EP1844210B1 - Device for braking the rotation of a drive shaft of the leaf of a high-speed door - Google Patents

Description

The present invention relates to a tree braking device of a flexible or rigid and articulated apron of a rapid industrial, commercial, domestic or garage door.

To close an opening made in a partition separating two spaces, it is possible to use a fast door having a flexible apron that winds or folds at the lintel of the door. This type of door has the advantage of being able to open and close very quickly with a speed greater than 0.5 m / s. Such a door is particularly suitable for equipping a bay through which a large traffic flows.

To move the deck, the door is equipped with a drive kinematic chain that can rotate a shaft on which can roll the deck directly or on which can wrap the straps that allow the folding of the deck.

The kinematic chain generally comprises an electric motor which, via a gearbox, drives the shaft in rotation.

Of course, the elements of the drive train are dimensioned to undergo a very large number of cycles. Nevertheless, one can deplore a mechanical break in the gearbox, a breakage of a coupling between the shaft and the gearbox, etc ...

In such a case, the tree is no longer controlled; he is then completely free in rotation. Under the effect of gravity, the deck can then fall suddenly since the tree to which the deck is bound is no longer able to control the fall of the latter.

There is a risk of accident if, simultaneously with the fall of the deck, a person through the door and is in the path of the deck.

The document WO 2006/082319 A describes a braking device according to the preamble of claim 1.

An object of the invention is to provide a braking device for a fast door flexible apron securing the operation thereof especially in case of a mechanical failure of its kinematic drive chain.

The subject of the invention is essentially a braking device according to the wording of claim 1.

The idea underlying the invention is to detect an increase in the speed of rotation of the shaft beyond a predetermined threshold. In practice, the increase in the speed of rotation of the shaft occurs in case of breakage of an element of the driving kinematic chain, so that the shaft is completely free to rotate and is driven by the weight of the apron. If the shaft is driven in overspeed, it induces a displacement of the weights that actuate braking means.

A specificity of flexible deck doors lies in the fact that they have a high normal operating speed. The breaking of the kinematic drive chain induces an overspeed which is however not significantly greater than the normal operating speed. In other words, the speed differential of the shaft between its normal operation and abnormal operation is not considerable. This is why each cavity is equipped with means for defining two operating modes of the weights, namely a normal operating regime in which the weight is maintained in an area comprising the proximal end of the cavity and an abnormal operating regime in which the movement of the weight is favored to operate the braking means.

In case of overspeed of the shaft and, therefore, the braking device, the centrifugal force that applies to the weight causes it to pass the protruding zone to reach the distal portion of the cavity. This distal portion, which has a less acute angle than the proximal portion, offers little restraint to the weight which can then actuate the braking means.

In another embodiment, each cavity has, on its wall on which the counterweight bears in operating condition, a rib which separates the distal end from the proximal end, the rib on which the counterweight is operating. normal of the door. The presence of this rib is then combined with the characteristic that the proximal and distal portions have radially increasing angles.

In another embodiment, ruptible means hold the flyweight at the proximal portion of the cavity, these ruptible means are likely to break in abnormal operation of the door releasing the weight to the proximal portion of the cavity.

It can be envisaged that the ruptible means consist of a wire whose resistance makes it possible to collect the centrifugal force applied to the flyweight operating at normal speed of the shaft but does not allow to collect the centrifugal force applied to the flyweight. in abnormal operation.

According to one possibility, the braking means comprise a movable assembly radially or axially on which the flyweights act, and a fixed assembly on which the movable assembly can come into contact by friction and / or meshing to slow the rotation of the shaft.

In one embodiment, each cavity receiving a flyweight has at its distal end a radially movable finger that can occupy a retracted position in which the finger is held by a spring or can occupy an extended position under the effect of a push by a weight, the finger in the extended position can engage in a light formed in a fixed disc. This embodiment has the advantage of involving only a small number of moving parts.

In another embodiment, each cavity receiving a flyweight is delimited by the wall formed in the flange by a wall of an axially movable assembly between a normal speed operating position in which the moving assembly is pushed towards the cavity by elastic means and an operating position at a speed exceeding a predetermined threshold in which each feeder axially pushes the moving assembly against a fixed disk. In this embodiment, the displacement of the flyweights is converted into an axial movement of a moving assembly which carries out the locking of the device cooperating with a fixed disk.

The braking can then be achieved through the characteristic that the movable assembly has, on a wall opposite its wall facing the cavity, at least one tooth capable of meshing with a tooth protruding from the fixed disk.

Preferably, the teeth of the movable assembly and the teeth of the fixed disk are against undercut and disengaged after their meshing only by a reverse rotation of the shaft. Thus, it is necessary that there is human intervention to unlock the rotation of the tree.

Blocking can also be achieved thanks to the characteristic that the axially movable assembly has on its wall opposite to its wall facing each cavity, a convergent frustoconical ring on which at least one pivoting lever rests, having a hook to its free end, the lever being pivotable between an operating position at normal speed of the shaft and a position of running at a speed of the shaft exceeding a predetermined threshold in which the ring presses each lever to rotate it to pick a fixed bar.

One can, moreover, consider to provide a slowing of the rotation of the device before its complete braking. For this purpose, the axially movable assembly has on its wall opposite its wall facing the cavity a seal that can frictionally brake the rotation against a fixed element.

To ensure its axial movement relative to its axis, the device comprises a linear ball bearing for sliding the movable assembly relative to the axis.

It should also be noted that the device may comprise means of connection with a control unit making it possible to postpone triggering of the device.

• Figure 1 représente, de façon schématique, une porte équipée d'un dispositif de freinage agissant sur un arbre lorsque la vitesse de rotation de l'arbre dépasse sa vitesse normale de fonctionnement,
• Figures 2 à 5 représentent en perspective avec une coupe partielle une forme de réalisation du dispositif de freinage dans plusieurs configurations de fonctionnement de celui-ci,
• Figures 6 à 9 représentent en perspective avec une coupe partielle une autre forme de réalisation du dispositif de freinage dans plusieurs configurations de fonctionnement de celui-ci,
• Figure 10 représente à une echelle agrandie un détail du dispositif de freinage représenté aux Figures 6 à 9,
• Figure 11 à 14 représentent en perspective avec une coupe partielle une autre forme de réalisation du dispositif de freinage dans plusieurs configurations de fonctionnement de celui-ci,

For a good understanding, the invention is described with reference to the accompanying drawing showing, by way of non-limiting example several embodiment of a braking device according thereto according thereto.

• Figure 1 schematically represents a door equipped with a braking device acting on a shaft when the speed of rotation of the shaft exceeds its normal operating speed,
• Figures 2 to 5 show in perspective with partial section an embodiment of the braking device in several operating configurations thereof,
• Figures 6 to 9 show in perspective with a partial section another embodiment of the braking device in several operating configurations thereof,
• Figure 10 represents on an enlarged scale a detail of the braking device shown in Figures 6 to 9 ,
• Figure 11 to 14 show in perspective with a partial section another embodiment of the braking device in several operating configurations thereof,

For simplicity, the elements found in these different embodiments, or which are similar from one embodiment to another, are designated by the same reference numerals.

Conventionally, a rapid door intended to close a bay in a partition has two uprights 2 which are generally each connected at their upper end by a transverse cover 3.

One of the uprights 2 supports drive means of a shaft 4 which are inside the transverse cover 3. The drive means generally comprise an electric motor 5 and a gear 6 which provide the link with the drive. tree 4.

In the illustrated example of the door, an apron is suspended from the shaft 4; the apron winds on the shaft 4 to clear the passage and unrolls the shaft 4 to close the passage.

Another way of moving the deck is to hang the deck on the uprights 2 and provide straps one end of which is connected to the shaft 4 and whose other end is connected to the threshold of the deck. During the rotation of the shaft 4, the straps are wound on the shaft and thus raise the apron that folds below the transverse cover.

The specificity of the door according to the invention lies in the fact that a braking device 8 is disposed at the end of the shaft.

We will refer first to Figures 2 to 5 which illustrate a first embodiment of the device. As shown in figure 2 , the braking device 8 has an axis 9 which, at its free end, has a hexagonal section; it can be engaged in a housing of the same section made in the shaft 4 of the door.

The device has an axially movable assembly 11 which is rotated with the axis 9.

This mobile assembly 11 comprises a sleeve 10 which is engaged on the axis 9 and is secured thereto by a key 15. Axially, the sleeve 10 is stopped by an elastic ring.

The sleeve 10 receives a support sleeve 12 on which is fixed a disc 13. This disc 13 is equipped with several radial teeth 14 whose function will appear later. Note however that the teeth 14 have a profile against undercut.

A point that is important to note is that a linear ball bearing 16 is interposed between the sleeve 10 and the intermediate sleeve 12.

Thus, the movable assembly 11 is rotated by the axis 9 and is capable of axial displacement thanks to the ball bearing 16 linear. The axial displacement of the moving assembly 11 is limited by a spring 21 disposed axially with the axis 9.

A flange 17 engaged on the axis 9 makes it possible to enclose several flyweights 18 - in the example represented the flyweights 18 are six in number - which bear against the disc 13 of the moving assembly 11. As can be seen see FIGS, each weight 18 is enclosed in a cavity 19. The cavity 19 is, in the embodiment shown, defined by a wall of the movable assembly 11 and a wall 20 formed in the flange 17. This wall is very characteristic since as can be seen it has two successive parts, namely a proximal portion which is close to the axis of rotation of the axis 9 and a distal portion 20b which moves away from this axis . The flange 17 is integral in rotation with the axis 9 by the key 15.

The specificity of the wall 20 is that the proximal portion 20a forms a first angle with the axis of rotation and the distal portion 20b forms a second angle with the axis of rotation, this second angle being greater than the first.

It is also noted that a projecting zone 22 separates the distal portion from the proximal portion.

The device also has a fixed assembly which, in the example shown, is a disc which has four teeth having a profile against undercut.

The operation of the braking device is therefore as follows.

Figure 2 shows the device at rest, the flyweight 18 then rests at the proximal end of the cavity 19.

When the door is in action and, therefore, that the shaft 4 rotates to raise or lower the curtain, the weight 18 is subjected to a centrifugal force which thus moves away from the axis of rotation and puts bearing against the projecting zone 22 of the wall 20 of the cavity 19. This normal operating state of the door is illustrated by the figure 3 .

On the other hand, if the speed of rotation increases beyond a predetermined threshold, the centrifugal force which increases because of the speed pushes the weight 18 beyond the projecting zone 22 of the cavity 19. The figure 4 shows this state.

The weight 18 is then supported on the distal portion of the cavity. This has a relatively obtuse angle, the flyweight 18 reaches the distal end of the cavity 19 and pushes the movable assembly towards the fixed disk.

As shown then figure 5 the respective teeth 14, 24 of the movable assembly 11 and the fixed disk 23 mesh with each other and makes a mechanical connection between the moving assembly 11 and the fixed disc 23, thereby blocking the rotation of the device and therefore of the shaft.

Figures 6 to 9 show an alternative embodiment of the device which also has an axially movable assembly 25 under the action of the flyweights 18. The main difference to the mobile assembly described above is that the moving assembly 25 has, on its wall opposite its wall in view of the cavity 19, a frustoconical ring 26.

The means, permitting the axial displacement of the moving assembly 25 are similar to those allowing the displacement of the moving assembly 11 and the flange 17 with its cavities 19 enclosing weights 18 is similar to that of the device of the Figures 2 to 5 .

It can also be seen that levers 27 are embarked on the braking device. These levers 27 are eccentric with respect to the axis of rotation and can pivot relative to respective axes 28, parallel to the axis of rotation of the device. Each lever 27 has, at its free end, a hook 30.

It is also noted that several fixed bars 29, six in number in the illustrated example, are placed around the braking device.

The operation of the device in this embodiment is as follows.

Figure 6 shows the device at rest; the weight 18 then rests against the proximal end of the cavity.

Figure 7 shows the device in normal operating mode; the weight 18 is then in abutment against the projection zone 22 of the cavity and against the wall of the moving assembly 25.

Figure 8 shows the device at the beginning of abnormal operating regime, that is to say in case of overspeed of the door shaft; the flyweight 18 pushed by the centrifugal force, exceeds the projecting zone 22 and then pushes the movable assembly 25 in an axial direction.

The figure 9 then illustrates the displacement of the movable element. This displacement has the effect of producing a rotation of the levers 27 because the frustoconical ring acts as a ramp on which the levers 27 rest. During rotation, each lever 27 comes, thanks to its hook 28, to pick a fixed bar 29, which interrupts the rotation of the device and thus of the shaft 4. The device then interrupts the rotation of the shaft 4.

The device of Figures 10 to 14 differs from the two previous embodiments in that a movable assembly 31 moves radially.

In this embodiment there is a flange 1 7 in which are arranged several cavities 19 containing flyweights. Each cavity 19, like the cavities of the two previous embodiments has a proximal portion 20a and a distal portion 20b, separated by a projecting zone 22, the distal portion forming an angle more open with the axis of rotation than the proximal part.

As regards the braking means, these are constituted by a movable element 31 radially engageable with a fixed element.

The movable element 31 has a radially movable pin 32 capable of occupying a retracted position 31 in which the finger 32 is held by a spring 33 in an extended position in the event of compression of the spring 33.

The fixed element is, in the example shown, a fixed ring 35 in which are formed radial apertures 36.

Figure 11 shows the device at rest, the weight 18 is then against the proximal end of the cavity.

Figure 12 shows the device in normal operating mode; the weight 18 is in abutment against the projecting zone 22 of the cavity.

Figure 13 shows the device at the beginning of abnormal operating regime, that is to say, in the event of overspeed of the shaft 4 of the door, the flyweight protrudes beyond the projecting zone 22 and comes to rest on the finger 32.

Figure 14 illustrates the thrust exerted by the weight 8 on the finger 32 which radially out the latter. The finger 32 then engages in a light of the ring, which has the effect of blocking the rotation of the device and therefore the shaft.

It should be noted that the cavity 19 may include an elastic means such as a flexible elastic blade that maintains the weight in the proximal portion of the cavity, when the door operates in normal mode.

The invention thus provides a braking device which, in its various embodiments, makes it possible effectively to stop the rotation of a shaft of a door when the drive chain breaks. of it.

The invention especially provides a braking device adaptable to soft curtain doors whose rotation speed of the shaft in normal operation and abnormal operation is close enough.

Of course, the invention is not limited to the embodiments described above by way of non-limiting example, but it encompasses all the embodiments.

Claims (13)

1. A device for braking the rotation of a shaft (4) for raising and lowering a flexible or rigid and articulated leaf (6) of a high-speed, industrial, commercial, domestic or garage door, said device comprising an endplate (17) rotated by the shaft (4), said endplate (17) having several cavities (19) each of which comprises a wall (20), which, serving as the support for a weight (18) in operating condition, is inclined relative to the axis of rotation of the endplate at an angle less than 90°, each cavity having a proximal end situated close to the axis of rotation of the endplate and a distal end at a distance from the axis of rotation of the endplate, each weight (18) traveling in one of said cavities between a position of operation at normal speed of the shaft (4) in which the weight is in a zone comprising the proximal end of the cavity (19) and a position of operation at a speed of the shaft (4) exceeding a predetermined threshold in which the weight (18) is in a zone comprising the distal end of the cavity and actuates means for braking the rotation of the shaft (4), said device being characterized in that each cavity (19) has means ensuring a stabilization of the position of the weight (18) in the zone comprising the proximal end of the cavity in operation at normal speed of the shaft and promoting a movement of the weight (18) toward the zone comprising the distal end of the cavity when the speed of rotation of the shaft (4) exceeds a predetermined threshold, each cavity (19) having, on its wall on which the weight presses, in operating condition, a first portion situated on the side of the proximal end having a relatively acute angle α relative to the axis of rotation of the device and a second portion situated on the side of the distal end having an angle β relative to the axis of rotation, the angle β being greater than the angle α and the junction between the first and the second portion forming a protruding zone (22) upon which the weight (18) presses in operation at normal speed.
2. The braking device as claimed in claim 1, characterized in that each cavity (19) has, on its wall on which the weight (18) presses in operating condition, a rib which separates the distal end from the proximal end, a rib on which the weight (18) presses in normal operation of the door.
3. The braking device as claimed in one of claims 1 or 2, characterized in that breakable means keep the weight (18) at the proximal end of the cavity, these breakable means capable of breaking in abnormal operation of the door releasing the weight toward the proximal end of the cavity.
4. The braking device as claimed in claim 3, characterized in that the breakable means consist of a wire whose strength makes it possible to sustain the centrifugal force applied to the weight (18) in operation at normal speed of the shaft but does not make it possible to sustain the centrifugal force applied to the weight in abnormal operation.
5. The braking device as claimed in one of claims 1 to 4, characterized in that the braking means comprise a radially or axially movable assembly (11, 25, 31) on which the weights (18) act and a fixed assembly (23, 29, 35) with which the movable assembly may come into contact by friction and/or meshing to brake the rotation of the shaft.
6. The braking device as claimed in claim 5, characterized in that each cavity (19) receiving a weight (18) has, at its distal end, a radially movable finger (32) that can occupy a retracted position in which the finger is retained by a spring (33) or can occupy a protruding position under the effect of a pressure by a weight (18), the finger (32) in the protruding position being able to engage in an opening (36) arranged in a fixed ring (35).
7. The braking device as claimed in claim 5, characterized in that each cavity (19) receiving a weight (18) is delimited by the wall (20) of an assembly (11, 25) that can move axially between a position of operation at normal speed in which the movable assembly is pushed in the direction of the cavity by elastic means and a position of operation at a speed exceeding a predetermined threshold in which each weight axially pushes the movable assembly against a fixed element (23, 29).
8. The braking device as claimed in claim 7, characterized in that the movable assembly (11) has, on a wall opposite to its wall facing the cavity (19), at least one tooth (14) capable of engaging in a tooth (24) protruding from a fixed disk (23).
9. The braking device as claimed in claim 8, characterized in that the teeth (14, 24) of the movable assembly and the teeth of the fixed disk are undercut and are disengaged after their engagement only by a reverse rotation of the shaft.
10. The device as claimed in claim 5, characterized in that the axially movable assembly (25) has, on its wall opposite to its wall facing each cavity, a convergent frustoconical ring (26) on which at least one pivoting lever (27) presses having a hook (30) at its free end, the lever (27) being able to pivot between a position of operation at normal speed of the shaft and a position of operation at a speed of the shaft exceeding a predetermined threshold in which the frustoconical ring presses on each lever (27) in order to cause it to pivot until it catches on a fixed bar (29).
11. The braking device as claimed in one of claims 7 to 10, characterized in that the axially movable assembly (11, 25) has, on its wall opposite to its wall facing the cavity, a pad for braking the rotation by friction against a fixed element.
12. The braking device as claimed in one of claims 7 to 11, characterized in that it comprises a linear ball bearing (16) making it possible to cause the movable assembly (11, 25) to slide relative to the spindle.
13. The braking device as claimed in one of claims 1 to 12, characterized in that it comprises means of connection with a control unit making it possible to transfer a triggering of the device.

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