EP0534089B1 - Dispositif de commande pour les tiges coulissantes d'une serrure d'une fenêtre ou d'une porte - Google Patents

Dispositif de commande pour les tiges coulissantes d'une serrure d'une fenêtre ou d'une porte Download PDF

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Publication number
EP0534089B1
EP0534089B1 EP92112839A EP92112839A EP0534089B1 EP 0534089 B1 EP0534089 B1 EP 0534089B1 EP 92112839 A EP92112839 A EP 92112839A EP 92112839 A EP92112839 A EP 92112839A EP 0534089 B1 EP0534089 B1 EP 0534089B1
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EP
European Patent Office
Prior art keywords
gearwheel
transmission
crank
toothing
positioning bar
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
EP92112839A
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German (de)
English (en)
Other versions
EP0534089A1 (fr
Inventor
Karl-Heinz Schmidt
Jürgen Sassmannshausen
Achim Türk
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.)
Siegenia Aubi KG
Original Assignee
Siegenia Frank KG
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Publication date
Application filed by Siegenia Frank KG filed Critical Siegenia Frank KG
Publication of EP0534089A1 publication Critical patent/EP0534089A1/fr
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Publication of EP0534089B1 publication Critical patent/EP0534089B1/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
    • E05C—BOLTS OR FASTENING DEVICES FOR WINGS, SPECIALLY FOR DOORS OR WINDOWS
    • E05C9/00—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing
    • E05C9/02—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening
    • E05C9/021—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening with rack and pinion mechanism
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B17/00—Accessories in connection with locks
    • E05B17/20—Means independent of the locking mechanism for preventing unauthorised opening, e.g. for securing the bolt in the fastening position
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05C—BOLTS OR FASTENING DEVICES FOR WINGS, SPECIALLY FOR DOORS OR WINDOWS
    • E05C9/00—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing
    • E05C9/02—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening
    • E05C9/026—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing with one sliding bar for fastening when moved in one direction and unfastening when moved in opposite direction; with two sliding bars moved in the same direction when fastening or unfastening comprising key-operated locks, e.g. a lock cylinder to drive auxiliary deadbolts or latch bolts
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05C—BOLTS OR FASTENING DEVICES FOR WINGS, SPECIALLY FOR DOORS OR WINDOWS
    • E05C9/00—Arrangements of simultaneously actuated bolts or other securing devices at well-separated positions on the same wing
    • E05C9/10—Actuating mechanisms for bars
    • E05C9/16—Actuating mechanisms for bars with crank pins and connecting rods
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
    • E05D15/00—Suspension arrangements for wings
    • E05D15/48—Suspension arrangements for wings allowing alternative movements
    • E05D15/52—Suspension arrangements for wings allowing alternative movements for opening about a vertical as well as a horizontal axis
    • E05D15/522—Suspension arrangements for wings allowing alternative movements for opening about a vertical as well as a horizontal axis with disconnecting means for the appropriate pivoting parts
    • E05D15/523—Suspension arrangements for wings allowing alternative movements for opening about a vertical as well as a horizontal axis with disconnecting means for the appropriate pivoting parts using movable rods
    • E05D15/524—Actuating mechanisms
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05B—LOCKS; ACCESSORIES THEREFOR; HANDCUFFS
    • E05B63/00—Locks or fastenings with special structural characteristics
    • E05B63/0017—Locks with sliding bolt without provision for latching
    • E05B63/0021—Locks with sliding bolt without provision for latching the bolt being shot over an increased length by a single turning operation of the key
    • 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
    • E05Y2900/148—Windows

Definitions

  • Actuating gears of this type have long been part of the prior art for the stated purpose, such as CH-PS 324 607 shows.
  • the total travel of the drive rod is divided into two sections of equal length, which is passed through from the basic switching position to the intermediate switching position, while the other is determined by the further movement of the actuating gear from the intermediate switching position to the end switching position.
  • the actuating gear Since the installation depth of the connecting rod fittings and the actuating gear in the window profile is narrowly limited, the actuating gear must have the smallest possible backset, i.e. get by with a small distance from the axis of rotation of the drive member mounted in the transmission housing from the front end face of the transmission housing. Therefore, the drive members can only get a relatively small radius, so that the achievable total travel range for the drive rods is within relatively narrow limits. In addition, the smallest possible backbone dimension is required.
  • actuating gears have already been created which use a gearwheel having several toothed segments with differently sized pitch circle diameters as the drive member, which has groups of engagement members on the drive rod interacts, whose position on the drive rod is matched to the different pitch circle diameters of the toothed segments.
  • the aim of the invention is to design an actuating gear of the type specified at the outset, in which an uneven subdivision of the total travel range for the drive rod coupled herewith can be achieved while maintaining a relatively small backset and backset dimension and a resulting minimal installation depth.
  • a subdivision of the total travel range is sought, which is approximately at a ratio of 2: 1, in such a way that the larger travel range portion, for example when the drive member moves from its basic switching position to an angular distance of 90 ° of which has the intermediate switching position, while then the smaller portion of the travel path is passed through as it moves further from the intermediate switching position mentioned to the end switching position, which is in turn at an angle of 90 ° from it.
  • an actuating gear corresponding to the input specification with these features is that a so-called large stroke gear can be created, which can be realized with a relatively small backset and backset and consequently with a small installation depth - in the direction parallel to the wing plane. This means that it does not differ, or only insignificantly, from the dimensions of the corresponding actuating gear with a normal total travel.
  • a large-stroke gearbox for a total travel between 50 mm and 70 mm, preferably about 60 mm can be created by the specified measures, in which two successive rotation angle ranges of 90 ° for the drive member considerably different travel ranges for the drive rod can be derived. Over the two partial rotation angle ranges of the actuating gear of 90 ° each, with the help of the design according to the invention, an advantageously different force / displacement implementation achieve and consequently improve the ease of use of the espagnolette fittings for windows and doors.
  • the gearwheel - as usual - has a circular rolling area and meshes with toothed racks aligned at least approximately parallel to the sliding direction of the drive rod.
  • the gear can also have a non-circular shape, e.g. have oval rolling area and comb with gear racks that are curved or inclined to the direction of sliding of the drive rod.
  • the drawer of the straight-pull crank consists of two links connected in series, e.g. whose common connecting joint or one of the links is slidably held in a fixed guide of the gear housing.
  • This stationary guide can extend approximately parallel to the direction of displacement of the drive rod in the gear housing or can also receive a course or a position in which the connecting joint between the two drawer link members is only in the middle rotary or intermediate switching position of the drive member is on a straight line through the crank pin of the straight thrust crank and through the axis of rotation of the gear on the drawer.
  • the invention also includes an embodiment of the fixed guide in the gear housing, which has a more or less curved or curved shape and consequently additionally influences the transmission of the drive movement generated by the drive member to the drive rod.
  • a design has also proven itself in which the total length of the drawer for the straight thrust crank to the crank radius of the drive member has a ratio of about 5: 1, while the length of the two links of the drawer has a ratio of about 2: 3 to one another stands.
  • the shorter link of the drawer should be assigned to the drive link and the longer link to the gear.
  • both members of the drawer have a shape which is slightly curved or kinked in the direction of their plane of movement, their kink or curvature position being rectified. This ensures that the bearing rosette of an operating hand lever is attached to the transmission housing without obstruction.
  • crank pin of the drive member of the straight thrust crank assumes an over-center position in the end switching position of the actuating gear, while it has an under-center position when the drive element is in the basic switching position and is supported.
  • the drive member can be blocked - preferably by an additional slide bolt accommodated in the gearbox housing, whereby for the actuation of the slide bolt into the gearbox housing e.g. a so-called profile cylinder can be used afterwards.
  • the actuating gear 1 for longitudinally displaceable connecting rods 17 on fittings of windows, doors or the like shown in FIGS. 1 to 5 of the drawing each have a gear housing 2, which is, for example, essentially trough-shaped or shell-shaped and on its open broadside a cover (not shown) can be closed, the outline of which is adapted to the gear housing 2.
  • the cover is supported on frames or projecting from the bottom 3 of the gear housing 2 at right angles. Walls 4 off.
  • a faceplate 5, for example made of strip material, is connected, for example riveted or welded, to the face of the gear housing 2.
  • a drive member 6 is rotatably supported between its base 3 and the cover over an angular range of 180 °, which carries a radially projecting crank arm 7 in which a crank pin 8 is seated.
  • a drawer 9 which in turn is formed by two links 10 and 11 connected in series. These have a connecting joint 12 in common, which is held displaceably in a fixed guide 13 of the gear housing 2, for example in elongated holes or slots in the base 3 and in the cover. 1 to 3 of the drawing, the fixed guide 13 is only indicated by a dash-dotted line, which extends in a straight line in the longitudinal direction of the gear housing 2.
  • a toothed wheel 15 is rotatably mounted about a central axis 14, which meshes on the one hand with a toothing 16 which is located on the in the gear housing 2 and along the faceplate 5 longitudinally displaceable drive rod 17 is located.
  • the toothed wheel 15 is constantly in engagement with a climbing toothing 18 which is arranged in a stationary manner in the gear housing 2, for example on its rear frame or wall 4.
  • Crank arm 7 and drawer 9 together form a straight sliding crank 7/9, which can be moved from the drive member 6, for example by a square drive mandrel of an operating hand lever or also a power drive is. It is assumed that the drive member 6 in two successive switching steps, each extending over angular distances of 90 °, from a basic switching position according to FIG. 1 into an intermediate switching position according to FIG. 2 and again from the intermediate switching position according to FIG. 2 3 is rotatable in the end switch position.
  • the straight push crank 7/9 on the one hand and the gear wheel 15, the toothing 16 and the climbing toothing 18 on the other hand are provided as intermediate gear members between the drive member 6 and the drive rod 17, which should not only bring about the conversion of a rotary drive movement into a linear output movement. Rather, the intermediate gear members also have the task of producing a relatively large total actuating path a for the drive rod 17 with a small installation depth for the actuating gear 1, which in turn is composed of two different partial actuating paths b and c.
  • the translation of the partial travel x and y that can be produced by the straight thrust crank 7/9 and the total travel z in the partial travel b and c as well as the total travel a of the drive rod 17 is achieved by the gear transmission 15 arranged downstream of the straight travel crank 7/9 / 16/18 causes because the gear 15 rolls on the one hand in the fixed climbing toothing 18 and on the other hand meshes with the toothing 16 in the lockable drive rod 17.
  • the transmission ratio z: a is determined by the pitch circle radius of the diametrically opposite toothed sections of the toothed wheel 15 which are respectively engaged with the climbing toothing 18 and the toothing 16.
  • both links 10 and 11 of the drawers 9 to be designed such that they have a shape which is slightly curved or kinked in the direction of their plane of movement. Their kink or curvature positions are aligned, as can be clearly seen from FIGS. 1 to 3 of the drawing.
  • crank arm 7 While in the basic switching position of the actuating gear 1, the crank arm 7 is supported on a stop 20 inserted into the gear housing 2 (FIG. 1), the crank arm 7 supports in its end switching position the rear frame or wall of the gear housing 2 on (Fig. 3).
  • FIGS. 4 and 5 of the drawing differ from those according to FIGS. 1 to 3 in various respects.
  • a gear 15 is also used in the gear transmission 15/16/18, which has a circular rolling area and meshes with teeth 16 and climbing teeth 18 aligned parallel to the sliding direction of the drive rod 17.
  • this gear wheel 15 is mounted on the link 11 of the drawer 9 about an axis 14 arranged eccentrically to its circumference.
  • the eccentricity of the axis 14 to the circumference or pitch circle of the toothing is laid so that with the help of the gear wheel 15 over the one part of the basic switching position and on the other hand from the intermediate switching position limited first partial travel distance comes into effect than over the second partial travel which is determined by the intermediate switching position and the final switching position.
  • the fixed guide 13 of the gear housing 2 does not interact with the connecting joint 12 between the two links 10 and 11 of the drawer 9, but rather with guide webs 21, which are rigidly arranged on the gear 11 bearing member 11 of the drawer 9.
  • the outer boundary surfaces of the guide webs 21 have a spherical or convex curvature and engage in longitudinal slots on the bottom 3 and on the cover of the gear housing 2 a, which have a slightly curved course and form the stationary guide 13. It has proven useful, for example, if the lower part of the fixed guide 13 runs with an inclined position of approximately 2 degrees with respect to the longitudinal direction of the transmission housing 2 and the upper part of the same follows this with an inclined position of approximately 4 to 5 degrees.
  • the two links 10 and 11 of the drawer 9 also have an aspect ratio of about 1: 1 to one another; however, the slightly curved or kinked shape of the links 10 and 11 is also present there, so that a collision with threaded bushings 22 is avoided, into which fastening screws for the bearing rose of an operating hand lever can be screwed.
  • the actuating gear 1 according to FIGS. 4 and 5 correspond in terms of their basic structure. However, while the actuating gear 1 according to FIG. 4 is designed for a relatively small backset of 20 mm, the actuating gear 1 according to FIG. 5 is equipped for a relatively large backset of e.g. 40 mm. The backbone dimension is the same in both cases and relatively small with less than 15 mm.
  • a bridging element 24 is positively engaged, which has a toothing 25 on its opposite longitudinal edge, with which the gear wheel 15 meshes.
  • the bridging element 24 is provided in this case with longitudinal guide grooves 26 which Guide webs 27 cooperate, which are located on the inside on the bottom 3 and on the cover of the gear housing 2.
  • the gear 15 of the gear 15/16/18 can also have a non-circular, e.g. oval, rolling area are provided as well as comb with gear racks 16 and 18 which are curved or inclined to the sliding direction of the toothed rack 17.
  • the gear 15 can also have two toothings with different pitch circle diameters and be designed so that each of these toothings meshes with only one of the toothed racks 16 and 18.
  • the actuating gear 1 can, if required, be equipped with a so-called profile locking cylinder, which fits into a recess 28 in the base 3 and in the cover of the gear housing housing which is closely matched to its profile 2 can be used. Via its beard or driver attachment, which can be rotated by key actuation, this profile locking cylinder acts within the transmission housing 2 on two additionally installed locking slides 29 and 30.
  • the locking slide 29 is arranged and designed so that the crank arm 7 can be blocked against rotation with its help in the basic switching position.
  • the arrangement and design of the bolt slide 30, however, are of such a type that it can be used to directly block the drive rod 17 in its intermediate switching position against displacement. .A blockage of the actuating gear 1 via the partial travel from the intermediate switching position to the end switching position is not provided.
  • the locking slide 29 is set with a cam or a tongue 31 in its path of movement.
  • a nose 23 of the locking slide 30 engages in a cutout 33 of the drive rod 17.
  • the locking slides 29 and 30 are designed and held in operative connection with one another in such a way that they can only be moved logically via the profile locking cylinder.
  • a leg spring 34 serves the purpose of securing the disengaged basic position of both locking slides 29 and 30, as can be seen in FIGS. 4 and 5. In the engaged position, the two locking slides 29 and 30 block each other, also under the influence of the leg spring 34, as long as the profile lock cylinder is not actuated.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Air-Flow Control Members (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Power-Operated Mechanisms For Wings (AREA)
  • Window Of Vehicle (AREA)

Claims (12)

  1. Mécanisme d'actionnement (1) pour des tringles de commande (17) pouvant coulisser longitudinalement sur des ferrures de fenêtres, de portes ou similaires, qui peuvent être amenées - manuellement et/ou par entraînement mécanique - dans plusieurs positions de commande différentes afin de pouvoir bouger le battant, vantail ou autre panneau par rapport au châssis fixe à partir d'une position de fermeture verrouillée dans plusieurs positions d'ouverture différentes, par exemple une position d'ouverture par basculement et une position d'arrêt parallèle ou une position d'ouverture par pivotement de même que, le cas échéant, dans une position d'aération à fente, parmi lesquelles une position d'ouverture, plus particulièrement la position d'ouverture par basculement ou la position d'arrêt parallèle, peut être forcément réglée - par l'intermédiaire de bras pouvant bouger du fait de la tringle de commande,
    dans lequel un élément d'entraînement (6) disposé dans un boîtier de manoeuvre (2) de manière à pouvoir tourner peut être pivoté à partir d'une position de commande de base (figure 1) en passant par au moins une position de commande intermédiaire (figure 2) dans une position de commande finale (figure 3) de même que la position de commande finale présente par rapport à la position de commande initiale un écart angulaire de 180° tandis que la respectivement une position de commande intermédiaire est située à un écart angulaire de 90° entre la position de commande de base et la position de commande finale,
    caractérisé en ce que,
    l'élément d'entraînement (6) est maintenu dans une connexion d'entraînement permanente avec la tringle de commande (17) guidée de manière à pouvoir coulisser de façon linéaire dans le boîtier de manoeuvre (2) par l'intermédiaire d'éléments de transmission intermédiaires (7 à 18) conçus pour une subdivision inégale de l'ensemble du parcours de réglage (a) de la tringle de commande (17) sur la zone qui sépare la position de commande initiale (figure 1) et la position de commande intermédiaire (figure 2) de même que celle qui sépare ladite position de commande intermédiaire (figure 2) et la position de commande finale (figure 3), en ce que comme éléments de transmission intermédiaires (7 à 18) sont connectés directement l'un derrière l'autre d'une part un mécanisme bielle-manivelle (7/9) pouvant être actionné par un élément d'entraînement pivotant (6) et d'autre part un engrenage (15/16/18) s'engrènant avec la tringle de commande (17),
    en ce que en outre un pignon (15) de l'engrenage (15/16/18) s'engrènant avec la crémaillère (16) de la tringle de commande (17) est monté avec son axe (14) sur une plaquette de poussée (9) du mécanisme bielle-manivelle (7/9) et en ce que enfin ledit pignon (15) se trouve en outre en engrènement permanent avec un endentement à plans inclinés (18) prévu de manière fixe dans le boîtier de manoeuvre (2) dans sa zone périphérique plus ou moins diamétralement opposée au point d'engrènement avec la crémaillère (16) de la tringle de commande (17).
  2. Mécanisme d'actionnement selon la revendication 1, caractérisé en ce que l'axe (14) du pignon (15) de l'engrenage (15/16/18) est disposé de façon excentrique par rapport à la circonférence respectivement au cercle primitif de référence de son endentement (figures 4 et 5).
  3. Mécanisme d'actionnement selon la revendication 1 ou 2, caractérisé en ce que le pignon (15) présente une zone à développante circulaire et s'engrène avec des crémaillères (16 et 18) orientées parallèlement à la direction de coulissement de la tringle de commande (17).
  4. Mécanisme d'actionnement selon la revendication 1 ou 2, caractérisé en ce que le pignon (15) présente une zone à développante non circulaire, par exemple ovale, et s'engrène avec des crémaillères ayant une forme courbée adaptée respectivement oblique à la direction de coulissement de la tringle de commande (17).
  5. Mécanisme d'actionnement selon les revendications 1 et 3, caractérisé en ce que le pignon (15) de l'engrenage (15/16/18) présente deux endentements de diamètre différent et en ce que chaque endentement s'engrène avec une des crémaillères (16 et 18).
  6. Mécanisme d'actionnement selon la revendication 1 et au moins l'une ou l'autre des revendications 2 à 5, caractérisé en ce que la plaquette de poussée (9) du mécanisme bielle-manivelle (7/9) se compose de deux éléments (10 et 11) montés l'un à la suite de l'autre dont l'articulation de jonction commune (12) est constamment maintenue de manière à pouvoir coulisser dans une glissière fixe (13) du boîtier de manoeuvre (2).
  7. Mécanisme d'actionnement selon la revendication 6, caractérisé en ce que la glissière fixe (13) s'étend dans le boîtier de manoeuvre (2) quelque peu parallèlement à la direction de coulissement de la tringle de commande (17) et/ou présente un parcours respectivement occupe une position dans lequel respectivement dans laquelle l'articulation de jonction (12) aménagée ici se situe entre les deux éléments des plaquettes de poussée (10 et 11) du moins dans la position médiane de commutation par pivotement de l'élément d'entraînement (6) plus ou moins sur une ligne de connexion par les tourillons de manivelle (8) du mécanisme bielle-manivelle (7/9) et par l'axe (14) du pignon (15) de la plaquette de poussée (9) (fig.2).
  8. Mécanisme d'actionnement selon l'une ou l'autre des revendications 1, 6 et 7, caractérisé en ce que la longueur totale de la plaquette de poussée (9) pour le mécanisme bielle-manivelle (7/9) a un rapport d'environ 5:1 par rapport au rayon de la manivelle de l'élément d'entraînement (6) et en ce que les longueurs des deux éléments (10 et 11) de la plaquette de poussée se situe l'un par rapport à l'autre dans un rapport de approximativement 2:3.
  9. Mécanisme d'actionnement selon la revendication 8, caractérisé en ce que l'élément plus court (10) de la plaquette de poussée (9) est relié à l'élément d'entraînement (6) et en ce que l'élément plus long (11) de cette même plaquette est relié au pignon (15).
  10. Mécanisme d'actionnement selon l'une ou l'autre des revendications 1 et 6 à 9, caractérisé en ce que les deux éléments (10 et 11) de la plaquette de poussée (9) présentent une forme légèrement courbée ou fléchie en direction de leur plan de mouvement, leur position d'inflexion ou de courbure étant dirigé du même côté.
  11. Mécanisme d'actionnement selon la revendication 1 et au moins l'une ou l'autre des revendications 7 à 9, caractérisé en ce que le tourillon de manivelle (8) de l'élément d'entraînement (6) du mécanisme bielle-manivelle (7/9) dans sa position de commande finale (figure 3) adopte une position de point mort haut tandis que le tourillon de manivelle (8) lorsque l'élément d'entraînement (6) est en appui et se touve en position de commande initiale (figure 1) adopte une position de point mort bas.
  12. Mécanisme d'actionnement selon la revendication 1 et au moins l'une ou l'autre des revendications 2 à 5, caractérisé en ce que la plaquette de poussée (9) du mécanisme bielle-manivelle (7/9) se compose de deux éléments (10 et 11) montés l'un à la suite de l'autre qui ont une articulation de connexion commune (12), l'élément (11) solidaire du pignon (15) de l'engrenage (15/16/18) étant maintenu de manière à pouvoir coulisser (21) le long d'une glissière fixe (13) dans le boîtier de manoeuvre (2), laquelle glissière s'étend de façon légèrement courbée et/ou obliquement par rapport à la direction de poussée de la tringle de commande (17) (figures 4 et 5).
EP92112839A 1991-09-27 1992-07-28 Dispositif de commande pour les tiges coulissantes d'une serrure d'une fenêtre ou d'une porte Expired - Lifetime EP0534089B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9112079U 1991-09-27
DE9112079U DE9112079U1 (de) 1991-09-27 1991-09-27 Betätigungsgetriebe für längsverschiebbare Treibstangen an Beschlägen von Fenstern und Türen o.dgl.

Publications (2)

Publication Number Publication Date
EP0534089A1 EP0534089A1 (fr) 1993-03-31
EP0534089B1 true EP0534089B1 (fr) 1996-11-27

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EP92112839A Expired - Lifetime EP0534089B1 (fr) 1991-09-27 1992-07-28 Dispositif de commande pour les tiges coulissantes d'une serrure d'une fenêtre ou d'une porte

Country Status (4)

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EP (1) EP0534089B1 (fr)
AT (1) ATE145702T1 (fr)
DE (2) DE9112079U1 (fr)
ES (1) ES2095363T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
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DE202008009184U1 (de) 2008-07-09 2009-11-12 Siegenia-Aubi Kg Verriegelungsvorrichtung
EP3128109A1 (fr) 2015-08-05 2017-02-08 Aug. Winkhaus GmbH & Co. KG Transmission d'entrainement pour une ferrure de bielle
EP3205797A1 (fr) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Transmetteur pour une crémone
EP3205798A1 (fr) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Mécanisme d'entraînement pour une crémone

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DE29600446U1 (de) 1996-01-12 1997-05-07 Siegenia-Frank Kg, 57074 Siegen Betätigungsgetriebe für Fenster und/oder Türbeschläge mit Stell- und/oder Verriegelungsgestänge o.dgl.
DE29719611U1 (de) * 1997-11-05 1999-03-11 Gretsch-Unitas GmbH Baubeschläge, 71254 Ditzingen Schloß, insbesondere Einsteckschloß für eine Außentür
DE19929742A1 (de) * 1999-06-17 2000-12-21 Hautau Gmbh W Getriebeanordnung für einen Stangenverschluss
AT408013B (de) * 1999-10-07 2001-08-27 Roto Frank Eisenwaren Drückerbetätigbares mehrriegelschloss
DE20313119U1 (de) * 2003-08-22 2003-11-06 SIEGENIA-AUBI KG, 57074 Siegen Treibstangenverschluss
DE10354185B4 (de) * 2003-11-20 2015-04-02 Aug. Winkhaus Gmbh & Co. Kg Kantengetriebe
EP2366855B1 (fr) * 2010-03-19 2014-07-23 ROTO FRANK Aktiengesellschaft Ferrure pour une fenêtre, une porte ou analogue, ainsi que fenêtre, porte ou analogue avec une ferrure
FR3133636B1 (fr) * 2022-03-21 2024-02-16 Ferco Dispositif de commande d’un système de verrouillage de type crémone pour un vantail coulissant

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202008009184U1 (de) 2008-07-09 2009-11-12 Siegenia-Aubi Kg Verriegelungsvorrichtung
EP2143859A2 (fr) 2008-07-09 2010-01-13 Siegenia-Aubi Kg Système de verouillage
EP3128109A1 (fr) 2015-08-05 2017-02-08 Aug. Winkhaus GmbH & Co. KG Transmission d'entrainement pour une ferrure de bielle
DE102015214936A1 (de) 2015-08-05 2017-02-09 Aug. Winkhaus Gmbh & Co. Kg Antriebsgetriebe für einen Treibstangenbeschlag
EP3205797A1 (fr) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Transmetteur pour une crémone
EP3205798A1 (fr) 2016-02-11 2017-08-16 Aug. Winkhaus GmbH & Co. KG Mécanisme d'entraînement pour une crémone
DE102016202064A1 (de) 2016-02-11 2017-08-17 Aug. Winkhaus Gmbh & Co. Kg Übersetzungsgetriebe für einen Treibstangenbeschlag
DE102016202063A1 (de) 2016-02-11 2017-08-17 Aug. Winkhaus Gmbh & Co. Kg Antriebsgetriebe für einen Treibstangenbeschlag

Also Published As

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ES2095363T3 (es) 1997-02-16
DE59207583D1 (de) 1997-01-09
DE9112079U1 (de) 1993-01-28
EP0534089A1 (fr) 1993-03-31
ATE145702T1 (de) 1996-12-15

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