Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
• • E—FIXED CONSTRUCTIONS
  • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
  • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
  • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
  • E06B9/56—Operating, guiding or securing devices or arrangements for roll-type closures; Spring drums; Tape drums; Counterweighting arrangements therefor
  • E06B9/68—Operating devices or mechanisms, e.g. with electric drive
  • E06B9/72—Operating devices or mechanisms, e.g. with electric drive comprising an electric motor positioned inside the roller
• • E—FIXED CONSTRUCTIONS
  • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
  • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
  • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
  • E06B9/56—Operating, guiding or securing devices or arrangements for roll-type closures; Spring drums; Tape drums; Counterweighting arrangements therefor
  • E06B9/80—Safety measures against dropping or unauthorised opening; Braking or immobilising devices; Devices for limiting unrolling
  • E06B9/82—Safety measures against dropping or unauthorised opening; Braking or immobilising devices; Devices for limiting unrolling automatic
  • E06B9/90—Safety measures against dropping or unauthorised opening; Braking or immobilising devices; Devices for limiting unrolling automatic for immobilising the closure member in various chosen positions
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
  • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
  • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
  • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
  • F16D67/02—Clutch-brake combinations
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
  • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
  • H02K7/102—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction brakes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D2127/00—Auxiliary mechanisms
  • F16D2127/001—Auxiliary mechanisms for automatic or self-acting brake operation
  • F16D2127/004—Auxiliary mechanisms for automatic or self-acting brake operation direction-responsive

Definitions

• the invention relates to a brake for a tubular motor for driving a roller shutter winding tube or the like. It relates more particularly to a brake device defined by the preamble of claim 1.
• Utility model IT-BO-92 U 000009 discloses a brake device arranged in the tube of the motor for driving the winding tube of a roller shutter or the like between the motor and a reduction gear.
• the brake is in the "braked” position, blocking the rotation of the winding tube, when the motor shaft is stopped and goes into the “free” position, releasing the rotation of the winding tube, when the motor shaft is trained.
• This brake device also has the function of transmitting mechanical torque from the motor to the reduction gear.
• the brake device comprises two brake discs arranged opposite, one of which is mounted in pivot connection on the motor shaft and terminates in a pinion engaging the reduction gear and has a cutout in which a pin housed in the motor shaft can move, the other of which is fixed to the motor tube.
• the device also comprises a compression spring between a bearing carrying the motor shaft and the brake disc mounted in pivot connection on the motor shaft.
• a compression spring between a bearing carrying the motor shaft and the brake disc mounted in pivot connection on the motor shaft.
• the object of the invention is to provide a brake device which overcomes this drawback and improves the devices known from the prior art.
• the invention proposes to produce a brake device in which the friction between the mechanical parts cooperating to separate the discs when the engine starts are reduced.
• the device according to the invention is characterized by the characterizing part of claim 1.
• Figures 1 to 12 are developed views of different auxiliary parts and neighboring parts having ramps explaining the operating principle of the different embodiments of the device according to the invention.
• Figure 1 is a view developed in the "braked" position of the auxiliary part and neighboring parts having ramps.
• Figure 2 is a view developed in the "free" position of the auxiliary part and neighboring parts having ramps, when the drive shaft is driven in a first direction of rotation.
• Figure 3 is a view developed in the "free” position of the auxiliary part and neighboring parts having ramps, when the drive shaft is driven in a second direction of rotation.
• FIG. 4 is a view developed in the "free” position of the auxiliary part and of the neighboring parts having additional ramps and stops, when the motor shaft is driven in the second direction of rotation.
• FIG. 5 is a view developed in the "braked" position of the auxiliary part and of the adjacent parts having parallel ramps.
• Figure 6 is a view developed in the "free" position of the auxiliary part and neighboring parts having parallel ramps, when the motor shaft is driven in a first direction of rotation.
• Figure 7 is a view developed in the "free" position of the auxiliary part and neighboring parts having parallel ramps, when the drive shaft is driven in a second direction of rotation.
• FIG. 8 is a view developed in the "free" position of the auxiliary part and of the neighboring parts having parallel ramps and additional stops, when the motor shaft is driven in a second direction of rotation.
• FIG. 9 is a view developed in the "braked” position of the auxiliary part and of the neighboring parts having ramps and stops.
• FIG. 10 is a view developed in the "free" position of the auxiliary part and of the neighboring parts having ramps and stops, when the motor shaft is driven in a first direction of rotation.
• FIG. 11 is a view developed in the "free" position of the auxiliary part and of the neighboring parts having ramps and stops, when the motor shaft is driven in a second direction of rotation.
• FIG. 12 is a view developed in the "free" position of the auxiliary part and of the neighboring parts having additional ramps and stops, when the motor shaft is driven in a second direction of rotation.
• FIG. 13 is a diagram in the "braked" position of the brake device according to a first embodiment.
• Figure 14 is a sectional view, in the "braked" position of the brake device according to a first embodiment.
• Figure 15 is a sectional view, in the "free" position of the brake device according to a first embodiment, when the motor shaft is driven in a first direction of rotation.
• FIG. 16 is a diagram in the "free" position of the brake device according to a first mode of embodiment, when the motor shaft is driven in a first direction of rotation.
• FIG. 17 is a diagram in the "free" position of the brake device according to a first embodiment, when the motor shaft is driven in a second direction of rotation.
• Figure 18 is a sectional view, in the "free" position of the brake device according to a first embodiment, when the motor shaft is driven in a second direction of rotation.
• Figure 19 is a sectional view, in the "braked" position of the brake device according to a second embodiment.
• Figure 20 is a sectional view, in the "braked" position of the brake device according to a third embodiment.
• Figure 21 is a sectional view, in the "braked" position of the brake device according to a fourth embodiment.
• Figure 22 is a sectional view, in the "braked" position of the brake device according to a fifth embodiment.
• Figure 23 is an exploded view of the device according to the first embodiment.
• FIG. 24 is a view developed in the "braked" position of the auxiliary part and of the neighboring parts having stops.
• Figure 25 is a sectional view of the device having a juxtaposition of seven brake discs.
• Figure 26 is a sectional view of an embodiment of the raceways for trapping the balls.
• Figure 27 is a partially cut developed view of a part having raceways for trapping the balls.
• Figure 28 is a detail view, in section, of a raceway for trapping the balls.
• the brake device consists of three juxtaposed discs 11, 5, 12, brought back into position against each other by a compression spring 4. Two of these brake discs 11 and 12 are linked to a drive shaft 1, the third is linked to a casing 2 by a slide link.
• the disc 11 is linked to the motor shaft 1 by a sliding pivot link.
• the other disc 12 is pivotally connected to the motor shaft 1 and is integral with a receiving shaft 3 causing a load.
• the two discs 11 and 12 are in slide connection with one another.
• the brake device has an auxiliary disc 13 secured to the drive shaft 1. Between this auxiliary disc 13 and the disc 11, an auxiliary part 6 is inserted.
• This auxiliary part 6 is in pivoting connection sliding on the motor shaft 1. It has an annular zone which comprises a succession of three ramps 63 and three stops 65 on each of its faces.
• the ramps 63 shown in Figures 1 to 4 and 9 to 12, are placed on either side of the auxiliary part 6 symmetrically. It should be noted that this symmetry is not necessary for the proper functioning of the device.
• These ramps 63 have slopes allowing them to cooperate with other ramps 63 of complementary shapes distributed over annular zones of the same diameter on the one hand the auxiliary disc 13 and on the other hand on the disc 11.
• These ramps 63 have raceways 62 receiving balls 61.
• the stops 65 present on the auxiliary part 6 cooperate with the ends 64 of the ramps of the brake disc 11 or of the auxiliary disc 13.
• stops 65 have two functions. On the one hand, they make it possible to limit the axial displacements of the parts 11, 6 and 13 by limiting the rotational strokes of these parts between them in order to prevent the balls 61 from escaping from the raceways 62. On the other hand apart, they allow the disc 11 to be driven in rotation by the auxiliary part 6 or the auxiliary part 6 by the auxiliary disc 13. However, it should be noted that these stops 65 are not necessarily necessary for the operation of the device. Indeed, the function of limiting the axial displacements of the parts 11, 6 and 13 can be provided for example, by a shoulder on the motor shaft 1 and the drive function can be provided by the contact actions of the balls 61 on the parts 11 , 6 and 13.
• This displacement of the ramps 63 one on the other is accompanied by an axial displacement against the action of the spring 4, of the auxiliary part 6 and of the disc 11, or according to the direction of rotation, of the single disc 11.
• the consequence of axial displacement is the appearance of a play between the brake discs 11, 5, 12.
• the auxiliary disc 13 When the drive shaft 1 rotates in a first direction, as shown in FIGS. 2, 10, 17 and 18, the auxiliary disc 13 creates, on the auxiliary part 6, via its ramps 63 forces whose orthoradial components are at the origin of its rotation drive. The brake disc 11 is then driven in rotation by obstacle of the stops 65 of the intermediate piece 6 on the ends 64 of the ramps of the brake disc 11.
• the auxiliary disc 13 rotates the auxiliary part 6 by obstacle of the ends 64 of its ramps on the stops 65 of the auxiliary part 6.
• the auxiliary part 6 creates, on the brake disc 11, by the intermediate of its ramps 63 efforts whose orthoradial components are at the origin of its rotation drive.
• the brake disc 11 is rotated when the engine is powered. It transmits its rotational movement to the receiving shaft 3 attacking the load by means of axes 19 hooped in the disc 11 and sliding in bores 18 made in the disc 12.
• the stops 65 necessary for the rotary drive of the disc 11 by the auxiliary part 6 or of the part auxiliary 6 by the auxiliary disc 13 can also be arranged on the auxiliary part 6 and on the auxiliary disc 13 as shown in FIGS. 9 to
• the additional stops 66 have two functions. On the one hand, they make it possible to limit the axial displacements of the parts 11, 6 and 13 by limiting the rotational strokes of these parts between them in order to prevent the balls 61 from escaping from the raceways 62. On the other hand apart, they allow the disc 11 to be driven in rotation by the auxiliary part 6 or the auxiliary part 6 by the auxiliary disc 13.
• the drive torque of the load by the motor is no longer the result of the orthoradial components of the forces of the ramps 63 on the balls 61, but mainly the result of the contact forces between the stops 65 and 66 or between the stops 65, 66 and the ends 64 of the ramps.
• the transmissible mechanical torque is then independent of the force exerted by the spring 4 and the shape of the ramps.
• the stiffness of the spring can then be chosen, keeping as the sole criterion the braking torque necessary for immobilizing the roller shutter.
• these additional stops 66 are not necessarily necessary for the operation of the device. Indeed, the function of limiting the axial displacements of the parts 11, 6 and 13 can be provided for example, by a shoulder on the motor shaft 1 and the drive function can be provided by the contact actions of the balls 61 on parts 11, 6 and 13.
• a second embodiment shown in Figure 19 differs from the first in that the auxiliary disc 23 is in slide connection with the drive shaft 1, in that the brake disc 22 secured to the receiver shaft 3 is in connection pivot sliding on the motor shaft 1 and in that the disc 21 is in pivot connection on the motor shaft.
• This architecture of the device makes it possible to accommodate the compression spring 4 in the receiving shaft 3, which gives the device a better compactness.
• the brake device consists of three juxtaposed discs 31, 5, 32, brought back into position against each other by a compression spring 4. Two of these brake discs 31 , 32 are linked to the motor shaft 1, the third disc 5 is linked to the casing 2 by a slide link.
• the disc 31 is secured to the drive shaft 1.
• the disc 32 is in pivoting connection sliding on the drive shaft 1 and is secured to the receiving shaft 3 driving the load.
• the compression spring 4 is supported on the disc 32 and on a stop on the motor shaft 1. Between the two discs linked to the motor shaft, an auxiliary part 6 is interspersed. This auxiliary part 6 is in pivoting connection sliding on the motor shaft 1. This auxiliary part 6 is identical to that described in the previous embodiments.
• the two brake discs 31, 32 have ramps 63 cooperating with the ramps 63 of the auxiliary part 6.
• the drive shaft 1 and the brake disc 31 are rotated.
• the ramps 63 of the brake disc 31 move on the ramps 63 of the auxiliary part 6 by pushing it axially.
• This auxiliary part 6 in fact pushes the brake disc 32 against the action of the compression spring 4.
• the device is then in the "free" position, the discs 31, 5, 32 no longer being pressed against each other.
• the engine torque is transmitted from the disc 31 to the receiving shaft 3 secured to the brake disc 32 via the auxiliary part 6.
• the ramps 63 of the auxiliary part 6 move on the ramps 63 of the brake disc 32 by pushing it against the action of the spring 4.
• the device is then in the "free” position.
• the engine torque is transmitted from the disc 31 to the receiving shaft 3 secured to the brake disc 32 via the auxiliary part 6.
• the brake disc 41 is linked to the motor shaft 1 by a slide link and in that the disc 42 is linked to the motor shaft 1 by a pivot link.
• the brake device has a brake disc 51 in pivoting connection sliding on the motor shaft 1 allowing it to translate up to a shoulder 53 and a brake disc 52 in pivot connection on the motor shaft 1.
• the third brake disc 5 is as seen in the previous embodiments in slide connection with the casing 2.
• an auxiliary part 7 shown in Figures 5 to 8 comprising a succession of ramps 63 and stops 65 on an annular area.
• the ramps 63 located on either side of the part 7 are parallel to each other. They cooperate with ramps 63 arranged on annular zones on the brake discs 51, 52.
• These ramps 63 are provided with raceways 62 receiving balls 61.
• the motor shaft 1 When the shutter motor is powered, the motor shaft 1 is rotated as well as the auxiliary part 7.
• the discs 51, 5, 52 are, in the "braked” position, pressed against each other.
• the auxiliary part 7 driven in rotation rotates relative to the discs 51, 52. This relative movement causes the displacement of the balls 61 in their paths 62 and the displacement of the ramps 63 linked to the auxiliary part 7 on the ramps 63 linked to the disc 52 if the motor shaft 1 rotates in a first direction as shown in FIG. 6 and on the ramps 63 linked to the disc 51 if the motor shaft 1 rotates in the other direction as shown in FIG. 7.
• This displacement of the ramps 63 one on the other is accompanied by an axial displacement against the action of the spring 4, of the auxiliary part 7 and of the disc 51 or according to the direction of rotation of the single disc 51.
• the consequence of axial displacement is the appearance a clearance between the brake discs 51, 5, 52.
• the auxiliary part 7 When the drive shaft 1 rotates in a first direction, as shown in FIG. 6, the auxiliary part 7 is pushed back due to its rotation relative to the disc 52 and pushes the disc 51 until it comes into contact with the shoulder 53. The auxiliary part 7 then creates on the disc 52 by means of its ramps 63 forces whose orthoradial components are at the origin of the drive of the disc 52 in rotation.
• the auxiliary part 7 pushes back the disc 51 and drives the disc 52 in rotation by obstacle stops 65 on the ends of the ramps 64 of the disc 52.
• the stops 65 necessary for the rotary drive of the disc 51 by the auxiliary part 7 or of the disc 52 by the auxiliary part 7 can also be arranged on the brake disc 51 and on the brake disc 52. Additional stops 66 shown in FIG. 8 can be practiced on the brake discs 51 and 52 to cooperate with those practiced on the auxiliary part 7 and thus carry out an obstacle drive of the various elements 51, 7, 52. Thanks to these additional stops, the torque d drive of the load by the motor is no longer the result of the orthoradial components of the forces of the ramps 63 on the balls 61, but mainly the result of the contact forces between the stops 65 and 66 or between the stops 65, 66 and the ends 64 of the ramps.
• the transmissible mechanical torque is then independent of the force exerted by the spring 4 and the shape of the ramps. The stiffness of the spring can then be chosen, keeping as the sole criterion the braking torque necessary for immobilizing the roller shutter.
• the ramps 63 may have raceways 84 in which the balls are trapped. This characteristic aims to facilitate the mounting of the device by integrating the balls 61 in the auxiliary part 6 or in the discs 11, 13 with which they form a sub-assembly.
• These paths of bearing 84 represented in FIGS. 26 to 28 consist of a lower part 83 of section having the shape of a semicircle with a diameter slightly greater than that of the balls and an upper part 82 consisting of two vertical walls connecting to the part lower 83.
• These paths 84 have a depth greater than the radii of the balls 61 and have in their upper part 82 lateral lips 81 vis-à-vis having a distance between them slightly less than the diameter of the balls 61.
• raceways 84 can be made indifferently on the auxiliary part, on the auxiliary disc or even on one of the brake discs.
• the invention can be applied to brake devices having a juxtaposition of more than three discs.
• an embodiment of the device derived from the first embodiment can be produced, as shown in FIG. 25.
• This device has a juxtaposition of seven brake discs.
• the brake discs 71, 72, 74 and 76 linked to the motor shaft are in sliding connection between them and the discs 73, 75 and 77 are in sliding connection with the casing 2.
• the brake discs, the auxiliary parts and the auxiliary discs fitted with ramps all have a succession of three ramps. However, it is also possible to carry out the invention using any number of ramps.
• the brake device according to the invention is of course applicable to any system comprising a motor driving a load.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Structural Engineering (AREA)
• Mechanical Engineering (AREA)
• Architecture (AREA)
• Civil Engineering (AREA)
• Power Engineering (AREA)
• Braking Arrangements (AREA)
• Operating, Guiding And Securing Of Roll- Type Closing Members (AREA)

Applications Claiming Priority (3)

Publications (1)

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ID=27799220

Family Applications (1)

Country Status (6)

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• 2002
  • 2002-03-25 FR FR0203670A patent/FR2837634B1/fr not_active Expired - Fee Related
• 2003
  • 2003-03-19 WO PCT/IB2003/001105 patent/WO2003081752A1/fr active Application Filing
  • 2003-03-19 AU AU2003209941A patent/AU2003209941A1/en not_active Abandoned
  • 2003-03-19 ES ES03744958T patent/ES2229969T1/es active Pending
  • 2003-03-19 JP JP2003579343A patent/JP2005521012A/ja active Pending
  • 2003-03-19 EP EP03744958A patent/EP1490945A1/de not_active Withdrawn

Non-Patent Citations (1)

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