EP3673132A1 - Entraînement linéaire à chaîne anti-retour - Google Patents

Entraînement linéaire à chaîne anti-retour

Info

Publication number
EP3673132A1
EP3673132A1 EP18745869.0A EP18745869A EP3673132A1 EP 3673132 A1 EP3673132 A1 EP 3673132A1 EP 18745869 A EP18745869 A EP 18745869A EP 3673132 A1 EP3673132 A1 EP 3673132A1
Authority
EP
European Patent Office
Prior art keywords
chain
drive motor
linear drive
depot
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP18745869.0A
Other languages
German (de)
English (en)
Inventor
Joel Tchaweu Tchatchoua
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Iwis Antriebssysteme GmbH and Co KG
Original Assignee
Iwis Antriebssysteme GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Iwis Antriebssysteme GmbH and Co KG filed Critical Iwis Antriebssysteme GmbH and Co KG
Publication of EP3673132A1 publication Critical patent/EP3673132A1/fr
Pending legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F11/00—Man-operated mechanisms for operating wings, including those which also operate the fastening
    • E05F11/02—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights
    • E05F11/04—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights with cords, chains or cables
    • E05F11/06—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights with cords, chains or cables in guide-channels
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F11/00—Man-operated mechanisms for operating wings, including those which also operate the fastening
    • E05F11/02—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights
    • E05F11/34—Man-operated mechanisms for operating wings, including those which also operate the fastening for wings in general, e.g. fanlights with screw mechanisms
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/611—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings
    • E05F15/616—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by push-pull mechanisms
    • E05F15/619—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by push-pull mechanisms using flexible or rigid rack-and-pinion arrangements
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/611—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings
    • E05F15/616—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by push-pull mechanisms
    • E05F15/622—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by push-pull mechanisms using screw-and-nut mechanisms
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/10—Covers; Housings
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/60—Suspension or transmission members; Accessories therefor
    • E05Y2201/622—Suspension or transmission members elements
    • E05Y2201/644—Flexible elongated pulling elements
    • E05Y2201/656—Chains
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/60—Suspension or transmission members; Accessories therefor
    • E05Y2201/622—Suspension or transmission members elements
    • E05Y2201/696—Screw mechanisms
    • E05Y2201/702—Spindles; Worms
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2800/00—Details, accessories and auxiliary operations not otherwise provided for
    • E05Y2800/72—Sets of mutually exchangeable elements, e.g. modular
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/10—Application of doors, windows, wings or fittings thereof for buildings or parts thereof
    • E05Y2900/13—Type of wing
    • E05Y2900/132—Doors
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/10—Application of doors, windows, wings or fittings thereof for buildings or parts thereof
    • E05Y2900/13—Type of wing
    • E05Y2900/148—Windows

Definitions

  • the present invention relates to a linear drive comprising a drive motor, a first engagement means drivable by the drive motor and a backstep chain, the backstay chain having second engagement means engaged with the first engagement means to drive the backstop chain.
  • an actuating element in which a back-rigid chain is moved by means of a spindle driven by a motor.
  • These actuators are used when opening and closing window sashes.
  • the electric motor used is provided with a gear and drives an arranged in extension of the engine spindle.
  • the back-rigid chain is arranged in the actuating element mainly in extension of the electric motor along the spindle, with which the chain is engaged.
  • the lifting movement of this actuating element takes place substantially perpendicular to the spindle axis, wherein the back-rigid chain is deflected by the electric motor and guided to the outside, where the chain is then connected to the element to be actuated.
  • This configuration results in a very slim shape of the actuator at a considerable length.
  • JP 201 1/137514 A and JP 201 1/144874 A Another type of linearly acting lifting drive is shown in JP 201 1/137514 A and JP 201 1/144874 A, wherein two chain strands are brought together in the manner of a zipper principle and are wedged rigidly into one another.
  • the chains are driven by a sprocket, which can intervene differently in the chain strands depending on the positioning of the motor. In this case, the sprocket on a réelle Vietnamese bemesser, which is greater than the width or the height of the associated motor.
  • a sub-strand of the chain is deflected into a chain depot, which runs meandering on the side of the engine.
  • the engagement in the chains takes place by means of a directly engaging in corresponding openings between the side plates sprocket or engaging in laterally projecting pin Triebstockrad.
  • an actuating mechanism for a sun visor is known, which is moved by means of two chain strands.
  • the chain strands are attached to two sides of the panel and are each driven by a worm. Since the two worms are driven by a motor, the helices of the worm are formed in opposite directions, whereby the two chain strands are deflected only after the engagement of the respective worm.
  • the linear drive according to the invention comprises a drive motor, a first engagement means which can be driven by the drive motor and a back-rigid chain.
  • the backstep chain has a second engagement means engaged with the first engagement means.
  • the linear drive according to the invention designed such that the back-rigid chain is at least partially guided along the drive motor.
  • the backstep chain can be guided along the drive motor either on the outside along the drive motor or, in the case of a hollow shaft motor, by guiding the backstep chain through the hollow shaft along the inside of the drive motor.
  • the linear drive also has a chain depot, which is at least partially disposed on the side opposite the exit of the motor shaft side of the drive motor. Due to this design, the linear drive according to the invention is designed to be particularly compact.
  • a chain depot in the context of this invention is any device that is capable of einhausen the unloaded part of the back rigid chain, restrict their freedom of movement, for example by the use of guides or rails or controlled in any other way to keep.
  • a back-stiff chain in the sense of this invention is a chain whose mobility in the chain links is limited by movement-inhibiting elements in at least one direction. These may be, for example, specially shaped chain links, such as those used in a conventional backstacked chain. However, it is also possible to use guide elements in combination with the chain, which restrict free mobility in the chain links in at least one direction.
  • the second backstay chain engagement means may be any backstay chain element. This includes in particular the roles of a roller chain, the bolts, outer or inner plates, reinforcements or additional attachments of the backrest chain.
  • the chain depot is adapted to receive at least 30%, preferably at least 75% and most preferably at least 90% of the unloaded part of the backstacked chain.
  • the chain depot is adapted to receive at least 30%, preferably at least 75% and most preferably at least 90% of the unloaded part of the backstacked chain.
  • the chain depot is arranged next to the drive motor. Due to this design, the linear drive is designed to be particularly compact and takes up little space in the installation of the linear drive.
  • the chain depot and the drive motor are arranged in a structural unit. Due to this type of linear drive is the Linear drive can be installed as an independent unit for many applications and can be exchanged quickly and inexpensively as needed.
  • the assembly is arranged in a housing which protects the components and the electrical connections against contamination, in particular moisture.
  • the drive motor has a transmission.
  • the transmission increases the torque and reduces the speed of the drive motor, which thus exerts large forces on the back stiff chain even with low power.
  • the transmission couples the drive motor with the drivable first engagement means.
  • the transmission is disposed between the drive motor and the first engagement means and increases the torque while reducing the speed of the first engagement means.
  • the linear drive has a first component.
  • the first component has the drive motor, the transmission and / or the first engagement means drivable by the drive motor.
  • the first component has a height, width and depth, as well as the chain depot.
  • the length values are dimensioned such that the height of the first component is greater than or equal to the height of the chain depot and / or the width of the first component is greater than or equal to the width of the chain depot and / or the depth of the first component is greater than or equal to the depth of the Chain depots amounts.
  • the drive motor has a height, width and depth, as well as the chain depot.
  • the drive motor has a height, width and depth, as well as the chain depot.
  • the length values are dimensioned such that the height of the drive motor is greater than or equal to the height of the chain depot and / or the width the drive motor is greater than or equal to the width of the chain depot and / or the depth of the drive motor is greater than or equal to the depth of the chain depot.
  • the back-rigid chain is guided along in a plane on the drive motor, which is arranged parallel to the geometric motor axis.
  • the back-rigid chain can be guided past the drive motor over a length which corresponds to at least 50% of the length, preferably at least 80%, of the length of the drive motor.
  • a deflection of the back-rigid chain takes place in the unloaded part of the back-rigid chain in the region of the chain depot.
  • a deflection of the back-rigid chain is particularly space-saving, so that a large area of the unloaded part of the back-rigid chain can be accommodated in the chain depot.
  • a portion of the back stiffener chain in the chain depot, can be accommodated, whose length corresponds to at least 1.5 times the length of the drive motor.
  • the length of the linear drive it makes sense to accommodate the largest possible portion of the length of the back-rigid chain in the chain depot.
  • the total length of the linear drive in the retracted state of the backwheele chain is considerably reduced at maximum retracted stroke of the actuator.
  • the back-stiff chain in the chain depot is deflectable storable in two parallel chain strands. A deflection of the back-rigid chain in two parallel chain sections is particularly space-saving.
  • the back-rigid chain in the chain depot is worm-shaped storable. A deflection of the back stiff chain in snail shape is particularly space-saving.
  • the remote from the back end chain is fixed in the region of the chain depot. If the lifting movement of the linear drive is maximum, the non-operating end of the backstacked chain can be secured in the chain depot, e.g. via positional elements attached to the back-rigid chain and detectable by means of sensors. The sensor then ensures a corresponding control of the drive motor, which shuts off the drive motor when reaching the maximum stroke length of the linear drive. Due to the positioning of the remote end of the back-end chain in the area of the chain depot, it is not necessary to guide the back-end chain into the chain depot during the reduction of the stroke length.
  • the engagement means is a worm or sprocket.
  • the chain depot is arranged between a base plate and a hood.
  • the chain depot has a substantially rectangular shape with flat side surfaces. One of the side surfaces is arranged adjacent to an outer side of the drive motor. In a preferred embodiment, the largest side surface of the chain depot is arranged adjacent to the outside of the drive motor.
  • the stroke takes place during extension of the back-rigid chain in one direction pointing away from the drive motor and or gear of the linear actuator.
  • the method according to the invention for storing a backstep chain of a linear drive has three method steps: In the first method step, a first engagement means is driven by a drive motor. In the second method step, the backstep chain is driven by the second engagement means of the backstacked chain engaged with the first engagement means. In the third method step, the back-rigid chain is guided along the drive motor into the chain depot.
  • the chain depot is at least partially disposed on the side opposite the exit of the motor shaft side of the drive motor.
  • the back stiff chain is guided along in a plane on the drive motor, which is arranged parallel to the geometric axis of the motor.
  • the transmission between the drive motor and engaging means thus changes the axis of rotation of the engaging means by a right angle to the geometric axis of the motor, that the back-rigid chain is guided parallel to the geometric axis of the motor.
  • the back-stiff chain is guided along a length of the drive motor, which corresponds to at least 50% of the length, preferably at least 80% of the length of the drive motor.
  • the back-rigid chain is deflected in the chain depot.
  • a deflection of the back-rigid chain is particularly space-saving, so that a large area of the unloaded part of the back-rigid chain can be accommodated in the chain depot.
  • a portion of the backstacked chain whose length is at least 1.5 times the length of the chain is accommodated in the chain depot Drive motor corresponds.
  • the largest possible portion of the length of the back-stiff chain is accommodated in the chain depot.
  • the total length of the linear drive in the retracted state of the backwheele chain is considerably reduced at maximum retracted stroke of the actuator.
  • the back stiff chain is deflected in the chain depot and stored in two mutually parallel chain strands.
  • a deflection of the back-rigid chain in two parallel chain sections is particularly space-saving.
  • the back-rigid chain is deflected in the chain depot and stored in a spiral shape.
  • a deflection of the back stiff chain in snail shape is particularly space-saving.
  • a second back stiffener chain is provided, wherein the second back stiffener chain has engagement means, which are also engaged with the helical groove of the screw to drive the second back stiffener chain synchronously to the first back stiffener chain.
  • the paired arrangement of two back-stiff chains in a linear drive standardized, rigid push chains can be used and absorb the transverse forces acting in the linear drive.
  • the engagement of the first and second backstep chain with corresponding engagement means in the helical groove of the same screw allows a synchronous drive, wherein the linear drive further requires a single drive motor and a single driven screw.
  • the limitation of the drive unit to a drive motor and a drivable screw for the first and second back stiff chain also reduces the space required for a linear drive according to the invention.
  • other back-stiff chains can also be used corresponding engagement means are brought into engagement with the helical groove of the worm and are driven synchronously in the linear drive according to the invention to the first and second spine chain.
  • the first back stiffener chain and the second back stiffener chain have alternating inner chain links and outer chain links interconnected by means of link pins, the stud axes of the link pins of the first backstep chain and the second backstep chain being guided in a common plane extending along or parallel to the geometric axis of the screw.
  • the two back-rigid chains are no longer deflected out of this plane, starting from the region of engagement with the worm drivable by the drive motor until it is connected to the actuated element, so that it is possible to apply a thrust force directly over the helical groove of the worm along this plane , Regardless of the possibility of applying a thrust force in the direction of the plane running along or parallel to the geometric axis of the worm via the drive drivable by the drive motor, the guidance of the first and second spider chain in this common plane is also suitable for achieving a compact design the back stiff chains can move very close along the drive motor and screw drive unit.
  • the rigid rear side of the first backstay chain and the rigid back side of the second backstop chain can be arranged on different sides of the plane.
  • a rigid connecting element is provided, wherein the ends of the first back stiffener chain and the second back stiffener chain are connected to the connecting element.
  • the paired arrangement of the first and second back stiffener chain on the connecting element not only allows the secure absorption of lateral forces, but also a bias of the first and second back stiffener chains to each other, wherein the bias acting in the two back stiffener chains can be adjusted individually.
  • the provision of such a rigid connecting element facilitates the use of such a linear drive for stage or lifting devices, in which an unintentional occurrence of high shear forces is possible.
  • a particular embodiment of the linear drive according to the invention provides that the first back stiffener chain and the second back stiffener chain are guided outside of the screw and with their engagement means at least partially along the drive motor, wherein the core diameter of the screw is greater than twice the distance of the motor axis the motor outer sides, where the first back stiffener chain and the second back stiffener chain are guided along.
  • This means that the region occupied by the drive motor of the linear drive is at least partially used at the same time also by the first and second backstep chain, whereby the linear drive, based on a specific chain length of the back-rigid chain, with a total low overall length.
  • the joint axes of the back-rigid chains can be aligned exactly perpendicular to the screw axis or at a distance offset from this axis.
  • the first and second back stiffener chain over a length of the drive motor can be guided, which corresponds to at least 50% of the length, preferably at least 80% of the length of the drive motor.
  • a considerable reduction in length occurs in particular when the thrust force is applied away from the drive motor, because then the non-pressurized length of the back-rigid chains can extend along the drive motor and does not lead to an overall extension of the linear drive.
  • a chain depot for the first spine chain and the second spine chain can be provided laterally along the drive motor, wherein the chain depots are each formed with at least two adjacent, preferably parallel sections of the first back stiffener chain or the second back stiffener chain.
  • These chain depots can each be designed as a total depot or as an intermediate depot for the first and second spine chains.
  • the remote end of the back-rigid chains is preferably fastened in the region of the chain depots.
  • this design may lead to a slightly wider configuration of the linear drive, but the overall length can be considerably shortened when retracted chains of the back stiff chains.
  • sections of the first and second spine chains whose lengths correspond at least to 1.5 times the length of the drive motor, can be accommodated in the chain depots.
  • the back-stiff chains are therefore in the chain depots meandering back and forth, which can also be done multiple times.
  • the geometric axis of the worm can be arranged coaxially to the motor axis, wherein the worm has an outer diameter which is greater than twice the distance of the motor axis to the motor outside, on one of the two backrest chains is guided along.
  • the drive motor may be provided with a gear which is coupled to the worm.
  • the transmission leads to a reduction of the rotational movement and an increase in the torque, with common ratios of 3: 1, 4: 1 or 6: 1.
  • the worm drivable by the drive motor transmits by means of the helical groove, the force of the drive motor on the first and second back-rigid chain. So that the back-rigid chains are exposed to as little wear as possible, a reduction in friction can be achieved by a suitable choice of material of the screw.
  • the worm may have a sleeve-shaped worm body and a non-rotatable drive shaft connected thereto.
  • the screw body can thereby be made of a low-cost, easily machined material, such as a plastic, wherein the friction properties of the screw body can be selected according to the engagement means of the two back-rigid chains. Further, the screw body can be easily replaced with a problematic wear by a new screw body, which in turn is rotatably connected to the drive shaft.
  • first back stiffener chain and the second back stiffener chain at least at predetermined intervals and at least laterally projecting laterally projecting chain pins as engaging means such that a protruding part of the chain pin with the screw in engagement is or can be brought.
  • back-stiff chains can be used, in which only at least some of the chain pins are made longer. All other components of such conventional back stiffener chains can be maintained in a similar manner and require no adjustment.
  • the engagement means comprise elements for reducing friction in the form of at least one rotatable roller or a sliding shoe, which engage in the helical groove of the worm.
  • Sliding shoes may for example have the shape of a key or the cross-sectional shape of an ellipse. Also, a height-convex feather key shape or elliptical shape can be used. All side surfaces can be made spherical.
  • the rollers can be ball bearings or even ball bearings. The use of sintered rollers, which may be soaked in a lubricant, is also possible.
  • the engagement means comprise elements for slip compensation in the form of a plurality of rotatable rollers arranged side by side on a projecting chain pin and / or a conically shaped roller and a helical groove adapted thereto.
  • first back stiffener chain and the second back stiffener chain are guided in the region of the screw in each case by means of a guide rail which has in each case one rear side facing away from the engagement sides of the chain and two outwardly facing sides.
  • a guide rail which has in each case one rear side facing away from the engagement sides of the chain and two outwardly facing sides.
  • the guide rails offer the possibility of a targeted guidance and support of the first and second back-rigid chain, for example in a chain depot.
  • the guide rails may also have rollers or wheels to reduce friction or be formed by rollers or wheels.
  • the linear drive is a compact unit and designed as a self-supporting construction, which can be used independently of the corresponding application conditions as a modular module .
  • a support structure with a base body and a first back stiffening chain and the second back stiffener chain bridging, arranged on the base body bearing plate is configured, wherein on one side of the bearing plate, the screw is mounted.
  • the main body further allows the arrangement of the linear drive in various installation situations.
  • the support structure may have a back plate bridging front plate at the front end of the body and an end plate at the rear end of the body, which are arranged substantially parallel to the bearing plate, and corresponding side parts, wherein the front plate, the bearing plate and the end plate by means of the side parts of the base body guided past the worm and the drive motor are connected to one another.
  • the front panel forms, possibly together with corresponding guide rails, an outlet for the actuating ends of the first and second backstatte chains, while all other components of the linear drive according to the invention within the support structure and are arranged protected. As a result, the possibly occurring by the Anbringsituation the linear drive forces can be absorbed and passed to the drive motor and the screw.
  • the front panel can also be used as a second bearing plate for the screw.
  • a cover may be provided which covers the open longitudinal sides of the support structure, wherein the worm, the drive motor and possibly the chain depots or the laterally guided on the worm and the drive motor sections of the first and second back-rigid chain between Base and cover are arranged.
  • the bushings of the two back-rigid chains should be provided from the housing with specially shaped brushes. These brushes could also relubricate the back stiff chains including the friction reducing elements.
  • position elements which can be detected by means of one or more sensors can be attached to the first and second backstep chain, wherein the position elements are, for example, clipped into the backstacked chains. Such position elements can be used as reference points of the linear drive according to the invention, with the aid of which a subdivision of the entire drive path and an electronic control can be made possible.
  • the worm drivable by the drive motor with helical groove is designed as a hollow screw, wherein the first and second rigid back chain are passed through the hollow screw parallel to each other and driven by the inner helical groove.
  • a hollow screw in addition to the other embodiments of the linear drive according to the invention allows a very narrow design.
  • the first back stiffener chain can be connected to a first drive unit with drivable screw and the second back stiffener chain to a second drive unit with drivable screw, the first back stiffener chain and second back stiffener chain are driven synchronously and a rigid Connecting element are interconnected.
  • the platform could serve a lifting system at the corners of which at least the first and second back-rigid chain are fastened torsionally stiff to each other.
  • a side view of a linear drive according to the invention a side view of the linear drive of FIG. 1, wherein a side cover has been omitted, the side view of the linear drive of FIG. 1 without cover 1, a side view of the essential functional components of the linear drive, an enlarged view of the functional components according to FIG. 4, a sectional side view of the screw and the two back-rigid chains, an enlarged detail view of the section VII from FIG. 7 , a sectional side view of another embodiment of the
  • the linear drive 1 shows a view of the linear drive 1 according to the invention, in the chain depot 29 of which the unloaded part 3u of the back-stiff chain 3 is mounted in two mutually parallel chain sections.
  • the linear drive 1 has a drive motor 15 and the first engagement means 19, which is formed in this embodiment as a hollow screw, which engages in arranged on the back-rigid chain 3 second engagement means.
  • the drive motor 15 coupled by means of motor shaft 44 to the transmission 16.
  • the engagement means 19 engages in the engagement region 28 in a back-rigid chain 3, which is designed here as an outer link chain.
  • the back-rigid chain 3 has inner chain links 24 connected via outer chain links 25.
  • Chain pins 27 connect an outer chain link 25 to an inner chain link 24.
  • Stiffening straps 26 limit bending of the backstep chain 3 only in one direction.
  • the housing 2 has a window opening 31, as well as the chain depot 29 has a window opening 29.1.
  • the chain depot 29 is arranged behind the drive motor 15.
  • Chain depot 29 and drive motor 15 are arranged to each other such that the back-rigid chain 3 is guided in a plane through the drive motor 15, which is arranged parallel to the geometric axis of the motor 15 of the drive motor.
  • the back-rigid chain can be guided past the drive motor over a length which preferably corresponds to at least 80% of the length of the drive motor.
  • To store the back-rigid chain 3 in the chain depot 29 drives the drive motor 15 via the motor shaft 44, gear 16, gear shaft 23 and engagement means 19, the back-rigid chain. If the stroke length is reduced, the back-stiff chain 3 is guided along the drive motor 15 through the motor shaft 44, transmission 16, transmission shaft 23 and engagement means 19 into the chain depot 29.
  • the unloaded part 3u of the back-stiffened warp 3 is deflected in such a way that the warp-resistant warp 3 is stored in two chain sections running essentially parallel to one another (FIG. 1 a).
  • the warp depot 29 is dimensioned so that at least 30%, particularly preferably 90%, of the unloaded part 3u of the backstacked warp is stored in the warp depot.
  • the non-operating end of the back-rigid chain 3 can be secured in the chain depot 29, e.g. via attached to the back-rigid chain 3 position elements that are detectable by sensors.
  • the sensor then ensures a corresponding control of the drive motor 15, which turns off the drive motor 15 when the maximum stroke length of the linear drive 1 is reached. Due to the positioning of the remote from the actuator back end of the back-rigid chain 3 in the chain depot 29 is a guide the back-rigid chain 3 in the chain depot 29 during the reduction of the stroke length is not necessary.
  • the unloaded part 3u of the back-stiffened chain 3 moves conditionally into the chain depot 29 due to its inherent rigidity.
  • FIG. 2 shows a view of the linear drive 1 according to the invention, in whose chain depot 29 the unloaded part 3u of the back-stiffened chain 3 is mounted in a helical form.
  • the linear drive 1 has a drive motor 15 and the first engagement means 19, which is formed in this embodiment as a sprocket, which engages in the formed by the chain pin 27 of the back-rigid chain 3 spaces.
  • the sprocket 19 perpendicular to the motor axis AM, the back-rigid chain 3 is moved along the motor axis AM.
  • the drive motor 15 couples by means of the motor shaft 44
  • the drive motor 15, motor shaft 44, gear 16, gear shaft 23 and engagement means 19 together with the chain depot 29 form a structural unit, which is protected by the housing 2 from contamination.
  • the engagement means 19 engages in the engagement region 28 in a back-rigid chain 3, which is designed here as an outer link chain.
  • the back-rigid chain 3 has inner chain links 24 connected via outer chain links 25.
  • Chain pins 27 connect an outer chain link 25 to an inner chain link 24.
  • Stiffening straps 26 limit bending of the backstep chain 3 only in one direction.
  • the housing 2 has a window opening 31.
  • the back-rigid chain 3 in the chain depot 29 drives the drive motor 15 via the motor shaft 44, gear 16, gear shaft 23 and engagement means 19, the back-rigid chain. If the stroke length is reduced, the back-stiff chain 3 is guided along the drive motor 15 into the chain depot 29. Due to the formation of the engagement means 19 as a sprocket, the back-rigid chain 3 is guided laterally along the drive motor 15. The chain depot 19 is therefore arranged laterally offset parallel to the motor axis AM behind the drive motor 15.
  • the height Hb of the first structural unit is greater than the height Hk of the chain depot (FIG. 2 a), the width Bb of the first structural unit is greater than the width Bk of the chain depot.
  • the depth Tk of the warp deposit is less than the depth Tb of the first assembly ( Figure 2 b). Due to these dimensions of the warp depot 29, the unloaded part 3u of the back-stiffened warp 3 is deflected in such a way that the back-stiff warp 3 is mounted in a helical form.
  • the unloaded part 3u of the back-rigid chain 3 have a greater length, so that the stroke length of the linear drive is increased.
  • the linear drive 1 has a drive motor 15 and the first engagement means 19, which is formed in this embodiment as a sprocket, which engages in the formed by the chain pin 27 of the back-rigid chain 3 spaces.
  • the sprocket 19 By rotation of the sprocket 19 perpendicular to the motor axis AM, the back-rigid chain 3 is moved along the motor axis AM.
  • the drive motor 15 coupled by means of motor shaft 44 to the transmission 16.
  • the engagement means 19 engages in the engagement region 28 in a back-rigid chain 3, which is designed here as an outer link chain.
  • the back-rigid chain 3 has inner chain links 24 connected via outer chain links 25.
  • Chain pins 27 connect an outer chain link 25 to an inner chain link 24.
  • Stiffening straps 26 limit bending of the backstep chain 3 only in one direction.
  • the housing 2 has a window opening 31, as well as the chain depot 29 has a window opening 29.1.
  • the back-rigid chain 3 in the chain depot 29 drives the drive motor 15 via the motor shaft 44, gear 16, gear shaft 23 and engagement means 19, the back-rigid chain. If the stroke length is reduced, the back-stiff chain 3 is guided along the drive motor 15 into the chain depot 29. Due to the formation of the engagement means 19 as a sprocket, the back-rigid chain 3 is guided laterally along the drive motor 15. The chain depot 19 is therefore arranged laterally offset parallel to the motor axis AM behind the drive motor 15.
  • the height Ha of the drive motor is less than the height Hk of the warp deposit (FIG. 3a)
  • the width Bk of the warp deposit is less than the width Ba of the drive motor.
  • the depth Tk of the warp deposit is also less than the depth Ta of the drive motor ( Figure 3b). ). Due to these dimensions of the warp depot 29, the unloaded part 3u of the backstep chain 3 is deflected in such a way that the back rigid chain 3 is mounted in two substantially parallel chain sections running.
  • the linear drive 1 has a drive motor 15 and the first engagement means 19, which is formed in this embodiment as a hollow screw, which engages in arranged on the back-rigid chain 3 second engagement means.
  • the drive motor 15 coupled by means of motor shaft 44 to the transmission 16.
  • the engagement means 19 engages in the engagement region 28 in a back-rigid chain 3, which is designed here as an outer link chain.
  • the back-rigid chain 3 has inner chain links 24 connected via outer chain links 25.
  • Chain pins 27 connect an outer chain link 25 to an inner chain link 24.
  • Stiffening straps 26 limit bending of the backstep chain 3 only in one direction.
  • the housing 2 has a window opening 31, as well as the chain depot 29 has a window opening 29.1.
  • To store the back-rigid chain 3 in the chain depot 29 drives the drive motor 15 via the motor shaft 44, gear 16, gear shaft 23 and engagement means 19, the back-rigid chain. If the stroke length is reduced, the back-stiff chain 3 is guided along the drive motor 15 through the motor shaft 44, transmission 16, transmission shaft 23 and engagement means 19 into the chain depot 29.
  • the warp depot 29 is only through a partition wall of the drive motor 15, motor shaft 44, gear 16, gear shaft 23 and engagement means 19th separated, the other sides of the chain depot 29 are bounded by the housing 2.
  • the width Bk of the warp deposit corresponds to the width Bb of the first component (FIG. 4a), likewise the depth Tk of the warp deposit corresponds to the width depth Tb of the first component (FIG. 4b). Due to these dimensions of the warp depot 29, the unloaded part 3u of the back-stiffened warp 3 is deflected in such a way that the back-stiff warp 3 is mounted in two chain sections running essentially parallel to one another.
  • This embodiment shows a comparatively simple construction of the linear drive according to the invention, in which the back-rigid chain 3 is nevertheless guided securely into the chain depot 29.
  • linear drive 1 comprises an elongated, cuboid housing 2, and a first back-rigid chain 3.1 and a second back-rigid chain 3.2, which are stiffened in opposite pivot directions.
  • a joint head 4 is provided with ball joint for pivotally mounting the linear drive 1.
  • numerous other mounting options for the linear drive 1 can be provided on the bottom 6 of the housing 2, wherein in addition to a pivotal mounting and a rigid attachment is possible.
  • An immediate attachment to the housing 2 is conceivable.
  • the back stiffening chains 3.1 and 3.2 move at the front end, ie the front side 5 of the housing 2, on and off.
  • the housing 2 comprises, in addition to the front plate 8 on the front 5 and an end plate 9 on the bottom 6, a cover 10 which is screwed to a base body 1 1 of the housing 2.
  • the housing 2 comprises a support structure to which, in addition to the front plate 8 and the end plate 9 arranged parallel thereto, the base body 1 1 belongs.
  • This can be clearly seen in the perspective side view of the linear drive 1 in FIG. 6.
  • one of the support structure of the linear drive 1 and a arranged between the front plate 8 and the end plate 9 bearing plate 12, which is parallel and at a distance from the front panel. 8 and end plate 9 between the two side parts 13 and 14 of the main body 1 1 extends.
  • the side parts 13, 14 are frontally screwed to the front plate 8 and the end plate 9 and laterally with the bearing plate 12.
  • the side parts 1 3, 14 extend over the entire length between the front plate 8 and the end plate 9.
  • the cover 10 therefore only serves to protect the components of the linear drive 1 arranged inside the support structure and described in more detail below. Also on the back of the support structure, a corresponding cover 10 may be arranged.
  • an electric drive motor 15 and a connected to the drive motor 15 gear 16 are arranged.
  • the drive unit of drive motor 15 and gear 16 is disposed between the bearing plate 12 and the end plate 9.
  • drive motor 15 and gear 16 are fastened together by means of a flange 17 on the bearing plate 12.
  • the attachment of the drive motor 15 together with the gear 16 is therefore only one side of the bearing plate 12, for example by means of screws.
  • the drive motor 15 is connected via corresponding electrical connections and electrical lines (not shown) to the electrical connection socket 7 on the end plate 9.
  • the gear 16 has in the present case a reduction of 4: 1, but other reductions are possible, for. Eg 6: 1 or 10: 1.
  • the back-end chains 3.1 and 3.2 emerging from the front panel 8 are connected at their projecting ends to a rigid connecting element 18. Since the first back stiffener chain 3.1 and the second back stiffener chain 3.2 are stiffened in opposite pivot directions, the connection via the rigidly attached to the two back stiffener chains 3.1 and 3.2 connecting element 18 in addition to the axial stiffness necessary for a linear drive 1 also allows the absorption of lateral forces.
  • a worm 19 is arranged between the front plate 8 and the bearing plate 12, which is driven via the gear 16 and the drive motor 15.
  • the worm 19 is rotatably mounted, wherein both in the bearing plate 12 and in the front plate 8 each have a ball bearing for supporting the worm 19 is provided.
  • the worm 19 is constructed in two parts and comprises a worm body 20 and a drive shaft 21 which extends through the sleeve-shaped worm body 20 and is non-rotatably connected thereto, see also FIGS. 9 and 13.
  • the worm body 20 is made of a softer material as the drive shaft 21, wherein both plastic with good sliding properties and softer metals, such as brass, can be used.
  • the worm 19 has on its lateral surface or its outer periphery a circumferential helical groove 22 with a predetermined pitch.
  • the helical groove 22 has a substantially rectangular cross-section.
  • the drive shaft 21 is rotatably connected to the transmission shaft 23.
  • the motor axis AM including the transmission axis AG is arranged coaxially with the worm axis AS.
  • An offset arrangement is possible, but must meet the space requirements of the linear actuator 1.
  • the diameter DS of the screw 19 is relatively large, so that the outer circumference of the screw 19 projects beyond the outer circumference of the drive motor 15, see also FIG. 10. This must be the case at least on the sides of the drive motor 15, the first back stiffener chain 3.1 and the second back-stiffened chain 3.2 are facing.
  • the screw 19, or the screw body 20 has a core diameter DK, which is also greater than the corresponding dimension of the drive motor 15 with gear 16 on the two back-rigid chains 3.1 and 3.2 facing sides.
  • the two back-stiff chains 3.1 and 3.2 are roller chains, which are constructed of alternating inner chain links 24 and outer chain links 25.
  • stiffening tabs 26 are arranged, which are arranged in the two spine chains 3.1 and 3.2 respectively in different pivot directions and ensure that at a substantially straight alignment of the back stiffened chains 3.1 and 3.2 a thrust safely is transferable.
  • the inner chain links 24 and the outer chain links 25 are pivotable relative to one another.
  • the outer chain links 25 each include the chain pins 27.1 and 27.2.
  • each second chain pin 27.1 is made extended in this way.
  • the pitch of the helical groove 22 corresponds approximately to the pitch of the back-rigid chains 3.1 and 3.2. For a good engagement between the worm 19 and the back-rigid chains 3.1 and 3.2, it is sufficient if every second chain pin 27.1 is extended.
  • the back-rigid chains 3.1 and 3.2 are aligned such that they are edgewise in the two side parts 13, 14 of the main body 1 1 along. In the present embodiment, therefore, the chain longitudinal axes KL of the first back stiffener chain 3.1 and the second back stiffener chain 3.2 are aligned parallel to the motor axis AM, gear axis AG and screw axis AS. In the engagement region 28 between the two spine chains 3.1, 3.2 and the screw 19 are the pin axes B1 of the chain pin 27.1 substantially exactly perpendicular to the screw axis AS.
  • the back-rigid chains 3.1 and 3.2 are deflected once within the housing 2, see also Fig.
  • each a chain depot 29 is formed.
  • the chain depots 29 each consist of two mutually parallel chain strands and the associated deflection region.
  • the retracted state of the linear drive 1 is therefore in the warehouses 29 each have a chain length of the backstreaked chain 3.1 and 3.2, which is greater than 1.5 times the total length of the drive unit of the drive motor 15 and gear 16th
  • the deflection of the back-rigid chains 3.1 and 3.2 naturally takes place about the axes of the chain pins in the respective pivoting direction of the back-rigid chains 3.1 and 3.2, so that the back-rigid chains 3.1 and 3.2 substantially in a plane (a plane perpendicular to the plane of FIG.
  • the two backstay chains 3.1 and 3.2 can also have a backlash in the chain links so that the above illustration is an idealized view.
  • the arrangement of the two back-rigid chains 3.1, 3.2 means that the front region, ie the actual operating region of the back-rigid chains 3.1, 3.2, centrally guided and only offset at the lower end of the housing 2 to the outside.
  • the front panel 8 has two window openings 31, through which the two back-rigid chains 3.1, 3.2 can move in and out.
  • the side parts 1 3 and 14 of the base body 1 1 have a recessed groove structure from the inside, so that the back-rigid chains 3.1, 3.2 can move within this groove structure.
  • the useful structure at the lower end of the housing 2 is designed such that the chain depots 29 form in this recessed groove structure.
  • guide rails 32 (see Fig. 8) can be introduced with a low coefficient of friction both at the bottom and on the side walls, which come to rest with the respective underside and the front and rear sides of the back stiffener chains 3.1 and 3.2.
  • These guide rails 32 can be configured interchangeable.
  • the chain sensor 34 may be connected to the receptacle 7 via a corresponding electrical lead (not shown) to communicate the respective signals.
  • an inner chain link 24 is shown in which a positioning element 36 is embedded between the rollers 35 of the inner chain link.
  • the positioning element 36 has a plastic holder 37 and a cylindrical permanent magnet 38.
  • the plastic holder 37 is adapted to the space between the rollers 35 and resiliently clipped into this space.
  • the positioning element 36 is located on an inner chain link 24, which can indicate both an end position and / or an intermediate position of the linear drive 1.
  • the chain sensor 34 detects the permanent magnet 38 and optionally switches off the drive motor 15.
  • the linear drive 1 has such a configuration and performance, which make it possible to use the linear drive 1 according to the invention for certain applications as an alternative to hydraulic and pneumatic cylinders.
  • the two back-rigid chains 3.1, 3.2 are firmly connected to each other at their on the front plate 8 protruding ends via the connecting element 18, wherein the connecting element 18 is fixed by appropriate securing bolts 30 with the at the end of the backrest chains 3.1, 3.2 protruding inner chain links 24 twisting.
  • the connecting element 18 causes a rigid connection of the two back stiffener chains 3.1, 3.2, whereby not only a linear movement of interconnected first and second spine chains 3.1 and 3.2 in the direction of the motor axis AM, the transmission axis AG and the screw axis AS is ensured, but also the absorption of lateral forces and an increase of the movable means of the linear drive 1 according to the invention load is possible.
  • the linear drive 1 allows, as an alternative to hydraulic or pneumatic cylinders, the application of a thrust force to an element to be moved.
  • the connecting element 18 is connected to a correspondingly actuated element, for example platform and lifting devices, but also windows, doors or gates, etc.
  • FIGS. 5 to 8 show a substantially retracted position of the linear drive 1.
  • the lower end of the linear drive 1 is fastened by means of the joint head 4 with ball joint on an axis provided therefor.
  • the joint head 4 with ball joint allows pivoting in two axes, similar to what is known in the arrangement of hydraulic and pneumatic cylinders. Instead of elaborate hydraulic or pneumatic circuits, this electrically operated linear drive 1 only needs to be connected to the power supply and possibly control electronics.
  • the drive motor 15 drives with its motor shaft via the reduction of the gear 16, the screw 19 at.
  • the back-rigid chains 3.1 and 3.2 are moved out of the housing 2 by means of the engagement of the longer chain pins 27. 1 into the helical groove 22. Accordingly, the element connected to the connecting element 18 is actuated.
  • the operation of the drive motor 15 is carried out until the corresponding desired length of the back-rigid chains 3.1, 3.2 is extended.
  • the two spine chains 3.1 and 3.2 can extend in the thrust region in a single plane, so that it is possible to dispense with the thrust region, in particular a deflection and an offset of the spine-resistant chains 3.1, 3.2.
  • a deflection takes place rather in the unloaded sections of the back-rigid chains 3.1, 3.2 in the range of the chain depots 29, ie the side of the drive motor 15 and the transmission 16.
  • rollers 39 are positioned and secured by a lock washer 40 respectively.
  • the rollers 39 are in contact with the driven flank of the helical groove 22 and act as frictional reduction elements. Rollers 39 made of correspondingly low-friction materials, for example plastic or lubricant-impregnated porous materials (eg sintered rollers) are used. As shown in FIGS.
  • a subdivision into a plurality of rollers 39 is preferably carried out, so that these also act simultaneously as an element for slip compensation serve to at least partially compensate for the present within the helical groove 22 depending on the diameter different speeds. As a result, the wear on the rollers 39 can be reduced accordingly.
  • the variant shown in FIGS. 11 and 12 can be used as an alternative to the back-rigid chains 3.1 and 3.2 as well as the worm 19 from the preceding embodiment.
  • FIG. 11 A further alternative of friction and slip engagement of the actuating region of the backstay chains 3.1 and 3.2 with respect to the embodiment of FIGS. 11 and 12 is shown with reference to FIG.
  • a single roller 41 is used in this embodiment, which is rotatably mounted on the protruding chain pin 27.1.
  • the roller 41 is conical and engages in a corresponding trapezoidal helical groove 22 a.
  • the conical roller 41 serves as an element for reducing friction. Due to the conical shape of the roller 41 and the adapted shape of the helical groove 22, this construction also serves as an element for slip compensation, since the speed differences within the helical groove 22 can be compensated via the conical roller 41.
  • the first engagement means 19 is a hollow screw and both gear and motor are designed so that the back-rigid chain 3 are passed centrally through the drive motor 15 and the gear 16.
  • the axis AH of the hollow screw 19 are designed substantially coaxially to the motor axis AM of the drive motor 15.
  • the drive shaft 21 of the drive motor 15 is designed as a hollow shaft.
  • the gear 16 is configured so that the back-rigid chain 3 can be passed centrally through the gear 16.
  • a central transmission hollow shaft offers.
  • the driving gear shaft 23 is configured as a hollow shaft and coupled to the hollow screw 19. In such an embodiment, it is not absolutely necessary to redirect the back-stiff chain 3.
  • the back-rigid chain 3 transmits a thrust in both directions.
  • the thrust force is applied away from the drive motor 15, because in this direction usually the largest actuation length is available (see thrust direction S in Fig. 6).
  • a suitable guide for the back-rigid chain 3 can then not extend through the hollow screw 19, but also through the gear 16 and the drive motor 15.
  • the linear actuator 1 is preferably driven electrically and can replace the concept hydraulic cylinder or pneumatic cylinder. Therefore, slim designs with a thrust force application in the longitudinal direction along the axis AH of the hollow screw 19 and the motor axis AM of the drive motor 15 are to be preferred.
  • the drive motor 15 together with the gear 16 and the hollow screw 19 can be accommodated in a common housing 2, at the front end of the actuating region of the back-rigid chain 3 emerges.
  • a chain depot 29 can be accommodated within this housing 2, so that there is a structural unit, similar to a hydraulic cylinder or a pneumatic cylinder.
  • the housing 2 may at a the actuating region of the back-rigid chain 3 opposite end with a corresponding attachment means, for. B.
  • First intervention means e.g. Worm, hollow worm, sprocket etc.
  • second engaging means e.g. Chain bolt, roller etc.

Landscapes

  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Refuge Islands, Traffic Blockers, Or Guard Fence (AREA)
  • Transmission Devices (AREA)

Abstract

La présente invention concerne un entraînement linéaire comprenant un moteur d'entraînement, un premier élément à engrènement ou à prise, pouvant être entraîné par le moteur d'entraînement, et une chaîne anti-retour, la chaîne anti-retour présentant des seconds éléments à engrènement ou à prise qui coopèrent avec le premier élément à engrènement ou à prise afin d'entraîner la chaîne anti-retour. Un dispositif de logement de chaîne est également prévu, lequel dispositif est disposé au moins en partie sur le côté du moteur d'entraînement (29) qui est opposé à la sortie (45) de l'arbre (44) de moteur, la chaîne anti-retour (3, 3.1, 3.2) étant guidée au moins en partie le long du moteur d'entraînement (29).
EP18745869.0A 2017-07-20 2018-07-19 Entraînement linéaire à chaîne anti-retour Pending EP3673132A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017116435.9A DE102017116435A1 (de) 2017-07-20 2017-07-20 Linearantrieb mit rückensteifer Kette
PCT/EP2018/069686 WO2019016337A1 (fr) 2017-07-20 2018-07-19 Entraînement linéaire à chaîne anti-retour

Publications (1)

Publication Number Publication Date
EP3673132A1 true EP3673132A1 (fr) 2020-07-01

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Family Applications (3)

Application Number Title Priority Date Filing Date
EP18789562.8A Pending EP3685000A1 (fr) 2017-07-20 2018-07-19 Entraînement linéaire ayant une chaîne de renfort arrière
EP18745869.0A Pending EP3673132A1 (fr) 2017-07-20 2018-07-19 Entraînement linéaire à chaîne anti-retour
EP18746127.2A Pending EP3676470A1 (fr) 2017-07-20 2018-07-19 Entraînement linéaire à chaîne anti-retour

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EP18789562.8A Pending EP3685000A1 (fr) 2017-07-20 2018-07-19 Entraînement linéaire ayant une chaîne de renfort arrière

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EP18746127.2A Pending EP3676470A1 (fr) 2017-07-20 2018-07-19 Entraînement linéaire à chaîne anti-retour

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DE (1) DE102017116435A1 (fr)
WO (3) WO2019016340A1 (fr)

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DE102020113726A1 (de) 2020-05-20 2021-11-25 Brose Schließsysteme GmbH & Co. Kommanditgesellschaft Türaufsteller mit Schubkette

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DK135995A (da) * 1995-12-01 1997-06-02 Rasmussen Kann Ind As Operator med mindst to udstillerelementer til åbning og lukning af svingbare vinduer
DE60216414T3 (de) 2002-04-09 2010-09-09 Vkr Holding A/S Kompakt-Aktuator
ITMI20061026A1 (it) 2006-05-25 2007-11-26 Autotek Srl Gruppo per la movimentazione di tendine e simili particolarmente su autoveicoli
JP2011137514A (ja) 2009-12-28 2011-07-14 Tsubakimoto Chain Co 噛合チェーン式進退作動装置
JP2011144874A (ja) 2010-01-14 2011-07-28 Tsubakimoto Chain Co 噛合チェーン式進退作動装置
DE102014101583A1 (de) * 2013-09-19 2015-03-19 Hörmann KG Antriebstechnik Türantriebsvorrichtung sowie damit versehene drehtür
DE202015100189U1 (de) * 2015-01-16 2015-03-04 SCHÜCO International KG Antriebsvorrichtung für den dreh- und kippbar an einem Blendrahmen angeordneten Flügel eines Fensters oder einer Tür

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DE102017116435A1 (de) 2019-01-24
EP3676470A1 (fr) 2020-07-08
WO2019016337A1 (fr) 2019-01-24
WO2019016340A1 (fr) 2019-01-24
WO2019016333A1 (fr) 2019-01-24
EP3685000A1 (fr) 2020-07-29

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