EP1528219B1 - Roller shutter - Google Patents

Abstract

An industrial roller shutter door rests on a horizontal spindle supported over the door frame by bearings at each end. The shutter slats deploy from the roll through a fixed downwards-directed slit, thereby progressively reducing the radial distance between the outermost slats and the spindle. Each end of the spindle rests in a bearing mount that progressively advances towards the slit as the radial distance reduces. The bearing advancement is synchronised at each end in a symmetrical plane.

Description

The invention relates to a roll end with a wound on a winding shaft curtain, a support means for supporting a bearing of the winding shaft, a support means associated drive means and a transmission with a transmission device for transmitting a rotational movement from an output member of the drive means to a driven unit on the winding shaft.

Such a Rollabschluss is for example from the US-A-1667081 known. This publication discloses a roll closure in the form of a manually operable shutter with a windable on a winding shaft curtain, a support means for supporting a bearing of the winding shaft, a drive means associated with the support means and a transmission with a transmission device for transmitting a rotary motion from an output member of the drive means to a driven unit on the winding shaft. The state of the art after the US-A-1667081 thus forms the preamble of the appended claim 1. The transmission device has a perpendicular to the winding shaft arranged rotary shaft, which meshes via a spur gear with a gear on the winding shaft.

In particular, the invention relates to a roll-up door, in which a relatively heavy rolling armor, which closes a door opening in the closed state, can be wound on a winding shaft mounted on supporting devices in the form of consoles above the door opening on the left and right. Such roller doors are usually provided with a geared motor which is attached to one of the two consoles and drives the winding shaft via a gearbox for opening and closing the roller door. As a transmission, for example, a chain transmission with a chain that is guided around a seated on an output shaft of the geared motor drive pinion and a seated on the winding shaft gear.

It is also basically known to arrange the winding shaft on the support displaceable. When unwinding and winding up the curtain, the winding radius changes accordingly. Without displacement, thus the insertion angle of the curtain would change in the left and right of the occlusive opening provided guides. With sliding axis of rotation of the winding shaft, the curtain can be inserted as straight as possible even with changing winding radius.

To move the winding shaft on the support different techniques and mechanics are known. From the WO 00/58592 It is known to provide for the displacement of a four-bar chain. It is expressly referred to the WO 00/58592 Referenced.

This in the WO 00/58592 Construction shown works very well for smaller rolling stock. As the size and weight of the curtain increased, however, a deformation of the console acting as a support device resulted in unpublished test series. This deformation which occurs under load can lead to wear, jamming or other impairment of the displacement mechanism, in particular in the case of support devices provided with a displacement device.

The invention has for its object to provide a roll closure of the type mentioned in which even with lighter or more filigree or equipped with pivoting support devices larger and / or heavy Behange driven without functional impairment are movable.

This object is achieved by a roll closure with the features of the attached claim 1.

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

According to the transmission device of the transmission is formed or arranged symmetrically. This occurs at a plane of symmetry that passes through the support device. The plane of symmetry is substantially perpendicular to the axis of rotation of the winding shaft.

The invention is based on the finding that a lateral force transmission from the output shaft of the drive to the winding shaft leads to a horizontal torque which is perpendicular to the opening plane of the roll termination. For example, the load side of a chain of a chain transmission used as a transmission device pulls the winding shaft down around the bearing supported on the support device. This torque must be absorbed by the support device, which deforms in the worst case accordingly. Now you can indeed dimension the support accordingly stronger, but this would lead to a higher cost in the production of the support device. This is particularly the case when the support device still includes a displacement mechanism for the bearing, such as in the WO 00/58592 described. The said torque must then be supported by the moving parts, which can lead to increased friction, increased wear or even the failure or breakage of these parts in the worst case.

The invention now proposes a balanced force transmission whose axis of symmetry or plane of symmetry passes through the support device. The plane of symmetry extends in particular between attachment points with which the support device is fixedly secured and / or on which a bearing of the winding shaft of whatever kind is supported on the support device. This is achieved by the reproduced in the characterizing part of the appended claim 1 features. Optionally, other symmetries, for example, a symmetry of the output member and / or the driven unit are provided in addition to the symmetry of the transmission element depending on the type of transmission.

As a support means consoles are provided in a preferred embodiment, which allow a displacement of the axis of rotation of the winding shaft for the purpose of adaptation to the respective winding radius. This is, for example, a joint bracket, preferably one of those in the WO 00/58592 described type.

The symmetrical power transmission according to the invention can be achieved in various ways. Thus, for example, the support means could be formed like a frame and the power transmission takes place within the frame. This is a possible way with simple support means, but relatively complicated with more complicated ones such as a four-bar console. Therefore, an embodiment is preferred, with a plurality of force transmission paths, which compensate each other for a horizontal, perpendicular to the axis of rotation of the winding shaft torques, wherein, for example, on both sides of the support means at least one transmission member of the transmission device is provided. This embodiment is based on the idea of distributing the power transmission on both sides of the support device so as to avoid a horizontal torque which is perpendicular to the closing plane of the roll termination.

The invention is particularly advantageous when the entire drive device is attached to the support device. Thus, the entire unit of support with attached drive and supported thereon winding shaft can be configured with symmetrically balanced power transmission.

The transmission is preferably a form-fitting traction mechanism, ie in particular a chain transmission or a toothed belt transmission. As a drive device electrical geared motors are preferably used, the output shaft is coupled by means of a self-locking gear provided on the drive to an electric motor. At standstill of Rollabschlusses thus bearing on the winding shaft weight of the curtain is transmitted via the positive gear on the self-locking drive gear and recorded there. To create the symmetry, the output shaft is preferably provided with a plurality of drive wheels, such as in particular drive pinions.

In order to create a safe, a door crash preventing positive power transmission, the drive wheels are preferably positively connected, for example by means of a feather key, rotatably connected to the output shaft. In a preferred embodiment, not only the transmission members, but also their drive wheels are arranged or formed symmetrically to the plane of symmetry.

The transmission of the transmission preferably has a plurality of axially juxtaposed parallel loaded Endloszugmittel. This allows for given gear ratios, the use of the smallest possible driven wheels on the winding shaft. If these driven wheels are too big, they could stand over the winding shaft, and the winding shaft would have be suitably relined to the opening boundary, if the curtain should run as perpendicular to the guides over the entire travel path of the roller shutter. For sprockets as small as possible (for example, less than about 300 mm in diameter) small drive wheels or pinions must be used at the output of the drive device at given gear ratios (eg 4: 1 and / or 3: 1). On the other hand, the traction means must have a very high security against breakage, for example, a sixfold security is required. If, for example, a chain is used as a traction device, it must have a large pitch with such a high resistance to breakage. Correspondingly large must be the sprockets, for example, sprockets with fewer than 11 teeth are currently not commercially available. Using a pinion with 11 teeth and correspondingly large pitch of the chain, then the driven wheels on the shaft at the given gear ratios are too large, and you have to work with relines.

These problems can be avoided in an advantageous embodiment of the invention by the plurality of juxtaposed parallel loaded traction means. Since the force can now be distributed to several traction means, they can be dimensioned correspondingly smaller. This results in chains that they can be performed with less division. Correspondingly smaller are the currently 11-toothed smallest available on the market pinion executable and correspondingly small, the driven wheels can be sized. Incidentally, a too large pitch would also cause the rotational movement to be more uneven the fewer teeth the pinion has. A non-uniform rotational movement means more drive on the entire surface of the Rollbehanges: But if several traction means loaded in parallel, and drive pinion can be used with more, correspondingly smaller spaced teeth, which contributes to smoothness.

Preferably, a plurality of traction means are respectively provided on both sides of the support means. This plurality of traction means may be formed for example by a double chain. Preference is given to one-piece Double chains, as used for example for driving camshafts of high-quality engines, are used.

Although other planes of symmetry are conceivable, as long as only the above-described torque is absorbed within the support means, it is preferred for reasons of simplicity, if the traction means are arranged symmetrically to the center plane of the support means forming the plane of symmetry. Accordingly, it is preferred if the driven unit has a plurality of wheels arranged on or on the winding shaft, such as, in particular, toothed wheels or toothed belt pulleys. The plurality of driven wheels is preferably designed and arranged symmetrically to the plane of symmetry.

It is thus preferred that both the transmission device and the driven member and the driven unit are arranged symmetrically and / or formed.

However, the symmetrical design preferably has the following exception: If a force transmission takes place on both sides of the drive device, it is preferred that the power transmission takes place on one of the sides in a completely positive manner and the other of the two force transmissions takes place in a force-locking manner. The form-fitting provides optimal security against falling of the curtain. A frictional connection allows each of the two transmission members to apply the same tensile force in order to completely eliminate the above-mentioned torque can. This solution is preferably achieved in a concrete embodiment in that at least a first or a first group of driven wheels is driven by a first transmission member of the transmission and is positively connected to the winding shaft and that at least a second or a second group of driven wheels by a second transmission member of the transmission is driven and is non-positively connected to the winding shaft. Of course, the adhesion could also be provided at another point of the power transmission, for example between the output shaft and the pinion seated thereon. It is preferred to provide the adhesion to the winding shaft, since there because of the larger diameter the driven wheels easier - for example by means of a clamping sleeve - can be achieved.

Fig. 1

eine Explosionsdarstellung einer Abstützeinrichtung für einen Rollabschluss in Form einer Gelenkkonsole für ein motorisch angetriebenes Rolltor auf einer Seite einer Wickelwelle des Rolltores, welche mit einem Elektroantrieb versehen ist;

Fig. 2a, 2b

im Schnitt und in Draufsicht eine bei der Anordnung von Fig. 1 verwendbare übliche Spannhülse;

Fig. 3

eine Seitenansicht auf die zusammengesetzte Anordnung von Fig. 1 in einer ersten Betriebsstellung;

Fig. 4

eine Ansicht wie in Fig. 3 auf die Anordnung in einer zweiten Betriebsstellung;

Fig. 5

eine Schnittdarstellung durch die Anordnung der Fig. 3 und 4 entlang der Linie C - C;

Fig. 6

einen Schnitt entlang der Linie B - B von Fig. 5 in der ersten Betriebsstellung (entsprechend Fig. 3); und

Fig. 7

einen Schnitt entlang der Linie B - B wie in Fig. 6 in der zweiten Betriebsstellung (entsprechend Fig. 4).

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

Fig. 1

an exploded view of a support device for a roll closure in the form of a joint bracket for a motor-driven roller shutter on one side of a winding shaft of the rolling shutter, which is provided with an electric drive;

Fig. 2a, 2b

in section and in plan view one in the arrangement of Fig. 1 usable standard adapter sleeve;

Fig. 3

a side view of the composite arrangement of Fig. 1 in a first operating position;

Fig. 4

a view like in Fig. 3 on the arrangement in a second operating position;

Fig. 5

a sectional view through the arrangement of Fig. 3 and 4 along the line C - C;

Fig. 6

a section along the line B - B of Fig. 5 in the first operating position (corresponding to Fig. 3 ); and

Fig. 7

a section along the line B - B as in Fig. 6 in the second operating position (corresponding Fig. 4 ).

In Fig. 1 a winding shaft 2 and a support means 4 for supporting the same is shown. The winding shaft 2 is part of a Rollabschlusses in the form of a roll-up door. The winding shaft 2 serves a curtain, not shown here, here a door leaf in the form of a roller door, a Rolltorgitters, a roller blind or Like, in the course of opening and closing a door opening also not shown and unwound. In this case, the support device 4 supports the winding shaft 2 at an edge region bordering the door opening, for example in the region of a camber 66 (see, for example, FIG. Fig. 3 ).

The support 4 has a fastened to the fall 66 joint console 6, which is substantially as in the WO 00/58592 is constructed described. Accordingly, the joint bracket 6 in the embodiment shown here, two four-bar linkages 8, by means of which a bearing for a winding shaft, here an over the joint bracket 6 inverted apron 10, can be slidably mounted. On the apron 10, a bearing block 12 for the storage of the winding shaft 2 is fixed here. In addition, a drive device in the form of a provided with gear part 14 and motor part 16 Wellentorantriebes 18 is attached to the movable skirt 10. The gear part 14 of the Wellentorantriebes has in a conventional manner a self-locking worm gear (not shown).

The transmission part 14 is provided with an output member in the form of an output shaft 20 which protrudes from both sides of the transmission part 14 and is provided at its free ends with drive wheels in the form of drive pinions 22, each with two adjacent sprockets. The drive pinions 22 are, as out Fig. 3 and 4 can be seen, by means of a feather key 24 positively against rotation on the output shaft 20 is placed.

To form a driven unit of the winding shaft 2, two driven wheels in the form of gears 28 are mounted on a smaller diameter bearing part 26 of the winding shaft 2 left and right of the bearing block 12, which are each provided on its outer circumference with two adjacent sprockets 30. The pair of left and right of the bearing block 12 arranged gears 28 forms the driven unit of a traction mechanism 32, which transmits the power from the output shaft 20 with a predetermined transmission ratio (4: 1 or 3: 1) on the winding shaft 2. A first gear 28a is by means of another key 34 (see Fig. 5 ) on the bearing part 26 of the winding shaft 2 mounted rotationally. The second gear 28b is frictionally mounted on the bearing part 26 of the winding shaft 2 by means of a clamping sleeve 36.

The traction mechanism 32 has as transfer elements two double chains 38, which are shown in the drawings only schematically by double-dashed lines. The double chains each have chain links, which two areas for simultaneously detecting the respective adjacent sprockets 30 of the gears 28 and the sprockets of the drive pinion 22. Comparable double chains are used for example for controlling camshafts in engines and are therefore commercially available. The traction mechanism 32 has two of these double chains 38, the left and right of the storage, here the apron 10, run. The drive pinions 22, the double chains 38 and the gears 28 are symmetrical to a plane of symmetry 40 (see Fig. 5 ), which extends perpendicular to the axis of rotation 41 of the winding shaft 2 through the joint bracket 6, more precisely between the articulation points on the lintel 66 and their guides for the sliding guide of the skirt 10 therethrough. In the exemplary embodiment, the plane of symmetry 40 coincides with the median plane of the hinge bracket 6 and the entire support device 4.

For synchronous driving of the sliding movement of the winding shaft 2 on the joint bracket 6, a second traction mechanism 42 is provided. The second traction mechanism 42 has a rotatably mounted on the winding shaft drive pinion 44 and a driven gear 46 and a transmission member in the form of a (single) chain 48. The driven gear 46 is seated on a shaft which is centrally located in the upper region of the skirt 10 Shift gear 50 drives. The displacement gear 50 has in addition to the drive shaft 52 and a mounted thereon by means of feather key positively driven pinion still a guide shaft 54 with attached guide pin 56 and a closed about the drive shaft 52 and the guide shaft 54 to an endless loop positive traction means 58, such as another chain or a toothed belt. The entire structure of the shift gear 50 is best Fig. 4 out. To a strand 60 of the traction means 58, a stationary plate 62 of the joint bracket 6 is connected.

For mounting the in Fig.1 shown support means the hinge bracket 6 is fastened with its attachment side 64 to the lintel. The output shaft 20 is connected by means of a further keyway connection with a hollow shaft on the drive gear in the transmission part 14. On the output shaft 20, the drive pinion 22 are rotationally fixed by means of the key 24. The entire shaft gate drive 18 is attached to the underside of the skirt 10. The bearing block 12 is fastened to the top of the skirt 10. The first gear 28a is rotationally fixed by means of the key 34 on the bearing member 26, and the second gear 28b is clamped by means of the clamping sleeve 36 on the other side of the bearing block 12 on the bearing member 26. For clamping, the clamping sleeve 36 as shown in the Fig. 2a and 2b shows around the circumference distributed clamping screws, which achieve via wedges a reduction in the inner diameter and an increase in the outer diameter. The drive pinion 44 is mounted non-rotatably on the outermost free end of the bearing part 26 by means of a feather key connection.

The following is with reference to the Fig. 3 and 4 explains the function of the roller door described here. Fig. 3 shows the position with fully unwound door leaf, ie the closed position. The apron 10 has been moved on the joint bracket 6 under the leadership of the four-bar linkage 8 very close to the camber 66. When opening the gate of the shaft gate operator is actuated. He drives the output shaft 20 at. The force is evenly distributed to the two double chains 38 distributed to the gears 28 and thus the winding shaft 2. Due to the symmetrical power transmission, a perpendicular to the door opening and horizontally directed torque in the support device 4 is avoided. As a result, lateral loads on the four-bar linkages 8 are avoided.

When turning the winding shaft 2 increases according to the rolled up curtain the winding radius. At the same time, the displacement gear 50 is driven via the second traction mechanism 42 with a suitable translation. This pulls the apron 10 and thus the bearing block 12 with the winding shaft 2 and the shaft gate drive 18 and the transmission 32, 42, 50 away from the fall 66. The leadership This displacement movement takes place via the four-bar linkages 8. Fig. 4 then shows the end position with fully opened roller door.

The Fig. 6 and 7 show the in the Fig. 3 and 4 shown respective end positions of the sliding movement in the section. It is clear to see the attachment of the strand 60 to the plate 62 and the guide on the four-bar linkages 8.

In the present embodiment in the form of a roll-up door, the single chain acting on conventional previously known roller doors has been replaced by two double chains 38. The symmetry of the arrangement eliminates the horizontal torque which is perpendicular to the opening plane of the door. In previous experiments, this torque has deformed the joint bracket 6 so that the construction did not withstand.

It is endeavored to use the smallest possible gears 28 (less than 300 mm in diameter), so that the curtain, so the door leaf, the rolling armor or the like, without relining vertically in guides, such as guide rails (not shown) enter the left and right of the door opening can.

Therefore, you have to use at given ratios (4: 1 and 3: 1) small drive pinion 22 at the output of Wellentorantriebes 18. With a required high breaking load for the drive chain (6-fold safety), this leads to a large division if one were to use a single chain. Such a large pitch indicates in a pinion with 11 teeth (sprockets with fewer teeth are not commercially available) that the pitch circle diameter is too large and thus the diameter of the sprockets, so here the gears 28. In addition, the rotational movement is the more non-uniform depending fewer teeth the drive pinion 22 has. Non-uniform rotational movement means more abrasion on the entire surface of the rolling armor.

• Kraftschluss, das Lasttrum beider Doppelketten 38 mit der gleichen Zugkraft zu beaufschlagen (nur ein ausgeglichener, hier symmetrischer Kraftfluss eliminiert das erwähnte Drehmoment vollständig) und durch den
• Formschluss optimale Sicherheit gegen Abstürzen des Rollpanzers.

Both drive pinion 22 on the output shaft 20 are positively secured against rotation with one key 24. The first sprocket 28a is also secured with a key 34 against rotation on the winding shaft 2. The other Sprocket 28b is fixed non-positively with the clamping sleeve 36 on the winding shaft. How to reach through the

• Tangle to apply the load of both double chains 38 with the same tensile force (only a balanced, here symmetrical power flow eliminates the mentioned torque completely) and by the
• Formschluss optimal security against crashes of the rolling armor.

As a clamping sleeve 36, a type is used here, in which two conical parts 68, 69 are clamped axially against each other.

The above-described second traction mechanism with sliding gear and the mechanics given thereby is a very interesting construction even without the present in the claims symmetric force distribution.

LIST OF REFERENCE NUMBERS

2

winding shaft

4

support means

6

joint console

8th

Four-bar chain

10

apron

12

bearing block

14

transmission part

16

engine part

18

Shaft gate operator (drive device)

20

output shaft

22

pinion

24

Adjusting spring

26

bearing part

28

Gears (sprockets)

30

Cassettes

32

traction drives

34

Key Connection

36

clamping sleeve

38

double chain

40

plane of symmetry

41

axis of rotation

42

second traction mechanism

44

pinion

46

driven gear

48

Chain

50

shift gear

52

drive shaft

54

return shaft

56

return sprocket

58

traction means

60

Trum

62

plate

66

Stu rz

68

conical part

69

conical part

Claims (15)

1. Roller closure having a curtain than can be wound onto a winding shaft (2), a support device (4) for supporting a mounting (12) of the winding shaft (2), drive means (18) associated with the support device (4) and a drive (32) with a transmission device (38) for transmitting a rotary movement from a power takeoff member (20, 22) of the drive means (18) to a driven unit (28, 28a, 28b, 26) on the winding shaft (2),
   characterised in that
   the transmission device (38) is constructed and/or arranged symmetrically with respect to a plane of symmetry (40) that extends through the support device (2) substantially perpendicularly to the rotation axis (41) of the winding shaft (2), so as to allow a balanced transmission of forces.
2. Roller closure according to claim 1, characterised in that the mounting (12) is movably held on the support device (4) so that the position of the winding shaft (2) can be adapted to the particular winding radius.
3. Roller closure according to claim 2, characterised in that the support device (4) has a sliding guide, particularly a four-joint guide (8), for the mounting (12).
4. Roller closure according to one of the preceding claims, characterised in that on both sides of the support device (4) there is at least one transmission member (38) of the drive apparatus (32).
5. Roller closure according to one of the preceding claims, characterised in that the drive means (18) are attached to the support device (4).
6. Roller closure according to one of the preceding claims, characterised in that the power takeoff member is formed as a power takeoff shaft (20) which is provided with a plurality of drive wheels, particularly drive pinions (22), for the drive in the form of a tension drive (32), particularly as an interlockingly engaging tension drive such as a chain drive or toothed belt drive.
7. Roller closure according to claim 6, characterised in that all the drive wheels (22) are connected for rotation with the power takeoff shaft (20) by interlocking engagement, in particular by means of an adjusting spring (24).
8. Roller closure according to one of claims 6 or 7, characterised in that the plurality of drive wheels (22) are arranged and/or constructed symmetrically with respect to the plane of symmetry (40).
9. Roller closure according to one of claims 6 to 8, characterised in that the tension drive (32) comprises a plurality of parallel loaded endless tension means (38) arranged axially adjacent to one another.
10. Roller closure according to claim 9, characterised in that on both sides of the support device (4) are provided two tension means arranged side by side or at least one multiple chain (38) with chain links which may engage a number of adjacent teeth simultaneously.
11. Roller closure according to one of the preceding claims, characterised in that the tension means (38) of the tension drive (32) are arranged parallel and symmetrically with respect to the central plane (40) of the support device (4) that forms the plane of symmetry and extends perpendicularly to the rotation axis (41) of the winding shaft (2).
12. Roller closure according to one of the preceding claims, characterised in that the driven unit (28, 28a, 28b, 26, 2) comprises a plurality of wheels, particularly gear wheels (28, 28a, 28b) or toothed belt pinions arranged side by side on the winding shaft (2).
13. Roller closure according to claim 12, characterised in that the plurality of driven wheels (28, 28a, 28b) are formed and/or arranged symmetrically with respect to the plane of symmetry (40).
14. Roller closure according to one of the preceding claims, characterised in that at least a first one (28a) or a first group of driven wheels are driven by a first transmission member (38) of the drive (32) and connected by interlocking engagement (34) with the winding shaft (2) and at least a second one (28a) or a second group of driven wheels are driven by a second transmission member (38) of the drive (32) and frictionally connected (36) to the winding shaft (2).
15. Roller closure according to one of the preceding claims, characterised in that the transmission device comprises at least one double chain (38), preferably a plurality of double chains (38) arranged symmetrically with the plane of symmetry (40).

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