 1992-12-10 1994-02-17 Gartner & Co J Multifunktionales Ventil
CN1078658C (zh) 1997-08-01 2002-01-30 盖慈有限公司 门扇驱动器
US10370885B1 (en) * 2015-12-31 2019-08-06 Larson Manufacturing Company Of South Dakota Hydraulic door closer with fluid overflow chamber
US11105135B2 (en) 2015-12-31 2021-08-31 Larson Manufacturing Company Of South Dakota, Llc Hydraulic door closer with fluid overflow chamber

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB628941A (en) * 1947-10-06 1949-09-07 Robert Edmund Rollings Improvements in or relating to door closers
DE2611607A1 (de) * 1976-03-19 1977-09-29 Eaton Gmbh Feststellvorrichtung fuer tuer-, tor- o.dgl. fluegel
DE3411189A1 (de) * 1984-03-27 1985-10-10 Dorma-Baubeschlag Gmbh & Co Kg, 5828 Ennepetal Selbsttaetiger tuerschliesser
DE8526660U1 (de) * 1985-09-18 1987-01-22 Gretsch-Unitas GmbH Baubeschläge, 7257 Ditzingen Türschließer

Also Published As

Publication number Publication date
DE58902439D1 (de) 1992-11-19
EP0328912A1 (fr) 1989-08-23
DE8801894U1 (de) 1988-03-24

Similar Documents

Publication Publication Date Title
EP1828651B1 (fr) Soupape de limitation de pression presentant une surface differentielle reduite
DE4034188C2 (fr)
DE2952237A1 (de) Drucksteuerventil
DE1925612A1 (de) Hydraulischer Teleskopstossdaempfer
EP0215264B1 (fr) Ferme-porte
DE19631625C2 (de) Hydraulikventil mit Druckbegrenzungs- und Einspeisefunktion
DE2513013A1 (de) Hydraulisches wegeventil zur steuerung des druckmittelflusses zu und von einem doppelseitig beaufschlagbaren hydraulikzylinder
EP0328912B1 (fr) Ferme-porte avec un dispositif d'arrêt hydraulique
EP0549628B1 (fr) Dispositif de commande pour un verin hydraulique
EP1293633B1 (fr) Ferme-porte
DE2254263A1 (de) Sicherheitsventil
DE4322289C1 (de) Ventilvorrichtung für fluide Medien
EP0328917B1 (fr) Ferme-porte
DE4005386C2 (de) Hydraulisch gedämpfter Schließer für Türen, Klappen o. dgl.
EP0285775B1 (fr) Ferme-porte
DE1269841B (de) Hydraulischer Stossdaempfer, insbesondere fuer Tuerschliesser
DE7615433U1 (de) Hydraulisch gedaempfter tuerschliesser
DE10003880B4 (de) Scharnier
DE10106892A1 (de) Vorgesteuertes 2/2-Wege-Sitzventil
AT524555B1 (de) Türschließer
EP1462047A1 (fr) Dispositif amortisseur
DE19524778B4 (de) Türschließer mit einem Verdrängerkolben
DE2440800A1 (de) Stroemungssteuerventilvorrichtung
EP0328933B1 (fr) Ferme-porte avec un dispositif d'arrêt hydraulique
DE2051331A1 (de) Türschließer

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: A1

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19890711

17Q First examination report despatched

Effective date: 19901023

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

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

Ref document number: 58902439

Country of ref document: DE

Date of ref document: 19921119

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
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: GB

Payment date: 20021227

Year of fee payment: 15

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

Ref country code: FR

Payment date: 20030110

Year of fee payment: 15

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

Ref country code: DE

Payment date: 20040108

Year of fee payment: 16

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: 20040126

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

Effective date: 20040126

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: 20040930

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050126

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: 20050802