EP2122093B1 - Ferme-porte - Google Patents

Ferme-porte Download PDF

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Publication number
EP2122093B1
EP2122093B1 EP07856536.3A EP07856536A EP2122093B1 EP 2122093 B1 EP2122093 B1 EP 2122093B1 EP 07856536 A EP07856536 A EP 07856536A EP 2122093 B1 EP2122093 B1 EP 2122093B1
Authority
EP
European Patent Office
Prior art keywords
door closer
pressure roller
output shaft
cam disc
closer
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
EP07856536.3A
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German (de)
English (en)
Other versions
EP2122093A1 (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.)
Dormakaba Deutschland GmbH
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Dormakaba 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.)
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Publication date
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Application filed by Dormakaba Deutschland GmbH filed Critical Dormakaba Deutschland GmbH
Priority to EP13005328.3A priority Critical patent/EP2725176B1/fr
Publication of EP2122093A1 publication Critical patent/EP2122093A1/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
    • E05F3/10—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
    • E05F3/104—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 cam-and-slide 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
    • E05Y2201/00—Constructional elements; Accessories therefor
    • E05Y2201/60—Suspension or transmission members; Accessories therefor
    • E05Y2201/604—Transmission members
    • 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
    • E05Y2201/638—Cams; Ramps
    • 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
    • E05Y2201/688—Rollers
    • 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
    • E05Y2600/00—Mounting or coupling arrangements for elements provided for in this subclass
    • E05Y2600/40—Mounting location; Visibility of the elements
    • 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
    • E05Y2800/15—Applicability
    • E05Y2800/17—Universally applicable
    • 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 a cam mechanism based on a door closer.
  • Door closers with cam mechanism typically have a Hubkurvenin rotatably mounted on an output shaft, which has a drainage surface on which a pressure roller unrolled pressed due to a closing spring.
  • the Hubkurvention seen in the direction of a longitudinal extension of the output shaft of the door closer may have a symmetrical or asymmetrical cross-sectional shape.
  • the pressure roller is mounted so that it can move on the Hubkurvenis to and from her. The movement takes place in the direction of the axis of rotation of the output shaft and away from it.
  • the torque curve is determined by the shape of the respective running surface of the Hubkurvenin. This means that the Hubkurvenin must be specially designed for each application, ie constructed.
  • asymmetric cam discs have been developed whose two drainage surface halves are designed for one operating mode.
  • the course of the respective torque curve defined by the shape of the run-off surfaces can not be changed.
  • DE 27 55 787 shows a door closer with the features of the preamble of claim 1.
  • Further generic door closers are eg off DE 29 38 445 or DE 19 506 220 known. If now a door provided with a door closer door are provided with a fire protection function, are in a predetermined first opening angle range (about 0 ° - 4 °) of a rotary wing and in a predetermined second opening angle range (about 88 ° - 92 °) of the rotary vane torques permitted only within predetermined limits. In addition, there is a minimum torque that must not be exceeded over the entire opening angle range of the rotary wing.
  • the object of the invention is to provide a door closer, which can be manufactured inexpensively adapted to the particular application or even adapted or converted in the assembled state to the particular application.
  • FIGS. 2B, 2C . 7D-7F . 10 and 11 embodiments shown are essential to the invention.
  • the embodiments shown in the other figures are merely examples, which are not attributable to the subject of the claim.
  • a door closer has a pressure roller, which rolls pressed against a cam disc of the door closer.
  • the Hubkurvenin is arranged rotatably on an output shaft.
  • the pressure roller is arranged with respect to an axial center of the output shaft so that the pressure roller moves along a path when opening or closing a coupled to the output shaft rotary vane becomes.
  • the torque curve is a characteristic of a voltage applied to the output shaft of the door closer torque in dependence on the opening angle of the rotary wing.
  • the advantage is that not only is the torque variable in proportion, but it is also possible to change the shape of the torque curve during a movement, i. H. a closing movement of a rotary wing, despite using a Hubkurvenectomy with one and the same shape to adapt to the particular application.
  • these operating modes include slide rail operation and normal or scissors linkage operation, and preferably additionally parallel linkage operation.
  • the described torque curve approximation results in particular in a fall installation of the door closer according to the invention in slide rail operation on a tape opposite side or in normal linkage operation on a hinge side.
  • the same effect results in particular in a door leaf assembly of the door closer according to the invention in slide rail operation on the hinge side or normal rod operation on the hinge opposite side.
  • the door closer is also applicable to both DIN-right and DIN-left swing doors.
  • the housing in the region of the drive shaft ends in each case one Through opening, which is optionally provided by means of a cap, so that the unused end of the output shaft is hidden from the outside.
  • the pressure roller is not fixed with respect to the Hubkurvenin in their position. Ie. during a rotation of the Hubkurvenin this moves the pressure roller to a predetermined position. The position reached then corresponds to the position at which the desired torque curve is achieved. The adjustment takes place with a symmetrical Hubkurvenin with respect to their symmetry axis. This can be done by the pressure roller is arranged displaceably in a direction transversely or at an angle between 0 ° and less than 90 ° to the above-described movement path of the pressure roller.
  • the invention provides, vorzuvercard the Hubkurvenis. This makes it possible to match the torque at an opening angle of 0 ° in the aforementioned modes to each other.
  • the Hubkurvention is symmetrical and preferably has a heart-shaped cross-sectional area. This has cost advantages compared to an asymmetric cam disc. On the one hand, the shape of only one half of the running surface of the Hubkurvenin to calculate and thus construct. Furthermore, fewer different drain surface shapes are required, which reduces the variety of Hubkurvenincilationn to be used and thus to manufacturing tools.
  • the door closer according to the invention is designed so that the direction of the movement path of the pressure roller in the assembled state of the door closer can be adjusted. This makes it possible, the door closer in the assembled state, d. H. on site, still to adapt to any peculiarities of the opening or closing process.
  • this makes it possible to provide the door closer with a new function in retrospect or, for example, switch from slide rail operation to normal linkage or parallel linkage operation or vice versa. Ie. one and the same door closer is universally applicable. The manufacturing costs are reduced because with fewer types of door closers, a variety of automatic functions, such as fire protection function, can be realized.
  • the arrangement consisting of at least one pressure roller and a closing spring rotatable and store lockable, wherein the rotation point is not the axial center of the output shaft of the door closer.
  • the arrangement can be mounted as a whole displaceable.
  • Figure 1A is schematically illustrated, which course has a force translation i cam in a symmetrically shaped Hubkurvenrion a conventional cam mechanism 'in response to an opening angle ⁇ of a rotary wing.
  • the force transmission ratio i cam At an opening angle ⁇ of 0 ° is the force transmission ratio i cam is substantially equal to 1. Thereafter, the force transmission ratio i cam falls within a relatively small opening angle range relatively steeply to a lower, minimum value and then increases again.
  • a force transmission curve according to the left-hand diagram in FIG Figure 1C , Unlike the in FIG. 1B shown power transmission curve is the force transmission i cam here at an opening angle ⁇ of 0 ° much higher, it may have a value between 3-7 or even tend to near infinity. After that, the force transmission i cam falls off similar to an upwardly open parabola. The negative increase in the power transmission curve is steadily decreasing. The resulting torque curve is right in Figure 1C shown.
  • the torque M is at the beginning, ie at an opening angle ⁇ of 0 °, relatively high and is about 3 - 4 Nm. Thereafter, the torque falls very sharply within a very small opening angle range and approaches a lower, minimum value.
  • the setting of a door rest position opening angle ⁇ in a range of about 0 °
  • Small changes in the opening angle ⁇ cause a large change in the torque M.
  • the pressure roller is movable along a path in which a direction of movement of the pressure roller in each point of the track does not intersect the axial center of the Hubkurvenin.
  • FIG. 1D two diagrams are shown, indicating the torque curves for a cam mechanism with conventionally arranged pressure roller in Gleitschienen- or normal rod operation.
  • the respective upper characteristic curve indicates the torque curve during an opening process
  • the lower characteristic curve shows the torque curve during a closing operation.
  • the differences between these characteristics are due to the fact that the opening takes place against the force of a closing spring.
  • the torque M at an opening angle ⁇ of 0 ° when opening in normal linkage operation is much higher (about 162 Nm) than in slide rail operation (about 111 Nm).
  • closing the torque M is at an opening angle ⁇ of 0 ° in normal linkage operation about 81 Nm and at Gleitschienen-operation about 55 Nm.
  • the differences of the torques M in the two operating modes to each other consequently amount to about 51 Nm or 26 Nm. Furthermore, the torque curve at normal start-up operation falls significantly steeper at the beginning than the torque curve at slide rail operation. The torque curves thus have different gradients.
  • Figure 1E shows torque curves, which are achieved when a pressure roller is arranged according to the invention.
  • the torque M In normal linkage operation, the torque M at an opening angle ⁇ of 0 ° when opening is about 142 Nm and when closing about 70 Nm.
  • the torque M In slide rail operation, the torque M at an opening angle ⁇ of 0 ° when opening is about 143 Nm and when closing about 71 Nm.
  • the differences of the torques M in the two modes of operation are only about 1 Nm, thus in a range between 0.7% and 1.5% with respect to a respective reference torque in one mode.
  • the torque curve in normal rod operation at an opening angle ⁇ of 0 ° does not drop as steep as in Figure 1E , Rather, the shapes of the torque curves, so the torque curves in the two modes are approximated.
  • the torques M in the mentioned modes are identical or very similar at a respective opening angle ⁇ .
  • the difference of the torque values at a respective opening angle ⁇ in the modes of operation is in a range of at most 10%, preferably 5% or less with respect to one of the applied torques in one of the modes.
  • a pressure roller 101 in a conventional arrangement of a pressure roller 101, as in the lower left in Figure 1F is shown in the diagram by means of a solid line torque curve is achieved, in both lower left rotation directions of Hubkurvenement 103.
  • the pressure roller 101 is arranged such that a defined by a direction of movement R B trajectory of the pressure roller 101, the axial center of an output shaft 104 cuts.
  • the pressure roller is thus centric with respect to the output shaft 104, a so-called eccentricity e is equal to 0.
  • An offset of the pressure roller causes when rotating the Hubkurvenement 103 along a first, according to Figure 1F upper run-surface section of Hubkurvenement 103 in a direction which is indicated by a dashed arrow, a torque curve according to the dashed line in the graph shown characteristic.
  • a torque M is increased at an opening angle ⁇ of 0 °.
  • a displacement amount of the pressure roller 101 according to FIG Figure 1F with respect to this direction of rotation of Hubkurvenissue 103 represents a so-called positive eccentricity (e> 0).
  • Rotation direction is preferably used in slide rail operation.
  • a door closer 100 has, as in FIGS. 2A-2C shown, a pressure roller 101 which is pressed by means of a closing spring 102 against a Hubkurvenis 103 which is rotatably mounted on an output shaft 104 of the door closer 100.
  • the pressure roller 101 is arranged so that a line defined by its substantially translational movement passes the axial center of the output shaft 104.
  • the closing spring 102 is arranged on one side of Hubkurvenin 103, on which also the pressure roller 101 is arranged.
  • the closing spring 102 presses the pressure roller 101 against the Hubkurvenissue 103 via an operative connection in the form of a connecting rod 111.
  • the connecting rod 111 is guided in a guide 105 so that it is only translationally on the Hubkurvenin 103 to or away from it.
  • a force of the closing spring 102 thus acts in the + x coordinate direction.
  • the shutter spring 102 as in FIG. 2B shown in an embodiment of the invention, be arranged on one side of Hubkurvenissue 103, which is opposite to the side on which the pressure roller 101 is arranged.
  • the closer spring 102 is coupled to the pressure roller 101 facing the end with a flap carriage 106.
  • the flap truck 106 has at least one connecting rod 111 and a tab 114 and extends in the x-coordinate direction.
  • the flap truck 106 passes the Hubkurvenation 103 at a predetermined distance.
  • the pressure roller 101 is mounted freely rotatably in the tab 114.
  • the force of the closing spring 102 acts in the -x coordinate direction.
  • the pressure roller 101 is analogous with respect to the Hubkurvenefficiency 103 FIG. 2A arranged.
  • the flap truck 106 may also, as in Figure 2C shown, be executed so that the at least one connecting rod 111 seen in xz plane in the x-coordinate direction seen laterally on the Hubkurvenis 103.
  • the pressure roller 101 is analogous with respect to the Hubkurvention 103 FIG. 2A arranged.
  • the closing spring 102 is operatively connected by means of a transmission gear, preferably in the form of a lever assembly with a pressure roller 101.
  • the closing spring 102 pulls the pressure roller 101 via a lever 107 in the direction Hubkurvenement 103, so acts in -x coordinate direction. Even if the trajectory of the pressure roller 101 describes a circle, it passes over the entire path of movement past the axial center of the output shaft 104.
  • FIG. 3B An alternative non-inventive lever arrangement is in FIG. 3B shown.
  • the closing spring 102 presses the pressure roller 101 via a lever 107 against the Hubkurvenization 103, ie in the + x coordinate direction.
  • the same applies as regards FIG. 3A the same applies as regards FIG. 3A .
  • door closer 100 is provided, the arrangement of Closing spring 102 and its operative connection with the pressure roller 101 (for example, the lever 107) rotated by one point, ie at an angle ⁇ to arrange, which point that does not correspond to the axial center of an output shaft 104 of the door closer 100.
  • door closer 100 has a Hubkurvention 103, the receptacle for the output shaft 104 is arranged off-center. Ie. the receptacle for the output shaft 104 is arranged in a direction along an axial extension of the output shaft 104 adjacent to a connection line between the pressure roller 101 and the axial center of a conventionally arranged output shaft.
  • the pressure roller 101 with respect to their direction of movement in an assembled state of the door closer 100, d. H. when assembled, adjustable to train.
  • a device 200 according to a first non-inventive embodiment for adjusting the position of a pressure roller 101 with respect to a Hubkurvenement 103 in the assembled state of the door closer 100 is in FIG. 6 shown.
  • a closer spring housing 108 receiving the closer spring housing 108 is freely pivotably mounted at one point.
  • the closer spring housing 108 is mounted lockable in a slot 113.
  • the locking is preferably carried out by means of a locking screw 204.
  • the slot 113 is formed in accordance with the movement path which passes through the locking screw 204 upon pivoting of the closing spring 102.
  • a closer spring housing 108 a spring stop of the closing spring 102 can be used.
  • the pressure roller 101 is operatively connected to the closing spring 102, preferably by means of a connecting rod 111.
  • the connecting rod 111 is mounted in a guide 105 translationally on the closing spring 102 to or away from it.
  • the connecting rod 111 is guided into the closing spring 102 and is guided translationally by means of the closing spring 102.
  • a closer spring housing 108 can be omitted.
  • the pressure roller 101 is mounted freely rotatably on the end of the connecting rod 111 facing away from the closing spring 102.
  • FIGS. 7A-7I shown at a setting device provided a translational displacement.
  • FIG. 7A illustrated variant not according to the invention, the above-described arrangement is moved in total.
  • the position of the closer spring housing 108 of the closer spring 102 is fixed by means of adjusting screws 205.
  • the adjusting screws 205 are freely rotatably mounted on one side of the closer housing 109 in such a way that they maintain their position with respect to the closer housing 109 in the direction of their longitudinal extent, ie in the y-coordinate direction in FIG FIG. 7A , do not change.
  • the closer spring housing 108 and thus the entire arrangement can be moved in the y-coordinate direction, so that a displacement of the arrangement according to FIG. 2A is reached.
  • Two independently rotatable adjusting screws 205 may cause a jamming under circumstances, so that an adjustment of the arrangement is no longer possible.
  • FIG. 7B illustrated not inventive variant only one adjustment screw 205 is provided.
  • part of a guide 201 preferably in the form of a guide projection 202, is furthermore preferably provided as part of a dovetail guide.
  • the other, preferably in the form of a groove 203 formed part of the guide 201 is formed on a side wall 115 of the closer spring housing 109.
  • two, provided on two different side walls 110, 115 guides 201 are formed so that tilting is avoided.
  • the only one adjusting screw 205 is preferably as in the embodiment according to FIG. 7A educated.
  • the pressure roller 101 is received in a flap truck 106, as in FIGS. 2B and 2C is shown, the pressure roller 101 according to an in FIG. 7C shown third variant not according to the invention slidably received in a formed in the flap carriage 106 slot 113.
  • the pressure roller 101 is preferably arranged freely rotatable on a bearing journal 112.
  • the bearing pin 112 in turn is received in the slot 113 and lockable by means of a locking screw 204 in the slot. Ie. not the entire assembly but only the pressure roller 101 itself is changed in position.
  • FIG. 7D is in a first variant of the invention, the pressure roller 101 of the door closer 100 instead of a flap carriage 106 to a mounting stop 207 fixed and freely rotatably mounted.
  • the mounting stop 207 is guided in the flap carriage 106, preferably in a slot 113 movable.
  • the attachment stop 207 has a locking stop 206, which has a threaded bore extending toward the tab carriage 106.
  • the flap carriage 106 has a through opening in such a way that a locking screw 204 is screwed from an outer side of the flap carriage 106 through the through opening into the threaded bore of the locking stop 206. Due to a rotation of the locking screw 204 of the mounting stop 207 and thus the pressure roller 101 can be moved to the flap carriage 106 to or away from it and thus be moved with respect to the Hubkurvenement 103.
  • a second variant according to the invention is in Figure 7E shown.
  • the attachment stop 207 has a rectangular cross section with a cavity as seen in the x-coordinate direction.
  • the mounting stop 207 can of course also be designed as a solid block.
  • the attachment stop 207 has a section extending in the y-coordinate direction toward the flap carriage 106.
  • the fastening stop 207 facing away from the end of this section is preferably guided in a slot 113 which is formed in the flap carriage 106 and extending in the z-coordinate direction.
  • a slot 113 on the inside of the flap truck 106 may also be formed in an xz-plane slot-shaped recess. Ie. the slot is not through the Laschenwagen 106 formed through.
  • the flap carriage 106 preferably has a continuous surface on the outside at least at this point.
  • a third variant according to the invention is an in FIG. 7F illustrated strap solution.
  • a tab 114 engages in a yz plane, the pressure roller 101.
  • an adjusting screw 205 is arranged in an xz plane in which the pressure roller 101 is located.
  • the adjusting screw 205 in the in Figures 7D - 7F shown variants to continue an inner side of the side wall 115 and support there, which is opposite to the side wall 115 through which the adjusting screw 205 is guided.
  • FIG. 7G illustrated variants not according to the invention provided to use a bearing pin 112, on which the pressure roller 101 is arranged.
  • a stop member 208 is preferably pushed by means of a bearing sleeve on which the pressure roller 101 receiving bearing pin 112.
  • the bearing pin 112 is thus freely rotatable with respect to the stop member 208.
  • the stop member 208 preferably has a bearing sleeve in which the bearing pin 112 is received.
  • the bearing sleeve preferably comprises a ball, roller or sliding bearing for the bearing journal 112.
  • a stop spring 210 is received in the form of a compression spring.
  • the pressure roller 101 is urged in this direction. Because of the very strong Force of the shutter spring 102, the pressure roller 101 is not pushed back by means of the stopper spring 210 to its original position. Only with a reverse rotation of the Hubkurvenin 103, not shown, the pressure roller 101 passes due to the shape of the drain surface of the Hubkurvenin 103 and the force of the closer spring 102 back to its original position.
  • the stop member 209 may be fixedly attached to the flap truck 106 or, as in FIG. 7H represented by means of a Einstellschrauben mechanism 'in the direction of the pressure roller 101 to be movable away from and to.
  • two stop members 209 are provided, which are arranged fixed or displaceable on each of an inner side of two oppositely disposed sides of the flap carriage 106.
  • the stop members 209 are preferably operatively connected by means of a respective stop spring 210 in the form of a compression spring with a stop member 208.
  • side walls 115 of a closer spring housing 108 or side walls 110 of a closer housing 109 may be used instead of the flap carriage 106.
  • lever assemblies in an adjustment 200 according to a in FIG. 8 illustrated non-inventive embodiment, the pivotally mounted point of the lever 107, which is not coupled to the connecting rod 111, preferably slidably mounted in a slot 113.
  • the recording and locking this position of the lever 107 is preferably carried out as in the pressure roller 101 of the embodiment described above.
  • adjusting device 200 Facing away from the pressure roller 101 and the closer spring housing 108 facing surface of a closer housing 109 or spring stop and the end facing the inside of the side wall 115 of the closer housing 109 are at least at one point to each other. Due to the concern, the end of the closer spring housing 108 or spring stop is guided by means of the inside of the side wall 115.
  • the operative connection between the closing spring 102 and pressure roller 101 is not rigid.
  • the operative connection consists of a connecting rod 111 and a lever 107, which are pivotally coupled together.
  • the connecting rod 111 and the lever 107 are coupled to the respective end facing away from the pivot with a spring stop or the pressure roller 101.
  • the pivot point is preferably formed by means of a guided and lockable in a slot 113 bearing journal 112.
  • At least one connecting rod 111 is preferably provided.
  • the connecting rod 111 as in FIG. 9D shown, guide holes in the form of slots 113.
  • the tab 114 is fixed by means of locking screws 204.
  • the shapes of the guide holes determine the displacement path for the tab 114 and thus the displacement of the pressure roller 101 with respect to the Hubkurvenin 103th
  • the flap truck 106 may also include only one connecting rod 111.
  • a guide of the flap carriage 106 is achieved by means of a slot in the tab 114, by means of which the tab engages or surrounds the output shaft 104.
  • a bearing sleeve is preferably arranged with, for example, a ball, roller or sliding bearing.
  • the bearing sleeve has an outer diameter which is substantially equal to an inner dimension of a cavity formed by the slot 113 or a recess, so that the bearing sleeve is guided guided.
  • the attachment stopper 207, the flap truck 106 or the journal 112 to which the pressure roller 101 is attached has an end in a direction substantially opposite to the pressing direction a mounting stop 211 on.
  • the attachment stop 211 is preferably designed like one of the attachment stops 207 described above.
  • a side wall 115 has a preferably in the x-coordinate direction extending through hole for pushing through and screwing a screw 212 into the mounting stop 211 on.
  • the pressure roller 101 is preferably arranged displaceably in a slot 113 by means of a bearing journal 112. By means of a fastening screw of the bearing pin 112 is locked in the slot 113.
  • the slot 113 may have any shape. It is not limited to a straight design and thus to a purely translational displacement of the pressure roller 101.
  • the pressure roller 101 can thus be positioned easier and more precise, since no contact forces are to be overcome, which would otherwise be transmitted from the closing spring 102 to the pressure roller 101.
  • a locking device 20 is also preferably provided. Because of such a locking device 20, the screw 204, 205, 212 can be fixed in position.
  • two guide members 21 are provided, which are preferably received and guided in a slot 113. This may be the slot 113, in which under certain circumstances, the respective screw 204, 205, 212 is added.
  • a placement part 22 is placed on the guide parts 21, a placement part 22 is placed.
  • the attachment part 22 preferably has passage openings which extend in the direction of the respective guide part 21.
  • the guide parts 21 each have at least one attachment opening, preferably in the form of a threaded bore on.
  • a fastening screw 23 is screwed from a guide parts 21 facing away from the side of the Aufjobeils 22 through a through hole into a respective threaded hole. It is of course any other type of non-positive and / or positive connection between Aufforceeil 22 and guide members 21 possible.
  • the Aufmeneil 22 has on a screw 204, 205, 212 facing side at the point where it meets the screw 204, 205, 212, a recess.
  • the recess has a shape that is complementary to the shape of the portion of the screw 204, 205, 212 that is received by the recess.
  • a positive connection between screw 204, 205, 212 and attachment part 22 is achieved. Due to the screwing with the guide parts 21 thus the screw 204, 205, 212 is securely fixed in its rotational position.
  • the screw 204, 205, 212 is further displaceable in the slot 113. A movement of the pressure roller 101 due to a rotation of the Hubkurvenement 103 is thus still guaranteed.
  • the guide parts 21 are omitted. Instead, the fastening screws are screwed into the respective wall, through which the screw 204, 205, 212 is guided.
  • the adjusting devices 200 according to Figures 3 . 4 . 9A and 9B are readily according to door closer 100 according to FIGS. 2A-3B applicable.
  • the adjusting devices 200 according to FIGS. 7A and 7B are with a door closer 100 according to FIGS. 2A-2C combined.
  • the adjusting device 200 is in particular for door closer 100 according to FIGS. 3A and 3B suitable while the adjusting 200 according to FIG. 7C for a door closer 100 according to Figure 2C is predestined.
  • the adjusting device 200 according to FIG. 9D is especially for door closers according to FIGS. 2A and 2B suitable.
  • the spring mounting of the pressure roller 101 can be combined with the adjustment devices 200 and door closers 100 described herein.
  • the locking devices 10 according to Figures 11A and 11B are applicable to all adjustment screws 205 described herein.
  • the adjusting screws 205 are not limited to the illustrated hexagon screws.
  • the recess of the Aufphineils 12 may have any complementary shape of the adjusting screw 205 used in each case. For example, if countersunk screws are used, their heads flush in the screw-in state, the Aufmeneil12 instead of a recess on a projection in complementary shape of the head of the countersunk screw. For example, if it is a Phillips countersunk screw, the protrusion has the shape similar to the head of a Phillips screwdriver.

Landscapes

  • Power-Operated Mechanisms For Wings (AREA)
  • Closing And Opening Devices For Wings, And Checks For Wings (AREA)

Claims (12)

  1. Ferme-porte (100), comprenant un arbre de sortie (104) sur lequel un disque à cames (103) est agencé de façon à résister à la rotation, et un rouleau de pression (101), dans lequel un ressort de fermeture (102) presse le rouleau de pression (101) contre une surface de roulement du disque à cames (103) par l'intermédiaire d'un chariot à éclisses (106), dans lequel le rouleau de pression (101) est agencé par rapport à un centre axial de l'arbre de sortie (104) de telle façon que le rouleau de pression (101) est déplacé, lors de l'ouverture ou la fermeture d'un vantail tournant qui peut être accouplé à l'arbre de sortie (104), le long d'un trajet, par le fait que le trajet défile à côté du centre axial de l'arbre de sortie (104), et en raison d'une configuration de la surface de roulement du disque à cames (103) avec un angle d'ouverture respectif du vantail tournant pour différents modes d'opération du ferme-porte (100), un couple de rotation très similaire ou identique est présent sur l'arbre de sortie (104),
    • dans lequel les modes d'opération comportent une opération du ferme-porte (100) avec une glissière ou une opération du ferme-porte (100) avec des tringles standards ou des tringles en ciseaux, et
    • dans lequel le ferme-porte (100), avec une opération à glissière est monté sur un côté charnières et avec une opération à tringles standards est monté sur un côté opposé aux charnières, ou dans lequel le ferme-porte (100) avec une opération à glissière est monté sur un côté opposé aux charnières et avec une opération à tringles standards est monté sur un côté charnières,
    • dans lequel le disque à cames (103), vu en une première direction (±y) parallèle à une extension longitudinale de l'arbre de sortie (104), présente une superficie de section symétrique,
    • dans lequel le défilement du trajet du rouleau de pression (101) est aménagé de telle façon que le ferme-porte (100) est aménagé sur une première portion de la surface de roulement du disque à cames (103) pour l'opération à glissière, et sur une deuxième portion de la surface de roulement du disque à cames (103) pour une opération à tringles standards, dans lequel un début des portions de la surface de roulement du disque à cames (103) consiste en un endroit de la surface de roulement du disque à cames (103) contre lequel le rouleau de pression (101) se colle lorsque le vantail tournant est fermé,
    • caractérisé en ce que
    le ferme-porte (100) présente un moyen d'ajustage (200) pour ajuster une distance du rouleau de pression (101) par rapport à son trajet dans un état de montage du ferme-porte (100),
    • dans lequel le moyen d'ajustage (200) comporte un butoir d'attachement (207), sur lequel le rouleau de pression (101) est agencé de façon stationnaire et librement rotative, dans lequel le butoir d'attachement (207) présente un perçage fileté, lequel s'étend en une deuxième direction (±z) transversalement par rapport à une extension longitudinale de l'arbre de sortie (104) et transversalement par rapport à une extension longitudinale du ferme-porte (100), dans lequel le chariot à éclisses (106) du ferme-porte (100) présente une ouverture de passage de telle façon qu'une vis (205) est vissée dans le perçage fileté depuis une face extérieure du chariot à éclisses (106), dans lequel le boutoir d'attachement (207) est supporté de façon guidée dans un guidage (113) d'un chariot à éclisses (106), qui est couplé au ressort de fermeture (102).
  2. Ferme-porte (100) selon l'une des revendications précédentes, dans lequel de ferme-porte (100) peut être monté sur un linteau, respectivement une portion supérieure d'un encadrement de porte ou un cadre, sur laquelle le vantail tournant est suspendu, ou peut être monté sur même le vantail tournant.
  3. Ferme-porte (100) selon l'une des revendications 1 à 2, dans lequel les modes d'opération comportent par ailleurs une opération du ferme-porte (100) avec des tringles parallèles.
  4. Ferme-porte (100) selon la revendication 1, dans lequel la superficie de section est aménagée en forme de coeur.
  5. Ferme-porte (100) selon la revendication 1 ou 4, dans lequel le point de rotation du disque à cames (103), vu dans la première direction (±y), est agencé à côté d'une ligne de symétrie de la superficie de section symétrique.
  6. Ferme-porte (100) selon l'une des revendications précédentes, dans lequel un boîtier du ferme-porte (100) présente, au moins en quelques régions, dans lesquelles les extrémités de l'arbre de sortie (104) sont agencées, une ouverture de passage dans une paroi latérale (115) respective, dans lequel les extrémités de l'arbre de sortie (104) sont aménagées de façon à pouvoir être couplées à un vantail tournant.
  7. Ferme-porte (100) selon la revendication 1, comprenant par ailleurs un moyen pour détacher le rouleau de pression (101) du disque à cames (103) dans l'état de montage du ferme-porte (100).
  8. Ferme-porte (100) selon l'une des revendications précédentes, dans lequel un agencement, consistant en au moins le ressort de fermeture (102), le rouleau de pression (101) et le chariot à éclisses (106), étant agencé de façon rotative entre eux dans un premier plan (x, z) transversalement par rapport à l'extension longitudinale de l'arbre de sortie (104), dans lequel un point de rotation de l'agencement présente une distance par rapport au centre axial du disque à cames (103) dans le premier plan (x, z),
    ou, dans le premier plan (x, z) sous un angle (α) par rapport à une ligne de connexion étant agencé de façon déplaçable et respectivement verrouillable entre le rouleau de pression (101) et le centre axial du disque à cames (103).
  9. Ferme-porte (100) selon l'une des revendications précédentes, dans lequel le rouleau de pression (101) est agencé de telle façon à être déplacé, lors d'une rotation du disque à cames (103) au moyen du disque à cames (103), en une position dans laquelle le trajet du rouleau de pression (101) défile à côté du centre axial de l'arbre de sortie (104).
  10. Ferme-porte (100) selon l'une des revendications précédentes, dans lequel, dans une position dans laquelle le vantail tournant est fermé, le disque à cames (103) est pré-tourné.
  11. Ferme-porte (100) selon l'une des revendications précédentes, comprenant par ailleurs au moins un dispositif (20), adapté à verrouiller au moins la vis (205) de façon à résister à la rotation.
  12. Ferme-porte (100) selon la revendication 10, dans lequel le dispositif comprend une pièce rapportée (22), laquelle, lors d'un placement sur la vis (205), aboutit en engrènement de rotation avec la tête de la vis et est agencée de façon verrouillable.
EP07856536.3A 2007-01-12 2007-12-11 Ferme-porte Active EP2122093B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13005328.3A EP2725176B1 (fr) 2007-01-12 2007-12-11 Ferme-porte

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710002651 DE102007002651B4 (de) 2007-01-12 2007-01-12 Türschließer
PCT/EP2007/010774 WO2008083805A1 (fr) 2007-01-12 2007-12-11 Ferme-porte

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP13005328.3A Division EP2725176B1 (fr) 2007-01-12 2007-12-11 Ferme-porte
EP13005328.3A Division-Into EP2725176B1 (fr) 2007-01-12 2007-12-11 Ferme-porte

Publications (2)

Publication Number Publication Date
EP2122093A1 EP2122093A1 (fr) 2009-11-25
EP2122093B1 true EP2122093B1 (fr) 2018-04-11

Family

ID=39201543

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EP07856536.3A Active EP2122093B1 (fr) 2007-01-12 2007-12-11 Ferme-porte
EP13005328.3A Active EP2725176B1 (fr) 2007-01-12 2007-12-11 Ferme-porte

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EP13005328.3A Active EP2725176B1 (fr) 2007-01-12 2007-12-11 Ferme-porte

Country Status (6)

Country Link
US (1) US8732904B2 (fr)
EP (2) EP2122093B1 (fr)
JP (1) JP2010515843A (fr)
CN (1) CN101573503B (fr)
DE (1) DE102007002651B4 (fr)
WO (1) WO2008083805A1 (fr)

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US9187943B2 (en) * 2013-08-02 2015-11-17 Dmg Mori Seiki Co., Ltd. Rotary damper
DE102013219037C5 (de) * 2013-09-23 2016-12-22 Geze Gmbh Türschließer
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Also Published As

Publication number Publication date
JP2010515843A (ja) 2010-05-13
EP2725176B1 (fr) 2018-09-05
EP2122093A1 (fr) 2009-11-25
EP2725176A2 (fr) 2014-04-30
US20100064472A1 (en) 2010-03-18
WO2008083805A1 (fr) 2008-07-17
CN101573503B (zh) 2014-03-12
CN101573503A (zh) 2009-11-04
DE102007002651A1 (de) 2008-07-17
EP2725176A3 (fr) 2014-08-27
DE102007002651B4 (de) 2015-04-30
US8732904B2 (en) 2014-05-27

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