EP3095942B1 - Pivoting door driving device - Google Patents

Description

The invention relates to a rotary door drive device 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.

Such swing door operators are often used in public buildings. The swing door drive device should be constructed as compact as possible, so that it can be integrated or mounted in or on the door frame, without that they dominate the appearance of the entrance area. Depending on the width and weight of the door and the length of time in which the swing door drive device to open and close the door, high forces are needed. Such high forces can not be applied by an electric motor within the swing door drive mechanism alone when directly connected to the swing lever of the rotary wing. Therefore, gears are often used, which are coupled to the electric motor.

From the DE 103 52 167 A1 an actuator for actuating a tailgate of a motor vehicle is known. In this is driven by a drive sun gear with a planet gear in engagement, wherein a first axis about which the sun gear is rotatably mounted and a second axis on which the planet gear is rotatably mounted, at their ends facing away from the drive in a common web are movably arranged and spaced from each other constantly. The planet gear engages in a stationary connected to the body gear segment. The gear rim segment facing the end of the web is movably connected via a third axis with a connecting rod, the end facing away from the third axis is movably connected via a fourth axis with an output element. The output element is connected with its fourth axis facing away from the tailgate. DE-A1-10352167 discloses the features of the preamble of claim 1. An electromechanical rotary vane drive is from the DE 21 2011 100 093 U1 known. The rotary wing of a swing door is driven by an electric motor, which has a transmission. In addition, there is still a gear ratio stage, which has a first drive wheel and a second drive wheel. Both drive wheels may be formed, for example, as gears and are engaged with each other. The rotary wing engages with a driving pin, which has contact with the gear ratio stage. As a result, the pivoting of the rotary wing takes place. A disadvantage of the DE 21 2011 100 093 U1 is that the structure with a plurality of movable gears is complicated and relatively large forces when opening or closing act on the rotary vane drive.

It is therefore an object of the invention to provide a swing door drive device, which allows a compact design and is loaded only with small forces when opening or closing the rotary wing of the swing door.

The object is achieved by the inventive swing door drive device according to the independent claim 1. Advantageous developments of the swing door drive device according to the invention are specified in the subclaims.

The swing door operator according to the invention comprises an electric motor with a motor shaft and a pivot lever which is pivotable about a pivot lever pivot axis. The pivot lever is connected at its free end with a sliding rail attached to the rotary or with a second lever attached to the rotary wing to form a toggle lever for opening the rotary wing or connectable. The electric motor is connected via a subsequent power transmission device with the pivot lever in operative connection, so that a rotation of the motor shaft of the electric motor has a pivoting of the pivot lever about its pivot lever pivot axis and thus a pivoting of the rotary wing result. The power transmission device comprises a sun gear and a planet gear. The planet gear is by means of a forced operation solely in at least one pitch circle along a side peripheral surface of the sun gear movable, wherein the teeth of the planetary gear mesh with the teeth of the sun gear. The planet gear is rotatably mounted with the pivot lever at an offset to the pivot lever pivot axis attack point. The planetary gear is operatively connected to the motor shaft of the electric motor such that rotation of the motor shaft causes rotation of the planetary gear on the side peripheral surface of the sun gear and thus unwinding of the planetary gear on the toothing of the sun gear Driving and pivoting of the pivot lever causes the pivot lever pivot axis. Advantageously, the use of a planetary gear and a sun gear, wherein the sun gear is fixed and immovable. The planetary gear is held by the positive guide so that it rolls on its rotation on the sun gear and is always in contact with this. An introduction of force into the planetary gear causes, due to an offset to the pivot axis of the pivot lever attack point, a lever, so that only relatively small forces when opening or closing act on the swing door drive device. The use of a sun gear and a planetary gear that can be moved around it also achieves high positioning accuracy. At the same time the swing door drive device according to the invention is very quiet. The planetary gear is at the point of attack on the pivot lever fixed but rotatably mounted and arranged the pivot lever pivot axis coincides with a center of the sun gear passing through the central axis. The power transmission device additionally has a guide lever pivotable about a guide lever pivot axis, and the guide lever pivot axis of the guide lever coincides with a center axis of the sun gear passing through the central axis, wherein the guide lever is rotatably mounted on the planet gear. This ensures that the planetary gear can only move in a circular path around the sun gear and is constantly with its teeth in engagement with the teeth of the sun gear.

The drive of the planet gear is done in different ways. Used is a first pulley, which is driven by the motor shaft. An axle body preferably extends from the center of the sun gear in at least a first direction and preferably coincides with the pivot lever pivot axis. In a first case, the axle body is rotatably mounted on the sun gear and a second deflection roller is rotatably mounted on the axle body and connected thereto. A third deflection roller is axially spaced from the second deflection roller also rotatably disposed on the axle body. In a second case, the axle body is rotatably anchored to the sun gear, in which case a second deflection roller is rotatably arranged on the axle body and wherein a third deflection roller axially spaced from the second deflection roller is also rotatably mounted on the axle body. The second pulley and the third pulley must, however, then be rotationally coupled so that they can not rotate relative to each other. In addition, a fourth deflection roller is necessary in both cases. This can either be arranged non-rotatably on an output shaft, wherein the output shaft is in turn rotatably mounted on the planetary gear. The fourth deflection roller can additionally or alternatively also be coupled directly against rotation to the planet gear. Further, a first power transmission means and a second power transmission means are necessary, wherein the first power transmission means interconnect the first and second power transmission idlers, and wherein the second power transmission means interconnects the third and fourth power transmission idlers.

Furthermore, it is advantageous if the planet gear and the output shaft are integrally formed, or if the planetary gear and the output shaft are formed in several parts, wherein the planetary gear in this case has a continuous receiving opening, which passes completely through the output shaft is.

In order to achieve a power transmission from the fourth deflection roller to the planetary gearwheel, these may comprise, for example, at least one fastening pin which engages in a corresponding attachment opening of the respective counterpart, whereby the planet gear and the fourth deflection roller are rotationally coupled.

The axle body additionally extends from the center of the sun gear in a second direction which is opposite to the first direction. The axle body also runs along the central axis, which preferably coincides with the pivot lever pivot axis. The pivot lever is pivotally mounted with its pivot lever pivot axis on the part of the axle body, which extends in the second direction. In addition and as an alternative, the guide lever with its guide lever pivot axis can also be mounted on the axle body. This is preferably pivotally mounted on the part of the axle body which extends in the first direction. The guide lever is in this case only, or predominantly for guiding the planetary gear and not for power transmission. The axle body can either be formed in one piece or in two parts. In the latter case, a first part of the axle body extends in the first direction and a second part of the axle body in the second direction. The first part or the second part may either be rotatably anchored or rotatably mounted on the sun gear. The type of attachment may differ from each other from the first or second part.

The center of the sun gear is not necessarily the part where the center of gravity lies. Rather, the center of the sun gear is always equidistant from the toothed side peripheral surface of the sun gear on which the planet gear is unrolled.

At the point of attack, on which the planet gear is rotatably mounted on the pivot lever, it may be, for example, a recess within the pivot lever or a projection on the pivot lever. In the former case, the planet gear engages with a part of its toothed peripheral surface directly into the recess and is rotatably mounted in this. It is also possible for a projection to be formed on the planetary gearwheel, that is to say extended in the direction of the pivoting lever, wherein this projection, which is preferably not toothed, is rotatably mounted within the recess. It is also possible that the output shaft completely passes through the planet gear and engages in the recess, wherein the output shaft is rotatably mounted within the recess. In the event that it is at the point of attack to a projection which is formed on the pivot lever, an opening must preferably be formed in the center of the planetary gear in which engages this projection.

It is also possible that the planetary gear is extended at least in the direction of the pivot lever by means of an extension element. This extension element may in the simplest case be a sleeve which engages in a projection of the planet gear and in a projection of the pivot lever, wherein both projections are rotatably mounted within the sleeve.

In order to additionally increase the leverage and increase the torque acting on the pivot lever, in addition to the diameter of the sun gear and the planet gear and the diameter of the first and second guide roller, and the third and fourth guide roller can be changed. In this case, the diameters of the first and second, or third and fourth deflection roller may be the same or different. As a result, various translations are possible. The diameter of each pulley can vary depending on the dimensions the swing of the swing door to be customized by a corresponding pulley is used.

The first and second, and third and fourth pulley is either a pulley or a gear. The first and second power transmission means are preferably a toothed belt or a chain, or even more gears that connect the first deflection roller with the second deflection roller, or the third deflection roller with the fourth deflection roller for transmitting power. All these power transmission means have in common that the first guide roller can not rotate relative to the second guide roller, and that the third guide roller also can not rotate relative to the fourth guide roller. This means that as soon as a deflection roller is rotated, the rotation of the further deflection roller takes place. The first and the second deflection roller, as well as the third and the fourth deflection roller, arranged without slip to each other.

Preferably, in the swing door drive device still an energy storage unit is formed, which comprises a cam unit consisting of at least two superimposed cams. The cam unit is rotatably mounted on the pivot lever and the cross-sections of the individual cams differ in plan view partially or completely from each other. The cam unit serves to ensure that the swing door can also be closed without power. For this purpose, on one of the various cams a prestressed rope or band one Force storage unit attached. This can be done for example with a fastening anchor, so a rope Bride. On the cam and a preloaded coil spring can be attached. As a result, a force is exerted on the pivot lever, which ensures a closing of the rotary wing of the swing door even without the use of the electric motor. The changing diameter of the cam causes depending on the rotational position of the swing door, the rope or the band, or an end of the prestressed coil spring at a different distance to the pivot lever pivot axis acts on this, whereby the torque is increased, especially in the position of the rotary wing in which he falls into the castle.

Each cam is preferably separated from the respective adjacent cam by a cutting disc, which has predominantly a larger diameter than the cam, whereby a guide channel for the rope or the band or a part of the coil spring is formed.

Each cam is penetrated by connecting holes through which a connecting pin or a connecting rivet is inserted, whereby the at least two cams are connectable or connected to the cam unit. The connection openings are arranged symmetrically such that each cam also forms the cam unit with the at least one other cam, with the introduction of the connecting pins or connecting rivets and the cutting discs, even if the underside of a cam is turned upwards or the cam itself rotated becomes. Due to the plurality of cams and the ability to connect them in any orientation to the cam unit, a cam unit is suitable for a variety of different swing doors. Depending on the weight of the door, the appropriate cam can be selected in their orientation during assembly, so that the swing door safely closes even when de-energized.

The pivot lever pivot axis of the pivot lever preferably extends through the center of the cam unit. The sun gear is also fixed and immovable, as its name suggests. The sun gear has a larger diameter than the planet gear. The sun gear extends over less than 360 °, preferably less than 270 °, more preferably less than 200 °, more preferably less than 180 °, more preferably less than 150 °, even more preferably less than 120 ° and is designed as a gear segment. The fact that the sun gear does not rotate and this is arranged stationary, the background noise in the operation of the swing door drive device is further reduced. Depending on the extent to which the rotary wing of the swing door to be opened, the sun gear may be formed as a more or less large gear segment and does not have to be performed completely round and his side peripheral surface must not be completely dented. As a result, the production costs can be further reduced.

Figur 1A:

eine räumliche Darstellung der erfindungsgemäßen Drehflügeltürantriebsvorrichtung bei geöffnetem Gehäuse, die mit einer Gleitschiene in Kontakt steht;

Figur 1B:

eine weitere räumliche Darstellung der erfindungsgemäßen Drehflügeltürantriebsvorrichtung bei geöffnetem Gehäuse, die mit einer Gleitschiene in Kontakt steht;

Figur 2:

eine räumliche Darstellung der erfindungsgemäßen Drehflügeltürantriebsvorrichtung in Explosivdarstellung;

Figuren 3A, 4A, 5A:

eine vereinfachte Darstellung der erfindungsgemäßen Drehflügeltürantriebsvorrichtung in Draufsicht, wobei der Schwenkhebel verschieden stark verschwenkt ist;

Figuren 3B, 4B, 5B:

eine weitere vereinfachte Darstellung der erfindungsgemäßen Drehflügeltürantriebsvorrichtung in Draufsicht, wobei der Schwenkhebel verschieden stark verschwenkt ist und wobei der Drehflügel sichtbar ist;

Figuren 6A,

6B: eine räumliche und eine seitliche Darstellung einer Kraftspeichereinheit der erfindungsgemäßen Drehflügeltürantriebsvorrichtung, die aus einer Feder und einer Kurvenscheibeneinheit besteht, die an dem Schwenkhebel angeordnet sind;

Figur 7:

eine seitliche Darstellung der Kurvenscheibeneinheit;

Figuren 8A - 8D:

verschiedene Kurvenscheiben, die übereinander angeordnet die Kurvenscheibeneinheit bilden; und

Figuren 9A - 9C:

eine räumliche und eine seitliche Darstellung und eine Draufsicht auf die Kraftspeichereinheit der erfindungsgemäßen Drehflügeltürantriebsvorrichtung, die aus der Feder und der Kurvenscheibeneinheit besteht, die an dem Schwenkhebel angeordnet sind.

Various embodiments of the invention will now be described by way of example with reference to the drawings. Same objects have the same reference numerals. The corresponding figures of the drawings show in detail:

FIG. 1A

a three-dimensional view of the swing door drive device according to the invention with the housing open, which is in contact with a slide rail;

FIG. 1B

a further three-dimensional view of the swing door drive device according to the invention with the housing open, which is in contact with a slide rail;

FIG. 2:

a spatial representation of the swing door drive device according to the invention in an exploded view;

FIGS. 3A, 4A, 5A:

a simplified representation of the swing door drive device according to the invention in plan view, wherein the pivot lever is pivoted different degrees;

FIGS. 3B, 4B, 5B:

a further simplified representation of the rotary door device according to the invention in plan view, wherein the pivot lever is pivoted different degrees and wherein the rotary wing is visible;

FIGS. 6A,

6B: a spatial and a lateral representation of an energy storage unit of the rotary door drive device according to the invention, which consists of a spring and a cam unit, which are arranged on the pivot lever;

FIG. 7:

a side view of the cam unit;

FIGS. 8A-8D:

various cams which, when arranged one above the other, form the cam unit; and

FIGS. 9A-9C:

a spatial and a side view and a plan view of the power storage unit of the invention of the swing door drive device consisting of the spring and the cam unit, which are arranged on the pivot lever.

Figure 1A shows a three-dimensional view of the swing door drive device 1 according to the invention with the housing open, which is in contact with a slide rail 2. Within the swing door drive device 1, an electric motor 3 is formed, at the motor shaft, a transmission 4 is connected. The transmission 4 is an angular gear, in particular a worm gear. Other types of transmissions are also possible, such as a bevel gear. A pivot lever 5, which is pivotable about a pivot lever pivot axis 6, is also arranged. The pivot lever 5 is connected at its free end 7 with a fixed to the rotary wing 8 slide rail 2. At its free end 7 is in the embodiment Figure 1A a driving pin 8 rotatably mounted on the pivot lever 5. At the driving pin 8, a carriage 9 is further arranged, on which the driving pin 8 is also preferably rotatably mounted. The carriage 9 is movable in the slide rail 2 back and forth.

In the embodiment Figure 1A takes place the installation of the swing door drive device 1 in the manner of a so-called "head assembly" in the functional position "slide rail 2 pulling", being pulled when opening the rotary wing 8 via the pivot lever 5 of the rotary wing 8 in the open position. It would of course also be possible that this works exactly the other way round, ie that a head assembly of the swing door drive device 1 in the functional position "slide 2 pushing" takes place, in which for opening the rotary wing 8 of the pivot lever 5 "pushes" the rotary wing 8.

In this context, it should be mentioned that the pivot lever can also be connected together with a second lever to form a toggle lever for opening the rotary wing 8.

The electric motor 3 is connected via a power transmission device 9 with the pivot lever 5 in operative connection, so that a rotation of the motor shaft of the electric motor 3, a pivoting of the pivot lever 5 about its pivot lever pivot axis 6 and thus has a total pivoting of the rotary wing 8 result.

To the power transmission device 9 includes a sun gear 10 and a planet gear 11. The planetary gear 11 is movable by means of a positive guide 12 only in at least one pitch along a side peripheral surface 13 of the sun gear 10, wherein the teeth of the planet -Zahnrads 11 engage the teeth of the sun gear 10. The planet gear 11 therefore moves in a circular path along the sun gear 10th

The sun gear 10 is fixed and immovable. It may be attached to a base plate 14, which in turn is mounted on a building wall 15. The sun gear 10 does not have to be round. It preferably extends over less than 360 °, preferably over less than 270 °, more preferably over less than 200 °, more preferably over less than 180 °, more preferably over less than 150 °, even more preferably over less than 120 ° and thereby formed as a gear segment. Characterized in that the sun gear 10 does not have on its entire side peripheral surface 13 teeth, but as in the illustrated embodiment Figure 1A consists of a half gear, it can be very easily attached with its non-dented portion of the side peripheral surface 13 on the base plate 14. The sun gear 10 also preferably has a larger diameter than the planet gear 11. The diameter of the sun gear 10 is preferably more than twice as large, more preferably more than three times as large, more preferably more than four times as large as the diameter of the planet gear 11th

The planetary gear 11 is rotatably mounted with the pivot lever 5 at an offset to the pivot lever pivot axis 6 attack point 16. This ensures that the pivot lever is automatically pivoted when the planet gear 11 rolls on the sun gear 10.

The planet gear 11 is as part of the power transmission device 9 with the motor shaft of the electric motor 3 in operative connection, that the rotation of the motor shaft rotation of the planetary gear 11 on the side peripheral surface 13 of the sun gear 10 and thus a rolling of the planet -Zahnrads 11 causes the teeth of the sun gear 10 under entrainment and pivoting of the pivot lever 5 about the pivot lever pivot axis 6.

The planet gear 11 is not driven directly by the motor shaft of the electric motor 3, but via the power transmission device 9. To the power transmission device 9 includes four pulleys 20, 21, 22, 23. A first guide roller 20 is driven by the motor shaft. The first guide roller 20 is either rotatably connected directly to the motor shaft, or it surrounds for the case that is coupled to the electric motor 2, a transmission 4, the transmission 4 leaving the drive train and is rotatably connected thereto. The rotation of the motor shaft therefore causes a rotation of the first guide roller 20th

The second deflecting roller 21 is disposed on an axle body 25 extending from the center of the sun gear 10 in at least a first direction. The center of the sun gear 10 is penetrated by the pivot lever pivot axis 6.

The axle body 25 may either be rotatably mounted on the sun gear 10 or it may be rotatably connected thereto, preferably anchored. In the event that the axle body 25 is rotatably mounted on the sun gear 10, the second guide roller 21 is rotatably mounted on the axle body 25. In the event that the axle body 25 is rotatably anchored to the sun gear 10, the second guide roller 21 is rotatably mounted on the axle body 25. For power transmission, a first force transmission means 26 is arranged between the first deflection roller 20 and the second deflection roller 21. In the illustrated embodiment of Figure 1A, the first power transmission means 26 is a timing belt. Such a toothed belt causes a rotation of the first guide roller 20 has a rotation of the second guide roller 21 result. The two pulleys 20, 21 are thus connected without slip. In this case, the first and second pulleys 20, 21 are pulleys. It would also be possible for the first and second deflection pulleys 20, 21 to be toothed wheels, with a chain extending between the two toothed wheels as first force transmission means 26. Incidentally, it would also be conceivable that between the first and second deflection rollers 20, 21 in the form of a gear at least one further, preferably a plurality of further gears are arranged, via which the power transmission takes place.

At the axle body 25 is still a third guide roller 22 is arranged, which is axially spaced from the second guide roller 21 is attached thereto. In the embodiment Figure 1A the third pulley 22 is disposed closer to the sun gear 10, as the second pulley 21. The opposite would also be possible.

In the event that the axle body 25 is rotatably mounted on the sun gear 10, the third guide roller 22 is rotatably disposed thereon. In the opposite case, that is, when the axle body 25 is anchored rotationally fixed to the sun gear 10, the third guide roller 22 is rotatably mounted on the axle body 25. Thus, the second guide roller 21 and the third guide roller 22 are further rotationally coupled, so they can not be rotated relative to each other, both pulleys 21, 22 still be connected to each other. This can be done for example by pins that pass through both pulleys 21, 22 or by a projection in one or both pulleys 21, 22, or engage in an opening or in openings of the respective adjacent pulley 21, 22. It may also be that both pulleys 21, 21 are glued together, or that both pulleys 21, 22 are integrally formed. A combination of these possibilities is also possible.

The fourth guide roller 23 is rotationally coupled to the planetary gear 11. It is also possible for the fourth deflection roller 23 to be arranged on an output shaft 27 which, in turn, is rotationally coupled to the planetary gear 11. The fourth guide roller 23 In this case it is also rotationally coupled to the output shaft 27.

The planet gear 11 and the output shaft 27 may be integrally formed.

As will be explained later, it is also possible that the planet gear 11 and the output shaft 27 are formed in several parts.

A second power transmission means 28 interconnects the third and fourth pulleys 22, 23 for power transmission. The third and fourth guide rollers 22, 23 may be a pulley or gears, the second transmission means 28 preferably being a toothed belt or a chain. It is also possible to arrange further toothed wheels between the third and the fourth deflection rollers 22, 23 as a force transmission means 28.

In the event that a slip detection is ensured, instead of a toothed belt or a chain and a normal V-belt can be used.

The diameter of the pulleys 20, 21, 22, 23 can be chosen arbitrarily and be different.

FIG. 1B shows a further graphical representation of the swing door drive device 1 according to the invention with the housing open, which is in contact with a slide rail 2. The first guide roller 20 is connected to the second guide roller 21 via the power transmission means 26 in the form of a toothed belt. The pivot lever pivot axis 6 passes through the center of the planet gear 11 and passes through the axle body 25. The pivot lever pivot axis 6 extends through the center of the second guide roller 21 and the third guide roller 22. The pivot lever pivot axis 6 is arranged stationary. In contrast, the planet gear 11 moves around the sun gear 10 in a circle. The axis of rotation of the planet gear 11 is arranged parallel to the pivot lever pivot axis 6, but does not coincide with this.

Within FIG. 1B is a forced operation 12 of the planetary gear 11 can be seen. The positive guide 12 of the planetary gear 11 on the sun gear 10 is effected in that the planetary gear 11 is arranged at the point of action 16 on the pivot lever 5 fixed but rotatably mounted. The pivot lever pivot axis 6 coincides with a center of the sun gear 10 passing through the central axis. This means that the planet gear 11 can not move away from the sun gear 10 over the entire pivoting range of the pivot lever 5. In particular, the planet gear 11 can not descend to the "bottom", that is to say in the direction of the ground, because, although it is rotatably mounted on the point of action 16, it is also supported by it. The planet gear 11 can also be stored at the point of attack 16 so that it can not be "up", ie away from the slide 2, moved. After "outside", so for example radially outward, the planetary gear 11 can not remove, because it is held by the pivot lever 6 at the point of attack 16.

In the embodiment FIG. 1B is still to see an energy storage unit 30 having a cam unit 31 and a spring 32, in particular a tension spring. A compression spring could also be used. The power storage unit 30 serves to ensure that the rotary vane 8 closes safely even in currentless operation. The cam unit 31 is rotatably mounted on the pivot lever 5. The cam unit 31 is connected to a cable 33 or a band, which is preferably a steel cable or a steel band, with the spring 32 connected thereto biased. It is also possible that one end of the spring 32, which may be, for example, a coil spring, is connected directly to the cam unit 31. In particular, just before the rotary wing 8 falls into the lock, it is ensured by the force storage unit 30 that an additional torque is applied to the pivot lever 5, whereby the closing operation is supported. This situation is described in detail in the other drawings.

FIG. 2 shows a three-dimensional view of the swing door drive device 1 according to the invention in an exploded view. The individual deflection rollers 20, 21, 22, 23 have different diameters. The positive guide 12 of the planetary gear 11 on the sun gear 10 is additionally effected by means of a guide lever 35 whose guide lever pivot axis coincides with the pivot lever pivot axis 6 and in particular extends through the center of the sun gear 10 therethrough. The guide lever 35 is therefore preferably rotatably mounted on the axle body 25, which extends from the center of the sun gear 10 in the at least one first direction extends. The other end of the guide lever 35 is rotatably mounted on the planet gear 11 and on the output shaft 27. This prevents the planet gear 11 from losing contact with the sun gear 10.

The planet gear 11 and the output shaft 27 are formed in several parts in this case, wherein the planet gear 11 has a continuous receiving opening, which is completely penetrated by the output shaft 27. Since planetary gear 11 has at least one fastening pin 36 which engages in a corresponding mounting hole in the fourth guide roller 23, whereby the planet gear 11 and the fourth guide roller 23 are rotationally coupled. It is also possible that the at least one fastening pin 36 is additionally or alternatively arranged solely in the fourth deflection roller 23 and engages in a fastening opening within the planet gear 11.

The axle body 25 additionally extends from the center of the sun gear 10 in a second direction, which is opposite to the first direction where the second and third guide rollers 21, 22 are arranged. This part of the axle body 25 extends along the central axis, ie along the pivot lever pivot axis 6. The pivot lever 5 is pivotally mounted with its pivot lever pivot axis 6 on this part of the axle body 25 which extends in the second direction. In this case, the axle body 25 is formed in two parts, wherein the first part of the axle body 25 extends in the first direction and wherein the second part axle body 25 extends in the second direction. Both parts the axle body 25 are rotatably mounted in the center on the sun gear 10 in this embodiment. As already explained, it is also possible that the axle body 25 is formed in one piece and is rotatably anchored in the center with the sun gear 10. A rotationally fixed anchoring is also possible if the axle body 25 is formed in two parts.

The first part of the axle body 25 is longer than the second part of the axle body 25.

Within the embodiment of FIG. 2 the planet gear 11 is extended in the direction of the pivot lever 5 by means of an extension member 37. The planet gear 11 is rotatably or non-rotatably connected to the extension member 37, wherein the extension member 37 in turn rotatably or rotatably connected to the pivot lever 5. In this embodiment, the pivot lever 5 has a projection, not shown, which engages in the extension member 37, which has the shape of a sleeve, wherein the planet gear 11 also has a projection, not shown, which also engages in the extension member 37. As a result, the planet gear 11 is rotatably mounted on the pivot lever 5, wherein the pivot lever 5 is taken along by the rolling of the planetary gear 11 along the side peripheral surface 13 on the sun gear 10, whereby a pivoting of the pivot lever 5 is triggered. The carriage 9 moves along the slide rail 2, whereby the rotary wing 8 is opened or closed.

The cam unit 31 has a continuous slot in the axial direction which engages with a pin which is fixedly connected to the pivot lever 5. This ensures that the cam unit 31 is rotatably connected to the pivot lever 5. The cam unit 31 may also have a continuous recess which is completely penetrated by the second part of the axle body 25. In this case, the second part of the axle body 25 passes completely through the cam unit 31 and is furthermore mounted in a recess within the pivot lever 5. It is also possible that the second part of the axle body 25, the cam unit 31 is not completely penetrated but ends within the recess. In this case, the pivot lever 5 is rotatably connected to the cam unit 31, which in turn is mounted on the second part of the axle body 25. This ensures that the pivot lever pivot axis 6 does not move away from the center of the sun gear 10.

The energy storage unit 30 in turn has a spring 32 and a cable 33, or a band, which is in contact with the cam unit 31, as will be explained in more detail in the further drawing figures.

The first power transmission means 26 is not pivotable in contrast to the second power transmission means 28. The second power transmission means 28 is also, as the guide lever 35 in a circular path, pivoted by rotation of the planetary gear 11. The second power transmission means 28 and the guide lever 35 are axially spaced from each other but arranged congruently one above the other.

The FIGS. 3A . 4A and 5A show a simplified representation of the swing door drive device 1 according to the invention in plan view, wherein the pivot lever 5 is pivoted different degrees. This means that the planet gear 11 engages at different locations on the side peripheral surface 13 of the sun gear 10. Within FIG. 3A the rotary vane 8 is closed and the planet gear 11 is located at a first position on the sun gear 10. The first and second power transmission means 26, 28 are aligned approximately parallel.

Within FIG. 4A the electric motor 3 by means of the pulleys 20, 21, 22, 23 and the two power transmission means 26, 28, the planetary gear 11 is driven and this is to a certain extent already on the side peripheral surface 13 of the sun gear 10 unrolled, stands with but this still engaged. The pivot lever 5 has therefore been pivoted about its pivot lever pivot axis 6, which results in that the carriage 9, which is fixed to one end of the pivot lever 5, is displaced within the slide rail 2, whereby the rotary wing 8 is opened a little.

Within FIG. 5A the pivot lever 5 has been pivoted so far that the rotary wing 8 is fully open. In this case, the rotary wing 8 is pivoted by 90 °. The planet gear 11 is in this case in a second position on the sun gear 10 at.

Between the first position where the rotary wing 8 is fully closed and the second position where the rotary wing 8 is fully opened, the planetary gear 11 is unrolled on the side peripheral surface 13 of the sun gear 10 and stands between them Positions constantly engaged with the teeth of the sun gear 10.

The FIGS. 3B . 4B . 5B show a further simplified representation of the swing door drive device 1 according to the invention in plan view, wherein the pivot lever 5 is pivoted different degrees. In contrast to the FIGS. 3A . 4A . 5A show the FIGS. 3B . 4B . 5B additional details, such as the rotary wing 8 and illustrate how the carriage 9, which is rotatably mounted at one end of the pivot lever 5 and is in engagement with the slide rail 2, is moved over these two different opening positions of the rotary wing 8. Also shown is an energy storage unit 30, which has a spring 32 and a cam unit 31.

The FIGS. 6A and 6B show a spatial and a lateral representation of the power storage unit 30 of the rotary door drive device 1 according to the invention, which consists of a spring 32 and a cam unit 31.

A first end 40 of the spring 32 is firmly anchored to the base plate 14 and / or on the housing wall 15. a second end 41 is connected to the cam unit 31 by means of the cable 33. The cam unit 31 is in turn rotatably mounted on the pivot lever 5 and anchored thereto. The cam unit 31 preferably has a receiving opening into which the second part of the axle body 25 protrudes. The second part is the part which extends in the second direction, ie away from the deflection rollers 21, 22. The axis of rotation of the cam unit 31 preferably coincides with the pivot lever pivot axis 6 of the pivot lever 5.

The second part of the axle body 25 can completely penetrate the cam unit 31, or come to rest within it.

The cam unit 31 is composed of at least two cam plates 42 _1, 42 ₂ ... 42 _n are _n by cutting discs 43 _1, 43 _2, ..., 43 separated from each other. The cutting discs 43 ₁ , 43 ₂ , ..., 43 _n are arranged on each of the end faces of the cam discs 42 ₁ , ..., 42 _n . Between two cams 42 ₁ , ..., 42 _n , however, there is only one cutting disc 43 ₁ ,..., 43 _n . The cutting discs 43 ₁ ,..., 43 _n have predominantly a larger diameter than the cam discs 42 ₁ ,..., 42 _n . This means that there may well be areas where the distance from a point on the side peripheral surface to the center of the cam 42 ₁ , ..., 42 _{n is the} same as the distance of a point on the side peripheral surface towards the center of the cutting wheel 43 ₁ , ..., 43 _n . Predominantly, however, the distance from the side circumferential surface of a cam 42 ₁ , ..., 42 _n toward its center is smaller than the distance from the side peripheral surface of a blade 43 ₁ , ..., 43 _n towards its center , This will create a guide channel for each cam 42 ₁ , ..., 42 _n formed, in which the rope 33 or a band or a part of a coil spring can be inserted and guided. Within the drawing figures 6A and 6B, a cable 33 is arranged in a guide channel. At least one or each cam 42 ₁ , ..., 42 _n includes a fastening anchor (rope-Bride), at the end of the prestressed rope or the band, which is connected at its other end to the spring 32, fastened or attached. By the prestressed spring 32, a force is transmitted to the cam disk 42 ₁ ,..., 42 _n via the cable 33 or the belt, by which in turn a torque is generated which assists in closing the rotary vane 8.

FIG. 7 shows a side view of the cam unit 31. The cross sections of the individual cams 42 ₁ , ..., 42 _n differ in plan view partially or completely from each other. The cutting discs 43 ₁ ,..., 43 _n preferably have the same cross section.

The FIGS. 8A to 8D show various cams 42 ₁ , ..., 42 _n , which are arranged one above the other, the cam unit 31 form. Each cam 42 ₁ , ..., 42 _n is penetrated by connecting openings 44 through which a connecting pin or a connecting rivet is inserted or inserted. Thereby, it is possible that at least two cam plates 42 _1, 42 ₂ ... 42 _n together with the respective blades 43 _1, ..., 43 _n to the cam unit 31 can be connected or are connected. It should be noted that the connecting openings 44 are preferably arranged symmetrically such that each cam 42 ₁ , ..., 42 _n then with the at least one another cam plate 42 ₁ , ..., 42 _n and the respective cutting disc 43 ₁ , ..., 43 _n with introduction of the connecting pins or connecting rivets, the cam unit 31 forms when the bottom of a cam 42 ₁ , ..., 42 _n after turned up. This is true even if the cam 42 ₁ , ..., 42 _n only rotated, preferably in 90 ° increments is rotated. For example, it is the cams 42 ₁ , ..., 42 _n , which in the Figures 8A and 8D are shown to the same cams 42 ₁ , ..., 42 _n , wherein the cam has been reversed once. The connecting openings 44 are preferably arranged symmetrically around the recess into which the second part of the axle body 25 is inserted. The cam unit 31 additionally has a mounting opening 45, which preferably fully penetrates the cam unit 31 in the axial direction. The attachment opening 45 is preferably formed on the edge of the cam unit 31 and accessible from the outside, that is from the side peripheral surface of the cam unit 31. In this attachment opening 45 preferably engages a projection or a pin which is rotatably anchored to the pivot lever 5 or rotatably mounted on this. This ensures that the cam unit 31 is rotatably mounted on the pivot lever 5. The attachment opening 45 preferably passes through all the cutting discs 43 ₁ ,..., 43 _n and possibly also one or more cam discs 42 ₁ ,..., 42 _n .

Each cam 42 ₁ , ..., 42 _n is designed such that the distance from the side peripheral surface towards the center of the cam 42 ₁ , ..., 42 _n , ie towards the recess through which the second part of the axle body 25 led is different. When the pivot lever 5 is pivoted by the planet gear 11 in its axis of rotation 6, the cam 42 ₁ , ..., 42 _n taken and also pivoted about the pivot lever rotation axis 6. A cable 33, which is biased by a spring 32 and connected to one of the cams 42 ₁ , ..., 42 _n , thereby comes at different points with the side peripheral surface of the respective cam 42 ₁ , ..., 42 _n in contact. Depending on the distance of these points to the axis of rotation, a different high torque to the cam 42 ₁ , ..., 42 _n and thus transferred to the pivot lever 5. A greater distance between the side peripheral surface toward the axis of rotation at the point where the rotary wing 8 falls into the lock ensures that a higher force acts on the pivot lever 5, whereby the rotary wing 8 securely falls into the lock.

The use of a plurality of cams 42 ₁ ,..., 42 _n allows "standard cams 31" suitable for a plurality of rotary blades 8 to be used. The cable 33 is simply attached to the appropriate cam 42 ₁ , ..., 42 _n or the respective cam 42 ₁ , ..., 42 _n or the entire cam unit 31 are rotated to place a right-handed a left-turning swing door in the closing process to support. This facilitates assembly.

The FIGS. 9A to 9C show a spatial and a lateral view and a plan view of the power storage unit 30 of the rotary door drive device 1 according to the invention, which consists of the spring 32 and the cam unit 31, which on the pivot lever 5 are arranged. The rope 33 will, as in Figure 9A shown to the appropriate cam 42 ₁ , ..., laid 42 _n and fastened with a fastening anchor 47, that is a so-called rope Bride. The fastening anchor 47 can be, for example, the projection or the pin which is formed on the pivot lever 5. Within Figure 9A are the cam unit 31 in one piece and the pivot lever 5 integrally formed. However, it is also possible that the cam unit 31 and the pivot lever 5 are formed in several parts. The second part of the axle body 25 can also be of different lengths. Depending on how many cams 42 ₁ , ..., 42 _n the cam unit 31 is made, the second part of the axle body 25, which dips into the cam unit, more or less long.

Within FIG. 9C dashed lines the actual cam 42 ₁ , ..., 42 _n shown. The cable 33 winds almost completely around a cam 42 ₁ , ..., 42 _n around and is firmly connected to the fastening anchor 47.

The axis of rotation of the cam 42 ₁ , ..., 42 _n and the axis of rotation 6 of the pivot lever 5 coincide. However, the center of gravity of the respective cam 42 ₁ ,..., 42 _n preferably does not coincide with the axis of rotation 6 of the pivoting lever 5. The situation is different for the cutting discs 43 ₁ , ..., 43 _n . Through the center of gravity, preferably, the pivot lever pivot axis 6 runs.

Claims (16)

1. Pivot door drive device (1) for driving a pivot leaf (8) of a pivot door, comprising the following features:

   - an electric motor (4) comprising a motor shaft;

   - a pivot lever (5) that can be pivoted about a pivot lever pivot axis (6);

   - the pivot lever (5) is connected or can be connected at the free end thereof to a slide rail (2) fastened to the pivot leaf (8) or to a second lever fastened to the pivot leaf (8), forming a bell-crank lever for opening the pivot leaf (8);

   - the electric motor (4) is operatively connected to the pivot lever (5) by means of a downstream force-transmission apparatus (9) such that rotation of the motor shaft of the electric motor (4) leads to the pivot lever (5) being pivoted about the pivot lever pivot axis (6) thereof and thus to the pivot leaf (8) being pivoted;

   - the force-transmission apparatus (9) includes a sun gear (10) and a planet gear (11);

   - the planet gear (11) can be moved by means of a restraint (12) only at least in a semicircle along a lateral circumferential surface (13) of the sun gear (10), the teeth of the planet gear (11) engaging with the teeth of the sun gear (10);

   - the planet gear (11) is rotatably mounted by means of the pivot lever (5) at an engagement point (16) that is offset with respect to the pivot lever pivot axis (6); and

   - the planet gear (11), as part of the force-transmission apparatus (9), is operatively connected to the motor shaft of the electric motor (4) such that the rotation of the motor shaft leads to rotation of the planet gear (11) at the lateral circumferential surface (13) of the sun gear (10), and thus leads to the planet gear (11) rolling on the teeth of the sun gear (10), taking the pivot lever (5) therewith and pivoting said lever about the pivot lever pivot axis (6);

   and the restraint (12) of the planet gear (11) on the sun gear (10) being realised by the following features: - the planet gear (11) is arranged so as to be mounted in a stationary but rotatable manner at the engagement point (16) on the pivot lever (5); and the pivot lever pivot axis (6) of the pivot lever (5) coincides with a central axis extending through the centre of the sun gear (10); characterised by the following features:

   - the restraint (12) of the planet gear (11) on the sun gear (10) is further realised by the following features:

   a) the sun gear (10) is arranged so as to be stationary and immovable; and

   b) the force-transmission apparatus (9) has a guide lever (35) that can be pivoted about a guide lever pivot axis; and

   the guide lever pivot axis of the guide lever (35) coincides with a central axis extending through the centre of the sun gear (10); and
   the guide lever (35) is rotatably connected to the planet gear (11).
2. Pivot door drive device (1) according to claim 1, characterised by the following feature:

   - the guide lever (35) is arranged on a first side of the sun gear (10) and the pivot lever (5) is arranged on a second side of the sun gear (10) opposite the first side.
3. Pivot door drive device (1) according to any of the preceding claims, characterised by the following features:

   - a first deflection roller (20) can be driven by the motor shaft;

   - an axle body (25) extends from the sun gear (10) in at least a first direction; and

   a) the axle body (25) is rotatably mounted on the sun gear (10); and
   a second deflection roller (21) is non-rotatably arranged on the axle body (25); and
   a third deflection roller (22) is non-rotatably arranged on the axle body (25) so as to be axially spaced from the second deflection roller (21); or

   b) the axle body (25) is non-rotatably anchored in the sun gear (10); and
   a second deflection roller (21) is rotatably mounted on the axle body (25); and
   a third deflection roller (22) is rotatably mounted on the axle body (25) so as to be axially spaced from the second deflection roller (21); and
   the second deflection roller (21) and the third deflection roller (22) are rotationally coupled such that they cannot rotate relative to one another; and

   - a fourth deflection roller (23) is:

   a) arranged so as to be rotationally coupled to an output shaft (27), the output shaft (27) being arranged so as to be rotationally coupled to the planet gear (11); and/or

   b) arranged so as to be rotationally coupled to the planet gear;

   - a first force-transmission means (26) interconnects the first and the second deflection roller (20, 21) for force transmission;

   - a second force-transmission means (28) interconnects the third and the fourth deflection roller (22, 23) for force transmission.
4. Pivot door drive device (1) according to claim 3, characterised by the following features:

   - the planet gear (11) and the output shaft (27) are integral; or

   - the planet gear (11) and the output shaft (27) are made of a plurality of parts and/or the planet gear (11) has a continuous receiving opening that is fully penetrated by the output shaft (27).
5. Pivot door drive device (1) according to either claim 3 or claim 4, characterised by the following feature:

   - the planet gear (11) and/or the fourth deflection roller (23) have at least one fastening pin (36), which engages in at least one corresponding attachment opening in the fourth deflection roller (23) and/or in the planet gear (11), as a result of which the planet gear (11) and the fourth deflection roller (23) are rotationally coupled; or
6. Pivot door drive device (1) according to any of claims 3 to 5 and either claim 1 or claim 2, characterised by the following features:

   - the axle body (25) extends from the sun gear (10) additionally in a second direction opposite to the first direction;

   - the axle body (25) extends along the pivot lever pivot axis (6);

   - the pivot lever (5) having the pivot lever pivot axis (6) is pivotally mounted in the part of the axle body (25) that extends in the second direction; and/or

   - the guide lever (35) having the guide lever pivot axis is pivotally mounted in the part of the axle body (25) that extends in the first direction; and/or

   - the axle body (25) is:

   a) integral; or

   b) the axle body (25) is made of two parts, a first part of the axle body (25) extending in the first direction and a second part of the axle body (25) extending in the second direction, and a first part and a second part either being non-rotatably anchored in and/or rotatably mounted on the sun gear (10).
7. Pivot door drive device (1) according to any of the preceding claims or according to any of claims 3 to 6, characterised in that the engagement point (16) is:

   a) a recess within the pivot lever (5), in which

   - the planet gear (11) together with part of the toothed circumferential lateral surface (13) thereof engages and is rotatably mounted therein; or

   - a projection on the planet gear (11) engages and is rotatably mounted; or

   - the output shaft (27) extending through the planet gear (11) engages and is rotatably mounted; or

   b) a projection on the pivot lever (5), which projection engages in an opening formed preferably in the centre of the planet gear (11).
8. Pivot door drive device (1) according to claim 7, characterised by the following feature:

   - the planet gear (11) is extended towards the pivot lever (5) by means of an extension element (37).
9. Pivot door drive device (1) according to any of claims 3 to 8, characterised by the following features:

   - a drive (4), in particular a worm drive, is arranged on the motor shaft of the electric motor (4), and the first deflection roller (20) surrounds the drive train actuating the drive (4) and is connected thereto for conjoint rotation; or

   - the first deflection roller (20) is connected to the motor shaft for conjoint rotation.
10. Pivot door drive device (1) according to any of claims 3 to 9, characterised by the following features:

    - with respect to the first and the second deflection roller (20, 21):

    a) the diameter of the first deflection roller (20) corresponds to the diameter of the second deflection roller (21); or

    b) the diameter of the first deflection roller (20) is larger than the diameter of the second deflection roller (21); or

    c) the diameter of the first deflection roller (20) is smaller than the diameter of the second deflection roller (21);

    and

    - with respect to the third and the fourth deflection roller (22, 23):

    a) the diameter of the third deflection roller (22) corresponds to the diameter of the fourth deflection roller (23); or

    b) the diameter of the third deflection roller (22) is larger than the diameter of the fourth deflection roller (23); or

    c) the diameter of the third deflection roller (22) is smaller than the diameter of the fourth deflection roller (23);
11. Pivot door drive device (1) according to any of claims 3 to 10, characterised by the following features:

    - the first and the second deflection roller (20, 21) is a pulley or a gear; and

    - the third and the fourth deflection roller (22, 23) is a pulley or a gear; and

    - the first force-transmission means (26) is a toothed belt or a chain or at least a further gear; and

    - the second force-transmission means (28) is a toothed belt or a chain or at least a further gear.
12. Pivot door drive device (1) according to any of the preceding claims, characterised by the following features:

    - an energy accumulator unit (30), including a disc cam unit (31) consisting of at least two disc cams (42₁, ..., 42_n) arranged on top of one another;

    - the disc cam unit (31) is non-rotatably arranged on the pivot lever (5);

    - the cross sections of the individual disc cams (42₁, ..., 42_n) differ from one another in plan view either in part or in full.
13. Pivot door drive device (1) according to claim 12, characterised by the following features:

    - each disc cam (42₁, ..., 42_n) is penetrated by connection openings (44) through which a connection pin or a connection rivet can be guided or is guided, as a result of which the at least two disc cams (42₁, ..., 42_n) can be connected or are connected to the disc cam unit (31); and/or

    - the connection openings (44) are symmetrically arranged such that each disc cam (42₁, ..., 42_n) together with the at least one other disc cam (42₁, ..., 42_n), with the connection pins or connection rivets being inserted, also forms the disc cam unit (31) when the lower face of a disc cam (42₁, ..., 42_n) is rotated upwards.
14. Pivot door drive device (1) according to either claim 12 or claim 13, characterised by the following features:

    - each disc cam (42₁, ..., 42_n) includes a fastening armature (47) to which one end of a preloaded cable (33) or band of the energy accumulator unit (30) or one end of a preloaded spiral spring of the energy accumulator unit (30) can be fastened or is fastened, as a result of which a force is exerted on the pivot lever (5) which ensures the pivot leaf (8) of the pivot door is closed even without the electric motor (3) being used;

    - each disc cam (42₁, ..., 42_n) is separated from the relevant adjacent disc cam (42₁, ..., 42_n) by a separating disc (43₁, ..., 43_n) that has a larger diameter than the disc cams (42₁, ..., 42_n), as a result of which a guide channel for the cable (33) or band or part of the spiral spring is formed.
15. Pivot door drive device (1) according to any of the preceding claims or according to any of claims 12 to 14, characterised by the following feature:

    - the pivot lever pivot axis (6) of the pivot lever (5) extends through the centre of the disc cam unit (31).
16. Pivot door drive device (1) according to any of the preceding claims, characterised by the following features:

    - the sun gear (10) has a larger diameter than the planet gear (11); and/or

    - the sun gear (10) extends over less than 360°, preferably less than 270°, more preferably over less than 200°, more preferably over less than 180°, more preferably over less than 150°, more preferably over less than 120°, and is designed as a gear segment.

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