EP1505239B1 - Drive for a leaf, in particular rotary drive for a door, a window or the like - Google Patents

Abstract

A power system for an industrial swing door has a lift cam plate (47) that is asymmetric when seen in axial presentation. The plate has two asymmetric outer profiles. Depending upon the installation, one profile or the other operates in conjunction with the door movement.

Description

The invention relates to a drive for a preferably only in one direction in an open position and in the opposite direction in the closed position rotatable rotary wing, in particular rotary drive for a door, a window or the like, according to the preamble of claim 1.

An electromechanical rotary vane drive for swing vanes of doors or the like has become known, for example, from EP 0 565 565 B1. This drive preferably comprises a DC motor with an adjoining in the axial extension of the DC motor gear, the transmission is on the output side with an angular gear in operative connection. An output shaft is arranged perpendicular to the housing longitudinal axis and coupled with a linkage for driving a rotary vane. Also, a return spring unit is provided which dimensioned according to the pre-publication accordingly is and in the axial interior surrounds the electric motor and / or the transmission. Transmission output side, the housing side supported at its other end coil spring is supported on a driver which is rotatably connected to an output shaft of the transmission performing intermediate shaft.

With such an electromechanical drive can be performed in a comfortable manner, in particular using sensors, an automatic door opening and closing operation. The corresponding mechanical spring arrangement is always clamped and relaxed again. The return spring device is merely provided in order to ensure a secure closing of the door in an emergency situation (in particular in the event of a power failure or in the event of failure of control components). However, since such drives are usually provided with a damping device, the closing force of the spring must be sufficiently high to not only a return of the door in the closed position, but especially when reaching the closed position a secure engagement or locking, if necessary Snap in, etc. to allow in the closed position (as regulated in the EC standard EN1154).

When using toggle or scissors levers this is usually possible because such a toggle lever or scissors linkage has a high power ratio due to the kinematics in the last phase of the closing movement of a wing, so that at the end of the closing forces rise significantly again. But if such a drive at least partially or exclusively only be used together with a slide, so can then no longer realize the desired high closing forces, especially in the last phase of the closing movement.

Therefore, a variety of solutions have been proposed to provide increased closing forces, especially in the last closing phase, especially in door closers (without electromechanical or hydraulic drive) but also in motor-driven drives available.

According to DE 199 56 005 A1, WO 02/064932 A1 and EP 0 856 628 A1, for example, a door closer for mounting on a door with rotary blades is proposed, whose closing spring is indirectly or directly supported on a piston or a piston-cylinder device , While the piston cooperates via an internal gear device with a housing mounted in the housing shaft. The closing shaft is coupled to achieve improved power generation, especially in the last area of the closing phase with a telescopic sliding arm, which is designed as an external gear device with an external Obersetzungsverhältnis, which is constant over the rotation angle of the closing shaft torque curve on the closing shaft in a moment course on the Door transformed, which falls in a range of small door opening angle substantially such that at a small door opening angle, a relatively large moment on the door and a large door opening angle a relative small moment on the door is generated.

But all these solutions require a high production cost, since the rack-like construction on the one hand and the gears meshing therewith, on the other hand, have different tooth sizes, tooth thicknesses and tooth spacing, in order to generate this continuous different torque generation.

According to DE 196 41 799 A1, in order to improve the course of the torque, it has even been attempted to form the guide curve in a slide rail in deviation from conventional door closers, not parallel to the plane of the wing or frame plane, but curved.

In addition, a number of other Vorveröffentlichungen have become known that work with a different design principle. For example, from DE 40 38 720 C2 an upper door closer with a slide rail linkage, with a spring arrangement and with a damping piston has become known. The closing shaft has a Hubkurvenscheibe whose associated in the opening direction cam track of at least one pressurized roller and its associated in the closing direction cam track is pressurized by a damping piston on another role. The Hubkurvenbahn is provided with changing radius so that the Hubkurvenscheibe and thus the closing shaft is adjusted in the closing direction by initiating the closing force on the spring assembly. Upon reaching the final closed position, the Hubkurvenscheibe has a low-lying convex curvature region corresponding to the closed position of the door, whereby the door is held in a force-loaded position.

The corresponding Hubkurvenscheibe has in side view of the heart shape approximate waveform. The respective radial distance of the tread can be adapted to the circumstances be adapted on site so that a respective desired force profile, with which the door to be closed is applied, can be generated.

Based on this principle, further modifications have become known, for example according to DE 100 31 785 C2, in which instead of a spring arrangement, two mutually parallel spring arrangements are used, which act on the corresponding Hubkurvenscheibe.

According to WO 00/42282 A1 (corresponding to DE 100 01 950 A1), two force accumulators are also used, which, however, are arranged opposite to one another by 180 °, relative to the output shaft, whereby the entire installation space is further increased.

In the case of a motor drive, in particular an automatic leaf and in particular door leaf drive, a corresponding space, for example, for an electric motor drive unit and for a downstream gear unit is initially required. In addition, a damping device should be provided in order to dampen the door appropriately and slowly in the closed position. This can be achieved, for example, by a hydraulic damping device, but preferably by an electromechanical damping device, for example by switching over the electric motor required for opening the door to generator operation and possibly short-circuiting it. Only in the event that the short circuit of the generator, the closing movement is too slow, in one or the other case between the inputs of the electric motor and a corresponding load can be switched, for example, a low-impedance Load to thereby achieve a preferred and optimal closing speed depending on the size of the load. Should be next to another needed for the power failure or generally for emergency operation, provided with an energy storage locking device, this requires a considerable amount of construction.

Furthermore, there is the problem of creating a possibility that especially at the end of the closing process, the required and desired high closing forces are generated when the locking mechanism is not cooperating with a scissor or toggle linkage, but also with a slide or should be used as a direct drive.

Finally, from DE 936912 B a closing device for swing doors is known which operates without a separate electric motor drive. This locking device for swing doors has a cam with a cam curve which is provided on one side with a circumferentially changing radius and on the opposite side with a cylindrical cam portion, so that in particular a formed in the form of a roller locking member due to the cylindrical configuration the cam can not exert any restoring forces on the wing.

From US-B-6 530 178 an automatic door drive according to the preamble of claim 1 can be seen as known, which has a closing spring. This closing spring receives in the interior an electric motor drive with axially downstream transmission, which drives a transverse to the axial direction of the electric motor and the transmission drive shaft, which is unilaterally led out of the overall housing and this protrudes. By the electric motor, the door can be opened, wherein a closing movement can be initiated via the spring assembly so formed on the spring assembly. The device is such that the spring acts on a transmission device with a parabolic curved device, with which cooperates a roller-shaped follower member which sits on a connected to the output shaft and rotating with this disc. The actuating surface of the cam device is configured such that the flanks of this cam device are formed asymmetrically, wherein this cam member can be installed in two installation positions rotated by 180 °, so that the force transmission in different opening directions of a door is different.

Object of the present invention is in contrast to provide an improved drive for a rotary door sash, in particular an improved rotary door drive for doors or the like, which includes an energy storage device, which ensures a closing of a wing in case of failure of the drive and in particular in an emergency situation. The drive should be suitable for different applications, for example in conjunction with a slide or in interaction with a scissors linkage. In this case, the force curve, according to which a wing can be closed, should be comparable in both cases. Preferably, the closing forces acting on the wing, especially at small opening angles, preferably as short as possible and to reach the closed position to be as high as possible in order to always ensure a safe closing. These closing forces should also preferably be so high and sufficient that they despite existing damping device allow a secure closure.

The object is achieved according to the features specified in claim 1. Advantageous embodiments of the invention are specified in the subclaims.

By the present invention, a drive for a wing, in particular an electromechanical drive for a wing, created - as in the prior art - an energy storage, preferably in the form of a spring assembly comprises, which with a cam or Hubkurvenscheibe for bringing about a mechanical closing operation of a door leaf cooperates. After manually opening a door, the corresponding force storage device acts with the lifting curve in the sense of a door closer, preferably to bring even in the presence of a damping device, the door, especially at the end of the closing movement safely in the closed position.

In the case of an automatic door drive, in particular an automatic rotary vane drive, the mentioned mechanical locking device using the force accumulator and the Hubkurvenscheibe is used as a safety device in case of power failure or failure of a control component, that is generally in an emergency situation.

According to the Hubkurvenscheibe is formed asymmetrically. This allows it to be used for different applications. Thus, the cam or cam disc can be designed asymmetrically so that then uses an approximately half the area of the disc is when the drive device works together with a slide rail and the opening movement takes place pulling. The other half of the cam disc can be used when a toggle or scissors linkage is used, which opens the door abutting. Likewise, however, a Hubkurvenscheibe can be used, the opposite cam surfaces are designed so that the drive interacts with a pushing working slide rail or with a pulling working slide rail. Likewise, the invention can also be used for a swing door, which can therefore be opened to both sides. Also in the case of such a swing door each wing can be swung back safely in the closing direction within the scope of the invention.

Thus, the wing drive according to the invention can be designed for a variety of purposes, namely for installation in connection with a slide (which is "pull" mounted in operation, for example), as well as in connection with a scissor linkage, which, for example, in operation "push" is used. A conversion for one or the other application is not necessary.

A significant advantage of the invention consists in the fact that the drive according to the invention has a drive axle which has two connection in the axial direction offset from each other, so opposite ends each have a connection option to here, for example, a scissors or toggle mechanism or eg a sliding lever for opening and Close a door to connect. Thus, only by different assembly of this drive and thus by selectable use the first or second connection option to the output shaft automatically one or the other half of the Hubkurbelscheibe and the related force curve are effective. Preferably, one half of the cam curve is designed so that it is particularly suitable in interaction with a toggle linkage, whereas the other half of the cam curve is adapted to the use of a Gleithebelgestänges. Thus, in each case only by using one or the other connection possibility without the need of opening the housing and an internal conversion of a cam disk the optimum force curve can be preselected on site alone.

In principle, it would also be conceivable that a Hubkurven- or cam disc is used, the asymmetry is constructed and adapted so that such a drive, for example, once "push" with a slide during operation or the other part of the asymmetrically shaped Hubkurvenscheibe in interaction with a slide rail in the "pull" mode of operation is adjusted.

Finally, such an asymmetrical Hubkurvenscheibe could also be used for a swing door, which works for example in connection with a slide rail. Because in the one opening direction of the swing door, the function "slide pulling" is present, while for the swing door, if it is pushed open in the other direction, the function "slide abutting" is present. Also, such applications have not been possible.

It is surprising that it is a motorized wing drive now was possible to accommodate the desired power storage-locking device for a very compact and space-saving and on the other about closing forces especially at the end of the closing movement to produce, so that such a drive and locking device not only using a toggle lever or scissor linkage, but can also be used in connection with a slide rail and the fulfillment of the EN 1154 standard.

Preferably, it is provided that the longitudinal axis or direction of action of the energy storage device for the mechanical closing device is arranged axially offset from an output or intermediate shaft on which the Hubkurven- or cam disc is co-rotating. Furthermore, a transmission device or a transmission gear is provided in order to transmit the force applied by the force accumulator to a running on the circumference of the Hubkurvenscheibe or camshaft pressure device.

The transmission device or the transmission gear can for example also consist of a hydraulic arrangement to forward the pressure from the energy storage on the Hubkurvenwellen. Preferably, however, a transmission gear, in particular a lever mechanism in the form of a one-armed or two-armed lever (rocker) is used.

Preferably, the axis of rotation on the one hand and the relative distance of the pressure element supported on the lever gear to the other can be selected so that here again a further force transmission is achieved, whereby the contact forces, with which a pressure roller on the Hubkurvenscheibe is pressed, is increased again and thus at the end of the closing movement, the desired high return pivoting forces can be applied.

The arrangement may be constructed so that the energy storage device is preferably effective in the form of the spring force accumulator on pressure or train.

About the output shaft can be used in the context of the invention, both a toggle lever or scissors linkage, but equally a slide rail to safely close a wing, especially a door in case of failure of the other drive unit or in an emergency situation. This mechanical locking device for the mentioned emergency situation can also be used in the case of a direct drive, when the cam disk acts, for example, directly on the axis of rotation of a wing.

Figur 1:

eine schematische perspektivische Darstellung eines erfindungsgemäßen Antriebes für einen Flügel, der in sogenannter Kopfmontage mit einem Gleitgestänge in der Funktion "ziehend" montiert ist;

Figur 2:

eine zu Figur 1 vergleichbare Darstellung, bei der der Antrieb in Kopfmontage im Zusammenspiel mit einem Gleitgestänge montiert ist, und zwar in der Funktion "drückend";

Figur 3:

eine entsprechende Darstellung eines Antriebes, montiert in Kopfmontage im Zusammenspiel mit einem Scherengestänge in der Funktion "drückend";

Figur 4:

eine schematische perspektivische Darstellung eines in Kopfmontage montierten Antriebes im Zusammenspiel mit einen Scherengestänge in der Funktion "ziehend";

Figur 5:

eine schematische perspektivische Darstellung des erfindungsgemäßen Antriebes bei abgenommenen Gehäuse;

Figur 6:

eine perspektivische Darstellung der wesentlichen Teile des erfindungsgemäßen Antriebes;

Figur 7:

eine perspektivische Darstellung der mechanisch wirkenden Schließeinheit;

Figur 8a

eine schematische Seitenansicht auf die Nockenscheibe oder Hubkurvenscheibe in einer ersten Ausführungsform;

Figur 8b:

eine entsprechende Darstellung zu Figur 8 für ein abgewandeltes Ausführungsbeispiel;

Figur 9a:

eine perspektivische Darstellung einer Hubkurvenscheibe, die aus vier Einzelscheiben zusammengesetzt ist;

Figur 9b:

die in Figur 9 a gezeigte Hubkurvenscheibe, bei der die vier Einzelscheiben in Abstand voneinander einzeln dargestellt sind;

Figur 10a:

ein Diagramm zur Erläuterung des Momentenverlaufs bei einem Drehflügelantrieb nach dem Stand der Technik, welcher mit einem Gleitgestänge "ziehend" arbeitet;

Figur 10b:

ein Diagramm zur Verdeutlichung des Momentenverlaufs bei einem Drehflügelantrieb mit Gleitgestänge "ziehend" gemäß der vorliegenden Erfindung;

Figur 11a:

ein entsprechendes Diagramm bezüglich des Momentenverlaufs bei einem herkömmlichen Drehflügelantrieb, welcher mit einem Gleitgestänge "stoßend" arbeitet;

Figur 11b:

ein Diagramm zur Verdeutlichung des Momentenverlaufs bei einem Drehflügelantrieb mit Gleitgestänge "stoßend" entsprechend der vorliegenden Erfindung;

Figur 12:

ein zu den Figuren 1 bis 7 abgewandeltes Ausführungsbeispiel mit einer Übertragungseinrichtung in Form eines Übersetzungsgetriebes nach Art eines einarmigen Hebels;

Figur 13:

eine Darstellung des erfindungsgemäßen Antriebes in Form eines Direktantriebes, bei der die Abtriebswelle direkt mit der Türachse gekoppelt ist;

Figur 14:

ein zu Figur 13 abgewandeltes Ausführungsbeispiel; und

Figur 15:

ein nochmals abgewandeltes Ausführungsbeispiel eines indirekten Kettenantriebes, der mit dem erfindungsgemäßen Antrieb gekoppelt ist.

Further advantages, details and features will become apparent from the illustrated with reference to drawings embodiment. In detail:

FIG. 1:

a schematic perspective view of a drive according to the invention for a wing, which is mounted in so-called head assembly with a slide link in the function "pulling";

FIG. 2:

a representation comparable to Figure 1, in which the drive is mounted in head assembly in interaction with a slide link, in the function "oppressive";

FIG. 3:

a corresponding representation of a drive, mounted in head assembly in conjunction with a scissor linkage in the function "pushing";

FIG. 4:

a schematic perspective view of a mounted in head assembly drive in conjunction with a scissor linkage in the function "pulling";

FIG. 5:

a schematic perspective view of the drive according to the invention with the housing removed;

FIG. 6:

a perspective view of the essential parts of the drive according to the invention;

FIG. 7:

a perspective view of the mechanically acting closing unit;

FIG. 8a

a schematic side view of the cam or Hubkurvenscheibe in a first embodiment;

FIG. 8b:

a corresponding representation to Figure 8 for a modified embodiment;

FIG. 9a:

a perspective view of a Hubkurvenscheibe, which is composed of four individual discs;

FIG. 9b:

the Hubkurvenscheibe shown in Figure 9 a, in which the four individual disks are shown separated from each other at a distance;

FIG. 10a:

a diagram for explaining the torque curve in a rotary vane drive according to the prior art, which works with a sliding link "pulling";

FIG. 10b:

a diagram for illustrating the torque curve in a rotary vane drive with sliding link "pulling" according to the present invention;

FIG. 11a:

a corresponding diagram with respect to the torque curve in a conventional rotary vane drive, which "works" with a slide linkage;

FIG. 11b:

a diagram for illustrating the torque curve in a rotary vane drive with sliding link "pushing" according to the present invention;

FIG. 12:

a modified to Figures 1 to 7 embodiment with a transmission device in the form of a transmission gear in the manner of a one-armed lever;

FIG. 13:

a representation of the drive according to the invention in the form of a direct drive, in which the output shaft is coupled directly to the door axis;

FIG. 14:

a modified to Figure 13 embodiment; and

FIG. 15:

a further modified embodiment of an indirect chain drive, which is coupled to the drive according to the invention.

In Figure 1, a door frame 1 is shown to illustrate the different ways of use, in which on a right-hand rotation axis 3, a wing 5 is pivotally suspended. In this case, it is a door wing of the swing door.

About the drive 7, which has a vertical output shaft 9, according to this embodiment, a door in its closed position by means of an energy storage device - will be adjusted later - be adjusted in the embodiment of Figure 1 at the upper horizontal sash 5 'a Sliding rail 11 is mounted, in which an end 13'a of a rotationally fixed to the output shaft 9 connected pivot lever 13 engages.

In the embodiment according to Figure 1, the assembly is mounted in the manner of a so-called "head assembly" in the functional position "sliding link pulling", wherein when the door is opened via the pivot lever 13, the door is pulled into the open position.

Figure 2 shows a head assembly of the drive 7 in the functional position "sliding linkage pushing", since here to open the door of the pivot lever 13 "pushes" the door.

However, the same drive 7 can basically also be used to open or close a door in connection with a toggle lever and scissors linkage 17. The drive in question is mounted in head assembly on the upper horizontal portion of a door frame, wherein the scissor linkage 17 is connected at its one end to the vertical output shaft 9 of the drive and the opposite end of the toggle linkage 17 on a vertical axis 10 at the upper horizontal frame 5 'of the door leaf 5 is fixedly mounted. Figure 3 shows the head assembly in conjunction with a scissors linkage in the position "pushing" (because the door is pressed in the open position on the toggle lever) and in Figure 4 in head assembly in the function "pulling". In this case, the output axis 9 opposite end of the toggle linkage 17 is rotatably supported on a transverse arm 19 about a vertical axis, which is fixedly mounted on the wing 5.

Based on Figure 5, the drive 1 is shown with the housing removed. In other words, in the drive represented in FIG. 5, the bottom plate (which is mounted on the vertical side of the door frame in the illustrations of the drive in FIGS. 1 to 4) in this perspective illustration is omitted. In this case, the opposite end faces 21 (FIGS. 1 to 4) relative to the representation of the drive in FIG. 5 can still be positioned further to the left or further to the right relative to the base or base plate, so that even more installation space within the housing for further Components, in particular of electrical components, transformers, etc., is available.

FIG. 5 shows the drive block 23 penetrated by the output shaft 9. As can also be seen, in particular, in conjunction with FIG. 6, the drive unit 25 comprises an electric motor 25a, in particular a DC motor, whose motor output shaft 27 is drivingly connected to a subsequent transmission gear 31 via an intermediate gear 29 in the embodiment shown. The transmission input shaft 31a is driven by a revolving belt 33 from the engine output shaft 25a. Since the engine output shaft or the engine output disk is smaller in size than the transmission input shaft or transmission input disk 31a, a desired transmission ratio results in smaller output numbers.

At the output of the transmission gear 31 (which may also be constructed arbitrarily and is formed in the simplest case only in the form of a transmission device) a bevel gear 35 is arranged in the embodiment shown, which meshes with a larger sized conical output gear 37. The two bevel gears 35 and 37 also form a gear ratio. Again, only a simple transmission can be provided. Such a transmission or translating transmission can take place by means of all suitable measures, for example via friction wheels, belt drive, etc. The output gear 37 is seated on the output shaft 9, which passes through the output gear 37, so that at both opposite ends of the output shaft 9 a connection option A1 and A2 is to here, for example, a scissor linkage or a cooperating with a slide opening or closing levers mounted in a rotationally fixed. This also opens up the possibility of using the drive arrangement both in the case of a right-hand as well as a left-hinged wing, since the drive can be easily mounted rotated by 180 ° on the upper door frame on its vertical surface.

FIG. 5 schematically shows an electronics box 39 in which all or essential parts of an automatic door control can be accommodated. In the embodiment according to FIG. 5, for example, further electronic components and above all a transformer inside the housing, which is needed for an automatic rotary-wing drive, could be accommodated on the left next to the drive block 23. With regard to the electrical / electronic mode of operation, reference is made to the previously known door control drives.

In the embodiment shown, an automatic door control could be performed with such a rotary wing drive. In particular, in conjunction with a sensor which is mounted above a door, the door could be opened automatically when someone moves closer and automatically closed again after passing through. The drive can be carried out according to the previously known drives. During an electric motor-controlled closing movement, as well as in the event of power failure, especially in an emergency situation, a damping device is also effective. The additionally provided damping device in order to ensure a low-control closing movement of the door or the door leaf, for example, using take a hydraulic damper. Preferably, however, the damping is realized in that the electric motor required to open the door is used when closing the door leaf as a generator, which can be shorted to it. It may be advisable, however, not to short-circuit the generator without resistance, but with the interposition of a low-impedance load in order to be able to produce a closing effect that is dampened but still perceived as sufficient. Ultimately, both measures slow the closing movement to an optimum value.

However, in order to ensure a safe swinging back the door in the closed position and possibly a latching of the door in the closed position in case of failure of the power or failure of the drive unit in an emergency situation, generally in an emergency situation, a mechanical clamping unit 41 is provided, the energy storage 43rd , a transmission device or transmission gear 45 and a cam or Hubkurvenscheibe 47 includes, which are arranged rotatably in the embodiment shown on the output shaft 9. This cam or Hubkurvenscheibe 47 can also be arranged on an offset to the output shaft 19 intermediate shaft, which is only in drive connection with the output shaft 9. This would preferably be an intermediate shaft parallel to the output shaft 9.

As can be seen from the illustrations according to FIGS. 5, 6 and in particular FIG. 7, the force accumulator 43 in the illustrated embodiment consists of a helical spring 43 'which, once under pressure, is fixed to the housing at its rear side facing the drive unit 25 is supported on a stop 51 located there, and on the opposite side to a stop 53 which is pivotally supported about an axis extending parallel to the output shaft 9 axis 55.

The axis 55 is part of the transmission gear 45, which in the illustrated embodiment consists of a two-armed lever 57, i. a double lever or rocker 57 a is formed, which is pivotable about a tilting axis 59.

At the opposite end to the axis 55 of the lever 57, a further axis 61 is anchored and held about which a pressure roller 63 is freely rotatable, which runs on a peripheral surface 65 of the cam or cam disc 47.

In Figure 6 and 7 while the cam plate 47 is shown in its initial position in which the wing 5 is in its Verschließstellung. If the wing 5 in one of the embodiments according to Figure 1 to 4 are pivoted manually or by means of the motor drive means in the open position, and would then enter an emergency situation, so would be on the pressurized energy accumulator 43 in the form of coil spring 43 ', a contact pressure on the movable stop 53 are exerted, which then acts on the one free end of the lever mechanism 45, so that the opposite lever arm of the lever mechanism is pressed via the pressure roller 63 on the peripheral surface 65. The curve of the peripheral surface 65 is such that changes over the entire adjustment of the radial distance of the tread to the axis 9 and continues to decrease, until in the final Closed position the pressure roller 63 in a concave, recessed fixed section 67 or just before it comes to rest, in which the door is exactly in the closed position (Figure 8a and 8b). In the case of a swing door, the pressure roller 63 will actually come to lie in the concave recessed portion 67. In the case of a door to be opened only in one direction, the setting is usually made so that upon reaching the closed position of the wing, the pressure roller 63 is in a position in which they shortly before reaching the lowest point of the recessed portion 67 to lie comes. As a result, a biasing force which is still maintained in the closed position is still generated on the wing. Overall, the highly compact arrangement also results from the fact that the coil spring 43 passes in its axial extent at the transverse thereto, in the embodiment shown perpendicular thereto aligned output shaft 9, without cutting them. As a result, the entire space within the housing of the drive device can be optimally utilized. At the end of the force accumulator, which is preferably formed from a helical spring, then connects the translation or deflection gear, which is designed so that the force transmission quasi back again takes place in the opposite direction, namely to the cam plate 47 to running. The entire arrangement of the coil spring, the cam plate 47 and the lever-translation gear 57, 57 a and 57 b is preferably arranged in a common plane, which supports the overall compact design. The output shaft 9 is preferably oriented perpendicular to this extending in the longitudinal direction of the drive housing extending plane. Because in this arrangement, the cam plate 47 next to and below the coil spring 43 'are housed.

The aforementioned output shaft 9 may represent only an intermediate shaft in a modified embodiment, so that for example via a further drive connection (for example via two intermeshing gears) an output can be made on a further shaft, which serves as the final output shaft.

Two possible embodiments of the cam or cam disc 47 are shown in FIGS. 8a and 8b.

The Hubkurvenscheibe 47 is formed asymmetrically. In FIG. 8a, for example, the left circumferential surface 65a is designed so that it can preferably be used in conjunction with a scissor or toggle linkage if this is used in the so-called "pushing" mode. The right circumferential or running surface 65b of the cam disk 47 is intended to be used when, for example, the mechanical safety locking mechanism cooperates with a slide linkage in the functional position "pulling".

Of course, another Hubkurvenscheibe 47 are used, as shown for example in a schematic side view in Figure 8b. There, the treads are designed and optimized differently, namely such that, for example, the peripheral surface 65a (left in Figure 8b), in particular for use with a slide linkage, in the functional position "pushing" and the right surface 65b in conjunction with a slide linkage in the Function position "pulling" is optimized.

The Hubkurvenscheiben 47 described above, for example, be provided internally with an opening 47a, in which an internal toothing 47b is formed. If the output shaft or intermediate shaft 9 has a corresponding external toothing with the same tooth sequence, then a stroke cam disk 47 formed in this way for producing a rotational connection with the associated output shaft or intermediate shaft 9 can be realized solely by plugging.

Such Hubkurvenscheibe 47 is usually produced in a complex, several steps comprehensive machining process. Likewise, such Hubkurvenscheibe but also in a fine blanking process can be made completely in one operation. In order to obtain the fine cutting and thus a sufficiently good cylindrical surface, the cam plate is preferably composed of a plurality of thin-walled disks 47 '. FIGS. 9a and 9b show such a lifting cam disk composed of four partial disks.

In principle, however, other force storage devices may be used instead of the mentioned force accumulator 43, for example in the form of the helical spring 43, for example hydraulic energy accumulators, gas springs, etc.

In all cases, an adjustment of the pressure force by an integrated adjuster 71 (Figure 6 and 7) take place, which consists in the embodiment shown from an adjusting screw 73, which via a threaded seat with its movable stop 53 in the direction of the energy storage 43 and turned can be, whereby the contact forces are increased or minimized. The adjustment device 71 in the form of the adjusting screw 73 is supported preferably directly or indirectly on a thread on the axis 55 from.

Due to the described structure results in a highly compact overall arrangement, since the spring energy storage on the one hand has sufficient space to use a corresponding sufficiently large-sized coil spring, but on the other hand by the mentioned lever mechanism optimal feedback and force on a cam disc 47 is possible, the can rotate immediately below a seated below the spring accumulator output shaft.

Characterized in that the force of the energy accumulator 43 is transmitted via the intermediate gear 45 in each case via parallel axes 45, 59 and 61 on the pressure roller 33 and then on the Hubkurvenscheibe 47, this results in an optimal side support and recording the considerable high forces. The coil spring 43 'is axially held and supported by an inner centering rod 44 against lateral deflection. The centering rod 44 is preferably connected at its one end to the stop 53 and thus with the adjusting screw 73 and immersed at its opposite end in a receiving portion 44 a, which is connected to the opposite stop 51. This can be adjusted by turning the adjusting screw 73, the effective length between the stops 51, 53, without this being hindered by the centering rod 44. By the transmission device in the form of the transmission gear, in addition, a force transmission, for example by a factor of 1.5 to 10.5, preferably 1.5 to 5 can be achieved, preferably for example By a factor of 2, this means that the spring arrangement or generally the energy storage device can be dimensioned smaller by a factor of 2 than in the prior art.

In the following, first of all, FIGS. 10a and 10b will be discussed. FIG. 10 a shows the torque curve for a wing, in particular door leaf, in the range of 0 ° (corresponds to the closed position up to 90 ° open position for a certain size, for example EN 6).

This curve according to FIG. 10a indicates on the y-axis the respective torque amount in newton millimeters with respect to the generated torque curve, namely for a swing door operator which works with a "sliding linkage" and according to the prior art a linear spring characteristic having.

The curve according to 10a is based on the following parameters: Door opening angle = 90 Gr. Slide lever length = 450 mm Center distance output door hinge = 280 mm Frictional torque = 5 Nm at the output Spring preload 38.3 Nm at the output Increase of spring preload 30% to 180 degrees on the downforce

Comparison of minimum values on the door leaf according to EN 1145 for size 6

Min. Closing moment in delivery (0-4 degrees) 54 Nm (54 Nm) Do. in open position 88-92 degrees) 18 Nm (46 Nm) Do. in between 11 Nm (max 58 Nm, at least 46 Nm)

This curve according to FIG. 10a is now compared with the torque curve according to FIG. 10b, the torque curve according to FIG. 10b reproducing the torque curve when a vane drive according to the present invention is used. It can be seen that not only the closing forces are significantly greater immediately in the last angular range before reaching the closed position, but that - as always desired - is initially assumed in the opening range of 90 ° from an initial clamping force, wherein in the following angular range the closing forces then become lower during the closing process, in order finally to allow the closing forces to increase significantly again immediately in the last angular range before reaching the actual closed position, and this even if a damping device is provided. In the present case is used as a damping device of the electric drive motor, which is used when closing the wing as a generator whose electrical connections are directly short-circuited or electrically connected with the interposition of a preferably low-impedance load to produce the desired closing speed.

Further, reference is made below to the figures 11a and 11b, wherein the figure 11a shows the torque curve according to a previous solution and that for a rotary vane drive, with a "slide bar" in the operating mode "pushing" works. FIG. 11b shows the torque curve when the present invention is applied. The curves according to FIGS. 11a and 11b are obtained when the following basic data are used: Door opening angle = 90 Gr. Slide lever length = 450 mm Center distance output door hinge = 280 mm Frictional torque - = 5 Nm at the output Spring preload 39 Nm at the output Increase of spring preload 30% to 180 degrees on the downforce

Comparison of minimum values on the door leaf according to EN 1145 for size 6

Min. Closing moment in delivery (0-4 degrees) 54 Nm (55 Nm) Do. in open position (88-92 degrees) 18 Nm (30 Nm) Do. in between 11 Nm (max 58 Nm, at least 30 Nm)

Based on FIG. 12, it is merely shown that, instead of a two-sided lever or a rocker 57a, a one-sided lever 57b can also be used as a lever gear 47. In this case, however, an energy storage device 43, for example in the form of a helical spring 43, must be used, which generates the contact forces on the train. Also by this, the pressure roller 63 mounted on the lever mechanism 47 in the form of the one-sided lever 57b is pressed onto the circumferential surface 65 of the cam disk 47 and causes the same backward pivoting of an open one Door. Here, too, an additional force transmission to the cam disc 47 can be generated by the positioning of the pressure roller 63 holding axis 61, corresponding to the distance between the axis 61 to the tilting axis 59 in relation to the distance between the axis 55 (to which the tension spring 43 'attaches) and the tilting axis 59th

A possibly slightly differently shaped double lever can not be used in contrast to Figure 7 with a compression spring, but with a spring loaded on train spring device, namely, when the camshaft deviating to Figure 7 on the opposite side of the pressure roller 63 comes to rest. In contrast to FIG. 11, however, a compression spring device can also be used when a one-armed lever is used, even if the cam disk is mounted there on the opposite side of the pressure roller. To achieve the least possible space-consuming structure in this case, the lever configurations and / or the tilting axes 59 of the levers would be located elsewhere than in the embodiment of Figure 7 and 11, ie, the tilting axes 59 would be preferred in the latter two applications be provided further left lying.

With reference to FIGS. 13 et seq., It is merely shown that a drive constructed in this way can also be used as a direct drive, for example in FIG. 13 as a direct drive which is coupled to a door axis. The mechanical locking mechanism can be used in such an electromechanical drive in a wing, in which the opening movement "pulling", "pushing" or "pendulum" is realized. Also in so-called Escape route doors would be considered a so-called break-out solution, in which, for example, opens a hinged door on the electromechanical drive into an interior and closes and can be turned on in an emergency to the outside. Also in this case, the explanatory mechanical restoring device would be returned via the energy storage of the wing back to its closed position.

In the embodiment shown in Figure 14, the illustrated drive is constructed so that it interacts indirectly with a lever or a slide rail in the wing. Again, the structure may be such that the function "pulling", "pushing" or "oscillating" or "break out" is realized.

Based on the embodiment shown in Figure 15 it is shown that the drive can also interact directly indirectly by means of a chain drive, countershaft or other gear design with the axis of rotation of a wing. The explained, the safety mechanical locking mechanism can work effectively, regardless of whether the wing here with respect to its electromechanical opening and closing operation according to the design principle of "pulling", "pushing", "oscillating" or under realization of a "break-out" Solution that is implemented.

Claims (19)

1. Drive for a swivel-door leaf (or window casement) which can be rotated preferably just in one direction into an open position and in the opposite direction into a closed position, in particular rotary drive for a door, a window or the like, having the following features:

   - having a motor-operated drive unit (25), which preferably comprises an electric motor (25a) and at least one downstream gear mechanism (29, 31),

   - having an output shaft (9), which can be coupled at least indirectly to a leaf (or casement) (5) at at least one coupling location (A1),

   - preferably having a damping device for damping the closing and/or opening movement of the leaf (5),

   - the drive unit (25) is in drive-connection with the output shaft (9),

   - also provided is an energy-store device (43), via which a contact-pressure member, preferably in the form of a contact-pressure roller (63), rolls with contact pressure on the circumferential surface of an eccentric cam disc (47),

   - the eccentric cam disc (47) is arranged in a rotationally fixed manner on the output shaft (9) or an intermediate shaft,

   - the eccentric cam disc (47) is configured asymmetrically, as seen in the axial direction, and

   - the eccentric cam disc (47) comprises two asymmetric circumferential-surface or running-surface regions (65a and 65b),
   characterized by the following further features:

   - the output shaft (9) has a respective attachment means (A1, A2) at its two opposite ends, and

   - depending on the installation position and attachment of a pivot lever (13) or toggle lever (17) at one or other of the attachment means (A1, A2), in the case of a leaf which can only be opened in one direction, either only one circumferential-surface or running-surface region (65a) or the other circumferential-surface or running-surface region (65b) is active when the swivel-door leaf is adjusted.
2. Drive according to Claim 1, characterized in that the eccentric cam disc (47) is configured asymmetrically such that one part of the circumferential or running surface is suitable for interacting with a sliding rail during "pulling" operation and the second part of the circumferential or running surface, which is asymmetric in relation to the first, is suitable for interacting with a scissors linkage during "pushing" operation.
3. Drive according to Claim 1, characterized in that the eccentric cam disc (47) is configured asymmetrically such that one part of the circumferential or running surface is suitable for interacting with a sliding rail during "pulling" operation and the second part of the circumferential or running surface, which is asymmetric in relation to the first, is suitable for interacting with a sliding rail during "pushing" operation.
4. Drive according to Claim 1 or 3, characterized in that the asymmetric eccentric cam disc (47) is designed for operating a swing door in addition to operating a swivel door, one asymmetric circumferential-surface region (65a) being active when the swing door is opened in one direction and the second circumferential-surface region (65b) being active when the swing door is opened in the other direction.
5. Drive according to one of Claims 1 to 4, characterized in that the drive can be used as a direct drive in the case of which the output shaft (9) is preferably connected to a leaf spindle.
6. Drive according to one of Claims 1 to 5, characterized by the following features:

   - the energy-store device (43) is arranged such that its longitudinal axis or direction of action passes by the output or intermediate shaft (9), on which the eccentric cam disc (47) is seated, at a distance therefrom,

   - there is provided a transmission device (45), via which the energy-store device (43) subjects the contact-pressure member or the contact-pressure roller (63) to pressure.
7. Drive according to Claim 6, characterized in that the transmission device (45) comprises a transmission gear mechanism which preferably provides for transmission towards higher forces.
8. Drive according to Claim 6 or 7, characterized in that the transmission device (45) comprises a lever or lever mechanism (57).
9. Drive according to one of Claims 6 to 8, characterized in that the transmission device (45) comprises a double lever or a rocker (57a), preferably in the manner of a shift lever.
10. Drive according to one of Claims 6 to 9, characterized in that the transmission device (45) comprises a single lever (57b), preferably in the manner of a shift lever.
11. Drive according to one of Claims 1 to 10, characterized in that provided at one of the opposite force-application points of the energy-store device (43) is an adjusting device (71), via which the active forces can be adjusted manually.
12. Drive according to Claim 11, characterized in that the adjusting device (71) comprises an adjusting member, preferably in the form of an adjusting screw (73), via which it is possible to change the position of a force-application surface, preferably in the form of a stop (53).
13. Drive according to one of Claims 1 to 12, characterized in that the energy-store device (43) comprises a pressure-exerting device, preferably a helical spring (43').
14. Drive according to one of Claims 1 to 13, characterized in that the energy-store device (43) preferably comprises a tension spring, preferably in the form of a helical spring (43').
15. Drive according to one of Claims 6 to 10, characterized in that the transmission device (45) is constructed such that it can be used to provide for force transmission to higher contact-pressure forces in the direction of the eccentric cam disc.
16. Drive according to one of Claims 6 to 10 or 15, characterized in that the energy-store device (43) is supported, by way of its one stop (51), adjacent to the drive unit (25), preferably adjacent to the electric motor (25a).
17. Drive according to one of Claims 6 to 10 or 15, 16, characterized in that the energy-store device (43) formed in the manner of a helical spring (43') has its axial direction extending parallel to the axial direction of the electric motor (25a).
18. Drive according to one of Claims 7 to 10 or 15 to 17, characterized in that the gear-mechanism unit (31) has its longitudinal axis extending parallel to the electric motor (25a) and/or parallel to the longitudinal axis of the energy-store device (43) or of the helical spring (43'), the gear mechanism (33) being arranged parallel to the energy-store device or the helical spring (43').
19. Drive according to one of Claims 6 to 10 or 15 to 18, characterized in that the helical spring (43'), the eccentric cam disc (47) and the lever-type transmission mechanism (57; 57a, 57b) are arranged such that a cross-sectional plane which passes through the eccentric cam disc (47) transversely to the output or intermediate shaft (9) coincides with a cross-sectional plane which passes through the lever mechanism (57; 57a, 57b) transversely to the associated tilting spindle (59), and in that, in this common cross-sectional surface, the central axis ends up extending through the energy-store device (43) or the helical spring (43').

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