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EP3821103B1 - Drive system driving a screen, and apparatus comprising such a system - Google Patents

Drive system driving a screen, and apparatus comprising such a system Download PDF

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Publication number
EP3821103B1
EP3821103B1 EP19736732.9A EP19736732A EP3821103B1 EP 3821103 B1 EP3821103 B1 EP 3821103B1 EP 19736732 A EP19736732 A EP 19736732A EP 3821103 B1 EP3821103 B1 EP 3821103B1
Authority
EP
European Patent Office
Prior art keywords
drive system
compensation spring
spring
screen
turns
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19736732.9A
Other languages
German (de)
French (fr)
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EP3821103A1 (en
Inventor
Adrien Brondex
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Somfy Activites SA
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Somfy Activites SA
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Publication date
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Publication of EP3821103A1 publication Critical patent/EP3821103A1/en
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Publication of EP3821103B1 publication Critical patent/EP3821103B1/en
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
    • E06B9/56—Operating, guiding or securing devices or arrangements for roll-type closures; Spring drums; Tape drums; Counterweighting arrangements therefor
    • E06B9/68—Operating devices or mechanisms, e.g. with electric drive
    • E06B9/72—Operating devices or mechanisms, e.g. with electric drive comprising an electric motor positioned inside the roller
    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
    • E06B9/24—Screens or other constructions affording protection against light, especially against sunshine; Similar screens for privacy or appearance; Slat blinds
    • E06B9/40—Roller blinds
    • E06B9/42—Parts or details of roller blinds, e.g. suspension devices, blind boxes
    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
    • E06B9/56—Operating, guiding or securing devices or arrangements for roll-type closures; Spring drums; Tape drums; Counterweighting arrangements therefor
    • E06B9/60—Spring drums operated only by closure members

Definitions

  • the invention relates to a system for driving a screen, in particular a roll-up screen.
  • the invention also relates to a closing, screening or solar protection installation comprising such a drive system.
  • a closing, screening or solar protection installation comprises a screen that can be moved between two so-called end-of-travel positions, in particular a roll-up screen, such as a flexible apron, for example an apron formed by slats hinged together in the case of a rolling shutter or an awning fabric.
  • the closure installation also comprises a winding shaft, for example a winding tube on which the roll-up screen is fixed and is rolled up, or a shaft on which a cord or lace of the screen is wound.
  • the installation also comprises a drive system comprising an actuator comprising an electric motor, the actuator driving the winding shaft in rotation to deploy or fold the screen. The latter is therefore moved facing an opening in order to selectively close the latter.
  • the weight of this screen exerts a variable torque on the drive system, in particular depending on the position of this screen.
  • the object of the present invention is to produce a closing, screening or solar protection installation, as defined above, whose electrical consumption is low, in which, for example, the actuator is powered by an independent current source. , for example by cells or batteries.
  • Such a compensation spring makes it possible to generate a torque between a fixed part of the actuator and the winding shaft, this spring being kinematically connected, by one of its ends, with a fixed structure and, by its other end , with a movable part connected to the screen, in particular connected to the winding shaft.
  • the purpose of the compensation spring is to accompany the gear motor forming the actuator during the rising from a canvas or other type of screen.
  • WO 03/083245 describes a drive system comprising such a compensation spring.
  • the compensation force exerted by the spring is adapted to the torque developed by the screen which influences the drive means.
  • This torque is a function of the parameters relating to the drive system of the screen, for example the winding diameter, the dimensions of the screen, its specific weight and its position relative to the opening.
  • the parameters of the compensation spring in particular the length of wire and/or the number of turns, are determined according to the parameter parameters relating to the drive system of the screen.
  • means for adjusting the initial stress of a compensation spring may be provided.
  • the electric motor itself can be used to preload the compensating spring, to adjust the balance point of the screen. This point of balance is preferably provided at a point different from the end-of-stroke positions of the screen, for example halfway through the screen.
  • the compensation spring As the compensation spring is put under stress, that is to say rolls up on itself and its diameter decreases, it lengthens. In the known systems, provision is therefore made for the installation to stretch the spring in order to provide sufficient space for its fully wound configuration. In this case, the length of the installed compensation spring is greater than its length at rest and the turns of the installed compensation spring are not contiguous. This solution is not entirely satisfactory because in this case the spring is not maintained, is unstable and generates noise.
  • the radial space for the elongation or the displacement of the turns with respect to the axis of the winding tube is very limited.
  • Contact between the coils of the spring and the actuator and/or the winding tube generates noise in operation, which is unacceptable.
  • US 2012/000615 describes a drive system for a screen, which comprises as sole source of torque a spring which is radially isolated from a winding tube by a plastic sleeve.
  • This prior art relates to systems without an electric actuator and produces noise due to the contact of the coils of the spring with each other.
  • the invention intends to remedy by proposing a new drive system allowing the reduction of the noise caused by the spring despite a limited space for its assembly.
  • the invention relates to a system for driving a screen, comprising an actuator intended to drive in rotation a winding tube acting on the screen, and a compensation spring, mounted around the actuator and comprising several turns formed by winding a wire.
  • This system is characterized in that it comprises at least one plastic rod interposed between two consecutive turns of the compensation spring, and in that an external radius of said at least one rod is greater than a maximum external radius of the compensation spring. compensation.
  • the plastic inter-turn rods avoid noisy metal/metal contact between the spring and the winding tube.
  • the invention also relates to a closing, screening or solar protection installation comprising a screen, a frame, a winding tube and a drive system as mentioned above.
  • the figure 1 represents a closing, screening or solar protection installation 200 comprising a screen 6, a frame 4, a winding shaft 5 and a drive system 1 for the screen 6, in particular a roll-up screen, such as a roller shutter, mounted in a frame of a door or window opening of a building.
  • the drive system 1 comprises an actuator 3 intended to drive the winding shaft 5 in rotation in the form of a winding tube of the windable screen, and a compensation spring 7 transmitting to the winding 5 a torque delivered by actuator 3.
  • Frame 4 supports winding shaft 5.
  • a central axis X or reference axis of the drive system 1 is defined, which is a longitudinal axis of the winding shaft 5, of the actuator 3 and of the compensation 7 in assembled configuration.
  • the terms “axial” and “radial” are used with reference to this central axis X.
  • the actuator 3 is mounted at least partially inside the winding tube 5 and drives the latter in rotation via a connecting piece or drive wheel 34.
  • the winding tube 5 is mounted with the possibility of rotation in the frame 4 by means of bearings or bearings 42, 44.
  • the actuator 3 is also arranged along the central axis X. It comprises a casing or tubular casing 30, and housed in the tubular casing 30, a power supply assembly 24, comprising for example accumulators or power batteries 26, an electronic control unit 31, an electric motor 33, as well as a reduction gear and a brake (not shown).
  • the supply assembly 24 can be housed in a second tubular casing, connected to the tubular casing 30 in which the electric motor 33 is located.
  • the compensation spring 7, working in torsion around the central axis X is mounted around the tubular casing 30 and acts to return the screen 6 to a rolled-up position.
  • the electric motor 33 of the actuator 3 has a stator 37 fixed relative to the casing 30, and a rotor 38 driving, via the reducer, an output shaft 32.
  • the output shaft 32 drives the tube of winding 5 via the wheel 34 fixed in rotation on the output shaft 32 and on the winding tube 5.
  • the electronic control unit 31 ensures the operation of the electric motor 33 by connecting, according to the movement orders received, the power supply to the accumulators or batteries 26 and the electric motor 33.
  • the actuator 3 comprises a head 36, closing one end of the casing 30, and which projects outside of the winding tube 5.
  • the head 36 of the actuator enables the support of the actuator 3 on the frame 4 and consequently the support of the winding tube 5 at the level of a fixed part of the building.
  • the winding tube is supported on the frame at the end opposite the head 36 of the actuator on a shaft 40 of frame 4.
  • An attachment piece 11 is located on the tubular casing 30 and fixed in rotation and in translation with respect to the tubular casing 30.
  • the compensation spring 7 can be constituted in known manner by one or more elastic elements, such as torsion springs, positioned in series, to obtain the desired characteristics in terms of elongation and stiffness.
  • the compensation spring is shown on the figure 1 partially hidden by the tubular casing 30, to simplify the figure.
  • the compensation spring 7 is attached to fixing points of the drive system 1: on the one hand by a first end 73 to the attachment piece 11 integral with the casing 30 and on the other hand by a second end 74 to the drive wheel 34.
  • the second end 74 can be attached to output shaft 32.
  • the attachment piece 11 is fixed to the casing 30 in a non-rotating manner and non-movable in translation along the central axis X.
  • the first end 73 of the compensation spring 7 is therefore connected to a fixed part of the actuator 3 , through the attachment piece 11, while the second end 74 is connected to a rotating part of the actuator 3 or to the winding shaft 5.
  • the compensation spring 7 is shown unstretched and fixed only to the drive wheel 34 and not to the attachment part 11.
  • the compensation spring 7, represented schematically on the figures 2 and 3 can be constituted in known manner by one or more elastic elements, such as torsion springs, constituted by a spring wire wound in a helix. These torsion springs can be positioned in series, to obtain the desired characteristics in terms of elongation and stiffness.
  • L7 the length of the compensation spring 7 at rest, taken in the direction of the reference axis X.
  • L4 the length between the drive wheel 34 and the attachment piece 11 in the same direction. This length L4 substantially corresponds to the length of the compressed compensation spring 7.
  • L3 denotes the length of actuator 3 taken in the same direction. The lengths L7 and L4 are less than the length L3 and the compensation spring 7 does not substantially protrude beyond the ends of the actuator 3, which gives the actuator sub-assembly a compact and monolithic character, simplifying its handling and saving installation time.
  • the compensation spring 7 comprises a first series of turns 70, called contiguous turns, having at rest a first spacing E70 and at least a second series of turns 72, called non-contiguous turns, having at rest a second spacing E72 whose value is greater than the value of the first spacing E70.
  • the compensation spring 7 is a spring with contiguous turns at rest, which is stretched before being fixed between the two fixing points, so that its length L8 when it is positioned is greater than its length L7 at rest. All the turns are then not contiguous.
  • a rotation of the electric motor causes a rotation of the drive wheel 34 and a modification of the torque applied to the compensation spring 7, since its second end 74 rotates around the reference axis X with the drive wheel 34 while its first end 73 remains fixed relative to the tubular casing 30 of the actuator 3 which is itself fixed relative to the reference axis X.
  • the modification of the torque applied to the compensation spring 7 modifies its elongation, which has the effect of modifying the diameter of the turns and the spacing between the turns which constitute it, since the spacing between the two ends 73 and 74 of the compensation spring 7 is fixed.
  • the compensation spring 7 is stressed (that is to say that it winds up on itself), its length increases and when the stress is released, the length of the compensation spring 7 decreases.
  • the compensation spring 7, which is metallic, must be kept away from any metallic part. More particularly, contact with the winding tube 5, which is generally metallic, must be avoided.
  • the system 1 comprises at least one ring 9 interposed between two consecutive turns 70 and 71 of the compensation spring 7.
  • the ring 9 is made of plastic material, for example polyoxymethylene (POM) or other, which makes it possible to guarantee a reduced friction between turns 70 and 71.
  • POM polyoxymethylene
  • the rod 9 comprises a cylindrical outer wall 94 coming into contact with an internal surface 50 of the winding tube 5.
  • the rod 9 comprises a cylindrical internal wall 95 coming into contact with an external surface 302 of the tubular casing 30.
  • the rod 9 comprises also side walls 97 or 98 of concave shape, the radius of curvature of which is substantially equal to the radius of the wire constituting the compensation spring 7.
  • These rods 9 have an internal radius R95 less than a minimum internal radius R7 of the compensation spring 7 and therefore come into contact with the tubular casing 30 instead of the compensation spring 7.
  • the internal radius R95 can be between 90% and 99% of radius R7, or else be less than radius R7 by 0.1 to 1 mm.
  • the rod 9 always remains closer to the tubular casing 30 than the compensation spring 7, which avoids any contact between the compensation spring 7 and the tubular casing 30.
  • the rods 9 have an outer radius R94 greater than a maximum outer radius R8 of the turns of the compensation spring 7 and therefore come into contact with the winding tube 5 instead of the compensation spring 7.
  • the external radius R94 can be between 101% and 110% of the radius R8, or else be greater than the radius R8 by 0.1 to 1 mm.
  • the rod 9 always remains closer to the winding tube 5 than the compensation spring 7, which avoids any contact between the compensation spring 7 and the winding tube 5.
  • the rod 9 is formed by an unclosed ring, that is to say not forming a complete circumference around the axis X.
  • the rod 9 has two ends 91 and 92.
  • the circumferential length of the rods 9, that is to say taken around the central axis X, is greater than one revolution of the compensation spring 7 around the axis X, in order to guarantee continuous contact of the plastic material of the rods 9 with the winding tube 5.
  • the rod 9 In an assembled state between the turns 70 and 71, the rod 9 is mechanically constrained by the shape of the compensation spring 7 so that its diameter is reduced and its ends 91 and 92 are juxtaposed axially.
  • the external radius R8 and the internal radius R7 of the compensation spring 7 or the equivalent diameters also vary with the diameter of the turns of the compensation spring 7.
  • the number of rods 9 can vary according to the length of the compensation spring 7 and the axial position of the rods 9 is guaranteed by a slight axial preload force exerted on the compensation spring 7.
  • the system 1 comprises three rods 9 visible at the figure 4 .
  • a ring 9 as shown in figures 4 to 7 can easily be positioned between two contiguous turns 70 and 71 in the first embodiment.
  • a second and a third embodiment are shown in the figures 8 to 11 .
  • the elements common to the first embodiment bear the same references and operate in the same way.
  • the external 94 and internal 95 walls of the rod 9 have a respective width I94, I95, taken along the central axis X, preferably greater than the diameter D7 of the wire constituting the compensation spring 7, in particular greater than several times the diameter D7 spring wire.
  • the width I94 or I95 of the outer wall 94 and/or of the inner wall 95 is chosen to be greater than the maximum distance dM between two turns 70 and 71 plus the diameter D7.
  • only the internal wall 95, respectively external 94 can have a width greater than the diameter D7.
  • the inner inner wall 95, respectively outer 94 may have a width greater than the diameter D7 on each axial side of the rod 9 or on one side only.
  • the widths I94, I95 can be provided less than the diameter D7 at the ends 91, 92 intended to overlap.
  • the length of the rod 9 can be chosen such that the two ends 91 and 92 are distant from each other when the rod 9 is used with the minimum diameter of the turns, that is to say the place of the compensation spring 7 where the turns have the smallest diameter with respect to the central axis X. This makes it possible to prevent the outer 94 and/or inner 95 walls of a first end 91 from overlapping with the external 94 and/or internal 95 of a second end 92.
  • the rod 9 may comprise at least one means for attaching to a turn 71 on at least one of the side walls 97 or 98 of the rod 9.
  • This attachment means may for example take the form of a C-shaped clip , formed by two tabs 99, of complementary shape to the diameter D7et in which a turn 71 can be housed and remain maintained.
  • One or more attachment means can be provided on the circumferential length of the rod 9, ensuring that they are away from the ends 91 and 92 of the rod 9, to avoid overlapping.
  • the attachment means can be provided over the entire circumferential length of the rod 9 with the exception of the overlapping ends 91 and 92.
  • the attachment means can be provided over the entire circumferential length of the rod 9 in the case where the circumferential length of the rod 9 is chosen such that the two ends 91 and 92 are far from each other when the rod 9 is used with the minimum diameter of the turns and therefore do not overlap.
  • the rod 9 may comprise a concave surface 95a provided on the inner wall 95.
  • the concave surface 95a is adapted to receive a turn 70 of the compensation spring 7.
  • the concave surface 95a has a concavity oriented facing the tubular casing 30.
  • the concave surface 95a has convergent edges 99 forming the hooking means allowing the retention of the turn 70 integral with the rod 9.
  • the internal wall 95 is then not in contact with the tubular casing 30.
  • the side walls 97 and 98 may be planar axial surfaces.
  • the attachment means can be provided on only one of the side walls 97 and 98, while the second opposite side face does not include any axial projecting elements, as is visible on the figure 9 . Thus, the risks of overlapping are eliminated.
  • the ring 9 may have means for attaching a turn 70 on the side of the side wall 97 of the ring 9, and on the other side, a side wall 98 formed by a flat axial surface.
  • This flat axial surface serves as a support for a second turn 71 adjacent to turn 70.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Operating, Guiding And Securing Of Roll- Type Closing Members (AREA)
  • Flexible Shafts (AREA)
  • Springs (AREA)

Description

L'invention concerne un système d'entraînement d'un écran, en particulier d'un écran enroulable. L'invention concerne également une installation de fermeture, d'occultation ou de protection solaire comprenant un tel système d'entraînement.The invention relates to a system for driving a screen, in particular a roll-up screen. The invention also relates to a closing, screening or solar protection installation comprising such a drive system.

De manière classique, une installation de fermeture, d'occultation ou de protection solaire comprend un écran déplaçable entre deux positions dites de fin de course, en particulier un écran enroulable, tel qu'un un tablier souple, par exemple un tablier formé par des lames articulées entre elles dans le cas d'un volet roulant ou une toile de store. L'installation de fermeture comprend également un arbre d'enroulement, par exemple un tube d'enroulement sur lequel est fixé et s'enroule l'écran enroulable ou un arbre sur lequel s'enroule un cordon ou une lacette de l'écran. L'installation comprend également un système d'entraînement comprenant un actionneur comprenant un moteur électrique, l'actionneur entraînant l'arbre d'enroulement en rotation pour déployer ou replier l'écran. Celui-ci est donc déplacé en regard d'une ouverture afin d'obturer sélectivement celle-ci. Le poids de cet écran (poids du tablier lui-même ou poids d'une barre dite « barre de charge » lestée, destinée à faciliter la descente d'une toile, sous l'effet du poids combiné de la toile et de la barre de charge) exerce sur le système d'entraînement un couple variable, notamment en fonction de la position de cet écran.Conventionally, a closing, screening or solar protection installation comprises a screen that can be moved between two so-called end-of-travel positions, in particular a roll-up screen, such as a flexible apron, for example an apron formed by slats hinged together in the case of a rolling shutter or an awning fabric. The closure installation also comprises a winding shaft, for example a winding tube on which the roll-up screen is fixed and is rolled up, or a shaft on which a cord or lace of the screen is wound. The installation also comprises a drive system comprising an actuator comprising an electric motor, the actuator driving the winding shaft in rotation to deploy or fold the screen. The latter is therefore moved facing an opening in order to selectively close the latter. The weight of this screen (weight of the apron itself or weight of a bar called a weighted "load bar", intended to facilitate the descent of a canvas, under the effect of the combined weight of the canvas and the bar load) exerts a variable torque on the drive system, in particular depending on the position of this screen.

Dans une installation classique, le déroulement ou la descente de l'écran se faisant sous l'effet du poids de la partie déroulée de l'écran, la consommation électrique est minimale. En revanche, les efforts pour enrouler ou remonter l'écran sont conséquents et donc pénalisent la consommation électrique globale de l'installation.In a conventional installation, the unrolling or lowering of the screen taking place under the effect of the weight of the unrolled part of the screen, the electrical consumption is minimal. On the other hand, the efforts to roll up or raise the screen are substantial and therefore penalize the overall electrical consumption of the installation.

La présente invention a pour but de réaliser une installation de fermeture, d'occultation ou de protection solaire, tel que définie plus haut, dont la consommation électrique est faible, dans laquelle par exemple, l'actionneur est alimenté par une source de courant autonome, par exemple par des piles ou des batteries.The object of the present invention is to produce a closing, screening or solar protection installation, as defined above, whose electrical consumption is low, in which, for example, the actuator is powered by an independent current source. , for example by cells or batteries.

Il est connu dans l'art antérieur, pour diminuer la consommation électrique d'un système d'entraînement d'écran, d'utiliser des ressorts dits "de compensation" pour compenser au moins partiellement le couple variable créé par le tablier.It is known in the prior art, to reduce the electrical consumption of a screen drive system, to use so-called "compensation" springs to compensate at least partially for the variable torque created by the apron.

Un tel ressort de compensation permet de générer un couple entre une partie fixe de l'actionneur et l'arbre d'enroulement, ce ressort étant cinématiquement relié, par l'une de ses extrémités, avec une structure fixe et, par son autre extrémité, avec une partie mobile reliée à l'écran, en particulier reliée à l'arbre d'enroulement. Le ressort de compensation a pour but d'accompagner le motoréducteur formant l'actionneur pendant la remontée d'une toile ou d'un autre type d'écran. WO 03/083245 décrit un système d'entrainement comportant un tel ressort de compensation.Such a compensation spring makes it possible to generate a torque between a fixed part of the actuator and the winding shaft, this spring being kinematically connected, by one of its ends, with a fixed structure and, by its other end , with a movable part connected to the screen, in particular connected to the winding shaft. The purpose of the compensation spring is to accompany the gear motor forming the actuator during the rising from a canvas or other type of screen. WO 03/083245 describes a drive system comprising such a compensation spring.

Pour qu'une installation fonctionne correctement, il est nécessaire que l'effort de compensation exercé par le ressort soit adapté au couple développé par l'écran qui influe sur les moyens d'entraînement. Ce couple est fonction des paramètres relatifs au système d'entraînement de l'écran, par exemple le diamètre d'enroulement, les dimensions de l'écran, son poids spécifique et sa position par rapport à l'ouverture. Les paramètres du ressort de compensation, notamment la longueur de fil et/ou le nombre de spires, sont déterminés en fonction des paramètres paramètres relatifs au système d'entraînement de l'écran. De plus, pour permettre un meilleur équilibrage du système d'entraînement, des moyens de réglage de la contrainte initiale d'un ressort de compensation peuvent être prévus. Lors de l'installation du système d'entraînement, le moteur électrique lui-même peut servir pour précontraindre le ressort de compensation, afin de régler le point d'équilibre de l'écran. Ce point d'équilibre est préférentiellement prévu en un point différentié des positions de fin de course de l'écran, par exemple à mi-course de l'écran.For an installation to operate correctly, it is necessary for the compensation force exerted by the spring to be adapted to the torque developed by the screen which influences the drive means. This torque is a function of the parameters relating to the drive system of the screen, for example the winding diameter, the dimensions of the screen, its specific weight and its position relative to the opening. The parameters of the compensation spring, in particular the length of wire and/or the number of turns, are determined according to the parameter parameters relating to the drive system of the screen. In addition, to allow better balancing of the drive system, means for adjusting the initial stress of a compensation spring may be provided. When installing the drive system, the electric motor itself can be used to preload the compensating spring, to adjust the balance point of the screen. This point of balance is preferably provided at a point different from the end-of-stroke positions of the screen, for example halfway through the screen.

Au fur et à mesure que le ressort de compensation est mis sous contrainte, c'est-à-dire s'enroule sur lui-même et que son diamètre diminue, il s'allonge. Dans les systèmes connus, on prévoit donc à l'installation d'étirer le ressort afin de prévoir un espace suffisant pour sa configuration complètement enroulée. Dans ce cas, la longueur du ressort de compensation installé est supérieure à sa longueur au repos et les spires du ressort de compensation installé sont non jointives. Cette solution n'est pas entièrement satisfaisante car dans ce cas le ressort n'est pas maintenu, est instable et génère du bruit.As the compensation spring is put under stress, that is to say rolls up on itself and its diameter decreases, it lengthens. In the known systems, provision is therefore made for the installation to stretch the spring in order to provide sufficient space for its fully wound configuration. In this case, the length of the installed compensation spring is greater than its length at rest and the turns of the installed compensation spring are not contiguous. This solution is not entirely satisfactory because in this case the spring is not maintained, is unstable and generates noise.

En effet, en particulier dans la configuration où le ressort de compensation est installé autour de l'actionneur et à l'intérieur d'un tube d'enroulement, l'espace radial pour l'allongement ou le déplacement des spires par rapport à l'axe du tube d'enroulement est très limité. Un contact entre les spires du ressort et l'actionneur et/ou le tube d'enroulement génère du bruit en fonctionnement, ce qui est inacceptable.Indeed, in particular in the configuration where the compensation spring is installed around the actuator and inside a winding tube, the radial space for the elongation or the displacement of the turns with respect to the axis of the winding tube is very limited. Contact between the coils of the spring and the actuator and/or the winding tube generates noise in operation, which is unacceptable.

US 2012/000615 décrit un système d'entrainement pour un écran, qui comprend pour seule source de couple un ressort qui est isolé radialement d'un tube d'enroulement par un manchon en matière plastique. Cet art antérieur concerne les systèmes sans actionneur électrique et produit du bruit de part le contact des spires du ressort entre elles. US 2012/000615 describes a drive system for a screen, which comprises as sole source of torque a spring which is radially isolated from a winding tube by a plastic sleeve. This prior art relates to systems without an electric actuator and produces noise due to the contact of the coils of the spring with each other.

C'est à ces inconvénients qu'entend remédier l'invention en proposant un nouveau système d'entraînement permettant la réduction du bruit occasionné par le ressort malgré un espace limité pour son montage.It is these drawbacks that the invention intends to remedy by proposing a new drive system allowing the reduction of the noise caused by the spring despite a limited space for its assembly.

A cet effet l'invention concerne un système d'entraînement d'un écran, comprenant un actionneur destiné à entraîner en rotation un tube d'enroulement agissant sur l'écran, et un ressort de compensation, monté autour de l'actionneur et comprenant plusieurs spires formées par enroulement d'un fil. Ce système est caractérisé en ce qu'il comprend au moins un jonc en matière plastique interposé entre deux spires consécutives du ressort de compensation, et en ce qu'un rayon externe dudit au moins un jonc est supérieur à un rayon externe maximal du ressort de compensation.To this end, the invention relates to a system for driving a screen, comprising an actuator intended to drive in rotation a winding tube acting on the screen, and a compensation spring, mounted around the actuator and comprising several turns formed by winding a wire. This system is characterized in that it comprises at least one plastic rod interposed between two consecutive turns of the compensation spring, and in that an external radius of said at least one rod is greater than a maximum external radius of the compensation spring. compensation.

Grâce à l'invention, les joncs inter-spires en matière plastique évitent un contact métal/métal bruyant entre le ressort et le tube d'enroulement.Thanks to the invention, the plastic inter-turn rods avoid noisy metal/metal contact between the spring and the winding tube.

Selon des aspects avantageux mais non obligatoires de l'invention, un tel système d'entraînement peut incorporer une ou plusieurs des caractéristiques suivantes, prises selon tout combinaison techniquement admissible :

  • Le jonc comprend une paroi externe cylindrique venant en contact avec une surface interne du tube d'enroulement.
  • La largeur de la paroi externe est supérieure au diamètre du fil constituant le ressort de compensation, en particulier supérieure à plusieurs fois le diamètre du fil constituant le ressort de compensation.
  • Le jonc comprend une paroi interne cylindrique et un rayon interne du jonc est inférieur à un rayon interne minimal du ressort de compensation.
  • La largeur de la paroi interne est supérieure au diamètre du fil constituant le ressort de compensation, en particulier supérieure à plusieurs fois le diamètre du fil constituant le ressort de compensation.
  • Le jonc présente un moyen d'accroche à une spire.
  • Le jonc a une longueur circonférentielle supérieure à un tour de rotation du ressort de compensation autour d'un axe central du système d'entraînement.
  • Le système d'entraînement comprend plusieurs joncs interposés entre deux spires consécutives du ressort répartis à différents endroits du ressort le long de l'axe central.
  • Le ressort de compensation comprend une première série de spires, dites spires jointives, ayant au repos un premier écartement et au moins une deuxième série de spires, dites spires non jointives, ayant au repos un second écartement dont la valeur est supérieure à la valeur du premier écartement.
According to advantageous but not obligatory aspects of the invention, such a drive system can incorporate one or more of the following characteristics, taken according to any technically admissible combination:
  • The rod comprises a cylindrical outer wall coming into contact with an inner surface of the winding tube.
  • The width of the outer wall is greater than the diameter of the wire constituting the compensation spring, in particular greater than several times the diameter of the wire constituting the compensation spring.
  • The rod comprises a cylindrical internal wall and an internal radius of the rod is less than a minimum internal radius of the compensation spring.
  • The width of the internal wall is greater than the diameter of the wire constituting the compensation spring, in particular greater than several times the diameter of the wire constituting the compensation spring.
  • The rod has a means of attachment to a turn.
  • The ring has a circumferential length greater than one turn of rotation of the compensation spring around a central axis of the drive system.
  • The drive system comprises several rods interposed between two consecutive coils of the spring distributed at different locations of the spring along the central axis.
  • The compensation spring comprises a first series of turns, called contiguous turns, having at rest a first spacing and at least a second series of turns, called non-contiguous turns, having at rest a second spacing whose value is greater than the value of the first spacing.

L'invention concerne également une installation de fermeture, d'occultation ou de protection solaire comprenant un écran, un châssis, un tube d'enroulement et un système d'entraînement tel que mentionné ci-dessus.The invention also relates to a closing, screening or solar protection installation comprising a screen, a frame, a winding tube and a drive system as mentioned above.

L'invention sera mieux comprise et d'autres avantages de celle-ci apparaîtront plus clairement à la lumière de la description qui va suivre, faite à titre d'exemple non limitatif en référence aux dessins annexés dans lesquels :

  • La figure 1 est une vue schématique d'une installation de fermeture, d'occultation ou de protection solaire comprenant un système d'entraînement conforme à l'invention ;
  • La figure 2 est une vue latérale schématique d'un ressort de compensation du système d'entraînement de la figure 1 au repos ;
  • La figure 3 est une vue similaire à la figure 2, dans une configuration montée du ressort de compensation ;
  • La figure 4 est une vue partielle du ressort de compensation d'un système d'entraînement conforme à l'invention ;
  • Le figure 5 est une vue de côté, montrant un ressort et un jonc du système de la figure 1 ;
  • La figure 6 est une coupe longitudinale du système de la figure 1 selon un premier mode de réalisation ;
  • La figure 7 est une vue en perspective du jonc de la figure 5, dans une configuration non contrainte selon un premier mode de réalisation ;
  • La figure 8 est une vue en coupe longitudinale d'une partie d'un système d'entraînement conforme à un deuxième mode de réalisation ;
  • La figure 9 est une vue en coupe longitudinale d'une partie d'un système d'entraînement conforme à un troisième mode de réalisation ;
  • Les figures 10 et 11 sont des vues similaires à la figure 9 représentant des variantes du troisème mode de réalisation.
The invention will be better understood and other advantages thereof will appear more clearly in the light of the following description, given by way of non-limiting example with reference to the appended drawings in which:
  • The figure 1 is a schematic view of a closing, screening or solar protection installation comprising a drive system according to the invention;
  • The picture 2 is a schematic side view of a compensating spring of the drive system of the figure 1 at rest ;
  • The picture 3 is a view similar to the picture 2 , in a mounted configuration of the compensating spring;
  • The figure 4 is a partial view of the compensation spring of a drive system according to the invention;
  • the figure 5 is a side view, showing a spring and a ring of the system of the figure 1 ;
  • The figure 6 is a longitudinal section of the system of the figure 1 according to a first embodiment;
  • The figure 7 is a perspective view of the ring of the figure 5 , in an unconstrained configuration according to a first embodiment;
  • The figure 8 is a longitudinal sectional view of part of a drive system according to a second embodiment;
  • The figure 9 is a longitudinal sectional view of part of a drive system according to a third embodiment;
  • The figures 10 and 11 are views similar to the figure 9 representing variations of the third embodiment.

La figure 1 représente une installation de fermeture, d'occultation ou de protection solaire 200 comprenant un écran 6, un châssis 4, un arbre d'enroulement 5 et un système d'entraînement 1 de l'écran 6, notamment un écran enroulable, tel qu'un volet roulant, monté dans un encadrement d'une ouverture de porte ou de fenêtre d'un bâtiment. Le système d'entraînement 1 comprend un actionneur 3 destiné à entraîner en rotation l'arbre d'enroulement 5 sous forme d'un tube d'enroulement de l'écran enroulable, et un ressort de compensation 7 transmettant à l'arbre d'enroulement 5 un couple délivré par l'actionneur 3. Le châssis 4 supporte l'arbre d'enroulement 5.The figure 1 represents a closing, screening or solar protection installation 200 comprising a screen 6, a frame 4, a winding shaft 5 and a drive system 1 for the screen 6, in particular a roll-up screen, such as a roller shutter, mounted in a frame of a door or window opening of a building. The drive system 1 comprises an actuator 3 intended to drive the winding shaft 5 in rotation in the form of a winding tube of the windable screen, and a compensation spring 7 transmitting to the winding 5 a torque delivered by actuator 3. Frame 4 supports winding shaft 5.

On définit un axe central X ou axe de référence du système d'entraînement 1, qui est un axe longitudinal de l'arbre d'enroulement 5, de l'actionneur 3 et du ressort de compensation 7 en configuration assemblée. Dans ce qui suit, les termes « axial » et « radial » sont employés en référence à cet axe central X.A central axis X or reference axis of the drive system 1 is defined, which is a longitudinal axis of the winding shaft 5, of the actuator 3 and of the compensation 7 in assembled configuration. In what follows, the terms “axial” and “radial” are used with reference to this central axis X.

L'actionneur 3 est monté au moins partiellement à l'intérieur du tube d'enroulement 5 et entraîne celui-ci en rotation par l'intermédiaire d'une pièce de liaison ou roue d'entraînement 34. Le tube d'enroulement 5 est monté avec possibilité de rotation dans le châssis 4 par l'intermédiaire de paliers ou roulements 42, 44. L'actionneur 3 est disposé également le long de l'axe central X. Il comprend une enveloppe ou carter tubulaire 30, et logés dans le carter tubulaire 30, un ensemble d'alimentation 24, comprenant par exemple des accumulateurs ou des piles d'alimentation 26, une unité électronique de pilotage 31, un moteur électrique 33, ainsi qu'un réducteur et un frein (non représentés). Alternativement, l'ensemble d'alimentation 24 peut être logé dans un deuxième carter tubulaire, connecté au carter tubulaire 30 dans laquelle se trouve le moteur électrique 33. Le ressort de compensation 7, travaillant en torsion autour de l'axe central X, est monté autour du carter tubulaire 30 et agit pour ramener l'écran 6 vers une position enroulée.The actuator 3 is mounted at least partially inside the winding tube 5 and drives the latter in rotation via a connecting piece or drive wheel 34. The winding tube 5 is mounted with the possibility of rotation in the frame 4 by means of bearings or bearings 42, 44. The actuator 3 is also arranged along the central axis X. It comprises a casing or tubular casing 30, and housed in the tubular casing 30, a power supply assembly 24, comprising for example accumulators or power batteries 26, an electronic control unit 31, an electric motor 33, as well as a reduction gear and a brake (not shown). Alternatively, the supply assembly 24 can be housed in a second tubular casing, connected to the tubular casing 30 in which the electric motor 33 is located. The compensation spring 7, working in torsion around the central axis X, is mounted around the tubular casing 30 and acts to return the screen 6 to a rolled-up position.

Le moteur électrique 33 de l'actionneur 3 présente un stator 37 fixe par rapport au carter 30, et un rotor 38 entraînant, par l'intermédiaire du réducteur, un arbre de sortie 32. L'arbre de sortie 32 entraîne le tube d'enroulement 5 par l'intermédiaire de la roue 34 fixée en rotation sur l'arbre de sortie 32 et sur le tube d'enroulement 5. L'unité électronique de pilotage 31 assure le fonctionnement du moteur électrique 33 en mettant en relation, selon les ordres de déplacement reçus, l'alimentation électrique des accumulateurs ou piles 26 et le moteur électrique 33. Dans ce mode de réalisation, l'actionneur 3 comporte une tête 36, fermant une extrémité du carter 30, et qui fait saillie à l'extérieur du tube d'enroulement 5. La tête 36 de l'actionneur permet le support de l'actionneur 3 sur le châssis 4 et par conséquent le support du tube d'enroulement 5 au niveau d'une partie fixe du bâtiment. Elle permet de plus la reprise de couple en sortie d'actionneur. Elle peut être pourvue d'une trappe d'accès non représentée aux accumulateurs ou piles 26 contenues dans le carter tubulaire 30. Le tube d'enroulement est supporté sur le châssis à l'extrémité opposée à la tête 36 de l'actionneur sur un arbre 40 du châssis 4.The electric motor 33 of the actuator 3 has a stator 37 fixed relative to the casing 30, and a rotor 38 driving, via the reducer, an output shaft 32. The output shaft 32 drives the tube of winding 5 via the wheel 34 fixed in rotation on the output shaft 32 and on the winding tube 5. The electronic control unit 31 ensures the operation of the electric motor 33 by connecting, according to the movement orders received, the power supply to the accumulators or batteries 26 and the electric motor 33. In this embodiment, the actuator 3 comprises a head 36, closing one end of the casing 30, and which projects outside of the winding tube 5. The head 36 of the actuator enables the support of the actuator 3 on the frame 4 and consequently the support of the winding tube 5 at the level of a fixed part of the building. It also allows torque recovery at the actuator output. It may be provided with an access hatch, not shown, to the accumulators or batteries 26 contained in the tubular casing 30. The winding tube is supported on the frame at the end opposite the head 36 of the actuator on a shaft 40 of frame 4.

Une pièce d'accroche 11 est située sur le carter tubulaire 30 et fixée en rotation et en translation par rapport au carter tubulaire 30.An attachment piece 11 is located on the tubular casing 30 and fixed in rotation and in translation with respect to the tubular casing 30.

Le ressort de compensation 7 peut être constitué de façon connue par un ou plusieurs éléments élastiques, comme des ressorts de torsion, positionnés en série, pour obtenir les caractéristiques souhaitées en termes d'allongement et de raideur. Le ressort de compensation est représenté sur la figure 1 partiellement masqué par le carter tubulaire 30, pour simplifier la figure. Le ressort de compensation 7 est fixé à des points de fixation du système d'entraînement 1: d'une part par une première extrémité 73 à la pièce d'accroche 11 solidaire du carter 30 et d'autre part par une seconde extrémité 74 à la roue d'entraînement 34. En variante la deuxième extrémité 74 peut être fixée à l'arbre de sortie 32.The compensation spring 7 can be constituted in known manner by one or more elastic elements, such as torsion springs, positioned in series, to obtain the desired characteristics in terms of elongation and stiffness. The compensation spring is shown on the figure 1 partially hidden by the tubular casing 30, to simplify the figure. The compensation spring 7 is attached to fixing points of the drive system 1: on the one hand by a first end 73 to the attachment piece 11 integral with the casing 30 and on the other hand by a second end 74 to the drive wheel 34. Alternatively the second end 74 can be attached to output shaft 32.

La pièce d'accroche 11 est fixée sur le carter 30 de manière non rotative et non-mobile en translation selon l'axe central X. La première extrémité 73 du ressort de compensation 7 est donc reliée à une partie fixe de l'actionneur 3, par le biais de la pièce d'accroche 11, tandis que la seconde extrémité 74 est reliée à une partie rotative de l'actionneur 3 ou à l'arbre d'enroulement 5. Sur la figure 1, le ressort de compensation 7 est représenté non étiré et fixé uniquement à la roue d'entraînement 34 et non à la pièce d'accroche 11.The attachment piece 11 is fixed to the casing 30 in a non-rotating manner and non-movable in translation along the central axis X. The first end 73 of the compensation spring 7 is therefore connected to a fixed part of the actuator 3 , through the attachment piece 11, while the second end 74 is connected to a rotating part of the actuator 3 or to the winding shaft 5. On the figure 1 , the compensation spring 7 is shown unstretched and fixed only to the drive wheel 34 and not to the attachment part 11.

Le ressort de compensation 7, représenté de manière schématique sur les figures 2 et 3, peut être constitué de façon connue par un ou plusieurs éléments élastiques, comme des ressorts de torsion, constitués par un fil de ressort enroulé en hélice. Ces ressorts de torsion peuvent être positionnés en série, pour obtenir les caractéristiques souhaitées en termes d'allongement et de raideur.The compensation spring 7, represented schematically on the figures 2 and 3 , can be constituted in known manner by one or more elastic elements, such as torsion springs, constituted by a spring wire wound in a helix. These torsion springs can be positioned in series, to obtain the desired characteristics in terms of elongation and stiffness.

On note L7 la longueur du ressort de compensation 7 au repos, prise selon la direction de l'axe de référence X. On notre L4, la longueur entre la roue d'entraînement 34 et la pièce d'accroche 11 selon la même direction. Cette longueur L4 correspond sensiblement à la longueur du ressort de compensation 7 comprimé. On note L3 la longueur de l'actionneur 3 prise selon la même direction. Les longueurs L7 et L4 sont inférieures à la longueur L3 et le ressort de compensation 7 ne fait pas sensiblement saillie au-delà des extrémités de l'actionneur 3, ce qui confère au sous-ensemble actionneur un caractère compact et monolithique simplifiant sa manipulation et permettant es gains de temps en installation.We note L7 the length of the compensation spring 7 at rest, taken in the direction of the reference axis X. We denote L4, the length between the drive wheel 34 and the attachment piece 11 in the same direction. This length L4 substantially corresponds to the length of the compressed compensation spring 7. L3 denotes the length of actuator 3 taken in the same direction. The lengths L7 and L4 are less than the length L3 and the compensation spring 7 does not substantially protrude beyond the ends of the actuator 3, which gives the actuator sub-assembly a compact and monolithic character, simplifying its handling and saving installation time.

Selon un premier mode de réalisation, le ressort de compensation 7 comprend une première série de spires 70, dites spires jointives, ayant au repos un premier écartement E70 et au moins une deuxième série de spires 72, dites spires non jointives, ayant au repos un second écartement E72 dont la valeur est supérieure à la valeur du premier écartement E70.According to a first embodiment, the compensation spring 7 comprises a first series of turns 70, called contiguous turns, having at rest a first spacing E70 and at least a second series of turns 72, called non-contiguous turns, having at rest a second spacing E72 whose value is greater than the value of the first spacing E70.

Selon un deuxième mode de réalisation, le ressort de compensation 7 est un ressort à spires jointives au repos, qui est étiré avant d'être fixé entre les deux points de fixation, de sorte que sa longueur L8 lorsqu'il est positionné est supérieure à sa longueur L7 au repos. Toutes les spires sont alors non jointives.According to a second embodiment, the compensation spring 7 is a spring with contiguous turns at rest, which is stretched before being fixed between the two fixing points, so that its length L8 when it is positioned is greater than its length L7 at rest. All the turns are then not contiguous.

Lorsque le système d'entraînement 1 est en configuration de fonctionnement, une rotation du moteur électrique entraîne une rotation de la roue d'entraînement 34 et une modification du couple appliqué au ressort de compensation 7, puisque sa deuxième extrémité 74 tourne autour de l'axe de référence X avec la roue d'entrainement 34 alors que sa première extrémité 73 demeure fixe par rapport au carter tubulaire 30 de l'actionneur 3 qui est lui-même fixe par rapport à l'axe de référence X.When the drive system 1 is in the operating configuration, a rotation of the electric motor causes a rotation of the drive wheel 34 and a modification of the torque applied to the compensation spring 7, since its second end 74 rotates around the reference axis X with the drive wheel 34 while its first end 73 remains fixed relative to the tubular casing 30 of the actuator 3 which is itself fixed relative to the reference axis X.

La modification du couple appliqué au ressort de compensation 7 modifie son allongement, ce qui a pour effet une modification du diamètre des spires et de l'écartement entre les spires qui le constituent, vu que l'écartement entre les deux extrémités 73 et 74 du ressort de compensation 7 est fixe. En particulier, lorsque le ressort de compensation 7 est contraint (c'est-à-dire qu'il s'enroule sur lui-même), sa longueur augmente et lorsque la contrainte est relâchée, la longueur du ressort de compensation 7 diminue.The modification of the torque applied to the compensation spring 7 modifies its elongation, which has the effect of modifying the diameter of the turns and the spacing between the turns which constitute it, since the spacing between the two ends 73 and 74 of the compensation spring 7 is fixed. In particular, when the compensation spring 7 is stressed (that is to say that it winds up on itself), its length increases and when the stress is released, the length of the compensation spring 7 decreases.

Ces variations de longueur et donc de diamètre doivent être prises en compte lors du dimensionnement du ressort de compensation 7 pour que celui-ci soit adapté à l'installation 200 de fermeture, d'occultation ou de protection solaire.These variations in length and therefore in diameter must be taken into account when sizing the compensation spring 7 so that it is suitable for the installation 200 for closing, screening or solar protection.

Pour limiter l'impact bruit du système d'entraînement 1, le ressort de compensation 7, qui est métallique, doit être éloigné de toute partie métallique. Plus particulièrement, le contact avec le tube d'enroulement 5, généralement métallique, doit être évité.To limit the noise impact of the drive system 1, the compensation spring 7, which is metallic, must be kept away from any metallic part. More particularly, contact with the winding tube 5, which is generally metallic, must be avoided.

Pour cela, le système 1 comporte au moins un jonc 9 interposé entre deux spires 70 et 71 consécutives du ressort de compensation 7. Le jonc 9 est en matière plastique, par exemple en polyoxyméthylène (POM) ou autre, ce qui permet de garantir un frottement réduit entre les spires 70 et 71.For this, the system 1 comprises at least one ring 9 interposed between two consecutive turns 70 and 71 of the compensation spring 7. The ring 9 is made of plastic material, for example polyoxymethylene (POM) or other, which makes it possible to guarantee a reduced friction between turns 70 and 71.

Le jonc 9 comprend une paroi externe cylindrique 94 venant en contact avec une surface interne 50 du tube d'enroulement 5. Le jonc 9 comprend une paroi interne cylindrique 95 venant en contact avec une surface externe 302 du carter tubulaire 30. Le jonc 9 comprend également des parois latérales 97 ou 98 de forme concave, dont le rayon de courbure est sensiblement égal au rayon du fil constituant le ressort de compensation 7.The rod 9 comprises a cylindrical outer wall 94 coming into contact with an internal surface 50 of the winding tube 5. The rod 9 comprises a cylindrical internal wall 95 coming into contact with an external surface 302 of the tubular casing 30. The rod 9 comprises also side walls 97 or 98 of concave shape, the radius of curvature of which is substantially equal to the radius of the wire constituting the compensation spring 7.

Ces joncs 9 ont un rayon intérieur R95 inférieur à un rayon interne minimal R7 du ressort de compensation 7 et viennent donc contacter le carter tubulaire 30 à la place du ressort de compensation 7. A titre d'exemple, le rayon interne R95 peut être compris entre 90% et 99% du rayon R7, ou bien être inférieur au rayon R7 de 0,1 à 1 mm. Ainsi, le jonc 9 reste toujours plus proche du carter tubulaire 30 que le ressort de compensation 7, qui évite tout contact entre le ressort de compensation 7 et le carter tubulaire 30.These rods 9 have an internal radius R95 less than a minimum internal radius R7 of the compensation spring 7 and therefore come into contact with the tubular casing 30 instead of the compensation spring 7. By way of example, the internal radius R95 can be between 90% and 99% of radius R7, or else be less than radius R7 by 0.1 to 1 mm. Thus, the rod 9 always remains closer to the tubular casing 30 than the compensation spring 7, which avoids any contact between the compensation spring 7 and the tubular casing 30.

De la même manière, les joncs 9 ont un rayon externe R94 supérieur à un rayon exterme maximal R8 des spires du ressort de compensation 7 et viennent donc contacter le tube d'enroulement 5 à la place du ressort de compensation 7. A titre d'exemple, le rayon externe R94 peut être compris entre 101% et 110% du rayon R8, ou bien être supérieur au rayon R8 de 0,1 à 1 mm. Ainsi, le jonc 9 reste toujours plus proche du tube d'enroulement 5 que le ressort de compensation 7, qui évite tout contact entre le ressort de compensation 7 et le tube d'enroulement 5.In the same way, the rods 9 have an outer radius R94 greater than a maximum outer radius R8 of the turns of the compensation spring 7 and therefore come into contact with the winding tube 5 instead of the compensation spring 7. As a For example, the external radius R94 can be between 101% and 110% of the radius R8, or else be greater than the radius R8 by 0.1 to 1 mm. Thus, the rod 9 always remains closer to the winding tube 5 than the compensation spring 7, which avoids any contact between the compensation spring 7 and the winding tube 5.

Grâce au jonc 9, on provoque un contact plastique/métal entre le tube d'enroulement 5 et le jonc 9, ce qui ne produit qu'un bruit négligeable, et non un contact métal/métal entre le ressort de compensation 7 et le tube d'enroulement 5 beaucoup plus bruyant, d'autant plus important que les surfaces du jonc 9 et du tube d'enroulement 5 sont en déplacement relatif l'une par rapport à l'autre lors du fonctionnement de l'installation 200. De la même manière et pour les mêmes raisons, on provoque un contact plastique/métal entre le carter tubulaire 30 et le jonc 9. En outre, cette solution permet de garantir une compacité radiale satisfaisante, car il n'est pas nécessaire de prévoir un espace radial conséquent entre le tube 5 et le ressort de compensation 7, ni entre le carter tubulaire 30 et le ressort de compensation 7.Thanks to the rod 9, a plastic/metal contact is caused between the winding tube 5 and the rod 9, which produces only negligible noise, and not a metal/metal contact between the compensation spring 7 and the tube 5 winding much noisier, all the more important that the surfaces of the rod 9 and the winding tube 5 are in relative displacement relative to each other during operation of the installation 200. same way and for the same reasons, a plastic/metal contact is caused between the tubular casing 30 and the rod 9. In addition, this solution makes it possible to guarantee satisfactory radial compactness, since it is not necessary to provide a radial space consequent between the tube 5 and the compensation spring 7, nor between the tubular casing 30 and the compensation spring 7.

Le jonc 9 est formé par un anneau non fermé, c'est-à-dire ne formant pas une circonférence complète autour de l'axe X. Le jonc 9 présente deux extrémités 91 et 92.The rod 9 is formed by an unclosed ring, that is to say not forming a complete circumference around the axis X. The rod 9 has two ends 91 and 92.

La longueur circonférentielle des joncs 9, c'est-à-dire prise autour de l'axe central X, est supérieure à un tour de rotation du ressort de compensation 7 autour de l'axe X, afin de garantir un contact continu de la matière plastique des joncs 9 avec le tube d'enroulement 5. Cela se traduit par le fait que le jonc 9 présente deux extrémités 91 et 92 qui se juxtaposent. Dans un état libre du jonc 9 représenté à la figure 7, c'est-à-dire en l'absence de contrainte mécanique, les extrémités 91 et 92 ne sont pas juxtaposées. Dans un état assemblé entre les spires 70 et 71, le jonc 9 est contraint mécaniquement par la forme du ressort de compensation 7 de sorte que son diamètre est réduit et que ses extrémités 91 et 92 sont juxtaposées axialement. Ainsi, le rayon externe R8 et le rayon interne R7 du ressort de compensation 7 ou les diamètres équivalents, varient également avec le diamètre des spires du ressort de compensation 7.The circumferential length of the rods 9, that is to say taken around the central axis X, is greater than one revolution of the compensation spring 7 around the axis X, in order to guarantee continuous contact of the plastic material of the rods 9 with the winding tube 5. This results in the fact that the rod 9 has two ends 91 and 92 which are juxtaposed. In a free state of the rod 9 shown in figure 7 , that is to say in the absence of mechanical stress, the ends 91 and 92 are not juxtaposed. In an assembled state between the turns 70 and 71, the rod 9 is mechanically constrained by the shape of the compensation spring 7 so that its diameter is reduced and its ends 91 and 92 are juxtaposed axially. Thus, the external radius R8 and the internal radius R7 of the compensation spring 7 or the equivalent diameters also vary with the diameter of the turns of the compensation spring 7.

Le nombre de joncs 9 peut varier selon la longueur du ressort de compensation 7 et la position axiale des joncs 9 est garantie par un léger effort axial de précharge exercé sur le ressort de compensation 7. Dans le présent exemple, le système 1 comprend trois joncs 9 visibles à la figure 4.The number of rods 9 can vary according to the length of the compensation spring 7 and the axial position of the rods 9 is guaranteed by a slight axial preload force exerted on the compensation spring 7. In the present example, the system 1 comprises three rods 9 visible at the figure 4 .

Un jonc 9 tel que représenté aux figures 4 à 7 peut facilement être positionné entre deux spires jointives 70 et 71 dans le premier mode de réalisation.A ring 9 as shown in figures 4 to 7 can easily be positioned between two contiguous turns 70 and 71 in the first embodiment.

Un deuxième et un troisième mode de réalisation sont représentés sur les figures 8 à 11. Dans ces modes de réalisation, les éléments communs au premier mode de réalisation portent les mêmes références et fonctionnent de la même manière.A second and a third embodiment are shown in the figures 8 to 11 . In these embodiments, the elements common to the first embodiment bear the same references and operate in the same way.

Il est nécessaire de prévoir des moyens pour maintenir le jonc 9 positionné entre deux spires, y compris lorsque celles-ci sont éloignées l'une de l'autre.It is necessary to provide means for holding the rod 9 positioned between two turns, including when the latter are remote from each other.

Dans le deuxième mode de réalisation représenté sur la figure 8, les parois externes 94 et internes 95 du jonc 9 ont une largeur respective I94, I95, prise selon l'axe central X, de préférence supérieure au diamètre D7 du fil constituant le ressort de compensation 7, en particulier supérieure à plusieurs fois le diamètre D7 du fil de ressort. Autrement dit, on choisit la largeur I94 ou I95 de la paroi externe 94 et/ou de la paroi interne 95 supérieure à la distance maximale dM entre deux spires 70 et 71 additionné du diamètre D7. Ainsi, même dans le cas où le jonc 9 est installé entre deux spires 70 et 71 non jointives, il reste maintenu par au moins deux spires adjacentes 70 et 71 éloignées l'une de l'autre. Alternativement, de façon non représentée, seule la paroi interne 95, respectivement externe 94 peut avoir une largeur supérieure au diamètre D7. La paroi interne interne 95, respectivement externe 94 peut présenter une largeur supérieure au diamètre D7 de chaque côté axial du jonc 9 ou bien d'un seul côté.In the second embodiment shown in the figure 8 , the external 94 and internal 95 walls of the rod 9 have a respective width I94, I95, taken along the central axis X, preferably greater than the diameter D7 of the wire constituting the compensation spring 7, in particular greater than several times the diameter D7 spring wire. In other words, the width I94 or I95 of the outer wall 94 and/or of the inner wall 95 is chosen to be greater than the maximum distance dM between two turns 70 and 71 plus the diameter D7. Thus, even in the case where the rod 9 is installed between two non-contiguous turns 70 and 71, it remains held by at least two adjacent turns 70 and 71 remote from each other. Alternatively, in a manner not shown, only the internal wall 95, respectively external 94 can have a width greater than the diameter D7. The inner inner wall 95, respectively outer 94 may have a width greater than the diameter D7 on each axial side of the rod 9 or on one side only.

De façon non représentée, les largeurs I94, I95 peuvent être prévues inférieures au diamètre D7 au niveau des extrémités 91, 92 destinées à se chevaucher. Alternativement, la longueur du jonc 9 peut être choisie telle que les deux extrémités 91 et 92 sont éloignées l'une de l'autre lorsque le jonc 9 est utilisé avec le diamètre minimal des spires, c'est-à-dire l'endroit du ressort de compensation 7 où les spires ont le diamètre le plus faible par rapport à l'axe central X. Ceci permet d'éviter que les parois externe 94 et/ou interne 95 d'une première extrémité 91 ne se superposent avec les parois externe 94 et/ou interne 95 d'une deuxième extrémité 92.In a manner not shown, the widths I94, I95 can be provided less than the diameter D7 at the ends 91, 92 intended to overlap. Alternatively, the length of the rod 9 can be chosen such that the two ends 91 and 92 are distant from each other when the rod 9 is used with the minimum diameter of the turns, that is to say the place of the compensation spring 7 where the turns have the smallest diameter with respect to the central axis X. This makes it possible to prevent the outer 94 and/or inner 95 walls of a first end 91 from overlapping with the external 94 and/or internal 95 of a second end 92.

Selon un troisième mode de réalisation représenté à la figure 9, le jonc 9 peut comprendre au moins un moyen d'accroche à une spire 71 sur au moins une des parois latérales 97 ou 98 du jonc 9. Ce moyen d'accroche peut par exemple prendre la forme d'un clip en forme de C, formé par deux pattes 99, de forme complémentaire du diamètre D7et dans laquelle une spire 71 peut se loger et rester maintenue. Ainsi, même dans le cas où le jonc 9 est installé entre deux spires adjacentes 70 et 71 non jointives, il reste maintenu à une des deux spires adjacentes. Un ou plusieurs moyens d'accroche peuvent être prévus sur la longueur circonférentielle du jonc 9, en veillant à ce que ceux-ci soient éloignés des extrémités 91 et 92 du jonc 9, pour éviter un chevauchement.According to a third embodiment shown in figure 9 , the rod 9 may comprise at least one means for attaching to a turn 71 on at least one of the side walls 97 or 98 of the rod 9. This attachment means may for example take the form of a C-shaped clip , formed by two tabs 99, of complementary shape to the diameter D7et in which a turn 71 can be housed and remain maintained. Thus, even in the case where the rod 9 is installed between two adjacent turns 70 and 71 not contiguous, it remains held at one of the two adjacent turns. One or more attachment means can be provided on the circumferential length of the rod 9, ensuring that they are away from the ends 91 and 92 of the rod 9, to avoid overlapping.

Alternativement, en variante non représentée, le moyen d'accroche peut être prévu sur toute la longueur circonférentielle du jonc 9 à l'exception des extrémités 91 et 92 se chevauchant. Alternativement, le moyen d'accroche peut être prévu sur toute la longueur circonférentielle du jonc 9 dans le cas où la longueur circonférentielle du jonc 9 est choisie telle que les deux extrémités 91 et 92 sont éloignées l'une de l'autre lorsque le jonc 9 est utilisé avec le diamètre minimal des spires et donc ne se chevauchent pas.Alternatively, in a variant not shown, the attachment means can be provided over the entire circumferential length of the rod 9 with the exception of the overlapping ends 91 and 92. Alternatively, the attachment means can be provided over the entire circumferential length of the rod 9 in the case where the circumferential length of the rod 9 is chosen such that the two ends 91 and 92 are far from each other when the rod 9 is used with the minimum diameter of the turns and therefore do not overlap.

Comme représenté sur la figure 10, le jonc 9 peut comprendre une surface concave 95a prévue sur la paroi interne 95. La surface concave 95a est adaptée pour recevoir une spire 70 du ressort de compensation 7. La surface concave 95a présente une concavité orientée en regard du carter tubulaire 30. La surface concave 95a présente des bords convergents 99 fomant les moyens d'accroche permettant la retenue de la spire 70 solidaire du jonc 9. La paroi interne 95 n'est alors pas en contact avec le carter tubulaire 30. Dans ce cas de figure, les parois latérales 97 et 98 peuvent être des surfaces axiales planes.As shown on the figure 10 , the rod 9 may comprise a concave surface 95a provided on the inner wall 95. The concave surface 95a is adapted to receive a turn 70 of the compensation spring 7. The concave surface 95a has a concavity oriented facing the tubular casing 30. The concave surface 95a has convergent edges 99 forming the hooking means allowing the retention of the turn 70 integral with the rod 9. The internal wall 95 is then not in contact with the tubular casing 30. In this case, the side walls 97 and 98 may be planar axial surfaces.

Le moyen d'accroche peut être prévu sur une seule des parois latérales 97 et 98, tandis que la deuxième face latérale opposée ne comporte pas d'éléments en saillie axiale, comme cela est visible sur la figure 9. Ainsi, les risques de chevauchement sont éliminés.The attachment means can be provided on only one of the side walls 97 and 98, while the second opposite side face does not include any axial projecting elements, as is visible on the figure 9 . Thus, the risks of overlapping are eliminated.

Comme représenté sur la figure 11, le jonc 9 peut présenter des moyens d'accroche d'une spire 70 du côté de la paroi latérale 97 du jonc 9, et de l'autre côté, une paroi latérale 98 formée par une surface axiale plane. Cette surface plane axiale sert d'appui à une deuxième spire 71 adjacente à la spire 70.As shown on the figure 11 , the ring 9 may have means for attaching a turn 70 on the side of the side wall 97 of the ring 9, and on the other side, a side wall 98 formed by a flat axial surface. This flat axial surface serves as a support for a second turn 71 adjacent to turn 70.

Les caractéristiques techniques des modes de réalisation et variantes décrits ci-dessus, notamment les deuxième et troisième modes de réalisation, peuvent être combinés pour former de nouveaux modes de réalisation de l'invention.The technical characteristics of the embodiments and variants described above, in particular the second and third embodiments, can be combined to form new embodiments of the invention.

Claims (10)

  1. Drive system (1) for driving a screen (6), comprising an actuator (3) designed to drive in rotation a winding tube (5) acting on the screen (6), and a compensation spring (7), which is mounted around the actuator (3) and has several turns (70, 71, 72) formed by winding a wire, characterized in that the drive system (1) comprises at least one ring (9) made of plastic material that is placed between two adjacent tums (70, 71) of the compensation spring (7), and in that an external radius (R94) of said at least one ring (9) is greater than a maximum external radius (R8) of the compensation spring (7).
  2. Drive system according to claim 1, characterized in that said at least one ring (9) comprises a cylindrical external wall (94) that comes into contact with an internal surface (50) of the winding tube (5).
  3. Drive system according to claim 2, characterized in that the width of the external wall (94) is greater than the diameter (D7) of the wire that constitutes the compensation spring (7), in particular multiple times greater than the diameter (D7) of the wire that constitutes the compensation spring (7).
  4. Drive system according to one of the preceding claims, characterized in that said at least one ring (9) comprises a cylindrical internal wall (95) and in that an internal radius (R95) of said at least one ring (9) is less than a minimum internal radius (R7) of the compensation spring (7).
  5. Drive system according to claim 4, characterized in that the width of the internal wall (95) is greater than the diameter (D7) of the wire that constitutes the compensation spring (7), in particular multiple times greater than the diameter (D7) of the wire that constitutes the compensation spring (7).
  6. Drive system according to one of the preceding claims, characterized in that said at least one ring has an attachment means (99) for attaching to a turn (70, 71, 72).
  7. Drive system according to one of the preceding claims, characterized in that said at least one ring (9) has a circumferential length that is greater than one turn of rotation of the compensation spring (7) about a central axis (X) of the drive system (1).
  8. Drive system according to one of the preceding claims, characterized in that it comprises a plurality of rings (9) each of said plurality of rings being placed between two adjacent tums (70, 71) of the spring (7), said plurality of rings being distributed at different locations of the spring (7) along a central axis (X) of the drive system (1).
  9. A drive system according to one of the preceding claims, characterized in that the compensation spring (7) comprises a first series of turns (70), referred to as contiguous turns, which have at rest a first spacing (E70), and at least one second series of turns (72), referred to as non-contiguous turns, which have at rest a second spacing (E72) with a value that is greater than the value of the first spacing (E70).
  10. A closure, screening, or solar protection system installation (200) that comprises a screen (6), a frame (4), a winding tube (5), and a drive system (1) according to one of the preceding claims.
EP19736732.9A 2018-07-11 2019-07-10 Drive system driving a screen, and apparatus comprising such a system Active EP3821103B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1856379A FR3083817B1 (en) 2018-07-11 2018-07-11 SYSTEM FOR DRIVING A SCREEN AND INSTALLATION INCLUDING SUCH A SYSTEM
PCT/EP2019/068507 WO2020011841A1 (en) 2018-07-11 2019-07-10 Drive system driving a screen, and apparatus comprising such a system

Publications (2)

Publication Number Publication Date
EP3821103A1 EP3821103A1 (en) 2021-05-19
EP3821103B1 true EP3821103B1 (en) 2022-11-30

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Application Number Title Priority Date Filing Date
EP19736732.9A Active EP3821103B1 (en) 2018-07-11 2019-07-10 Drive system driving a screen, and apparatus comprising such a system

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US (1) US11230884B2 (en)
EP (1) EP3821103B1 (en)
FR (1) FR3083817B1 (en)
WO (1) WO2020011841A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11988040B2 (en) * 2018-01-16 2024-05-21 Crestron Electronics, Inc. System and method for reducing friction in a counterbalancing spring of a roller shade

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US799075A (en) * 1905-01-31 1905-09-12 Kinnear Mfg Co Roller for fire-resisting curtains.
US1561551A (en) * 1922-06-19 1925-11-17 Atlee J Lewis Spring roller for sun visors
US1641506A (en) * 1923-11-14 1927-09-06 Hugo A Huelse Fire door
US2765843A (en) * 1954-04-05 1956-10-09 Andrew G Nilles Truck cover
US4429729A (en) * 1982-07-09 1984-02-07 Clopay Corporation Window shade clutch assembly
IT1234071B (en) * 1989-05-12 1992-04-29 Sunproject Srl PERFECTED DEVICE WITH ROLLER ROLLER FOR CURTAIN TYPE
US5419010A (en) * 1993-05-03 1995-05-30 Wayne-Dalton Corp. Compact counterbalancing system for sectional doors
EP0821130B1 (en) * 1996-07-23 2001-12-19 P.E.I. Protezioni Elaborazioni Industriali S.r.l. A roller for rewinding and tensioning a flexible element such as a sheet of material,shutter or similar,in particular for protection on machines
ES2152135B1 (en) * 1997-10-14 2001-10-16 Box Control S L PERFECTED DEVICE FOR AUTOMATIC BAND WINDING.
FR2837865B1 (en) * 2002-03-28 2005-07-29 Simu MANUFACTURING MECHANISM AND CLOSURE OR SOLAR PROTECTION INSTALLATION INCORPORATING SUCH A DEVICE
DE102005033275B4 (en) * 2005-07-15 2009-09-10 Webasto Ag Winding shaft for a roller blind device
DE102006046440B3 (en) * 2006-09-25 2008-04-24 Bos Gmbh & Co. Kg The blind assembly
TW201215760A (en) * 2010-07-05 2012-04-16 Macauto Ind Co Ltd Sunshade curtain
SE535383C2 (en) * 2010-11-10 2012-07-17 Markisol Holding Ab Device for biasing a reeling mechanism

Also Published As

Publication number Publication date
US11230884B2 (en) 2022-01-25
EP3821103A1 (en) 2021-05-19
FR3083817A1 (en) 2020-01-17
FR3083817B1 (en) 2020-10-09
US20210246723A1 (en) 2021-08-12
WO2020011841A1 (en) 2020-01-16

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