EP1431496A2 - Entraínement servo-électrohydraulique pour commande de porte, fenêtre ou similaire - Google Patents

Entraínement servo-électrohydraulique pour commande de porte, fenêtre ou similaire Download PDF

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Publication number
EP1431496A2
EP1431496A2 EP03029398A EP03029398A EP1431496A2 EP 1431496 A2 EP1431496 A2 EP 1431496A2 EP 03029398 A EP03029398 A EP 03029398A EP 03029398 A EP03029398 A EP 03029398A EP 1431496 A2 EP1431496 A2 EP 1431496A2
Authority
EP
European Patent Office
Prior art keywords
valve
door drive
drive according
electro
servo door
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Withdrawn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
EP03029398A
Other languages
German (de)
English (en)
Other versions
EP1431496A3 (fr
Inventor
Sven Busch
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.)
Dorma Deutschland GmbH
Original Assignee
Dorma Deutschland GmbH
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 Dorma Deutschland GmbH filed Critical Dorma Deutschland GmbH
Publication of EP1431496A2 publication Critical patent/EP1431496A2/fr
Publication of EP1431496A3 publication Critical patent/EP1431496A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/065—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the rack-and-pinion type
    • 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
    • E05F15/50—Power-operated mechanisms for wings using fluid-pressure actuators
    • E05F15/53—Power-operated mechanisms for wings using fluid-pressure actuators for swinging wings
    • 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
    • E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
    • E05F3/223—Hydraulic power-locks, e.g. with electrically operated hydraulic valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/025—Installations or systems with accumulators used for thermal compensation, e.g. to collect expanded fluid and to return it to the system as the system fluid cools down
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/224—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston which closes off fluid outlets in the cylinder bore by its own movement
    • 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
    • E05F3/102—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 rack-and-pinion transmission between driving shaft and piston within the closer housing
    • 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
    • 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

Definitions

  • the invention relates to an electrohydraulic servo door drive for driving a door, a window or the like with an open function, whereby to perform the hold-open function in the hydraulic circuit a valve is arranged.
  • Such a servo door drive is well known.
  • the hold-open function of the servo door drive usually by a solenoid valve reached, which the discharge of the hydraulic fluid from the piston chamber of the servo door drive prevented.
  • a disadvantage of this embodiment is the space required for this and the additional costs.
  • valve is designed as a hydraulically controlled hold-open valve costs can be saved because such a hold-open valve is cheaper than the solenoid valve previously used. Because the solenoid valve must be purchased while the hydraulically controlled Hold-open valve can be manufactured by yourself.
  • the Advantage of improved fire protection since the valve according to the invention in the event of a power failure, the servo door drive according to the invention connected door closes automatically. A failure in one Case is excluded and the efficiency of the door operator is not affected. Furthermore, due to the construction according to the invention Overload protection integrated in the servo door drive as well as one Closing sequence control for a double-leaf door.
  • the door can be kept permanently open, since only a low control pressure is required, which, for. B. from a motor pump unit over a very long period of time without the risk of Overheating, and maintain with minimal brush burn can be.
  • the servo door drive according to the invention when switched off Motor works unaffected by the hydraulic drive, so that no additional switching valve is required.
  • An open valve according to the invention preferably consists of a 2-2-way valve.
  • This 2-2-way valve allows the hydraulic fluid to flow back be prevented from the piston space into a tank space.
  • the 2-2-way valve is designed to be relatively small Control pressure is a pressure several times greater in the piston chamber of the servo door drive can be held. This way the door can be against the The spring force of the servo door drive can be kept permanently open the engine is only lightly loaded.
  • the hold-open valve has one Control piston and a check valve on.
  • the control piston is through controlled a lower pump pressure compared to the delivery pressure, which results in a large control area compared to the sealing area of the 2-2-way valve is available.
  • Through the check valve achieved a hydraulic separation of the piston chamber and pump, so that a backflow of hydraulic fluid from the piston chamber over the Check valve is prevented. This is required to the 2-2 way valve to control using the pump pressure. If namely the delivery pressure the pump is less than the pressure in the piston chamber, are both areas hydraulically separated from each other so that the 2-2-way valve with The pump can be controlled.
  • the pressure in the piston chamber of the servo door drive is preferably around several times greater than the control pressure in the hold-open valve. In this way can a door provided with the servo door drive according to the invention against the spring force permanently existing in the swing door operator Spring to be kept open.
  • a DC motor as an electronically commutated motor or as a speed-controllable alternating or three-phase motor provided motor, which is a pump drives, because only with such engines, the engine torque and engine speed can be changed and a permanent open function with low Power losses can be realized.
  • the inflow and the backflow of the hydraulic circuit are preferred separated from each other. This reduces the number of required Valves, but requires an additional hydraulic line.
  • check valve in the control piston of the hold-open valve integrated.
  • this can Check valve also provided in a bypass to the hold-open valve his.
  • Throttle valves are provided.
  • the hold-open valve according to the invention is preferably via the Pump pressure controlled.
  • the electrohydraulic device is Servo door drive with an auxiliary device for execution a support function for the operation of the door, the window or the like.
  • This enables the integration of others Basic functions in the door operator. So z. B. the door from the user without any significant effort and supported by the drive without the door opening automatically. The door can then again with a according to the fire protection regulations sufficiently large torque can be closed without motor power.
  • a hold-open function or a closing delay can be activated can be integrated into the servo door drive according to the invention.
  • End position damping can be implemented to stop the To prevent door.
  • the auxiliary device has a motor amplifier connected to the motor, especially according to the PWM principle (pulse width modulation), on.
  • the motor amplifier is connected to a control and current regulation connected.
  • control and current regulation preferably provided with a D / A converter.
  • Figure 1 is a servo door drive according to the invention after a first Embodiment shown.
  • the closing movement of the swing door drive controlled by throttle valves.
  • the servo door drive has a piston chamber 1, in which a piston 2 is movable against the force of a spring 3.
  • the piston 2 is with a Toothing 4 provided, which meshes with a pinion 5, which with a Locking mechanism, not shown, for a door, a window or the like works together.
  • the toothing 4 is shown in the Embodiment formed inside the piston 2. As a result of one Movement of the piston 2 is via the toothing 4, the pinion 5 in one Offset rotary movement.
  • the piston 2 is at both ends with sealing washers 10 and 11 provided which sealing on an inner wall of the piston chamber 1 concern.
  • the sealing washers 10 and 11 are to avoid destructive overpressures pressure relief valves 12 and 13 brought in.
  • the pressure relief valve 13 is only in combination with hydraulic opening damping by a throttle valve 18 necessary, because otherwise none in this area of the piston chamber 1 critical pressures can occur.
  • a check valve 15 which is a manual opening enables the door even when the drive is switched off.
  • a check valve 14 leaves the hydraulic fluid with little loss when the door is opened automatically flow past throttle valves 17 into the piston chamber 1. How the valves 12 to 18 are arranged in detail, can be seen in Figure 1 become.
  • the check valve 15 is located in the sealing disk 10 and the pressure relief valve 12. Here is the pressure relief valve 12 spring loaded. Furthermore, the valves 12 and 15 are used antiparallel. The same number and type of valves 13 and 16 are also in the Sealing disc 11 is present, only these valves are in the same direction installed so that an overpressure from the spring chamber into the piston 2 can escape.
  • the piston 2 is driven by a hydraulic circuit, which Hydraulic lines to the piston chamber 1 is connected.
  • a pump 6 is provided which is driven by a motor 7 becomes.
  • the motor 7 is preferably as a DC motor or as speed-controllable AC or three-phase motor designed because at these engine types the engine torque and engine speed on simple Ways can be varied and a continuous function with little Power losses can be realized.
  • the 2-2-way valve is designed with a relatively small control pressure on the control piston 22 a multiple times greater pressure in the piston chamber 1 of the swing door drive can be kept and the return flow the hydraulic fluid in the tank space 8 is prevented, so that the door, window or the like is kept permanently open can be, the motor 7 is only slightly loaded. If So the delivery pressure of the pump 6 is less than the pressure in the piston chamber 1, both areas are hydraulically separated from each other, so with the help the pump 6 now controls the 2-2-way valve by the control piston 22 can be.
  • the throttle valves 17 and 18 are also provided in the hydraulic circuit, which are used to control the opening and closing movements and the exact arrangement of which can be seen in FIG. 1.
  • the exact routing and connection of hydraulic lines 41 to 46 of the hydraulic circuit are shown in Figure 1. In doing so the hydraulic lines 43 and 45 controlled by the piston 2.
  • the tank room 8 is z. B. by a hydraulic accumulator formed, even with a small change in volume of the hydraulic fluid, how they can arise from temperature changes, an approximately constant low pressure on the suction side of the pump 6 causes so that a shaft sealing ring of the pump is permanently relieved.
  • This compensation memory can, for example, by a gas bubble Gas bubble accumulator with elastic membrane or bubble, a piston accumulator be formed with or without a spring or the like.
  • FIG. 2 shows a second embodiment of the invention Swing door drive shown.
  • This embodiment differs from that shown in Figure 1 in that here the inflow from the backflow is separated.
  • This has the advantage that the same function Check valve 14 of Figure 1 is no longer required, instead a hydraulic line 47 is required. Since in the shown in Figure 2 Hydraulic opening damping can be dispensed with the pressure relief valve 13 from FIG. 1 is also eliminated and by a Connection line 48 to be replaced. As in this case, the structure of the Hydraulic lines and the arrangement of the various valves Figure 2 shows.
  • FIG. 3 shows a first embodiment of the hold-open valve 20.
  • the 2-2-way valve 21 is on the left in Figure 3 through the Hydraulic line 41 with the pump 6 and on the right in Figure 3 connected to the piston chamber 1 by the hydraulic line 42.
  • a hydraulic line 46 directed upwards leads to the tank space 8
  • Control piston 22 is provided with a through bore 49, which consists of two areas with different diameters. On the for Piston chamber 1 leading side is the diameter of the through hole 49 smaller than on the side leading to pump 6. In the bigger one
  • the check valve 23 is arranged in the area of the through bore 49, which is integrated in the control piston 22.
  • control piston 22 there is between the control piston 22 and the one leading to the pump 6 Side (hydraulic line 41) arranged the spring element 27, which the control piston 22 to the right in Figure 3 in the direction of the connection of the hydraulic line 42 to the piston chamber 1 and thus in this position closes the hydraulic line 42 to the hydraulic line 46.
  • the check valve 23 and the hydraulic medium open can from the hydraulic line 41 through the through hole 49 flow into the hydraulic bore 42.
  • the control piston 22 can through a circumferential seal 24 or through the annular gap of a corresponding one Tight fit to be sealed.
  • FIG. 4 shows a second alternative embodiment of the hold-open valve 20 shown.
  • the connections 41 and 42 are the same as in the Explained in connection with Figure 3.
  • the difference to the embodiment according to Figure 3 is that the check valve 23 with the Spring element 26 is not integrated in the control piston 22, but in a bypass 50 is arranged, the connection of the hydraulic line 42 connects to the piston chamber 1 with the hydraulic line 41 to the pump 6. There is no through bore within the control piston 22.
  • the closing function is shown in the alternative embodiment in FIG the 2-2-way valve function through a separate closing body 9 realized in the form of a ball. This has the advantage that the Locking body 9 itself centered within a conical recess 53 and positional tolerances between the control piston 22 and the valve seat be balanced.
  • the control piston 22 is also through the spring element 27 biased towards the closing body 9.
  • FIG. 5 shows a third alternative embodiment of the hold-open valve 20, in contrast to the embodiments according to FIG Figure 3 and Figure 4, the inflow to the piston chamber 1 through the hydraulic line 42 and the bypass 50 and the return of the hydraulic fluid done separately by the hydraulic line 47.
  • FIG. 6 shows a fourth alternative embodiment of the hold-open valve 20, in contrast to the previously described embodiments the 2-2-way valve is designed as a slide valve.
  • the closing body of the 2-2-way valve is replaced by a cylindrical body formed, which closes the hydraulic line 46 depending on the switching position or releases.
  • the hydraulic line 46 ends on the one hand again in the Space of the control piston 22 and at the same time in one of the hydraulic lines 42 upstream space 52, in which a piston 51 is located.
  • the piston 51 is free-floating and much smaller in diameter than the control piston 22.
  • FIG. 7 shows a fifth alternative embodiment of the hold-open valve 20 shown, in which an adjustable valve 28 between Hydraulic line 41 and 46 is arranged to when the drive is switched off to achieve a faster pressure equalization on the control piston 22 and thereby increase the switching speed of the 2-2-way valve 21 and at the same time by suitable adjustment of a valve 28 the resulting additional leakage during operation to an acceptable level Limit measure.
  • FIG. 8 shows a sixth alternative embodiment of the hold-open valve 20, in contrast to the embodiment according to FIG Figure 7, the valve 28 is designed so that with increasing pressure in the Hydraulic line 41, the leakage flow additionally occurring at valve 28 is reduced or completely avoided when the operating pressure is reached can be.
  • a throttle body 29 of the throttle valve is supported 28 on a spring 31, so that when the pressure in the hydraulic line increases 41 the gap of the valve seat to the throttle body 29 is reduced or is closed completely. In this way, a small Switching time of the 2-2-way valve can be achieved without an additional Have to accept leakage current.
  • the throttle body 29 stands with an adjusting pin 30, which is equipped with a spring 32, in operative connection.
  • the pump 6 When the door is opened, the pump 6 generates a volume flow of hydraulic fluid, which is conveyed into the piston chamber 1. To do this, the Pump 6 due to the inertia of the door and the force of the spring 3 exert a correspondingly increased pressure on the piston 2. This increased Pressure closes and prevents the 2-2-way valve through the control piston 22 thereby draining the volume of liquid conveyed into the tank room 8.
  • the pump pressure is reduced.
  • the Check valve 23 of the hydraulically controlled hold-open valve 20 the pressure in the piston chamber 1 is maintained and a backflow into the pump 6 prevented.
  • the 2-2-way valve is replaced by a small one Control pressure from the pump 6 still kept closed.
  • the unit consisting of pump 6 and motor 7 is complete off. This also happens in the event of a power failure. As a result, the pressure drops due to leakage in the pump 6 or on the control piston 22 or on the additional valve 28 below a limit value, where the 2-2-way valve opens so that the hydraulic fluid flows through the throttle valves 17 can flow into the tank space 8.
  • a hydraulic pressure limitation or pressure control valve can be provided or you can Driving torque of the pump 6 by the motor torque or the motor current regulate.
  • the motor 7 is connected to a motor amplifier 51, who preferably works on the PWM principle.
  • the motor amplifier 51 is connected to a control and current regulation 52, in which is also a D / A converter 54 is arranged. Both the motor amplifier 51 as well as the control and current regulation 52 are included a voltage supply 55 connected.
  • With the control and current regulation 52 is also connected to a position transmitter 53 which is connected to the Pinion 5 interacts and the position of pinion 5 or piston 2 determined.
  • FIG. 2 shows a further embodiment of the servo door drive according to the invention shown. This differs from that shown in FIG. 1 through a different line routing and a different valve arrangement. As can be seen in particular in the upper left part of FIG. 2 here is a separation of the supply and discharge of the hydraulic fluid of the piston chamber 1 through the hydraulic lines 41, 42 and 47 Service. Furthermore, a hydraulic opening damping is shown in FIG as well as a closing damper with two pressure ranges Service.
  • the door drive shaft angle (phi) is a function of the spring force, the pump pressure, the motor torque and the motor current shown. It can be seen that the user exerts only a small force must to open the door.
  • the motor voltage is a manipulated variable for controlling the motor speed. At the same time, torque is limited by regulation given the motor current. The operating speed is therefore through Torque limitation below the motor characteristic at a maximum Drive voltage.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Power-Operated Mechanisms For Wings (AREA)
EP03029398A 2002-12-20 2003-12-19 Entraînement servo-électrohydraulique pour commande de porte, fenêtre ou similaire Withdrawn EP1431496A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10261225 2002-12-20
DE10261225A DE10261225B4 (de) 2002-12-20 2002-12-20 Elektrohydraulischer Servotürantrieb zum Antrieb einer Tür, eines Fensters oder dergleichen

Publications (2)

Publication Number Publication Date
EP1431496A2 true EP1431496A2 (fr) 2004-06-23
EP1431496A3 EP1431496A3 (fr) 2009-09-30

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Application Number Title Priority Date Filing Date
EP03029398A Withdrawn EP1431496A3 (fr) 2002-12-20 2003-12-19 Entraînement servo-électrohydraulique pour commande de porte, fenêtre ou similaire

Country Status (3)

Country Link
US (1) US6978609B2 (fr)
EP (1) EP1431496A3 (fr)
DE (1) DE10261225B4 (fr)

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CN101033671B (zh) * 2006-03-10 2012-06-27 Faac股份公司 用于门的移动的双效液压致动操作系统
EP3034890B1 (fr) 2014-12-17 2019-06-12 dormakaba Deutschland GmbH Soupape hydraulique et unité de commande d'entraînement comprenant une telle soupape hydraulique
EP4279695A1 (fr) * 2022-05-20 2023-11-22 GEZE GmbH Entraînement de porte

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DE102004061624C5 (de) * 2004-12-17 2011-02-03 Dorma Gmbh + Co. Kg Türantrieb, insbesondere Drehtürantieb
DE102004061628B4 (de) * 2004-12-17 2008-12-04 Dorma Gmbh + Co. Kg Türantrieb, insbesondere Drehtürantrieb
DE102004061619C5 (de) * 2004-12-17 2011-09-29 Dorma Gmbh + Co. Kg Türantrieb, insbesondere Drehtürantrieb
DE102004061626B4 (de) * 2004-12-17 2008-09-11 Dorma Gmbh + Co. Kg Türantrieb, insbesondere Drehtürantrieb
DE102004061627B4 (de) * 2004-12-17 2007-02-01 Dorma Gmbh + Co. Kg Türschließer
DE102004061620B3 (de) * 2004-12-17 2006-06-14 Dorma Gmbh + Co. Kg Türantrieb, insbesondere Drehtürantrieb
DE102004061630C5 (de) * 2004-12-17 2015-12-24 Dorma Deutschland Gmbh Türantrieb, insbesondere Drehtürantrieb
ITRM20060085U1 (it) * 2006-05-17 2007-11-18 Findisa S R L Sistema oleodinamico a bassa tensione a controllo elettronico di movimentazione di chiusure automatiche
GB2456508B (en) * 2008-01-15 2012-11-28 Heath Samuel & Sons Plc Door closer
US8261491B2 (en) 2008-04-02 2012-09-11 Leon Yulkowski Concealed electrical door operator
US8653982B2 (en) 2009-07-21 2014-02-18 Openings Door monitoring system
US8779713B2 (en) * 2010-04-16 2014-07-15 Yale Security Inc. Door closer with dynamically adjustable latch region parameters
US8564235B2 (en) * 2010-04-16 2013-10-22 Yale Security Inc. Self-adjusting door closer
CN102878125A (zh) * 2012-09-30 2013-01-16 徐州大亚自动装备有限公司 液压开窗机闭环控制系统
DE102014102806A1 (de) * 2014-03-03 2015-09-03 Mack Rides Gmbh & Co. Kg Sperrvorrichtung für eine Achse
US9651130B2 (en) * 2014-07-30 2017-05-16 Td Ip Holdco, Llc Gear assembly with spiral gears
US10378262B2 (en) 2014-10-23 2019-08-13 Leon Yulkowski Door operator and clutch
DE102015210860A1 (de) 2015-06-12 2016-12-15 Lehnhoff Hartstahl Gmbh & Co. Kg Schnellwechsler
CN105736796B (zh) * 2016-03-30 2018-09-21 太原理工大学 一种机电联动液控闸阀驱动器
DE202017105031U1 (de) * 2017-08-22 2017-08-29 Edscha Engineering Gmbh Antriebsvorrichtung für eine Fahrzeugklappe
CN113898263B (zh) * 2021-10-11 2023-05-23 苏世博（南京）减振系统有限公司 一种乘用车尾门防掉落保护装置

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US20040182234A1 (en) 2004-09-23
DE10261225B4 (de) 2006-11-16
DE10261225A1 (de) 2004-07-15
US6978609B2 (en) 2005-12-27
EP1431496A3 (fr) 2009-09-30

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