EP3245373B1 - Entraînement à chaîne en poussée - Google Patents

Entraînement à chaîne en poussée Download PDF

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Publication number
EP3245373B1
EP3245373B1 EP16702037.9A EP16702037A EP3245373B1 EP 3245373 B1 EP3245373 B1 EP 3245373B1 EP 16702037 A EP16702037 A EP 16702037A EP 3245373 B1 EP3245373 B1 EP 3245373B1
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EP
European Patent Office
Prior art keywords
chain
push
pull chain
pull
actuator according
Prior art date
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Application number
EP16702037.9A
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German (de)
English (en)
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EP3245373A1 (fr
Inventor
Reiner Aumüller
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.)
Aumueller Aumatic GmbH
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Aumueller Aumatic GmbH
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Publication date
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Publication of EP3245373A1 publication Critical patent/EP3245373A1/fr
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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
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/611—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings
    • E05F15/616—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by push-pull mechanisms
    • E05F15/619—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by push-pull mechanisms using flexible or rigid rack-and-pinion arrangements
    • 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
    • E05F11/00—Man-operated mechanisms for operating wings, including those which also operate the fastening
    • E05F11/02—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights
    • E05F11/04—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights with cords, chains or cables
    • E05F11/06—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights with cords, chains or cables in guide-channels
    • 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
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/60—Suspension or transmission members; Accessories therefor
    • E05Y2201/622—Suspension or transmission members elements
    • E05Y2201/644—Flexible elongated pulling elements
    • E05Y2201/656—Chains

Definitions

  • the invention relates to a chain thrust drive with the features in claim 1.
  • the US 6,952,916 B1 shows a chain push drive with a push chain, which is designed in a first variant as a link chain and is arranged in a surrounding link casing.
  • the link pins of the link chain protrude beyond the outer link plates and rest on the outside of these link plates with a flattened and widened pin head.
  • the rigid chain is designed as a multi-link connector, which has male links with molded bolts and female links with receiving openings in which the bolts are accommodated with a compressed bolt head.
  • the links each have an L-shape with an upright wall part and a transverse foot part.
  • the bolts and the receiving holes are formed on the upright wall parts, respectively.
  • the links meet at the foot parts, which are alternately directed towards each other.
  • the US 6,173,532 B1 shows another linear chain whose chain links are formed by individual left and right link plates with chain pins.
  • the link plates have flattened areas at both ends, through which the chain pins are pushed through.
  • the individual link plates are lined up in the longitudinal direction of the chain and overlap one another with their flattened areas facing one another.
  • the chain bolts each have a flattened and widened bolt head with which they are flush lie on the outside of the link plate and are accommodated in a recess.
  • the DE 20 2012 001 762 U1 and the US 4,941,316A show chain thrust drives with thrust chains, the chain links of which have inner and outer link plates with a mutual back stop, with inner and outer link plates arranged in pairs and in parallel, which overlap one another at the chain pins.
  • the inner and outer link plates each have a cylindrical link plate eye for the continuous chain pin, which connects the link plates to one another in the axial and transverse directions.
  • the chain pins protrude beyond the outer link plates and lie flat on the outside of this link plate with a flattened and widened pin head.
  • the invention solves this problem in the features of claim 1.
  • the claimed countersunk arrangement and design of the bolt heads of the linear chain can be achieved by the claimed countersunk arrangement and design of the bolt heads of the linear chain.
  • the LinearChain is significantly slimmer and more compact than previous LinearChains, which have rivet bolt heads that are curved far outwards.
  • the sunken bolt head arrangement also allows the linear chain to be guided more easily and better in and on the housing of the chain linear drive. In addition, damage to sash and frame parts is avoided if the linear chain slips along. Furthermore, advantages in terms of improving lateral rigidity are achieved.
  • the chain links have inner and outer link plates with a mutual back stop. At least the outer link plates have plate eyes with a conical countersink for accommodating the likewise conical bolt heads. On the one hand, this is favorable for the countersunk arrangement and for the nevertheless high strength and holding power of the bolt heads and the bolt connection. On the other hand, the form-fitting contact of the conical shapes improves the connection and power transmission between the link plate and the bolt head and increases the supporting effect against lateral forces and the lateral rigidity of the linear chain.
  • the chain thrust drive for movable sashes has a multi-link thrust chain that has back rigidity and lateral rigidity. Due to its back and side rigidity, in particular the limited back and side bending, the linear chain has advantages in terms of improved application options, greater operational reliability and better assembly options.
  • the claimed chain thrust drive can be rigidly attached to a movable wing or to a frame. It can also be concealed in the hollow interior of a frame or sash profile. The claimed chain thrust drive no longer needs the previously customary swiveling housing bearings.
  • the chain thrust drive for movable sashes in particular window sashes, has a multi-link linear chain which has a mouthpiece at the free end and is received countersunk in a housing of the chain thrust drive together with the mouthpiece in the retracted position.
  • this has the advantage that the chain thrust drive can be very small and compact. This makes it easier and simpler to install it concealed within a sash or frame profile.
  • the assembly slots on a sash or frame profile that were previously necessary with the above mouthpieces can be omitted with the embodiment according to the invention.
  • Another advantage is the defined position of the mouthpiece in the retracted position. The mouthpiece can mesh with the driven sprocket of the chain thrust drive.
  • the mouthpiece has other advantages for the linear chain, especially in connection with its back and side rigidity.
  • the mouthpiece can have an angle of attack and an oblique orientation to the last chain link of the linear chain. This has advantages for the specification and definition of the bending of the rigid chain that is desired per se during its travel movements.
  • the rigid chain can be brought into a predetermined bending shape to achieve the desired rigidity. Accidental chain bending in the opposite direction and the rigid chain instability that this causes can be avoided with a high degree of certainty.
  • the rigidity of the back of the linear chain can be improved by a special design of the inner and outer link plates and the resulting back stop.
  • the desired chain bend over the back area can be better defined and adjusted.
  • a better power transmission and supporting effect of the linear chain bent over the back is also favorable.
  • the back stop is formed by a laterally protruding edge flange on one link plate and a front stop edge on the respective other link plate that interacts with it.
  • the mouthpiece also acts in the aforementioned manner for this advantageous.
  • the linear chain claimed also has a desired bending in the lateral direction, which, however, can be limited in the manner mentioned. Thanks to the lateral chain bending or side bending, there is no need for a pivotable mounting of the chain thrust drive housing.
  • the stressed chain guidance in the area of the outlet opening of said housing also has a positive effect on the precise guidance and influencing of the bending of the rigid chain.
  • the stressed linear chain can also be accommodated in a very space-saving manner within the housing of the chain linear drive in a so-called chain station. It can be easily rolled in and out. Additional management and guidance means are not necessary.
  • the chain drive for movable sashes in particular window sashes, has a multi-link linear chain, with the chain drive being assigned a control for synchronizing its extension and retraction movements with another chain drive, with the control having a synchronization factor ( ⁇ ) for the compensation of arrangement-related different paths and / or speeds of the chain thrust drives includes.
  • ⁇ synchronization factor
  • different effective radii of several joint chain thrust drives acting on a moving wing can be compensated. This is particularly advantageous for trapezoidal or triangular wings.
  • the inclusion of a synchronization factor greatly facilitates synchronization control of multiple chain thrusters.
  • the invention relates to a chain thrust drive (1).
  • the invention also relates to a leaf drive (32) with two or more chain thrust drives (1, 1').
  • the chain thrust drive (1) shown serves to move and actuate movable, in particular pivotable, wings (2). These can be opened or closed or brought into a predetermined or freely selectable intermediate position.
  • Such wings (2) can be, for example, window wings, door wings, flap wings or the like. These are preferably parts of buildings.
  • the wings (2) can be movably, in particular pivotably, mounted on a surrounding frame (6) by means of one or more bearings (5).
  • the wing (2) and the frame (6) together can form a window, a door, a flap or the like.
  • the wings (2) and frame (6) usually have a rectangular shape. Alternatively, they can have a different shape, e.g figure 12 trapezoidal shape shown. Furthermore, a triangular shape, a round or oval shape or any other geometric frame and wing shape is possible.
  • the wing (2) and the frame (6) can be made of any material, such as wood, plastic, metal or the like. Or composite materials. They can be solid or designed as hollow profiles.
  • the chain thrust drive (1) has a housing (8) with a drive unit (11) and with one or more thrust chains (4) driven by it.
  • the housing (8) can be mounted on the wing (2) or on the frame (3). It can be installed on the outside or countersunk in the sash or frame profile.
  • the housing (8) can be rigidly mounted on or in the wing (2) or frame (6).
  • the linear chain (4) has a mouthpiece (29) at its free end, which can be connected to the frame (6) or leaf (2) by means of a fitting (7).
  • Figure 12 and 13 show an example of such an arrangement with the housing (8) on the frame (6) and the fitting (7) on the wing (2). The arrangement can also be reversed.
  • the linear chain (4) has a multi-link design. In addition to the mouthpiece (29), it has several chain links (18). The last rear chain link (18) is fixed in the housing (8) by means of a pin or the like. The linear chain (4) can be extended and retracted from the housing (8) by the drive unit (11). It is moved here via a driven chain wheel (14) which meshes with the chain links (18) and preferably also with the mouthpiece (29).
  • the rigid chain (4) has a back stiffness and a lateral stiffness. It can develop pressure or shear forces when extending. She can bend over her back and to the side. These bends are desirable and serve to stabilize the thrust chain (4) in its axial direction in a pressure-resistant manner and to transmit the thrust forces to the moving wing (2).
  • figure 10 illustrates the resulting back bend and figure 11 the side bend.
  • the back and side bending (R,S) is limited by the chain shape. This can be determined by the chain construction. When the maximum back and side bending (R, S) that occurs under load is reached, the linear chain (4) becomes rigid in the axial direction and can develop the axial and shear forces acting during extension.
  • the outlet opening (9) is preferably arranged on the broad side of the housing (8).
  • the chain thrust drive (1) can be mounted on the wing (2) or frame (6) either horizontally or be arranged vertically or possibly also at an angle. It is aligned with the respective adjacent bearing (5) in such a way that the back or a side surface of the linear chain (4) is directed towards the bearing (5). As a result, the shear-stable bending line according to Figure 10 or 11 reached.
  • the chain links (18) have link plates (19,20) with chain pins (25) which connect the link plates (19,20) to one another in the axial and transverse directions.
  • inner and outer link plates (19, 20) are arranged in pairs and in parallel and overlap one another at the chain pins (25) or chain joints.
  • the inner and outer link plates (19, 20) each have a link eye (24) for the continuous link pin (25) at their axial ends.
  • the link plates (19, 20) could have a rounded contour on the belly side. Figure 7 to 9 show this arrangement.
  • the chain bolts (25) have bolt heads (26) at their ends. These are recessed. The bolt heads (26) do not protrude or protrude only minimally beyond the respective side surface of the chain links (18). This results in a substantially flat side surface on both sides of the chain.
  • the chain pins (25) are preferably designed as rivets. Alternatively, they can be designed in a different way, e.g. as screw bolts.
  • the bolt heads (26) can have a conical jacket shape at the transition point to the bolt shank (27) with a smaller diameter, which corresponds to the aforementioned conical countersinking and for a positive connection between the Bolt heads (26) and the strap eyes (24) provides.
  • the push chain (4) has a continuous slit on the back and on the opposite abdominal area. It can be used for drive and guidance purposes.
  • the chain links (18) have inner and outer link plates (19,20) with a mutual back stop (21).
  • the back stop (21) is preferably formed by a laterally projecting edge flange (22) on a link plate (19,20) and a front stop edge (23) cooperating therewith on the adjacent link plate (20,19).
  • the position and dimensions of the end faces of the edge flanges (22) and the stop edges (23) are preferably selected in such a way that there is a small axial distance when the linear chain (4) is in the axially extended position. This enables the above-mentioned back bending of the linear chain (4).
  • the stop position of the back stops (21) can, for example, only be reached when the desired and possibly defined back bend (R) is assumed.
  • the edge flanges (22) are preferably located on the back area of the outer link plates (20) and are directed towards the inside of the rigid chain (4). As a result, they overlap with the associated inner link plates (19) in the axial direction.
  • the edge flange (22) can be formed in one piece and formed by a bend in the rear edge of the strap. This arrangement has the advantage that the bending curve is directed towards the outside of the chain in each case, whereby a curve and chain edge contour that is favorable for starting and sliding is formed. Alternatively, the arrangement may be reversed, with the edge flange located on the inner link plates (19) and facing outwards.
  • the mouthpiece (29) is preferably designed and arranged in such a way that the linear chain (4) together with the mouthpiece (29) is received countersunk in the housing (8) in the retracted position.
  • the mouthpiece (29) does not protrude or only slightly out of the outlet opening (9).
  • the mouthpiece (29) is preferably designed in such a way that, in the retracted position, it meshes with the driven sprocket (14) of the chain thrust drive (1).
  • the mouthpiece is designed as a U-shaped bracket, the parallel bracket arms (30) of which form inner link plate parts. They can be connected in an articulated manner to the outer link plates (20) of the last chain link (18) at the free end of the chain via the last chain pin (25).
  • the bracket arms (30) have the same orientation as the inner link plates (19).
  • the connecting web between the hoop arms (30) is preferably aligned transversely to the plate plane and parallel to the longitudinal axes of the chain pins (25).
  • the axial length of the U-shaped bracket is preferably selected to be large enough to provide space for a connecting element with the fitting (7) and also for the engagement of a tooth of the chain wheel (14).
  • the mouthpiece (29) is preferably aligned at an angle ( ⁇ ) obliquely to the longitudinal axis of the last chain link (18).
  • figure 7 and 9 clarify this arrangement.
  • the mouthpiece (29) is inclined downwards towards the lower-lying chain pin (25) in relation to the back of the chain.
  • the inclined position and the angle of attack ( ⁇ ) are favorable in order to force the linear chain (4) in the bending direction that stiffens the back during the extension movement.
  • the angle of attack ( ⁇ ) has a suitable size for this. The size of the angle can depend on the design and the length of the linear chain (4).
  • the angle of attack ( ⁇ ) can e.g be in a range between 5° and 15°. It is preferably about 8°.
  • a chain guide (15) is arranged on the housing (8) in the area of the outlet opening (9).
  • the chain guide (15) can be made in one piece or in several pieces. In the embodiment shown and preferred, it has a curved guide bar (16) engaging on the open chain back. This is arranged inside the housing (8) and deflects the linear chain (4) from the outlet opening (9) to the chain station by an angle of essentially 90°.
  • the guide rail (16) has a T-shaped cross section, for example, with the central T-bar engaging in the rear slot on the linear chain (4) and guiding and supporting the chain links (18) on the back area when moving in and out. This support is advantageous for achieving the desired bending line and the respective back and/or lateral rigidity.
  • the guide strip (16) can be made of a wear-resistant and low-friction material, such as plastic.
  • the guide rail (16) is arranged opposite the driven sprocket (14).
  • the chain bar (16) is bent concentrically relative to the sprocket (14) and its axis of rotation.
  • the chain pins (25) can come into peripheral guiding engagement with the pin shank (27) of the chain pins (25) or with a chain roller (29) rotatably arranged on the pin shank (27).
  • the linear chain (4) can thus be guided in a U-shape on three sides in the deflection area in the housing (8).
  • the sprocket wheel (14) engages in the linear chain (4) through the ventral slot, with its teeth meshing with the bolt shanks (27) or the chain rollers (28).
  • the chain guide (15) can also have a lateral guide plate (17) at the outlet opening (9).
  • the guide plate (17) can be present individually or in multiples. In particular, according to the dashed representation in figure 4 be arranged on opposite sides of the outlet opening (9).
  • the guide plate (17) provides lateral guidance for the incoming and outgoing linear chain (4) and is preferably located on the inside of the lateral chain bend.
  • the guide plate (17) can be made of a low-wear and low-friction material, for example plastic, and can form a sliding plate for the adjacent side surface of the linear chain (4).
  • the countersunk bolt heads (26) and the essentially flat side surface of the chain that is achieved as a result are advantageous here.
  • the driven chain wheel (14) is arranged in the interior of the housing (8) and in the area below the outlet opening (9). It is driven by the drive unit (11).
  • This has a drive motor (12) and a preferably multi-stage gear (13) for connecting the drive motor (12) and chain wheel (14).
  • the multi-stage gear (13) is preferably formed by spur gears with external teeth.
  • the output shaft of the drive motor (12) is preferably designed as a screw shaft or worm shaft. Alternatively, another training is possible.
  • the drive motor (12) can be controlled or regulated. It is preferably designed as an electric motor, for example as an electric stepping motor. It can be designed, for example, as a DC motor with a low voltage of approximately 10 to 30 V, preferably approximately 24 V. Alternatively, an AC motor is possible.
  • the linear chain drive (1) has a control unit with which the inward and outward movements of the linear chain (4) can be controlled and, if necessary, also regulated.
  • the chain thrust drive (1) can have a suitable sensor system for regulation. This can be a path sensor or a position sensor, for example. Alternatively or additionally, a speed sensor can be present. Such a sensor system can be arranged, for example, on the drive motor (12). It can be designed as an incremental or absolute rotary encoder, for example.
  • the sensor system can have its own evaluation unit and can optionally communicate independently with the environment. It can also be connected to the control unit. This can take care of signal evaluation and external communication.
  • the control unit can be integrated in the housing (8) or alternatively be arranged externally. It can be a motor controller or have an extended range of controls and functions.
  • the control unit can, for example, according to Figure 2 and 3 be designed as a control board.
  • the chain thrust drive (1) and the control unit can be connected to an external energy supply, in particular a power supply, by means of a connecting line (10). If necessary, control signals can also be transmitted via the connection line (10).
  • the connection line (10) is preferably arranged on the front side of the housing (8).
  • the chain thrust drive (1) can be assigned a controller (3) for synchronizing its extending and retracting movements with the extending and retracting movements of another chain thrust drive (1').
  • This synchronization control (3) can be arranged externally. It can alternatively be designed and arranged as a component of the aforementioned control unit, in particular as an implemented hardware or software module.
  • the Chain thrust drives (1, 1') can each have their own or alternatively a common synchronizing control (3).
  • the multiple chain thrust drives (1, 1') can be of the same design as one another.
  • Each of the chain thrust drives (1, 1') can have a control unit and its own or an associated synchronizing control (3). With a multiple arrangement of synchronization control (3), an equal control arrangement or a master-slave arrangement is possible.
  • the synchronization can depend on the arrangement and design of the respective chain thrust drive (1,1'). In particular, there can be a dependency on the respective effective radius (r, r') between the respective linear chain (4) and the associated bearing (5).
  • the several chain thrust drives (1,1') are preferably arranged with the same effective radii (r) on the pivoting horizontal side or on the vertical sides of the wing (2) or frame (6).
  • Figure 12 and 13 illustrate another embodiment with a different wing shape and different arrangements of the chain thrust drives (1,1 ').
  • the wing (2) can, for example, figure 12 have the trapezoidal shape shown or a triangular shape, an oval shape or another shape deviating from the rectangular geometry.
  • the chain thrust drives (1, 1') are arranged at different distances and effective radii (r, r') in relation to the respectively associated bearing (5).
  • r, r' effective radii
  • FIG 13 explains this arrangement.
  • the synchronization control (3) is in for the sake of simplicity figure 12 shown as an external control module. It can alternatively be designed as an integrated controller in the aforementioned manner.
  • the controller (3) for synchronizing the extension and retraction movement of the various chain thrust drives (1,1') contains a synchronization factor ( ⁇ ). This compensates for the different paths and/or speeds of the chain thrust drives (1, 1') and their different effective radii (r, r') caused by the arrangement.
  • the synchronization factor ( ⁇ ) can be constant and is determined according to the theorem of intercepts and used for the synchronization.
  • the synchronization factor ( ⁇ ) represents the relationship between the paths and speeds of the respective chain thrust drives (1,1') and their thrust chains (4), determined according to the theorem of rays and dependent on the ratio of the effective radii (r, r').
  • the respective target value of one or more other chain linear drives (1') is calculated taking into account the synchronization factor ( ⁇ ). and predetermined.
  • the synchronization and default can also be reversed in in the opposite direction between the chain thrust drives (1', 1).
  • the sunken arrangement of the bolt heads (26) can be used individually or in combination with the design of the mouthpiece (29) and/or the control design with the synchronization factor ( ⁇ ).

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  • Power-Operated Mechanisms For Wings (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Claims (15)

  1. Entraînement de poussée à chaîne pour des vantaux mobiles (2), notamment des vantaux de fenêtre, l'entraînement de poussée à chaîne (1) présentant une chaîne de poussée (4) à plusieurs éléments, la chaîne de poussée (4) présentant plusieurs éléments de chaîne (18) avec des maillons de chaîne (19, 20) et des tourillons de chaîne (25) ainsi que des têtes de tourillon (26) encastrées,
    - les éléments de chaîne (18) présentant des maillons de chaîne intérieurs et extérieurs (19, 20) avec une butée dorsale (21) mutuelle,
    - des maillons de chaîne intérieurs et extérieurs (19, 20) agencés respectivement par paires et parallèlement étant présents, 20), qui se chevauchent les uns les autres au niveau des tourillons de chaîne (25),
    - les maillons de chaîne intérieurs et extérieurs (19, 20) présentant chacun à leurs extrémités axiales un œillet de maillon (24) pour le tourillon de chaîne (25) traversant,
    qui relie les maillons de chaîne (19, 20) entre eux dans la direction axiale et transversale et
    - au moins les maillons de chaîne extérieurs (19, 20) présentant des œillets de maillon (24) avec un chanfreinage conique pour la réception encastrée des têtes de tourillon (26) également coniques.
  2. Entraînement de poussée à chaîne selon la revendication 1, caractérisé en ce que les têtes de tourillon (26) ont, au niveau de l'emplacement de transition avec la tige de tourillon (27) de diamètre plus petit, une forme d'enveloppe conique qui correspond au chanfreinage conique susmentionné et qui assure une liaison par complémentarité de forme entre les têtes de tourillon (26) et les œillets de maillon (24).
  3. Entraînement de poussée à chaîne selon la revendication 1 ou 2, caractérisé en ce que la chaîne de poussée (4) présente une rigidité dorsale et une rigidité latérale.
  4. Entraînement de poussée à chaîne selon la revendication 1, 2 ou 3, caractérisé en ce que l'entraînement de poussée à chaîne (1) est prévu et configuré pour un agencement rigide sur un vantail mobile (2) ou sur un cadre (6).
  5. Entraînement de poussée à chaîne selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la chaîne de poussée (4) présente à l'extrémité libre une embouchure (29) et est reçue en position rentrée avec l'embouchure (29) sous forme encastrée dans un boîtier (8) de l'entraînement de poussée à chaîne (1), l'embouchure (29) étant de préférence orientée en position de butée avec un angle d'inclinaison (α) en oblique par rapport à l'axe longitudinal du dernier élément de chaîne (18).
  6. Entraînement de poussée à chaîne selon l'une quelconque des revendications précédentes, caractérisé en ce que les têtes de tourillon (26), de préférence configurées sous forme de rivets, ne dépassent pas ou seulement de manière minimale de la surface latérale des éléments de chaîne (18).
  7. Entraînement de poussée à chaîne selon l'une quelconque des revendications précédentes, caractérisé en ce que la butée dorsale (21) est formée par une bride de bord (22) faisant saillie latéralement sur un maillon de chaîne (19, 20) et par une arête de butée frontale (23) coopérant avec celle-ci sur l'autre maillon de chaîne respectif (20, 19).
  8. Entraînement de poussée à chaîne selon l'une quelconque des revendications 5 à 7, caractérisé en ce que l'embouchure (29) de la chaîne de poussée (4) s'engrène en position rentrée avec une roue à chaîne entraînée (14) de l'entraînement de poussée à chaîne (1).
  9. Entraînement de poussée à chaîne selon l'une quelconque des revendications précédentes, caractérisé en ce que l'entraînement de poussée à chaîne (1) présente un boîtier (8) avec une ouverture de sortie (9) et une unité d'entraînement (11) pour la chaîne de poussée (4).
  10. Entraînement de poussée à chaîne selon la revendication 9, caractérisé en ce qu'un guide de chaîne (15) est agencé sur le boîtier (8) dans la zone de l'ouverture de sortie (9), lequel présente de préférence une baguette de guidage (16) courbée s'engageant sur le dos de chaîne ouvert, le guide de chaîne (15) présentant de préférence une plaque de guidage latérale (17) sur l'ouverture de sortie (9).
  11. Entraînement de poussée à chaîne selon l'une quelconque des revendications 9 à 10, caractérisé en ce que l'unité d'entraînement (11) présente un moteur d'entraînement (12) agencé en oblique dans le boîtier (8) et une transmission à plusieurs étages (13) avec la roue à chaîne (14) côté sortie.
  12. Entraînement de poussée à chaîne selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une commande (3) est associée à l'entraînement de poussée à chaîne (1) pour la synchronisation de ses mouvements de sortie et de rentrée avec un autre entraînement de poussée à chaîne (1'), la commande (3) contenant un facteur de synchronisation (Δ) pour la compensation de courses et/ou de vitesses différentes des entraînements de poussée à chaîne (1, 1') dues à l'agencement.
  13. Entraînement de poussée à chaîne selon la revendication 12, caractérisé en ce que la commande (3) est agencée dans l'entraînement de poussée à chaîne (1).
  14. Entraînement de vantail pour des vantaux mobiles (2), notamment des vantaux de fenêtre, avec plusieurs entraînements de poussée à chaîne (1, 1'), qui présentent chacun une chaîne de poussée (4), caractérisé en ce que les entraînements de poussée à chaîne (1, 1') sont configurés selon au moins l'une quelconque des revendications 1 à 13.
  15. Entraînement de vantail selon la revendication 14, caractérisé en ce que les entraînements de poussée à chaîne (1, 1') agissent à différents emplacements du vantail mobile (2) et avec différents rayons d'action (r, r'), la commande (3) synchronisant les différents mouvements de sortie et de rentrée des entraînements de poussée à chaîne (1, 1') avec le facteur de synchronisation (Δ).
EP16702037.9A 2015-01-13 2016-01-13 Entraînement à chaîne en poussée Active EP3245373B1 (fr)

Applications Claiming Priority (2)

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DE202015100105.3U DE202015100105U1 (de) 2015-01-13 2015-01-13 Kettenschubantrieb
PCT/EP2016/050537 WO2016113286A1 (fr) 2015-01-13 2016-01-13 Entraînement à chaîne en poussée

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EP3245373B1 true EP3245373B1 (fr) 2022-12-07

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DE202017101221U1 (de) 2017-03-03 2018-06-05 Aumüller Aumatic GmbH Kettenschubantrieb
DE102017011091B4 (de) 2017-11-30 2022-08-04 Die Referenz für Antriebstechnik GmbH Kettenantrieb für Lasten wie Fenster oder Rauchabzüge
DE102018104768A1 (de) * 2018-03-02 2019-09-05 Iwis Antriebssysteme Gmbh & Co. Kg Aktuator mit rückensteifer Kette
DE102019100837A1 (de) * 2019-01-14 2020-07-16 Kingspan Holdings (Ireland) Limited Kettenantrieb
CN109826527A (zh) * 2019-02-28 2019-05-31 南京涵铭置智能科技有限公司 一种智能开窗机构及其开窗方法
CN112386083A (zh) * 2020-11-18 2021-02-23 广东奥科伟业科技发展有限公司 可防止链条弯曲的推窗帘***及其控制方法

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US6173532B1 (en) * 1999-09-03 2001-01-16 Armand S. Beausoleil Automatic garage door opener
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EP3245373A1 (fr) 2017-11-22
DK3245373T3 (da) 2023-02-27
WO2016113286A1 (fr) 2016-07-21
CN107208447B (zh) 2021-01-12
CN107208447A (zh) 2017-09-26
PL3245373T3 (pl) 2023-04-03
DE202015100105U1 (de) 2016-04-11

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