SI9110990A - Lifting Door with Lamellate Shield in Guideways - Google Patents

Abstract

Until now known lifting door as a door guard openings at which the door leaf is guided laterally and lifts vertically, they do not have because of their construction sufficient fast-flowing properties and, when running, cause excessive noise. The lifting doors of the invention comprise guides (2) arranged on both opposite sides sides (3) of the door opening (1), and lamellar armor (12) with blades (14), which are spaced apart mounted on hinge straps (20) to shamrock the studs (24, 24 ') inside the space (34) grip between adjacent lamellae (14). Use of lift doors as high-speed doors.

Description

Lifting doors with slats in guides

EFAFLEX TransportLagertechnik GmbH

The invention relates to a sliding door with lamellar armor, which can be transported vertically upwards from the closed to the open position of the door opening in guides.

As an example of sliding doors, roller shutters are known as the vertical opening closure of a passage or transport door, which shutter door is typically composed of roller shutter consisting of angularly adjustable slats on each side of the door opening by means of vertical guideways rails guided to the closed position, the winding shaft on which the shutter armor is attached and by means of which the latter is raised and retracted in the open position, the electric drive, as well as the catching device that prevents the roller armor from collapsing, in case the drive fails.

Roller shutter, as part of a roller shutter, which closes and protects the door opening, consists of articulated interlocking lamellae, generally profile sections, e.g. of extruded aluminum materials. The height of each blade is generally about 80 to 120 mm. These profile sections are mainly intended as insertable profiles which, due to their design without joint members, are articulated to one another by roller armor. In a typical aluminum extruded prod, the joint is designed e.g. as a pan and a bridge, so that when the profiles are pushed into each other, such a designed joint can receive and transfer when winding the shutter armor of the acting force. According to all the rules, the lamellar joint of the blades has a large clearance. In addition, the molding of the extruded profiles should be designed in such a way as to prevent the accumulation of dirt and water in the joints and to ensure sufficient tightness against wind gusts.

The bundle layers on the winding shaft are formed by interconnected profiles having a certain profile height. Each profile rests on the most protruding edge of the profile below. Direction by the cross section of the bundles within its layer

21619PR0.IV The bundles occupy the profile and follow the profile contact point. Its randomly occupied position redefines the layout of the next associated profile. This results in an incorrect arrangement of the layers of individual roller shutter profiles in the coiled bundle. It follows, inter alia, that e.g. only a single edge of a single roller shutter profile supports the entire load of the free-hanging section, which can result in significant edge pressures.

To protect against lateral displacement, the flanges or flanges are usually attached to the sides of the roller shutter profiles. fins running in corresponding vertical guide rails with the rule as a U-shaped cross-section. These vertical guides are funnel-shaped at their upper inlet so that the roller shutter can flow into the vertical guide without obstruction without the risk of being hit.

With its initial profile, the roller shutter is so fastened to the winding shaft that the fastening with the door closed is located away from the armored side of the shaft, ie. that armor or. armor extending the end plate encloses the shaft by at least 180 °. This ensures that the armor is broadly supported by friction forces, thus not reducing the full weight of the armor to the hangers. The door is closed when the end profile is in close contact with the lower edge of the opening, ie. generally to the ground. Otherwise, the shutter armor should not collapse. The entire armor - up to the end profile - remains as hanging as the load on the shaft, or. shaft axles. In this case, in general, the shutter door is fundamentally different from the threaded window, which is mainly intended as an additional opening closure.

In the open position of the shutter door, the shutter armor in the area of the upper door crossbar of the door opening is wound on the winding shaft. The drive is mostly secured to the upper door leaf and therefore cannot be damaged by the vehicle in the driveway. As a rule, an electric motor is generally provided, resulting in a manually operated auxiliary drive.

In electric motor drive, the roller shutter shaft is driven by a constant speed, ie. with constant angular velocity. This raises the roller armor attached to the shaft and winds it on the shaft. First, the effective winding radius, which is constantly increasing when winding, is crucial for the lifting speed, since the lower parts of the roller shutter rest on the already wound upper parts. As the lifting speed changes in a disproportionate proportion to the radius of the envelopes, the shutter doors run slowly upwards first, in order to flow faster towards the upper part. When observing the kinematic conditions closely and keeping in mind the thickness and height of the profile, it is

21619PR0.IV Observe the required roller armor enclosure as a polygon. When winding, the profiles first rest on the round winding shaft. Flat profiles form a polygon on it. The corners of the polygon are farther away from the center point of the shaft than the center of the side of the polygon. If the roller shutter shaft now rotates at a constant angular velocity, the shutter armor is pulled upwards once with one lever corresponding to the length to the corner point of the polygon, and to that length of the lever corresponding to the lifting speed, and at the next moment with a lever corresponding to the length to the polygon side, and with this proper lifting speed. The lifting speed is directly proportional to the operating, unsteady and irregularly occurring levers, and is therefore characterized by sufficiently strong and instantaneous oscillations when winding the shutter armor. In this connection, highly variable mass acceleration and deceleration of the roller armor mass occur, which remains to be wound. These mass accelerations also pass into the gearbox of the drive machine, which must be designed for the proper degree of unevenness, otherwise failure may occur. In principle, these accelerations become smaller as the thickness of the roller shutter door becomes thicker. the closer the polygon approaches the circle. However, since the greatest mass acceleration and deceleration occur when the shutter armor is still far below, these forces are thus multiplied on both sides by the considerable inherent weight of the shutter armor.

The mass acceleration and deceleration of the developed shutter armor are reflected as oscillations. These oscillations also act on the building's winding shaft, so when static calculations are made, care must be taken to keep its own oscillatory number outside the shutter frequency. Otherwise, the lifting speed of the shutter door needs to be drastically reduced. With the angular velocity of the roller shutter shafts unchanged, the frequency of oscillations increases and their amplitude decreases with the thickening of the roller shutters. This means that the sound of the shutter door develops more strongly, the longer the shutter armor comes down.

In addition to the aforementioned irregularities of the manual ratios in the winding of the profiles in the form of a polygonal course, there is a further reason for the roller shutter known so far, which also leads to extremely problematic kinematic conditions. As the driven roller shutter shaft cannot exert any compressive force on the roller shutter, it is necessary to ensure that in the upward lifted state, the weight of the free-standing roller shutter armor with the lower rail is greater than that of rest. Only then, as a result of its own gravity, the armor automatically moves when the shaft is driven in a downward direction. The minimum friction for the armor is given when upwards

21619PR0.IV Rises perpendicularly to rails in raised state. This input method is called normal layout. Depending on how far the roller shutter is unwound, the diameter of the sheath is reduced. The armor then fades into the guides. When the roller shutter is completely drained, but - as is the case with roller shutters - it still hangs in tow on the shaft, the whole weight of the roller shutter, depending on the circumstances, hangs on only one profile on the shaft of the profiles. Observing a vertical cross section through the roller shutter door, we learn that the pulling force of the entire net weight of the armor lies not in the plane of the door, but in a straight line connection from the bottom piece to the effective radius of the sheath. The roller shutter is deformed in the middle between the guides in order to get as close as possible to the tensile stress. The profile ends, however, are held by the guides and cannot follow the tensile line. While the tensile stress resulting from the sheer weight of the shutter armor pulls the armor from the door plane in the direction of the shaft at the top, they bend the guide ends of the profile ends back to the door plane. In this way, the individual profile ends are not only loaded on bending but also on the grip. In doing so, the greatest bending and twisting moments occur at the inlet.

In order to reduce the normal layout of the sealing problems that occur at the time of installation, it has been suggested that the bending of the shaft will be limited by the installation of a pressure shaft. In doing so, we lease the quieter and noisier running of the shutters (cf. Horst Giinter Steuff, Das RolltoF, Diisseldorf, Wemer Verlag GmbH, 1987, p. 93).

The unfavorable kinematics described above, in its basic features, have been known as (for now, barely modified) roller shutters for more than a hundred years, as the main reason for the development of running noise, and lastly for the unsatisfactory property of fast running. Essentially, the profile noise resulting from running joints occurs mainly in the upward movement of the roller shutter door, and then especially strongly in the lower third of the door opening as long as the roller shutter door is in the normal position. Noise is generated near the passage where the profiles bend, are loaded with high tensile forces, and are said to rotate in the joints.

Although the roller shutter doors known to date have been considered as a cost-effective solution for a long time due to their force and shape-locking blades with regard to wind pressure tightness and safety against undue opening, the poor fast-rolling properties of conventional shutters when used as industrial doors were soon recognized as defective. At normal shutter speeds, the running speeds are about 0.25 to 0.35 ms' ¹ .

21619PR0.IV

In the industrial field, high-speed roller shutters with a flat door leaf made of flexible material, which can be wound on a winding shaft or winding drum, also acted as an additional closing of the openings. Such roller shutters also offer the advantage of optical transparency when selecting the flexible material appropriately. They are widespread, for example. Macrolon foil or soft PVC foil. This advantage over opaque materials, however, is lost over time, as optical transparency is affected by the induction of dust and the like in the winding of the foil and the associated surface entrainment.

Given the limited space available above the area of the upper doorway and the large diameter of the shaft core, which is common in shutters made of foil, the foils of such shutters must be as thin as possible, otherwise the winding diameter becomes completely too large. In addition, using a thin film to allow for faster neck movement at the same time for easier winding. The smaller thickness of the foils and the corresponding lower self-weight of the door leaf lead to reduced wind strength. As an aid, it has been suggested here to provide for additional weight in the form of a spacer end profile arranged on the lower edge of the door leaf or spring-loaded tensioning straps running over the floor-mounted tensioning rollers.

The biggest drawback with foil shutters therefore comes from the behavior of the door leaf at wind pressure, which is closer to the sail behavior than to the plate behavior. As the door leaf is supported only on the winding shaft, the door leaf is significantly inflated and protruded under wind load and consequently raised. Therefore, given the lack of security against undue opening, such shutters are only intended as an additional door opener.

These are further known. sectional doors, also used for large door openings. Conventional sectional doors consist essentially of armor with suitably high sections that can be switched from a vertical closure position to an upper position below the ceiling by means of a pulley.

With the proper height of the individual sections used for sectional doors, a mechanically completely more compact construction method is achieved with a correspondingly better construction based on the reduced number of connecting elements of the sections, such as hinges or the like, and also the reduction of the number of front faces to be sealed. strength against wind, as well as safety against undue opening. Furthermore, the high height of each section allows for transparent sections in the form of glass or plastic windows.

21619PR0.IV

The compact construction method for sectional doors further enables the provision of lightweight aluminum sections that are filled with, for example, thermal and acoustic insulation. plastic materials to allow e.g. Garage doors also open and close manually at larger door widths without additional electric motor drive.

As a rule, in the closed position, the individual sections are aligned with each other so that the entire front face of one section is always available for sealing. The sectional doors thus appear to be a beautifully closed door with a continuous outer surface, without any intermediate gap. Further improved sealing is achieved e.g. with rubber inserts, which are pressed together in a closed position with one another by a cross-section. Alternatively, sections along the front of the entire width of the door comprise a protuberance which, as a pen-groove connection, engages the corresponding deepening of the adjacent section when the section is rotated in the same plane, which further improves the mechanical strength of the door leaf against wind pressure even at larger door widths.

On the inside of the door, the sections are connected by a series of individual hinges, which are positioned at regular intervals throughout the width of the door to give sufficient strength and support. The hinges arranged on the side edge of the sections are generally designed at the same time as a roller holder which, at the edge region of the sectional door, can run in a guide rail with a U-shaped cross-section. Because the individual hinges are so attached to the sections that they can be swung inwards, there are problems to the extent that the hinged parts of the hinges are optically disrupted on the inside of the door and present a risk of injury. A further risk of damage to the sectional doors is the bending of the sections with the resulting open slits or openings. when twisting the sections backwards and closing the slit.

A further disadvantage of sectional doors with relatively high sections is given in relation to the arched guide portion above the area of the upper doorway where the individual sections are rotated from vertical to horizontal. This swing, of course, leads to sudden overturning acceleration and, accordingly, in rapid manipulation to the considerable force action on the individual sections. As a result of the different radial deviations of the guide cylinders from the actual position of the section in the upper path of the curve, acceleration and deceleration forces occur, with the overall uneven flow of forces due to the flat design of finite-height blades acting as a polygon in the curve, that sectional doors can as a rule

21619PR0.IV only operate at lower running speeds, without the risk of increased noise.

The transverse forces transmitted through a series of individual hinges also accommodate the bodies of the sections, thereby loading them. As the sections are twisted, the forces applied to the edge shims and the corresponding guide rail essentially depend on the speed of opening and closing the sectional door. Due to the design not generally designed for high speeds, the use of sectional doors as high-speed industrial doors is limited.

In the case of sectional doors, a pulley with pull and support ropes as well as a rope drum is arranged as a drive system as a rule. In the upward movement of the door, the support rope is pulled against the rope drum, while at the same time the rope is pulled from the rope drum. With the downward movement of the door, the tow rope will bend and pull the door down, while, at the same time, the support rope will be unwound from the rope drum without delay. The load rope is thus constantly loaded on the tension and cannot run past the rope drum. The drive of the drive shaft is monitored by an electric motor, e.g. arranged directly below the ceiling.

To compensate for the weight of the door leaf, torsion springs are provided in a known manner, arranged coaxially to the passing drive shaft. In the closed position of the door, the torsion springs are fully tensioned and are relieved when lifting the door leaf upwards. These torsion springs are subject to high wear and therefore have a long life span. Particularly with the frequent and abrupt change of direction of movement of the sectional doors, torsion springs suffer from the backward motion of a considerable dynamic stress peak. With the failure of the torsion springs, the accompanying maintenance and replacement parts are of course time consuming and extensive for the sectional doors.

Due to the arrangement of the drive shaft with torsion springs over the arch and the electric motor in the vicinity of the drive shaft, the conventional sectional door must take into account the considerable need for space above the top door crossbar, which, without special structural measures, such as eg. to provide a double horizontal guide below the ceiling or to equip a drive shaft with torsion springs at the far end of the running rails, not exceeding a typical value of 400 mm. In addition to this, sectional doors have an excessively large space requirement, essentially corresponding to the bright height of the door opening. Since the available free space is in depth, i.e. the dimension between the trailing edge of the upper doorway and the next obstacle in the depth of space, such as underscore,

21619PR0.IV A wall, vent, fan or the like, generally tightly measured, in many cases cannot be fitted to a known sectional door.

It is an object of the invention to create a lift door that allows for rapid noise reduction when opening and closing doors, while providing in the closed state sufficient tightness against the effects of wind and weather as well as security against unjustified opening, and consequently also required for large doors Heights only a small space above the upper doorway.

This task is accomplished by a sliding door with features as claimed in claim 1.

In the case of a sliding door according to the present invention, the guides, each arranged on opposite sides of the door opening, are designed so that, starting from a vertical section extending vertically about the height of the door opening, the guides extend into a helical, outwardly extending spiral door. section. This means that even at higher door heights, the required space for the lamella armor in the open position at the depth of the door is kept as small as possible, without the need for a substantially elevated height above the top door bar. According to the invention, the lamellar armor is transportable in the helical section of the guides in the open position of the lifting door, so that a series of lamellae enters the spiral path and are completely homeless to each other, so that no friction or friction forces are applied to the lamellae. compressive forces, thereby enabling significant lifting gate speeds without creating excessive noise. The door openings of the overlapping blade of the lamellae armor are designed to be angularly positioned and made of rigid material so that the lifting doors in the closed position have sufficient mechanical stability to withstand higher wind loads and to provide security against undue opening.

For the adaptation to different door heights, according to claim 2, extension sections are provided, which are essentially simply horizontally inserted into the helical section of the guides.

According to a further embodiment of the invention, it is contemplated according to claim 3 that the guides are designed as a pair of rods of circular cross-section so that particularly elongated sections of guides can be produced.

According to claim 4, a mass balancing comprising a balancing spring and a strap fastened to the latter, which can be wound onto a co-operating shaft together with the lift gate drive, is provided as an improvement of the lift gate drive according to the invention.

21619PR0.IV predefined core diameter. The main advantages of this mass balance lie mainly in the extended life of the mass balance without the need for additional transmission means to achieve the desired characteristics.

The actuator, which is preferred over the possible running speeds of the lifting doors according to the invention, comprises, according to claim 5, an endless chain driven by an electric motor that is fixed in place on the lamellae. The endless chain is guided in such a way that, when traveling up and downwardly pulling the lamellae, the gripping traction forces are completely in the plane of the door leaf.

According to claim 6, a sealing lip is arranged horizontally along the entire door width as the upper end of the door opening, which prevents rain, dirt or the like from entering the upper area of the lift door.

For the sake of further characterization, we refer and refer to the parallel German patent application of the same applicant of today, entitled Lifting doors with lamellae with angularly adjustable slats (agent sign 11EF01412) or. Opening element (agent sign 11EF01432).

Further features and appropriateness of the invention are illustrated by way of the figures from the following description of an embodiment, where FIG. 1 is an exemplary view of a sliding door according to the invention in partial lateral view; 2 is a partial rear view of the rear panel of the slats according to the invention, FIG. 3 is a schematic view of the section along line III-III of FIG. 2, FIG. 3A is an enlarged detail X of FIG. 3, FIG. 4 is a plan view of the lamellar armor of the present invention; 5 is a cross-sectional side view of a sliding door according to the invention, FIG. 6 is a schematic side view of a mass balance representation of an embodiment of a lift door according to the invention, and FIG. 7 features in FIG. 6 shows the mass balance according to the invention.

As illustrated in FIG. 1 and FIG. 4 shows the exemplary embodiment of the lifting doors according to the invention guides 2 and 2 ', which are each arranged on both opposite sides 3 and 3' of the door opening 1. Hereinafter,

21619PR0.IV the reference numbers in each case of the corresponding portions of the lifting doors arranged on page 3 ', so that it is no longer necessary to make explicit reference thereto. Each guide 2,2 'comprises a vertical section 4 extending vertically from the door opening extending about the height of the upper door rail 6 and extending into the spiral inwardly extending helical section 10 in the upper edge region of the door opening at the inlet 8 of the lift door. The lamellar armor 12 for covering the door opening with a light door height h in the closed position is transportable upward into the helical section 10 of each guide in the open position of the lifting door, so that the lamellar armor is arranged spirally without touching the adjacent lamella 14 side by side. An endless chain 16 and an electric motor 18 are provided as the drive for the lamella armor 12.

In FIG. 2, 3 and 4 show the details of the lamellar armor according to the invention. On each side of the lamella armor 12, a shimmer strip 20, 20 'is provided in each case, comprising a length substantially corresponding to the height of the neck opening 1. Each shimmer band 20,20' consists of rigidly shamer members 22, which are connected jointly and through each other. shamer plugs 24, 24 'angularly set against each other. Each shamiric member is in a known manner at its end attached to a rolled eye into which a shamiric plug can be inserted 24. Each adjacent hinge joints are articulated to each other so that their eyes are coaxially arranged to each other in which they are supported. total shamir plug 24.

In the foregoing example, coaxial to the shammer studs 24, 24 'roller bearings 26,26', which serve the roller guides of the shammer belts 20 and 20 'in the guides 2 and 2' are further provided. In the example shown, each guide comprises a pair of rods 28 and 30 of circular cross-section, spaced at regular intervals with each other, which spacing is selected fitting to the diameter of the cylinders 26. The hinge straps 20, 20 'and the rods 28, 30 are made e.g. . made of solid metal material, while cylinders 26 may also be made of plastic. To protect the lamella armor against the failure of the guide, each cylinder 26, 26 'has a holding flange 27, 27' whose outer diameter is greater than the bright bar spacing 28.30.

The slats 14 are e.g. by means of screw connections 32, 32 'so arranged and secured to the hinge straps 20, 20' that, by the resulting spacing of each adjacent lamellae 14, a space 34 is accommodated, into which the shamir studs 24, 24 'or. the hinge plugs comprising the eyes of the hinge members 22, 22 ', as best illustrated in FIG. 3. Thereby, it is achieved according to the invention that the geometrical pivot axis 36 is completely within the region,

21619PR0.IV bounded by the outer main surfaces 38 and 40 of the lamella armor 12. By this position of the articulated axis 36, the opening width of the angle between adjacent lamellae 14 is reduced to a minimum by the angular positioning of the lamella armor, accordingly Reduces tipping acceleration when imported into the top bent bus. This further increases the possible running speeds of the lift doors shown without creating excessive noise.

Blades with height e.g. up to 150 mm are completely independent of each other and individually mounted on shamrock strips 20, 20 'such that e.g. the lack of one whole blade does not entail any influence on the mechanical stability and mode of operation of the sliding door according to the invention. The hinge straps 20, 20 ' form a kind of load-bearing frame. the skeleton of the lamellar armor, which takes over everything in the movement of the lifting door of the force generated. Due to the mechanical all-round holding of the hinge straps 20, 20 'together, the tensile forces take over the hinge straps 20, 20' and are not transferred to the blades 14. By transferring and distributing the corresponding forces on the articulated, continuous but tensely rigid strap, even at extremely fast travel the lifting door achieves a steady and smooth movement.

Since the individual lamellae 14 are first positioned at a suitable distance from each other on the hinge straps 20,20 'in order to create space for the hinge studs, the adjacent lamellae 14 are also in contact with the closed position of the door to each other, thus leaving the usual sectional doors, the familiar carbide noise of the closing doors of the sliding doors according to the invention is also completely eliminated.

To enhance the mechanical stability of the lamellar armor and to increase the tightness without compromising the properties of the submitted lift doors in terms of noise, sealing strips 42 in the form of rubber strips are provided, which are arranged approximately over the entire door width between the hinge straps 20, 20'j and interconnecting opposite sides of adjacent blades 14. Each of the seals of the laths 42 is coaxially spaced coaxially to the adjacent hinge axis 36 such that the sealing rails 42 are loaded solely by bending at the angular placement of the blades 12 in the upper guide region. The sealing rails 42 only grip with less lateral clearance in a direction perpendicular to the plane of the door leaf in the louvers 14, so that the louver armor 12 under pressure exerts a stress on a certain point, with corresponding back forces immediately acting against the pressure load. Each sealing strip 42 comprises, on opposite sides of the groove or bale 44, which grip into properly formed

21619PR0.IV cutouts of slats 14.

As can be seen most clearly with the enlarged cutout of FIG. 3A, each thickening 44 comprises a support surface 43 arranged opposite the corresponding retaining surface 45 of the blade 14. The offset of the support surface 43 from the respective retaining surface 45 of the blade 14 is - with respect to easy and interfering, secure mounting by inserting the sealing strip 42 with the bushings 44 from side to recess 46 - selected as small as possible so that, in the closed position of the lamella armor, it causes the sealing strip 42 to roll sideways and, after touching the insertion of the support surface 43 with the holding surface 45, load the sealing strip 42 to a tension adjacent lamellae. At even smaller deviations of the observed lamellae from the plane of the door leaf, ie. as long as the support surface 43 does not touch the opposing support surface 45, the sealing strip 42 to the adjacent lamellae is only stressed by bending, leading to this corresponding return force. Since the distance between the supporting surface 43 and the associated retaining surface 45 is chosen minimal in order to maintain the tensile load of the sealing strip, even with minor deviations, the resulting pressure loads on the lamellae from the first directly affected sealing strip 42 are transferred and distributed. also to adjacent seals. Under compressive loading, the lamellar armor of the invention therefore preferably behaves as a homogeneous flat plate with a proper force distribution in the plane of the plate, however allowing slight bending. Therefore, the sealing rails 42 cause a significant increase in the mechanical stability of the lamellae, so that the lifting door in the closed position without further resistance to high wind or otherwise compressive loads.

Of course, the lifting doors of the invention offer sufficient security against undue opening, so that the lifting doors of the invention can be provided as a permanent closure of the door opening.

In order to protect against withdrawal of the lamellae 12 in the event of the occurrence of even greater compressive forces, retaining flanges 27, 27 'are arranged on opposite sides of the lamellae, which in the embodiment shown are designed as outer plates with a larger diameter than the diameter of the cylinders 26, 26'. The mounting flanges 27, 27 'are so arranged with a smaller distance (not more closely spaced in the plan) from the adjacent support surface of the guide rods 28, 30 that they tend to support only with a very strong bending of the lamellae 14 when loading on the outside of the guide rods 28, 30 , so that the lamellar armor can withstand relatively low compressive loads

21619PR0.IV serviceable and transportable. By describing the well-distributed force distribution along the door plane 42 in the plane of the door, even at point load, the retaining flanges 27, 27 'of the loaded lamella 14, with a strong bending thereof, are prevented from supporting them early and thus obstructing the movement of the lamella armor.

In the embodiment of FIG. 3 comprises each of the blades 14 of the sealing nose 48 projecting on the outside 38 in the plane of the door leaf, which causes the nose 48 to reduce the distance from the adjacent blades. Due to the sealing nose 48, the sealing strip 42 is no longer recognizable in the closed position of the sealing strip 42. The sealing strip 42 is then visible only from the inside (see rear view according to Fig. 2). At the same time, it is based on FIG. 3 shows embodiments of the sealing nose 48 given a more beautiful appearance of the lamellar armor 12 in the form of a uniformly smooth plate.

In order to protect the fingers and thus to prevent injury by accidentally touching the moving parts, according to FIG. 4, at each inner and outer side of the door opening, sealing lip 50, 50 'projecting in the closed position projecting to the position of the sealing strips 42 in the plane of the door leaf. On the outside of the door opening 1, the sealing lips located at the same time form a seal against surfaces, dust, or the like. The lip seals may be made again e.g. made of rubber.

In cross-section, an analogously designed sealing lip 52 is disposed in the region of the upper doorway 6 (Fig. 5) and extends horizontally essentially along the entire width of the door opening. The sealing lip 52 prevents rain or dirt from entering the upper area of the liftgate.

In order to seal the lifting door from the floor, FIG. 3 intended conclusion 54 e.g. made of rubber, which is attached to the uppermost lamella.

As already explained by FIG. 1, the lifting doors of the invention include guides 2 and 2 'which, in the upper door area and under the ceiling, designated by reference 55, are designed as a spiral inwardly spiral section 10. In the open position of the lifting doors, the lamellar armor 12 is thus transportable in spiral section to take a series of lamellae spiral course and not touch each other. In the opposite of the known roller shutter doors, in which the shutter armor is wound on the winding shaft, according to the invention, the lamella armor is continuously guided so that the slats do not touch each other anywhere. This completely avoids the roller shutter door's emerging compressive forces on the slats so as to allow a sufficiently smooth running that allows high speeds. Unlike conventional sectional doors, the upper rail is not guided as a straight line

21619PR0.IV directly below the ceiling, which, especially at higher door heights, led to a considerable need for space in the door depth. Contrary to this, the spiral section 10 corresponding to FIG. 1 shows the three separate sections 56, 58 and 60. As shown, the portion of the separate section 60 directly to the separate section 56 so that the inner radius of the arc 56 approximately corresponds to the outer radius of the arc 60. The outer radius of the arc 58 corresponds to the outer radius of the arc 56 .

According to FIG. 1, the smallest possible radius of curvature of the guide 2 is equal to the radius of the most within the lying separate section 60. This radius is selected so that, depending on the distance from the adjacent hinge plugs (see Fig. 3), the correct entry of the lamella armor 12 in spiral section 10, without having to bake e.g. self-locking of angularly placed lamellae in a narrow, separate section. Such self-restraint would later occur when, at the inlet of the lamella armor 12, the direction of the rolling friction force directed at any point in the direction parallel to the guide is smaller than the correspondingly effective rolling friction proportion, which is again proportional to the normal force available at that location. . In practice, however, the minimum possible radius is limited by the fact that the angular positioning of the slats of the sealing strip bends, thereby producing the return forces that the lift gate drive must overcome and the greater the narrower the arc.

The helical arrangement of the guide 2 optimally utilizes the available height g above the area of the upper doorway. Separate sections 56, 58, 60 can be manufactured in a standardized manner for all practically occurring door heights, so that the lift doors according to the invention, independently of the respective door height, offer the advantage of a uniform height above the upper door bar. Adjustment of the entire bus length to the appropriately used single door height is ensured by separately inserted, horizontally extending extension sections 62 of length a. In the example shown, by inserting extension sections 62, the length of the common bus 2 increases by a total of 3x. Because these extension parts are essentially individual parts of a lift door that must be individually manufactured or made. made available to the door height appropriately, the lifting door of the invention can be manufactured to a large number of pieces at an affordable price, which can be used for everyday needs outside the industrial field.

Specific numerical values are given below for further illustration. At normal bright door heights h = 3 tn, 4.5 m, 6 m, the values of extension sections 62 are each a = 0 m, 0.5 m, 1 m, so that at a fixed value

21619PR0.IV The installation height above the upper door g = 0.5 m, when increasing the bright door height from 3 m to 6 m, the need for space increases only by 1 m in depth. The diameter of the cylinders 26 and thus the clear distance of the guides are about 4 cm. In this arrangement, e.g. fully open the door h = 3 m in no less than 2 s.

According to FIG. 1, an electric motor 18 is arranged in the open space remaining in the interior of the spiral section 10, which is in connection with the drive cylinder 64. The line-dotted line in FIG. 1 is a schematic representation of an endless chain 16 driven by a drive roller 64 and a moto 18 driven by rotary rollers 66, 68, 70 (Fig. 5) and 72. On the opposite side of the 3 'door there are (not shown) rotary rollers corresponding to rotary cylinders 68, 70, 72, of which one rotary cylinder is e.g. via a clutch and a torsion shaft, a rotary rigidly connected to a gear wheel designed by the rotary roller 72, which drives a further (not shown) endless chain. At this point, as a further advantage of the lifting door according to the invention, it is observed that, depending on the desired door width, the torsion shaft represents a single mounting element which can be custom-made at the appropriate length.

In the region of the lower lamella, an endless chain 16 is fixed to the lamella armor via a strap 74. According to FIG. 5, the connection of the chain to the lamellar armor is most expediently provided in such a way that the gripping tensile force in the upward movement of the lamellar armor from the closed to the open position extends completely within the plane of the door leaf, thereby avoiding a horizontally flowing force which could lead to a torque. lamellae armor, which would exert force on the guides, trying to push the guides apart while the cylinders would be subjected to increased wear due to the massive load.

The stirrup 74 further comprises e.g. protruding, rigid end 76 which, in the open position of the door, almost without noise, hits a rubber bumper 78 disposed above the upper door crossbar.

According to FIG. 6, a mass balancing act 80 is provided for adjusting the actuating gate of the acting tensile force to the respective mass of the free length of the lamellar armor, comprising a balancing spring 82 and a strip 84 of as inelastic and tensile-solid material attached thereto. The lower end, as a helical spring of the designed leveling spring 82, is firmly connected to the ground. Through the roller 86, the strip 84 is secured by a shaft 88 which e.g. over in Figs. 1 and 5 of the rotating roller 72 shown interact with the lift gate actuator by strapping the strap in upward movement of the slats

21619PR0.IV unscrews the shaft 88, the spring 82 is relieved accordingly, and when lowering the lamella armor, the strap 84 is applied with a suitable tensile force to the leveling spring 82 so that they are tensioned and secured to the shaft 88.

Shaft 88 comprises a predetermined diameter of the core, the value of which is selected such that, depending on the thickness of the strip 84, length L, _{of the} resting springs 82, the spring hardness of the balancing springs 82 as well as the total weight of the lamellar armor, the desired mass balancing characteristic 80 of FIG. 7, corresponding to the door height.

In FIG. 7 is for e.g. light door height 3 m to the right in mm Applied each time the clear height of the remaining door opening giving a value of 0 mm completely closed and a value of 3000 mm fully open door and upwards the actuated total mass G _{T of the} free lamellae as full line, and also the actuated spring force F _f as a dashed line. Kotse can see from FIG. 7, the mass balance 80 is so adjusted that, when the door is closed, the balancing spring is so far compressed that an excess spring force of about 260 N. is available through the mass of the lamellar armor. without additional propulsion up to almost the height at which the mass force of the free lamellae is in equilibrium with the appropriate spring force. In FIG. 7 means the point where the lines intersect, ie at a height of about 1 m. In the further upward movement of the door, the respective mass force is in equilibrium with the active mass force, so that the actuator must essentially only act against the available friction forces. Further details can be read directly from FIG. 7 without further clarification.

For spatial reasons, a lifting gate according to the invention provides a mass balancing on each side of the door with at least one counterbalancing spring in each case.

The mass balance presented here has decisive advantages over the known solutions. Compared to the torsion springs used in conventional sectional doors, the service life of the designed counterbalancing spring is significantly increased due to its use as a helical spring. The life span of the coil spring is almost twice the life of the torsion spring. This reduces the problem of permanent replacement of power units in sectional doors. Otherwise, the side balancing springs 82 have no need for space above the upper doorway.

A further advantage of the mass balance according to the invention is given by using a strip 84, the thickness of which is 2 mm, as appropriate. In this case, at

21619PR0.IV In particular, the use of wire rope required the further transfer of e.g. in the form of a free cylinder, since the rope can only be wound side by side with the drum, with a sufficiently large core diameter. However, according to the invention, the belt can be wound onto a shaft protrusion with a relatively small core diameter without breaking the belt, so that an additional transfer means can be dispensed with. In addition, the strap curves over each other so that, as desired, the winding radius increases rapidly when the door is open, but changes slightly with the door fully closed when the door is closed.

As can be seen without further notice, the mass-balancing characteristics described in the specific manner described above have special significance in combination with the further features of the present invention, but also have the independent meaning that these advantages can be applied in general, regardless of the details of the door construction method.

Claims (6)

PATENT APPLICATIONS A lift door with lamellae (12) comprising a series of rigidly shaped lamellae (14), a door opening width (1) overlapping, and angularly adjustable faces and guides (2, 2 ') arranged on either side door (3, 3 ') of the door opening (1), and projecting from a vertical opening about the height of the door opening (1) of the running vertical section (4) at the inlet (8) of the lift door, extending in a spiral inward direction a spiral section (10) in which the rails (12) are so transportable when the lift doors are open that the set of slats (14) is in a helical line and is not in contact with each other. Lift door according to claim 1, characterized in that the helical section (10) of the guides (2, 2 ') comprises a substantially horizontally extending, separately insertable extension section (62). Lift door according to claim 1 or 2, characterized in that the guides (2, 2 ') are provided as a pair of bars (28.30) of circular cross-section. A lift door according to any one of the preceding claims, characterized by a mass balancing (80) for adjusting to the actuating the lifting door of a working tractive force, each weight of the free length of the lamella armor, wherein the mass balancing (80) comprises a tensile or compressive load balancing spring (82). ) and a strap (84) fastened to the latter, which can be wound into one another by wrapping a shaft (88) which cooperates with the lift gate drive and which has a predetermined core diameter. Lift door according to one of the preceding claims, characterized by an endless chain (16) connected to the lamella armor (12) and which can be driven by an electric motor (18). Lifting door according to one of the preceding claims, characterized by a sealing lip (52) arranged horizontally at the inlet (8) of the lifting door over approximately the entire door width and projecting perpendicularly to the plane of the door leaf into the guide area (2,2 '). .