EP1965018B1 - Door with tension spring compensation and drive device for this purpose - Google Patents

Description

The invention relates to a roller shutter with a closing element for opening and closing a building opening movable shutter and a door shaft which is coupled to the closure element for common movement and with an acting on the door shaft counterbalancing device having at least one spring element which upon rotation of the door shaft in a first direction tensioned and relieved upon rotation in a second direction.

Such roller doors or other overhead doors with Torwelle are among others available from Hörmann KG on the market.

AT 341 177 B relates to such a roller shutter with a winding body for articulated lamellae, wherein acting in the Aufwickelsinn a Torkörpers formed by the lamellae on the winding body springs are provided.

US 2004/163777 A1 relates to an industrial roller door with a widening from top to bottom door leaf for fast and quiet operation. US 812 722 A also relates to a roller door that can be operated quietly.

DE 298 04 411 U1 refers to roller shutter with a flexible door leaf and an elastic band, which always biases the gate in the Aufwickelsinn. DE 39 05 224 A1 also relates to a roll-up door with a flexible door leaf. Also DE 87 17 192 U1 1 relates to a roller shutter with a flexible door leaf, the weight compensation is accomplished by means of a chain hoist.

Roller shutters are known, they have similar to a blind the task of closing passages. The closure element is designed in particular as a curtain for roller doors. The curtain is formed, for example, from individual interlocking jointed panels or Rolltorstäben which are rolled up to form a winding shaft formed as a Torwelle a bale or roller shutter.

To drive such roller doors usually a recessed in the winding shaft tubular motor or a flanged on the winding shaft worm gear motor is provided.

There are also spring compensations provided for the weight balance of the door curtain. Such a spring compensation is carried out to reduce the drive power often by a arranged in the door or winding shaft torsion spring or on the door or winding shaft about an axis rotatably arranged coil spring packages.

Safety requirements for power-operated doors, which have recently become increasingly stringent, can only be met on roll-up doors with elaborate mechanical and electronic elements. This makes such gates consuming and expensive.

The object of the invention is to develop a goal of the type mentioned above, and in particular a roller door, which can be driven with simple drive means of lower power and with a simple and inexpensive construction meets the required in different standards safety conditions. To achieve this object, a gate with the features of the attached claim 1 is provided.

Advantageous embodiments of the invention are the subject of the dependent claims.

According to an advantageous embodiment of the invention, the above-mentioned object is achieved by providing a roller shutter with a straightforward DC motor, such as a 24V windscreen wiper motor, and a spring balance is provided. The spring compensation is preferably designed such that it corresponds to the torque characteristic of the Rolltorballens, so as to keep the drive power as low as possible. As a result, even simple motors with low demands on their performance can be used.

Advantageously, a spring compensation is arranged outside the winding shaft or the door shaft or outside of the roller door bale. Particularly preferably, the spring balance is performed by at least one Zugfederpaket.

The execution of a weight compensation device with a tension spring is a particularly simple and uncomplicated way to adjust the compensation characteristic as close as possible to the torque characteristics of the up and unwinding curtain.

The tension spring acts on the door shaft to compensate. Due to the spiral winding of the Rolltorballens to obtain a nonlinear torque characteristic. An advantageous solution to make the Zugfedercharakteristik so that it approximately corresponds to the torque characteristic of a roller shutter, can be achieved by a changing in the course of Torweges in gear ratio transmission, which is connected between the tension spring and the door shaft.

A corresponding transmission device has, for example, a winding drum for winding up a traction spring connecting the tension spring with the torque shaft, which provides a different winding radius for the traction means in different door positions. For example, for this purpose, a conical cable drum for winding a designed as a cable device traction means is provided.

The spring element of the weight compensation device preferably has a plurality of tension springs, in particular a tension spring package. Thus, even if a spring breaks, the holding force is made available by the one additional tension spring or by the several other tension springs, so that the curtain is prevented from falling when the spring breaks. Danger of spring fragments in case of spring break can be avoided by interlacing several springs. For example, an outer and an inner tension spring are provided, which are arranged concentrically to each other, for example. An avoidance of a hooking of the individual spring coils into each other and a safe collection of spring fragments can be achieved by an opposite winding of the inner and outer spring. In reverse winding intersecting spring portions of the two springs are provided with each spring winding, which avoid flying around of spring fragments.

In order to avoid finger-locking in the tensioned springs, these are preferably arranged concealed. They are covered for example by a frame or other frame element of the door. For example, they are guided in a cavity of the goal frame or surrounded by frame profile parts. With one end is the spring assembly and / or the at least one tension spring on one fixedly mounted frame part fastened. At the other end preferably the traction means attacks.

The traction means is further preferably divided into a plurality of substantially parallel traction elements. Thus, a crash is avoided even with breakage of one of the tension elements, so that special sensing and catching elements can be saved in the event of cable breaks. For example, the traction means has at least two approximately parallel guided tension cables, in particular wire cables.

• In bevorzugter Ausgestaltung ist eine Notentriegelungsvorrichtung vorgesehen, mit der eine Entkupplung eines Motors in Notfällen, insbesondere zur Notöffnung bei Stromausfall, vom Innenraum und/oder auch von außen ohne besonderes Werkzeug, wie beispielsweise Handkurbel oder Nothandkette, erzielbar ist.
• Ein besonderer Federausgleich ist vorgesehen, damit das Tor im Notfall manuell über Aufwickeln des Behanges geöffnet werden kann und damit nur eine geringe Antriebsleistung erforderlich ist.
• Vorzugsweise ist ein Federpaket mit wenigstens zwei Federn vorgesehen. Einzelne Zugfedern sind weiter vorzugsweise ineinander verschachtelt Bei einem Federbruch gibt es so keinen unmittelbaren Torabsturz; und wegen der Verschachtelung ist keine Federbruchsicherung notwendig.
• Der Einsatz von zwei Zugelementen pro Zugmittel, beispielsweise von wenigstens zwei Zugseilen, gilt als Seilbruchsicherung.
• Durch den Einsatz eines Gleichstrom-Motors lässt sich eine Steuerung realisieren, die sicherheitstechnische Anforderungen - beispielsweise Schließkraftbegrenzung - auf einfache, kostengünstige Weise erfüllt.

Advantages of the invention and / or preferred embodiments thereof are:

• In a preferred embodiment, an emergency release device is provided with a decoupling of a motor in emergencies, especially for emergency opening in case of power failure, from the interior and / or from the outside without special tools, such as hand crank or emergency hand chain, can be achieved.
• A special spring compensation is provided so that the door can be opened manually in an emergency by winding the curtain and thus only a small drive power is required.
• Preferably, a spring assembly is provided with at least two springs. Single tension springs are further preferably nested in each other in a spring break so there is no immediate door crash; and because of the nesting no spring breakage is necessary.
• The use of two traction elements per traction device, for example, at least two traction cables, is considered as cable breakage protection.
• Through the use of a DC motor, a control can be realized, the safety requirements - such as clamping force limitation - met in a simple, cost-effective manner.

The advantageously provided drive unit has in a particularly preferred embodiment, a drive motor which is provided with a high-ratio worm gear. The translation is preferably in the range of 1:50 to 1: 200 and is 1:91, for example. Especially with such high Translations in the worm gear to achieve a secure static self-locking.

Further, in a particularly preferred embodiment, a traction mechanism is still provided, with which the drive unit is coupled to the winding shaft. This traction mechanism is preferably used for further reduction.

In particular, an emergency unlocking possibility can be achieved with such a traction mechanism particularly easy, with which the door in emergencies, eg. B. power failures, easy to open.

For example, to the output side (Torwelle, winding shaft), the drive speed is again reduced by a trained example as a chain drive traction mechanism in the ratio 1: 3.

An emergency release can be achieved particularly easily by a decoupling, which takes place by the motor with its output gear, such as a drive chain pinion, from the engagement region of the traction means of the traction mechanism, such as a chain is pivoted.

In a corresponding pivot bearing a secure mounting of the motor drive unit with a simple design of the holder is possible. Also, you can get in such a pivoting device, for example, by pivoting beyond the dead center, a safe operating position under tension of the traction device. Preferably, the pivoting device is designed according to the principle of a toggle lever or has a toggle lever.

In particular, the traction means of a traction mechanism can be easily tensioned by pivoting and without a large force requirement. If a toggle lever principle is used, the actuating forces can be further reduced and still achieve a high clamping force.

The engine can be kept in its operating position, for example by a locking element.

In order to enable a safe unlocking, for example via a Bowden cable, from the outside, a bias voltage can be provided which biases the engine out of its operating position in an emergency unlocking position. One then only needs the locking element, for example by means of the Bowden cable to unlock from the outside, so that the engine in its Notentriegelungstellung and thus out of engagement with the transmission device which couples the engine to the door shaft jumps. Then the curtain can then be pushed manually. The spring balancer ensures safe winding even with such manual sliding.

This type of emergency release can also be provided at other gates, with or without a different weight balance.

Fig. 1

eine Innenansicht auf ein Rolltor mit Antrieb und Gewichtsausgleichseinrichtung;

Fig. 2

die Antriebsvorrichtung für das Rolltor nach Fig. 1 in einer Betriebsstellung;

Fig. 3

die Antriebsvorrichtung von Fig. 2 in Notentriegelungsstellung und

Fig. 4

ein Diagramm, das die Drehmomente, die durch den Behang, die Feder und die Antriebseinrichtung an der Wickelwelle des Rolltores ausgeübt werden, über den Torweg hinweg aufgetragen.

An embodiment of the invention will be explained in more detail with reference to the accompanying drawings. It shows:

Fig. 1

an interior view of a roller shutter with drive and counterbalancing device;

Fig. 2

the drive device for the roller door after Fig. 1 in an operating position;

Fig. 3

the drive device of Fig. 2 in emergency unlocking position and

Fig. 4

a diagram that applied the torques exerted by the curtain, the spring and the drive device on the winding shaft of the roller door, across the door path across.

This in Fig. 1 Roller door designated generally by 10 has a door shaft in the form of a winding shaft 12, a closure element for opening and closing a building opening 14 in the form of a curtain 18 which can be wound onto the winding shaft 12 to form a gate 16 and a frame 20.

The frame 20 is to be fixed as a stationary frame member at the boundary of the building opening 14 and has each left and right of the building opening 14 depending on a guide 22 for the curtain 18. On the frame 20 two bearings 24 are further provided for the winding shaft 12.

At a first end of the winding shaft 12, a drive device 26 engages. At a second end of the winding shaft 12 engages a weight balancer 28.

The weight balancing device 28 has a spring element in the form of a spring assembly 30, which is formed from at least one inner tension spring 32 and an outer tension spring 34. The inner tension spring 32 is approximately concentrically received within the outer tension spring 34 so that the tension springs 32, 34 are arranged interleaved with each other. The tension springs 32, 34 are, as not shown in detail, wound in opposite directions. The spring assembly 30 is received in a cavity of the frame 20, as indicated by a dashed line shown Zargenprofilteil 36, which conceals the spring package 30 against access by persons. A first end of the spring assembly 30 is hooked via a spring seat 38 with hooks 40 to a stationary region of the frame 20. At the second free end, the spring assembly 30 is connected to a transmission device 42, by means of which the tensile force of the tension springs 32, 34 is applied as a torque to the winding shaft 12. The transmission device 42 is designed such that the torque caused by the tensile force is dependent on the position of the winding shaft 12 and the path-dependent torques exerted by the Torballen 16 and the curtain 18 in the different door positions, counteracts and so these torques possible compensated accordingly.

In the example shown, the transmission device 42 has a traction mechanism 44 and a winding drum 46 with rotation angle-dependent and thus torwegabhängigem winding radius. The traction means 44 has two approximately parallel guided tension elements in the form of two wire ropes 48. The winding drum 46 is particularly preferably designed as a conical cable drum.

In Fig. 4 the torque characteristics of the torque exerted on the winding shaft by the curtain 18 and the gate 16 and the torque exerted on the winding shaft 12 by the weight balancing device 28 are plotted over the gate path s. The torques D are plotted on the y-axis and the gate travel s is plotted on the x-axis.

As can be seen, the winding drum 46 is designed in such a way that the tensile force of the spring assembly 30 exerts a torque 52 which, as far as a difference over almost the entire door travel, corresponds as far as possible to the torque 50 exerted by the curtain. Although the torques 50, 52 act in practice against each other, they are in Fig. 4 plotted on the same side of the x-axis to better compare their amounts.

The curve 54 shows the torque 54 provided by the drive device 26 likewise plotted over the door path s. Due to the approximation of the torques 50, 52 over the entire door travel, the drive device 26 only has to provide a very small torque 54, namely approximately the difference between the torque curves 50, 52.

Close to the far right in the torque characteristic of Fig. 4 illustrated closed position - "gate to" 56 - supports the curtain 18 with its provided with seal end profile 60 on the floor 62. The curtain 18 is, see Fig. 1 , made of individual hinged to each other roller shutter bars 64 - profile bars made of metal - formed, which are then relieved near the position "gate to" 56 successively. Accordingly, the force exerted by the curtain 18 on the door shaft torque 50 decreases rapidly in the vicinity of the closed position 56 down to zero.

However, the weight compensation device with the spring assembly 30 still counteracts with a certain amount. Against this remaining torque 68 of the weight balancing device in position "gate to" 56 then acts a corresponding counter torque of the drive device. The drive device 28 is, as will be explained in more detail below, provided with a self-locking gear. The so-acting self-locking motor provides a locking torque 66 available, which counteracts opening the door curtain.

Accordingly, in the illustrated embodiment of the weight balancing device 28, two tension spring cables are in the "gate open" position 58, as in FIG Fig. 1 represented, placed parallel to the large winding diameter of the winding drum 46 and wind up to the position "gate to" 56 on the smallest winding diameter. As a result, a possible falling torque 52 is achieved in the closed position. The residual torque 68 in the "gate to" position 56 is generated by the drive device, in particular a drive motor, and held by the self-locking.

How out Fig. 3 As can be seen, the drive torque 54 is constant or nearly constant over almost the entire door travel s. It is therefore also possible to provide for a simple safety shutdown when running onto obstacles by providing a shutdown threshold which is constant over the doorway and for a parameter monitored in the usual manner and representing the drive torque (eg current, line, speed, etc.).
The following is based on the representations in the FIGS. 2 and 3 the drive device 26 explained in more detail.

The drive device 26 has a drive unit 70 with a motor 72 and a transmission device 74.

The motor 72 is a simple 24 volt DC motor in the illustrated example. The transmission device 74 has a self-locking gear in the form of a high-ratio worm gear 76 and a traction mechanism 78. The traction mechanism 78 is also configured by reducing and preferably designed as a positive traction mechanism 78, so for example as a toothed belt gear or, as shown here, as a chain transmission with a link chain 80 as traction means. The traction means of the traction mechanism 78 is closed to an endless loop and to a (smaller) output gear 82 of the drive assembly 70, here at the output of the worm gear 76, and placed around a (larger) drive wheel 84 on the winding shaft 12 around.

Further, an emergency unlocking device 86 is provided for decoupling the motor 72 from the winding shaft 12 for emergency opening. The emergency unlocking device 86 is formed in the illustrated example by a pivotable mounting 88 of the drive unit 70. The pivotable bearing 88 has a stationary, here on the guide 22, to be fixed hinge bracket 90 as a fastener and about an axis of rotation 92 to the hinge bracket 90 pivotable support for the drive unit 70, here in the form of a pinion receptacle 94 on which the drive pinion trained drive wheel 82 is mounted.

The pinion holder 94 is by a biasing element, here in the form of a push-off spring 96 in the in Fig. 3 shown Notentriegelungsstellung (drive unit 70 is pivoted away from the guide 22) biased. In this emergency unlocking position, the output gear 82 is not engaged with the link chain 80. The pinion receiver 94 is provided with two plates 100 spaced apart by spacers 98. Between these plates 100 then the loosely hanging endless loop of the link chain 80 is guided. Since the output gear 82 is mounted within this endless loop in the pinion seat 94, the link chain 80 can also be in the in Fig. 3 Unlocked state shown not remove from their position between the plates 100. It will be understood that plates are not necessarily required for this, other guide elements may be used to maintain the position of the link chain 80 in the unlocked state.

In Fig. 2 the operating position is shown, in which the pinion seat 94 is pivoted about the axis of rotation 92 toward the hinge block 90 and the guide 22. The output gear 82, which is in the form of a pinion, is engaged with the link chain 80 and clamps the link chain 80 accordingly.

There is a locking element 102 is provided which locks the pivotable bearing 88 in this operating position.

The locking element 102 has a pivot bolt 104 which braces an extension 106 of the pinion seat 94 between itself and the guide 22. For this purpose, the pivot bolt 104 is braced by means of a tensioning element 108, here in the form of a vertical tensioner. The clamping element 108 can be a this offset to a pivot axis of the pivot bolt 104 arranged pivot axis bring into an approximately perpendicular to the pivot bolt clamping position. At the free end of the clamping element 108 is a Entkupplungsleine 110 or in an alternative, not shown embodiment, a Bowden cable attached, which can pull the clamping element 108 out of its clamping position. In such a case, the push-off spring 96 pushes the pinion seat 94 in the in Fig. 3 illustrated emergency unlocking position.

The extension 106 is formed in the form of an angle, which is engaged behind for locking by a projection 112 of the pivot lever 104. If the projection 112 engages on the extension 106, the holder with its axis of rotation 92 and the pivoting bolt 104 form with its pivot axis 114 a toggle lever by means of which the clamping forces for tensioning the traction means - in this example the link chain 80 - can be easily applied ,

LIST OF REFERENCE NUMBERS

10

rolling gate

12

winding shaft

14

building opening

16

Torballen

18

curtain

20

frame

22

guide

24

camp

26

driving device

28

Weight balancer

30

spring assembly

32

inner tension spring

34

outer tension spring

36

Zargenprofilteil

38

spring seat

40

Hitch

42

transmission device

44

traction means

46

winding drum

48

wire ropes

50

Torque by hanging

52

Torque through weight balancing device

54

Torque of the drive device

56

Gate to

58

door open

60

End profile

62

ground

64

roller door bars

66

Locking moment Motor self-locking

68

Torque of the counterweight device in the "gate closed" position

70

power unit

72

engine

74

transmission device

76

worm gear

78

traction drives

80

link chain

82

output gear

84

drive wheel

86

emergency unlocking

88

swiveling storage

90

joint Bock

92

axis of rotation

94

Chink intake

96

Press-off spring

98

spacer

100

plates

102

locking element

104

swivel bolt

106

extension

108

clamping element

110

Entkupplungsleine

112

head Start

114

swivel axis

s

torweg

Claims (13)

1. A roll-up door (10) with a movable door curtain (18) used to open and close an opening in a building (14) with a winder shaft (12), whereby the door curtain (18) can be wound up on the winder shaft (12) in a spiral-like manner and with a weight balancing device (28) that is connected to the winding shaft (12) and that has at least one spring element (30) that can be tensioned when the winder shaft (12) is turned into a first direction and the tension of which can be relieved when the winder shaft (12) is turned into a second direction, whereby at least one spring element (30) is equipped with at least one tension spring (32, 34), whereby at least one tension spring (32, 34) is coupled to the winder shaft (12) via a drive device (42) with a modifiable transfer ratio; characterized by the fact that the transfer ratio is contingent upon the turning angle of the winder shaft (12) in such a manner that the tensioning force of the tension spring (32, 34) is largely transferred in accordance with the door path contingent torque characteristics so that the tensioning force of the tension spring (32, 34) applies a torque (52), which, with the exception of a difference amount, is largely equivalent to the torque (50) applied by the door curtain (18) across virtually the entire door path.
2. The roll-up door according to Claim 1,
   characterized by the fact
   that the door curtain (18) comprises multiple roll-up door rods (64) that are jointed together.
3. The roll-up door according to the above Claims,
   characterized by the fact
   that the spring element has a spring assembly (30) consisting of several tension springs (32, 34).
4. The roll-up door according to Claim 3,
   characterized by the fact
   that the spring assembly (30) is equipped with at least one external tension spring (34) and at least one interior tension spring (32) surrounded by the external tension spring (34) or with tension springs nested into each other (32, 34).
5. The roll-up door according to Claim 4,
   characterized by the fact
   that the tension springs (32, 34) are positioned largely concentrically to each other.
6. The roll-up door according to one of Claims 4 or 5,
   characterized by the fact
   that the interior and the external tension springs (32, 34) are wound in opposite directions from each other.
7. The roll-up door according to one of the above Claims
   characterized by the fact
   that a door frame element (20, 22, 36) to be mounted permanently to the opening of the building (14) is called for, whereby the spring element (30) and/or at least one tension spring (32, 34) of the same are mounted to the door frame element (20, 22, 36) with the first end.
8. The roll-up door according to Claim 7,
   characterized by the fact
   that the tension spring element (30) is situated in such a manner that it is framed by the door frame element (20).
9. The roll-up door according to one of the above Claims,
   characterized by the fact
   that the drive device (42) transfers the tension force of the tension spring (32, 34) in the opposite direction of the torque characteristic (50) applied by the weight of the locking element (16, 18) over the progression of the door path (s) to the door shaft (12).
10. The roll-up door according to one of the above Claims,
    characterized by the fact
    that on the second end of the spring element (30) and/or at least one tension spring (32, 34) of the former a tensioning material (44) is connected that is mounted to a winding device (46) turning with the door shaft (12) in such a manner that it can be wound up.
11. The roll-up door according to Claim 10,
    characterized by the fact
    that the winding device preferably has a conically shaped winding drum (46), which provides different winding radiuses for the tensioning material (44) in the different door settings.
12. The roll-up door according to Claims 10 or 11,
    characterized by the fact
    that the tensioning material (44) has at least two tensioning elements (48) that are largely guided in parallel to each other.
13. The roll-up door according to Claim 12,
    characterized by the fact
    that the tensioning elements are tensioning ropes, in particular wire ropes (48).

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