EP1948898B1 - High-speed industrial roller gate - Google Patents

Abstract

A high-speed industrial roller door includes a door leaf that is guided in lateral guides and a drive that acts on the door leaf to displace the latter from an open position into a closed position and vice versa. The door leaf is held in the open position so that adjacent areas of the door leaf are not in contact with one another, in a spiral section of the lateral guides located in the vicinity of the door lintel. The roller door also includes a weight compensation device. The drive has two extension arms that are coupled via joints to the lintel end of the door leaf, said arms being situated at a distance from one another across the door width and being synchronously pivoted about a pivoting axis in a central area of the spiral section. The distance between the coupling points of the extension arms on the door leaf and the pivoting axis of the extension arms can be varied. This permits the provision of a roller door with a drive that is situated near the door lintel, for which the degree of potential damage during a collision with the door leaf is reduced in relation to prior arrangements.

Description

The invention relates to a high-speed industrial rolling door according to the preamble of claim 1.

Roller shutters are known in practice in a variety of design ways. A comparatively simple structure while rolling doors on which a flexible curtain is wound in the course of the opening movement of the roll-up door on a winding shaft in the area of the lintel. The lintel-side end of the flexible door leaf is for this purpose fixed to the winding shaft and it arises in the course of the opening movement, a constantly growing winding of layers of the curtain, these layers come to lie directly adjacent to each other. Such roller doors have proven very successful in practice and are widely used, since they are inexpensive to provide and have a relatively low weight, which also has an advantageous effect in terms of energy consumption.

A disadvantage of this type of roller doors, however, lies in the fact that the turns of the door leaf designed as a blind scratch and pollute already after a relatively short time due to their direct mutual contact in the winding. This applies equally to roller doors with one Lamella armor instead of a flexible curtain, as they are also known from practice.

For special applications and in particular for a high-speed operation with a movement speed of more than one meter per second, it has therefore gone over to lead the door leaf in the lintel area of the door opening without contact. Examples of such roller doors are inter alia in the DE 40 15 215 A1 , of the DE 199 15 376 A1 and the DE 102 36 648 A1 given. In these constructions, the door leaf, whether it is now a lamellar armor or a flexible curtain, etc., guided in lateral guide rails, which open in the region of the lintel above the door opening in a spiral section in which the door leaf in an elongated or approximately round Winding is performed.

In contrast to the input described roller doors with directly wound on a winding roller blind, the winding forms in a non-contact guide not from the inside out, but from outside to inside, that is, the leading, so fall end of the Torblatt runs in the course of the opening movement of Rolling gates progressively further into a central region of the spiral section.

Such roller doors are characterized by excellent properties, so that they have proven themselves especially in industrial applications. In particular, a reliable and permanent Torabschluß can be made with it, with very high speeds of movement of up to four meters per second are possible.

On the other hand, this type of door leaf guide in the winding required a completely new drive technology, since the winding shaft itself was obsolete by this construction methods. In these roller doors, the drive motor is indeed for reasons of space further arranged in the area of the lintel; However, the introduction of the driving force on the door leaf takes place at the bottom end. In the currently customary Ausgestaltungsweisen the drive motor usually acts on a toothed belt on drive rollers in the form of pulleys, which are also located on both sides of the gate in the lintel area and in turn each via toothed belt on a bar or the like. Acting on both sides of the bottom end of the door leaf rigid is coupled. The two side toothed belts are in this case firmly connected to these brackets or the like, so that the rotational movement of the drive motor finally moves to a lifting or lowering movement of the door leaf.

In particular, when designed as a lamellar door leaves, it has also proven this case when a counterweight device is provided, which serves to balance the Torblattgewicht a lift gate. This typically has spring elements, which are under maximum bias with the door closed and therefore support the opening movement of the door leaf. Thus, however, not only a reduction of the required drive torque is achieved in the operation of such a lifting door, but with proper Einjustierung the arrangement prevents an immediate crash of the door leaf in case of failure.

In practice, weight balancing devices of a type prevailed in high-speed industrial doors, as for example in the WO 91/18178 is explained. Such a weight compensation device typically has, as a spring element, a helical spring and a tension element fastened thereto, generally in the form of a band. The lower end of the spring element is fixedly connected to the ground, while the upper end is coupled by the tension element with a winding shaft arranged on the side of the hoistway winding shaft. The tension element is in the course of the closing process of the lifting gate on this winding shaft directly superimposed layers wound so that the spring element increasingly tensioned. On the other hand, the opening movement of the door leaf is connected to a unwinding of the tension element of the winding shaft, so that in this case results in a relaxation of the spring element. The winding shaft is coupled to the drive of the lifting gate.

Also, this type of drive for a roller shutter has proven itself in practical use for many years. However, the elements of the drive mechanism are subject to a not inconsiderable risk of damage in the event of a collision of the door leaf with another object.

It should be noted that the bottom end of a door leaf is particularly vulnerable to collisions. Such collisions can occur, for example, when a forklift driver misjudges the speed of movement of the door leaf and sets his vehicle too early in the course of the opening movement of the door leaf. Other sources of danger are often present when large-sized goods are transported, which limit the field of view. The result of such a collision is then usually a deformed or broken closure element of the door leaf, wherein at the same time present in the lateral guides lateral bracket or the like. Of the drive mechanism can be affected.

In order to address this problem, the Applicant has developed an active crash system which allows deflection of the lower portion of the door leaf from the door leaf plane in the event of a collision as soon as a predetermined amount of lateral force is exceeded. This development has the same in the German patent application DE 103 42 302 A1 described roller door with collision protection. With this system it is possible to change the function of the Rolltores impairing damage to the gate to prevent as much as possible. In addition, so that the risk of damage to elements of the drive mechanism can be significantly reduced because the present in the side frames bracket, etc. are free from the usually occurring in the central region of the door opening load as soon as the door leaf is deflected in this area.

Despite the considerable advantages in practice, this special roller door with the active crash system is subject to the problem that, when the door leaf is deflected, there is no longer a closure element which establishes a transverse connection between the two lateral guide devices. The points of attack for the initiation of the driving force on the door leaf are therefore no longer based against each other in the event of a collision, which leads to tilting moments occurring in the lateral guides. Even if these tilting moments can be limited by correspondingly accurate guide elements, this results nevertheless in increased wear, as well as a considerable additional cost factor. Moreover, in unfavorable cases, it can still not be ruled out that the coupling points for the driving force will also be affected in the event of a collision, for example if a collision takes place directly adjacent to the lateral frames.

From the document WO 95/30064 A is a roller shutter with the features of the preamble of claim 1 is known.

The invention has the object of developing a high-speed Industrierolltor the generic type such that the extent of possible consequential damage can be reduced in a collision on the door leaf.

This object is achieved by a high-speed industrial roller door with the features of claim 1. This is characterized in particular by the fact that the cantilever arms are coupled by means of joints to the lintel end of the door leaf.

The invention thus provides, in an industrial rolling gate with a contactlessly wound door leaf in the open position, to initiate the driving force on the lintel end of the door leaf. Although the distance of the camber-side end of the door leaf from the center of the spiral constantly changes in the course of the opening movement of the door leaf, the drive mode of the door leaf according to the invention is reliably realized, since a corresponding length compensation is provided on the cantilever arms.

The industrial roller door according to the invention is characterized by the very considerable advantage in practice that the entire drive technology of the door leaf can be placed in the lintel area of the door opening and thus substantially protected against collisions in particular. As a result, the extent of damage in the event of collision compared to conventional roller doors can be significantly reduced overall.

In addition, the present invention Industrierolltor thus also in a much shorter time and with much less effort put back into a ready-to-use condition when it comes to damage to the door leaf, since only individual slats or blind sections are to be replaced without direct connection to the drive.

In addition, by the spaced in the door width apart from each other boom arms continues a reliable introduction of Drive forces achieved in the door leaf, even if roller doors are available with greater widths of, for example, six meters and more.

Another advantage is that the roller shutter according to the invention has a weight compensation device. By such a weight compensation device, as is conventional in itself, is achieved by bias that a smaller driving force is required to open the door leaf, as if such a weight compensation is not given. It should be noted that the door leaf must be pulled in the opening movement against gravity upwards to be included in the spiral section in the lintel. This movement supports the weight compensation device by a spring bias, which is introduced in the course of the closing movement of the door leaf in the door assembly.

In the context of the invention, the use of such a weight compensation device has the particular advantage that the required drive force, when the effective lever length of the boom arms is greatest, namely at the beginning of the opening movement, can be significantly reduced. Although with increasing progress of the opening movement, the support effect is reduced by the weight balancing device, but at the same time also reduces the effective lever arm on the boom arms, as the fall-side end of the door leaf increasingly enters the central region of Torabschnitts. Therefore, according to the invention, the energy consumption for this movement can be kept particularly low, wherein also the stress of the components of the drive is also lower. This results in a total of greater reliability and longevity of the door assembly. Furthermore, it is thus possible to achieve particularly high speeds of movement.

Characterized in that the cantilever arms are pivotable synchronously with each other about a pivot axis in a central region of the spiral portion, a tilting of the door leaf in the guides during movement is reliably avoided. The roller door according to the invention can thereby be operated very reliably and at high speed.

The variability of the effective lever length on the cantilever arms also takes account of the changing radius in the course of the spiral. In cooperation with the articulated Ankopplungsweise way so tilting or excessive friction load of the door leaf in the spiral section can be reliably avoided.

Another advantage is that the previously customary toothed belts, chains or the like for the transmission of the driving force from the motor arranged in the fall to the bottom end plate of the door leaf omitted according to the invention. This reduces the space required in the side frames, which can be made slimmer. In addition, in the area of the lateral frames, there are thus fewer elements according to the invention at which dirt etc. could accumulate. Here, in particular, the conventionally used toothed belt with its large number of teeth have not been unproblematic, especially when the roller door was used in the pharmaceutical sector or in clean rooms. In these special fields of application, the good cleaning ability of the roller door is of considerable importance. By inventively achieved simplified design of the gate assembly is taken into account, so that the roller door according to the invention is particularly well suited especially for these purposes.

Another advantage of the invention Industrierolltores is that by dispensing with the timing belt, chains or the like for the transmission higher reliability can be achieved because these elements Represent wearing parts. The industrial roller door according to the invention is therefore characterized by a particularly low maintenance and high reliability with high durability.

In addition, it also offers greater security than conventional roller doors, since risk factors such as an accidental crash of the door leaf in a broken toothed belt are eliminated according to the invention.

Furthermore, it has a particularly simple structure, since the door leaf is simply guided in the side frames and can be free of lateral connections.

Although this is from the Dutch patents NL 1015953 and NL 1016983 a shutter to the completion of a window opening on a building has become known, which contains at first glance similar system elements. This shutter has a guided in lateral guides lamellar armor, which is movable by means of a drive from an open position to a closed position and vice versa. The lamellar armor is accommodated in the open position in a arranged in the region of the opening lintel spiral portion of the lateral guides such that adjacent areas of the tank are present without contact to each other. In addition, the drive has two cantilever arms mounted in a drive shaft, by means of which it is rigidly coupled to a lintel-side end of the lamellar shell. The cantilever arms are spaced apart from one another in the door width and are pivotable synchronously by means of the drive shaft in a pivot axis in a central region of the spiral section. Further, the distance between the coupling points of the cantilever arms on the door leaf and the pivot axis of the cantilever arms is variable.

The principle shown in these documents may be applicable to manual or motor driven at low speeds blinds when in the Guides given sufficient scope for Abwinkelbewegungen the individual slats; However, it is by no means applicable to high-speed industrial rolling doors, since the high dynamic loads prevailing in high-speed operation would not be controllable in these known blinds. It should be noted, for example, that is not borne by the rigid coupling of the cantilever arms on the uppermost lamella of the curtain the fact that in the spiral section constantly changing angular position of this last lamella to the drive shaft. In order to avoid tilting of this uppermost blade even at low speeds of movement, therefore, a guide with a great game is required. At high speeds of movement of more than one meter per second, as are common in high-speed industrial rolling doors, also occur to deformations of the slats due to the changing dynamic loads, which would lead to uncontrollable states of motion with such loose guidance in the lateral guides.

In addition, in these known blinds no weight compensation device is provided and also not required, since the dimensions of the building opening to be closed are usually low and thus only a small weight at low speed is movable. Accordingly, only comparatively small torques act on the cantilever arms in the prior art. In an industrial rolling door operated at high speed, completely different balance of forces exist here, which can be reliably controlled, in particular, by means of a weight compensation device.

The documents NL 1015953 and NL 1016983 Thus, describe an arrangement which is not suitable for a high-speed operation and the use of the completion of door openings in industrial buildings. In addition, from these writings also no suggestion, an articulated coupling to make the cantilever arms at the fall end of the door leaf or to provide a weight balancing device. Furthermore, such shutters are not subject to a collision problem, as it is given in usually heavily frequented Industrierolltoren. As a result, they could not provide any stimulus to solve the task.

Advantageous developments of the industrial rolling door according to the invention are the subject of the dependent claims.

Thus, the cantilever arms can be made telescopic, whereby the measure of the effective distance between the coupling points of the cantilever arms on the door leaf and the pivot axis of the cantilever arms is variable with particularly simple structural means. Thus, the spiraling continuously changing radii can be easily taken into account when inserting the lintel-side end of the door leaf in the spiral section.

In this case, it is possible that the telescopic extension arms each contain a tubular guide part and a piston part guided in a freely displaceable manner. Due to the free displaceability of the piston part, each cantilever arm can then automatically adapt to the variable radius in the spiral section, without the need for active action, for example for controlling the effective length on the cantilever arms. This allows a particularly simple construction can be achieved, which is characterized by a low maintenance, high reliability and low deployment costs.

It is further advantageous if the extension arms are arranged on a common drive shaft, which is driven in rotation by a motor of the drive. Then, with simple structural means a reliable synchronous movement of the cantilever arms can be made about its pivot axis. In addition, this does not increase the space required for the drive of the industrial rolling door according to the invention, since the drive shaft can be arranged in the usually open central region of the spiral section, that is requires no significant space outside of the defined by the spiral portion movement range of the door leaf. In addition, malfunctions in the operation of the industrial roller door can be avoided even more reliably since, for example, skipping a toothed belt by one tooth can not occur according to the invention after the toothed belts have been removed and the two extension arms are arranged on a common drive shaft.

If the motor directly drives the drive shaft, an even more reliable and simpler design for the industrial rolling door according to the invention can be realized. In particular, this can be a chain, a timing belt or the like for the transmission of the driving force from the engine to the drive shaft can be avoided, whereby the number of components of the drive is reduced overall, while a higher resistance compared to the prior art can be achieved. To reduce the space requirement, an angle motor is preferably used for this purpose.

In addition, the cantilever arms can be coupled to an element extending over the entire door width. Compared to the construction according to DE 103 42 302 A1 , which uses the active crash system, then there is the advantage that the driving force introduced at at least two points acts on a transversely extending element in the transverse direction of the door opening, so that tilting moments, as in the deflected door leaf in this prior art, can be avoided. As a result, the cost of the required side guides at the bottom end of the door leaf can be significantly reduced compared to the prior art. The design effort for the roller door according to the invention is therefore substantially lower than in the prior art. It can also be within the scope of the invention, a door leaf with deflectable Mid-range as in the DE 103 42 302 A1 be used advantageously to avoid damage to the door leaf.

It is a further advantage if the door leaf has two lateral hinge bands, which are each arranged adjacent to the guides, wherein the extension arms are respectively coupled to lintel-side end portions of the hinge bands. Such hinges are, for example, from the above cited DE 40 15 215 A1 are known and serve to reliably absorb the loads occurring in the course of the opening or closing movement and to keep the attached Torabschlußelement as the lamellar armor or a curtain to a considerable extent free of these loads. By the direct interaction of the cantilever arms with these hinge bands, the forces required for the movement can be introduced in an optimal manner to such a door leaf. As a result, the risk of damage to the door leaf can be kept particularly low due to the dynamic loads.

If the lintel-side end portions of the hinge straps are adjustable in their length in the direction of movement of the door leaf, can be done with simple means tolerance compensation in the arrangement, so as to achieve the most accurate vertical orientation of the door leaf. The problem of possible tilting of the door leaf, e.g. due to not exactly the same angle cantilevered boom arms with the associated risk of jamming of the door leaf in the lateral guides can thus be effectively eliminated.

It is a further advantage if the weight compensation device has a spring element, a tension element and a winding device, wherein one end of the spring element can be fixed on the bottom side, the tension element having one end on the spring element and the other end on the winding device is fastened, wherein the winding device can be coupled to a drive of the rolling or lifting gate, wherein the tension element on the winding device is so wound up or unwound that the spring element has its greatest bias when a door leaf of the lifting gate is in the closed position, and is substantially relieved when the door leaf is in the open position. In this case, the tension element can have a smaller width at the end facing the winding device than at the end facing the spring element, and the winding device can have a shaft and a guide device mounted thereon, by means of which the tension element can be wound such that the winding layers are in contact with each other, wherein the guide means for this purpose has circumferentially guide surfaces in the winding direction steadily growing radius.

This makes it possible for the first time to wind the tension element without contact, whereby the torque required for effective weight compensation can be provided with little design effort and an increased life is achieved.

Thus, automatically resulting from the contact-free winding enlarged radii in the winding, which is why a small number of revolutions of the winding device is sufficient to produce the desired bias of the spring element. This is particularly advantageous in the case of door leaves guided without contact in the winding, since here too there is only a reduced number of rotary movements of the drive shaft in comparison to conventional contact-wound door leaves. Thus, it is inventively usually possible to dispense with additional transmission gear, etc., and to drive the counterbalancing device directly through the drive shaft for the door leaf with. The construction of a lift gate equipped with this weight compensation device can thus be made structurally simple. This in turn is advantageous in terms of reduced wear and the improved life of such a lifting gate.

Furthermore, resulting from the present in the winding larger radii longer lever lengths, which in turn result in greater torques than in a conventional contacting winding of the tension element. The weight compensation device can thus be used advantageously even with very large and heavy gates.

In addition, the configuration according to the invention has the advantage that the choice of the effective radius, or the effective lever length on the guide device is ausgestaltbar regardless of the thickness of the tension element, since this only appropriately designed guide surfaces must be formed on the guide means. This allows a professional alone by targeted shaping of the guide means make an individual adjustment of the weight balance to the respective dimension of the Hubtorblatts and its weight, without having to take this example, for example, on the thickness of the tension element, the core diameter of a winding shaft consideration.

Another advantage of this weight balancer is that the tension member is due to its special design free from axial displacements wound up. This makes it possible to avoid one-sided loads on the tension element and the wear of this thoroughly stressed in use element can thus be kept low. This has an advantageous effect on the life of the weight balancing device.

Here it is already out of the WO 2004/076795 A1 become known, the door leaf of a lifting gate in such a way that it has a smaller width at the lintel end than at the bottom end. Furthermore, it is out of this Scripture known to provide two axially spaced modules on which the door leaf is wound without contact, wherein the two modules have circumferentially guide surfaces in the winding direction steadily growing radius. However, this configuration refers exclusively to a way to wind a door leaf contactless and thus avoid scratching or damage. With regard to weight compensation, this document refers to the above-explained conventional coil spring and tension band configuration in which the tension band is wound on a winding shaft in a contacting manner. A suggestion to provide instead of or in addition to the door leaf, a non-contact winding of the drawstring of counterbalance is not clear from this document. In addition, the busy WO 2004/076795 A1 nor in the slightest with the problem of setting a suitable weight compensation characteristic on such a lifting gate.

Furthermore, the width of the tension element can increase stepwise from the end facing the winding device to the end facing the spring element, wherein the guide means comprises at least two guide portions, each of which are spirally formed and axially offset from each other, that at an inner guide portion an outer guide portion pair connects, the minimum guide surface radius corresponds to the maximum guide surface radius of the inner guide portion. This can be realized with relatively little design effort, an advantageous arrangement, since the guide surfaces are provided on each guide section only in one plane. At the point at which the inner guide portion can not continue to offer the corresponding spiral guide surface, so after a complete revolution, according to the invention assumes an axially outer pair of guide section with adapted radius in cooperation with a correspondingly adapted wider section of the tension element further Guidance function. With this configuration, two complete revolutions of the guide device can already be realized with a radius which increases continuously in the winding direction, which is sufficient for many applications. Should more than two revolutions of the guide device be required, further outer pairs of guide sections can follow, which are designed accordingly and, in turn, interact with an even wider section of the tension element.

Alternatively, it is also possible that the width of the tension member steadily increases from the end facing the winding device to the end facing the spring element, and that the guide means comprises two guide spirals extending axially from one central portion with increasing radius away from each other extend outside. This also makes a non-contact winding of the tension element possible, but a three-dimensional configuration of the guide surfaces is required. However, this configuration also makes it possible to provide the guide surfaces with a continuously increasing radius in the winding direction.

If the tension member is a chain, a stable yet winding-wise very flexible configuration of this component of the weight balancer can be provided. In particular, such a chain has a very high tensile strength, which is why it can be used particularly advantageously on lifting gates with large dimensions of, for example, 8 m width and 6 m height.

Alternatively, it is also possible that the tension element is formed as a band. This configuration is particularly advantageous if the width of the tension element increases steadily from the end facing the winding device to the end facing the spring element, since such a design mode with a belt manufacturing technology is easier to implement as with a chain. As a material for such a band are, for example, metal or plastic and in particular fiber-reinforced plastics into consideration.

It is a further advantage if the spring element has at least one helical spring. Compared to other spring-elastic elements, which can also be used in itself, coil springs have already proven themselves in practice in known weight compensation devices many times because of their robustness and reliability. In addition, with such coil springs can easily provide the desired spring properties.

In this case, it is also advantageous if the guide device is mounted on the drive shaft, on which also the extension arms are arranged. Then, a particularly compact and robust construction can be achieved, since a separate drive for the weight compensation device or transmission elements such as toothed belts or the like are not required.

Fig. 1

eine perspektivische Ansicht eines erfindungsgemäßen Industrierolltores zur Verdeutlichung des Antriebsmechanismus im Sturzbereich der Toröffnung;

Fig. 2

eine schematische Seitenansicht eines Spiralabschnitts am erfindungsgemäßen Industrierolltor in einer ersten Ausführungsform; und

Fig. 3

eine schematische Vorderansicht im Bereich der Antriebswelle am erfindungsgemäßen Industrierolltor gemäß der ersten Ausführungsform;

Fig. 4

eine perspektivische Ansicht der Ankopplungsstelle eines Auslegerarms an das Torblatt gemäß einer zweiten Ausführungsform;

Fig. 5

eine Seitenansicht der Anordnung gemäß Fig. 4;

Fig. 6

eine perspektivische Ansicht eines mit einer Gewichtsausgleichseinrichtung ausgestatteten Hubtores, wobei das Torblatt sowie weitere Bestandteile des Hubtores zur Verdeutlichung weggelassen sind;

Fig. 7

eine Seitenansicht des Hubtores gemäß Fig. 6, wobei ebenfalls das Torblatt weggelassen ist;

Fig. 8

eine Vorderansicht des Hubtores gemäß Fig. 6;

Fig. 9

eine perspektivische Ansicht einer Führungseinrichtung der Gewichtsausgleichseinrichtung;

Fig. 10

eine Seitenansicht der Führungseinrichtung gemäß Fig. 9 mit schematischer Darstellung der Bewegungsbahn des Zugelements;

Fig. 11

eine Draufsicht dieser Führungseinrichtung;

Fig. 12

eine Draufsicht auf das Zugelement; und

Fig. 13

die Charakteristik der Gewichtsausgleichseinrichtung.

The invention will be explained in more detail in exemplary embodiments with reference to the figures of the drawing. It shows:

Fig. 1

a perspective view of an industrial rolling door according to the invention to illustrate the drive mechanism in the lintel area of the door opening;

Fig. 2

a schematic side view of a spiral section on the industrial rolling gate according to the invention in a first embodiment; and

Fig. 3

a schematic front view in the region of the drive shaft at Industrierolltor according to the invention according to the first embodiment;

Fig. 4

a perspective view of the coupling point of a cantilever arm to the door panel according to a second embodiment;

Fig. 5

a side view of the arrangement according to Fig. 4 ;

Fig. 6

a perspective view of a equipped with a weight compensation device lifting gate, the door leaf and other components of the lifting gate are omitted for clarity;

Fig. 7

a side view of the lifting gate according to Fig. 6 , wherein also the door leaf is omitted;

Fig. 8

a front view of the lifting gate according to Fig. 6 ;

Fig. 9

a perspective view of a guide means of the weight balancing device;

Fig. 10

a side view of the guide device according to Fig. 9 with a schematic representation of the trajectory of the tension element;

Fig. 11

a plan view of this guide device;

Fig. 12

a plan view of the tension element; and

Fig. 13

the characteristic of the weight balance device.

As shown in the figures, a Industrierolltor, hereinafter referred to as Rolltor 1, a door leaf 2, which has articulated mutually coupled lamellae 21, which are guided by means of rollers 22 in lateral guides 3 and 4. The rollers 22 are mounted on lateral hinge straps 23, which record the tension and thrust loads on the door leaf 2 and hold the lamellae 21.

The guides 3 and 4 each have a vertical portion 31 and 41, the upper end in Fig. 2 can be seen, and which extends from the camber-side end shown to the bottom end of the roll-up door 1 in a conventional manner, but as well as the frames is not shown in more detail in the figures. On the fall side, the vertical sections 31 and 41 each open into a spiral section 32 or 42 in the form of a round spiral, in which the door leaf 2 is received in the open position of the roller shutter 1 in such a way that the individual lamellae 21 are in contact with each other in a spiral winding.

The movement of the door leaf 2 between its end positions is effected by a drive 5. This has a motor 51, here an angle motor, which is received in the region of the lintel in the region of a side frame and is coupled there directly to a drive shaft 52. The drive shaft 52 passes through the spiral section 32 or 42 of the guides 3 and 4 in a central region. On the drive shaft 52 on both sides of the door opening in each case adjacent to the spiral section 32 and 42 cantilever arms 53 and 54 are arranged. The extension arms 53 and 54 respectively pass through the drive shaft 52 centrally and project radially therefrom.

As in particular from the Fig. 2 and 3 can be seen, each cantilever arm 53 and 54, a guide member 531 and 541, which is fixedly connected to the drive shaft 52. In each guide part 531 and 541, respectively, a piston part 532 and 542 is positively received and guided freely displaceable. A spaced from the guide member 531 and 541 present end of the piston member 532 and 542 and has a coupling point 533 and 543, by means of each arm 53 and 54 with the fall-side end of the Torblatts 2 is hinged. At the lintel-side end of the door leaf 2, this is an over the entire gate width extending element (here in this first embodiment, a blade 21) before, whereby the driving force is transmitted uniformly on the Torblattbreite.

• In den Figuren 2 und 3 ist der Zustand gezeigt, in dem das Rolltor 1 in seiner Schließstellung vorliegt, das heißt das Torblatt 2 die Toröffnung vollständig abdeckt. Zum Öffnen des Rolltores 1 wird der Motor 51 derart betätigt, daß er eine Drehbewegung auf die Antriebswelle 52 überträgt, mittels der das Torblatt 2 nach oben in den Spiralabschnitt 32 bzw. 42 bewegt wird. Hierzu wird die Drehbewegung der Antriebswelle 52 über die Auslegerarme 53 und 54 und die Ankopplungsstellen 533 und 543 auf das sturzseitige Ende des Torblatts 2 aufgebracht. Gemäß der Darstellung in Fig. 2 wird jeder Auslegerarm 53 bzw. 54 hierzu entgegen dem Uhrzeigersinn gedreht. Mit dieser Drehbewegung wird das Torblatt 2 in den Spiralabschnitt 32 bzw. 42 eingezogen und bildet mit fortlaufender Öffnungsbewegung des Torblatts 2 den Spiralwickel im Torsturzbereich.

The roller shutter 1 is operated as follows:

• In the Figures 2 and 3 the state is shown in which the roller door 1 is in its closed position, that is, the door leaf 2 completely covers the door opening. To open the roller shutter 1, the motor 51 is actuated so that it transmits a rotational movement to the drive shaft 52, by means of which the door leaf 2 is moved upward in the spiral section 32 and 42, respectively. For this purpose, the rotational movement of the drive shaft 52 via the extension arms 53 and 54 and the coupling points 533 and 543 applied to the fall-side end of the door leaf 2. As shown in Fig. 2 each cantilever arm 53 or 54 is rotated counterclockwise thereto. With this rotational movement, the door leaf 2 is drawn into the spiral section 32 and 42 and forms with continuous opening movement of the door leaf 2, the spiral winding in the lintel area.

Due to the spiral shape of the side guides 3 and 4 in the lintel area, the distance between the pivot axis of the cantilever arms 53 and 54, which coincides with the axis of rotation of the drive shaft 52, and the coupling points 533 and 543 on the cantilever arms 53 and 54. This change in length is automatically compensated by the special configuration of the cantilever arms 53 and 54, since each piston part 532 and 542 is slidably received in the guide part 531 and 541, respectively.

In the open position of the roller doors 1 are the extension arms 53 and 54 in the dashed lines in Fig. 2 shown position, from which it can be seen that their effective lever length compared to the excellent initial state has significantly reduced. How out Fig. 2 Furthermore, it can be seen that the length of the piston member 532 or 542 is selected such that it does not project beyond the other end of the associated guide member even in the maximum inserted state in the guide member 531 or 541, that it conflicts with a winding of the door leaf 2 in the spiral section 32 and 42 passes.

As can be seen from this explanation, the maximum lever arm length is present on the cantilever arms 53 and 54 at the beginning of the opening movement. In order to keep the burden here on the drive 5 low, the roller shutter 1 has a in the Fig. 1 to 3 not shown weight balancing device, which is formed in this embodiment in a conventional manner. This supports the drive 5 just at the beginning of the opening movement due to their spring bias, so that the forces to be introduced here by the drive 5 are comparatively low. A further reduction of the driving forces is possible in that the length of the door leaf 2 is selected such that the coupling points 533 and 543 are present in the closed position of the door leaf 2 at the entrance to the spiral section 32 and 42 and the boom arms 53 and 54 thus not as in Fig. 2 represented an attack angle of more than 90 ° to the door leaf 2 have, but in all areas of movement substantially perpendicular to the associated torrel-side end of the door leaf 2 are present.

The Fig. 4 and 5 show a second embodiment of the present invention, which differs from the first embodiment in particular in the manner of coupling the cantilever arms 53 and 54 to the door leaf 2. Components of the rolling door 1 which correspond to those in the first embodiment are designated by the same reference numeral.

As from the representations in the Fig. 4 and 5 can be seen, the hinge bands 23, of which only one is shown in these figures, on fall side end provided with an end portion 24 to which the boom 54 shown here is rotatably coupled via a hinge. In this embodiment, the two end sections 24 are connected to one another over a transverse strut 25 over the entire door width. Furthermore, a roller 22 is also mounted on this.

With the modification according to this second embodiment is achieved without extension of the door leaf, that the cantilever arms 53 and 54 are present at an angle of attack of 90 ° to the door leaf 2, such as Fig. 5 clarified. The driving forces for the initiation of the movement of the door leaf 2 are thus low even in the closed position, since the cantilever arms 53 and 54 are present in this starting position substantially perpendicular to the associated torrel-side end of the door leaf, namely the end portions 24.

Furthermore, the end portions 24 are formed in several parts, so that they are seen in their length in the direction of movement of the door leaf 2 adjustable. For a tolerance compensation is possible to avoid an inclination of the door leaf 2 in the side guides 3 and 4. In the embodiment shown this is made possible by an adjustable screw connection.

Based on Fig. 6 to 13 a further embodiment of a roller shutter 1 is explained below, which is designed as a lifting door and provided with a weight compensation device 6. Components of the rolling door 1, which correspond to those in the first embodiment are again denoted by the same reference number, with a detailed explanation of these features is omitted to avoid repetition.

Like from the FIGS. 6 to 8 can be seen, the lifting gate 1 on a weight compensation device 6, which includes a spring element 61, a tension member 62 and a winding device, a Guide means 63 and a shaft 64 has. The guide device 63 is mounted on the shaft 64. As can also be seen from the figures, the shaft 64 is coupled directly to the drive shaft 52 and rotates with this in an operation of the motor 51 with.

The spring element 61 has four coil springs 611 in the present embodiment, which are fixed on the bottom side. With their other end, the coil springs 611 are connected via a bracket 612 fixed to the tension element 62, which is designed here as a chain. The lintel-side end of the tension element 62 is deflected in the region of the lintel about a deflection roller 65 and is fastened to the guide device 63.

In the Fig. 9 to 12 the guide device 63 is shown together with the tension member 62 in more detail. As in particular from the Fig. 7 and 8th can be seen, the tension member 62 is wound without contact in the course of the closing movement of the door leaf 2 by means of the guide means 63. The tension member 62 is fixed to an attachment point 66 on the guide means 63 and extends in the wound state according to the dash-two-dotted line 67 according to Fig. 7 which describes the chain running center.

Like from the Fig. 9 to 12 can be seen, the guide means 63 an inner guide portion 631, a first outer guide portion 632 and a second outer guide portion 633 on. The guide portions are formed so that they have circumferentially guide surfaces with a continuously growing in the winding direction radius. Further, the two outer guide portions 632 and 633 are configured as a pair of disks 632a and 632b, and 633a and 633b, which axially enclose the inner guide portion 631, respectively. The second outer guide portion 633 further includes the first outer guide portion 632 axially.

In addition, the maximum guide surface radius of the inner guide portion 631 corresponds to the minimum guide surface radius of the first outer guide portion 632, so that there is a smooth transition here. Likewise, the maximum guide surface radius of the first outer guide portion 632 is configured corresponding to the minimum guide surface radius of the second outer guide portion 633.

As in particular from Fig. 12 can be seen, the pulling element 62 is thereby formed so that it has an increasing width in the direction of the bottom end of its fall-side end. In the present embodiment, the tension element 62 has three different widths corresponding to the number of guide sections. In Fig. 11 For clarity, the chain is shown in a cut state as it comes to rest on the guide portions of the guide 63. It can be seen that the tension member 62 is thus wound without contact and without an axial displacement relative to the shaft 64 in the guide means 63.

For this purpose, the width of the tension element 62 is selected at the fall end so that this section 62a can be wound directly onto the inner guide portion 631. A second portion 62b of the tension member 62 having a mean width corresponds to the width of the first outer guide portion 632, so that this portion 62b of the tension member 62 is wound on the guide surfaces thereof. Accordingly, the width of a subsequent spread portion 62 c of the tension member 62 is adapted to the width of the second outer guide portion 633 so as to come to rest on the guide surfaces thereof. By the above-explained adjustments of the radii of the individual guide sections 631 to 633 results in a steady transition in the course of the winding process, d h. a uniform winding of the tension element 62 during the closing movement of the door leaf second

In Fig. 13 is schematically illustrated by characteristics of the characteristic of the weight balancer 6. In this case, an exemplary gate height of 6 m is shown, to the right, the respective clear height of the remaining door opening is applied. The value "0.00" thus stands for the fully closed lifting gate 1, while the value "6.00" stands for the fully opened lifting gate 1. At the top, the torque acting on the drive shaft 52 is given based on the weight of the free door leaf section with a curve 81 through the diamonds, while the moment acting on the drive shaft 52 by the weight balancer 6 is indicated by a curve 82 passing through the squares , It indicates the moment caused by the spring element 61.

How to get the Fig. 13 takes, the weight compensation device 6 is set so that when the door is closed, the spring element 61 is stretched so far that an excess of the torque produced by the weight of the door leaf torque excess of about 200 Nm is present. As a result, when the closed lifting gate 1 is actuated, the door leaf 2 ascends upwards to approximately that height without additional drive, in which the weight force of the free door leaf section is in equilibrium with the applied spring force of the spring element 61 Fig. 13 this is a place where the two lines intersect, ie at a height of about 2.5 m.

Upon further opening of the door leaf, the respectively required drive torque is almost in equilibrium with the torque provided by the weight compensation device 6, so that the drive 5 must act substantially only against the existing frictional forces.

When the gate is fully open, the moment provided by the weight balancing device 6 exceeds that shown in FIG in the diagram in Fig. 13 in turn, the torque produced by the weight of the door leaf 2 on the drive shaft 52, so that a crash of the door leaf is reliably prevented even with a defect of the drive 5.

In addition to the illustrated embodiments, the invention allows for even more design approaches.

So it is also possible that the distance between the coupling points 533 and 543 of the cantilever arms 53 and 54 on the door leaf 2 and the pivot axis of the cantilever arms 53 and 54 is changed in any other way than by a telescopic design of the cantilever arms. For example, the cantilever arms may also have a predetermined length, in which case elements in the region of the coupling points are mounted so as to be longitudinally displaceable on the cantilever arms. Such a design is particularly conceivable when the cantilever arms are seen in gate width outside of the guides 3 and 4 are arranged for the door leaf 2 and the coupling member 32 passes through the spiral portion 42. In this case, the overall length of the cantilever arms of minor importance, since a collision with turns of the door leaf 2 in the spiral section 32 and 42 can not occur.

The extension arms can also be designed to be telescopically two or more times. Thus, in particular, the total length of the piston part can be reduced, whereby any conflicts with turns of the door leaf 2 in the open position can be even better avoided.

Furthermore, it is also possible that three, four or more cantilever arms are provided for driving the roller shutter. This is likely to be the case in particular when larger door widths of six meters or more are given.

Moreover, it is also not necessary that the piston member is guided freely displaceable in the tubular guide member. Here also a controlled leadership would be possible. In addition, the guide member also need not be tubular, but may, for example, a polygonal, possibly open on one side cross-sectional shape, as long as the piston member is guided therein reliably and form-liquid. The cross-sectional shape of the guide part or of the piston part guided therein must be neither circular nor polygonal in a certain way. An oval configuration of the cross section or a combination of different cross-sectional shapes is also possible.

Furthermore, the cantilever arms 53 and 54 need not be arranged on a common drive shaft; Instead, on both sides of the door opening coaxially mounted drive shaft sections may be present, to each of which a boom is coupled. The weight compensating device 6 can also be mounted on a separate bearing shaft.

In addition, it is also possible that the motor 51, the drive shaft 52 or the drive shaft sections and / or the counterbalance device 6 does not drive directly, but indirectly via timing belt, chains, gear, etc. With regard to a compact arrangement as possible, however, is a direct drive of these components preferable.

Moreover, it is for the roller door 1 according to the invention essentially irrelevant, which type of door leaf 2 is present. The inventively provided force on the lintel end of the door leaf 2 can be equally for lamellar armor, mounted in frame flexible hangings, door leaves as in the DE 102 36 648 A1 described, etc. apply. Depending on the type of door leaf 2 and / or the field of application of the roller shutter 1, it may also be possible to To dispense with the side guide rollers 22 on the door leaf 2 and this easy to lead sliding. This is particularly advantageous in applications of the roller door 1 for clean rooms, in the pharmaceutical industry, etc., as it can then keep better pure.

Furthermore, it is also possible to use such a weight compensation device in all the illustrated embodiments. In addition, such may also be arranged in both lateral frames. In particular, with door leaves with larger widths, this can be advantageous to reduce one-sided loads on the arrangement.

The number of coil springs 611 of the spring element 61 is determined by the given loads, i. H. in particular according to the type of door leaf, its weight and its dimensions. In addition, it is also possible to provide other resilient elements instead of coil springs such. B. elastic bands etc.

The tension element 62 does not have to be configured as a chain, but may also be present in the form of a ribbon. For this purpose, a dimensionally stable material, in particular a metal is preferable.

The number of guide sections on the guide device 63 depends on the length of the tension element 62 and thus indirectly on the door height. Accordingly, more or less than the described three guide sections can be given.

Furthermore, it is also possible to use a guide device, which has two guide spirals, which extend from a central portion with increasing radius axially further away from each other to the outside. This embodiment is particularly suitable in connection with a continuous or at least quasi-continuous from the end facing the winding device to the end facing the spring element in width widening tension element, which can be wound directly contactless and free of axial displacement thereon. In this embodiment, the tension element is preferably formed as a band.

Furthermore, it is not absolutely necessary to provide the transverse rods 25 according to the second embodiment, since the cross-bracing given over the uppermost lamella of the door leaf 2 is often sufficient.

Tolerance compensation by adjusting the distance between the door leaf and the coupling points of the cantilever arms can also be done in other ways than through the multi-part end portions 24. In particular, other devices can take over this function, if such end portions should not be given in one embodiment.

Claims (15)

1. A high-speed industrial roller door (1) having a door leaf (2) which covers the door opening and which is guided in lateral guides (3, 4), a drive (5) which acts on the door leaf (2) in order to move it from an open position into a closed position and vice versa, wherein in the open position the door leaf (2) is accommodated in a spiral section (32, 42), arranged in the vicinity of the door lintel, of the lateral guides (3, 4) in such a way that adjacent areas of the door leaf (2) are not in contact with one another, and having a weight compensation device (6),
   wherein the drive (5) has at least two extension arms (53, 54) by means of which it is coupled to a lintel-side end of the door leaf (2), wherein the extension arms (53, 54) are arranged spaced apart from one another in the width of the door and can be pivoted synchronously about a pivoting axis in a central area of the spiral section (32, 42), and wherein the distance between coupling points (533, 543) of the extension arms (53, 54) on the door leaf (2) and the pivoting axis of the extension arms (53, 54) can be varied,
   characterized
   in that the two extension arms (53, 54) are coupled to the lintel-side end of the door leaf (2) via joints.
2. The industrial roller door as claimed in claim 1, characterized in that the extension arms (53, 54) are telescopic.
3. The industrial roller door as claimed in claim 2, characterized in that the telescopic extension arms (53, 54) each contain a tubular guide part (531, 541) and a piston part (532, 542) which is guided therein in a freely displaceable manner.
4. The industrial roller door as claimed in one of claims 1 to 3, characterized in that the extension arms (53, 54) are arranged on a common drive shaft (52) which is driven in rotation by a motor (51) of the drive (5).
5. The industrial roller door as claimed in claim 4, characterized in that the motor (5) drives the drive shaft (52) directly.
6. The industrial roller door as claimed in one of claims 1 to 5, characterized in that the extension arms (53, 54) are coupled to an element (25) which extends over the entire width of the door.
7. The industrial roller door as claimed in one of claims 1 to 6, characterized in that the door leaf (2) has two lateral hinge belts (23) which are each arranged adjacent to the guides (3, 4), wherein the extension arms (53, 54) are each coupled to lintel-side end sections (24) of the hinge belts (23).
8. The industrial roller door as claimed in claim 7, characterized in that the lintel-side end sections (24) of the hinge belts (23) can be adjusted in length viewed in the direction of movement of the door leaf (2).
9. The industrial roller door as claimed in one of claims 1 to 8, characterized in that the weight compensation device (6) has a spring element (61), a tensile element (62) and a winding device,
   wherein one end of the spring element (61) can be secured to the floor,
   wherein the tensile element (62) is attached by one end to the spring element (61) and by the other end to the winding device,
   wherein the winding device can be coupled to a drive (5) of the lifting door (1), wherein the tensile element (62) can be wound onto the winding device and unwound from it in such a way that the spring element (61) has its highest degree of prestress when a door leaf (2) of the lifting door (1) is in the closed position, and is essentially relieved of stress when the door leaf (2) is in the open position,
   wherein the tensile element (62) has a smaller width at the end facing the winding device than at the end facing the spring element (61), and
   wherein the winding device has a shaft (64) and a guide device (63) which is mounted thereon and by means of which the tensile element (62) can be wound up in such a way that the winding layers are not in contact with one another, wherein, for this purpose, the guide device (63) has, on the circumference, guide faces with a radius which increases continuously in the winding direction.
10. The industrial roller door as claimed in claim 9, characterized in that the width of the tensile element (62) increases incrementally from the end facing the winding device to the end facing the spring element (61), and in that the guide device (63) has at least two guide sections (631, 632, 633) which are each embodied in the form of a spiral and are offset axially with respect to one another in such a way that an outer guide section pair (632a, 632b) whose minimum guide face radius corresponds to the maximum guide face radius of the inner guide section (631) adjoins an inner guide section (631).
11. The industrial roller door as claimed in claim 9, characterized in that the width of the tensile element increases continuously from the end facing the winding device to the end facing the spring element, and in that the guide device has two guide spirals which, starting from a central section, extend axially further apart from one another toward the outside with an increasing radius.
12. The industrial roller door as claimed in one of claims 9 to 11, characterized in that the tensile element (62) is a chain.
13. The industrial roller door as claimed in one of claims 9 to 11, characterized in that the tensile element is a belt.
14. The industrial roller door as claimed in one of claims 9 to 13, characterized in that the spring element (61) has at least one helical spring.
15. The industrial roller door as claimed in one of claims 9 to 14, characterized in that the guide device (63) is mounted on the drive shaft (52) on which the extension arms (53, 54) are arranged.

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