EP3563022B1 - Actionneur à amortisseur hydraulique et charnière à fermeture automatique comprenant l'actionneur - Google Patents

Actionneur à amortisseur hydraulique et charnière à fermeture automatique comprenant l'actionneur Download PDF

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Publication number
EP3563022B1
EP3563022B1 EP17823166.8A EP17823166A EP3563022B1 EP 3563022 B1 EP3563022 B1 EP 3563022B1 EP 17823166 A EP17823166 A EP 17823166A EP 3563022 B1 EP3563022 B1 EP 3563022B1
Authority
EP
European Patent Office
Prior art keywords
closure member
damper shaft
compartment
barrel
actuator
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.)
Active
Application number
EP17823166.8A
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German (de)
English (en)
Other versions
EP3563022C0 (fr
EP3563022A1 (fr
Inventor
Joseph Talpe
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Locinox NV
Original Assignee
Locinox NV
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Filing date
Publication date
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Publication of EP3563022A1 publication Critical patent/EP3563022A1/fr
Application granted granted Critical
Publication of EP3563022C0 publication Critical patent/EP3563022C0/fr
Publication of EP3563022B1 publication Critical patent/EP3563022B1/fr
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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
    • E05F3/08—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes in which a torsion spring rotates a member around an axis arranged in the direction of the axis of the piston
    • 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
    • E05F3/20—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices in hinges
    • 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
    • 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
    • E05Y2800/40—Physical or chemical protection
    • E05Y2800/414—Physical or chemical protection against high or low temperatures
    • 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
    • E05Y2900/40—Application of doors, windows, wings or fittings thereof for gates

Definitions

  • the present invention relates to hydraulically damped actuator for closing a closure member hinged to a support.
  • the present invention also relates to a hydraulically damped, self-closing hinge for hinging a closure member to a support which comprises the actuator.
  • the actuator comprises: an energy storing mechanism configured for storing energy when said closure member is being opened and for restoring said energy to effect closure of said closure member, the energy storing mechanism comprising a first and a second actuation member and a spring mechanism arranged between both actuation members, the actuation members being rotatable with respect to one another around a rotation axis in a first mutual direction to store said energy in said spring mechanism and in a second mutual direction, which is opposite to said first mutual direction, to restore said energy; a damping mechanism configured for damping a closing movement of said closure member, the damping mechanism comprising: a closed cylinder cavity that has a longitudinal direction and is filled with a volume of hydraulic fluid; a damper shaft having a first end extending into the cylinder cavity
  • Such a hydraulically damped actuator is disclosed in EP-A-2295693 and EP-A-2356305 .
  • the actuator disclosed therein is intended to be mounted to an outdoors hinged closure member, e.g. a gate, to effect closure thereof.
  • the closed cylinder cavity is filled with hydraulic fluid to damp the motion of the piston.
  • the hydraulic fluid is located in the low pressure compartment.
  • the piston is displaced and hydraulic fluid flows through the one-way valve and the restricted fluid passage to the high pressure compartment without severely affecting the motion of the piston.
  • the closure member is opened, the hydraulic fluid is located in the high pressure compartment.
  • the one-way valve is closed and hydraulic fluid is forced to flow from the high pressure compartment to the low pressure compartment via the restricted fluid passage thereby acting against the sliding movement of the piston, thus damping the closing movement of the closure member.
  • a disadvantage of this actuator is that it could be damaged due to an expansion of the hydraulic fluid. This is especially the case when the hydraulic fluid contains no gas, or no gas bells or bubbles, the presence of which would allow the hydraulic fluid to expand but may cause problems with the functioning of the actuator as the gas bubbles may hamper the dampening effect of the actuator.
  • actuators are used outdoor large temperature variations are not uncommon. For example, summer temperatures above 70°C. when the hydraulic damper is exposed to sunlight and winter temperatures below -30°C. are possible, i.e. temperature variations up to and exceeding 100°C.
  • there are also the daily temperature variations between night and day which can easily exceed 30°C when the actuator is subjected to direct sunshine. These temperature variations cause expansion, and also contraction, of the hydraulic fluid, which expansion causes significant pressures in the closed cylinder cavity possibly resulting in damage to the actuator.
  • a know solution to this problem is to include a small quantity of air or another gas inside the closed cylinder cavity, e.g. up to 5% of the total volume of the hydraulic fluid. This quantity can be added on purpose, but is, more often, the result of not carefully filing the entire closed cylinder cavity. The air is compressed as the hydraulic fluid expands and vice versa without excessive pressures in the closed cylinder cavity.
  • a downside of this solution is that the air can be displaced through the restricted fluid passage resulting in a loss in pressure on the piston and thus an uneven damping of the closure member. As such, air is ideally avoided in a hydraulically damped actuator.
  • EP-A-2840212 Another known solution is proposed in EP-A-2840212 in which a compressible closed-cell foam element, i.e. a pressure compensation mechanism, is introduced into the closed cylinder cavity, which is formed by the entire actuator.
  • the element is compressed when the hydraulic fluid expands and vice versa, thereby avoiding excessive pressures.
  • the actuator is intended only for indoor use with a limited range in temperature variations, as compared to outdoor use, making it possible to use a small element thereby maintaining a compact actuator.
  • the foam element is usually not exposed to low temperatures, which frequently occur outdoors, at which temperatures the foam would become brittle and would be damaged by the daily cycle of expansion and contraction, especially during the winter.
  • said pressure compensation mechanism comprises an expansion channel with a plunger that fits into the expansion channel and is slidably received therein, the plunger dividing the expansion channel into a first compartment which is in fluid communication with said cylinder cavity and a second compartment that is sealed off from the first compartment by said plunger, the second compartment allowing the plunger to slide within the expansion channel to compensate said changes of the volume of the hydraulic fluid.
  • the expansion channel provides sufficient space to allow the hydraulic fluid to expand without resulting in excessive pressures that could damage the closed cylinder cavity even for large outdoors temperature variations.
  • the actuator is more resistant to temperature variations.
  • the plunger seals off the first compartment from the second compartment ensuring that the contents of the second compartment, e.g. gas or air, cannot enter in the first compartment. As such, the gas or air in the expansion channel cannot enter the closed cylinder cavity and thus cannot disrupt the normal operations of the hydraulic damper.
  • said second compartment comprises a biasing member urging the plunger towards said second compartment to pressurize the hydraulic fluid.
  • said biasing member comprises a compression spring.
  • the biasing member exerts a pressure on the hydraulic fluid thereby alleviating the effects caused by negative pressures in the hydraulic fluid that may act on sealing ring or rings in the hydraulic actuator, which negative pressures could cause air or gas to be sucked into the closed cylinder cavity via the sealing ring.
  • the plunger is provided with a seal that engages an inner surface of the expansion channel.
  • the seal is an example of how the plunger may seal off the second compartment from the first compartment in an easy manner.
  • said first compartment of the expansion channel is part of said low pressure compartment.
  • the plunger and the biasing member in the expansion channel are not exposed to the high pressures when closing the closure member. Furthermore, if the expansion channel would be fluidly connected to the high pressure compartment this would affect the normal operation of the damping mechanism.
  • said second compartment of the expansion channel is filled with a gas, in particular with air.
  • the hydraulic fluid is free of gas bells or bubbles.
  • the expansion channel has a cylindrical cross-section.
  • said damper shaft is rotatable around a rotation axis that extends substantially in said longitudinal direction with said first end having an end face and a portion with a non-circular cross-section
  • the damping mechanism comprising a spindle made of a synthetic material and having a recess with a non-circular cross-section fitting onto said portion of the damper shaft, the spindle being fixed onto said first end of the damper shaft and having an outer threaded portion with a screw axis which coincides with said rotation axis, the piston having an inner threaded portion with a screw axis which also coincides with said rotation axis, the outer threaded portion of the spindle on the damper shaft being in engagement with the inner threaded portion of the piston to operatively couple the piston to said damper shaft.
  • the spindle provides a simple design to transfer the rotation of the damper shaft into a translation of the piston.
  • said recess in the spindle has a bottom which engages said end face of the damper shaft, the spindle being fixed to the damper shaft by at least one bolt that is bolted through the bottom of the spindle into the end face of the damper shaft, the at least one bolt having a head which is sunk into the bottom of the spindle and being offset with respect to said rotation axis to irrotatably fasten the spindle to the damper shaft.
  • the at least one bolt By fastening the spindle to the damper shaft by at least one bolt that is bolted through the bottom of the spindle into the end face of the damper shaft and that is offset with respect to the rotation axis and has a head which is sunk into the spindle, the at least one bolt also transfers a rotational motion of the damper shaft to the spindle. As such, less force is exerted onto the recess with the non-circular cross-section in the spindle which is thus less prone to wear out and cause leeway between the piston and the damper shaft.
  • the expansion channel is formed by a cavity inside the damper shaft.
  • the expansion channel is formed by a cavity adjacent to said cylinder cavity.
  • the spring provides a simple design to store energy from the pivoting motion of the hinge members.
  • the actuator is configured to be mounted with said longitudinal direction having a near vertical orientation.
  • a hydraulically damped, self-closing hinge for hinging a closure member to a support
  • the hinge comprising: a first hinge member comprising a first barrel and a first leaf fixed to said first barrel and configured to be fixed to one of: the support and the closure member; a second hinge member pivotably mounted on the first hinge member through the intermediary of a first and a second rolling bearing, the second hinge member comprising a second barrel and a second leaf fixed to said second barrel and configured to be fixed to the other one of: the support and the closure member; and an actuator as described above, the first connection element being formed by one of: the first and the second hinge member and the second connection element being formed by the other one of: the first and the second hinge member.
  • This hinge has the same advantages as the actuator described above.
  • said first barrel has a main body and a hollow shaft extending from said main body with the damper shaft extending through the hollow shaft, the second barrel being pivotably mounted on said hollow shaft through the intermediary of said rolling bearings each having an inner race and an outer race, the inner races of said rolling bearings radially engaging an outer surface of said hollow shaft, the outer races of said rolling bearings radially engaging an inner surface of said second barrel, the inner race of the first rolling bearing being axially engaged by a first abutment on said first barrel, the inner race of the second rolling bearing being axially engaged by a second abutment fixed onto said hollow shaft, the outer race of the first rolling bearing being axially engaged by a third abutment on the inner surface of said second barrel, the outer race of the second rolling bearing being axially engaged by a fourth abutment on the inner surface of said second barrel.
  • the hinge is able to be formed as a barrel hinge having only two knuckles, with the first knuckle being formed by the first barrel and the second knuckle being formed by the second barrel, which is very compact.
  • the invention generally relates to a hydraulically damped actuator for closing a closure member 1 hinged to a support 2.
  • the closure member 1 may be a door, a gate or a window, in particular an outdoors door or gate that may be subjected to large temperature variations.
  • the support 2 may, for example, be a wall or a post.
  • the actuator comprises a first and a second connection element, the first connection element being configured to connect the actuator to the support 2 and the second connection element being configured to connect the actuator to the closure member 1.
  • the actuator further comprises an energy storing mechanism and a damping mechanism, both of which are operatively connected with the closure member 1 and the support 2 via the first and second connection elements.
  • the energy storing mechanism is configured for storing energy when the closure member 1 is being opened and for restoring the energy to effect closure of the closure member 2.
  • the damping mechanism is configured for damping a closing movement of the closure member 1.
  • the actuator is provided as a separate device that is used in combination with hinges, which actuator can be retrofitted onto an existing hinged closure member 1.
  • Such separate devices are, for example, disclosed in EP-B-2356304 , EP-B-2470739 and US-A-2009/107051 . Details of combining the devices disclosed therein with the actuator of the present invention are given below.
  • the closure member 1 is hinged to the support 2 with a height adjust mechanism for adjusting the height of the closure member 1 with respect to the support 2 as described in EP-B-1528202 and with an anti-theft mechanism as described in EP-B-2778330 .
  • the actuator is provided in the form of a hinge as illustrated in Figures 1A and 1B .
  • the closure member 1 is hinged to the support 2 by means of a hydraulically damped, self-closing hinge.
  • the hinge comprises a first and a second hinge member 4, 5 with the first hinge member 4 being fixed to the support 2 and the second hinge member 5 being fixed to the closure member 1 for both a right-handed and a left-handed closure member 1 as illustrated in Figures 1A and 1B respectively.
  • the hinge is turned upside down for a left-handed closure member 1 with respect to its orientation for a right-handed closure member 1. Therefore, the first hinge member 4 may also be referred to as the fixed hinge member 4 and the second hinge member may also be referred to as the moveable hinge member 5.
  • the fixed hinge member 4 comprises a first barrel 6 fixed to a first leaf 8, also referred to as the fixed barrel 6 and the fixed leaf 8, while the moveable hinge member 4 comprises a second barrel 7 fixed to a second leaf 9, also referred to as the moveable barrel 7 and the moveable leaf 9.
  • the leaves 8, 9 are used to fix the hinge to the closure member 1 and to the support 2 while the barrels 6, 7 function as the knuckles of the hinge and also house the energy storing and the damping mechanisms.
  • the fixed leaf 8 is angled to match an angle of the support 2 so as to be always fixed in a same position with respect to the support, i.e. in order to be always aligned with the other hinge used to hinge the closure member to the support.
  • the moveable leaf 9 is arranged such that it is possible to move the hinge, in particular the hinge axis of the hinge, closer and further away with respect to the closure member 1 and the fixed leaf 9 is arranged such that it is possible to adjust the height of the closure member 1 with respect to the support 2.
  • the fixed leaf 8 comprises horizontal grooves 77 that are placed above one another (shown in Figure 4B ) that cooperate with grooves on mounting plates applied underneath the heads of the bolts 80 used to mount the fixed leaf 8 onto the support 2.
  • the fixed leaf 9 also has two vertical slots (not shown), on above the other, for receiving the bolts 80. The cooperating grooves and the vertical slots enable to move the closure member 1 higher and/or lower with respect to the support 2.
  • the moveable leaf 9 comprises vertical grooves 78 that are placed sideways with respect to one another and horizontal slots 88 (shown in Figure 4A ).
  • the vertical grooves 78 cooperate with grooves on mounting plate applied underneath the heads of the bolts 80 used to mount the moveable leaf 9 onto the closure member 1.
  • These cooperating grooves and horizontal slots 88 enable to move the closure member 1 closer and/or further away with respect to the support 2.
  • the leaves 8, 9 are preferably fixed to the support 2 and the closure member 1 respectively using fixture sets as described in EP-B-1907712 , i.e. by inserting bolts 80 through fixation elements 81 into nut elements 79 that automatically fasten due to a square cross-section that fits into a square section (not shown) of a locking plate 82 ( shown in Figure 4A ).
  • each of the leaves 8, 9 is covered with a cover cap 84, 85 to cover the grooves 77, 78 and the fixture sets 79, 80.
  • the hinge members 4, 5 are extruded profiles with certain sections being milled and/or grinded away to form ledges, collars, protrusions, etc.
  • the hinge members 4, 5 are manufactured from extruded aluminium which is less porous as cast aluminium so that it is leak-free with respect to hydraulic fluid.
  • FIGS 1A and 1B show a longitudinal cross-section of the hydraulically damped, self-closing hinge mounted on a closed right-handed and a closed left-handed closure member 1 respectively.
  • Both barrels 6, 7 have a longitudinal direction 10, 11, which longitudinal directions 10, 11 are preferably substantially the same.
  • the moveable barrel 7 is pivotably mounted onto a hollow shaft 12 that forms a part of the fixed barrel 6 using two ball bearings 13, 14.
  • the barrels 6, 7 thus act as knuckles of the hinge with the moveable barrel 7 being pivotable with respect to the fixed barrel 6 around a pivot axis 15 which, preferably, extends in the longitudinal directions 10, 11.
  • the inner races 19, 20 of the ball bearings 13, 14 radially contact the outer surface of the hollow shaft 12 and the outer races 21, 22 of the ball bearings radially contact the inner surface of the moveable barrel 7.
  • the ball bearings 13, 14 thus enable a pivoting motion of the moveable barrel 7 with respect to the hollow shaft 12 and thus with respect to the fixed barrel 6.
  • the first hinge member 4 is fixed to and supported by the support 2; the first ball bearing 13 is supported by the first hinge member 4 as the first inner race 19 rests upon a first abutment 23 formed by the ledge 18 of the fixed barrel 6; the first ball bearing 13 supports the second hinge member 5 as a third abutment 25 formed by the collar 16 rests upon the first outer race 21; and the closure member 1 is fixed to and supported by the second hinge member 5.
  • the closure member 1 is supported via the first ball bearing 13.
  • the first hinge member 4 is fixed to and supported by the support 2; the second ball bearing 14 is supported by the first hinge member 4 as the second inner race 20 rests upon a second abutment 24 formed by the ring 17 of the fixed barrel 6; the second ball bearing 14 supports the second hinge member 5 as a fourth abutment 26 formed by the collar 16 is supported by the second outer race 22; and the closure member 1 is fixed to and supported by the second hinge member 5.
  • the closure member 1 is supported via the second ball bearing 14.
  • one or both the ball bearings 13, 14 may be replaced by a same number of rolling bearings including but not limited to cylindrical roller bearings, spherical roller bearings, gear bearings, tapered rolling bearings and needle roller bearings.
  • the collar 16 which acts as both the third and fourth abutments 25, 26 may be implemented in various alternative ways.
  • the collar 16 may be split into two parallel collars by an annular groove; the collar 16 may be discontinuous, e.g. a ring of protrusions from the inner surface of the moveable barrel 7 may also form the collar 16; axial protrusions may be provided onto the collar 16 in which case the third and fourth abutments 25, 26 are formed by these projections; etc.
  • the first abutment 23 formed by the ledge 18 on the fixed barrel 6 may also be formed by a further collar on the outer surface of the hollow shaft 12 or may be formed by multiple protrusions therefrom or by axial protrusions from the ledge 18.
  • One continuous collar 16 on the inner surface of the moveable barrel is however preferred.
  • This collar is preferably part of the extruded profile and is produced by widening the boring in the extruded profile above and below the collar so that the collar remains. In this way, a strong collar is obtained, which is made of extruded aluminium and which can resist high stresses.
  • the ring 17 is formed by an actuation member of the energy storing mechanism (as described below) which is fastened to the hollow shaft 12 by a ring screw or nut 27 that is screwed onto a threaded portion 3 of the hollow shaft 12 (as illustrated in Figure 4A ).
  • the threaded portion 3 is located at the free end of the hollow shaft 12.
  • the actuation member of the energy storing mechanism is rotatably locked with respect to the hollow shaft 12 by having a non-circular cross-section, in particular a flat side 67 as illustrated in Figure 4A that abuts with a corresponding flat side 83 of the hollow shaft 12.
  • the configuration of the ball bearings 13, 14, the ledge 18 and the ring 17 is advantageous as it allows the hinge to be easily assembled.
  • the fixed hinge member 4 is assembled first with the first ball bearing 13 being placed around the hollow shaft 12.
  • the moveable hinge member 5 is placed onto the hollow shaft 12 with the collar 16 resting on the first ball bearing 13.
  • the second ball bearing 14, together with the other internal elements in the moveable hinge member 5, are then placed via an opening in the top of the moveable hinge member 5 which is finally sealed with a second end cap 28.
  • the energy storing mechanism is contained in the moveable barrel 7 and comprises a first actuation member 29 formed by the ring 17, a second actuation member 30 and a torsion spring 31 connected with one end to the first actuation member 29 and with the other end to the second actuation member 30.
  • the second actuation member 30 is ring-shaped and placed onto the free end of a damper shaft 32.
  • the second actuation member 30 is rotatably locked to the moveable barrel 7 and the damper shaft 32 by a pin 33 (shown in Figure 4A ) that is placed in respective openings 34, 35, 57 in the damper shaft 32, the first actuation member 29 and the moveable hinge member 5 (shown in Figure 4A ).
  • the second actuation member 30 further comprises a hole (not shown) in which an end of the torsion spring 31 is placed.
  • the first actuation member 29, formed by the ring 17, is irrotatably fixed to the hollow shaft 12, and thus to the fixed barrel 6, by the ring screw 27.
  • the first actuation member 29 further comprises a hole 36 (shown in Figure 4A ) in which the other end of the torsion spring 31 is placed. This end of the torsion spring 31 is thus irrotatably coupled to the fixed hinge member 4 and thus to the support 2.
  • the energy storage mechanism also comprises padding to prevent the spring 31 from buckling due to the large forces exerted thereon.
  • the padding comprises three rings 37 placed around the damper shaft 32 in the opening between the damper shaft 32 and the torsion spring 31. The padding rings 37 are free to rotate with the damper shaft 32 and do not contact the torsion spring 31 thus causing no significant friction.
  • the damper shaft 32 provides the coupling between the energy storing mechanism and the damping mechanism, and transfers the opening and closing movement of the closure member 1 to the damping mechanism.
  • the damper shaft is rotatable around a rotation axis 38 that is substantially the same as the pivot axis 15 and the longitudinal directions 10, 11.
  • the damper shaft 32 extends through the hollow shaft 12, as such entering the fixed barrel 6 in which the damping mechanism is housed.
  • the hydraulic damper mechanism comprises the fixed barrel 6 which forms a part of the fixed hinge member 4 and which is closed off at the bottom by an oil cap 39 to define a closed cylinder cavity 40.
  • This cylinder cavity 40 has a longitudinal direction which is the same as the first longitudinal direction 10.
  • the damper mechanism further comprises a piston 41 placed in the fixed barrel 6 to divide the cylinder cavity 40 into a high pressure compartment 42 and a low pressure compartment 43 (illustrated in Figures 2A , 2D , 3A and 3D ).
  • FIG 5A A perspective view of the damper shaft 32 and the piston 41 placed thereon is shown in Figure 5A , which illustrates that the piston 41 has three outward projections 44 which are guided in three grooves 45 in a base element 46 (shown in Figure 4B ) which is also arranged in the cylinder cavity 40.
  • the base element 46 fits in the fixed hinge member 4 and is irrotatably locked therein by means of three bolts 47 (shown in Figure 4B ) which are bolted into corresponding holes in the top of the fixed hinge member 4.
  • the piston 41 can substantially not rotate within the fixed barrel 6 and is slidable in the longitudinal direction 10 of the cylinder cavity 40 between two extreme positions, namely a closed position illustrated in Figures 1A and 1B and an open position illustrated in Figures 2B , 2C , 3B and 3C .
  • the hydraulic damper mechanism further comprises the rotating damper shaft 32.
  • the rotating damper shaft 32 is irrotatably coupled to the moveable hinge member 5.
  • the damper shaft 32 therefore rotates together with the closure member 1.
  • the damper shaft 32 rotates over substantially the same angle with respect to the fixed barrel 6 as the angle over which the moveable hinge member 5 rotates with respect to the fixed hinge member 4.
  • the damper shaft 32 enters the low pressure compartment 43 of the cylinder cavity 40 through the side of the fixed barrel 6, i.e. the hollow shaft 12.
  • a third bearing 48 and a seal 49 are provided between the damper shaft 32 and the fixed hinge member 4, as also illustrated in the exploded view of Figure 4B .
  • the third bearing 48 provides a smooth and easy rotation between the damper shaft 32 and the fixed barrel 6 and also aligns the damper shaft 32 with the hollow shaft 12 with a tolerance of less than 100 ⁇ m, preferably less than 20 ⁇ m. As such, friction and wear of the seal 49 can be kept to a minimum so that it remains liquid tight even after prolonged use.
  • the hinge can thus be mounted upside down without hydraulic liquid escaping by gravity along the rotating damper shaft 32.
  • a spindle 50 is provided between the damper shaft 32 and the piston 41, which spindle is preferably made of a synthetic material which can easily be moulded into the required shape.
  • the spindle 50 is injection moulded from a thermoplastic material.
  • the spindle 50 is mounted onto an end 52 of the damper shaft 32.
  • the spindle 50 is provided with an outer threaded portion 55 that engages an inner threaded portion 56 on the piston 41.
  • the outer threaded portion 55 is provided with a first, external (male) screw thread which has a screw axis which substantially coincides with the rotation axis 38 of the damper shaft 32 and which cooperates with an internal (female) screw thread on the piston 41.
  • the piston 41 Since the piston 41 is irrotatably fixed within the fixed barrel 6, via the upward projections 44 and grooves 45, the piston 41 slides with respect to the fixed barrel 6. In particular, the piston 41 moves towards the damper shaft 32 when the closure member 1 is opened and it moves away from the damper shaft 32 when the closure member 1 is closed.
  • the screw threads are therefore right-handed screw threads.
  • the threaded portions 55, 56 have a screw thread with a high lead angle.
  • the outer threaded portion 55 has a lead angle of at least 45° and more preferably at least 55° and most preferably at least 60°. In the illustrated embodiment, the lead angle is equal to about 66°.
  • the outer threaded portion 55 preferably has at least 5 starts and more preferably at least 7 starts and 10 starts in the illustrated embodiments. The larger lead angle increases the amount of force that is exerted onto the spindle 50 when transferring a rotation from the damper shaft 32 to a sliding motion of the piston 41. These large forces are known to lead to a deformation of the spindle 50 after a period of time.
  • the spindle 50 is irrotatably coupled to the damper shaft 32 in two ways as shown in the exploded view of Figure 5C .
  • the spindle 50 is provided with a recess 51 having a non-circular cross-section, specifically, with two flat sections.
  • the proximal end 52 of the damper shaft 32 is provided with a corresponding non-circular cross section on which the spindle 50 is mounted.
  • the spindle 50 is fastened to the end face 68 of the damper shaft 32 with two bolts 53.
  • the bolts 53 are bolted through a bottom 86 of the spindle 50 into the end face 68 of the damper shaft 32 as illustrated in the cross-sectional view of Figure 5B .
  • each of the bolts 53 is offset with respect to the rotation axis 38 of the damper shaft 32 and has a head 54 that is sunk into the spindle 50.
  • the head 54 of the bolt 53 used to fix the spindle 50 to the damper shaft 32 has, in general, a circular cross-section so that it can engage the inner wall of the recess in the bottom of the spindle wherein it is received.
  • the lateral side of the circular head has a height which is equal to at least 1 mm, more preferably of at least 2 mm.
  • the bolts 53 transfer a significant part of the rotation of the damper shaft 32 to the spindle 50 causing a significant decrease in pressure on the recess 51 and thus a lower chance that the plastic spindle 50, in particular the recess 51 therein, may be deformed due to excessive forces on the spindle 50.
  • the bolts 53 are bolted in a direction that is substantially parallel to the rotation axis 38 of the damper shaft, but it will be appreciated that other orientations of the bolts 53 are also possible.
  • the bolts 53 could be angled with respect to the damper shaft 32.
  • the spindle 50 has the overall shape of a cup that is filled by the end 52 of the damper shaft 32. Specifically, the spindle 50 does not extend beyond the bolts 53, but rather the first threaded portion 55 is provided between the bolts 53 and the base element 46.
  • the spindle 50 has a length L and the recess 51 has a depth D, both measured in the direction of the rotation axis 38 of the damper shaft 32 (as illustrated in Figure 5B ), with the depth D comprising at least 50%, preferably at least 60% and more preferably at least 70% of the length L of the spindle 50. This configuration further enhances the overall strength of the spindle 50 and thus its durability.
  • the hydraulic damper mechanism comprises a one-way valve 58 which allows the hydraulic fluid to flow from the low pressure compartment 43 of the cylinder cavity 40 to the high pressure compartment 42 thereof when the closure member 1 is opened.
  • the opening movement of the closure member 1 is therefore not damped or at least to a smaller extent than the closing movement.
  • this one-way valve 58 is provided in the piston 41.
  • At least one restricted fluid passage is provided between the two compartments 42, 43 of the cylinder cavity 40.
  • One restricted fluid passage is formed by a channel 59 connecting, in all the possible positions of the piston 41, i.e. in all positions between its two extreme positions, the low pressure compartment 43 with the high pressure compartment 42 thereof.
  • This channel 59 is provided with an adjustable valve 60, in particular a needle valve, so that the flow of hydraulic liquid through this channel 59 can be controlled.
  • the channel 59 could be provided in the cylindrical wall of the fixed hinge member 4, but, in the illustrated embodiments, this channel 59 is provided in a tubular member 61 that is integrally formed with the oil cap 39 at and end of the cylinder cavity 40 that is closed off by a first end cap 87.
  • the tubular member 38 projects into the cylinder cavity 40 in the longitudinal direction 11 thereof.
  • the needle of the adjustable valve 60 is screwed through an opening in the oil cap 39 into the tubular member 61 so that the adjustable valve 60 is adjustable from the outside upon removal of the first end cap 87.
  • the channel 59 in the tubular member 61 has a first opening 62 ending above the piston 41 in the low pressure compartment 43 of the cylinder cavity 40 and two second openings 63 ending below the piston 41 in the high pressure compartment 42 of the cylinder cavity 40.
  • the tubular member 61 further comprises a second channel 64 that has a first opening 65 about midway of the tubular member 61 and the two second openings 63 ending below the piston 41.
  • hydraulic fluid can flow along the second channel 64 from the high pressure compartment 42 of the cylinder cavity 40 to the low pressure compartment 43 thereof.
  • the second channel 64 forms a by-pass which causes an increase of the closing speed at the end of the closing movement, i.e. a final snap, to ensure that the closure member 1 is reliably closed.
  • a second adjustable valve 66 in particular a needle valve, is provided so that the flow of hydraulic liquid through the channel 64 can be controlled to control the closing speed of the closure member 1 during the final snap.
  • Figures 2A and 3A show a cross-sectional view of a right-handed and a left-handed closure member 1 respectively when it is halfway opened, e.g. when the closure member 1 has been rotated approximately 90° with respect to the support 2.
  • first actuation member 29 has remained stationary, while the second actuation member 30 has rotated over 90° thereby storing energy in the torsion spring 31.
  • the damper shaft 32 has transferred the same rotation to the damping mechanism causing the piston 41 to move towards the damper shaft 32 as indicated by the dashed arrow.
  • FIGS 2C and 3C illustrate the fully opened position of a right-handed and a left-handed closure member 1 respectively.
  • the energy that was stored in the spring 31 is now restored to close the closure member 1.
  • the spring 31 urges the second actuation member 30 to move relative to the first actuation member 29.
  • the damper shaft 32 transfers this rotation to the piston 41 which is now moved away from the damper shaft 32 as indicated by the dashed arrow.
  • the one-way valve 58 is now shut and the hydraulic fluid is forced through the restricted fluid passage formed by channel 59 in the tubular member 61. This restricted flow thus damps the closing movement.
  • the hinge described above is mainly used outdoors where large temperature variations are not uncommon. For example, summer temperatures up to 70°C when the hinge is exposed to sunlight and winter temperatures below -30°C are not uncommon, i.e. temperature variations up to and possibly even exceeding 100°C are possible. Moreover, there are also daily temperature variations between night and day which can easily exceed 30°C when the hinge is subjected to direct sunshine. These temperature variations cause expansion, and also contraction, of the hydraulic fluid, which could affect the operation of the damping mechanism.
  • the expansion due to temperature variations can be up to 1% of the volume of hydraulic fluid for a temperature variation of 10°C, depending on the expansion coefficient of the hydraulic fluid. As such, an expansion of, for example, up to 3 cc for a temperature difference of 50°C is possible.
  • the hydraulic fluid is preferably free of gas bells or bubbles.
  • the hydraulic fluid is considered to be free of gas bells or bubbles when the volume of gas entrained in the hydraulic fluid, for example in the form of bells, bubbles or an emulsion, is below 1,5%, preferably below 1%, more preferably below 0,5%, advantageously below 0,1% and more advantageously below 0,05% of the total volume of hydraulic fluid.
  • the volume of gas entrained in the hydraulic fluid may be determined by measuring the decrease in volume of the hydraulic fluid due to an increase in pressure, i.e. measuring the adiabatic bulk modulus of the hydraulic fluid at various pressures.
  • the adiabatic bulk modulus is constant irrespective of the pressure, while, for a hydraulic fluid with entrained gas, the adiabatic bulk modulus only becomes constant after a threshold pressure has been exceeded, which threshold pressure corresponds to the pressure when all entrained gas has been compressed.
  • a measure of the volume of entrained gas in the hydraulic fluid is the difference in volume between the hydraulic fluid under atmospheric pressure and the hydraulic fluid under the threshold pressure. The volume of entrained gas is then about equal, but not exceeding, this difference in volume.
  • expansion of the hydraulic fluid is therefore countered by means of an expansion channel 69 with a moveable plunger 70 therein as shown in Figures 7A, 7B , 8A and 8B.
  • the plunger 70 divides the expansion channel 69 into a first compartment 71 having a first volume that is in fluid communication with the cylinder cavity 40 via a fluid channel 75 and a second compartment 72 having a second volume.
  • the plunger 70 has a ring-shaped seal 73 on its outside to prevent leaks between the hydraulic fluid and the pressure relief compartments 71, 72. As such, the plunger 70 acts a moveable seal. It will be readily appreciated that multiple ring-shaped seals 73 may also be provided.
  • the expansion channel 69 is provided adjacent to the fixed barrel 6, i.e. it is formed as a part of the fixed leaf 8.
  • the expansion channel 69 is provided in the damper shaft 32.
  • the first compartment 71 is in fluid communication with the low pressure compartment 43 of the cylinder cavity 40.
  • the plunger 70 is not exposed to the high pressures that result from the normal operation of the damping mechanism. This is advantageous as, exposing the first compartment 71 to the high pressure compartment 42 would affect the closing movement of the closure member 1, i.e. the hydraulic fluid would not only flow via the channel 59 but would also enter the first compartment 71 by displacing the plunger 70.
  • the second compartment 72 is also provided with a biasing member formed by a compression spring 74 and an end cap 76 that seals off the expansion channel 69 from the outside, by two sealing rings 89, and that urges the plunger 70 towards the fluid channel 75.
  • This spring 74 is that the hydraulic fluid is pressurised so that negative pressures in the hydraulic fluid are alleviated.
  • the hydraulic fluid is usually added at room temperature, e.g. near 20°C. When the hinge is exposed to temperatures down to -30°C a negative pressure would occur in the hydraulic fluid in the absence of the compression spring 74.
  • the pressure relief compartment 76 is filled, besides the compression spring 74, with air and is closed off by the end cap 76.
  • the end cap 76 provides an airtight seal, the gas in the pressure relief compartment 76 could be pressurised to assist or replace the compression spring 74.
  • the volume of the expansion channel 69 and the first and second volumes are mainly determined in function of the expected increase in volume of the hydraulic fluid.
  • the first volume is preferably at least 1.5 cc, more preferably at least 2 cc, advantageously at least 2.5 cc and more advantageously at least 3 cc when the plunger 70 is pushed as far back as possible into the expansion channel 69, i.e. when the first volume is maximal.
  • the maximal second volume is preferably substantially the same as the maximal first volume to provide enough space for the compression spring 74.
  • first hinge member 4 may be fixed to the closure member 1 and the second hinge member 5 may be fixed to the support 2 without modifying the internal structure of the hinge as described above.
  • the actuator may also be provided as a separate device that can be retrofitted onto an existing hinged closure member 1 or that can be used with separate hinges.
  • the actuator of the present invention can be constructed in a same way as the actuator disclosed in EP-B-2356304 .
  • the actuator disclosed therein is mounted in a vertical position on a support 2 onto which the closure member 1 is hinged. At the top it has a rotating arm which is slidably mounted on the hinged closure member 1 so that when the hinged closure member 1 is opened or closed, a damper shaft also rotates within the actuator.
  • Such a closing device is offered for sale by the applicant under the names "Verticlose” and "Samson”.

Landscapes

  • Closing And Opening Devices For Wings, And Checks For Wings (AREA)
  • Fluid-Damping Devices (AREA)

Claims (15)

  1. Actionneur à amortissement hydraulique pour fermer un élément de fermeture (1) articulé sur un support (2), l'actionneur comprenant :
    - un mécanisme d'accumulation d'énergie configuré pour accumuler de l'énergie lorsque ledit élément de fermeture (1) est ouvert et pour restaurer ladite énergie afin d'effectuer la fermeture dudit élément de fermeture (1), le mécanisme d'accumulation d'énergie comprenant un premier et un deuxième élément d'actionnement (29, 30) et un mécanisme à ressort (31) disposé entre les deux éléments d'actionnement (29, 30), les éléments d'actionnement (29, 30) pouvant tourner l'un par rapport à l'autre autour d'un axe de rotation (38) dans une première direction mutuelle pour stocker ladite énergie dans ledit mécanisme à ressort (31) et dans une deuxième direction mutuelle, qui est opposée à ladite première direction mutuelle, pour restaurer ladite énergie ;
    - un mécanisme d'amortissement configuré pour amortir un mouvement de fermeture dudit élément de fermeture (1), le mécanisme d'amortissement comprenant :
    - une cavité cylindrique fermée (40) qui a une direction longitudinale (10) et est remplie d'un volume de fluide hydraulique ;
    - un arbre d'amortisseur (32) ayant une première extrémité s'étendant dans la cavité cylindrique (40), l'arbre d'amortisseur (32) pouvant tourner autour l'axe de rotation (38) qui s'étend sensiblement dans ladite direction longitudinale (10) et étant configuré pour transférer le mouvement d'ouverture et de fermeture de l'élément de fermeture (1) au mécanisme d'amortissement ;
    - un piston (41) à l'intérieur de ladite cavité cylindrique (40) de manière à diviser la cavité cylindrique (40) en un compartiment haute pression (42) et un compartiment basse pression (43), le piston (41) étant couplé de manière opérationnelle audit arbre d'amortisseur (32) pour être mobile entre deux positions extrêmes dans ladite direction longitudinale (10) ;
    - une soupape unidirectionnelle (58) permettant l'écoulement de fluide du compartiment basse pression (43) au compartiment haute pression (42) lorsque ledit élément de fermeture (1) est ouvert ; et
    - au moins un passage de fluide restreint (59) entre les compartiments (42, 43) ;
    - un mécanisme de compensation de pression pour compenser les changements du volume dudit fluide hydraulique lors des variations de température de celui-ci ; et
    - un premier et un deuxième élément de connexion, le premier élément de connexion étant configuré pour connecter l'actionneur au support (2) et le deuxième élément de connexion étant configuré pour connecter l'actionneur à l'élément de fermeture (1), le mécanisme d'accumulation d'énergie étant connecté de manière opérationnelle avec ledit premier élément de connexion et ledit deuxième élément de connexion et le mécanisme d'amortissement étant connecté de manière opérationnelle avec ledit premier élément de connexion et ledit deuxième élément de connexion,
    caractérisé en ce que
    ledit mécanisme de compensation de pression comprend un canal de dilatation (69) avec un piston plongeur (70) qui s'adapte dans le canal de dilatation (69) et est reçu de manière coulissante dans celui-ci, le piston plongeur (70) divisant le canal de dilatation (69) en un premier compartiment (71) qui est en communication fluidique avec ladite cavité cylindrique (40) et un deuxième compartiment (72) qui est isolé du premier compartiment (71) par ledit piston plongeur (70), le deuxième compartiment (72) permettant au piston plongeur (70) de coulisser à l'intérieur du canal de dilatation (69) pour compenser lesdits changements de volume du fluide hydraulique.
  2. Actionneur selon la revendication 1, caractérisé en ce que ledit deuxième compartiment (72) comprend un élément de sollicitation poussant le piston plongeur (70) vers ledit deuxième compartiment (72) pour mettre sous pression le fluide hydraulique.
  3. Actionneur selon la revendication 2, caractérisé en ce que ledit élément de sollicitation comprend un ressort de compression (74).
  4. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que le piston plongeur (70) est muni d'un joint (73) qui vient en prise avec une surface intérieure du canal de dilatation (69).
  5. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que ledit premier compartiment (71) du canal de dilatation (69) fait partie dudit compartiment basse pression (43).
  6. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que le fluide hydraulique est exempt de cloches ou de bulles de gaz.
  7. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que ledit deuxième compartiment (72) du canal de dilatation (69) est rempli d'un gaz, notamment d'air.
  8. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de dilatation (69) présente une section transversale cylindrique.
  9. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que ladite première extrémité présente une face d'extrémité (68) et une portion (52) de section non circulaire, le mécanisme d'amortissement comprenant une broche (50) réalisée en matière synthétique et présentant un évidement (51) de section non circulaire s'adaptant sur ladite portion (52) de l'arbre d'amortisseur (32), la broche (50) étant fixée sur ladite première extrémité de l'arbre d'amortisseur (32) et ayant une portion filetée extérieure (55) avec un axe de vis qui coïncide avec ledit axe de rotation (38), le piston (41) ayant une portion filetée intérieure (56) avec un axe de vis qui coïncide également avec ledit axe de rotation (38), la portion filetée extérieure (55) de la broche (50) sur l'arbre d'amortisseur (32) étant en prise avec la portion filetée intérieure (56) du piston (41) pour coupler fonctionnellement le piston (41) audit arbre d'amortisseur (32).
  10. Actionneur selon la revendication 9, caractérisé en ce que ledit évidement (51) dans la broche (50) a un fond (86) qui engage ladite face d'extrémité (68) de l'arbre d'amortisseur (32), la broche (50) étant fixée à l'arbre d'amortisseur (32) par au moins un boulon (53) qui est boulonné à travers le fond (86) de la broche (50) dans la face d'extrémité (68) de l'arbre d'amortisseur (32), ledit au moins un boulon (53) ayant une tête qui est enfoncée dans le fond (86) de la broche (50) et étant décalé par rapport audit axe de rotation (38) pour fixer de manière non rotative la broche (50) à l'arbre d'amortisseur (32).
  11. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal de dilatation (69) est formé par une cavité à l'intérieur de l'arbre d'amortisseur (32).
  12. Actionneur selon l'une quelconque des revendications 1 à 10, caractérisé en ce que le canal de dilatation (69) est formé par une cavité adjacente à ladite cavité cylindrique (40).
  13. Actionneur selon l'une quelconque des revendications précédentes, caractérisé en ce que l'actionneur est configuré pour être monté avec ladite direction longitudinale (10) ayant une orientation quasi verticale.
  14. Charnière à amortissement hydraulique et à fermeture automatique pour articuler un élément de fermeture (1) à un support (2), la charnière comprenant :
    - un premier élément de charnière (4) comprenant un premier cylindre (6) et une première lame (8) fixée audit premier cylindre (6) et configurée pour être fixée à un des éléments suivants : le support (2) et l'élément de fermeture (1) ;
    - un deuxième élément de charnière (5) monté de manière pivotante sur le premier élément de charnière (4) par l'intermédiaire d'un premier et d'un deuxième paliers à roulement (14) (13, 14), le deuxième élément de charnière (5) comprenant un deuxième cylindre (7) et une deuxième lame (9) fixée audit deuxième cylindre (7) et configurée pour être fixée à l'autre élément parmi le support (2) et l'élément de fermeture (1) ; et
    un actionneur selon l'une quelconque des revendications précédentes, le premier élément de connexion étant formé par un élément parmi les suivants : le premier et le deuxième élément de charnière (4, 5) et le deuxième élément de connexion étant formé par l'autre élément parmi : le premier et le deuxième élément de charnière (4, 5).
  15. Charnière selon la revendication 14, caractérisée en ce que ledit premier cylindre (6) a un corps principal et un arbre creux (12) s'étendant à partir dudit corps principal avec l'arbre d'amortisseur (32) s'étendant à travers l'arbre creux (12), le deuxième cylindre (7) étant monté de manière pivotante sur ledit arbre creux (12) par l'intermédiaire desdits paliers à roulement (13, 14) ayant chacun une bague intérieure (19, 20) et une bague extérieure (21, 22), les bagues intérieures (19, 20) desdits paliers à roulement (13, 14) s'engageant radialement dans une surface extérieure dudit arbre creux (12), les bagues extérieures (21, 22) desdits paliers à roulement (13, 14) étant engagée radialement dans une surface intérieure dudit deuxième cylindre (7), la deuxième bague (19) du premier palier à roulement (13) étant engagée axialement par une première butée (23) sur ledit premier cylindre (6), la bague intérieure (20) du deuxième palier à roulement (14) étant engagée axialement par une deuxième butée (24) fixée sur ledit arbre creux (12), la bague extérieure (21) du premier palier à roulement (13) étant engagée axialement par une troisième butée (25) sur la surface intérieure dudit deuxième cylindre (7), la bague extérieure (22) du deuxième palier à roulement (14) étant engagée axialement par une quatrième butée (26) sur la surface intérieure dudit deuxième cylindre (7).
EP17823166.8A 2016-12-27 2017-12-22 Actionneur à amortisseur hydraulique et charnière à fermeture automatique comprenant l'actionneur Active EP3563022B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16206970 2016-12-27
PCT/EP2017/084566 WO2018122210A1 (fr) 2016-12-27 2017-12-22 Actionneur à amortissement hydraulique et charnière à fermeture automatique comprenant l'actionneur

Publications (3)

Publication Number Publication Date
EP3563022A1 EP3563022A1 (fr) 2019-11-06
EP3563022C0 EP3563022C0 (fr) 2023-06-07
EP3563022B1 true EP3563022B1 (fr) 2023-06-07

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Country Link
EP (1) EP3563022B1 (fr)
PL (1) PL3563022T3 (fr)
WO (1) WO2018122210A1 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2295693A1 (fr) * 2009-08-27 2011-03-16 Joseph Talpe Mécanisme de fermeture de porte

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2208349C3 (de) * 1972-02-22 1979-12-06 J. Saajos Rakennustakomo, Lohja (Finnland) Hydraulischer Türschließer
BE1015758A3 (nl) 2003-10-31 2005-08-02 Talpe Joseph Mechanisme voor het op een instelbare hoogte aan een steun ophangen van een poort.
EP1746293A1 (fr) 2005-07-20 2007-01-24 Joseph Talpe Dispositif de fixation pour structures creuses et surfaces planes
DE102006012757B4 (de) * 2006-03-17 2014-03-27 Dorma Gmbh + Co. Kg Türbetätigungsvorrichtung, insbesondere für eine Drehtur
US20090107051A1 (en) 2007-10-29 2009-04-30 Joseph Talpe Closure mechanism
EP2356305B1 (fr) 2008-11-14 2017-03-29 Joseph Talpe Mécanisme de fermeture bidirectionnelle
PL2778330T3 (pl) 2013-03-11 2016-01-29 Locinox Zespół zawiasowy
DE102013106087A1 (de) 2013-06-12 2014-12-18 Dorma Gmbh + Co. Kg Türbetätiger mit einem Druckausgleichselement

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2295693A1 (fr) * 2009-08-27 2011-03-16 Joseph Talpe Mécanisme de fermeture de porte

Also Published As

Publication number Publication date
PL3563022T3 (pl) 2023-10-09
EP3563022C0 (fr) 2023-06-07
WO2018122210A1 (fr) 2018-07-05
EP3563022A1 (fr) 2019-11-06

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