EP2308154A2

EP2308154A2 - Tubular motor for roll-up shutters and the like

Info

Publication number: EP2308154A2
Application number: EP09772298A
Authority: EP
Inventors: Andrea Malausa; Lorenzo Galberti
Original assignee: Nice SpA
Current assignee: Nice SpA
Priority date: 2008-06-30
Filing date: 2009-06-12
Publication date: 2011-04-13
Also published as: ITPN20080055A1; WO2010000598A3; WO2010000598A2

Abstract

The invention relates to a tubular motor (20) adapted to drive a roller (DR), on which sliding or roll-up shutters (TP), roller blinds, or the like, as typically used in connection with windows and doors, can be rolled up, comprising a head (22) and a tubular body (24). The head in turn comprises a first gear ring (G1 ) mounted externally and in a rotatable manner on said head, so as to be able to receive rotary motion from the roller, and provided with a first toothing (TH1), and a second gear ring (G2) mounted internally in said head and provided with a second toothing (TH2), wherein said second toothing is operatively connected with said first toothing, and said second gear ring is operatively connected with an end-of- travel or stop device (S) provided inside the head, so as to be able to transmit a rotary motion corresponding to the rotation of the roller to said device. In view of reducing the size of the gear motor and cutting costs, said first and second toothings extend along circumferences that have different diameters.

Description

TUBULAR MOTOR FOR ROLL-UP SHUTTERS AND THE LIKE

DESCRIPTION

The present invention relates to a tubular motor for roll-up shutters, roller blinds, and the like, adapted to rotatably drive a roller, on which sliding or roll-up shutters, roller blinds, or the like, as typically used in connection with windows and doors, can be rolled up.

Home automation, as well as industrial automation, includes applications enabling blinds, shutters and similar door and window covers to be driven and handled without any effort with the help of a tubular motor reducer, or gearmotor, which is fitted into and connected inside the roller on which the shutter, blind or the like is due to roll up.

A gearmotor 20 of the above-noted kind is made up (cf. Figure 1 and, for instance, also WO2006045724) by having a head 22, which contains appropriate control devices (of either a mechanical or an electronic kind), duly joined with a tubular body 24 firmly connected/secured thereto, said tubular body containing the electric drive motor and a mechanical speed-reducer, or speed-reducing gears. At an end portion thereof, the head 22 features a base 26 for attachment - either directly or via an appropriate support (not shown) interposed therebetween - to the building wall W; at the opposite end portion thereof, it is provided with a cylindrical body 28, onto which the tubular body 24 is fitted. At the opposite end portion of the tubular body 24 there is protruding the output shaft 30 of the drive motor, which is connected to a roller DR via an appropriate adapter 31. The roller DR, on which a shutter or blind TP is able to roll up, interacts with an internally toothed ring gear G that is rotatably shrink-fitted, or press-fitted, onto the cylindrical body 28. The ring gear G transmits the rotary motion of the roller DR into the cylindrical body 28, where an end-of-travel detector S (Stop) of an either mechanical or electronic kind is adapted to count the number of revolutions of the roller DR, thereby monitoring the position of the shutter or blind TP. The detector S is firmly joined with the cylindrical body 28 and is placed therewithin. As it may be readily appreciated, the actual purpose of such detector is to cut off the operation of the electric drive motor when the shutter or blind TP reaches up or down to a pre-defined upper or lower end-of-travel position, respectively.

A typical feature of drive systems of the above-noted kind is given by the fact the shutter or blind TP must necessarily be able to be rolled up or down even under power failure or motor failure conditions, i.e. when there is no power supply or the drive motor somehow fails to operate.

To cope with circumstances of this kind, use is therefore made of a purpose-fit device that is built into the base 26, along with a turning rod adapted to be inserted in said device in the base 26. When this rod is turned, either manually or with the help of a screwer as commonly used in the art, this causes the cylindrical body 28, the tubular body 24, the output shaft 30 of the motor, the adapter and, as a result, even the roller DR to rotate relative to the base 26, whereas the body 28 and the tubular body 24 keep motionless on the base 26, i.e. relative to the latter, under regular operating conditions, i.e. when movement is regularly generated by the electric drive motor.

The above-described operation is generally and technically termed as "override or fast-help manoeuvre" in the art.

It is anyway absolutely necessary to ensure that the detector S is able to correctly "count" the position of the shutter or blind TP in both in both operating conditions and modes of the system, i.e. when the electric drive motor is regularly operating and when the need arises for the "override or fast-help manoeuvre" to be used, instead. To such purpose use is therefore made of ingeniously contrived geared mechanisms, which involve both the cylindrical body 28 and the gear ring G and include parts that shall be described in greater detail below.

In this description, some reference numerals are kept unvaried to specially indicate correspondence with the illustration in Figure 1 , while the suffixes "a" and "b" will be used to distinguish different solutions belonging to the prior art. With reference to Figures 5 to 8, an internally toothed gear ring Ga (rinG) is mounted externally on a cylindrical body 28a in a rotatable manner relative thereto, so that an internal toothing THa (TootHing) thereof is able to mesh with a small toothed wheel or spur gear WHa hinged on within a slot SLa of the cylindrical body 28a (Figures 7 and 8). Such spur gear WHa in turn meshes with a first internal toothing TH-Ia (TootHing Inner) of a second gear ring G-Ia (ring Inner) rotatably placed within the cylindrical body 28a and giving a second toothing TH- 12a, with which it is able to mesh with a toothed wheel WHSa (Wheel Stop) that transmits the rotary motion to the end-of-travel device S (not shown in these Figures), which, while being still provided inside the cylindrical body 28a, is however secured to the base 26. In this connection, reference should be specially made to Figures 5 and 6, in which the sole gears are shown for reasons of greater perspicuity. The cylindrical body 28a has an annular thickening or annularly protruding portion 29a with an external toothing (not shown), upon which the turning rod used to perform the afore-cited override or fast-help manoeuvre is able to act, and with which the cylindrical body 28a is caused to rotate on the - in all cases stationary - base 26. As a result, even the tubular body 24 (Figure 1 ) and the roller DR are caused to rotate (the output shaft 30 is locked by the non- operating or turned-off motor).

It should be noticed that, even in this case, the gear ring Ga still "reports" the revolutions of the roller DR to the detector S. In fact, by rotating the cylindrical body 28a, via the chain [tubular body 24 -> output shaft 30 -> adapter -> roller DR] also the gear rings Ga, G-Ia, which behave as if they were firmly joined with each other, are caused to rotate. As far as the small toothed wheel or spur gear WHSa is concerned, a rotation of the gear ring G-Ia is the same regardless of the roller DR rotating owing to its being driven by the electric motor or manually by an aforecited override or fast-help manoeuvre. This practically ensures that the end-of- travel device S is in all cases able to always and unvaryingly detect and count in the same manner the revolutions performed by the roller DR.

A second kind of construction, which differs slightly from the above-described one, but is still based on the same principle, is illustrated in Figures 9 to 12, in which the same reference numerals are used to indicate similar parts and details functionally corresponding to the ones used in the preceding case (except that the suffix "b" is used for the parts that are typical of this second embodiment). In this case, the gear rings Gb and C-Ib have their toothings provided in different positions as compared with the previously discussed case; however, the overall operating mode is substantially the same: the gear ring Gb rotates on the cylindrical body 28b and causes, with a toothing THb thereof, the small toothed wheel or spur gear WHb to rotate accordingly; this toothed wheel or spur gear WHb causes in turn an inner gear ring G-Ib to rotate, which again causes a gear wheel WHSb to rotate. As in the previously discussed case, under power failure or failed motor conditions, the cylindrical body 28b is driven in the override mode, i.e. with a manual fast-help manoeuvre, to thereby cause the gear wheel WHSb, which is connected to the end-of-travel or stop device S, to rotate.

It can be noticed that the gear rings Ga, G-Ia, Gb, G-Ib are provided in a juxtaposed, i.e. side-by-side arrangement relative to each other, and that the respective toothings THa, THb, TH-Ia, TH-Ib thereof are distributed over a circumference having the same radius. In the first embodiment, such toothings are of an external kind; in the second embodiment, they are of the internal type.

Furthermore, the toothings THa and TH-Ia, THb and TH-Ib have the same circumference, the same number of teeth and the same diametral pitch or module.

Although these systems are largely known to be quite good and effective in working, there is however a constant need arising for the size of the head 22 to be reduced as far as possible. In other words, reducing the size by even a few centimetres, or fraction thereof, practically means that the possibility is created for additional component parts to be accommodated there and/or the same head to be more conveniently fitted in place in building constructions that are increasingly requiring compact parts and small dimensions to be installed there.

In addition, reducing the size of the head allows for material to be saved under beneficial effects on the overall costs of the drive system altogether.

It is therefore a main object of the present invention to provide a device of the afore-noted kind, which is very compact in size and has correspondingly reduced space requirements for installation.

According to the present invention, such aim is reached (cf. Figures 2 to 4) in a tubular motor adapted to drive a roller, on which sliding or roll-up shutters, roller blinds, or the like, as typically used in connection with windows and doors, can be rolled up, and comprising a head and a tubular body, wherein such head in turn comprises:

- a first gear ring G1 mounted externally on and in a rotatable manner relative to said head, so as to be able to receive rotary motion from the roller, and provided with a first toothing TH1 , and

- a second gear ring G2 mounted internally on said head and provided with a second toothing TH2, said second toothing being operatively connected with said first toothing, and said second gear ring being operatively connected with an end- of-travel or stop device S provided inside the head so as to be able to transmit a rotary motion corresponding to the rotation of the roller to said device, characterized in that said first and second toothings TH1 , TH2 extend along circumferences that have different diameters.

Comparing Figures 5 to 12 (prior art) with Figures 2 to 4 (present invention) enables the features of the invention to be most clearly recognized. In particular, special attention should be devoted to the geometrical relation existing between the respective toothings TH1 and TH2 of two gear rings G1 , G2 used in the mechanism according to the present invention.

Therefore, the size and/or the arrangement of the gear rings G1 , G2 is/are effective in drastically reducing the dimensions of the head both lengthwise and crosswise, while keeping the quality-related properties thereof unaltered.

The significant compactness of the mechanism according to the present invention and the resulting space saving effect both in the axial and the transverse direction as compared with prior-art devices can be most readily appreciated. Further advantages are:

- reduced costs due to lower material usage;

- possibility for motors to be used also in applications requiring or involving small build-in dimensions, such as for example in the case of blinds or shutters rolling up inside a related box;

- the same box can be made to a more compact size, owing exactly to the motor installed thereinside being smaller.

The invention may be embodied in a number of different manners, e.g.

- the first and second gear rings may be provided concentrically inside each other, i.e. one inside the other, so as to have a symmetric system;

- the second gear ring may have the second toothing and the third toothing extending along circumferences of a same diameter (thereby maximizing manufacturing simplicity and convenience, and cutting overall costs owing to greater simplicity in providing the required die);

- the second toothing of the second gear ring may be provided externally, while the third toothing may on the contrary be provided internally (for greater effectiveness in operation);

- the third toothing may transfer rotary motion to a gear wheel provided in communication with the end-of-travel or stop device S;

- the motor may comprise two gears (W1 , W2) having parallel axes and meshing with each other, adapted to enable rotary motion to be transferred from the first gear ring to the second gear ring by meshing with the respective toothings thereof (minimization of space requirements: the size of the gear rings G1 , G2 and, as a result, the position of the gears W1 and W2 depend on the size and bulk of the end-of-travel or stop device S placed thereinside, so that modifying the latter would possibly enable the size of the gear rings G1 , G2 to be modified accordingly);

- the axes of the two gears (W1 , W2) may be provided to lie at different distances from the axis of rotation of the two gear rings;

- the first and second toothings may feature a different diametral pitch or module and the one (W2) of the two gears that meshes with the second gear ring G2 may be double, in the sense that it may have two toothings of differing diametral pitch or module, wherein one of said two diametral pitches, or modules, is equal to the one of the second toothing;

- the motor may comprise a surface slot on the body of the head to accommodate the body of said two gears; - the toothings TH1 , TH2 of the gear rings G1 , G2, which are operatively connected with each other, may lie along substantially co-planar circumferences (in view of optimizing miniaturization).

Features and advantages of the present invention will anyway be more readily understood from the description of a preferred embodiment that is given below by way of non-limiting example with reference to the accompanying drawings, in which:

- Figure 1 is a simplified schematic view of a drive system;

- Figure 2 is a cross-sectional view along the plane M-Il of Figure 3;

- Figure 3 is a front view of two gear rings according to the present invention;

- Figure 4 is a cross-sectional view along the plane IV-IV of Figure 3;

- Figure 5 is a perspective view of two gear rings as used in a tubular motor head according to the prior art;

- Figure 6 is a vertical cross-sectional view of the assembly shown in Figure 5;

- Figure 7 is an exploded view of a part of a prior-art tubular motor head, the same one as shown in Figures 5 and 6;

- Figure 8 is a view of the head shown in Figure 7, as viewed in the assembled state thereof;

- Figure 9 is a perspective view of two gear rings as used in another tubular motor head according to the prior art;

- Figure 10 is a vertical cross-sectional view of the assembly shown in Figure 9; - Figure 11 is a view of the head shown in Figure 12, as viewed in the assembled state thereof;

- Figure 12 is an exploded view of a part of a prior-art tubular motor head, the same one as shown in Figures 9 and 10;

- Figure 13 is an exploded view of a part of a tubular motor head according to the present invention;

- Figure 14 is a view showing in a slightly enlarged scale the component parts of the tubular motor head illustrated in Figure 13, as viewed in the assembled state thereof;

- Figure 15 is an enlarged view of a detail of Figure 14.

In the illustrations of Figure 13 et seq., there can be noticed a cylindrical body CC of a motor head according to the present invention. Not shown is on the contrary the stationary base (of a kind as is largely known as such in the art; cf. detail indicated at 26 in Figure 1 ), on which the cylindrical body CC is mounted in a rotatable manner; however, substantial correspondence to Figure 1 is maintained as far as the reference numerals used to indicate the various parts are concerned (under sole addition of the differentiating prefix 1 in this case). Reference should additionally be made to Figures 2 to 4.

The above-cited cylindrical body CC is comprised of a tubular casing 128, on which there is rotatably fitted a gear ring G1 having a slightly larger diameter and featuring an internal toothing TH1. At an end portion of said tubular casing 128 there is provided a flange 129 with a toothing (not shown) on the surface thereof, upon which there is due to act a worm screw (not shown, either) arranged orthogonally thereto and adapted to be actuated directly by the user during a "fast- help override manoeuvre" as explained afore. In the proximity of the flange 129, the tubular casing 128 has an aperture 140 in which there are rotatably accommodated and hinged, with the aid of pegs 168, two gear wheels W1 and W2 provided in a side-by-side arrangement, such wheels having mutually interacting toothings that protrude both outwards from and inwards into the tubular casing 128. The gear wheels W1 , W2 have the axis of rotation thereof extending along a same arc of circumference.

When the gear ring G1 is fitted onto the tubular casing 128 (Figures 14 and 15), the toothing TH1 thereof is able to mesh with the one of the gear wheel W1 , but not with the one of the gear wheel W2, since this is smaller, actually. Furthermore, the gear wheel W2 has a second co-axial toothing TW2 having a same number of teeth, but a smaller diameter (double gear, with two different diametral pitches or modules).

Inside the tubular casing 128, close to the slot 140, there is placed a second gear ring G2 having an external toothing TH2 and an internal toothing TH3. The toothing TH2 and the diametrical dimensions of the gear ring G2 are such as to ensure effective meshing with the toothing TW2 of the gear wheel W2. On the contrary, the toothing TH3 meshes with an inner gear WHST that is connected to an end-of-travel or stop device S housed within the tubular casing 128.

Ultimately, the above-described gear system is effective in ensuring correct transmission of the number of revolutions being performed by the roller DR to the end-of-travel or stop device S both when the electric drive motor is operating regularly and during manually performed "fast-help override manoeuvres".

Normally, the roller DR causes the gear ring G1 to rotate and the latter transmits, at a 1 -to-1 ratio, its own number of revolutions to the gear ring G2. Via the toothing TH3, the gear ring G2 is then able to transmit a certain number of revolutions on to the gear WHST, which conveys it to the end-of-travel device S. During a "fast-help override manoeuvre", the gear ring G1 behaves as if it were firmly joined to the tubular body 128 that is being rotated manually. As a result, via the gears W1 , W2 said tubular body 128 causes the gear ring G2 and, jointly therewith, the gear WHST to rotate. In both cases, to a same angular displacement of the roller DR there corresponds the same number of revolutions on the gear WHST.

Claims

-CLAIMS

1. Tubular motor (20) adapted to drive a roller (DR), on which sliding or roll-up shutters (TP), roller blinds, or the like, as typically used in connection with windows and doors, can be rolled up, comprising a head (22) and a tubular body (24), said head in turn comprising:

- a first gear ring (G1 ) mounted externally and in a rotatable manner on said head, so as to be able to receive rotary motion from the roller, and provided with a first tooth ing (TH 1 ), and

- a second gear ring (G2) mounted internally in said head and provided with a second toothing (TH2), said second toothing being operatively connected with said first toothing, and said second gear ring being operatively connected with an end- of-travel or stop device (S) provided inside the head, so as to be able to transmit a rotary motion corresponding to the rotation of the roller to said device, characterized in that said first and second toothings extend along circumferences that have different diameters.

2. Tubular motor according to claim 1 , wherein said first and second gear rings are arranged concentrically inside one another.

3. Tubular motor according to claim 1 or 2, wherein the second gear ring (G2) comprises a third toothing (TH3) that is operatively connected with said end-of- travel device.

4. Tubular motor according to claim 3, wherein the second gear ring has the second and third toothings thereof extending along circumferences of equal diameter.

5. Tubular motor according to claim 3 or 4, wherein the second toothing (TH2) of the second gear ring (G2) extends externally, whereas the third toothing (TH3) extends internally.

6. Tubular motor according to any of the claims 3 to 5, wherein the third toothing (TH3) transfers rotary motion to a gear wheel (WHST) that is provided in communication with the end-of-travel device (S).

7. Tubular motor according to any of the preceding claims, comprising two gears (W1 , W2), having parallel axes and meshing with each other, adapted to enable rotary motion to be transferred from the first gear ring to the second gear ring by the meshing of the respective toothings thereof.

8. Tubular motor according to claim 7, wherein the axes of the two gears (W1 , W2) are provided at different distances from the axis of rotation of the two gear rings.

9. Tubular motor according to claim 7 or 8, wherein the first and second toothings (TH1 , TH2) feature a different diametral pitch, or module, and the one (W2) of said two gears that meshes with the second gear ring (G2) is double, in the sense that it has two toothings (W2, TW2) of differing diametral pitch or module, one of said two diametral pitches, or modules, being equal to the one of the second toothing.

10. Tubular motor according to any of the claims 7 to 9, comprising a surface slot (140) on the body of the head to accommodate the body of said two gears (W1 , W2).

11. Tubular motor according to any of the preceding claims, wherein the toothings (TH1 , TH2) of the gear rings (G1 , G2), which are operatively connected with each other, lie along substantially co-planar circumferences.