(19)
(11)EP 3 736 403 B1

(12)EUROPEAN PATENT SPECIFICATION

(45)Mention of the grant of the patent:
08.11.2023 Bulletin 2023/45

(21)Application number: 20173555.2

(22)Date of filing:  07.05.2020
(51)International Patent Classification (IPC): 
E05F 15/611(2015.01)
E05F 15/63(2015.01)
E05F 15/635(2015.01)
E05F 3/22(2006.01)
E05F 1/16(2006.01)
E05F 15/619(2015.01)
E05F 15/632(2015.01)
E05F 15/649(2015.01)
E05F 1/10(2006.01)
(52)Cooperative Patent Classification (CPC):
E05F 15/611; E05F 15/63; E05F 15/619; E05F 15/632; E05F 15/649; E05F 15/635; E05Y 2201/71; E05Y 2201/716; E05Y 2201/712; E05Y 2201/618; E05Y 2900/132; E05Y 2900/40; E05F 1/10; E05F 1/1041; E05F 1/16; E05F 3/224

(54)

MOTOR-DRIVEN ACTUATOR AND DISPLACEABLE BARRIER PROVIDED WITH SUCH ACTUATOR, PARTICULARLY SUITABLE FOR AUXILIARY OR EMERGENCY DRIVES

MOTORBETRIEBENES BETÄTIGUNGSELEMENT UND MIT EINEM SOLCHEN BETÄTIGUNGSELEMENT VERSEHENE VERSCHIEBBARE BARRIERE, INSBESONDERE GEEIGNET FÜR HILFS- ODER NOTANTRIEBE

ACTIONNEUR MOTORISÉ ET BARRIÈRE DÉPLAÇABLE MUNIE D'UN TEL ACTIONNEUR, PARTICULIÈREMENT ADAPTÉ AUX ENTRAÎNEMENTS AUXILIAIRES OU DE SECOURS


(84)Designated Contracting States:
AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

(30)Priority: 10.05.2019 IT 201900006733

(43)Date of publication of application:
11.11.2020 Bulletin 2020/46

(73)Proprietor: FAAC S.p.A.
40069 Zola Predosa (BO) (IT)

(72)Inventors:
  • ACETO, Danilo
    40069 Zola Predosa (BO) (IT)
  • MAGNONI, Samuele
    40132 Bologna (IT)

(74)Representative: Bonatto, Marco et al
Barzanò & Zanardo Milano S.p.A. Via Borgonuovo, 10
20121 Milano
20121 Milano (IT)


(56)References cited: : 
EP-A1- 2 933 415
WO-A1-2015/058035
WO-A1-2012/010111
US-A1- 2016 033 024
  
      
    Note: Within nine months from the publication of the mention of the grant of the European patent, any person may give notice to the European Patent Office of opposition to the European patent granted. Notice of opposition shall be filed in a written reasoned statement. It shall not be deemed to have been filed until the opposition fee has been paid. (Art. 99(1) European Patent Convention).


    Description

    Field of the invention



    [0001] The present invention relates to a motorized drive for movable barriers such as doors, main doors, gates, swing shutters, sliding walls or partitions, and a movable barrier comprising said motorized drive.

    [0002] Said drive is particularly suitable for use as an auxiliary or emergency actuator.

    Background art



    [0003] The wings of the common doors and main doors generally open by rotating about 90° or slightly more, requiring a variable torque from the possible actuator that operates them.

    [0004] Generally said actuator comprises a rotary electric motor and a speed reduction unit generally comprising one or more circular wheel gears and/or worm screw systems.

    [0005] Said rotary electric motor generally acts as the main motor: under conditions of normal operation said doors, main doors or, more generally, movable barriers are operated by said electric motor.

    [0006] In the initial and final phases of the opening or closing movement, i.e. acceleration and deceleration, the wing requires relatively high torques and low rotation speeds from the motor of the actuator.

    [0007] On the other hand, in the intermediate phase of the movement the torque that the motor must deliver is almost zero, only having to overcome the frictions present in the rotating pairs of the wings, while the rotation speed is high.

    [0008] Currently said composite actuations comprising accelerations, decelerations and zero acceleration phases are carried out exclusively by piloting the electric motor of the actuator, in order to obtain the desired speed trend of the wing despite the different torque requirements, or with kinematic systems downstream of the electric motor.

    [0009] The authors of the present invention have found that it would be desirable to make the resistant torque which the motor must overcome and the speed which it must reach at the various positions of the wing or in any case at the various instants of the drives more uniform: this would allow at least to adopt motors with lower rated power as well as kinematic systems with lower gear ratios downstream of the electric motor, all with the same weight and inertia of the wing to be operated, and of the frictions to be overcome.

    [0010] In some applications, for example when a door or other movable barrier must be kept normally closed/opened respectively and must be respectively opened/closed only under particular conditions - for example it must be opened only to allow a person, a vehicle or other object to pass through and then closed, think for example of some doors of some hospital wards - it is desired to equip said movable barriers also with an auxiliary motor capable of closing/reopening respectively said movable barriers even under conditions of failure or lack of power supply of the main electric motor.

    [0011] As an auxiliary motor, it is possible to think of adopting a spring, for example metallic, which however typically applies to the speed reducer of the actuator a strongly variable force or torque depending on the degree of compression and the spring itself.

    [0012] Typically an ordinary spring, for example a compression spring, applies to the speed reducer a very high driving force or torque at the beginning of the closing or opening movement, and very low if not zero towards the end of said movement.

    [0013] Therefore the wing or other movable barrier generally starts -or tends to start- its emergency closing or opening with a too abrupt and energetic movement, in some cases even dangerous for people and things nearby, and ends it weakly and slowly with a weak push, sometimes even without being able to finish it.

    [0014] The emergency closing or opening movement is initially all the more abrupt the greater the elastic energy it is desired to store in the spring, which is generally the greater, the greater the weight and inertia of the wing or other movable barrier to operate.

    [0015] In addition, the greater the elastic energy to be stored in the spring, the greater the torque that the main motor - for example electric - of the actuator must apply to compress the spring and therefore the greater the size and the rated power of the main motor.

    [0016] The publication EP2933415A1 discloses a door drive comprising an electric motor and an auxiliary spring motor.

    [0017] The auxiliary spring motor comprises a rack and pinion system; in order to optimize the torque produced by the metal spring the pinion toothing has an approximately spiral shape instead of a circular shape.

    [0018] The publication US2016/0033024A1 discloses a further motorized door drive provided with a pair of non-circular gears driven by a metal spring.

    [0019] The two non-circular gears have spiral-shape toothinga and rotate about respective shafts.

    [0020] The publication WO2015/058035A1 discloses a further motorized door drive provided with a spring motor and a rack and pinion mechanism; the pinion toothing has a non-circular shape.

    [0021] The publication WO2012/010111A1 discloses a damping unit for doors or turnstiles provided with a gas spring driving, or driven by, a pair of non-circular gears.

    [0022] The authors of the present invention have found that it would be desirable to make the resistant torque that the auxiliary motor of an actuator of a wing of a main door, partition or other movable barrier must overcome to open or close the movable barrier and compress the spring more uniform: this would allow at least to adopt auxiliary and main motors of lower rated power as well as kinematic systems with lower reduction ratios downstream of the electric motor, all with the same weight and inertia of the wing to be operated, and of the frictions to be overcome.

    [0023] An object of the present invention is therefore to obviate the above mentioned drawbacks and in particular to provide a drive to open and/or close for example a wing of a door, gate, main door or swing shutter or still wall or sliding partition, wherein the resistant torque applied by the wing required from the motor - for example from the auxiliary motor - of the drive during the closing and/or opening movements to open and/or close the wing and to compress the spring is more uniform than the one applied by existing drives.

    Summary of the invention



    [0024] Said purpose is achieved, according to a first aspect of the present invention, with a motorized drive having the features according to claim 1.

    [0025] In a motorized drive according to a particular embodiment of the invention, the first (11, 11', 11") and/or the second toothed profile (13, 13', 13") has a pitch profile whose shape is chosen from the following group: elliptic shape, elliptical arc shape, parabolic shape, hyperbolic shape, oval shape, curvilinear and oblong shape, lobed shape with one or more lobes, polynomial, sinusoidal and logarithmic shape.

    [0026] In a motorized drive according to a particular embodiment of the invention, the second toothed profile (13, 13', 13") comprises a section whose pitch profile has been obtained by imposing the tangency without sliding on the pitch profile of the first toothed profile (11, 11', 11").

    [0027] In a motorized drive according to a particular embodiment of the invention, first toothed profile (11') is delimited by a first and a second end, the first (11') and the second (13') toothed profile engage in at least one point of mutual contact (PCN) and have shapes such that the radius (RP1') of the first toothed profile aligned with said mutual contact point (PCN) progressively increases as the point of mutual contact (PCN) moves towards said first or second end.

    [0028] In a motorized drive according to a particular embodiment of the invention, the radius (RP1') of the first toothed profile (11') reaches its minimum value at the first end of the first toothed profile (11').

    [0029] In a motorized drive according to a particular embodiment of the invention, the radius (RP1') of the first toothed profile (11') reaches its maximum value at the second end of the first toothed profile (11').

    [0030] In a motorized drive according to a particular embodiment of the invention, the auxiliary motor (7') is driven by the release force of a spring (19) or of another elastic element, and the spring (19) or other elastic element are configured to operate the second toothed profile (13') for example by pushing it or pulling it longitudinally to itself.

    [0031] In a particular embodiment of the invention, such motorized drive comprises a preload adjustment system (24) configured to adjust the preload force of the spring or another elastic element (19).

    [0032] In a motorized drive according to a particular embodiment of the invention, the preload adjustment system (24) comprises a guide pin (15) configured to be rotated on itself so as to adjust the preload force of the spring or another elastic element (19).

    [0033] In a particular embodiment of the invention, said motorized drive comprises a motor driven by the release force of a spring or other elastic element, and the spring or other elastic element are configured to operate the second toothed profile 13' for example by pushing it or pulling it longitudinally to itself.

    [0034] In a second aspect of the invention, this object is achieved with a movable barrier having the features according to claim 14.

    [0035] The dependent claims are directed to further features of the invention.

    [0036] The advantages attainable with the present invention shall become more readily apparent, to the person skilled in the art, by the following detailed description of a particular, non-limiting embodiment, shown with reference to the following schematic figures.

    List of Figures



    [0037] 

    Figure 1 shows a side view of a motorized drive according to a first particular embodiment of the invention;

    Figure 2 shows a perspective view of a door connected by an articulated arm to the motorized drive of Figure 1, in which the door is closed;

    Figure 3 shows a top view of the open door of Figure 2;

    Figure 4 shows a first top view of a door connected by a sliding arm to the motorized drive of Figure 1 according to a second particular embodiment of the invention, in which the door is closed;

    Figure 5 a second top view of the door of Figure 4, in which the door is open;

    Figure 6 shows the pitch profiles of the main drive of the motorized drive of Figure 1;

    Figure 7 shows the pitch profiles of the auxiliary drive of the motorized drive of Figure 1;

    Figure 8 shows the toothed profiles of the gear with a variable transmission ratio of the main drive of the motorized drive of Figure 1, in the position in which the door is completely closed, observing the toothed profiles according to a direction parallel to their rotation axes;

    Figure 9 shows the toothed profiles of the gear with a variable transmission ratio of the auxiliary drive of the motorized drive of Figure 1, in the position in which the door is completely closed and observing the toothed profiles according to a direction parallel to the rotation axis of the first tooth profile;

    Figure 10 shows the toothed profiles of Figure 8, in a position in which the door is partially open;

    Figure 11 shows the toothed profiles of Figure 9, in a position in which the door is partially open;

    Figure 12 shows the toothed profiles of Figure 8, in a position in which the door is completely open;

    Figure 13 shows the toothed profiles of Figure 9, in a position in which the door is completely open;

    Figure 14 shows a graph indicative of the reduction ratio of a kinematic mechanism with articulated arm of a known type, for operating wings of doors and main doors with an electric motor;

    Figure 15 shows a graph indicative of the reduction ratio of the reduction unit of Figures 6, 8, 10, 12 or of Figures 19-22;

    Figure 16 shows a side view of a motorized drive according to a third particular embodiment of the invention;

    Figure 16A shows an enlarged detail of Figure 16;

    Figure 17 shows a top view of an open door and connected through an articulated arm to the motorized drive of Figure 16;

    Figure 18 shows a first top view of a door connected through a sliding arm to the motorized drive of Figure 17 according to a fourth particular embodiment of the invention, in which the door is closed;

    Figure 19 shows a second top view of the door of Figure 18, in which the door is open;

    Figure 20 shows the toothed profiles of the gear with a variable transmission ratio of the main drive of the motorized drive of Figure 16, in the position in which the door is completely closed or at the maximum of its closing, observing the toothed profiles according to a direction parallel to their rotation axes;

    Figure 20A shows a first enlarged view of Figure 20, with a detail of the first stop tooth of the second toothed profile;

    Figure 20B shows a second enlarged view of Figure 20, with a detail of the second stop tooth of the second toothed profile;

    Figure 20C shows an enlarged view of Figure 20B, with a detail of the second stop tooth of the second toothed profile; Figure 21 shows the toothed profiles of Figure 20, in a position in which the door is partially open;

    Figure 22 shows the toothed profiles of Figure 20, in a position in which the door is completely open or at its maximum opening.

    Figure 23 shows a graph indicative of the reduction ratio of the reduction unit of Figures 7, 9, 11, 13 or 19-22.


    Detailed description



    [0038] Figures 1-3, 6-15 relate to a barrier and to the relative drive according to a first particular embodiment, indicated with the overall reference 1.

    [0039] As shown in Figure 2-5, 17-19 said barrier 1, 1', 1", 1III can be for example a door, such as a door inside a building or that separates the inside from the outside but, in other embodiments not shown, it can be for example a main door, a gate, porthole, a swing shutter for example of a garage, a sliding wall or partition or other sliding wing.

    [0040] In the present description, a door, gate or main door refer to barriers comprising one or two wings which can be reversibly opened and closed by rotating each one around a relative rotation axis substantially vertical or in any case inclined less than 45° with respect to the vertical.

    [0041] In the present description, swing shutter means a barrier comprising one or two wings which can be reversibly opened and closed by rotating each one around a relative rotation axis substantially horizontal or in any case inclined less than 45° with respect to a horizontal plane.

    [0042] A porthole can be opened or closed by rotating around a horizontal, vertical axis or having any angle with respect to a horizontal plane.

    [0043] Each barrier 1, 1', 1", 1III comprises a wing 3 and a motorized drive 5, 5" configured to open and/or close the relative wing 3.

    [0044] Like for example shown in Figures 2-5, 17-19 the wing 3 can reversibly close a space 2 delimited by a frame 4, which can for example be fixed to the wall of a building.

    [0045] The motorized drive 5, 5" can for example be fixed to the frame 4 or directly to the wall of said building.

    [0046] In other embodiments not shown the motorized drive 5, 5" can for example be fixed to the wing 3.

    [0047] According to the invention, the motorized drive 5, 5" comprises:
    • an electric motor 7;
    • a first reduction unit 9, 9" through which the motor 7 can operate the wing 3 by opening and closing it reversibly.


    [0048] According to the invention, the motorized drive 5, 5" also comprises a second reduction unit 9' through which the auxiliary motor 7' can operate the closure of the wing 3.

    [0049] Preferably, the auxiliary motor 7' comprises a helical spring 19 and is driven by it.

    [0050] "Motor" in the present description does not refer only to an electric or internal combustion motor but also other devices capable of providing mechanical power, such as for example the elastic energy motor 7' shown in Figures 9, 11, 13.

    [0051] Accotrding to the invention, and like in the embodiment of Figure 1, 16 the motor 7 is electric.

    [0052] The motor 7 preferably acts as a main motor.

    [0053] The elastic energy auxiliary motor 7' is preferably configured to absorb mechanical energy during the opening of the wing 3 and release it during the closing thereof.

    [0054] The auxiliary motor 7' can be connected to the wing 3 through the second reduction unit 9'.

    [0055] The reduction unit 9; 9" comprises a first toothed profile 11; 11" and a second toothed profile 13; 13" which engage together between them forming a gear with a variable transmission ratio depending on the angular and/or linear position of at least one of the two toothed profiles 11, 13; 11", 13".

    [0056] At least one of the first 11; 11'; 11" and the second toothed profile 13; 13'; 13" forms at least one toothed section having a pitch profile CPR1, CPR2; CPR1", CPR2" substantially different from a full circumference, from a single arched circle and not even straight.

    [0057] Like for example in the embodiments of the accompanying figures, the first 11, 11', 11" and the second toothed profile 13, 13', 13" can be toothings of cylindrical gears with straight teeth, but in other embodiments not shown they can also be toothings with helical and/or conical teeth.

    [0058] The first 11; 11" and the second toothed profile 13; 13" are mounted on suitable shafts, not shown, and configured to rotate around respective axes AX11, AX13.

    [0059] The two axes AX11, AX13 are preferably parallel to each other and arranged at a fixed distance from each other.

    [0060] The distance between the respective rotation axes AX11, AX13 and a point of the pitch curve CPR11, CPR13 respectively of the toothing 11, 13; 11", 13" in question in the present description is considered as the radius RP1, RP2 of the toothing associated with that point and the angular position α11, α13 of that point with respect to the respective axis AX11 or AX13.

    [0061] Preferably the first toothed profile 11; 11" advantageously has a pitch profile as a whole closed on itself so as to allow the profile 11; 11" to describe full rotations rotating on itself when engaged with another toothed profile ( Figures 1, 6, 7; 20-22).

    [0062] Like in the embodiments of Figures 1, 6, 8; 20-22 the first toothed profile 11; 11" advantageously has a pitch profile whose shape is approximated by points from the following table 11A or 11B or 11E; the points are defined by the polar coordinates α11, RP1, where the angle α11 can be for example referred to the possible axis of symmetry AXS11 of the toothed profile 11, 11"; like for example in the embodiments of Figures 1, 6, 8; 20-22 the axis of symmetry AXS11 passes through the rotation axis AX11 and through the point where the radius RP1 is minimum.
    -Table 11A-
    PointAngle α11 [degrees]Radius RP1 Minimum values 2 [mm]Radius RP1 Maximum values 2 [mm]Radius RP1 Minimum values 1Radius RP1 Maximum values 1 [mm]
    1 0 13.94592 20.91888 12.20268 22.66212
    3 20 14.62896 21.94344 12.80034 23.77206
    5 40 16.08328 24.12492 14.07287 26.13533
    7 60 17.62376 26.43564 15.42079 28.63861
    9 80 18.87952 28.31928 16.51958 30.67922
    11 100 19.71208 29.56812 17.24807 32.03213
    13 120 20.12744 30.19116 17.61151 32.70709
    15 140 20.73872 31.10808 18.14638 33.70042
    17 160 20.23528 30.35292 17.70587 32.88233
    19 180 20.23528 30.35292 17.70587 32.88233
    21 200 20.23528 30.35292 17.70587 32.88233
    23 220 20.73872 31.10808 18.14638 33.70042
    25 240 20.12744 30.19116 17.61151 32.70709
    27 260 19.71208 29.56812 17.24807 32.03213
    29 280 18.87952 28.31928 16.51958 30.67922
    31 300 17.62376 26.43564 15.42079 28.63861
    33 320 16.08328 24.12492 14.07287 26.13533
    35 340 14.62896 21.94344 12.80034 23.77206
    37 360 13.94592 20.91888 12.20268 22.66212
    -Table 11B-
    PointAngle α11 [degrees]Radius RP1 Values 5 [mm]Radius RP1 Minimum values 4Radius RP1 Maximum values 4 [mm]Radius RP1 Minimum values 3Radius RP1 Maximum values 3 [mm]
    1 0 17.4324 16.56078 18.30402 15.68916 19.17564
    3 20 18.2862 17.37189 19.20051 16.45758 20.11482
    5 40 20.1041 19.098895 21.109305 18.09369 22.11451
    7 60 22.0297 20.928215 23.131185 19.82673 24.23267
    9 80 23.5994 22.41943 24.77937 21.23946 25.95934
    11 100 24.6401 23.408095 25.872105 22.17609 27.10411
    13 120 25.1593 23.901335 26.417265 22.64337 27.67523
    15 140 25.9234 24.62723 27.21957 23.33106 28.51574
    17 160 25.2941 24.029395 26.558805 22.76469 27.82351
    19 180 25.2941 24.029395 26.558805 22.76469 27.82351
    21 200 25.2941 24.029395 26.558805 22.76469 27.82351
    23 220 25.9234 24.62723 27.21957 23.33106 28.51574
    25 240 25.1593 23.901335 26.417265 22.64337 27.67523
    27 260 24.6401 23.408095 25.872105 22.17609 27.10411
    29 280 23.5994 22.41943 24.77937 21.23946 25.95934
    31 300 22.0297 20.928215 23.131185 19.82673 24.23267
    33 320 20.1041 19.098895 21.109305 18.09369 22.11451
    35 340 18.2862 17.37189 19.20051 16.45758 20.11482
    37 360 17.4324 16.56078 18.30402 15.68916 19.17564
    -Table 11E-
    PointAngle α11 [degrees]Radius RP1 Values 6 [mm]Radius RP1 Minimum values 6
    1 0 17.00 17.87
    2 10 17.23 18.11
    3 20 17.83 18.74
    4 30 18.66 19.62
    5 40 19.60 20.61
    6 50 20.56 21.62
    7 60 21.48 22.58
    8 70 22.30 23.45
    9 80 23.01 24.19
    10 90 23.58 24.79
    11 100 24.02 25.26
    12 110 24.34 25.58
    13 120 24.53 25.79
    14 130 24.63 25.89
    15 140 25.28 26.57
    16 150 24.66 25.93
    17 160 24.66 25.93
    18 170 24.66 25.93
    19 180 24.66 25.93
    20 190 24.66 25.93
    21 200 24.66 25.93
    22 210 24.66 25.93
    23 220 25.28 26.57
    24 230 24.63 25.89
    25 240 24.53 25.79
    26 250 24.34 25.58
    27 260 24.02 25.26
    28 270 23.58 24.79
    29 280 23.01 24.19
    30 290 22.30 23.45
    31 300 21.48 22.58
    32 310 20.56 21.62
    33 320 19.60 20.61
    34 330 18.66 19.62
    35 340 17.83 18.74
    36 350 17.23 18.11
    37 360 17.00 17.87


    [0063] The pitch profiles CPR1, CPR2; CPR1", CPR2" are indicated in Figure 8; 20-22 with dash-dotted lines.

    [0064] The value of the radius RP1 at each point is preferably comprised between the respective minimum 1 and maximum value 1, more preferably comprised between the respective minimum 2 and maximum value 2, more preferably comprised between the respective minimum 3 and maximum value 3, more preferably comprised between the respective minimum 4 and maximum value 4; more preferably comprised between the respective minimum 6 and maximum value 6 and even more preferably about equal to the respective value 5 indicated in table 11A or 11B.

    [0065] The dimensions of the pitch profile CPR1 of the first toothed profile 11, 11" can clearly vary by increasing or decreasing in scale the values of table 11A or 11B or 11E, but for example retaining its shape.

    [0066] Preferably the radius RP1 has a single point of absolute minimum (at point 1, 37 of the embodiments of table 11A) along the pitch profile CPR1, CPR1".

    [0067] Preferably the pitch profile CPR1, CPR1" is symmetrical with respect to an ideal plane passing through said point of absolute minimum and through the rotation axis AX11.

    [0068] Preferably a portion of the pitch profile CPR1 around the point of absolute minimum is substantially straight and symmetrical with respect to the plane of symmetry of the profile CPR1, CPR1" and this substantially straight portion subtends an angle α11P comprised between about 50-75° with reference to the rotation axis AX11.

    [0069] Preferably the portion of the pitch profile CPR1 diametrically opposite to the point of absolute minimum substantially forms an arc of a circle, it is also symmetrical with respect to the plane of symmetry of the profile CPR1 and subtends an angle α11C comprised between about 50-90° with reference to the rotation axis AX11.

    [0070] Preferably the radius RP1 reaches two absolute maximum values on the entire pitch profile CPR1 arranged outside both the section in which this profile is substantially straight, and the section in which it is substantially an arc of a circle.

    [0071] Preferably the second toothed profile 13, 13" forms at least a toothed section having a pitch profile substantially different from a full circumference, from a single arc of a circle and not even straight.

    [0072] Preferably the second toothed profile 13, 13', 13" forms at least a toothed section having a pitch profile as a whole substantially open, that is, not closed on itself (Figures 1, 6, 8, 20-22).

    [0073] Like in the embodiments of Figures 1, 6, 8; 20-22 the second profile 13; 13" advantageously has a pitch profile CPR2; CPR2" whose shape is approximated by points from the following table 13A or 13B or 13E; the points are defined by the polar coordinates α13, RP2, where the angle α13 can be for example referred to the possible axis of symmetry AXS13 of the toothed profile 13, 13"; like for example in the embodiments of Figures 1, 6, 8; 20-22 the axis of symmetry AXS13 passes through the rotation axis AX13 and through the point where the radius RP2 is minimum.
    -Table 13A-
    PointAngle α13 [degrees]Radius RP2 Minimum values 2 [mm]Radius RP2 Maximum values 2 [mm]Radius RP2 Minimum values 1Radius RP2 Maximum values 1 [mm]
    1 100 37.65408 56.48112 32.94732 61.18788
    2 -90 36.57824 54.86736 32.00596 59.43964
    3 80 34.84488 52.26732 30.48927 56.62293
    4 -70 33.44368 50.16552 29.26322 54.34598
    5 60 32.44296 48.66444 28.38759 52.71981
    6 -50 31.82656 47.73984 27.84824 51.71816
    7 40 31.36472 47.04708 27.44413 50.96767
    8 30 31.36472 47.04708 27.44413 50.96767
    9 20 31.36472 47.04708 27.44413 50.96767
    10 10 31.36472 47.04708 27.44413 50.96767
    11 0 31.36472 47.04708 27.44413 50.96767
    12 10 31.36472 47.04708 27.44413 50.96767
    13 20 31.36472 47.04708 27.44413 50.96767
    14 30 31.36472 47.04708 27.44413 50.96767
    15 40 31.36472 47.04708 27.44413 50.96767
    16 50 31.82656 47.73984 27.84824 51.71816
    17 60 32.44296 48.66444 28.38759 52.71981
    18 70 33.44368 50.16552 29.26322 54.34598
    19 80 34.84488 52.26732 30.48927 56.62293
    20 90 36.57824 54.86736 32.00596 59.43964
    21 100 37.65408 56.48112 32.94732 61.18788
    -Table 13B-
    PointAngle α11 [degrees]Radius RP1 Values 5 [mm]Radius RP1 Minimum values 4Radius RP1 Maximum values 4 [mm] RadiusRadius RP1 Minimum values 3Radius RP1 Maximum values 3 [mm] Radius
    1 -100 47.0676 44.71422 49.42098 42.36084 51.77436
    2 -90 45.7228 43.43666 48.00894 41.15052 50.29508
    3 80 43.5561 41.378295 45.733905 39.20049 47.91171
    4 -70 41.8046 39.71437 43.89483 37.62414 45.98506
    5 60 40.5537 38.526015 42.581385 36.49833 44.60907
    6 -50 39.7832 37.79404 41.77236 35.80488 43.76152
    7 40 39.2059 37.245605 41.166195 35.28531 43.12649
    8 30 39.2059 37.245605 41.166195 35.28531 43.12649
    9 20 39.2059 37.245605 41.166195 35.28531 43.12649
    10 10 39.2059 37.245605 41.166195 35.28531 43.12649
    11 0 39.2059 37.245605 41.166195 35.28531 43.12649
    12 10 39.2059 37.245605 41.166195 35.28531 43.12649
    13 20 39.2059 37.245605 41.166195 35.28531 43.12649
    14 30 39.2059 37.245605 41.166195 35.28531 43.12649
    15 40 39.2059 37.245605 41.166195 35.28531 43.12649
    16 50 39.7832 37.79404 41.77236 35.80488 43.76152
    17 60 40.5537 38.526015 42.581385 36.49833 44.60907
    18 70 41.8046 39.71437 43.89483 37.62414 45.98506
    19 80 43.5561 41.378295 45.733905 39.20049 47.91171
    20 90 45.7228 43.43666 48.00894 41.15052 50.29508
    21 100 47.0676 44.71422 49.42098 42.36084 51.77436
    -Table 13E-
    PointAngle α13 [degrees]Radius RP2 Minimum values 6 [mm]Radius RP2 Maximum values 6 [mm]
    1 0 45.89 48.24
    2 10 44.58 46.87
    3 20 42.47 44.65
    4 30 40.76 42.85
    5 40 39.54 41.57
    6 50 38.79 40.78
    7 60 38.23 40.19
    8 70 38.23 40.19
    9 80 38.23 40.19
    10 90 38.23 40.19
    11 100 38.23 40.19
    12 110 38.23 40.19
    13 120 38.23 40.19
    14 130 38.23 40.19
    15 140 38.23 40.19
    16 150 38.79 40.78
    17 160 39.54 41.57
    18 170 40.76 42.85
    19 180 42.47 44.65
    20 190 44.58 46.87
    21 200 45.89 48.24


    [0074] The value of the radius RP2 at each point of the pitch curve CPR2, CPR2" is preferably comprised between the respective minimum 1 and maximum value 1, more preferably comprised between the respective minimum 2 and maximum value 2, more preferably comprised between the respective minimum 3 and maximum value 3, more preferably comprised between the respective minimum 4 and maximum value 4, more preferably comprised between the respective minimum 6 and maximum value 6 and even more preferably about equal to the respective value 5 indicated in table 13A or 13B or 13E.

    [0075] The dimensions of the pitch profile CPR2; CPR2" of the second toothed profile 13, 13" can clearly vary by increasing or decreasing in scale the values of table 13A or 13B or 13E, but for example retaining its shape.

    [0076] The pitch profiles defined by the Values 5 of tables 11A, 11B, 11E, 13A, 13B, 13E are shown in Figure 6, engaged together between them.

    [0077] Preferably the pitch profile CPR2; CPR2" is substantially symmetrical with respect to a plane passing through the axis of rotation AX13.

    [0078] Preferably a portion of the pitch profile CPR2; CPR2" close to the plane of symmetry substantially has the shape of an arc of a circle, and subtends an angle α13C comprised between about 50-100° with reference to the axis of rotation AX13.

    [0079] Preferably the second pitch profile CPR2; CPR2" overall subtends an angle α13 comprised between about 170°-240° with reference to the axis of rotation AX13, more preferably comprised between 190°-210° and even more preferably about equal to 200°.

    [0080] In other embodiments not shown the first 11; 11" and the second toothed profile 13; 13" can have for example the shape of a full ellipse, a simple ellipse arc or also other forms.

    [0081] Average radius RP1_m refers to the mean- preferably arithmetic, not weighted - on a round angle, or more generally on the angle subtended to the first toothed profile 11, 11" of the radius RP1.

    [0082] Similarly, average radius RP2_m refers to the mean-preferably arithmetic, not weighted - on a round angle, or more generally on the angle subtended to the second toothed profile 13, 13" of the radius RP2.

    [0083] Like in the embodiment of the accompanying figures, the first toothed profile 11, 11" forms the pinion of the gear, in the sense that its average radius RP1_m is equal to or less than the average radius RP2_m of the second toothed profile 13, 13".

    [0084] Advantageously, while the pitch profiles of the first 11; 11" and of the second toothed profile 13; 13" rotate around the respective axes AX11, AX13, they are tangential to each other without mutual sliding; more particularly the second toothed profile 13; 13" is advantageously obtained by imposing the tangency without sliding on the pitch profile CPR1, CPR1" of the first toothed profile 11, 11".

    [0085] Like in the embodiments of the accompanying figures, the second toothed profile 13, 13" can be interrupted at or near the points where the radius RP2 reaches its maximum.

    [0086] Advantageously the first 11, 11" and the second toothed profile 13, 13" are such that their point of mutual contact PCN is at the maximum distance from the axis of rotation AX11 when it is at the minimum distance from the second axis AX13 or close thereto, like shown for example in Figure 10, 20-22 or near said minimum distance.

    [0087] Advantageously the first 11, 11" and the second toothed profile 13, 13" are such that their point of mutual contact PCN is at the minimum distance from the axis of rotation AX11 when it is at the maximum distance from the second axis AX13, like shown for example in Figure 8, 12; 20, 22 or near said maximum distance.

    [0088] Advantageously the second toothed profile 13" is provided with a stop tooth 130 configured to prevent the first toothed profile 11, 11" from continuing its rotation on the second profile 13" when the two profiles are meshed together (Figure 16-18, 20A, 20B, 20C).

    [0089] For this purpose, each stop tooth 130 has at least one side whose shape is substantially complementary - i.e. it substantially forms its positive cast- to the shape of the spaces of the teeth of the first toothed profile 11, 11", with shape tolerances sufficiently narrow so as to prevent the mutual rolling of the two toothed profiles meshed together (Figure 16-18, 20A, 20B).

    [0090] For this purpose at least part of the perimeter profile of each stop tooth 130 forms the positive cast of said spaces 110 with a shape tolerance TF preferably equal to or less than 0.5 millimetres in default with respect to the profile of the spaces 110, more preferably equal to or less than 0.1 millimetres, more preferably equal to or less than 0.05 millimetres, and even more preferably equal to or less than 0.025 millimetres (Figure 20B, 20C).

    [0091] The downward shape tolerance TF is measured in a direction perpendicular to the profile of the stop tooth 130 and/or of the corresponding space 110.

    [0092] The downward shape tolerance TF at each point of the profile of the stop tooth 130 and/or of the corresponding space 110.

    [0093] Aforesaid tolerance TF is preferably respected on a section of each stop tooth 130 which extends for at least 0.2 times the height HDN of said tooth 130, more preferably which extends for at least 0.3 times or 0.5 times or 0.7 times or 0.9 times the height HDN, and more preferably extends over the entire height HDN of the stop tooth 130 in question.

    [0094] Preferably the second toothed profile 13" is provided with two stop teeth 130 (Figure 16).

    [0095] The remaining teeth 132 of the second toothed profile, like for example also those of the first profile 11, 11", can have involute profiles or in any case be common gear teeth configured to allow another meshed toothing to roll over it.

    [0096] The stop teeth 130 are useful for making mechanical limit stops which - possibly in combination with other mechanical, electromechanical or electronic limit stops - prevent the first toothed profile 11, 11" from making excessive rotations on the second profile 13" so as to disengage therefrom.

    [0097] The two stop teeth 130 can be found, for example, near or at the ends of the arch formed as a whole by the second pitch profile CPR2" (Figure 20, 20A, 20B, 20C).

    [0098] Preferably the transmission ratio p [rho] of the transmission unit 9 ranges from 0.1-4 times, between 0.15-1.61 times, between 0.1-3 times, between 0.19-1.29 times, between 0.25-2.5 times, between 0.25-0.97 times, between 0.3-1 times, between 0.37-0.65 times, considering in said intervals both the minimum and maximum values that the transmission ratio p [rho] reaches during the operation of a same transmission unit 9, 9".

    [0099] The ratio between the maximum ρ_max and the minimum p_min value that the transmission ratio p [rho] of the transmission unit 9, 9" reaches during its operation is preferably comprised between, 1-4 times, between 0.70-4.35 times, between 0,1-3 times, between 0.87-3.48 times, between 0.25-2.5 times, between 1.16-2.61 times, and for example equal to 3 times or 1.74 times.

    [0100] Figure 15 shows indicatively a possible trend of the reduction ratio (i.e. the inverse of the transmission ratio) of the reduction unit 9.

    [0101] The rotation of the toothed profile 11, 11" is reported along the abscissa axis, the reduction ratio along the ordinate axis.

    [0102] Advantageously, the trend of the reduction ratio shown in Figure 15 gives a greater initial reduction (in the first phase of the motion of the wing 3), a lower central reduction (in the central phase of the motion of the wing 3) and a greater final reduction (in the third phase of the motion of the wing 3).

    [0103] Said trend of the reduction ratio makes the torque required from the motor to move the wing 3 to be very uniform during the duration of the motion.

    [0104] Like for example in the embodiment of Figures 2, 3 the motorized drive 5; 5" can further comprise an actuating kinematic mechanism comprising in turn an articulated arm 6.

    [0105] The articulated arm 6 can be fixed to the wing 3 and to the rest of the drive 5 without being able to slide with respect to the wing and the rest of the drive 5; for example it can be fixed to a bracket 8 integrally fixed to the wing 3 without being able to slide with respect thereto.

    [0106] The articulated arm 6 can comprise for example two levers 10, 12 connected together by a hinge or other articulation.

    [0107] In other embodiments not shown the articulated arm 6 can comprise a greater number of levers or more complex lever systems.

    [0108] Like for example in the embodiments of Figures 4, 5; 18, 19 the motorized drive 5; 5" can further comprise an actuating kinematic mechanism comprising in turn a sliding guide 12' and an arm 10' sliding in said guide 12'.

    [0109] The arm 10' can for example comprise a shoe or other slider engaged with the guide 12' so that it can slide along it.

    [0110] Thanks to the greater uniformity of the resistant loads they offer, gears comprising at least one toothed wheel whose pitch profile is substantially different from a full circumference, from a simple arc of circle and it is not even straight can be advantageously applied not only to electric motors but also for example to spring motors or more generally to elastic energy motors such as for example those shown in Figures 6-9; 16.

    [0111] Said spring or elastic energy motor 7' is configured to be driven respectively by a spring or more generally by elastic energy.

    [0112] Said spring or elastic energy motor 7' can be used as a mechanical energy accumulator - for example elastic through the spring 19- to be used as an auxiliary motor in case of emergency, for example to partially or completely close a wing 3 in the event of fault or lack of power supply of the main motor - for example electric - 7 of the motorized drive 5, 5" for example in the event of an electrical fault or in any case interruption of the power supply line of the motor 7.

    [0113] The motor 7' comprises a reduction unit 9' in turn comprising a first 11' and a second toothed profile 13' engaged together to form a gear.

    [0114] The first toothed profile 11' is configured to rotate on itself around a first axis of rotation AX11', for example because it is mounted on a respective shaft.

    [0115] The second toothed profile 13' is instead configured to translate along a straight axis 13' and substantially acts as a rack.

    [0116] The two axes AX11' and Ax13' are preferably perpendicular to each other.

    [0117] Advantageously, the second toothed profile 13' has a pitch profile CPR2' substantially neither straight nor constituted by a simple arc of a circle.

    [0118] As shown in Figures 7, 9 the pitch profile CPR2' of the second toothed profile 13' preferably has a slightly convex and curved shape.

    [0119] More preferably the shape of the pitch profile CPR2' is approximated by points from the following table 13C or 13D or 13F, whose points are defined by the Cartesian coordinates L13'i, Si where L13'i is the distance of a point P13'i from the axis AX13', distance measured in a direction perpendicular to this axis, and Si is the distance of the point P13'i from a point of origin OR of the axis AX13'.
    -Table 13C-
    Point P13'iPosition Si along the axis X [mm]Position L13'i Minimum values 2 [mm]Position L13'i Maximum values 2 [mm]Position L13'i Minimum values 1Position L13'i Maximum values 1 [mm]
    1 0 4.88184 7.32276 4.27161 7.93299
    2 3.3124 5.35488 8.03232 4.68552 8.70168
    3 6.6248 5.79752 8.69628 5.07283 9.42097
    4 9.9372 6.20976 9.31464 5.43354 10.09086
    5 13.2496 6.592 9.888 5.768 10.712
    6 16.562 6.90512 10.35768 6.04198 11.22082
    7 19.8744 7.27048 10.90572 6.36167 11.81453
    8 23.1868 7.56984 11.35476 6.62361 12.30099
    9 26.4992 7.84544 11.76816 6.86476 12.74884
    10 29.8116 8.09992 12.14988 7.08743 13.16237
    11 33.124 8.33624 12.50436 7.29421 13.54639
    12 36.4364 8.5576 12.8364 7.4879 13.9061
    13 39.7488 8.76736 13.15104 7.67144 14.24696
    14 43.0612 8.96904 13.45356 7.84791 14.57469
    15 46.3736 9.16608 13.74912 8.02032 14.89488
    16 49.686 9.36192 14.04288 8.19168 15.21312
    17 52.9984 9.55984 14.33976 8.36486 15.53474
    -Table 13D-
    Point P13'iPosition Si along the axis X [mm]Position L13'i transverse to the axis-Values 5 [mm]Position L13'i Minimum values 4Position L13'i Maximum values 4 [mm]Position L13'i Minimum values 3Position L13'i Maximum values 3 [mm]
    1 0 6.1023 5.797185 6.407415 5.49207 6.71253
    2 3.3124 6.6936 6.35892 7.02828 6.02424 7.36296
    3 6.6248 7.2469 6.884555 7.609245 6.52221 7.97159
    4 9.9372 7.7622 7.37409 8.15031 6.98598 8.53842
    5 13.2496 8.24 7.828 8.652 7.416 9.064
    6 16.562 8.6314 8.19983 9.06297 7.76826 9.49454
    7 19.8744 9.0881 8.633695 9.542505 8.17929 9.99691
    8 23.1868 9.4623 8.989185 9.935415 8.51607 10.40853
    9 26.4992 9.8068 9.31646 10.29714 8.82612 10.78748
    10 29.8116 10.1249 9.618655 10.631145 9.11241 11.13739
    11 33.124 10.4203 9.899285 10.941315 9.37827 11.46233
    12 36.4364 10.697 10.16215 11.23185 9.6273 11.7667
    13 39.7488 10.9592 10.41124 11.50716 9.86328 12.05512
    14 43.0612 11.2113 10.650735 11.771865 10.09017 12.33243
    15 46.3736 11.4576 10.88472 12.03048 10.31184 12.60336
    16 49.686 11.7024 11.11728 12.28752 10.53216 12.87264
    17 52.9984 11.9498 11.35231 12.54729 10.75482 13.14478
    -Table 13F-
    Point P13'iPosition Si along the axis X [mm]Position L13'i Minimum values 6Position L13'i Maximum values 6 [mm]
    1 0 5.95 6.25
    2 3.3124 6.53 6.86
    3 6.6248 7.07 7.43
    4 9.9372 7.57 7.96
    5 13.2496 8.03 8.45
    6 16.562 8.42 8.85
    7 19.8744 8.86 9.32
    8 23.1868 9.23 9.70
    9 26.4992 9.56 10.05
    10 29.8116 9.87 10.38
    11 33.124 10.16 10.68
    12 36.4364 10.43 10.96
    13 39.7488 10.69 11.23
    14 43.0612 10.93 11.49
    15 46.3736 11.17 11.74
    16 49.686 11.41 11.99
    17 52.9984 11.65 12.25


    [0120] The value of the distance L13'i in each point P13'i is preferably comprised between the respective minimum 1 and maximum value 1, more preferably comprised between the respective minimum 2 and maximum value 2, more preferably comprised between the respective minimum 3 and maximum value 3, more preferably comprised between the respective minimum 4 and maximum value 4, more preferably comprised between the respective minimum 6 and maximum value 6 and even more preferably about equal to the respective Value 5 indicated in table 13C or 13D or 13F.

    [0121] The dimensions of the pitch profile CPR2' of the rack 13' can clearly vary by increasing or decreasing in scale the values of table 13C or 13D or 13F, but for example retaining its shape.

    [0122] Advantageously, the pitch profiles CPR1', CPR2' of the first 11' and of the second toothed profile 13', while the first rotates around the axis AX11' and the second slides along the axis AX13', are tangent to each other without mutual sliding; more particularly the second toothed profile 13' is advantageously obtained by imposing the tangency without sliding on the pitch profile CPR1' of the first toothed profile 11'.

    [0123] The distance between the axis of rotation AX11' and a point of the pitch curve CPR1' of the toothing 11' in the present description is considered as the radius RP1' of the toothing associated with that point and the angular position α11' [alpha_11'] of that point with respect to the axis AX11'.

    [0124] The distance between the sliding axis AX13' and a point PCN of the pitch curve of the toothing 13' is measured according to a direction perpendicular to the axis AX13'.

    [0125] As shown for example in Figures 7, 9, 20, 22 advantageously the radius RP1' at the beginning of the first toothed profile 11' has a minimum value, then progressively increases as the angular position α11' of the point of the pitch profile considered with respect to the axis AX11' increases and reaches its maximum value for example at the end of the toothed profile 11' itself.

    [0126] The radius RP1' can possibly reach its maximum value in a toothed section which during normal operation of the gear never engages with the second toothed profile 13'.

    [0127] Preferably the first toothed profile 11' has a pitch profile CPR1' whose shape is approximated by points from the following table 11C or 11D or 11F, whose points are defined by the polar coordinates RP1', α11'
    -Table 11C-
    PointAngle α11' [degrees]Radius RP1' Minimum values 2 [mm]Radius RP1' Maximum values 2 [mm]Radius RP1' Minimum values 1 [mm]Radius RP1' Maximum values 1 [mm]
    1 0 15.2 22.8 13.3 24.7
    3 20 14.5268 21.7902 12.71095 23.60605
    5 40 13.57272 20.35908 11.87613 22.05567
    7 60 12.9632 19.4448 11.3428 21.0652
    9 80 12.45616 18.68424 10.89914 20.24126
    11 100 12.02432 18.03648 10.52128 19.53952
    13 120 11.66256 17.49384 10.20474 18.95166
    15 140 11.33864 17.00796 9.92131 18.42529
    17 160 11.04224 16.56336 9.66196 17.94364
    19 180 10.76072 16.14108 9.41563 17.48617
    21 200 10.48352 15.72528 9.17308 17.03572
    -Table 11D-
    PointAngle α11' [degrees]Radius RP1' Values 5 [mm]Radius RP1' Minimum values 4 [mm]Radius RP1' Maximum values 4 [mm]Radius RP1' Minimum values 3 [mm]Radius RP1' Maximum values 3 [mm]
    1 0 19 18.05 19.95 17.1 20.9
    3 20 18.1585 17.250575 19.066425 16.34265 19.97435
    5 40 16.9659 16.117605 17.814195 15.26931 18.66249
    7 60 16.204 15.3938 17.0142 14.5836 17.8244
    9 80 15.5702 14.79169 16.34871 14.01318 17.12722
    11 100 15.0304 14.27888 15.78192 13.52736 16.53344
    13 120 14.5782 13.84929 15.30711 13.12038 16.03602
    15 140 14.1733 13.464635 14.881965 12.75597 15.59063
    17 160 13.8028 13.11266 14.49294 12.42252 15.18308
    19 180 13.4509 12.778355 14.123445 12.10581 14.79599
    21 200 13.1044 12.44918 13.75962 11.79396 14.41484
    -Table 11F-
    PointAngle α11' [degrees]Radius RP1' Minimum values 6 [mm]Radius RP1' Maximum values 6 [mm]
    1 0 18.53 19.48
    3 20 17.70 18.61
    5 40 16.54 17.39
    7 60 15.80 16.61
    9 80 15.18 15.96
    11 100 14.65 15.41
    13 120 14.21 14.94
    15 140 13.82 14.53
    17 160 13.46 14.15
    19 180 13.11 13.79
    21 200 12.78 13.43


    [0128] The value of the radius RP1 at each point is preferably comprised between the respective minimum 1 and maximum value 1 indicated in the table, more preferably comprised between the respective minimum 2 and maximum value 2, more preferably comprised between the respective minimum 3 and maximum value 3, more preferably comprised between the respective minimum 4 and maximum value 4; more preferably comprised between the respective minimum 6 and maximum value 6 and even more preferably about equal to the respective value 5 indicated in table 11C or 11D or 11F.

    [0129] The dimensions of the pitch profile CPR1 of the first toothed profile 11' can clearly vary by increasing or decreasing in scale the values of table 11C or 11D, but for example retaining its shape.

    [0130] The pitch profiles defined by the Values 5 of the tables 11C, 11D, 13C, 13D are shown in Figure 7, 16, 20-22 engaged together between them.

    [0131] Transmission ratio of the gear - namely sprocket/rack pair - formed by the toothed profiles 11', 13' means in the present description the quantity ρ' [rho prime] = Δs/Δβ, where Δs is the linear displacement made by the rack 13' following a rotation equal to an angle β [beta] of the sprocket 11'.

    [0132] The rotation Δβ [delta_beta] can be expressed for example in radians.

    [0133] The greater the radius RP1' of the first toothed profile 11' at point PCN where the two toothed profiles 11', 13' engage, the greater the instantaneous linear displacement Δs [delta-s] of the rack.

    [0134] Preferably the transmission ratio ρ' [rho] of the second reduction unit 9' is comprised between 0.021-0.192 times, or between 0.026-0.154 times, between 0.035-0.115 times or between 0.053-0.077, considering in these intervals both the minimum and maximum values that the transmission ratio ρ' [rho] reaches during the operation of a same reduction unit 9'.

    [0135] The ratio between the maximum ρ'_max and the minimum ρ'_min value that the transmission ratio ρ' [rho] of the reduction unit 9' reaches during its operation is preferably comprised between 0.6-3.75 times, or between 0.75-3 times or between 1-2.25 times, and for example equal to 1.5 times.

    [0136] Figure 23 shows indicatively a possible trend of the reduction ratio (i.e. the inverse of the transmission ratio) of the reduction unit 9'.

    [0137] The abscissa indicates the angular position - for example in degrees - of the sprocket 11', the ordinate the reduction ratio, i.e. the ratio between the variation of the angular position of the sprocket 11' and the linear displacement of the rack 13', for example the degrees per millimeter, [°/mm]).

    [0138] Advantageously, the reduction ratio trend shown in Figure 23 has been defined in such a way as to confer a lower initial reduction in the initial compression phase of the spring 19 and a greater final reduction in the final compression phase of the spring 19.

    [0139] Eventually, the ratio between the maximum ρ'_max and the minimum ρ '_min value that the transmission ratio ρ' [rho] of the transmission unit 9' reaches during its operation can be comprised between 1-5 times or between 1.5-2.5 times, and for example equal to 2 times.

    [0140] The auxiliary motor 7' can comprise:
    • a helical spring 19;
    • a guide pin 15 inserted inside the spring 19 to keep it straight when it is compressed;
    • a slider 14 integral with the toothed profile 13' which can slide along the guide pin 15
    • a shoulder 16;
    • the toothed profile 11'.


    [0141] The second toothed profile 13' is preferably integral with the slider 14 which is fixed to the first guide pin 15 so that it can slide along it.

    [0142] In any case, the spring 19 preferably rests against the slider 14 and the shoulder 16, pressing against them and tending to move them away from each other.

    [0143] The motorized drive 5 preferably comprises a casing 25 to which one or more of the toothed wheels or cams 11', 11", 13', 13", 15, 17, 23, the motor 7, 7', the spring 19 and/or the guide pin 15 are fixed and in which they are possibly contained.

    [0144] The casing 25 may optionally form a box or other shell which encloses one or more of the toothed wheels or cams 11', 11", 13', 13", 15, 17, 23, the motor 7, 7', the spring 19 and/or the guide pin 15.

    [0145] The drive 5, 5" advantageously comprises a system 24 for adjusting the preload force of the spring 19 or other elastic element (Figures 16, 16A).

    [0146] Said preload adjustment system 24 advantageously comprises the shoulder 16 and an end 26 of the guide pin 15 itself.

    [0147] For this purpose, the shoulder 16 is preferably obtained on a bush 27 coaxial with the guide pin 26 and with the axis x13'.

    [0148] The outer sides of the end 26 of the pin 15, also called the adjustment end, are preferably threaded and the bush 27 is preferably screwed onto them, it also being provided with an internal thread coaxial with the guide pin 26 and the axis AX13'.

    [0149] For this purpose, the bush 27 can for example also be an internally threaded nut, for example a hexagonal nut.

    [0150] The end of the adjustment pin 26 and of the guide pin 15 is preferably connected to the casing 25 for example by means of the block 28 so as to be able to rotate on itself and around the axis AX13'.

    [0151] The guide pin 15 has for example a hexagonal hollow seat 29 - preferably coaxial with the pin 15 itself and with the axis x13'- through which the pin 15 can be rotated on itself and around the axis AX13'.

    [0152] The hexagonal hollow seat 29 is preferably obtained at one end of the guide pin 15 indicated in the present description as "adjustment end".

    [0153] The pin 15 is preferably fixed to the casing 25 so that it cannot slide along its axis AX13', for example because it is axially blocked at or in proximity to its end 33 opposite the adjustment end of the pin 15 (Figure 16) .

    [0154] Preferably the bush 27 is fixed to the casing 25 so as to be able to translate along the adjustment pin 26 without however being able to rotate on itself and with respect to the casing 25.

    [0155] For this purpose, the adjustment system of the preload 24 can comprise one or more pins or anti-unscrewing pins 31 and one or more corresponding slots 32.

    [0156] Each slot 32, drawn with a dashed and double-dotted line in Figure 16A, extends substantially parallel to the axis AX13' of the pin 15; each slot 32 can be obtained for example in the casing 25.

    [0157] Each anti-unscrewing pin or pin 31 is fixed on the bush 27 so as to protrude radially therefrom, and is inserted in a respective slot 32.

    [0158] By rotating the guide pin 15 axially on itself, the bush 27 is screwed or unscrewed on the pin 15 itself, making it slide axially along the pin 15 together with the shoulder 16 and thus adjusting the preload of the spring 19.

    [0159] Said preload can be adjusted, for example, according to the inertia of the wing 3 to be operated.

    [0160] In order to be able to be rotated on itself for example by means of a tool or with bare hands, the guide pin 15 can be provided with an engagement portion also different from the hexagonal hollow seat 29; said engagement portion may comprise, for example, a simple slot configured to house a flat blade screwdriver, a hollow seat for square wrenches or a notch for cross-tip screwdrivers.

    [0161] The helical spring 19 can have, for example, a characteristic curve with linear elasticity, but it can also have a non-linear characteristic curve.

    [0162] In other embodiments not shown, the helical metal spring 19 can be replaced or combined with other types of springs or other elastic elements made of materials, including non-metallic ones, for example elastomeric.

    [0163] As shown for example in Figure 1, the elastic energy motor 7' can advantageously be combined with the motorized drive 5.

    [0164] For this purpose, the elastic energy motor 7' can for example drive the electric motor 7 and/or be driven by it, for example as will be described in more detail below.

    [0165] For this purpose, the toothed profiles 13, 11' are keyed onto the same shaft and/or integrally fixed to one another in such a way that the respective axes of rotation AX13 and AX11' coincide.

    [0166] In other words, the second toothed profile 13 of the first reduction unit 9 and the first toothed profile 11' of the second reduction unit (9') are coaxial.

    [0167] The toothed profiles 13, 11' are operated simultaneously by both the electric motor 7 and the elastic energy motor 7'.

    [0168] An example of operation and use of the barrier 1, 1', 1", 1III and the relative drive 5, 5" described above is now described.

    [0169] Assuming that the wing 3 is initially closed, and therefore substantially coplanar to the surface of the wall 2, in this condition the two toothed profiles 11, 13; 11", 13" are in the condition of Figure 8, 16 with their contact point PCN at minimum distance from the axis of rotation AX11 and maximum distance from the axis of rotation AX13, so as to minimize the transmission ratio ρ [rho] = RP1/RP2 of the transmission unit 9, 9".

    [0170] Again in this condition, the two toothed profiles 11', 13' can be in the condition of Figure 9, for example, where their contact point PCN' is at a minimum distance from the axis AX13' and at a maximum distance from the axis AX11'.

    [0171] In this condition, the second toothed profile 13' applies to the rocket 11' a torque with maximum arm but with a minimum elastic force, since the spring is at the minimum degree of compression of its movements.

    [0172] In the condition of Figure 20, 20A, the stop tooth 130 of the second toothed profile 13" is jammed in a space between two adjacent teeth of the toothed profile 11", that is, it is in an end-of-stroke position.

    [0173] With reference to Figures 8, 9, 20 to open the wing 3 the electric motor 7 rotates for example the first toothed profile 11 counterclockwise, and the second toothed profile 13 clockwise; with reference to Figure 9, the first toothed profile 11' is rotated clockwise by the electric motor 7, sliding the slider 14 to the right along the guide pin 15.

    [0174] The slider 14 thus begins to compress the spring 19 when the transmission ratio ρ'= Δs/Δβ is maximum or close to its maximum value, amplifying the elastic deformation force applied by the spring 19 to the slider to the maximum; however, said deformation force is minimal when the spring has just started to deform.

    [0175] As the two toothed profiles rotate, the distance of their contact point PCN from the axis AX11 increases while the distance of the same point from the axis AX13 progressively decreases, consequently increasing the transmission ratio ρ [rho] = RP1/RP2 of the transmission unit 9, 9".

    [0176] This means that the motorized drive 5, 5" starts to open the relative wing 3 with a minimum transmission ratio ρ [rho], the pinion 11, 11" applies an initially maximum driving and then progressively decreasing torque to the driven toothing 13, 13", rotating the toothing 13, 13" at an initially minimum and progressively increasing speed.

    [0177] At the same time the first toothed profile 11' continues to rotate clockwise and the second profile 13' continues to slide to the right, continuing to compress the spring 19.

    [0178] The transmission ratio ρ' decreases progressively, and this fact is at least partially compensated by the progressive increase in the elastic force with which the spring 19 opposes the displacement of the slider 14 as it is deformed.

    [0179] In the condition of Figure 10, 21 the distance of the contact point PCN of the profiles 11, 13; 11", 13" from the axis AX11 substantially reaches its maximum value, while the distance of the point PCN from the axis AX13 reaches its minimum value, causing the transmission ratio ρ [rho] to reach its maximum value.

    [0180] The condition of Figure 10, 21 is particularly suitable for the intermediate phase between the acceleration and deceleration phases of the rotation of the wing, whether it is opening or closing: the wing does not require further acceleration, on the contrary it is about to be braked and therefore it requires only a minimum driving torque from the motor 7, for example just sufficient to overcome the internal frictions at the hinges of the wing and in general the frictions that oppose the movement of the wing 3.

    [0181] In this phase it is sufficient that the motor 7 rotates the wing 3 at the maximum possible speed by applying low driving torques and imparting on it almost zero or very low accelerations, since the wing 3 is now launched and can continue its motion even only thanks to its inertia.

    [0182] At the same time the auxiliary motor 7' is in the condition of Figure 11, in which with respect to Figure 9 the first toothed profile 11' is rotated more clockwise, the slider 14 is more displaced to the right, the spring 19 is more compressed and the transmission ratio ρ' has decreased.

    [0183] Once the phase of Figure 10, 21 has been overcome, the wing 3 must be decelerated because it is approaching the end of its stroke, that is, for example, to the fully open position.

    [0184] It is therefore useful that the motor 7 applies a progressively increasing braking torque to the wing 3, at the same time slowing down its rotation, and precisely for this purpose after the condition of Figure 10, 21 the distance of the contact point PCN of the profiles 11, 13; 11", 13" from the axis AX11 decreases again, while the distance of the point PCN from the axis AX13 increases again, progressively and reducing again the transmission ratio ρ [rho].

    [0185] In the subsequent condition of Figure 12, 22 corresponding for example to a condition of full opening of the wing 3, the distance of the contact point PCN of the profiles 11, 13; 11", 13" from the axis AX11 has reached a second minimum value, while the distance of the point PCN from the axis AX13 has reached its maximum value again, making the transmission ratio p [rho] reach its minimum value again.

    [0186] This means that switching from the condition of Figure 10; 21 to that of Figure 12; 22 the pinion 11 is able to energetically brake the wing 3 with a progressively increasing torque, imposing a progressively decreasing speed on it.

    [0187] In the condition of Figure 12; 22 the motor can for example stop the rotation of the toothed profiles 11, 13; 11", 13" by correspondingly stopping the wing 3 for example in a fully open position.

    [0188] In the condition of Figure 22, the stop tooth 130 is jammed or in any case blocked in the space of the toothed profile 11" preventing the latter from rolling further on the first toothed profile 13"; in other words, the tooth 130 is in a second end-of-stroke position.

    [0189] While the gear 11, 13; 11", 13" is in the condition of Figure 12, the gear 11', 13' is in that of Figure 13 in which, with respect to Figure 12, the first toothed profile 11' is further rotated clockwise, the slider 14 is further displaced to the right, the spring 19 is compressed to the maximum and the transmission ratio p' is at its minimum value.

    [0190] The work of the electric motor 7 served in part to open the wing 3, in part to store elastic energy in the spring 19.

    [0191] The reduction unit 9, 9" and more generally the gear comprising the toothed profiles 11, 13; 11", 13" are therefore able to achieve a lower transmission ratio ρ [rho] = RP1/RP2 in the initial acceleration and final deceleration phases of the wing 3, and a greater transmission ratio ρ [rho] in the central phase of the motion of the wing, making the resistant torque applied to the motor 7 more uniform with respect to a transmission unit provided exclusively with gears with circular toothed profiles and without a gearbox.

    [0192] At the same time, the progressive increase in the compression force of the spring 19 is at least partially compensated by the progressive decrease in the transmission ratio ρ', which tends to make the resistant torque that the electric motor 7 must overcome in order to compress the spring 19 more constant.

    [0193] In normal operating conditions, when the electric motor 7 closes the wing 3 it is helped by the spring 19 which decompresses, giving the elastic energy stored during the door opening phase back.

    [0194] Again in normal operating conditions, the wing 3 can be kept open by the torque generated by the electric motor 7 which is kept constantly powered.

    [0195] In the event of an anomaly, for example in the event of a fault in the power supply line of the electric motor 7, the elastic energy motor 7' advantageously operates the wing 3 by closing it again.

    [0196] In doing so, the elastic energy motor 7' can for example drag the electric motor 7 and the gears and/or worm screws 15, 17, 19, 21, 23 of the relative speed reducer into rotation.

    [0197] The user can open the door 3 by hand, loading the spring 19.

    [0198] In doing so, the user can for example drag the electric motor 7 and the gears and/or worm screws 15, 17, 19, 21, 23 of the relative speed reducer into rotation.

    [0199] In the previous example of operation, the motorized drive 5 has been configured so that in the event of a failure, the elastic energy auxiliary motor 7' tends to close the door or other movable barrier 3.

    [0200] Alternatively, the drive 5 can be configured so that in case of failure the auxiliary motor 7' tends to open the door or other movable barrier 3; this configuration is useful for example to open a series of doors of a building in case of anomaly, to favour a natural convection creating a chimney effect.

    [0201] In this case the electric motor 7 loads the spring 19 by closing the door 3, and is helped by the spring 19 when it opens the door 3.

    [0202] Therefore in general in the mechanism of Figure 1 the progressive increase of the radius RP1' corresponding to the point of contact between the two toothed profiles 11', 13' partially compensates for the progressive decrease in the thrust of the spring 19, and the wing 3 is driven by the auxiliary motor 7' with a more constant driving torque.

    [0203] More generally, from the preceding description it is clear that the transmission units 9, 9', 9" with a variable transmission ratio, having an extremely simple mechanical construction, are able to make the resistant torque applied to the motor of a drive of a movable barrier such as for example the rotating wing of a door, main door, gate or swing shutter, or even the sliding wing of a wall or sliding partition much more uniform.

    [0204] Having to overcome a more uniform resistant torque, the motor 7 can have a smaller size; for example, the authors of the present invention have succeeded in reducing the size and rating power of the electric motors 7 by about half, for the same opening time of the wing 3.

    [0205] For the same installed electrical power of the motor 7, the maximum rotation speed can be considerably reduced, for example halved, thereby reducing the vibrations and noise of speed of the reduction unit.

    [0206] By operating more often in conditions closer to optimal conditions, said motor can operate with greater efficiency, and consequently less heating and stress in the case of an electric motor 7.

    [0207] For the same reasons, the entire motorized drive 5, 5" can be sized more lightweight and less massively than if it had a fixed transmission ratio.

    [0208] In particular with an actuator 5, 5" with the same installed electrical power, the speed and consequently also the time for opening and closing the wing 3 according to the weight of the latter can be adjusted in a wider range - for example double - with respect to a transmission with front gears with constant transmission ratio.

    [0209] The resistant torque applied to the motor of a drive of a movable barrier of aforesaid type can be made even more uniform by the possible articulated arm 6.

    [0210] Figure 14 shows indicatively a possible trend of the reduction ratio -that is the inverse of the transmission ratio- of a single articulated arm 6 formed by two levers hinged depending on the opening angle of the wing of a door, such as for example the door 3 of figure 2.

    [0211] The rotation of the wing 3 is shown along the abscissa axis, the reduction ratio along the ordinate axis.

    [0212] The transmission ratio of the arm 6 contributes to making the overall transmission ratio of the motorized drive 5; 5" more similar to the desired speed profile, with an initial section of acceleration of the wing, an intermediate section at almost constant speed of the wing and a final section of deceleration of the wing, which corresponds to applying to the electric motor 7 a very constant resistant torque as the opening angle of the wing 3 changes.

    [0213] On the other hand, a kinematic mechanism with a shoe-like arm has an almost uniform transmission ratio depending on the opening angle of the wing.

    [0214] To obtain the desired speed profile, the motor is forced to impose high torques in acceleration and deceleration.

    [0215] Due to the uniform transmission ratio of the kinematic mechanism with shoe-like arm, a manufacturer is often obliged to declare lower values of maximum inertia of the wing with respect to a kinematic mechanism with articulated arm.

    [0216] Advantageously, with the introduction of the variable transmission ratio of the reduction unit 9, 9", on the other hand, it is possible to guarantee the desired speed profile also by using a kinematic mechanism with shoe-like arm by applying a constant resistant torque to the motor.

    [0217] Furthermore, the reduction unit 9; 9" allows to declare a single value of maximum inertia of a wing that can be operated with a motorized drive, regardless of whether the drive includes a kinematic mechanism with articulated arm or it is shoe-like.

    [0218] An advantage of the mechanical energy accumulator with spring and variable transmission ratio comprising the motor 7' and the reduction unit 9', compared to an actuator with fixed transmission ratio, is to provide a movement torque 3 of the wing substantially constant throughout its movement, and for example sufficient to ensure that the wing, in the final stop position when closing, has a high residual torque for operating mechanical lock bolts, as is often required.

    [0219] At the same time it is required that, in the absence of voltage in the power supply system of the electric motor 7 of the main actuator, it is possible to manually open the wing with a constant torque or that in any case it is not desired that the torque to be performed manually increases in the subsequent opening phases of the wing.

    [0220] With a rack and pinion transmission system with constant transmission ratio, in the fully open end position of the wing 3 the spring 19 would be compressed to the maximum and the torque transmitted by it would be maximum; to open the wing 3 manually, it would be necessary to apply a higher and higher torque to it which would give the perception that the drive 5 is being blocked, opposing the opening.

    [0221] With an auxiliary actuator 7', 9' with variable transmission ratio, said unpleasant perception is not present.

    [0222] Furthermore, the auxiliary actuator 7', 9' can have an overall length, according to the sliding direction FC of the rack 13', considerably reduced - for example by about 30% - with respect to a transmission with fixed ratio considering that the average torque transmitted in the system with fixed ratio is equal to the constant torque transmitted by the system with variable ratio.

    [0223] The toothed gears 11, 13; 11', 13'; 11", 13" previously described are capable of reproducing a wide range of movements of a wing, in particular reproducing a wide range of speed profiles, providing high torques and low actuation speeds when high accelerations or decelerations are desired, for example at the beginning and at the end of a closing or opening movement of a rotating or sliding wing 3, and weak torques and high speeds for example in the central phase of opening or closing a rotating or sliding wing or in any case in phases of the movement in which an almost constant speed of the wing is desired.

    [0224] The motorized barrier 1, 1', 1", 1III advantageously comprises a logic control unit, comprising for example one or more electronic microprocessors, and one or more remote control device through which a user can remotely control the opening or closing of the wing or wings 3 by sending appropriate command signals to the logic control unit.

    [0225] Said command signals can be sent for example by radio or acoustic waves, or again be for example optical signals.

    [0226] The embodiments described above are susceptible to numerous modifications and variants, without departing from the scope of the present invention, which is defined by the claims.

    [0227] Every reference in this description to "an embodiment", "an embodiment example" means that a particular feature or structure described in relation to such embodiment is included in at least one embodiment of the invention and in particular in a specific variant of the invention as defined in a main claim.

    [0228] The fact that such expressions appear in various passages of the description does not imply that they are necessarily referred solely to the same embodiment.

    [0229] For example, the materials used, as well as the dimensions thereof, can be of any type according to the technical requirements.

    [0230] It must be understood that an expression of the type "A comprises B, C, D" or "A is formed by B, C, D" also comprises and describes the particular case in which "A is made up of B, C, D".

    [0231] The expression "A comprises an element B" unless otherwise specified is to be understood as "A comprises one or more elements B".

    [0232] References to a second, third, fourth entity and so on do not necessarily imply the existence of a first, second and third entity respectively but they are simply a conventional name to indicate that an nth entity might be different and distinct from any other 1, 2th ... (n-1), (n+1)-th entities, if they existed.

    [0233] The examples and lists of possible variants of the present application are to be construed as nonexhaustive lists.


    Claims

    1. Motorized drive (5, 5") configured to open and/or close a wing (3) of a barrier such as a door, main door, gate or swing shutter, a wall or sliding partition or other sliding wing, wherein the motorized drive (5) comprises an electric motor (7), a first reduction unit (9, 9") through which the motor (7) can operate the wing (3) opening and/or closing the same, an auxiliary elastic energy motor (7'); and wherein:

    - the first reduction unit (9, 9") comprises a first (11, 11") and a second toothed profile (13, 13") engaging together, thus realizing a gear with a variable transmission ratio depending on the angular and/or linear position of at least one of the two toothed profiles; and

    - at least one of the first (11, 11") and of the second toothed profile (13, 13") forms at least one toothed section having a pitch profile which is substantially non-circular or not formed by a simple arc of a circle or a straight line

    - the elastic energy auxiliary motor (7') comprises a second reduction unit (9') which in turn comprises a first (11') and a second toothed profile (13') engaged together to form a gear;

    - the first (11') toothed profile of the second reduction unit (9') and the second toothed profile (13) of the first reduction unit (9) are configured to be operated both by the electric motor (7) and by the auxiliary elastic energy motor (7');

    - the motorized drive (5, 5") is configured for operating the closure of the wing (3) through the second reduction unit (9')
    characterized in that

    - the elastic energy auxiliary motor (7') can be connected to the wing (3) through the second reduction unit (9');

    - the first (11') toothed profile of the second reduction unit (9') and the second toothed profile (13) of the first reduction unit (9) are keyed onto the same shaft and/or integrally fixed to one another in such a way that the respective axes of rotation (AX13) and (AX11') coincide.


     
    2. Drive (5, 5") according to claim 1, wherein the first toothed profile (11') is configured to rotate about itself around a third rotation axis (AX11') and has a pitch profile having substantially the same shape, even if dimensions possibly different, with respect to a pitch profile whose points are at a distance (RP1') from this axis of rotation comprised between the Minimum Values_1 and the Maximum Values_1 indicated in the following Table 11C
    PointAngle α11' [degrees]Radius RP1' Minimum values 1 [mm]Radius RP1' Maximum values 1 [mm]
    1 0 13.3 24.7
    3 20 12.71095 23.60605
    5 40 11.87613 22.05567
    7 60 11.3428 21.0652
    9 80 10.89914 20.24126
    11 100 10.52128 19.53952
    13 120 10.20474 18.95166
    15 140 9.92131 18.42529
    17 160 9.66196 17.94364
    19 180 9.41563 17.48617
    21 200 9.17308 17.03572
    , wherein said distance (RP1') and said pitch profiles are considered in a plane perpendicular to the third axis of rotation (AX11').
     
    3. Drive (5, 5") according to one or more of the preceding claims, wherein the second toothed profile (13') is configured to slide along a fourth axis (AX13') and has a pitch profile having substantially the same shape, even if dimensions possibly different, with respect to a pitch profile whose points are at a distance (L13') from a fifth axis comprised between the Minimum Values_1 and the Maximum Values_1 indicated in the following Table 13C
    Point P13'iPosition Si along the axis X [mm]Position L13'i Minimum values 1Position L13'i Maximum values 1 [mm]
    1 0 4.27161 7.93299
    2 3.3124 4.68552 8.70168
    3 6.6248 5.07283 9.42097
    4 9.9372 5.43354 10.09086
    5 13.2496 5.768 10.712
    6 16.562 6.04198 11.22082
    7 19.8744 6.36167 11.81453
    8 23.1868 6.62361 12.30099
    9 26.4992 6.86476 12.74884
    10 29.8116 7.08743 13.16237
    11 33.124 7.29421 13.54639
    12 36.4364 7.4879 13.9061
    13 39.7488 7.67144 14.24696
    14 43.0612 7.84791 14.57469
    15 46.3736 8.02032 14.89488
    16 49.686 8.19168 15.21312
    17 52.9984 8.36486 15.53474
    , wherein this fifth axis is parallel with respect to said fourth axis (AX13') and said distance (L13') and said pitch profiles are considered in a plane passing through this fifth axis.
     
    4. Drive (5, 5") according to claim 2, wherein the first toothed profile (11') has a pitch profile having substantially the same shape, even if dimensions possibly different, with respect to a pitch profile whose points are at a distance (RP1') from this axis of rotation comprised between the Minimum Values_2 and the Maximum Values_2 indicated in the following Table 11C
    PointAngle α11' [degrees]Radius RP1' Minimum values 2 [mm]Radius RP1' Maximum values 2 [mm]
    1 0 15.2 22.8
    3 20 14.5268 21.7902
    5 40 13.57272 20.35908
    7 60 12.9632 19.4448
    9 80 12.45616 18.68424
    11 100 12.02432 18.03648
    13 120 11.66256 17.49384
    15 140 11.33864 17.00796
    17 160 11.04224 16.56336
    19 180 10.76072 16.14108
    21 200 10.48352 15.72528

     
    5. Drive (5, 5") according to claim 2, wherein the first toothed profile (11') has a pitch profile having substantially the same shape, even if dimensions possibly different, with respect to a pitch profile whose points are at a distance (RP1') from this axis of rotation comprised between the Minimum Values_3 and the Maximum Values_3 indicated in the following Table 11D
    PointAngle α11' [degrees]Radius RP1' Minimum values 3 [mm]Radius RP1' Maximum values 3 [mm]
    1 0 17.1 20.9
    3 20 16.34265 19.97435
    5 40 15.26931 18.66249
    7 60 14.5836 17.8244
    9 80 14.01318 17.12722
    11 100 13.52736 16.53344
    13 120 13.12038 16.03602
    15 140 12.75597 15.59063
    17 160 12.42252 15.18308
    19 180 12.10581 14.79599
    21 200 11.79396 14.41484

     
    6. Drive (5, 5") according to claim 3, wherein the second toothed profile (13') has a pitch profile having substantially the same shape, even if dimensions possibly different, with respect to a pitch profile whose points are at a distance (L13') from a fifth axis comprised between the Minimum Values_2 and the Maximum Values_2 indicated in the following Table 13C
    Point P13'iPosition Si along the axis X [mm]Position L13'i Minimum values 2 [mm]Position L13'i Maximum values 2 [mm]
    1 0 4.88184 7.32276
    2 3.3124 5.35488 8.03232
    3 6.6248 5.79752 8.69628
    4 9.9372 6.20976 9.31464
    5 13.2496 6.592 9.888
    6 16.562 6.90512 10.35768
    7 19.8744 7.27048 10.90572
    8 23.1868 7.56984 11.35476
    9 26.4992 7.84544 11.76816
    10 29.8116 8.09992 12.14988
    11 33.124 8.33624 12.50436
    12 36.4364 8.5576 12.8364
    13 39.7488 8.76736 13.15104
    14 43.0612 8.96904 13.45356
    15 46.3736 9.16608 13.74912
    16 49.686 9.36192 14.04288
    17 52.9984 9.55984 14.33976

     
    7. Drive (5, 5") according to claim 3, wherein the second toothed profile (13') has a pitch profile having substantially the same shape, even if dimensions possibly different, with respect to a pitch profile whose points are at a distance (L13') from a fifth axis comprised between the Minimum Values_3 and the Maximum Values_3 indicated in the following Table 13D
    Point P13'iPosition Si along the axis X [mm]Position L13'i Minimum values 3Position L13'i Maximum values 3 [mm]
    1 0 5.49207 6.71253
    2 3.3124 6.02424 7.36296
    3 6.6248 6.52221 7.97159
    4 9.9372 6.98598 8.53842
    5 13.2496 7.416 9.064
    6 16.562 7.76826 9.49454
    7 19.8744 8.17929 9.99691
    8 23.1868 8.51607 10.40853
    9 26.4992 8.82612 10.78748
    10 29.8116 9.11241 11.13739
    11 33.124 9.37827 11.46233
    12 36.4364 9.6273 11.7667
    13 39.7488 9.86328 12.05512
    14 43.0612 10.09017 12.33243
    15 46.3736 10.31184 12.60336
    16 49.686 10.53216 12.87264
    17 52.9984 10.75482 13.14478

     
    8. Drive (5, 5") according to one or more of the preceding claims, wherein the first toothed profile (11') substantially acts as a pinion or a sprocket.
     
    9. Drive (5, 5") according to one or more of the preceding claims, wherein both the first (11, 11") and the second toothed profile (13, 13") form at least one toothed section having a pitch profile which is substantially non-circular and neither exclusively an arched circle nor straight.
     
    10. Drive (5, 5") according to one or more of the preceding claims, wherein the second toothed profile (13') substantially acts as a rack.
     
    11. Drive (5, 5") according to one or more of the preceding claims, wherein the auxiliary motor (7') is a motor driven by the release force of a spring (19) or other elastic and/or pneumatic or energy storage element.
     
    12. Motorized drive (5, 5") at least according to claim 2 configured to store mechanical energy during the opening of the wing (3) by activating:

    - an initial phase in which the second reduction unit (9') transfers mechanical energy from the wing (3) to the auxiliary motor (7') by operating the latter with a reduction ratio;

    - a final phase in which the second reduction group (9') transfers mechanical energy from the wing (3) to the auxiliary motor (7') by operating the latter with a greater reduction ratio than the initial phase.


     
    13. Motorized drive (5, 5") at least according to claim 2, configured to transfer mechanical energy during the closing of the wing (3) by activating:

    - an initial phase in which the second reduction unit (9') transfers mechanical energy from the auxiliary motor (7') to the wing (3) with a reduction ratio;

    - a final phase in which the second reduction unit (9') transfers mechanical energy from the auxiliary motor (7') to the wing (3) with a lower reduction ratio than the initial phase.


     
    14. Movable barrier (1) comprising a wing (3) of door, gate, swing shutter or wall or sliding partition and a motorized drive (5) having the features according to one or more of the preceding claims and configured to open and close said wing.
     


    Ansprüche

    1. Motorischer Antrieb (5, 5"), der zum Öffnen und/oder Schließen eines Flügels (3) einer Barriere wie einer Tür, einer Haupttür, eines Tores oder eines Klappladens, einer Wand oder einer Schiebetrennwand oder eines anderen Schiebeflügels konfiguriert ist, wobei der motorische Antrieb (5) einen Elektromotor (7), eine erste Untersetzungseinheit (9, 9"), durch die der Motor (7) den Flügel (3) zum Öffnen und/oder Schließen desselben betreiben kann, einen elastischen Hilfsenergiemotor (7') umfasst; und wobei:

    - die erste Untersetzungseinheit (9, 9") ein erstes (11, 11") und ein zweites Zahnprofil (13, 13") umfasst, die miteinander in Eingriff stehen, wodurch ein Getriebe mit einem variablen Übersetzungsverhältnis in Abhängigkeit von der Winkel- und/oder linearen Position von mindestens einem der beiden Zahnprofile realisiert wird; und

    - mindestens eines zwischen dem ersten (11, 11") und dem zweiten Zahnprofil (13, 13") mindestens einen Zahnabschnitt mit einem im Wesentlichen unrunden oder nicht durch einen einfachen Kreisbogen oder eine Gerade gebildeten Teilungsprofil bildet

    - der elastische Hilfsenergiemotor (7') eine zweite Untersetzungseinheit (9') umfasst, die wiederum ein erstes (11') und ein zweites Zahnprofil (13') umfasst, die miteinander in Eingriff stehen, um ein Getriebe zu bilden;

    - das erste (11') Zahnprofil der zweiten Untersetzungseinheit (9') und das zweite Zahnprofil (13) der ersten Untersetzungseinheit (9) so konfiguriert sind, dass sie sowohl vom Elektromotor (7) als auch vom elastischen Hilfsenergiemotor (7') betrieben werden können;

    - der motorische Antrieb (5, 5") zum Betreiben des Schließens des Flügels (3) durch die zweite Untersetzungseinheit (9') konfiguriert ist,
    dadurch gekennzeichnet, dass

    - der elastische Hilfsenergiemotor (7') über die zweite Untersetzungseinheit (9') mit dem Flügel (3) verbunden werden kann;

    - das erste (11') Zahnprofil der zweiten Untersetzungseinheit (9') und das zweite Zahnprofil (13) der ersten Untersetzungseinheit (9) auf die gleiche Welle aufgekeilt und/oder einstückig miteinander fixiert sind, sodass die jeweiligen Drehachsen (AX13) und (AX11') zusammenfallen.


     
    2. Antrieb (5, 5") nach Anspruch 1, wobei das erste Zahnprofil (11') so konfiguriert ist, dass es um sich selbst um eine dritte Drehachse (AX11') dreht und ein Teilungsprofil aufweist, das im Wesentlichen die gleiche Form, auch wenn die Abmessungen möglicherweise unterschiedlich sind, in Bezug auf ein Teilungsprofil aufweist, dessen Punkte in einem Abstand (RP1') von der Drehachse liegen, die zwischen den Minimalwerten_1 und den Maximalwerten_1 enthalten sind, die in der folgenden Tabelle 11C angegeben sind
    PunktWinkel α11' [Grad]Radius RP1' Minimalwerte 1 [mm]Radius RP1' Maximalwerte 1 [mm]
    1 0 13,3 24,7
    3 20 12,71095 23,60605
    5 40 11,87613 22,05567
    7 60 11,3428 21,0652
    9 80 10,89914 20,24126
    11 100 10,52128 19,53952
    13 120 10,20474 18,95166
    15 140 9,92131 18,42529
    17 160 9,66196 17,94364
    19 180 9,41563 17,48617
    21 200 9,17308 17,03572
    wobei der Abstand (RP1') und die Teilungsprofile in einer Ebene senkrecht zur dritten Drehachse (AX11') betrachtet werden.
     
    3. Antrieb (5, 5") nach einem oder mehreren der vorhergehenden Ansprüche, wobei das zweite Zahnprofil (13') so konfiguriert ist, dass es entlang einer vierten Achse (AX13') gleitet und ein Teilungsprofil aufweist, das im Wesentlichen die gleiche Form, auch wenn die Abmessungen möglicherweise unterschiedlich sind, in Bezug auf ein Teilungsprofil aufweist, dessen Punkte in einem Abstand (L13') von einer fünften Achse liegen, die zwischen den Minimalwerten_1 und den Maximalwerten_1 enthalten sind, die in der folgenden Tabelle 13C angegeben sind
    Punkt P13'iPosition S; entlang der Achse X [mm]Position L13'i Minimalwerte 1Position L13'i Maximalwerte 1 [mm]
    1 0 4,27161 7,93299
    2 3,3124 4,68552 8,70168
    3 6,6248 5,07283 9,42097
    4 9,9372 5,43354 10,09086
    5 13,2496 5,768 10,712
    6 16,562 6,04198 11,22082
    7 19,8744 6,36167 11,81453
    8 23,1868 6,62361 12,30099
    9 26,4992 6,86476 12,74884
    10 29,8116 7,08743 13,16237
    11 33,124 7,29421 13,54639
    12 36,4364 7,4879 13,9061
    13 39,7488 7,67144 14,24696
    14 43,0612 7,84791 14,57469
    15 46,3736 8,02032 14,89488
    16 49,686 8,19168 15,21312
    17 52,9984 8,36486 15,53474
    wobei die fünfte Achse parallel in Bezug auf die vierte Achse (AX13') ist und der Abstand (L13') und die Teilungsprofile in einer durch die fünfte Achse verlaufenden Ebene betrachtet werden.
     
    4. Antrieb (5, 5") nach Anspruch 2, wobei das erste Zahnprofil (11') ein Teilungsprofil aufweist, das im Wesentlichen die gleiche Form, auch wenn die Abmessungen möglicherweise unterschiedlich sind, in Bezug auf ein Teilungsprofil aufweist, dessen Punkte in einem Abstand (RP1') von der Drehachse liegen, die zwischen den Minimalwerten_2 und den Maximalwerten_2 enthalten sind, die in der folgenden Tabelle 11C angegeben sind
    PunktWinkel α11' [Grad]Radius RP1' Minimalwerte 2 [mm]Radius RP1' Maximalwerte 2 [mm]
    1 0 15,2 22,8
    3 20 14,5268 21,7902
    5 40 13,57272 20,35908
    7 60 12,9632 19,4448
    9 80 12,45616 18,68424
    11 100 12,02432 18,03648
    13 120 11,66256 17,49384
    15 140 11,33864 17,00796
    17 160 11,04224 16,56336
    19 180 10,76072 16,14108
    21 200 10,48352 15,72528

     
    5. Antrieb (5, 5") nach Anspruch 2, wobei das erste Zahnprofil (11') ein Teilungsprofil aufweist, das im Wesentlichen die gleiche Form, auch wenn die Abmessungen möglicherweise unterschiedlich sind, in Bezug auf ein Teilungsprofil aufweist, dessen Punkte in einem Abstand (RP1') von der Drehachse liegen, die zwischen den Minimalwerten_3 und den Maximalwerten_3 enthalten sind, die in der folgenden Tabelle 11D angegeben sind
    PunktWinkel α11' [Grad]Radius RP1' Minimalwerte 3 [mm]Radius RP1' Maximalwerte 3 [mm]
    1 0 17,1 20,9
    3 20 16,34265 19,97435
    5 40 15,26931 18,66249
    7 60 14,5836 17,8244
    9 80 14,01318 17,12722
    11 100 13,52736 16,53344
    13 120 13,12038 16,03602
    15 140 12,75597 15,59063
    17 160 12,42252 15,18308
    19 180 12,10581 14,79599
    21 200 11,79396 14,41484

     
    6. Antrieb (5, 5") nach Anspruch 3, wobei das zweite Zahnprofil (13') ein Teilungsprofil aufweist, das im Wesentlichen die gleiche Form aufweist, auch wenn die Abmessungen möglicherweise unterschiedlich sind, in Bezug auf ein Teilungsprofil, dessen Punkte in einem Abstand (L13') von einer fünften Achse liegen, die zwischen den Minimalwerten_2 und den Maximalwerten_2 enthalten sind, die in der folgenden Tabelle 13C angegeben sind
    Punkt P13'iPosition Si entlang der Achse X [mm]Position L13'i Minimalwerte 2 [mm]Position L13'i Maximalwerte 2 [mm]
    1 0 4,88184 7,32276
    2 3,3124 5,35488 8,03232
    3 6,6248 5,79752 8,69628
    4 9,9372 6,20976 9,31464
    5 13,2496 6,592 9,888
    6 16,562 6,90512 10,35768
    7 19,8744 7,27048 10,90572
    8 23,1868 7,56984 11,35476
    9 26,4992 7,84544 11,76816
    10 29,8116 8,09992 12,14988
    11 33,124 8,33624 12,50436
    12 36,4364 8,5576 12,8364
    13 39,7488 8,76736 13,15104
    14 43,0612 8,96904 13,45356
    15 46,3736 9,16608 13,74912
    16 49,686 9,36192 14,04288
    17 52,9984 9,55984 14,33976

     
    7. Antrieb (5, 5") nach Anspruch 3, wobei das zweite Zahnprofil (13') ein Teilungsprofil aufweist, das im Wesentlichen die gleiche Form aufweist, auch wenn die Abmessungen möglicherweise unterschiedlich sind, in Bezug auf ein Teilungsprofil, dessen Punkte in einem Abstand (L13') von einer fünften Achse liegen, die zwischen den Minimalwerten_3 und den Maximalwerten_3 liegen, die in der folgenden Tabelle 13D angegeben sind
    Punkt P13'iPosition Si entlang der Achse X [mm]Position L13'i Minimalwerte 3Position L13'i Maximalwerte 3 [mm]
    1 0 5,49207 6,71253
    2 3,3124 6,02424 7,36296
    3 6,6248 6,52221 7,97159
    4 9,9372 6,98598 8,53842
    5 13,2496 7,416 9,064
    6 16,562 7,76826 9,49454
    7 19,8744 8,17929 9,99691
    8 23,1868 8,51607 10,40853
    9 26,4992 8,82612 10,78748
    10 29,8116 9,11241 11,13739
    11 33,124 9,37827 11,46233
    12 36,4364 9,6273 11,7667
    13 39,7488 9,86328 12,05512
    14 43,0612 10,09017 12,33243
    15 46,3736 10,31184 12,60336
    16 49,686 10,53216 12,87264
    17 52,9984 10,75482 13,14478

     
    8. Antrieb (5, 5") nach einem oder mehreren der vorhergehenden Ansprüche, wobei das erste Zahnprofil (11') im Wesentlichen als Ritzel oder Kettenrad wirkt.
     
    9. Antrieb (5, 5") nach einem oder mehreren der vorhergehenden Ansprüche, wobei sowohl das erste (11, 11") als auch das zweite Zahnprofil (13, 13") zumindest einen Zahnabschnitt mit einem im Wesentlichen unrunden und weder ausschließlich bogenförmigen noch geraden Teilungsprofil bilden.
     
    10. Antrieb (5, 5") nach einem oder mehreren der vorhergehenden Ansprüche, wobei das zweite Zahnprofil (13') im Wesentlichen als Zahnstange wirkt.
     
    11. Antrieb (5, 5") nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Hilfsmotor (7') ein Motor ist, der durch die Auslösekraft einer Feder (19) oder eines anderen elastischen und/oder pneumatischen oder Energiespeicherelements angetrieben wird.
     
    12. Motorischer Antrieb (5, 5") mindestens nach Anspruch 2, der zum Speichern mechanischer Energie während des Öffnens des Flügels (3) konfiguriert ist, indem Folgendes aktiviert wird:

    - eine Anfangsphase, in der die zweite Untersetzungseinheit (9') mechanische Energie vom Flügel (3) auf den Hilfsmotor (7') überträgt, indem der letztere mit einem Untersetzungsverhältnis betrieben wird;

    - eine Endphase, in der die zweite Untersetzungsgruppe (9') mechanische Energie vom Flügel (3) auf den Hilfsmotor (7') überträgt, indem der letztere mit einem größeren Untersetzungsverhältnis als die Anfangsphase betrieben wird.


     
    13. Motorischer Antrieb (5, 5") mindestens nach Anspruch 2, der zum Übertragen mechanischer Energie während des Schließens des Flügels (3) konfiguriert ist, indem Folgendes aktiviert wird:

    - eine Anfangsphase, in der die zweite Untersetzungseinheit (9') mechanische Energie vom Hilfsmotor (7') mit einem Untersetzungsverhältnis auf den Flügel (3) überträgt;

    - eine Endphase, in der die zweite Untersetzungseinheit (9') mechanische Energie vom Hilfsmotor (7') auf den Flügel (3) mit einem geringeren Untersetzungsverhältnis als die Anfangsphase überträgt.


     
    14. Bewegliche Barriere (1) umfassend einen Flügel (3) von Tür, Tor, Klappladen oder Wand oder Schiebetrennwand und einen motorischen Antrieb (5) mit den Merkmalen nach einem oder mehreren der vorhergehenden Ansprüche, der zum Öffnen und Schließen des Flügels konfiguriert ist.
     


    Revendications

    1. Entraînement (5, 5") motorisé configuré pour ouvrir et/ou fermer un vantail (3) d'une barrière telle qu'une porte, une porte d'entrée, un portail ou un volet battant, une paroi ou cloison coulissante ou un autre vantail coulissant, dans lequel l'entraînement motorisé (5) comprend un moteur électrique (7), une première unité de réduction (9, 9") par le biais de laquelle le moteur (7) peut actionner le vantail (3) en ouvrant et/ou en fermant celui-ci, un moteur auxiliaire (7') à énergie élastique; et dans lequel:

    - la première unité de réduction (9, 9") comprend un premier (11, 11") et un second profil denté (13, 13") mis en prise ensemble, réalisant ainsi un engrenage ayant un rapport de transmission variable en fonction de la position angulaire et/ou linéaire d'au moins l'un des deux profils dentés; et

    - au moins l'un parmi le premier (11, 11") et le second profil denté (13, 13") forme au moins une section dentée ayant un profil de pas qui est sensiblement non circulaire ou qui n'est pas formé par un arc de cercle simple ou une ligne droite

    - le moteur auxiliaire (7') à énergie élastique comprend une seconde unité de réduction (9') qui à son tour comprend un premier (11') et un second profil denté (13') mis en prise ensemble pour former un engrenage;

    - le premier (11') profil denté de la seconde unité de réduction (9') et le second profil denté (13) de la première unité de réduction (9) sont configurés pour être actionnés à la fois par le moteur électrique (7) et par le moteur auxiliaire (7') à énergie élastique;

    - l'entraînement motorisé (5, 5") est configuré pour actionner la fermeture du vantail (3) par le biais de la seconde unité de réduction (9'),
    caractérisé en ce que

    - le moteur auxiliaire (7') à énergie élastique peut être relié au vantail (3) par le biais de la seconde unité de réduction (9');

    - le premier (11') profil denté de la seconde unité de réduction (9') et le second profil denté (13) de la première unité de réduction (9) sont clavetés sur le même arbre et/ou fixés de manière solidaire l'un à l'autre d'une manière telle que les axes de rotation (AX13) et (AX11') respectifs coïncident.


     
    2. Entraînement (5, 5") selon la revendication 1, dans lequel le premier profil denté (11') est configuré pour être en rotation sur lui-même autour d'un troisième axe de rotation (AX11') et possède un profil de pas ayant sensiblement la même forme, même si les dimensions sont éventuellement différentes, par rapport à un profil de pas dont les points sont à une distance (RP1') de cet axe de rotation comprise entre les valeurs minimales_1 et les valeurs maximales_1 indiquées dans le tableau 11C suivant
    PointAngle α11' [degrés]Valeurs minimales 1 du Rayon RP1' [mm]Valeurs maximales 1 du Rayon RP1' [mm]
    1 0 13,3 24,7
    3 20 12,71095 23,60605
    5 40 11,87613 22,05567
    7 60 11,3428 21,0652
    9 80 10,89914 20,24126
    11 100 10,52128 19,53952
    13 120 10,20474 18,95166
    15 140 9,92131 18,42529
    17 160 9,66196 17,94364
    19 180 9,41563 17,48617
    21 200 9,17308 17,03572
    , dans lequel ladite distance (RP1') et lesdits profils de pas sont considérés dans un plan perpendiculaire au troisième axe de rotation (AX11').
     
    3. Entraînement (5, 5") selon l'une ou plusieurs des revendications précédentes, dans lequel le second profil denté (13') est configuré pour coulisser le long d'un quatrième axe (AX13') et possède un profil de pas ayant sensiblement la même forme, même si les dimensions sont éventuellement différentes, par rapport à un profil de pas dont les points sont à une distance (L13') d'un cinquième axe comprise entre les valeurs minimales_1 et les valeurs maximales_1 indiquées dans le tableau 13C suivant
    Point P13'iPosition Si le long de l'axe X [mm]Valeurs minimales 1 de la Position L13'iValeurs maximales 1 de la Position L13'i [mm]
    1 0 4,27161 7,93299
    2 3,3124 4,68552 8,70168
    3 6,6248 5,07283 9,42097
    4 9,9372 5,43354 10,09086
    5 13,2496 5,768 10,712
    6 16,562 6,04198 11,22082
    7 19,8744 6,36167 11,81453
    8 23,1868 6,62361 12,30099
    9 26,4992 6,86476 12,74884
    10 29,8116 7,08743 13,16237
    11 33,124 7,29421 13,54639
    12 36,4364 7,4879 13,9061
    13 39,7488 7,67144 14,24696
    14 43,0612 7,84791 14,57469
    15 46,3736 8,02032 14,89488
    16 49,686 8,19168 15,21312
    17 52,9984 8,36486 15,53474
    , dans lequel ce cinquième axe est parallèle par rapport audit quatrième axe (AX13') et ladite distance (L13') et lesdits profils de pas sont considérés dans un plan passant par ce cinquième axe.
     
    4. Entraînement (5, 5") selon la revendication 2, dans lequel le premier profil denté (11') possède un profil de pas ayant sensiblement la même forme, même si les dimensions sont éventuellement différentes, par rapport à un profil de pas dont les points sont à une distance (RP1') de cet axe de rotation comprise entre les valeurs minimales_2 et les valeurs maximales_2 indiquées dans le tableau 11C suivant
    PointAngle α11' [degrés]Valeurs minimales 2 du Rayon RP1' [mm]Valeurs maximales 2 du Rayon RP1' [mm]
    1 0 15,2 22,8
    3 20 14,5268 21,7902
    5 40 13,57272 20,35908
    7 60 12,9632 19,4448
    9 80 12,45616 18,68424
    11 100 12,02432 18,03648
    13 120 11,66256 17,49384
    15 140 11,33864 17,00796
    17 160 11,04224 16,56336
    19 180 10,76072 16,14108
    21 200 10,48352 15,72528

     
    5. Entraînement (5, 5") selon la revendication 2, dans lequel le premier profil denté (11') possède un profil de pas ayant sensiblement la même forme, même si les dimensions sont éventuellement différentes, par rapport à un profil de pas dont les points sont à une distance (RP1') de cet axe de rotation comprise entre les valeurs minimales_3 et les valeurs maximales_3 indiquées dans le tableau 11D suivant
    PointAngle α11' [degrés]Valeurs minimales 3 du Rayon RP1' [mm]Valeurs maximales 3 du Rayon RP1' [mm]
    1 0 17,1 20,9
    3 20 16,34265 19,97435
    5 40 15,26931 18,66249
    7 60 14,5836 17,8244
    9 80 14,01318 17,12722
    11 100 13,52736 16,53344
    13 120 13,12038 16,03602
    15 140 12,75597 15,59063
    17 160 12,42252 15,18308
    19 180 12,10581 14,79599
    21 200 11,79396 14,41484

     
    6. Entraînement (5, 5") selon la revendication 3, dans lequel le second profil denté (13') possède un profil de pas ayant sensiblement la même forme, même si les dimensions sont éventuellement différentes, par rapport à un profil de pas dont les points sont à une distance (L13') d'un cinquième axe comprise entre les valeurs minimales_2 et les valeurs maximales_2 indiquées dans le tableau 13C suivant
    Point P13'iPosition Si le long de l'axe X [mm]Valeurs minimales 2 de la Position L13'i [mm]Valeurs maximales 2 de la Position L13'i [mm]
    1 0 4,88184 7,32276
    2 3,3124 5,35488 8,03232
    3 6,6248 5,79752 8,69628
    4 9,9372 6,20976 9,31464
    5 13,2496 6,592 9,888
    6 16,562 6,90512 10,35768
    7 19,8744 7,27048 10,90572
    8 23,1868 7,56984 11,35476
    9 26,4992 7,84544 11,76816
    10 29,8116 8,09992 12,14988
    11 33,124 8,33624 12,50436
    12 36,4364 8,5576 12,8364
    13 39,7488 8,76736 13,15104
    14 43,0612 8,96904 13,45356
    15 46,3736 9,16608 13,74912
    16 49,686 9,36192 14,04288
    17 52,9984 9,55984 14,33976

     
    7. Entraînement (5, 5") selon la revendication 3, dans lequel le second profil denté (13') possède un profil de pas ayant sensiblement la même forme, même si les dimensions sont éventuellement différentes, par rapport à un profil de pas dont les points sont à une distance (L13') d'un cinquième axe comprise entre les valeurs minimales_3 et les valeurs maximales_3 indiquées dans le tableau 13D suivant
    Point P13'iPosition Si le long de l'axe X [mm]Valeurs minimales 3 de la Position L13';Valeurs maximales 3 de la Position L13'i [mm]
    1 0 5,49207 6,71253
    2 3,3124 6,02424 7,36296
    3 6,6248 6,52221 7,97159
    4 9,9372 6,98598 8,53842
    5 13,2496 7,416 9,064
    6 16,562 7,76826 9,49454
    7 19,8744 8,17929 9,99691
    8 23,1868 8,51607 10,40853
    9 26,4992 8,82612 10,78748
    10 29,8116 9,11241 11,13739
    11 33,124 9,37827 11,46233
    12 36,4364 9,6273 11,7667
    13 39,7488 9,86328 12,05512
    14 43,0612 10,09017 12,33243
    15 46,3736 10,31184 12,60336
    16 49,686 10,53216 12,87264
    17 52,9984 10,75482 13,14478

     
    8. Entraînement (5, 5") selon l'une ou plusieurs des revendications précédentes, dans lequel le premier profil denté (11') agit sensiblement comme un pignon ou une roue dentée.
     
    9. Entraînement (5, 5") selon l'une ou plusieurs des revendications précédentes, dans lequel à la fois le premier (11, 11") et le second profil denté (13, 13") forment au moins une section dentée ayant un profil de pas qui est sensiblement non circulaire et qui n'est ni exclusivement un arc de cercle ni droite.
     
    10. Entraînement (5, 5") selon l'une ou plusieurs des revendications précédentes, dans lequel le second profil denté (13') agit sensiblement comme une crémaillère.
     
    11. Entraînement (5, 5") selon l'une ou plusieurs des revendications précédentes, dans lequel le moteur auxiliaire (7') est un moteur entraîné par la force de relâchement d'un ressort (19) ou d'un autre élément élastique et/ou pneumatique ou de stockage d'énergie.
     
    12. Entraînement (5, 5") motorisé au moins selon la revendication 2 configuré pour stocker de l'énergie mécanique pendant l'ouverture du vantail (3) en activant:

    - une phase initiale au cours de laquelle la seconde unité de réduction (9') transfère de l'énergie mécanique du vantail (3) au moteur auxiliaire (7') en actionnant ce dernier avec un rapport de réduction;

    - une phase finale au cours de laquelle le second groupe de réduction (9') transfère de l'énergie mécanique du vantail (3) au moteur auxiliaire (7') en actionnant ce dernier avec un plus grand rapport de réduction que lors de la phase initiale.


     
    13. Entraînement (5, 5") motorisé au moins selon la revendication 2 configuré pour transférer de l'énergie mécanique pendant la fermeture du vantail (3) en activant:

    - une phase initiale au cours de laquelle la seconde unité de réduction (9') transfère de l'énergie mécanique du moteur auxiliaire (7) au vantail (3') avec un rapport de réduction;

    - une phase finale au cours de laquelle la seconde unité de réduction (9') transfère de l'énergie mécanique du moteur auxiliaire (7) au vantail (3') avec un plus petit rapport de réduction que lors de la phase initiale.


     
    14. Barrière mobile (1) comprenant un vantail (3) de porte, de portail, de volet battant ou de paroi ou cloison coulissante et un entraînement (5) motorisé ayant les caractéristiques selon l'une ou plusieurs des revendications précédentes et configuré pour ouvrir et fermer ledit vantail.
     




    Drawing



















































































    Cited references

    REFERENCES CITED IN THE DESCRIPTION



    This list of references cited by the applicant is for the reader's convenience only. It does not form part of the European patent document. Even though great care has been taken in compiling the references, errors or omissions cannot be excluded and the EPO disclaims all liability in this regard.

    Patent documents cited in the description