EP2628888B1 - Elektromechanischer rotationsantrieb für eine last mit einem momentenbegrenzer - Google Patents

Elektromechanischer rotationsantrieb für eine last mit einem momentenbegrenzer Download PDF

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Publication number
EP2628888B1
EP2628888B1 EP13155746.4A EP13155746A EP2628888B1 EP 2628888 B1 EP2628888 B1 EP 2628888B1 EP 13155746 A EP13155746 A EP 13155746A EP 2628888 B1 EP2628888 B1 EP 2628888B1
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EP
European Patent Office
Prior art keywords
torque
actuator according
motor
friction
drive shaft
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Active
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EP13155746.4A
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English (en)
French (fr)
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EP2628888A1 (de
Inventor
Aymeric Soudy
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Simu SAS
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Simu SAS
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Publication date
Application filed by Simu SAS filed Critical Simu SAS
Priority to PL13155746T priority Critical patent/PL2628888T3/pl
Publication of EP2628888A1 publication Critical patent/EP2628888A1/de
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
    • E06B—FIXED OR MOVABLE CLOSURES FOR OPENINGS IN BUILDINGS, VEHICLES, FENCES OR LIKE ENCLOSURES IN GENERAL, e.g. DOORS, WINDOWS, BLINDS, GATES
    • E06B9/00—Screening or protective devices for wall or similar openings, with or without operating or securing mechanisms; Closures of similar construction
    • E06B9/56—Operating, guiding or securing devices or arrangements for roll-type closures; Spring drums; Tape drums; Counterweighting arrangements therefor
    • E06B9/68—Operating devices or mechanisms, e.g. with electric drive
    • E06B9/74—Operating devices or mechanisms, e.g. with electric drive adapted for selective electrical or manual operation

Definitions

  • the invention relates to an electromechanical actuator driving a load around a geometric axis of rotation. It relates more particularly to a mechanism of the above type, for driving the load motorized and manually, especially in case of failure of the engine or its power supply. It relates in particular to a mechanism of the previous type, for the driving of a roller shutter. It also relates to certain technological bricks used in such an electromechanical drive actuator. It relates in particular to a torque transmission mechanism whose function is to transmit any driving torque from a first rotating member to a second rotating member, but to block the second rotating member in the absence of engine torque applied by the first rotating member, whatever the direction of rotation. It also relates to a mechanism combining an engine and a torque limiter.
  • an electromechanical actuator for axially rotating a shutter comprising an electric motor for driving the shutter through a main drive shaft, and a troubleshooting operation comprising a torque transmission mechanism provided manually by means of a crank, to drive the shutter in the event of failure or failure of the power supply of the electric motor.
  • the torque transmission mechanism comprises a bidirectional freewheel for transmitting to an intermediate shaft any motor torque exerted by the crank on a secondary drive member and for securing the intermediate shaft to the fixed frame in the absence of a driving torque exerted by the secondary tree.
  • bidirectional free wheel any mechanism for transmitting from a driving shaft - here the secondary drive shaft - to a driven shaft - here the intermediate shaft - a driving torque exerted by the drive shaft, regardless of the direction of rotation of the two shafts, and prohibits the transmission of torque and energy from the driven shaft to the drive shaft.
  • the motor directly drives the motor shaft which is uncoupled from the intermediate shaft and the secondary drive shaft, by displacement of a first brake plate.
  • the brake couples the motor shaft to a fixed frame. If the roller shutter exerts on the drive shaft a torque, for example due to the weight of an already deployed portion of the flap, the motor shaft remains stationary, because of its kinematic connection to the frame via the mechanism to bidirectional free wheel.
  • the two-way freewheel couples the secondary drive shaft to the shaft secondary drive, so that the torque exerted by the user is transmitted to a second brake plate, and the housing of the actuator which then rotates on itself to drive the shutter.
  • the link to the frame of the bidirectional freewheel mechanism is also not explained. Its implementation is complex because of the rotation of the actuator housing when using a repair maneuver.
  • the use of a bidirectional freewheel mechanism incorporating a brake spring creates complex design constraints and is not necessarily suitable in heavy load driving cases, such as commercial grids.
  • the invention aims to overcome the disadvantages of the state of the art and to propose, in a small footprint, a reliable mechanism that allows the drive by a motor or by a secondary power source, in practice produced manually by a user .
  • the torque limiter is calibrated to fully transmit any torque less than or equal to a reference limit torque, and not to transmit torque greater than the reference limit torque.
  • the reference limit torque is preferably greater than the maximum engine torque of the electric motor and preferably less than the maximum torque allowed by the drive train. transmission between the motor and the load, in other words the breaking torque of the most fragile element of the transmission kinematic chain.
  • the torque limiter has friction surfaces pressed against each other with a predetermined force.
  • the friction surfaces are preferably frustoconical for optimization of the axial and radial dimensions, but other shapes can also be envisaged.
  • the frustoconical friction surfaces are particularly suitable since it allows, for a given engine power, to accommodate the torque limiter in the internal diameter of the motor stator.
  • one of the friction surfaces is integral with the intermediate driven member which can be made in a single piece or in several interconnected parts, forming a compact assembly.
  • the torque limiter and the bidirectional coupling have a multifunctional common member, which results in a gain in compactness.
  • the torque limiter comprises at least one elastic return member exerting the predetermined force.
  • the actuator comprises a disengagement control for uncoupling the torque limiter when the motor is powered.
  • This clutch acts preferentially on one of the parts of the torque limiter.
  • the torque limiter thus also fulfills a clutch or brake function, in order to, in certain operating modes, interrupt the transmission kinematic chain between the main motor shaft and the secondary drive member. This multiplicity of functions in the same organ is particularly advantageous for the compactness of the whole.
  • the clutch control comprises a yoke of ferromagnetic material activated by a field induced by the motor and movable between a coupling position and a disengagement position.
  • the movement of the cylinder head may in particular be a translation movement parallel to the main drive shaft.
  • the breech is in this case the only moving part in translation, the other parts, and in particular the secondary drive member, the intermediate driven member and the main drive shaft being in axial rotational movement.
  • these rotations are around a single geometric reference axis of the mechanism.
  • the mechanism thus has a high degree of integration in a small radial and axial space.
  • the elastic return member referred to above reminds the cylinder head to the coupling position.
  • the cylinder head is provided with one of the friction surfaces.
  • the invention is particularly suitable for driving shutters or commercial grilles.
  • a rotary drum driven by the drive shaft and having a cylindrical outer surface for winding a shutter or a grid constituting the load.
  • the mechanism further comprises a secondary drive member rotating the secondary drive member.
  • a secondary drive member rotating the secondary drive member.
  • the secondary drive member is shaped to allow a user to manually drive the secondary drive member. This may include a crank with a bevel gear, or a belt and pulley device.
  • the actuator comprises at least one sliding or rolling bearing ensuring the connection between the intermediate driven member and the main drive shaft, for guiding the friction cone relative to the shaft when a pair is exerted on the crank and the free rotation of the shaft during operation of the engine.
  • the bearing preferably comprises an outer ring integral with the intermediate driven member, an inner ring secured to the main drive shaft and, if appropriate, rolling bodies arranged between the rings.
  • the main drive shaft can drive the load either directly or via a speed reducer.
  • the speed reducer and the torque limiter are preferably located on either side of the engine.
  • the torque limiter is then calibrated to transmit fully any torque less than or equal to a reference limit torque, and not to transmit torque greater than the reference limit torque, the reference limit torque being greater than the maximum motor torque of the electric motor. and less than the maximum permissible torque of the gearbox.
  • the first friction member is a multifunctional member for controlling the coupling or uncoupling of the torque limiter according to the presence or absence of power to the motor.
  • the torque limiter is uncoupled when the engine is powered, and coupled when the engine is not powered.
  • the torque limiter can function as a brake if the second friction member is fixed or coupled to a fixed frame. It may also be, according to a preferred embodiment, coupled to a troubleshooting crank or other troubleshooting driver, possibly via a bidirectional coupling, for example a two-way freewheel coupling.
  • the predetermined force is preferably such that the torque limiter transmits integrally any torque less than or equal to a reference limit torque, and is not capable of transmitting torque greater than the reference limit torque.
  • the reference limit torque is preferably greater than the maximum engine torque of the electric motor. This arrangement is particularly useful when the second friction member is coupled to a troubleshooting drive member, the maximum torque must be controlled, including a manually driven crank.
  • the reference limit torque is lower than the maximum torque allowed by the transmission kinematic chain between the motor and the load, in other words the breaking torque of the most fragile element of the drive train. of transmission.
  • the first and second friction surfaces are frustoconical.
  • This arrangement makes it possible to limit the outside diameter of the friction surfaces and the elastic restoring force of the return member, for a given reference limit torque, while preserving a very great simplicity for the device. It also influences the dimensioning of the motor itself, since it is the magnetic flux of the motor which must generate the force opposing the elastic return member. It is therefore possible, with frustoconical friction surfaces, and at equal power of the motor, to accommodate the torque limiter in the internal diameter of the stator of the motor.
  • the second friction member is secured to a rotary receiving member, in a first position, to secure the second friction member to a fixed frame, and in a second position to secure the second member of friction to a secondary drive shaft.
  • the actuator comprises a speed reducer, the speed reducer and the torque limiter being preferably located on either side of the engine.
  • the torque limiter is preferably calibrated to transmit fully any torque less than or equal to a reference limit torque, and not to transmit torque greater than the reference limit torque, the reference limit torque being greater than the maximum engine torque of the electric motor. and less than the maximum permissible input torque of the gearbox.
  • the first friction member consists of a part, which reduces the number of parts and simplify assembly.
  • the torque transmission mechanism constitutes a bidirectional coupling in the sense that it operates in both directions of rotation, the function of which is to transmit any engine torque from the first member rotating towards the second rotating member, but to prevent any transmission of torque. motor from the second member rotating towards the first rotating member, blocking in this case the rotation of the second rotating member.
  • the equi-part arrangement of the locking elements ensures a good distribution of the contact points ensuring the transmission of torque between the first rotating member and the second rotating member, or between the second rotating member and the fixed drum. This balanced distribution limits the stresses perpendicular to the reference axis. It makes it possible to limit in particular the wear of the rotating guide bearings of the first rotating member and / or the second rotating member.
  • This mechanism can be implemented as a technological brick in different locations of a transmission kinematic chain, and in particular between a secondary drive shaft and a primary drive shaft, where appropriate with the interposition of a torque limiter as indicated below. the previous aspect of the invention.
  • the locking elements are rollers, preferably cylindrical rollers.
  • the pairs of blocking elements are three or more.
  • the number of three is preferred insofar as it constitutes an ideal compromise between the desire for a balanced distribution of the blocking elements and the resulting bulk.
  • the mechanism further comprises resilient return members of each locking member to the locking position, which can be constituted by leaf springs.
  • each spring blade cooperates with two locking elements associated with two opposite directions of rotation. It is thus possible to ensure the elastic return of the locking elements with a reduced number of parts, in this case as many springs as pairs of locking elements.
  • each spring blade cooperates with two locking elements by separating them from one another. Both blocking elements may belong to two adjacent pairs. This arrangement is particularly advantageous from the point of view of space.
  • the first rotating member forms a star comprising a pair of pair of locking elements, each branch being preferably disposed between the two locking elements of a pair of locking element, and being movable between a middle position without contact with the locking elements, a driving position in a direction of rotation in contact with one of the locking elements and a driving position in the opposite direction of rotation in contact with the other element blocking.
  • the second rotating member is provided with a friction surface
  • the mechanism further comprising a third member rotating about the reference geometric axis and having a friction surface disposed facing the friction surface.
  • the third rotating member being movable in translation by relative to the second member rotating between a coupling position in which the friction surface of the third rotating member is in contact with the friction surface of the second rotating member, and a disengagement position in which the friction surface of the third rotating member is away from the second rotating member.
  • the third rotating member can advantageously be returned to the contact position by a return spring.
  • the mechanism may further comprise a counter-torque member, in particular a friction element, in particular a friction seal, in particular an O-ring, for exerting a predetermined pair of friction between the second rotating member and the fixed drum.
  • a counter-torque member in particular a friction element, in particular a friction seal, in particular an O-ring, for exerting a predetermined pair of friction between the second rotating member and the fixed drum.
  • FIG. 1 is schematically illustrated a motorized actuator 10 housed in a cylindrical fixed housing 12 which may for example be disposed at the end or inserted inside a winding tube of a curtain or shutter or other load .
  • the mechanism 10 comprises an electric motor 14 composed of a stator 16 and a rotor 18 forming a main drive shaft 20, a speed reducer 22 connected to the main drive shaft 18 and having an output shaft 23 designed to drive a load, and a recovery device 24 to allow driving of the motor shaft 20 in case of failure of the motor 14 or its power supply.
  • the recovery device 24 and the speed reducer 22 are located on either side of the motor 14 at both ends of the shaft 20.
  • the troubleshooting device 24 consists of a secondary drive member 26, here a crank handle, a bevel gear 28 for transmitting the rotation of the crank handle to a secondary drive shaft of troubleshooting 30, d a bi-directional freewheel 32 and a torque limiter 34.
  • the motor shaft 20 and the secondary drive shaft 30 rotate around a same reference geometric axis 100 of the mechanism.
  • the bidirectional free wheel 32 illustrated on the Figures 2 to 4 , has an input member 36 integral with the recovery shaft 30 and forming therewith a secondary drive member 38, a multifunctional intermediate driven member 40 consisting of a receiving member 40.1 and a friction cone 40.2 secured to each other, a fixed drum 42 consisting of a drum having a cylindrical wall 42.1 rotated radially inwardly and a guide shoulder 42.2.
  • the fixed drum 42 has been intentionally omitted to allow the spring blades 48 and the receiving part 40.1 to be seen.
  • the free wheel also comprises three pairs 44 of cylindrical rollers 44.1, 44.2 housed in housings 46 delimited by a wall 40.11 or 40.12 of the receiving part 40.1 forming a ramp and the cylindrical wall 42.1 of the fixed drum 42.
  • the rollers are pressed against these walls by springs 48.
  • Each pair of rollers 44 comprises a roller 44.1 cooperating with a wall 40.11 of the receiving part and associated with a direction of rotation 100.1 around the geometric axis 100, and a roller 44.2 cooperating with a wall 40.12 of the receiving part and associated with the opposite direction of rotation 100.2.
  • each spring 48 is constituted by a blade having in the plane of the figure 3 a general shape of W with curved ends to each accommodate a roller 44.1 or 44.2 and push in a position of contact with the walls 40.11 or 40.12 of the receiving part 40.1 and the wall 42.1 of the fixed drum.
  • the receiving part 40.1 has been deliberately omitted to allow the spring blades 48 to be viewed.
  • the input member 36 and the intermediate driven member 40 can rotate around the reference geometrical axis 100 in the direction 100.1 and the meaning 100.2.
  • the input member 36 has a general star shape with as many branches 36.1 as pairs of rollers 44, here three.
  • Each branch 36.1 enters a housing 46 between the two rollers 44.1, 44.2 of a pair to cooperate alternately with one or the other.
  • the bidirectional free wheel 32 is completed by a friction seal 50 disposed in a groove 40.13 of the receiving part 40.1 and coming into contact with the cylindrical wall 42.1 of the fixed drum 42.
  • the friction cone 40.2 is provided with frustoconical friction linings 52 and is an integral part of the torque limiter 34, which further comprises a yoke 54 forming a frustoconical bowl with a friction surface 56 facing that of the friction cone 40.2 .
  • the yoke 54 is made of a low hysteresis ferromagnetic material, and is connected to the main drive shaft 20 by a key 58 which allows sliding in translation parallel to the reference geometric axis 100 of the yoke 54 relative to the shaft. 20 but prohibits any rotation between these two parts.
  • the yoke 54 and the friction cone 40.2 respectively form a first friction member and a second friction member of the torque limiter 34. It is also shown on FIG. figure 5 a ball bearing 62 disposed between the friction cone 40.2 and the shaft 20, guiding the friction cone relative to the shaft 20 when a torque is exerted on the crank and the free rotation of the shaft 20 during operation of the engine.
  • the mechanism works as follows.
  • the bi-directional freewheel 32 is in the middle position shown in FIG. figure 3 : the branches 36.1 are without contact with the rollers 44.1, 44.2, halfway between the rollers 44.1, 44.2, which are wedged between the wall 42.1 of the fixed drum 42 and the wall 40.11 or 40.12 of the receiving part 40.1, solidarising these two pieces by jamming.
  • a motor torque applied in a direction 100.1 or in the other 100.2 to the friction cone 40.2 is integrally transmitted to the fixed drum 42, without causing rotation of the intermediate driven member 40 or the secondary drive member 38 due to jamming rollers between the wall 42.1 of the fixed drum 42 and the wall 40.11 or 40.12 of the receiving part 40.1. No engine torque can therefore be transmitted from the friction cone 40.2 to the secondary drive member 38.
  • the torque limiter 34 and the free wheel 32 then have a brake function, preventing any inadvertent rotation of the driven motor shaft 20. by the charge.
  • the friction o-ring 50 constitutes a counter-torque member which introduces a slight torque of friction to limit or avoid a saccade effect when the load is not constant. This is the case for example when the load is constituted by a slatted shutter or a large grid that takes place.
  • the yoke 54 moves axially under the effect of the magnetic field induced in the direction 100.4 and is pressed against the motor by binding the spring 60, canceling the air gap and releasing the limiter of torque 34.
  • the rotor 18 is then free to rotate and drive the speed reducer 22 and the load.
  • the spring 60 appears partially inserted in the rotor 18. It could alternatively be contained in the volume of the cylinder head 54.
  • the cylinder head 54 As soon as the power supply of the motor 14 is cut off, for example because the load has reached the desired position, the cylinder head 54, repelled by the spring 60, moves and comes back against the friction cone 40.2. The latter can not rotate due to the median positioning of the bidirectional free wheel, so that the rotor 18 is also immobilized, ensuring the positioning of the load.
  • the frustoconical shape of the friction surfaces 52, 56 of the torque limiter is particularly suitable for limiting the diameter of the torque limiter in the inner diameter of the stator 16 and the cylinder 12 without oversizing the spring 60, so the motor.
  • other forms may where appropriate be adopted, providing a plateau torque limiter or multi-disk.
  • the friction surfaces may be directly formed on the friction cone and the cylinder head, or consist of inserts.
  • the bidirectional freewheel 32 may have any suitable structure, with rollers, balls, ratchets, or cams for example. It can consist of two stages of freewheeling in series.
  • the same mechanism can be used with a secondary engine instead of the crank.

Landscapes

  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Operating, Guiding And Securing Of Roll- Type Closing Members (AREA)
  • Transmission Devices (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (15)

  1. Elektromechanischer Aktuator für den rotierenden Antrieb einer Last, der aufweist:
    - einen Elektromotor (14), um die Last mit Hilfe einer Hauptmotorwelle (20) anzutreiben,
    - ein sekundäres führendes Organ (38), und
    - einen Momentübertragungsmechanismus, der mit dem sekundären führenden Organ und einem geführten rotierenden Übergangsorgan (40) verbunden ist, der einen starren Rahmen (42) und eine bidirektionale Kupplung (32) aufweist, um an das geführte Übergangsorgan (40) jedes von dem sekundären führenden Organ (38) erzeugte Motormoment zu übertragen und um das geführte Übergangsorgan (40) bei Abwesenheit des von dem sekundären führenden Organ (38) erzeugten Motormoments mit dem starren Rahmen (42) zu verbinden,
    dadurch gekennzeichnet, dass er einen Momentbegrenzer (34) aufweist, der das geführte Übergangsorgan (40) mit der Hauptmotorwelle (20) verbindet.
  2. Aktuator nach Anspruch 1, dadurch gekennzeichnet, dass der Momentbegrenzer (34) eingestellt ist, um jedes Moment kleiner oder gleich einem Referenz-Grenzmoment vollständig zu übertragen, und um kein Moment zu übertragen, das größer als das Referenz-Grenzmoment ist, wobei das Referenz-Grenzmoment größer als das maximale Motormoment des Elektromotors (14) ist.
  3. Aktuator nach Anspruch 1 oder Anspruch 2, dadurch gekennzeichnet, dass der Momentbegrenzer (34) Reibeflächen (52, 53) aufweist, die mit einer vorbestimmten Kraft gegeneinander gedrückt werden.
  4. Aktuator nach Anspruch 3, dadurch gekennzeichnet, dass die Reibeflächen (52, 56) kegelstumpfförmig sind.
  5. Aktuator nach Anspruch 3 oder Anspruch 4, dadurch gekennzeichnet, dass eine (52) der Reibeflächen (52, 56) mit dem geführten Übergangsorgan (40) verbunden ist.
  6. Aktuator nach einem der Ansprüche 3 bis 5, dadurch gekennzeichnet, dass der Momentbegrenzer (34) mindestens ein elastisches Rückstellorgan (60) aufweist, das eine vorbestimmte Kraft ausübt.
  7. Aktuator nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass er eine Entkopplungssteuerung aufweist, um den Momentbegrenzer (34) zu entkoppeln, wenn der Motor (14) versorgt wird.
  8. Aktuator nach Anspruch 7, dadurch gekennzeichnet, dass die Entkopplungssteuerung ein Joch (54) aus ferromagnetischem Material aufweist, das von einem von dem Motor induzierten Feld aktiviert wird und zwischen einer Kopplungsstellung und einer Entkopplungsstellung beweglich ist.
  9. Aktuator nach Anspruch 8 in Kombination mit Anspruch 6, dadurch gekennzeichnet, dass das elastische Rückstellorgan (60) das Joch (54) in seine Kopplungsstellung zurückstellt.
  10. Aktuator nach einem der Ansprüche 7 bis 9 in Kombination mit einem der Ansprüche 3 bis 6, dadurch gekennzeichnet, dass das Joch (54) mit einer (56) der Reibeflächen (52, 56) ausgestattet ist.
  11. Aktuator nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass er ferner ein sekundäres Antriebsorgan (26), insbesondere eine Kurbel, aufweist, das das sekundäre führende Organ (38) rotierend antreibt.
  12. Aktuator nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass er ein glattes oder Wälzlager (62) umfasst, das die Verbindung zwischen dem geführten Übergangsorgan (40) und der Hauptmotorwelle (20) sicherstellt, um das geführte Übergangsorgan (40) im Verhältnis zur Hauptmotorwelle (20) zu führen, wenn ein Motormoment auf das sekundäre führende Organ (38) ausgeübt wird und die freie Rotation der Hauptmotorwelle (20) sicherzustellen, wenn der Motor (14) läuft.
  13. Aktuator nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass das sekundäre führende Organ (38), das geführte Übergangsorgan (40) und die Hauptmotorwelle (20) um eine selbe Geometrieachse drehen.
  14. Aktuator nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass er ein Untersetzungsgetriebe (22) aufweist, wobei sich das Untersetzungsgetriebe (22) und der Momentbegrenzer (34) vorzugsweise auf der einen und der anderen Seite des Motors (14) befinden.
  15. Aktuator nach Anspruch 14, dadurch gekennzeichnet, dass der Momentbegrenzer (34) eingestellt ist, um jedes Moment kleiner oder gleich einem Referenz-Grenzmoment vollständig zu übertragen, und um kein Moment zu übertragen, das größer als das Referenz-Grenzmoment ist, wobei das Referenz-Grenzmoment größer als das maximale Motormoment des Elektromotors (14) und kleiner als das zulässige maximale Eingangsmoment des Untersetzungsgetriebes (22) ist.
EP13155746.4A 2012-02-20 2013-02-19 Elektromechanischer rotationsantrieb für eine last mit einem momentenbegrenzer Active EP2628888B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL13155746T PL2628888T3 (pl) 2012-02-20 2013-02-19 Elektromechaniczny siłownik napędu obrotowego dla obciążenia z ogranicznikiem momentu obrotowego

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1251517A FR2987067B1 (fr) 2012-02-20 2012-02-20 Actionneur electromecanique d’entrainement en rotation d’une charge a limiteur de couple

Publications (2)

Publication Number Publication Date
EP2628888A1 EP2628888A1 (de) 2013-08-21
EP2628888B1 true EP2628888B1 (de) 2014-09-24

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EP13155746.4A Active EP2628888B1 (de) 2012-02-20 2013-02-19 Elektromechanischer rotationsantrieb für eine last mit einem momentenbegrenzer

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EP (1) EP2628888B1 (de)
JP (1) JP3183230U (de)
CN (1) CN203548661U (de)
FR (1) FR2987067B1 (de)
PL (1) PL2628888T3 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101846703B1 (ko) 2016-09-12 2018-04-06 현대자동차주식회사 회전체 구속시 회전체와 분리가능한 구동모터
EP3663501B1 (de) * 2018-12-03 2021-02-17 D&M Kg Wickelwellenanordnung für eine gebäudeöffnungsverschattungsvorrichtung

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Publication number Priority date Publication date Assignee Title
DE3420789A1 (de) * 1984-06-04 1985-12-05 Josef 7312 Kirchheim Pradler Antriebseinheit
DE3504489A1 (de) * 1985-02-09 1986-08-14 Lothar 7984 Wolpertswende Huber Vorrichtung zur handbetaetigung der elektromotorisch antreibbaren wickelwelle z.b. eines rolladens bei stromlosem elektromotor
FR2736087B1 (fr) * 1995-06-28 1998-01-09 Bubendorff Sa Volet roulant motorise

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Publication number Publication date
JP3183230U (ja) 2013-05-09
FR2987067B1 (fr) 2014-03-28
EP2628888A1 (de) 2013-08-21
PL2628888T3 (pl) 2015-03-31
CN203548661U (zh) 2014-04-16
FR2987067A1 (fr) 2013-08-23

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