EP2122093A1 - Ferme-porte - Google Patents

Ferme-porte

Info

Publication number
EP2122093A1
EP2122093A1 EP07856536A EP07856536A EP2122093A1 EP 2122093 A1 EP2122093 A1 EP 2122093A1 EP 07856536 A EP07856536 A EP 07856536A EP 07856536 A EP07856536 A EP 07856536A EP 2122093 A1 EP2122093 A1 EP 2122093A1
Authority
EP
European Patent Office
Prior art keywords
door closer
pressure roller
hubkurvenscheibe
output shaft
door
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07856536A
Other languages
German (de)
English (en)
Other versions
EP2122093B1 (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
Original Assignee
Dorma Deutschland GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=39201543&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2122093(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Dorma Deutschland GmbH filed Critical Dorma Deutschland GmbH
Priority to EP13005328.3A priority Critical patent/EP2725176B1/fr
Publication of EP2122093A1 publication Critical patent/EP2122093A1/fr
Application granted granted Critical
Publication of EP2122093B1 publication Critical patent/EP2122093B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • 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. In cross-section symmetrically shaped Hubkurvenin cause slide rail operation a different torque curve than in a normal or scissor linkage both in magnitude and in the course.
  • 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.
  • a door provided with a door closer door are to be 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.
  • a predetermined first opening angle range about 0 ° - 4 °
  • a predetermined second opening angle range about 88 ° - 92 °
  • the only known way to change the torque on the rotary wing are mechanisms for adjusting the bias of the closing spring.
  • Such mechanisms usually comprise an adjusting screw by means of which the position of a closer spring stop can be changed.
  • the size of the torque can be changed in a substantially constant ratio.
  • the shape of the torque curve remains unchanged. If a torque at an opening angle of 0 °, ie with the rotor closed, too high and an end torque, ie a torque at a maximum opening angle of, for example 90-100 °, only slightly larger than a permissible minimum torque could, by means of an adjustment
  • the closing spring preload the torque at an opening angle of 0 ° can be reduced, but at the same time the end torque would fall below the permissible minimum torque. Switching to a fire protection function would therefore be impossible. Replacing a door closer with a completely new one adds up to enormous costs.
  • the object of the invention is to provide a door closer which can be inexpensively manufactured adapted to the particular application or even adapted or converted in the assembled state to the particular application.
  • 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 is moved along a path when opening or closing a coupled to the drive shaft rotary vane.
  • Characterized in that the web passes by the axial center of the output shaft, and due to the design of the running surface of HubkurvenIO is at a respective opening angle of the rotary vane at different modes of the door closer to the output shaft in each case a very similar or identical torque. Ie. in one mode a curve of a voltage applied to the rotary vane, dependent on the opening angle of the rotary vane torque curve is achieved, which is identical or very similar to a torque curve in another mode.
  • 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 lintel mounting 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 Sliding rail operation on the belt side or in normal linkage operation on the opposite side of the belt.
  • the door closer can also be used both on DIN right and on DIN left rotary doors.
  • the housing in the region of the drive shaft ends in each case has a passage opening, which is optionally provided by means of a cover cap, so that the unused end of the output shaft is concealed to the outside.
  • the pressure roller is not fixed in relation 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 in a symmetrical Hubkurvenation with respect to the axis of symmetry.
  • 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 Andrückrol- Ie.
  • the distance to the articulation point of the normal linkage is equal to or greater than the distance to the rotation point of the rotary vane.
  • the Hubkurvenissue is symmetrical and preferably has a heart-shaped cross-sectional area. This has cost advantages compared to an asymmetric cam disc.
  • the shape of only one half of the running surface of the Hubkurvenin to calculate and thus construct.
  • fewer different drain surface shapes are required, which reduces the variety of Hubkurvenincistinum to be used and thus to manufacturing tools.
  • the door closer according to the invention is designed such that the direction of the movement path of the pressure roller can be adjusted in the assembled state of the door closer. 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. In addition, 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.
  • the arrangement consisting at least of a pressure roller and a closing spring rotatable and lockable store, 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. Further features and advantages of the invention will become apparent from the following description of preferred embodiments.
  • FIG. 1A is a diagram showing the progression of a force transmission ratio of a cam disc in a conventional cam mechanism as a function of an opening angle
  • FIG. 1B two diagrams which show the profile of the force transmission ratio or a torque as a function of the opening angle in a conventional cam mechanism in slide rail operation
  • FIG. 1C two diagrams showing the progression of the force transmission ratio or the torque as a function of the opening angle in a conventional cam mechanism in the normal rod operation
  • FIG. 1 D two diagrams which show torque curves during the opening and closing of a rotary vane in a conventional cam mechanism
  • FIG. 1E two diagrams which show torque characteristics during the opening and closing of a rotary vane in the case of a cam mechanism, wherein the pressure roller is offset according to the invention
  • FIG. 1F is a graph showing curves of torques as a function of the opening angle in a cam mechanism in normal linkage operation at different positions of the pressure roller;
  • FIGS. 2A-2C show a door closer with a cam disc arrangement according to a first embodiment of the invention in various variants
  • 3A, 3B a door closer with a Hubkurvenin- arrangement according to a second embodiment of the invention in different variants
  • Figure 4 a door closer with a Hubkurvenin- arrangement according to a third embodiment of the
  • FIG. 6 shows a device for adjusting the direction of movement of a pressure roller in relation to a cam disc according to a first embodiment of the invention
  • FIGS. 7A-7I show a device for adjusting the direction of movement of a pressure roller in relation to a cam disc according to a second embodiment of the invention in various variants;
  • FIG. 6 shows a device for adjusting the direction of movement of a pressure roller in relation to a cam disc according to a fourth embodiment of the invention,
  • FIGS. 9A-9D show a device for adjusting the direction of movement of a pressure roller in relation to a cam disc according to a fifth embodiment of the invention in various variants
  • Figures 11A, 11B Devices for locking an adjusting screw according to an embodiment of the invention.
  • Figure 1A is shown schematically, which course has a force transmission i Nock e at a symmetrically shaped Hubkurvenrion a conventional cam mechanism 'in response to an opening angle ⁇ of a rotary wing.
  • the force transmission i cam is substantially equal to 1.
  • the force transmission i N ⁇ bridge falls relatively steeply within a relatively small opening angle range to a lower, minimum value and then increases again.
  • Figure 1 B In the case of an aperture angle ⁇ of 0 ° is the Kraftüberset- wetting J Noc ke about 1, 5, and then falls initially similar to a down more open from the parable.
  • the negative slope of the curve is initially relatively small and increases with increasing opening angle ⁇ .
  • the power transmission curve In an opening angle range of about 80-90 °, the power transmission curve has the largest drop, ie the largest negative increase. After that, this negative increase decreases.
  • the resulting torque curve is shown on the right in FIG. 1B. It has a similar course to the force transmission curve.
  • the pressure roller is movable with respect to the cam disc along a path in which a direction of movement of the pressure roller does not intersect at any point of the track the axial center of the cam disc.
  • FIG 1 D 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 in slide rail 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.
  • FIG. 1E shows torque curves which are achieved when a pressure roller according to the invention is arranged.
  • 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 operating modes to each other are only about 1 Nm, thus are in a range between 0.7% and 1, 5% with respect to a respective reference torque in one mode.
  • the torque curve in normal linkage operation at an opening angle ⁇ of 0 ° does not drop as steep as in Figure 1 E. Rather, the shapes of the torque curves, ie 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 operating modes relative to one another preferably lies in a range of at most 10%, preferably 5% or less with respect to one of the applied torques in one of the operating modes.
  • the torque M can not only be increased at an opening angle ⁇ of 0 °. It is also possible to make the torque M at an opening angle ⁇ of 0 ° lower than the average torque applied during a moving operation of a rotary vane.
  • a torque curve shown in the diagram by a solid line is achieved, in both lower left directions of rotation of a Hubkurvenschei- be 103.
  • the pressure roller 101 is arranged such that one through one Direction of movement RB defined trajectory of the pressure roller 101, the axial center of an output shaft 104 intersects. 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 roll causes a stroke of the lifting cam 103 in a direction indicated by a dashed arrow along a first upper surface portion of the lifting cam 103 as shown in FIG Torque curve according to the dashed line in the graph shown characteristic.
  • a torque M is increased at an opening angle ⁇ of 0 °.
  • An offset dimension of the pressure roller 101 according to FIG. 1 F with respect to this rotational direction of the lifting cam 103 represents a so-called positive eccentricity (e> 0).
  • the direction of rotation is preferably used in slide rail operation.
  • a door closer 100 has, as shown in Figures 2A - 2C, a pressure roller 101, which is pressed by means of a closing spring 102 against a Hubkurvenin 103 is arranged rotationally fixed on an output shaft 104 of the door closer 100.
  • the pressure roller 101 is arranged so that a line defined by its essentially translatory movement passes the axial center of the output shaft 104.
  • the closing spring 102 is arranged on one side of the lifting cam 103, on which the pressure roller 101 is also arranged.
  • the closing spring 102 presses the pressure roller 101 against the Hubkurvenin 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 may be disposed on a side of the cam disc 103 opposite to the side where the pressure roller 101 is disposed.
  • the closer spring 102 is coupled to the flap roller 106 at the end facing the pressure roller 101.
  • the flap carriage 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 Hubkurvenance 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 arranged with respect to the Hubkurvenance 103 analogous to Figure 2A.
  • the flap carriage 106 may also be designed, as shown in FIG. 2C, such that the at least one connecting rod 111 is in an xz plane When viewed in the x-coordinate direction, the cam disk 103 passes laterally.
  • the pressure roller 101 is arranged with respect to the Hubkurvenization 103 analogous to Figure 2A.
  • the closing spring 102 is operatively connected to a pressure roller 101 by means of a transmission gear, preferably in the form of a lever arrangement.
  • the closing spring 102 pulls the pressure roller 101 in the direction of the lifting cam 103 via a lever 107, ie acts in the -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 lever arrangement is shown in FIG. 3B.
  • the closing spring 102 presses the pressure roller 101 against the lifting cam 103, d, via a lever 107. H. in + x coordinate direction.
  • the arrangement of the closing spring 102 and its operative connection with the pressure roller 101 is rotated by one point, ie. H. at an angle ⁇ , which point which does not correspond to the axial center of an output shaft 104 of the door closer 100.
  • a door closer 100 shown in FIG. 5 has a cam disc 103, the receptacle of which for the output shaft 104 is arranged off-center. Ie. the Receiving 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 embodiment of the invention 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 shown in Figure 6.
  • 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 closing spring housing 108 a spring stop of the closing spring 102 can also be used.
  • the pressure roller 101 is operatively connected to the closing spring 102, preferably by means of a connecting rod 11 1.
  • 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.
  • a translational displacement is provided in an adjustment device according to a second embodiment of the invention.
  • the above-described arrangement is displaced as a whole.
  • the position of the closer spring housing 108 of the closer spring 102 is determined 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. H. in the y-coordinate direction in Fig. 7A, do not change.
  • the closer spring housing 108 and thus the entire arrangement can be displaced in the y-coordinate direction, so that a displaceability of the arrangement according to FIG. 2A is achieved.
  • Two independently rotatable adjusting screws 205 can possibly cause a jamming, so that an adjustment of the arrangement is no longer possible.
  • only one adjusting screw 205 is provided.
  • On an inner side of at least one side wall 115 of the closer housing 109 is a part of a guide 201, preferably in the form of a guide projection 202, furthermore preferably 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 formed as in the embodiment of Figure 7A.
  • the pressure roller 101 is accommodated in a flap carriage 106, as shown in FIGS. 2B and 2C, the pressure roller 101 is slidably received in a slot 113 formed in the flap carriage 106 according to a third variant of this embodiment of the invention shown in FIG.
  • the pressure roller 101 is preferably freely rotatably mounted 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.
  • the pressure roller 101 of the door closer 100 is mounted fixedly and freely rotatably on a mounting stop 207 instead of on a lug carriage 106.
  • 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 passage opening in such a way that a locking screw 204 extends from an outer side of the flap carriage 106 through the passage opening into the threaded bore of the locking device. stop 206 screwed into it. Due to a rotation of the locking screw 204, the fastening stop 207 and thus the pressure roller 101 can be moved toward or away from the flap carriage 106 and thus be displaced with respect to the lifting cam 103.
  • 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 x-z plane slot-shaped recess. Ie. the oblong hole is not formed by the tab carriage 106.
  • the flap carriage 106 preferably has a continuous surface on the outside at least at this point.
  • a sixth variant is a tab solution shown in FIG. 7F.
  • a lug 114 surrounds the pressure roller 101 in a y-z plane.
  • An adjusting screw 205 is preferably arranged in an x-z plane in which the pressure roller 101 is located.
  • the adjustment screw 205 in the case of the variants shown in FIGS. 7D-7F. antenna continue to 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.
  • a stop member 208 is preferably pushed by means of a bearing sleeve on the Andrückrolie 101 receiving bearing pin 112.
  • the bearing pin 1 12 is thus arranged 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 1 12th
  • a stop spring 210 is received in the form of a compression spring.
  • the pressure roller 101 is urged in this direction. Due to the very strong force of the closing spring 102, the pressure roller 101 is not pushed back into its starting position by means of the stop spring 210. 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 mounted on the flap carriage 106 or, as shown in Figure 7H, by means of a Einstellschrauben mechanism 'in the direction of the pressure roller 101 to be movable away from and to be arranged. According to a variant shown in Figure 71, 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 stopper 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 can be used instead of the flap carriage 106.
  • the pivotally mounted location of the lever 107 which is not coupled to the connecting rod 111, is preferably slidably mounted in a slot 113.
  • the recording and locking of this position of the lever 107 is preferably carried out as in the pressure roller 101 of the embodiment described above.
  • an adjustment device 200 shown in FIG. 9A is provided according to a fifth embodiment of the invention. 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.
  • Preferably again only one adjusting screw 205 is analogous to the above description of an outer side of the closer housing 109 is screwed into the closer spring housing 108 or the spring stop. By rotating the adjusting screw 205, a pivoting of the arrangement is achieved.
  • 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 in a slot 113 and lockable bearing pin 1 12.
  • At least one connecting rod 111 is preferably provided.
  • the connecting rod 111 as shown in Figure 9D, 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 carriage 106 may also comprise only one connecting rod 111.
  • a guide of the flap carriage 106 is replaced by a long reaches hole in the tab 114, by means of which the tab surrounds the output shaft 104 or encloses.
  • 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.
  • FIG. 10 shows an embodiment by means of which it is possible, as it were, to lift off and thus release the pressure roller 101 from the lifting cam 103.
  • the pressure roller 101 is then no longer pressed against the Hubkurvenin 103.
  • the attachment stop 207, the flap carriage 106 or the bearing journal 112, on which the pressure roller 101 is mounted has a fastening stop 211 at one end in a direction substantially opposite to the pressure direction.
  • 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 in 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.
  • the locking device 20 preferably 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.
  • 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 adjustment devices 200 according to FIGS. 3, 4, 9A and 9B are readily applicable to the door closer 100 according to FIGS. 2A-3B.
  • the adjusting devices 200 according to FIGS. 7A and 7B can be combined with a door closer 100 according to FIGS. 2A-2C.
  • the adjustment device 200 is particularly suitable for door closers 100 according to FIGS. 3A and 3B, while the adjustment device 200 according to FIG. 7C is predestined for a door closer 100 according to FIG. 2C.
  • the adjusting device 200 according to FIG. 9D is particularly suitable for door closers according to FIGS. 2A and 2B.
  • the spring mounting of the pressure roller 101 can be combined with the adjustment devices 200 and door closers 100 described herein.
  • the device for releasing the pressure roller 101 shown in FIG. 10 is applicable to any door closer 100 described herein.
  • the locking devices 10 according to FIGS. 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 Aufmeneils 12 may have any complementary shape of the adjusting screw 205 used in each case. If countersunk screws are used, for example, whose heads terminate flush in the screw-in state, the mounting part 12 has a projection in complementary form of the head of the countersunk screw instead of a recess. 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)

Abstract

L'invention concerne un ferme-porte (100) présentant un arbre de sortie (104), sur lequel une came (103) est placée de façon bloquée en rotation, et un rouleau d'appui (101). Un ressort de fermeture (102) presse le rouleau d'appui (101) contre une surface de roulement de la came (103) par le biais d'une liaison fonctionnelle (106, 111, 107). Le rouleau d'appui (101) est agencé par rapport à un point central axial de l'arbre de sortie (104), de façon à pouvoir se déplacer le long d'une trajectoire lorsqu'un vantail accouplé à l'arbre de sortie (104) est ouvert ou fermé. L'invention se caractérise en ce que ladite trajectoire passe devant le point central axial de l'arbre de sortie (104) et la surface de roulement de la came (103) possède une configuration particulière. Ainsi, un couple de rotation très similaire ou identique est appliqué à l'arbre de sortie (104) lorsque le vantail est ouvert selon un angle d'ouverture respectif dans différents modes de fonctionnement du ferme-porte (100).
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 true EP2122093A1 (fr) 2009-11-25
EP2122093B1 EP2122093B1 (fr) 2018-04-11

Family

ID=39201543

Family Applications (2)

Application Number Title Priority Date Filing Date
EP13005328.3A Active EP2725176B1 (fr) 2007-01-12 2007-12-11 Ferme-porte
EP07856536.3A Active EP2122093B1 (fr) 2007-01-12 2007-12-11 Ferme-porte

Family Applications Before (1)

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

Country Status (6)

Country Link
US (1) US8732904B2 (fr)
EP (2) EP2725176B1 (fr)
JP (1) JP2010515843A (fr)
CN (1) CN101573503B (fr)
DE (1) DE102007002651B4 (fr)
WO (1) WO2008083805A1 (fr)

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US9095214B2 (en) * 2012-11-29 2015-08-04 Mansfield Engineered Components, Inc. Door closure mechanism for refrigerator or other appliance
KR101418581B1 (ko) * 2012-12-03 2014-07-10 (주) 다원에스디에스 도어 폐쇄력을 부가하는 유닛을 구비한 도어 클로저
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
AU2014337213B2 (en) 2013-10-18 2018-03-01 Yale Security, Inc. Apparatus for providing constant torque output from a door closer or operator
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Also Published As

Publication number Publication date
US8732904B2 (en) 2014-05-27
EP2725176B1 (fr) 2018-09-05
EP2725176A3 (fr) 2014-08-27
CN101573503A (zh) 2009-11-04
EP2122093B1 (fr) 2018-04-11
EP2725176A2 (fr) 2014-04-30
DE102007002651B4 (de) 2015-04-30
DE102007002651A1 (de) 2008-07-17
WO2008083805A1 (fr) 2008-07-17
CN101573503B (zh) 2014-03-12
US20100064472A1 (en) 2010-03-18
JP2010515843A (ja) 2010-05-13

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