FR2736087A1 - MOTORIZED SHUTTER - Google Patents

Abstract

The motorised roller shutter comprises a braked motor reducer (5) rotating a shutter winding tube (2) held at its ends (6,8) by support webs (3,4). A declutching coupling (11) is interposed between the motor reducer output shaft (10) and the winding tube. This enables, in the de-clutched position, the free rotation of the tube relative to the reducer under the influence of a force exerted directly on the shutter. A return spring (12), constrained during unwinding of the shutter, exerts a return couple on the winding tube. This causes tube rotation in the direction of shutter winding when a push is exerted on the shutter to open it. The winding tube is rotated by the reducer.

Description

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  The invention relates to a motorized rolling shutter comprising a brake gearmotor for driving in rotation a flow tube of an apron held, at its ends, by support cheeks.

  As appears, very clearly, with regard to the description

  which precedes, the present invention relates to the field of roller shutters for doors, windows or the like, comprising a geared motor with brake for the control of winding and unwinding

of the apron.

  Of course, we already know roller shutters responding to

  the description above. These generally include

  a winding tube around which is intended to be wound and which takes place an apron composed of a juxtaposition of blades at least articulated with respect to each other. In fact, the winding tube is kept in rotation at its ends by means of support cheeks disposed above the opening constituting the door, or the like, intended to be fitted with a rolling shutter. As regards, more particularly, the brake gearmotor, this is usually of the tubular type. Thus, while being fixed on one of the support cheeks, this tubular brake gearmotor is introduced into one of the ends of the winding tube and therefore comes to be housed inside the latter. Note, in this regard, that said winding tube is rotatably mounted, via an appropriate bearing, on said tubular gearmotor. At its opposite end, this winding tube is pivotally mounted on a section of axis crossing the

  plays support to which it is fixed.

  The problem, of course, with this type of motorized roller shutter is that the presence of the brake fitted to the gearmotor prevents manual drive of the winding tube in the event of an electrical failure, for example. To remedy this and, more particularly to allow the deployment or folding of the

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  roller shutter curtain in the event of a gearmotor malfunction or, quite simply, in the event of a mains supply failure, it is usual to equip this type of motorized roller shutter with a manual emergency control. This is in the form of a winch located on the side of the support cheek holding the axis section on which is rotatably mounted one of the ends of the winding tube. This winch acts, in reality, on a drive shaft passing through said support cheek as well as said axis section which is provided tubular, for this purpose. It thus authorizes the coaxial mounting of the drive shaft connected to the winch. Finally, this drive shaft is coupled to the output shaft of a differential, the input shaft of which is coupled to the output shaft of the geared motor.

  brake and the shell of which is made integral with the winding tube.

  Thus, in normal operation the gearmotor drives, through the differential, the winding tube of the roller shutter, knowing that the output shaft of this differential is locked in rotation by means of the winch which is either irreversible or braked. Otherwise, that is to say in case of malfunction of this engine, the control of the winch using appropriate control means, such as a crank, leads to the rotation of the shaft. training, this movement being transmitted to the

  winding tube through the differential.

  The major drawback resulting from such a design consists in that the operation by means of the crank acting on the winch turns out to be tedious. In particular, the mechanism is at the origin of a significant reduction ratio so that it is necessary to perform a multitude of crank turns to obtain the winding or the deployment of the deck. One can imagine that this slowness of the mechanism can lead to serious consequences, especially when it comes to evacuating, quickly, premises, for example in the event of fire and that the motor means are out of order , in particular due to a power cut in

electric energy.

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  The present invention is intended to meet this need by allowing a user to manually control the opening or

  quick closing of a motorized roller shutter.

  To this end, the invention relates to a motorized rolling shutter comprising a brake gearmotor for driving in rotation a winding tube of an apron held at its ends by support cheeks, characterized in that it comprises disengageable connecting means interposed between the output shaft of the gearmotor and the winding tube allowing, in the disengaged position, the free rotation of the latter relative to said gearmotor under the influence of an action exerted directly on

said apron.

  Advantageously, this roller shutter comprises, in combination, elastic return means put under stress during the unwinding of the deck, capable of exerting a return torque on the winding tube to cause the latter to rotate in the direction of the winding of the apron during a thrust exerted on the latter

  to obtain the opening of said roller shutter.

  In addition, according to a preferred embodiment, the disengageable connection means interposed between the output shaft of the gearmotor and the winding tube are associated, in addition, damping means allowing a progressive disengagement when the rolling shutter is in a position such that the above-mentioned elastic return means are under stress not compensated for by the weight of the

apron.

  The advantages arising from the present invention consist in that it suffices to disengage the connecting means connecting the output shaft of the gearmotor to the winding tube to allow the user to control the raising or lowering of the apron while acting. directly on the latter and, therefore, avoiding

any reduction ratio.

  The present invention, by providing the user with an easy and rapid rescue maneuver, responds advantageously

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  to the problem posed, not to mention that, from a mechanical point of view, this emergency maneuver proves to be very simple, a guarantee of its reliability. Other objects and advantages of the present invention will become apparent

  during the following description relating to a mode of

  realization which is given only by way of indicative and nonlimiting example.

  Understanding this description will be facilitated by

  referring to the attached drawings in which: - Figure 1 is a partial schematic view in section of a winding tube of a rolling shutter kept in rotation by supporting cheeks disposed at its ends, this figure i illustrating, moreover, a first embodiment of the disengageable connection means connecting the output shaft of the gearmotor to the winding tube; - Figures 2 and 3 illustrate schematically, partially and in section, a second embodiment of these disengageable connecting means coming to mechanically connect the output shaft of the gearmotor to the winding tube, Figure 2 corresponding to the engaged position, while Figure 3 shows the elements in the disengaged position; - Figures 4 and 5 correspond to schematic and sectional views illustrating a third embodiment of these disengageable connecting means according to the same principle as Figures 2 and 3; - Figure 6 shows, schematically and in perspective, the male part corresponding to the disengageable connection means as illustrated in Figures 4 and 5; - Figure 7 is a representation similar to Figure 6 illustrating the female part of these disengageable connecting means; - Figures 8, 9 and 10 correspond to partial schematic representations in section of disengageable connection means substantially similar to those illustrated in Figures 2 and 3 and

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  which have been associated with damping means making it possible to obtain a progressive disengagement; - Figure 11 shows schematically partially and in perspective of such damping means designed according to a second embodiment; - Figure 12 is a representation similar to Figure 11 and illustrating a third embodiment of these damping means; - Figures 13 and 14 show, respectively, a schematic perspective view and a partial view in section of these damping means designed according to a preferred embodiment. The present invention relates to a motorized roller shutter 1 shown schematically and partially in Figure 1 of the accompanying drawings. This roller shutter 1 comprises a winding tube 2 on which is wound and from which is unwound, normally, an apron (not shown) constituted by a juxtaposition of blades at least articulated with respect to each other. This winding tube 2 extends between two supporting cheeks 3, 4, coming to be placed in the upper part of the opening constituted by the door, window or

  similar, intended to accommodate said roller shutter 1.

  The latter being motorized, it includes a tubular type brake gear motor 5. More precisely, this brake gearmotor 5 is introduced into one of the ends 6 of the winding tube 2 while being fixed on the support cheek 3. In fact, at the level of this end 6 of the winding tube 2, that -this is mounted in rotation, by means of suitable means 7, on said brake gearmotor 5. At its opposite end 8 this winding tube 2 is engaged

  pivotally on an axis 9 fixedly mounted on the support cheek 4.

  The connection between the output shaft 10 of the gearmotor 5 and the winding tube 2 is effected by means of connection means 11 which are preferably of the disengageable type. Through this characteristic it is possible, once the means

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  link 11 disengaged, to control the free rotation of the winding tube 2 relative to the brake gearmotor 5. More particularly in the event of a malfunction of the latter, and once said connecting means 11 disengaged, action can be taken, directly on the roller shutter curtain to push it towards the

  high or, on the contrary, to close it.

  In this regard, as shown in FIG. 1, it is advantageous to equip, in combination, the roller shutter 1, with elastic return means 12 put under stress during the unfolding of the deck and able to exert a torque of recall on the winding tube 2 to ensure the driving thereof in rotation, in the direction of winding of said apron, when, precisely, the latter is pushed upwards to obtain the opening of the roller shutter 1. It is obvious, in fact, that in the absence of such elastic return means or equivalent means capable of controlling the winding of the apron on the winding tube 2, this apron, under the action from an upward thrust, risk of folding up in an uncontrolled manner inside the welcoming box, usually,

said winding tube 2.

  It will be noted that as means equivalent to the elastic return means 12 for controlling the winding of the apron on the winding tube 2, one can imagine the use of guides or even of a strap elastic return to ensure orientation

  of said deck around this winding tube 2.

  Anyway, according to the example illustrated in Figure 1, the elastic return means 12 are in the form of a helical spring 13 housed inside the winding tube 2 and one end 14 of which is made integral with the axis 9 on which this winding tube 2 is rotatably mounted. While the opposite end 15 of this spring 13 is made integral in rotation with said winding tube 2. In this regard and preferably, this end 15 of the spring 13 is fixedly mounted on a slider 16 which, while by being immobilized, in rotation, relative to said tube

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  winding 2, is able to move axially inside

this last.

  As for the releasable connecting means 11 proper, they are shown in different embodiments in the accompanying drawings. In particular, in the context of FIG. 1, these disengageable connecting means 11 are constituted by a differential 17 comprising an input shaft 18 coupled to the output shaft 10 of the brake gearmotor 5, a shell 19 made integral, in rotation

  of the winding tube 2 and an output shaft 20.

  In this regard, it should be observed that, to these disengageable connection means 11 are associated declutching and clutch control means 21 in the form of means for unlocking or rotationally blocking the output shaft 20 of the differential 17. Thus, according to this embodiment illustrated in FIG. 1, these declutching and clutch control means 21 consist of a locking pin 22 coupled to said output shaft 20 of the differential 17 and extending, coaxially, through the tubular axis 9 on which the winding tube 2 is rotatably mounted at its end 8. This locking pin 22 also passes through the cheek support 4 so as to cooperate, at this last, with locking means 23 able to immobilize or on the contrary to release in rotation said locking pin 22. By way of example illustrated in this FIG. 1, the locking means 23 are in the form of a part in "U" 24 which, when 'It is engaged on the flattened end 25 of the locking pin 22 immobilizes the latter in rotation. One can, of course, imagine any type of traction member to allow an operator to act easily on the locking means 23 and release, in rotation, the locking pin 22 when there is instead of ordering, manually,

  opening or closing the roller shutter curtain 1.

  If we now refer to Figures 2 and 3, we see that the disengageable connection means 11 are constituted, in this case, by two gears, in particular frustoconical, 26, 27, of which

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  one 26 is made integral in rotation with the winding tube 2, while the other 27 is mounted fixed in rotation on the output shaft of the brake gearmotor 5. As for the clutch and clutch control means 21, they are constituted, on the one hand, by a sliding mounting of one 27 of these gears relative to the output axis 10 and elastic return means 28 capable of pushing said gears 26, 27 into a engaged position. On the other hand, these clutch and clutch control means 21 comprise traction means 29 extending inside the winding tube 2 in order to cooperate with the sliding gear 27. These traction means 29 pass, moreover, through the support cheek 4, passing through the tubular axis 9, so as to make them accessible to the user and to enable him to control the disengagement or the clutch of said connecting means. disengageable 11. As part of the mounting recommended through Figures 2 and 3, we see that the elastic return means 28, in the form of a helical spring, are interposed between the gear 27 mounted fixed in rotation on the output shaft 10 and the free end of the latter, this so as to push this gear 27 in the direction of the gear 26 integral in rotation with the winding tube 2. As for the traction means 29, they have for the function, during a declutching command, of moving this gear 27 relative to the gear 26 by pulling it, precisely, in the direction of the free end of the output shaft 10,

  against said elastic return means 28.

  The embodiment corresponding to FIGS. 4 to 7 represents disengageable connection means 11 in the form of two plug-in parts 30, 31 which, in the plugged-in position, allow the drive of the winding tube 2 via the gearmotor 5 and , on the contrary, in the disconnected position, allow the free rotation of said

winding tube 2.

  As in the previous embodiment, there are, in this case, elastic return means 32 acting so as to keep the parts 30, 31 in the plugged-in position

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  and therefore constituting, in part, the clutch and clutch control means 21. Here again, these means 21 are supplemented by traction means 29 substantially similar to those described in the context of the embodiment corresponding to Figures 2 and 3 and which are made accessible to the user to enable him,

  specifically, to control the clutch.

  It should be observed that in a fully deployed position of the roller shutter deck, the weight of said deck rests entirely on the threshold of the door, window or the like, or on any stops located at the lower end of the guide rails inside which move, precisely, the blades making up this deck. At the same time, this deck no longer exerts torque on the winding tube 2, while conversely the elastic return means 12 are at maximum under stress and exert a significant return torque on this tube winding 2 in the direction of

the winding of said deck.

  If, at this instant, the user actuates the declutching command, the winding tube 2 is strongly rotated under the impulse of these elastic return means 12, in the direction of winding of the deck and, this, until the latter compensates,

  by its weight, this return force of the spring 13.

  It is obvious that this sudden acceleration of the rotation of the winding tube 2 has the consequence of placing heavy demands on the mechanics. Even assuming that it is defined as sufficiently resistant, the instantaneous release of the elastic return means 12 and the brutal driving of the winding tube 2 are at the origin

  a surprising operating noise.

  In order to remedy this problem and allow progressive compensation for the action exerted by the elastic return means 12 on the winding tube 2, this under the influence of the weight of the deck, it has been imagined to associate to the disengageable connection means 11 damping means 33 preventing, precisely, the expansion

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  brutal of said elastic return means 12 when these

  exert an uncompensated stress on the winding tube 2.

  Reference is now made to FIGS. 8 to 14 illustrating

  exemplary embodiments of these damping means 33.

  In particular, in the context of FIGS. 8 to 10, it is observed that the disengageable connection means 11 are presented, like the solution illustrated in FIGS. 2 and 3, in the form of two gears 26A, 27A, one of which 26A is made integral in rotation with the winding tube 2, while the other 27A is mounted fixed in rotation on the output shaft 10 of the brake gearmotor 5. In addition, the gear 27A is slidably mounted on this shaft output 10 and elastic return means 28A push said gears 26A, 27A into a engaged position. These Figures 8 to 10 illustrate, in addition, the clutch and clutch control means in the form of traction means 29 extending inside the tube

  winding 2 in order to cooperate with the sliding gear 27A.

  As for the damping means 33 proper, they are constituted, in this case, by a braking ring 34 of an expandable nature, for example rubber, interposed between the gears 26A and 27A and which is able to ensure the contact between them, both in a engaged position, as illustrated in the

  8, only in a disengaged position corresponding to FIG. 9.

  Very precisely, by exerting traction on the sliding gear 27A, the toothing of the latter comes, initially, to disengage from the corresponding toothing of the gear 26A integral in rotation with the winding tube 2. Simultaneously, the braking ring 34 moves into an expanded position and maintains contact between the gears 26A and 27B. Thus, the rotation of the gear 26A, under the action of the elastic return means 12 acting on the winding tube 2, is braked by means of said braking ring 34. Once the action of the means of elastic return 12 compensated by the torque applied to the winding tube 2 under the impulse of the weight of the bulkhead, the action exerted on it 2736087 continues the traction means 29 until there is have more contact with the

  braking ring 34 simultaneously with the two gears 26A, 27B.

  Of course, one can imagine a similar design in the context of an embodiment of disengageable connection means 11 as illustrated in FIGS. 4 to 7 o the gears, as appropriate, 26, 27 or 26A, 27A are replaced by plug-in parts 31, 30. The solution shown in FIG. 11 reveals shock-absorbing means 33 in the form of a flywheel 35 rotatably mounted on the axis 9 on which the tube is mounted. winding 2. This flywheel 35 is connected, more particularly by means of a spring 36 to a transmission wheel 37 integral in rotation with said winding tube 2. Thus, once the clutch control has been carried out, the elastic return means 12, illustrated in broken lines in FIG. 11, relax until their action is compensated for by the torque produced by the weight of the deck. Consequently, they rotate the winding tube 2 which, via the transmission wheel 37, must drive the flywheel 35. Also, this relaxation of the elastic return means 12 takes place, necessarily , gradually. It will be noted that this flywheel 35 does not create any discomfort for moving, subsequently and in the disengaged position of the disengageable connecting means 11, the apron of the roller shutter by direct action on the latter. Indeed, the speed communicated to the tube

  winding 2 under these conditions is comparatively very low.

  The solution presented in the context of FIG. 12 is, from the point of view of its operation, substantially similar to that corresponding to FIGS. 8 to 10. However, instead of exerting a braking action between two parts which, depending on whether they are in contact or not, authorize or not the drive of the winding tube 2 via the brake gear motor 5, said braking means 38 constituting the damping means 33, act on the slider 16 corresponding to the return means elastic 12 and mounted

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  integral in rotation with the winding tube 2. In fact, the braking means 38 are in the form of a braking disc 39 mounted stationary in rotation on the axis 9 with respect to which said winding tube 2 is pivotable. In reality, the brake disc 39 comes into contact with the front face 40 of the slider 16 only under certain conditions, that is to say when the elastic return means 12 are put under stress, resulting in an elongation of the spring 13 which then pushes the cursor 16 against the disc

braking 39.

  The latter is, moreover, slidably mounted on the axis 9 while a spring 41 attempts to push it back towards the cursor 16

  against a limit stop not visible in the drawings.

  Thus, it is understood that when deploying the apron, this results in the tensioning of the elastic return means 12 and, therefore, the progressive elongation of the spring 13. Beyond a given stroke of said apron and, therefore, of the elongation of a defined length of the spring 13, the cursor 16 comes into contact with the braking disc 39. Then, by further deploying the roller shutter deck, the spring 13 is further elongated so that the cursor 16 comes to push the brake disc 39 against the action of the spring 41. Therefore, when controlling the disengagement of the disengageable connection means 11, the elastic return means 12 are released and cause the tube to rotate winding 2 via the slider 16, the rotation of which is however braked under the influence of the braking disc 39. During this time, the length of the spring 13 decreases and the braking disc 39 abuts on the axis 9. As cursor 16 is no longer e n contact with this brake disc 39, the roller shutter can be manipulated by direct pull on the

apron without any difficulty.

  Consequently, it will be noted that, here again, the action of the damping means 33 can be limited in the particular situation where, in the final phase of deployment of the deck, the torque provided by the latter on the winding tube 2 decreases

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  gradually until reaching zero, while, for their part,

  elastic return means 12 are under maximum stress.

  The embodiment illustrated in the context of FIGS. 13 and 14 is somewhat particular insofar as there is a direct association between the disengageable connecting means 11 and the means

shock absorbers 33.

  More particularly, said disengageable connection means 11 consist, on the one hand, of a connection tube 42 mounted fixed in rotation on the output shaft 10 of the brake gearmotor 5. On the other hand, they comprise a wheel d drive 43 fitted on the tube

  42 and made integral in rotation with the winding tube 2.

  Finally, said disengageable connecting means 11 comprise a dog clutch 44 which, in the engaged position, aims to provide the connection between the connecting tube 42 and the drive wheel 43 and, of course, in the disengaged position to allow the free rotation of the latter relative to the brake gearmotor 5. Thus, this dog clutch 44 comprises, at least one drive finger 45 passing through an axial light 46 formed in the connecting tube 42 and coming to be housed in

  a groove 47 machined in the wall 48 of the drive wheel 43.

  By exerting traction on this dog clutch 44 which, moreover, is slidably mounted inside the connection tube 42, this by means of traction means 29 as already described above, his or her fingers drive 45 slide inside the axial slots 46 of the connecting tube 42 and, simultaneously, in the corresponding groove 47 at the level of the drive wheel 43. In this connection, this groove 47 has at least one oriented portion axially 47A and as long as the drive finger or fingers 45 of the dog clutch 44 remain engaged in this axial portion 47A of the groove 47, there is direct drive of the tube

  drive 2 by the brake gear motor 5.

  Furthermore, said groove 47 is necessarily open at its end 49 located in the direction from which the dog clutch 44 is pulled in order to obtain disengagement. So when under the command of

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  movement of the dog 44 its drive finger or fingers 45 come out of their corresponding groove 47 at the height of this through end 49, there is a disengagement, that is to say that the winding tube 2 can pivot freely relative to the geared motor brake 5. In fact, between this engaged position and the total disengaging position, the drive finger (s) 45 of the dog clutch 44 are deployed, in addition, in a portion of groove 47B playing the role of damping means 33, of which different modes of achievements have

already described.

  More particularly, this groove portion 47B is delimited by at least one side of helical shape 50 against which the drive finger 45 bears when the drive wheel 43 tends to be driven in rotation under the impulse of the means of

elastic return 12.

  More precisely, when these elastic return means 12 are under stress not compensated by the weight of the roller shutter deck, they tend to rotate the winding tube 2 to which the drive wheel 43 is made integral in rotation. Thus, when, under these conditions, the clutch is controlled and that, a pull is exerted on the dog clutch 44 against the action of a spring 28B tending to push it, systematically, in a engaged position, its or its drive fingers 45 move in the axial aperture (s) 46 of the connecting tube 42 and, simultaneously, in the axial portion 47A of the groove (s) 47 formed in the drive wheel 43. It is clearly understood that as long as this or these drive fingers 45 are kept engaged in this axial portion 47A of the groove 47, the drive wheel 43, under the action of the elastic return means 12, exerts only a torque on said training fingers t 45 of

dog 44.

  On the other hand, once released from this axial portion 47A, from the groove 47, the drive wheel 43, under the action of the means of

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  elastic return 12, acts on the drive finger or fingers 45 of this dog 44 via the helical side 50 of the portion 47B of this groove 47. Also, the stresses applied to this or these drive fingers 45 decompose into a torque and into an axial force oriented in the direction of declutching the dog clutch 44. In the end, this has the effect of gradually pushing said dog clutch 44 into its declutching position against the action of the spring 28B and of allow rotation, just as gradual, of the drive wheel 43 under the action of the elastic return means 12 coming, thus, slowly relax. It will be noted that the return force of the spring 28B and the pitch of the propeller corresponding to the helical part 47B of the groove 47, make it possible to intervene on

  the characteristics of the depreciation thus obtained.

  It will be understood that during this damping phase of the declutching action, the dog clutch 44 is more stressed by the drive wheel 43 than by the traction means 29. On the other hand, once the declutching position has been reached, these traction means 29 must be designed to maintain the dog clutch 44 in its disengaged position against the action of the spring 28A tending to push it back into the engaged position. Thus, these traction means 29 can be equipped with a control lever 51 having the possibility of occupying at least two stable equilibrium positions corresponding to the engaged position of the dog clutch 44 and to the disengaged position of the latter. Arises, then, the case of declutching when the action of the elastic return means 12 is, in reality, compensated by the torque exerted by the weight of the deck on the winding tube 2. If the portion 47B of the groove 47 is helical in shape, it is necessary, when the drive fingers 45 of the clutch dog 44 engage therein, to simultaneously control in rotation the drive wheel 43 and therefore the drive tube 2 under the impulse of this dog clutch 44 and therefore traction means 29. This is particularly restrictive and requires the installation of means

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  tensile 29 of mechanical strength designed for this purpose. In fact, to avoid this, the opposite side 52 of that 50, of helical shape, of this groove portion 47B extends, preferably, in the extension of the axial portion 47A from the latter to the through end 49 of the groove 47. More particularly, it is necessary to imagine the drive wheel 43 stationary in rotation. Thus, during the clutch release command, the drive finger or fingers 45 of the dog clutch 44 move, first of all, in the naxial portion 47A of the groove 47. Then, under the action of the traction means 29, this or these drive fingers 45 follow their

  progression until emerging from said groove 47 at its end 49.

  It should be noted that due to this configuration, this through end 49 of a groove 47 is widely open and

  facilitates the return to the engaged position of the dog clutch 44.

  In view of the above description, we understand well the

  advantages which flow from the present invention. Indeed, when it comes to maneuvering the roller shutter deck in the event of a malfunction of the brake gearmotor 5, it suffices to actuate the clutch and clutch control means 21 in order to disengage, in rotation, the winding tube 2 relative to this brake geared motor 5 to allow a user, in particular to open the roller shutter deck by acting directly on the deck. Such an emergency maneuver proves to be particularly rapid in execution so that one gains in security, in particular

  when there is an urgent need to evacuate premises.

  It is further observed that this emergency control mechanism for a motorized roller shutter is very simple compared to the known solution using a winch requiring for its control a crank of which not all the roller shutters are necessarily

equipped.

  Therefore, the present invention should be considered as

  representing a clear progress in the technical field considered.

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  Although the invention has been described in connection with an embodiment, it is understood that it is in no way limited thereto and that it is possible to make various modifications to it in terms of shapes, materials and combinations of these various elements, without departing from the scope and spirit of the invention.

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Claims (19)

Claims   1. Motorized roller shutter comprising a brake gear motor (5) for driving in rotation a winding tube (2) of an apron held at its ends (6, 8) by support cheeks (3, 4 ), characterized in that it comprises disengageable connecting means (11) interposed between the output shaft (10) of the geared motor (5) and the winding tube (2) allowing, in the disengaged position, the free rotation of the latter relative to said geared motor (5) under the influence of an action exerted directly on said apron.   2. Roller shutter according to claim 1, characterized in that it comprises, in combination, elastic return means (12) placed under stress during the course of the deck capable of exerting a return torque on the tube d winding (2) to drive the latter in rotation in the direction of the winding of the apron during a thrust exerted on the latter to obtain the opening of said roller shutter.   3. Roller shutter according to any one of claims i and   2, characterized in that the brake gearmotor (5) is of the tubular type engaged in one (6) of the ends of the winding tube (2) and made integral with a support cheek (3), said tube winding (2) being rotatably mounted by means (7)   suitable on said brake gear motor (5).   4. Roller shutter according to any one of claims 1 to 3,   characterized in that the disengageable connecting means (11) are   associated declutching and clutch control means (21).   5. Roller shutter according to claims 3 and 4, characterized by   the fact that the disengageable connecting means (11) consist of a differential (17) comprising an input shaft (18) coupled to the output shaft (10) of the brake gearmotor (5), a shell (19 ) made integral, in rotation, with the winding tube (2) and an output shaft (20) cooperating with the clutch control means and 19 2736087   clutch (21) in the form of unlocking or locking means   rotation of the output shaft (20) of the differential (17).   6. Roller shutter according to claim 5, characterized in that the clutch and clutch control means (21) consist of a locking pin (22) coupled to said output shaft (20) of the differential (17) and extending, coaxially, through a tubular axis (9) on which the winding tube (2) is rotatably mounted at its end (8), this blocking axis (22) passing through, moreover, the support cheek (4) so as to cooperate, at the level of the latter, with locking means (23) capable of immobilizing or on the contrary of releasing said axis of rotation blocking (22).   7. Roller shutter according to claims 3 and 4, characterized by   the fact that the disengageable connecting means (11) consist of two gears, in particular frustoconical, (26, 27) one of which (26) is made integral, in rotation, with the winding tube (2), while the other (27) is mounted fixed in rotation on the output shaft (10) of the brake gearmotor (5), the clutch and clutch control means (21) being constituted, on the one hand, by a sliding assembly of one (27) of these gears relative to the output axis (10) and elastic return means (28) capable of pushing said gears (26, 27) into a engaged position and, on the other hand, by traction means (29) cooperating with the sliding gear (27), these traction means (29) passing through the support cheek (4) passing through a tubular axis (9) on which is mounted in rotation the end (8) of the winding tube (2), this of   so as to make them accessible to a user.   8. Roller shutter according to claims 3 and 4, characterized by   the fact that the disengageable connecting means (11) are in the form of two plug-in parts (30, 31) which, in the plugged-in position, allow the drive of the winding tube (2) by means of the geared motor (5 ) and, on the contrary, in the disconnected position, allow the free rotation of said winding tube 2736087   (2), the clutch and clutch control means (21) being constituted, on the one hand, by elastic return means (32), acting so as to hold the parts (30, 31) in the plugged-in position and, on the other hand, by traction means (29) made accessible to the user to enable him to control the declutching.   9. Roller shutter according to any one of claims 2 to 8,   characterized by the fact that it comprises damping means (33) associated with the disengageable connection means (11) in order to compensate for the action exerted by the elastic return means (12) on the winding tube (2) when this action is not, moreover, compensated by the torque exerted by the weight of the apron on said tube winding (2).   10. Roller shutter according to claims 7 to 9, characterized by   the fact that the damping means (33) consist of a braking ring (34) of an expandable nature, for example rubber, interposed between the gears (26, 27; 26A, 27A) or between two plug-in parts (31, 30 ), this braking ring (34) being able to ensure contact between the latter, both in a engaged position and in a disengaged position so as to ensure the braking in rotation of the gear (26; 26A) or the plug-in part (31) integral with the winding tube (2) when the latter   is driven under the impulse of the elastic return means (12).   11. Roller shutter according to any one of claims 2 to   9, characterized in that the damping means (33) are in the form of a flywheel (35) rotatably mounted on an axis (9) on which the winding tube (2) is pivotally mounted, this flywheel (35) being connected, in particular by means of a spring (36), to a transmission wheel (37) integral in rotation of said winding tube (2).   12. Roller shutter according to any one of claims 2 to   9, the elastic return means (12) of which are in the form of a helical spring (13) housed inside the winding tube (2) and one end (14) of which is made integral with the axis (9) on 21 2736087   which is rotatably mounted this winding tube (2), while the opposite end (15) of this spring (13) is fixedly mounted on a slider (16) which, while being immobilized in rotation relative to the tube winding (2) is able to move axially inside the latter, characterized in that the damping means (33) are constituted by braking means (38) in the form of a braking disc (39) mounted stationary in rotation on the axis (9) and able to cooperate with the front face (40) of the slider (16), especially when the elastic return means (12) are under duress.   13. Roller shutter according to claim 12, characterized in that the brake disc (39) is slidably mounted on the axis (9) and kept pushed back in the direction of the cursor (16), against a stop of   limit switch, using a spring (41).   14. Roller shutter according to any one of claims 1, 2   and 9, characterized in that the disengageable connection means (11) consist, on the one hand, of a connection tube (42) mounted fixed in rotation on the output shaft (10) of the brake gear motor ( 5) and, on the other hand, by a drive wheel (43) fitted on the connection tube (42) and made integral in rotation with the winding tube (2), a dog clutch (44) mounted to slide at interior of the connection tube (42) further comprising at least one drive finger (45) passing through an axial lumen (46) formed in this connection tube (42) and being received in a groove (47) machined   in the wall (48) of the drive wheel (43).   15. Roller shutter according to claim 14, characterized in that the groove (47) decomposes, starting from the engaged position and in the direction of the disengaged position of the dog clutch (44), there is an axially oriented portion (47A) in which is engaged the drive finger (45) of said dog (44), in the engaged position, a portion (47B) comprising at least one side of helical shape (50) against which the drive finger (45) is supported when the drive wheel (43) tends to be rotated under 22 2736087   the impulse of the elastic return means (12), this being disengaged, said groove (47) being, moreover, emerging at its end (49), in the direction of which the dog clutch (44) is moved to obtain the declutching, allowing the release of said drive finger (45) from said groove (47) and the free rotation of the drive wheel (43) and therefore of the drive tube (2) by   relative to the output shaft (10) of the gearmotor (5).   16. Roller shutter according to any one of claims 14 and   , characterized in that the dog clutch (44) is subjected to the action   a spring (28B) ensuring its return to the engaged position.   17. Roller shutter according to any one of claims 13 to   16, characterized by the fact that it comprises declutching control means in the form of traction means (29) capable of exerting on the dog clutch (44) a traction against the action of the spring (28B) for   bring it into a disengaged position, starting from the engaged position.   18. Roller shutter according to claim 17, characterized in that the traction means (29) comprise a control lever (51) capable of occupying at least two stable equilibrium positions corresponding to the engaged position of the dog clutch ( 44) and at the position disengaged from the latter.   19. Roller shutter according to claim 15, characterized in that the opposite side (52) of that (50) of helical shape corresponding to the portion (47B) of the groove (47) extends in the extension of the portion axial (47A) from the latter to   the through end (49) of the groove (47).