EP1845226A1 - Schliessermechanismus - Google Patents

Schliessermechanismus Download PDF

Info

Publication number
EP1845226A1
EP1845226A1 EP06112642A EP06112642A EP1845226A1 EP 1845226 A1 EP1845226 A1 EP 1845226A1 EP 06112642 A EP06112642 A EP 06112642A EP 06112642 A EP06112642 A EP 06112642A EP 1845226 A1 EP1845226 A1 EP 1845226A1
Authority
EP
European Patent Office
Prior art keywords
rotary
closure mechanism
input element
output element
converting means
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.)
Withdrawn
Application number
EP06112642A
Other languages
English (en)
French (fr)
Inventor
Joseph Talpe, Jr.
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP06112642A priority Critical patent/EP1845226A1/de
Publication of EP1845226A1 publication Critical patent/EP1845226A1/de
Withdrawn legal-status Critical Current

Links

Images

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
    • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
    • E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
    • E05F3/10—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes with a spring, other than a torsion spring, and a piston, the axes of which are the same or lie in the same direction
    • E05F3/108—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes with a spring, other than a torsion spring, and a piston, the axes of which are the same or lie in the same direction with piston rod protruding from the closer housing; Telescoping closers
    • 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
    • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
    • E05F3/16—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with friction brakes
    • 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
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/21—Brakes
    • 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
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/23—Actuation thereof
    • E05Y2201/232—Actuation thereof by automatically acting means
    • E05Y2201/242—Actuation thereof by automatically acting means using threshold speed
    • 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
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/252—Type of friction
    • E05Y2201/26—Mechanical friction
    • 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
    • E05Y2201/20—Brakes; Disengaging means; Holders; Stops; Valves; Accessories therefor
    • E05Y2201/262—Type of motion, e.g. braking
    • E05Y2201/266—Type of motion, e.g. braking rotary

Definitions

  • the present invention relates to a closure mechanism for members hinged to structures as defined in the preamble of claim 1.
  • the closure mechanism defined in the preamble of claim 1 comprises more particularly a first and a second part, each one of them substantially rigid and pivotally attachable to one of the hinged member or structure, guided relative to each other in a linear translational motion between a first and a second position and urged towards a first position wherein the closure member is closed by a resilient element interposed between them.
  • the closure mechanism is of the type wherein the distance between the attachment points of the first and the second parts to the hinged member and the structure varies upon opening or closing of the hinged member not by a relative rotational motion of both parts with respect to one another but by a translational motion.
  • US-A-4 872 239 tries to remedy these problems by converting the relative linear translational motion of the first and second parts into a rotational motion and braking it by using a rotary braking device instead of the previous hydraulic dampers.
  • the rotary braking device of this prior art is a friction brake of the type that generates a constant braking torque, irrespective of the rotational speed of its input and thus of the closing speed of the hinged closure member.
  • An object of the present invention is therefore that of providing a closure mechanism with a safe closing speed at and from all opening angles and a high degree of reliability, even for outdoor applications.
  • the closure mechanism according to the invention is characterised in that the rotary braking device is of the type that, when in use, brakes its input element with a variable braking torque which increases and decreases with the rotational speed of the input element of the rotary braking device, the rotary braking device preferably comprising a centrifugal brake.
  • the braking torque of the closure mechanism increases with the closing speed of the hinged member until braking torque and driving force of the resilient element reach a state of equilibrium and the closing speed stabilises. In this way, the invention ensures a safe closing speed at and from all opening angles without compromising the closing performance.
  • centrifugal brakes to provide a variable braking torque, for instance in US-A-5 048 151 and in US-A-4 912 806 .
  • These prior art mechanisms comprise also two parts which are respectively attached to the hinged member and to the structure onto which the hinged member is mounted but the two parts are pivotally connected to one another so that a varying distance between their attachment points to the hinged member and the structure is obtained by a relative rotational motion.
  • One part is more particularly a lever arm so that the rotation of the closure member is converted in a corresponding rotation of the first gear wheel of the closure mechanism. In this way, when opening the closure member over an angle of 90°, the first gear wheel of the closure mechanism is also rotated only over a fraction of one rotation.
  • British patent GB 190002775 also proposed a centrifugal brake for a door check, however without such a high speed-up ratio. Due to the low speed-up ratio or in other words due to the small centrifugal force, it appears that this door check would not work satisfactorily, despite special measures having been taken to try to achieve the required braking force. First of all it is clear that the frictional coefficient between the braking pads (weighted arms) and the braking surface has to be quite high to be able to produce the required braking torque. In GB 190002775 this is attempted by the use of leather. An essential feature of the door check disclosed in GB 190002775 is further that it comprises means for urging the braking pads away from the braking surface.
  • the braking pads are in particular mounted on pivots that are inclined so that gravity tends to swing the braking pads away from the braking surface. It is clear that adjusting the weight of the braking pads, the inclination of their pivots and the frictional coefficient between the braking pads and the braking surface is quite delicate to achieve the desired braking effect. Moreover, the door check may become quite easily disordered when the frictional coefficient changes for example due to wear or to varying weather conditions (humidity, ice formation, temperature changes, etc.). It must also be noted that GB 190002775 concerns a door check that merely brakes external forces acting on the door, not a closure mechanism with a driving actuator.
  • the closure mechanism of the invention further comprises a transmission gearing comprising one or more stages increasing the rotational speed between the output element of the motion converting means and the input element of the rotary braking device. Increasing the rotational speed and reducing the torque at the rotary braking device, facilitates a progressive action of the rotary braking device while keeping it light and compact.
  • the closure mechanism of the invention further comprises a one-way clutch, preferably comprising a ratchet wheel, so as to enable rotation of said rotary output element of the motion converting means without rotating said rotary input element of the rotary braking device when the first part is moved towards the second position.
  • a one-way clutch preferably comprising a ratchet wheel
  • At least one speed-up stage of the transmission gearing is placed between the one-way clutch and the input element of the rotary braking device.
  • the advantage of this embodiment is to reduce the rotational speed of the one-way clutch so that it is less subjected to wear and produces less noise.
  • the closure mechanism of the invention further comprises a torque limiter, preferably comprising a friction clutch set to slip at a predetermined torque, so as to limit the maximum torque transmitted between said rotary output element of the motion converting means and said rotary input element of the rotary braking device.
  • a torque limiter preferably comprising a friction clutch set to slip at a predetermined torque, so as to limit the maximum torque transmitted between said rotary output element of the motion converting means and said rotary input element of the rotary braking device.
  • the torque limiter is contained within one gearwheel of the transmission gearing. This has the advantage of improved compactness.
  • At least one speed-up stage of the transmission gearing is placed between the output element of the motion converting means and the torque limiter.
  • the motion converting means comprises a rack-and-pinion gear.
  • the rack is formed on or attached to the first part.
  • the resilient element is a coil spring, which provides strength and reliability.
  • the closure mechanism of the invention also comprises a pivot device mounted on a base member of the first or second part for pivotally attaching said first or second part to the hinged member or structure, the pivot device being mounted so that it can rotate on the base member around a first axis substantially different to a second axis on which it is pivotally attachable to the hinged member or structure, the first axis being preferably substantially perpendicular to the second axis.
  • the closure mechanism adapts itself to various angles of attachment to the hinged member or structure and is protected from potential damage resulting from misalignment of the pivots.
  • Figs. 1 and 2 depict a closure member D, in this example a door leaf or garden gate, hinged to a structure F, in this example a post. Between the door leaf D and the post F, a compact closure mechanism C according to the invention, is installed which comprises a first part 1 which is pivotally attached to the hinged door leaf D, and a second part 2 which is pivotally attached to the door frame F.
  • the door leaf D and closure mechanism C are represented both in the open and closed position.
  • the first part 1 and second part 2 move towards each other in a relative translational motion.
  • the first part 1 and second part 2 are urged apart, thus pushing the door leaf D back towards the closed position wherein the first part 1 is in its first or extended position with respect to the second part 2.
  • the first part 1 comprises a sleeve 1' which is telescopically slidable over a corresponding sleeve 2' of the second part 2, so as to guide the first part 1 between its first position, wherein the door is closed, and a second position in a linear translational motion relative to the second part 2.
  • the closure mechanism C is mounted preferably in such a manner on the closure member D and on the structure f that, when opening the closure member D over an angle of 90°, the first part 1 moves over a distance of at least 100 mm, preferably over a distance of at least 120 mm with respect to the second part 2.
  • the first part moves over a distance of about 140 mm with respect to the second part.
  • the closure mechanism C also comprises means, including, for example, a plastic sliding bearing 3, for holding the first part 1 and the second part 2 together.
  • the closure mechanism C also comprises a resilient element 4 placed between the first and second parts 1, 2 so as to urge the first part 1 in the direction 5 of the linear translational motion towards its first position, i.e. towards the position wherein the closure member is closed.
  • the closure mechanism C further comprises a motion converting device 6 for converting the linear translational motion of said first part 1 relative to said second part 2 into a rotational motion of an output element 6o of said converting means 6, and a rotary braking device 7 which comprises an input element 7i coupled directly or indirectly to the output element 6o of the motion converting device 6 and arranged to be braked at least when the first part 1 moves towards its first position, i.e. when the closure member is closed by means of the resilient element 4.
  • the first part 1 comprises a base member 8, in the form of a cylindrical rod, and a pivot device 9 which can pivot with respect to this rod.
  • the second part 2 has the form of a housing containing i.a. the motion converting device 6 and the rotary braking device 7.
  • the resilient element 4 is embodied in a coil spring, which surrounds the base member 8 and is itself housed in the two telescoping sleeves 1' and 2', so as to be guided therein and protected from the outside environment.
  • the converting means 6 comprises a rack-and-pinion gear, with the rack 10 formed on the base member 8 of the first part 1 and a 12-teeth pinion 11 on the output element 6o of the motion converting means 6.
  • the motion converting means 6 could be of a different type, such as a ball screw, but the depicted rack-and-pinion gear has the advantages of cheapness, simplicity and reliability.
  • the coil spring as the resilient element 4, such as air and elastomeric springs, but the coil spring also appears to be particularly advantageous for this invention.
  • the rotary output element 6o of the motion converting means 6 is coupled, in the depicted normal closing operation, to the input element 7i of the rotary braking device 7 through a transmission gearing 12 comprising three stages increasing the rotational speed between the output element 6o of the motion converting means 6 and the input element 7i of the rotary braking device 7.
  • the transmission gearing 12 is a gearwheel train.
  • a significant advantage of the invention is that, since it does not require a high speed-up ratio between the output element 6o of the motion converting means 6 and the input element 7i of the rotary braking device 7, it allows the use of a simple transmission gearing 12, having at most four speed-up stages, and preferably at most three, as in this example wherein the transmission gearing 12 comprises three speed-up stages, each stage having individual speed-up ratios under 6 and preferably under 5 and gearwheels smaller than 8 cm in diameter, and preferably under 6 cm, so that the mechanism can be kept quite compact.
  • the total speed-up ratio of the transmission gearing 12 can be less than 80, preferably less than 60. However, it would be advantageous to have a speed-up ratio of more than 15, and preferably more than 25. As will appear from the following description, the total speed-up ratio of the transmission gearing illustrated in the figures is about 43.7.
  • a one way-clutch 13 is placed between the output element 6o of the motion converting means 6 and the transmission gearing 12.
  • This one-way clutch 13, as can be seen in Fig. 4, essentially consists in a ratchet-wheel 14 formed on the inside of a first gearwheel 15 of the transmission gearing 12, and two pawls 16, resiliently mounted on the output element 6o of the motion converting means 6, so as to engage with the ratchet wheel 14 only when the output element 6o rotates in one direction.
  • the first gearwheel 15, having 40 teeth engages a second pinion (not illustrated but having 12 teeth), formed on the same axle as a second gearwheel 17, which has 52 teeth and engages a third pinion 18 having 14 teeth.
  • this third pinion 18 is coupled to a torque limiter 19 in the form of a friction clutch interposed between the third pinion 18 and a third gearwheel 20 (which has 46 teeth).
  • the torque limiter 19 comprises a first friction disc 21, mounted so as to rotate with the third pinion 18, and a second friction disc 22, mounted so as to rotate with the third gearwheel 20.
  • the first and second friction discs 21, 22 are pushed together by a clutch spring 23 with a force that can be calibrated with a calibrating screw 24.
  • the maximum torque of the torque limiter 19 will depend on that force and the friction coefficient between the two friction discs 21, 22.
  • one of the friction discs 21 or 22 is made of stainless steel, whereas the other friction disc 21 or 22 is made of a friction material of the type used in brake pads, so that the friction coefficient between the two friction discs 21, 22 remains substantially constant, regardless of temperature or humidity.
  • a friction coefficient of at least 0.3 and preferably at least 0.35 allows the use of a small clutch spring 23, thus contributing to the compactness of the closure mechanism C.
  • the torque limiter 19 is contained within the third gearwheel 20, in an arrangement particularly advantageous for the purpose of obtaining a compact closure mechanism C.
  • the third gearwheel 20 engages a fourth pinion 25 (not illustrated in Fig. 3 but having 13 teeth) formed on the rotary input element 7i of the rotary braking device 7.
  • the rotary braking device 7 of this embodiment comprises essentially two braking pads 26 eccentrically hinged to the input element 7i of the rotary braking device 7, so as to be urged against a braking surface 27 (not illustrated in Fig. 6) surrounding them, with a centrifugal force proportional to the square of the rotational speed of the input element 7i of the rotary braking device 7.
  • centrifugal brake of this embodiment such as a rotary hydrodynamic brake
  • a rotary hydrodynamic brake can be considered, as long as they also generate a variable braking torque which increases and decreases with the rotational speed of the input element 7i of the rotary braking device 7.
  • the first part 1 moves, urged by the resilient element 4, in the direction 5 towards its first position in which the hinged member D will be closed.
  • the linear translational motion of the first part 1 relative to the second part 2 is converted by the motion converting means 6 into a rotational motion of the output element 6o of said motion converting means 6.
  • an angular motion of 90° by the hinged member D will be converted, through the linear translational motion of the first part 1 relative to the second part 2 and the motion converting means 6, into about four full revolutions of the output element 6o of said motion converting means 6.
  • This rotational motion is transmitted through the speed-up stages of the transmission gearing 12 to the input element 7i of the rotary braking device 7.
  • the rotational speed of the input element 7i of the rotary braking device 7 also increases. As the rotational speed of the input element 7i increases, so will the braking torque generated by the centrifugal brake in the rotary braking device 7, until it compensates the driving force of the resilient element 4. As the braking torque balances out the driving force of the resilient element 4, the first part 1 and therefore the hinged member will cease to accelerate. A state of equilibrium will be reached in which the braking torque and the driving force cancel each other until the first part 1 reaches first position is reached and/or the hinged member closes. In practice, the closure member may close in about 4 seconds.
  • this corresponds to a rotational speed of the input element 7i of the centrifugal brake 7 of about 2600 rpm, thus enabling an effective braking action even when the centrifugal brake 7 has limited dimensions (inner diameter of the braking surface smaller than 7 cm and preferably smaller than 5 cm) to fit in a compact closure mechanism.
  • Figs. 7 to 9 the operation of this closure mechanism C during an opening motion of the hinged member will be explained.
  • the one-way clutch 13 therefore has the purpose of letting the output element 6o of the motion converting means 6 freewheel during this opening motion, as depicted in Figs. 7 and 8, so that its rotational motion is not transmitted to the gearwheel 15.
  • the pawls 16 engage the ratchet wheel 14, and the one-way clutch 13 transmits the rotational motion of the output element 6o to the gearwheel 15, as depicted in Fig. 9.
  • Coupling the one-way clutch 13 directly to the output element 6o of the motion converting means has the advantage that, before the speed-up stages of the transmission gearing 12, the rotational speed is still moderate, and such one-way clutches perform more reliably at moderate rotational speeds.
  • Other arrangements of ratchet wheels, as well as alternative types of one-way clutches, as known by the skilled person, could alternatively be used.
  • Figs. 10 and 11 the operation of this closure mechanism C during an accelerated closing motion of the hinged member in which the driving force of the resilient element 4 is significantly reinforced by external forces, such as those exerted by a user, the wind, etc. will be illustrated.
  • the braking torque generated by the rotary braking device 7 and the rotational speed of the input element 7i of the rotary braking device 7 could increase so much that the closure mechanism could be overloaded and damaged.
  • the torque limiter 19 therefore has the purpose of limiting the maximum torque that can be transmitted between the motion converting means 6 and the rotary braking device 7 in such a situation to prevent an overload.
  • Figs. 10 and 11 the operation of this closure mechanism C during an accelerated closing motion of the hinged member in which the driving force of the resilient element 4 is significantly reinforced by external forces, such as those exerted by a user, the wind, etc.
  • the pivot device 9 of the first part 1 is illustrated in detail.
  • the pivot device 9 is mounted on the base member 8, i.e. onto the rod, so that it can rotate on said base member 8 around a first axis 28 perpendicular to a second axis 29 on which the pivot device 9 is pivotally attached to the hinged member D.
  • the first axis 28 is the axis of the linear translational motion of the first part 1 relative to the second part 2.
  • the purpose of the rotational mounting of the pivot device 9 is to enable the closure mechanism C to be adapted to various angles of attachment to the hinged member D or structure F, while ensuring that the rack-and-pinion motion converting means 6 is not submitted to damaging torsion loads.
  • the cylindrical rod forming the first part 1 comprises a circumferential notch 30 near the end of the first part distal to the second part 2.
  • the pivot device 9 in turn comprises at least one pin 31, preferably two, slotting into said circumferential notch 30 so as to restrain the pivot device 9 axially, while allowing its rotation around base member 8.

Landscapes

  • Closing And Opening Devices For Wings, And Checks For Wings (AREA)
EP06112642A 2006-04-13 2006-04-13 Schliessermechanismus Withdrawn EP1845226A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06112642A EP1845226A1 (de) 2006-04-13 2006-04-13 Schliessermechanismus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06112642A EP1845226A1 (de) 2006-04-13 2006-04-13 Schliessermechanismus

Publications (1)

Publication Number Publication Date
EP1845226A1 true EP1845226A1 (de) 2007-10-17

Family

ID=37075973

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06112642A Withdrawn EP1845226A1 (de) 2006-04-13 2006-04-13 Schliessermechanismus

Country Status (1)

Country Link
EP (1) EP1845226A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3109389A1 (de) * 2015-06-26 2016-12-28 Locinox Vorrichtung zum schliessen eines drehflügels

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1353219A (en) * 1919-12-22 1920-09-21 Thomas E Collins Door check and closer
US2708284A (en) * 1950-02-01 1955-05-17 Schlage Lock Co Magnetically damped door closer
EP0298514A1 (de) * 1987-07-10 1989-01-11 Kabushiki Kaisha Sankyo Seiki Seisakusho Mechanischer Türschliesser
US4872239A (en) * 1988-08-10 1989-10-10 The Chamberlain Group, Inc. Door closure with mechanical braking means
US6891479B1 (en) * 2003-06-12 2005-05-10 Jon E. Eccleston Remotely controllable automatic door operator and closer
US20050206286A1 (en) * 2004-03-16 2005-09-22 Manitowoc Foodservice Companies, Inc. Door control assembly

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1353219A (en) * 1919-12-22 1920-09-21 Thomas E Collins Door check and closer
US2708284A (en) * 1950-02-01 1955-05-17 Schlage Lock Co Magnetically damped door closer
EP0298514A1 (de) * 1987-07-10 1989-01-11 Kabushiki Kaisha Sankyo Seiki Seisakusho Mechanischer Türschliesser
US4872239A (en) * 1988-08-10 1989-10-10 The Chamberlain Group, Inc. Door closure with mechanical braking means
US6891479B1 (en) * 2003-06-12 2005-05-10 Jon E. Eccleston Remotely controllable automatic door operator and closer
US20050206286A1 (en) * 2004-03-16 2005-09-22 Manitowoc Foodservice Companies, Inc. Door control assembly

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3109389A1 (de) * 2015-06-26 2016-12-28 Locinox Vorrichtung zum schliessen eines drehflügels
US9765558B2 (en) 2015-06-26 2017-09-19 Locinox Device for closing a hinged member

Similar Documents

Publication Publication Date Title
US20090107051A1 (en) Closure mechanism
US7562757B2 (en) Actuating device with at least one actuating arm
US7296380B2 (en) Device for operating a door leaf or the like and door structure provided with such a device
US8281677B2 (en) Electromotive linear drive
US8567011B2 (en) Door closing mechanism
US20060131111A1 (en) Braking apparatus for closure members
FR2480457A1 (fr) Limiteur de force
CA2352620A1 (en) Anti-back drive chain hoist
EP0247148A1 (de) Zurückziehanordnung für türen oder fenster
EP1845226A1 (de) Schliessermechanismus
US20080010777A1 (en) Hinge damper in opening/closing device
CA2775463C (en) Self-closing device for sliding doors
US8510912B2 (en) Self-closing device for sliding doors
KR101805762B1 (ko) 차량용 도어체커
EP2186983A1 (de) Bidirektionaler Schließmechanismus
EP1620627B1 (de) Bewegungssteuerungsvorrichtung
JPH0740625Y2 (ja) 過負荷防止ドアクローザー
EP1681490B1 (de) Dämpfersystem zum Dämpfen der Rotationsbewegung eines Rotationskörpers und Scharnier mit einem solchen System
EP1486154A1 (de) Scharniersystem mit Dämpfer
JPH0235107B2 (ja) Jidoshayodoahandorusochi
JP7450266B2 (ja) 上げ下げ窓の釣合装置
JPH0450390Y2 (de)
JPH0710575U (ja) 開閉部材の作動緩衝装置
JPH0648072Y2 (ja) 便器等の調速装置
JP2007315052A (ja) 折り戸の連結装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20071204

17Q First examination report despatched

Effective date: 20080118

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20091103