EP0531320B1 - Vertical lift gate with strip cladding in guideways - Google Patents

Abstract

The gate of the invention comprises two guideways (2, 2') arranged on the opposite sides (3, 3') of the gate aperture (1) and strip cladding (12) with strips (14) arranged on hinge frames (20, 20') spaced in such a way that the hinge pins (24, 24') engage inside a space (34) between adjacent strips (14).

Description

The invention relates to a lifting gate according to the preamble of claim 1 with a lamellar armor which can be moved vertically upwards in guideways from a closed position into an open position of a gate opening.

From GB-A-1 172 560, for example, such a lifting gate with a multi-blade slat armor is known, which can be moved by means of spiral-shaped guiding devices arranged at the edge of the lifting gate opening. The spiral guide devices consist of curved and straight sections, the clear widths of the curved sections being always larger than the straight sections, so that a smooth entry into the spiral guide device is possible.

From CH-A-282 658 a lifting gate is known, in which a guide device in the form of round bars is provided, by means of which the lifting gate can be guided over rollers.

As a further example of a lifting door, a rolling door is known as a vertically opening closure of a door opening that can be walked on or driven on, which conventionally essentially consists of a roller shutter consisting of mutually angled slats which are guided into the closed position on the two side edges of the door opening by means of vertical guide rails. a winding shaft, to which the roll armor is fastened and by means of which the roll armor is raised and wound up into the open position, an electric motor drive, and a safety device which prevents the roll armor from falling if the drive fails.

The roll armor, as the protective part of a roller shutter that closes the door opening, consists of articulated slats, usually profile parts, for example extruded aluminum works. The height of the individual slats is usually about 80 to 120 mm. These profile parts are mostly provided as slide-in profiles, which due to their shape are connected to each other in an articulated manner without further connecting links to form the roll armor. In a typical aluminum extruded profile, the joint is designed, for example, as a pan and web, so that when the profiles are pushed into one another, the joint formed in this way is the same as when the roller curtain is rolled up can absorb and withstand occurring forces. The connection of the lamellas formed into a joint generally has a large amount of play. In addition, the shape of the nested profiles should be designed in such a way that a deposit of dirt and water in the joints is prevented, and sufficient tightness against wind attack is ensured.

The bale layers on the winding shaft are formed by the interconnected profiles, which have a certain profile height. Each profile lies on the most protruding edge of a profile of the layer below. The direction that a profile takes in the cross-section of the bale within its bale position depends on the point of contact of the profile. Due to its random position, it in turn determines the arrangement of the next profile connected to it. This results in an irregular position arrangement of the individual roller shutter profiles when the bale is wound up. It follows, among other things, that, for example, only a single edge of a single roller shutter profile supports the entire load of the still freely hanging armored part, which can result in considerable edge pressures.

To secure against lateral displacement, head pieces or end pieces are generally attached to the side of the roller shutter profiles, which run in corresponding vertical guide rails with a generally U-shaped cross section. These vertical guides are funnel-shaped at their upper inlet, so that the roll armor can run smoothly into the vertical guide when unrolled, without the risk of getting caught.

The roll armor is attached to the winding shaft with its initial profile so that the fastening with the gate closed is on the side of the shaft facing away from the armor is located, ie that the tank or the end plates extending the tank loop around the shaft by at least 180 °. This ensures that the tank is held largely by frictional forces, and thus not the full tank load acts on the suspensions. The gate is closed when the closing profile sealingly stands on the lower edge of the opening, ie generally on the floor. For the rest, the roll armor should not collapse. The entire tank - except for the final profile - thus remains attached to the shaft or shaft axis as a load. As a result, the roller shutter differs fundamentally from the roller shutter, which is usually provided as an additional closure of an opening.

In the open position of the roller door, the roll armor rolled up on the winding shaft lies in the lintel area of the door opening. Most of the time the operator is protected behind the lintel and therefore cannot be damaged by vehicles when entering the gate opening. An electric motor is usually provided as the drive, with a manually operated drive for makeshift operation.

In the case of an electric drive, the roller shutter shaft is driven at a constant speed, ie at a constant angular speed. As a result, the roll armor attached to the shaft is raised and wound onto the shaft. The decisive factor for the lifting speed is initially the effective winding radius, which is continuously increased during winding, since the lower parts of the roll armor lie on the already wound upper parts. Since the lifting speed changes in direct proportion to the bale radius, a roller door initially runs slowly upwards in order to get faster and faster upwards. If you take a closer look at the kinematic conditions, taking into account the thickness and height of the profiles, the roller shutter bale must be considered a polygon. Lie down when winding up the profiles first on the round winding shaft. The straight profiles form a polygon on it. The corners of the polygon are further away from the center of the wave than the centers of one side of the polygon. If the shaft of the roller shutter rotates at a constant angular speed, the roller shutter is pulled up once with a lever arm corresponding to the length of the corner point of the polygon and the lifting speed corresponding to this lever arm length, and the next moment with a length corresponding to one side of the polygon Lever arm and the corresponding lifting speed. The stroke speed is directly proportional to the lever arm that is effective, discontinuous and random, and is therefore characterized by correspondingly strong and sudden fluctuations when the roll armor is rolled up. This is accompanied by fluctuations in the mass accelerations and decelerations of the roll armor mass still being processed. These mass accelerations also go into the transmission of the drive machine, which has to be designed for a corresponding degree of non-uniformity, since otherwise failures can occur. In principle, these accelerations become smaller the thicker the roller gate bale becomes, ie the closer the polygon approaches a circle. However, since the greatest mass accelerations and decelerations occur when the armored vehicle is still far below, these forces multiply each other due to the considerable weight of the armored vehicle.

The accelerations and decelerations of the masses of the unrolled roll armor act as vibrations. These vibrations also act on the structure via the winding shaft, so that when the structure is statically calculated, care must be taken to ensure that the natural vibration number remains outside the rolling gate frequencies. Otherwise the lifting speed of the roller shutter must be reduced drastically. With constant angular velocity of the roller shutter shaft as the rolling gate bale becomes thicker, the frequency of the vibrations increases and their amplitude decreases. Conversely, this means that the sound generation when the roller shutter is actuated increases the further the roller shutter comes down.

In addition to the above-mentioned irregularities in the lever arm ratios when winding up the profiles in the form of polygon trains, there is another reason for the roller shutters known to date, which also leads to extremely problematic kinematic relationships. Since the driven shaft of a roller shutter door cannot exert any compressive forces on the roller shutter, it must be ensured that the drop weight of the freely hanging roller shutter part with the lower rail is greater than the friction of the rest when pulled up. This is the only way for the tank to move automatically as a result of its own gravity when the shaft is driven in a downward direction. The least amount of friction for the tank occurs when it runs vertically into the guides when pulled up. This type of attachment is called "normal display". The bale diameter decreases as the roll armor runs. The tank then runs increasingly obliquely into the inlets of the guides. If the roll armor has completely expired, but - as is usual with roller doors - still hangs on the shaft in the train, the entire load of the roll armor may only depend on a single profile of the profiles still on the shaft. When looking at a vertical cross-section through a roller door, it can be seen that the tensile force of the entire tank load is not in the door plane, but in the straight connection from the lower part to the effective bale radius. The armored vehicle will therefore deform in the middle between the guides in order to approximate the course of the tension. However, the profile ends are held by the guides and cannot follow the tension line. During the tensile stress resulting from the curtain's own load pulls the armor at the upper part out of the gate level towards the shaft, the guides bend the profile ends back to the gate level. As a result, the individual profiles are not only subjected to bending, but also to torsion. The greatest bending and torsional moments occur at the inlet.

In order to reduce the sealing problems associated with the way in which the "normal display" is attached, it has been proposed to limit the deflection by attaching a pressure shaft. However, this means that the roller shutter runs more restlessly and noisily (cf. Horst Günter Steuff, "Das Rolltor", Düsseldorf, Werner Verlag GmbH, 1987, p. 93)

The above-described unfavorable kinematics of the rolling shutter, which has been known for more than a hundred years (and has hardly been changed so far), is to be regarded as the main reason for the high noise level during the run, and ultimately also for the insufficient fast-moving properties of the rolling shutter. The running noises originating essentially from the profile joints occur mainly when the roller door is moving upwards and then particularly strongly in the lower third of the door opening, provided that the roller door has a "normal display". The noise is generated near the bushing, where the profiles bend, are subjected to high tensile forces and are supposed to rotate in the joints.

Although the previously known roller door was long considered the cheapest solution in terms of tightness against wind pressure and security against unauthorized opening due to its non-positive and form-fitting connections of the slats, the poor fast-moving properties of the conventional roller door were recognized as an early disadvantage when used as an industrial door been. The running speeds are around 0.25 to 0.35 m / s in the conventional roller door.

In the industrial sector, high-speed roller doors with a full-surface door leaf made of flexible material that can be wound onto a winding shaft or winding drum have also proven to be an additional opening closure. Such roller shutters also offer the advantage of optical transparency if the flexible material is selected appropriately. Macrolon films or soft PVC films, for example, are widespread. However, this advantage over opaque material is lost over time, since the optical transparency is impaired by the ingress of dust and the like when the film is wound up and the surface is scratched as a result.

In view of the limited space available over the lintel area and the large core diameter of the shaft, which is common in film roller doors, the films in this type of roller door must be as thin as possible, since the winding diameter will otherwise be too large. In addition, the provision of thinner foils also enables the door leaf to run faster due to the easier winding. However, the small thickness of the foils, and accordingly the low weight of the door leaf, leads to reduced wind resistance. To remedy this, it has been proposed to provide additional weight in the form of an end profile arranged at the lower edge of the door leaf, or spring-loaded tension belts which run over deflection rollers mounted on the floor.

The biggest disadvantage of the foil roller doors arises from the behavior of the door leaf in wind pressure, which approaches the behavior of a sail rather than the behavior of a panel. Since the door leaf is only supported on the winding shaft, the door leaf becomes significant under wind load inflated and bulged, and consequently also raised. Such rolling gates are therefore only to be regarded as an additional closure of a door opening with regard to inadequate security against unauthorized opening.

So-called sectional doors are also known, which are also used for large door openings. A conventional sectional door essentially consists of a tank with comparatively high sections which can be folded down from a vertical closed position into an upper horizontal position below the ceiling by means of a cable drive.

Due to the comparatively large height of the individual sections used in sectional doors, a mechanically overall more compact design is achieved due to the reduced number of connecting elements of the sections such as hinges or the like and also a reduction in the number of end faces to be sealed, with a correspondingly good strength against wind attack and security against unauthorized opening . Furthermore, the large height of the individual sections allows transparent sections to be provided in the form of glass or plastic windows.

The compact design of sectional doors also makes it possible to provide lightweight gates made of aluminum sections, which are filled with a plastic material for heat and sound insulation, for example, so that garage doors with larger door widths can only be opened and closed manually without an additional electric motor drive.

As a rule, the individual sections are aligned with one another in the closed position, so that the entire end face of a section is available for the seal. The sectional door thus appears to be cleanly closed Gate with a continuous outer surface, with no gaps in between. A further improved tightness is achieved, for example, by rubber inserts which are pressed together in the closed position by the sections lying one above the other. Alternatively, the sections have a bulge running across the entire width of the door on one end face, which engages in a corresponding recess in an adjacent section when the sections are pivoted into the same plane as a tongue and groove connection, which also increases the mechanical strength of the door leaf against wind pressure large door widths is further improved.

On the inside of the gate, the sections are connected by means of a plurality of individual hinges, which are attached at certain intervals across the entire width of the gate in such a number that sufficient strength and support is achieved. The hinges attached to the side edge of the sections are generally designed at the same time as a holder for a roller that can run in a guide rail with a U-shaped cross section at the edge region of the sectional door. Since the individual hinges are attached to the sections in such a way that the sections can be folded away towards the inside, problems arise in so far as the protruding parts of the hinges attached to the inside of the door are visually disturbing and dangerous. A further risk of injury with sectional gates arises when the sections are angled due to the open gaps that occur or when the sections are folded back and the column is closed.

Another disadvantage with sectional doors with relatively high sections arises in connection with the curved guide part above the lintel area, where the individual sections are folded down from the vertical position into the horizontal position. This folding naturally leads to sudden tipping accelerations and accordingly, when operated quickly, considerable force is exerted on the individual sections. As a result of the different radial distances between the guide rollers and the actual position of the mass of the section in the region of the upper cam track, acceleration and deceleration forces occur, the generally uneven force curve due to the flat design of the lamellae having a finite height, which in the cam track is in the manner of a polygon are present, which means that sectional doors can generally only be operated at lower running speeds, without the risk of excessive noise.

Via the multitude of individual hinges, the transferred transverse forces are also absorbed by the body of the sections and thus put a strain on them. The forces introduced when the sections are folded down into the edge hinges and correspondingly into the guide rail essentially depend on the speed at which the sectional door opens and closes. Due to the construction, which is principally not designed for high speeds, there are limits to the use of sectional doors as industrial doors with high-speed capability.

As a drive system for sectional doors, a cable pull device with pull cables and support cables, as well as cable drums arranged on a drive shaft, are generally provided. When the gate moves upwards, the suspension cables are wound onto the cable drums, while at the same time the pull cables unwind from the cable drum. When the door descends, the traction cables are wound up and thus pull the door down, while at the same time the suspension cables are unwound from the cable drums without becoming slack. As a result, the suspension cables are constantly under tension and cannot run off the cable drums. The drive of the The drive shaft takes place via an electric motor, which is arranged, for example, directly below the ceiling.

As is known, torsion springs are provided for balancing the door leaf weight, which are arranged coaxially to the continuous drive shaft. In the closed position of the door, the torsion springs are fully tensioned and are relaxed accordingly when the door leaf is raised. These torsion springs are subject to increased wear and are therefore considerably limited in their service life. Particularly when the direction of movement of the sectional door is reversed frequently and suddenly, the torsion springs suffer considerable dynamic tension peaks due to the jerky movements. Due to the failure of the torsion spring, the maintenance and replacement work associated with the sectional doors is naturally time-consuming and cumbersome.

Due to the arrangement of the drive shaft with the torsion springs above the arch and the electric motor in the vicinity of the drive shaft, a considerable space requirement above the lintel must be taken into account in conventional sectional doors, which without special design measures, such as providing a double horizontal guide below the ceiling, or Laying the drive shaft together with torsion springs to the extreme end of the running rails, typically not less than 400 mm. Added to this is the excessive space requirement in depth for sectional doors, which essentially corresponds to the clear height of the door opening. Since the free space generally available in depth, ie the dimension between the rear edge of the lintel and the next obstacle in the depth of the room, such as the beam, wall, ventilation pipe, fan or the like, will be limited, the installation of the known sectional door in many cases not be feasible.

The invention has for its object to provide a lifting gate, which allows fast opening with low noise when opening and closing the gate, and in the closed state offers sufficient tightness against wind and weather attack, as well as security against unauthorized opening, and beyond only requires a small amount of space above the lintel, even with larger door heights.

This object is achieved by a lifting gate with the features of claim 1.

In the lifting gate according to the present invention, the two pairs of guideways, which are each arranged on the two opposite sides of the gate opening, are designed such that, starting from a vertical section running approximately vertically over the height of the gate opening, the two guideways at the inlet of the Lift gates open into a spiral section that runs inwards. This ensures that the required space for the slat armor in the open position in the depth of the door is kept as small as possible even with a larger height of the door opening, without requiring a significantly increased space requirement in the height above the lintel. According to the invention, the slat armor can be moved into the spiral section of the guideways in the open position of the lifting gate in such a way that the plurality of slats are in a spiral path and are completely contact-free with respect to one another, so that there are no frictional or compressive forces on the slats and thus enables considerable running speeds of the lifting gate without excessive noise. The slats of the slat armor covering the width of the door opening are designed such that they can be angled relative to one another and are made of rigid material, so that the lifting gate is sufficient in the closed position has great mechanical stability to withstand even large wind loads and to ensure security against unauthorized opening.

In order to adapt to different door heights, extension sections are provided according to claim 2, which are simply inserted horizontally into the spiral section of the guideways.

In a further embodiment of the invention it is provided in accordance with claim 3 that the guideways are provided in the form of a pair of round rods, whereby in particular the arcuate sections of the guideway are easy to manufacture.

As an improvement of the drive of the lifting gate according to the invention, a weight compensation is provided according to claim 4, which has a compensation spring and a band attached to the compensation spring, which can be wound onto a shaft interacting with the drive of the lifting gate, this shaft having a predetermined core diameter. The main advantages of this weight balance lie primarily in an extended lifespan of the weight balance, without additional translation means being required to achieve the desired characteristic.

A drive which is advantageous with regard to the possible running speeds of the lifting gate according to the invention has, according to claim 5, an endless chain which can be driven by an electric motor and which is fastened at one point to the slat armor. The endless chain is guided in such a way that the tensile forces applied when the slat armor is raised and pulled down run completely in the plane of the door leaf.

According to claim 6, an approximately horizontally arranged sealing lip is provided as the upper end of the door opening, due to which it is prevented that rainwater, dirt or the like penetrates into the upper region of the lifting gate.

Fig. 1

eine teilweise Seitenansicht eines Ausführungsbeispieles des erfindungsgemäßen Hubtores;

Fig. 2

eine teilweise Rückansicht eines Lamellenpanzers entsprechend des erfindungsgemäßen Hubtores;

Fig. 3

eine schematische Schnittdarstellung entlang der Linie III-III in Fig. 2;

Fig. 3A

eine vergrößerte Darstellung der Einzelheit X aus Fig. 3;

Fig. 4

eine Draufsicht eines Lamellenpanzers gemäß der vorliegenden Erfindung;

Fig. 5

eine geschnittene Seitenansicht eines Ausführungsbeispieles des erfindungsgemäßen Hubtores;

Fig. 6

eine schematische Seitenansicht zur Darstellung des Gewichtsausgleiches eines Ausführungsbeispieles des erfindungsgemäßen Hubtores; und

Fig. 7

die Charakteristik des in Fig. 6 gezeigten Gewichtsausgleiches gemäß der Erfindung.

Further details and expediencies of the invention result from the following description of an embodiment with reference to the figures. It shows:

Fig. 1

a partial side view of an embodiment of the lifting gate according to the invention;

Fig. 2

a partial rear view of a slat armor corresponding to the lifting gate according to the invention;

Fig. 3

is a schematic sectional view taken along the line III-III in Fig. 2;

Figure 3A

an enlarged view of the detail X of Fig. 3;

Fig. 4

a top view of a lamellar armor according to the present invention;

Fig. 5

a sectional side view of an embodiment of the lifting gate according to the invention;

Fig. 6

is a schematic side view showing the weight compensation of an embodiment of the lifting gate according to the invention; and

Fig. 7

the characteristic of the weight balance shown in Fig. 6 according to the invention.

As illustrated in FIGS. 1 and 4, the illustrated embodiment of a lifting gate according to the invention has guideways 2 and 2 ', which are each arranged on the two opposite sides 3 and 3' of a gate opening 1. In the following, deleted reference numerals designate the corresponding parts of the lifting gate, which are arranged on the side 3 ', so that this need not be expressly mentioned below. Each guideway 2, 2 'has a vertical section 4 running vertically above the height of the door opening, which extends to approximately the height of the lintel 6, and opens at the inlet 8 of the lifting gate into a spiral section 10 running inwards in an upper edge region of the door opening . A slat armor 12 for covering the door opening with the clear door height h in the closed position can be moved upward into the spiral section 10 of each guideway into the open position of the lifting gate, in such a way that the slat armor is arranged spirally without lamella 14 lying next to one another. An endless chain 16 and an electric motor 18 are provided as the drive for the lamellar armor 12.

2, 3 and 4, details of the lamella armor according to the invention are shown. A hinge band 20, 20 'is provided on each of the two edge sides of the lamellar armor 12, which has a length that corresponds essentially to the height of the door opening 1. Each hinge band 20, 20 'consists of rigid hinge members 22 which are connected to one another in an articulated manner and via hinge pins 24, 24' are mutually angled. For this purpose, each hinge member is shaped in a known manner at its end to form a rolled-up eyelet into which the hinge pin 24 can be inserted. In each case two adjacent hinge members are connected to one another in an articulated manner in such a way that their eyes are arranged coaxially to one another, in which a common hinge pin 24 is mounted.

In the example shown, rollers 26, 26 'are furthermore mounted coaxially to the hinge pins 24, 24', which serve for the rolling guidance of the hinge straps 20 and 20 'in the guideways 2 and 2'. In the example shown, each guideway has a pair of round rods 28 and 30 which are arranged at a constant distance from one another which is selected to match the diameter of the rollers 26. The hinge straps 20, 20 'and the round bars 28, 30 are made, for example, of hard, metallic material, while the rollers 26 can also be made of plastic material. To secure the lamellar armor against falling out of the guideway, each roller 26, 26 'has a retaining collar 27, 27', the outer diameter of which is greater than the clear distance between the round bars 28, 30.

The slats 14 are, for example, placed and fastened on the hinge straps 20, 20 'by means of screw connections 32, 32' in such a way that a space 34 is formed by the resulting spacing of the respectively adjacent slats 14, in which the hinge pins 24, 24 ', or which engage the hinge pin 22 eyelets 22, 22 ', as best shown in FIG. According to the invention it is achieved that the geometric hinge axis 36 comes to lie completely within the area which is delimited by the two outer main surfaces 38 and 40 of the lamellar armor 12. This position of the hinge axis 36 ensures that the width of the angular opening between the adjacent slats 14 when angling of the slat armor is reduced to a minimum, so that the tilting accelerations are correspondingly reduced when entering the upper, bent guideway. As a result, the possible running speeds of the lifting gate shown are further increased without being accompanied by excessive noise.

The slats with a height of, for example, up to 150 mm are placed independently of one another and individually on the hinge straps 20, 20 ', so that, for example, the absence of an entire slat has no effect on the mechanical stability and functioning of the lifting gate according to the invention. The hinge straps 20 and 20 'thus form, as it were, the load-bearing framework or skeleton of the lamellar armor, which absorbs all the forces which arise during the movement of the lifting gate. Because of the mechanically continuous cohesion of the hinge band 20, 20 ', the tensile forces which occur are absorbed by the hinge bands 20, 20' and are not transmitted to the slats 14. By transferring and distributing the forces to an articulated, continuous, yet tensile band, a smooth and smooth movement is achieved even with extremely fast runs of the lifting gate.

Since the individual slats 14 are initially placed at a certain distance from one another on the hinge straps 20, 20 'in order to make room for the hinge pin, the adjacent slats 14 are also in the closed position of the door without touching one another, as a result of which the rattling noises known from conventional sectional doors when closing the gate with the lifting gate according to the invention also completely eliminated.

To increase the mechanical stability of the lamellar armor and to increase the tightness, but without the properties of the present lifting gate in terms of low noise, sealing strips 42 in the form of rubber strips are provided, which are arranged approximately over the entire width of the door between the hinge straps 20 and 20 ', and connect opposite sides of adjacent slats 14. Each sealing strip 42 is expediently arranged coaxially to the adjacent hinge axis 36, so that the sealing strips 42 are only subjected to bending when the lamellar armor 12 is bent in the upper guide region. The sealing strips 42 engage with only a little lateral play in the direction perpendicular to the door leaf plane in the slats 14, so that the slat armor 12 is put under tension at a certain point under pressure, and corresponding restoring forces act immediately against the pressure load. Each sealing strip 42 has beads or thickenings 44 on opposite sides which engage in correspondingly shaped recesses 46 in the lamellae 14.

As can best be seen from the enlarged detail according to FIG. 3A, each thickening 44 has a support surface 43 which is arranged opposite a corresponding holding surface 45 of the lamella 14. The distance between a support surface 43 and the associated holding surface 45 of the lamella 14 is - taking into account the requirement of a jam-free and trouble-free installation by inserting the sealing strip 42 with the thickening 44 into the recess 46 from the side - as small as possible, so that in the closed position of the lamellar armature, any pressure loads that may occur on the lamellar armor cause the sealing strip 42 to be tilted to the side and, after the support surface 43 comes into contact with the holding surface 45, the sealing strip 42 to the two adjacent slats is subjected to tension. With even smaller deflections of the slat under consideration from the door leaf level, ie as long as the support surface 43 is the opposite holding surface 45 is not touched, the sealing strip 42 is only subjected to bending in relation to the two adjacent slats, which lead to corresponding restoring forces. Since the distance between the support surface 43 and the associated holding surface 45 is selected to be minimal, in order to obtain a strain on the sealing strip as far as possible even with slight deflections, the pressure loads occurring on the lamellar armor from the sealing strip 42 which is initially directly affected are also applied to the adjacent sealing strips transferred and distributed. When subjected to a pressure load, the lamellar armor according to the invention thus behaves largely like a homogeneous flat plate with a corresponding force distribution in the plate plane, but nevertheless permits a low-force deflection. Therefore, the sealing strips 42 cause a noticeable increase in the mechanical stability of the lamellar armor, so that the lifting gate in the closed position easily withstands high wind or other pressure loads.

Of course, the lifting gate according to the invention also offers sufficient security against unauthorized opening, so that the lifting gate according to the invention can be regarded as a permanent closure of a gate opening.

To prevent pulling out of the lamellar armor 12 if even greater pressure forces occur, holding collars 27, 27 'are arranged on the two opposite sides of the lamellar armor, which in the exemplary embodiment shown are designed as an outer disk with a larger diameter than the diameter of the rollers 26, 26'. The retaining collars 27, 27 'are arranged at such a small distance (not shown in the drawing) from adjacent supporting surfaces of the guide rods 28, 30 that they are only loaded when the slats 14 are very strongly bent under load on the outside of the guide rods 28, 30 Get support so that the lamellar armor at relatively low Pressure loads can be operated and moved easily. The described good distribution of forces over the sealing strip 42 in the door leaf plane prevents the retaining collars 27, 27 'of a loaded slat 14 from reaching the support at an early stage due to its strong deflection and thereby hindering the movement of the slat armor, even in the event of selective loading.

In the exemplary embodiment shown in FIG. 3, each lamella 14 has a sealing lug 48 which projects on the outside 38 in the door leaf plane and on the basis of which the distance to an adjacent lamella is reduced. Due to the sealing lug 48, the sealing strip 42 can no longer be recognized from the outside in the closed position. The sealing strip 42 is then only visible from the inside (see rear view according to FIG. 2). At the same time, the design of the sealing nose 48 shown in FIG. 3 results in a more beautiful appearance of the lamellar shell 12 in the form of a more uniform, smooth surface.

As finger protection and thus to prevent injuries due to unintentional contact with moving parts, sealing lips 50, 50 'are provided on the inside and outside of the door opening according to FIG. 4, which in the closed position protrude to the position of the sealing strips 42 in the door leaf plane. The sealing lips located on the outside of the door opening 1 simultaneously form a seal against driving rain, dust or the like. The sealing lips can in turn be made of rubber, for example.

A sealing lip 52 formed analogously to this in cross-sectional shape is arranged in the region of the lintel 6 (FIG. 5) and extends horizontally essentially over the entire width of the door opening. The sealing lip 52 prevents rain water or dirt from entering the upper region of the lifting gate.

3, a seal 54 is provided, for example made of rubber, which is fastened to the lowest slat.

As already explained with reference to FIG. 1, the lifting gate according to the invention has the two guideways 2 and 2 ', which are present in the upper region of the gate and below the ceiling indicated by the reference number 55 as a spiral section 10 running inwards. In the open position of the lifting gate, the slat armor 12 can be moved into the spiral section in such a way that the plurality of slats are present in a spiral path and without contact with one another. In contrast to the known roller door, in which the roller shutter is wound up on a winding shaft, according to the invention the slat armor is always guided in such a way that the slats do not touch one another. As a result, the pressure forces on the slats occurring at the roller door are completely avoided, so that a correspondingly smooth running, which allows high speeds, is made possible. In contrast to the conventional sectional door, the upper guideway is not a straight line directly below the ceiling, which, especially with larger door heights, required considerable space in the depth of the door. In contrast, the spiral section 10 in accordance with the exemplary embodiment shown in FIG. 1 has the three arc sections 56, 58 and 60. As shown, part of the arc section 60 lies directly against the arc 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 guideway 2 is equal to the radius of the arc section 60 lying on the inside. This radius is the same here chosen that depending on the distance d between adjacent hinge pins (see Fig. 3) a proper entry of the slat armor 12 into the spiral section 10 is possible without, for example, fear of self-locking of the angled slats in the narrowest arc section. Such self-locking would occur at the latest when, when the lamellar armor 12 runs in, the force component directed parallel to the guideway to overcome the rolling friction at any point on the guideway becomes smaller than the rolling friction component acting accordingly at this point, which in turn is proportional to the normal force present at this point is. In practice, however, the smallest possible arc radius is already limited by the fact that the sealing strips are bent when the slats are angled, which creates restoring forces that have to be overcome by the drive of the lifting gate, and which are greater the closer the guide arc is selected.

Due to the spiral arrangement of the guideway 2, the existing height g above the lintel area is optimally used. The curved sections 56, 58, 60 can be produced in a standardized manner for all gate heights that occur in practice, so that regardless of the respective gate height, the lifting gate according to the invention offers the advantage of a uniform dimension for the fall height. The adjustment of the total length of the guideway in accordance with the individual gate height according to the user is ensured by separately usable, horizontally extending extension sections 62 of length a. In the case shown, the length of the entire guideway 2 is increased by a total of 3 × a by inserting the extension sections 62. Since these extension parts essentially represent the only parts of the lifting gate that have to be manufactured or made available individually according to the gate height, the lifting gate according to the invention can correspond to the large quantities are inexpensive to manufacture and therefore find their way into more everyday applications outside the industrial sector.

For further illustration, concrete numerical values are given below. With the usual clear gate heights of h = 3 m, 4.5 m, 6 m, the values of the extension sections 62 are each a = 0 m, 0.5 m, 1 m, so that with a fixed value of the overall height above the lintel g = 0.5 m with an increase in the clear gate height from 3 m to 6 m, the space requirement increases in depth by only 1 m. The diameter of the rollers 26 and thus the clear distance between the guideways is approximately 4 cm. With this arrangement it is possible, for example, to fully open the gate with the height h = 3 m in no less than 2 s.

1, the electric motor 18, which is connected to a drive roller 64, is arranged in the space remaining in the interior of the spiral section 10. The chain line 16 in FIG. 1 schematically indicates the endless chain 16, which is driven by the drive roller 64 and the motor 18, and is guided over deflection rollers 66, 68, 70 (FIG. 5), and 72. On the opposite side 3 'of the gate (not shown) deflection rollers are provided corresponding to the deflection rollers 68, 70, 72, and of which a deflection roller is connected, for example via a coupling and a torsion shaft, to the deflection roller 72 designed as a gearwheel, and another drives endless chain (not shown). At this point, it is noted as a further advantage of the lifting gate according to the invention that, depending on the desired gate width, the torsion shaft is the only component that can be made to order with a corresponding length.

In the area of a lower slat, the endless chain 16 is fastened to the slat armor via a bracket 74. 5 is the connection of the chain to the slat armor is most appropriately provided such that the tensile force acting when the slat armor is raised from the closed position to the open position runs entirely within the level of the door leaf, and thus horizontally extending force components are avoided which would lead to a tilting moment of the slat armor , whereby forces would act on the guideways that try to push the guides apart, while the rollers would be subject to increased wear due to the massive load.

The bracket 74 also has, for example, a projecting, rigid end 76 which, when the door is open, strikes a rubber buffer 78 mounted above the lintel with almost no noise.

According to FIG. 6, a weight compensation 80 is provided to adapt the pulling force acting on the drive of the lifting door to the respective weight of the free slat armor length, which has a compensation spring 82 and a band 84 fastened to it from a largely inelastic and tensile material. The lower end of the compensating spring 82 designed as a helical spring is firmly connected to the floor. Via a deflection roller 86, the band 84 is wound up with a shaft 88, which interacts, for example, via the deflection roller 72 shown in FIGS. 1 and 5, with the drive of the lifting gate, in such a way that the band 84 from the shaft 88 when the slat armature is raised is unwound and the spring 82 is relieved accordingly, and when the lamellar armor is lowered, the band 84 is wound onto the shaft 88 with a correspondingly exerted tensile force on the compensating spring 82, so that the latter is tensioned.

The shaft 88 has a predetermined core diameter, the value of which is selected such that, depending on the thickness of the band 84, the rest length L _{o of} the compensating spring 82, the spring strength of the compensation spring 82, and the total weight of the slat armor corresponding to the gate height, the desired characteristic of the weight compensation 80 according to FIG. 7 is achieved.

7 shows the respective clear height of the remaining door opening in millimeters for an exemplary clear door height of 3 m to the right, the value "0 mm" representing the completely closed door and the value "3000 mm" representing the fully open door , and upwards the total weight G _{T of} the free lamellar armature acting on the drive is plotted as a continuous line, and the spring force F _F also acting on the drive is plotted as a dashed line. As can be seen from FIG. 7, the weight compensation 80 is set such that when the gate is closed, the compensation spring is stretched to such an extent that an excess spring force of approximately 260 N is present in addition to the weight of the slat armor. This ensures that when the closed gate is actuated, the lamellar armor rises up to approximately the height at which the weight of the free lamellar armor is in balance with the corresponding spring force, even without an additional drive. In Fig. 7, this means the point where the two lines intersect, that is, at a height of approximately 1 m. As the door moves upwards, the respective weight force is approximately in equilibrium with the spring force acting, so that the drive essentially only has to act against the existing frictional forces. Further details can easily be found directly in FIG. 7 without the need for further explanation.

For reasons of space, a weight compensation with at least one compensation spring is provided on both sides of the gate in the lifting gate according to the invention.

The weight compensation shown here has decisive advantages over the known solutions. Compared to the torsion springs used in conventional sectional doors, the service life is significantly increased due to the use of a compensating spring in the form of a coil spring. The service life of a coil spring is approximately twice the service life of a torsion spring. This reduces the problem of laboriously replacing the power unit in the sectional door. Incidentally, the side compensating springs 82 do not require any space via camber.

Another advantage of the weight compensation according to the invention results from the use of the tape 84, which in the case shown has a thickness of 2 mm. In comparison, if a wire rope were to be used, in particular a further translation, for example in the form of a loose roll, would be necessary, since a rope could only be wound up side by side on a drum, with a correspondingly larger core diameter. According to the invention, however, the tape can be wound on a stub shaft with a relatively small core diameter without the tape rubbing through, so that additional translation means can be dispensed with. In addition, the tape is wound one on top of the other, so that, as desired, starting from the open position of the door, the take-up radius increases rapidly, but changes only slightly when the roll is almost completely wound when the door is in the closed position.

As can be readily recognized, the main advantages which can be achieved with the particular type of weight balancing described have particular importance in combination with the further features of the present invention, but they are also of independent importance, since these advantages are used regardless of details of the type of the door can be.

Claims (6)

1. A vertical lift gate comprising
   a strip cladding (12), comprising a plurality of strips (14) which are constructed
   rigidly,
   to cover the width of the gate aperture (1) and
   so as to be flexible relatively to one another; and
   guideways (2, 2'), which
   are disposed at the two opposite sides (3, 3') of the gate aperture (1) and,
   starting from a vertical section (4) extending vertically substantially over the height of the gate aperture (1), lead, at the gate entry (8), into a spiral section (10) extending spirally inwards, into which spiral section the strip cladding (12) is movable without obstruction in the open position of the gate in such manner that the majority of the strips (14) are situated in a spiral path and without contact with one another,
   characterised in that
   two pairs of guideways (28, 30) are provided, each pair of which has a constant clear guideway spacing, such spacing being equivalent to the diameter of the guide rollers (26, 26') running in each pair of guideways,
   the guide rollers (26, 26') have a retaining collar (27, 27') to secure the strip cladding (12) from dropping out of the guideways, the outside diameter of the retaining collar being larger than the clear spacing of the guideways of each pair.
2. A vertical lift gate according to claim 1, characterised in that the spiral section (10) of the guideways (2, 2') comprises a substantially horizontally extending and separably insertable extension section (62).
3. A vertical lift gate according to claim 1 or 2, characterised in that the pairs of guideways (2, 2') are provided in the form of round rods (28, 30).
4. A vertical lift gate according to any one of the preceding claims, characterised by a weight compensation (80) for matching the traction acting on the gate drive to the associated weight of the free strip cladding length, the weight compensation (80) comprising a tensionable or compressible compensating spring (82) and a band (84) secured to the compensating spring (82), such band being coilable in superposed coils on a shaft (88) co-operating with the gate drive, and the shaft (88) having a predetermined core diameter.
5. A vertical lift gate according to any one of the preceding claims, characterised by an endless chain (16) which is connected to the strip cladding (12) and which is drivable by an electric motor (18).
6. A vertical lift gate according to any one of the preceding claims, characterised by a sealing lip (52) which is disposed horizontally at the gate inlet (8) over substantially the entire gate width and which extends perpendicularly to the gate plane as far as the region of the guideways (2, 2').

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