EP3656959A2 - Drehflügelantrieb - Google Patents

Drehflügelantrieb Download PDF

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Publication number
EP3656959A2
EP3656959A2 EP19202707.6A EP19202707A EP3656959A2 EP 3656959 A2 EP3656959 A2 EP 3656959A2 EP 19202707 A EP19202707 A EP 19202707A EP 3656959 A2 EP3656959 A2 EP 3656959A2
Authority
EP
European Patent Office
Prior art keywords
output shaft
pressure roller
drive
rotary
cam disc
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP19202707.6A
Other languages
German (de)
English (en)
French (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
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.)
Filing date
Publication date
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Application filed by Dormakaba Deutschland GmbH filed Critical Dormakaba Deutschland GmbH
Publication of EP3656959A2 publication Critical patent/EP3656959A2/de
Withdrawn legal-status Critical Current

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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
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/611—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings
    • E05F15/614—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by meshing gear wheels, one of which being mounted at the wing pivot axis; operated by a motor acting directly on the wing pivot axis
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors
    • E05F15/611—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings
    • E05F15/63—Power-operated mechanisms for wings using electrical actuators using rotary electromotors for swinging wings operated by swinging arms
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
    • E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
    • E05F3/224—Additional arrangements for closers, e.g. for holding the wing in opened or other position for assisting in opening the wing
    • 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
    • E05Y2201/606—Accessories therefor
    • E05Y2201/618—Transmission ratio variation
    • 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
    • E05Y2400/00—Electronic control; Electrical power; Power supply; Power or signal transmission; User interfaces
    • E05Y2400/10—Electronic control
    • E05Y2400/30—Electronic control of motors
    • E05Y2400/3013—Electronic control of motors during manual wing operation
    • E05Y2400/3015—Power assistance
    • 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
    • E05Y2600/45—Mounting location; Visibility of the elements in or on the fixed frame
    • 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
    • E05Y2600/46—Mounting location; Visibility of the elements in or on the wing
    • 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
    • E05Y2800/00—Details, accessories and auxiliary operations not otherwise provided for
    • E05Y2800/15—Applicability
    • E05Y2800/17—Universally applicable
    • E05Y2800/172—Universally applicable on different wing or frame locations
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18288—Cam and lever
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18568—Reciprocating or oscillating to or from alternating rotary

Definitions

  • the invention relates to a rotary vane drive based on a cam mechanism.
  • Rotary vane drives with a cam mechanism typically have a cam disc which is arranged in a rotationally fixed manner on an output shaft and which has a run-off surface on which a pressure roller rolls, pressed on due to a closer spring.
  • the cam disc can have a symmetrical or asymmetrical cross-sectional shape when viewed in the direction of a longitudinal extension of the output shaft of the rotary leaf drive.
  • the pressure roller is mounted so that it can move towards and away from the cam disc. The movement takes place in the direction of the axis of rotation of the output shaft and away from it.
  • the torque curve is predetermined by the shape of the respective running surface of the cam disc. This means that the cam disc is specially designed for each application, i. H. must be constructed.
  • Cross-sectionally symmetrical cam plates produce a different torque curve in slide rail operation than in the case of a normal or scissor linkage, both in terms of amount and course.
  • a swing leaf is in a predetermined first opening angle range (approximately 0 ° - 4 °) and the rotating leaf in a predetermined second opening angle range (approx. 88 ° - 92 °) Torques only permitted within predetermined limits.
  • the only known way to change the torque on the rotary leaf are mechanisms for adjusting the preload of the closer spring.
  • Such mechanisms usually include an adjusting screw, by means of which the position of a closer spring stop can be changed.
  • the magnitude of the torque can thus be changed in a substantially constant ratio.
  • the shape of the torque curve remains unchanged.
  • the object of the invention is to provide a rotary vane drive which can be inexpensively manufactured to suit the particular application, or which can itself be adapted or converted to the respective application in the assembled state.
  • a rotary leaf drive comprises a closer section.
  • the closer section has an output shaft on which a cam disc is arranged in a rotationally fixed manner. It also has a pressure roller.
  • a closer spring presses the pressure roller against an outlet surface of the cam disc by means of an operative connection.
  • the pressure roller is arranged with respect to an axial center point of the output shaft so that the pressure roller is moved along a path when an opening or closing of a rotary wing coupled to the output shaft. Due to the fact that the web runs past the axial center of the output shaft, and due to the design of the run-off surface of the cam disc, with a respective opening angle of the rotary wing, different operating modes of the rotary wing drive have a very similar or identical torque on the output shaft. I.e. in the case of one operating mode, a course of a torque course which is applied to the rotating wing and is dependent on the opening angle of the rotating wing is achieved, which course is identical or very similar to a torque course in another operating mode.
  • the torque curve is a characteristic curve of a torque applied to the output shaft of the rotary leaf drive as a function of the opening angle of the rotary leaf.
  • the rotary vane drive further comprises a drive motor which is operatively connected to the output shaft.
  • the advantage is that not only is the torque changeable in the ratio, but it is also possible to change the shape of the torque curve during a movement, i. H. to adapt an opening or closing movement of a rotary leaf, despite the use of a cam disc with the same shape, to the respective application.
  • these operating modes include slide rail operation and normal or scissor linkage operation and preferably additionally parallel linkage operation.
  • rotary leaf drives Due to the comparatively high weight of rotary leaf drives, they are usually attached using lintel or head mounting. I.e. the respective swing door operator is mounted in a lintel, on an upper section of a door frame or a frame to which a swing door is attached. This section usually extends horizontally above a rotary wing.
  • door leaf assembly is also conceivable, in which the rotary leaf drive according to the invention is attached to the respective rotary leaf itself.
  • the described torque curve adjustment results in particular when the rotary leaf drive according to the invention is installed in a lintel when the slide rail is in operation on an opposite hinge side or in normal linkage operation on an hinge side.
  • the same effect results in particular when the door leaf assembly of the rotary leaf drive according to the invention is installed with slide rail operation on the hinge side or with normal linkage operation on the opposite hinge side.
  • the rotary leaf drive can also be used on both DIN-right and DIN-left swing leaf doors.
  • the housing in the area of the drive shaft ends each has a through opening, which is optionally provided with a cover cap, so that the unused end of the output shaft is covered to the outside.
  • the pressure roller is not fixed in its position with respect to the cam disc. I.e. when the cam disc rotates, it also 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 is preferably made in the case of a symmetrical cam disc with respect to its axis of symmetry.
  • the invention provides for the cam disc to be pre-twisted. This makes it possible to adjust the torque to one another at an opening angle of 0 ° in the aforementioned operating modes.
  • the maximum opening angle and leverage change as the distance to the point of rotation of the rotary wing increases. Because of these variations, it is possible to change the torques in a predetermined ratio. For example, the ratio of torque at an opening angle of 0 ° to final torque and due to the adjustment of the maximum opening angle, the torque curve can be changed. It has proven particularly advantageous if the distance to the articulation point of the normal linkage is equal to or greater than the distance to the point of rotation of the rotary wing.
  • the lifting cam is symmetrical and preferably has a heart-shaped cross-sectional area. This has cost advantages compared to an asymmetrical cam disc. On the one hand is the shape to calculate and construct only half of the run-off surface of the cam disc. Furthermore, less different run-off surface shapes are required, which reduces the variety of cam disks to be used and thus of manufacturing tools.
  • the rotary leaf drive is designed according to the invention in such a way that the direction of the movement path of the pressure roller can be set in the assembled state of the rotary leaf drive.
  • This makes it possible to turn the swing door drive even in the assembled state, ie. H. on site, to adapt to any peculiarities of the opening or closing process.
  • It also makes it possible to provide the rotary leaf drive with a new function afterwards or to switch from slide rail operation to normal linkage or parallel linkage operation or vice versa. This can take place in that the pressure roller is arranged to be displaceable in a direction transverse or at an angle between 0 ° and less than 90 ° to the above-described movement path of the pressure roller.
  • the arrangement consisting of at least one pressure roller and a closer spring can be rotatably and locked in place, the point of rotation not being the axial center of the output shaft of the rotary leaf drive.
  • the arrangement can be mounted so that it can move overall.
  • Figure 1A is shown schematically the course of a power transmission iN ocke in a symmetrically designed cam plate of a conventional cam mechanism as a function of an opening angle ⁇ of a rotary wing.
  • the force transmission ratio iN ocke is essentially equal to 1.
  • the force transmission ratio i N ⁇ c k e drops relatively steeply to a lower, minimum value within a relatively small opening angle range and then rises again.
  • a force transmission curve results according to the diagram on the left in Figure 1B .
  • the force transmission i Nock e is approximately 1.5 and then falls off like a downward open para.
  • the negative increase in the curve is initially relatively small and increases with an increasing opening angle ⁇ .
  • the force transmission curve has the greatest drop, ie the largest negative increase, in an opening angle range of approximately 80-90 °. After that, this negative increase will decrease.
  • the resulting torque curve is on the right in Figure 1B shown. It has a similar course to the force transmission curve.
  • the pressure roller can be moved with respect to the cam disc along a path in which a direction of movement of the pressure roller does not intersect the axial center point of the cam disc at any point on the path.
  • FIG. 1D two diagrams are shown, the torque profiles for a cam mechanism with a conventionally arranged pressure roller in slide rail or normal linkage operation.
  • the respective upper characteristic curve shows the torque curve during an opening process
  • the lower characteristic curve shows the torque curve during a closing process.
  • the differences between these characteristics are based on the fact that the opening takes place against the force of a closer spring.
  • the torque M at an opening angle ⁇ of 0 ° when opening with normal linkage operation is significantly higher (approx. 162 Nm) than with slide rail operation (approx. 111 Nm).
  • the torque M at an opening angle ⁇ of 0 ° is about 81 Nm in normal linkage operation and about 55 Nm in slide rail operation.
  • the differences between the torques M in the two operating modes are therefore approximately 51 Nm or 26 Nm.
  • the torque curve in normal linkage operation initially drops much steeper than the torque curve in slide rail operation. The torque curves therefore have different courses.
  • Figure 1E shows torque curves that are achieved when a pressure roller is arranged according to the invention.
  • the torque M at an opening angle ⁇ of 0 ° is about 142 Nm when opening and about 70 Nm when closing.
  • the torque M at an opening angle ⁇ of 0 ° is about 143 Nm when opening and about 71 Nm when closing.
  • the differences between the torques M in the two operating modes are only about 1 Nm, and are therefore in a range between 0.7% and 1.5% with respect to a respective reference torque in one operating mode.
  • the torque curve does not drop as steeply in normal linkage operation with an opening angle ⁇ of 0 ° as in Figure 1E . Rather, the shapes of the torque curves, i.e. the torque profiles in the two operating modes, are approximated.
  • the torques M in the operating modes mentioned are identical or very similar at a respective opening angle ⁇ .
  • the difference in the torque values at a respective opening angle ⁇ in the operating modes to one another is preferably in a range of a maximum of 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 have the torque M at an opening angle ⁇ of 0 ° below the average torque applied during a movement process of a rotating wing.
  • a torque curve shown in the diagram by means of a solid line is achieved, namely in both directions of rotation of a cam disc 103 indicated at the bottom left.
  • the pressure roller 101 is arranged such that a movement path of the pressure roller 101 defined by a direction of movement R 5 is the axial center of an output shaft 104 cuts.
  • the pressure roller is thus centered with respect to the output shaft 104, a so-called eccentricity measure e is equal to 0.
  • An offset of the pressure roller causes when rotating the cam disc 103 along a first, according to Figure 1F upper run-off surface section of the cam cam 103 in a direction indicated by a dashed arrow, a torque curve according to the characteristic curve shown in dashed lines in the diagram.
  • a torque M is increased at an opening angle ⁇ of 0 °.
  • An offset amount of the pressure roller 101 according to Figure 1F in relation to this direction of rotation of the cam disc 103 represents a so-called positive eccentricity (e> 0).
  • the direction of rotation is preferably used in slide rail operation.
  • a rotary leaf drive 10 has a closer section 100.
  • a closer section 100 has, as in FIG Figures 2A-2C shown, a pressure roller 101, which is pressed by means of a closer spring 102 against a cam 103, which is rotatably arranged on an output shaft 104 of the closer section 100.
  • the pressure roller 101 is arranged such that a line defined by its essentially translatory movement runs past the axial center of the output shaft 104.
  • the closer spring 102 is arranged on one side of the cam disc 103, on which the pressure roller 101 is also arranged.
  • the closer spring 102 presses the pressure roller 101 against the cam plate 103 via an operative connection in the form of a connecting rod 111.
  • the connecting rod 111 is guided in a guide 105 such that it can only be moved translationally towards or away from the cam plate 103.
  • the force of the closer spring 102 acts in the + x coordinate direction.
  • the closer spring 102 as in FIG Figure 2B can be arranged on a side of the cam disc 103 which is opposite the side on which the pressure roller 101 is arranged.
  • the closer spring 102 is coupled to a plate carriage 106 at the end facing the pressure roller 101.
  • the tab carriage 106 has at least one connecting rod 11 and a tab 114 and extends in the x coordinate direction.
  • the tab carriage 106 passes the cam 103 at a predetermined distance.
  • the pressure roller 101 is freely rotatably mounted in the tab 114.
  • the force of the closer spring 102 acts in the -x coordinate direction.
  • the pressure roller 101 is analogous to the cam cam 103 Figure 2A arranged.
  • the tab carriage 106 can also, as in Figure 2C shown, be designed such that the at least one connecting rod 111 in an xz plane in the x coordinate direction runs past the cam disc 103 laterally.
  • the pressure roller 101 is analogous to the cam cam 103 Figure 2A arranged.
  • the closer 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 closer spring 102 pulls the pressure roller 101 via a lever 107 in the direction of the cam disc 103, ie it acts in the -x coordinate direction. Even if the movement path of the pressure roller 101 describes a circle, it runs over the entire movement path past the axial center of the output shaft 104.
  • FIG. 3B An alternative lever arrangement is in Figure 3B shown.
  • the closer spring 102 presses the pressure roller 101 against the cam 103 via a lever 107, ie in the + x coordinate direction.
  • the closer section 100 shown according to a third embodiment of the invention provides for the arrangement of closer spring 102 and its operative connection with the pressure roller 101 (for example the lever 107) to be rotated around a point, ie in an angle ⁇ , which point is not the axial one
  • the center of an output shaft 104 of the closer section 100 corresponds.
  • FIG. 5 Shown closer section 100 according to a fourth embodiment of the invention has a cam disc 103, the receptacle for the output shaft 104 is arranged off-center. I.e. the receptacle for the output shaft 104 is arranged in a direction along an axial extension of the output shaft 104, next to a connecting line between the pressure roller 101 and the axial center of an output shaft arranged in a conventional manner.
  • the pressure roller 101 with respect to its direction of movement in an assembled state of the rotary leaf drive 10, ie. H. when assembled, adjustable training.
  • a device 200 according to a first embodiment of the invention for adjusting the position of a pressure roller 101 with respect to a cam disc 103 in the assembled state of the rotary leaf drive 10 is shown in FIG Figure 6 shown.
  • a closer spring housing 108 receiving the closer spring 102 is freely pivotable at one point. At another point, the closer spring housing 108 is locked in a slot 13. The locking is preferably carried out by means of a locking screw 204.
  • the elongated hole 113 is shaped according to the path of movement through which the locking screw 204 passes when the closer spring 102 is pivoted.
  • a closer spring housing 108 a spring stop of the closer spring 102 can also be used.
  • the pressure roller 101 is operatively connected to the closer spring 102, preferably by means of a connecting rod 111.
  • the connecting rod 111 is mounted in a guide 105 so that it can be moved translationally towards the closer spring 102 or away from it.
  • the connecting rod 111 is guided into the closer spring 102 and is guided in translation by means of the closer spring 102.
  • a closer spring housing 108 can be omitted.
  • the pressure roller 101 is freely rotatably mounted on the end of the connecting rod 111 facing away from the closer spring 102.
  • the arrangement described above is shifted overall.
  • 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 their position with respect to the closer housing 109 is in the direction of their longitudinal extension, ie in the y coordinate direction in Figure 7A , do not change.
  • the closer spring housing 108 and thus the entire arrangement can be displaced in the y coordinate direction, so that the arrangement can be displaced in accordance with Figure 2A is achieved.
  • the arrangement can also be pivoted to a certain extent.
  • two independently rotatable adjusting screws 205 can cause jamming, so that it is no longer possible to adjust the arrangement.
  • an adjusting screw 205 is provided on an inner side of at least one side wall 115 of the closer housing 109.
  • part of a guide 201 preferably in the form of a guide projection 202, is further preferably provided as part of a dovetail guide.
  • the other, preferably in the form of a groove 203, part of the guide 201 is formed on a side wall 115 of the closer spring housing 109.
  • two guides 201 are provided on two different side walls 110, 115, so that tilting is avoided.
  • the only one adjusting screw 205 is preferably as in the embodiment according to Figure 7A educated.
  • the pressure roller 101 received in a tab carriage 106, as in Figures 2B and 2C is shown, the pressure roller 101 according to one in Figure 7C Third variant of this embodiment of the invention shown is slidably received in an elongated hole 113 formed in the tab carriage 106.
  • the pressure roller 101 is preferably arranged to rotate freely on a bearing journal 112.
  • the bearing journal 112 in turn is received in the elongated hole 113 and can be locked in the elongated hole by means of a locking screw 204. I.e. not the entire arrangement but only the pressure roller 101 itself is changed in its position.
  • the pressure roller 101 of the closer section 100 is fixed in place and freely rotatable on a fastening stop 207 instead of on a tab carriage 106.
  • the fastening stop 207 is preferably movably guided in the tab carriage 106 in an elongated hole 113.
  • the fastening stop 207 has a locking stop 206, which has a threaded bore extending towards the plate carriage 106.
  • the tab carriage 106 has a through-opening such that a locking screw 204 from an outside of the tab carriage 106 through the through-opening is screwed through into the threaded bore of the locking stop 206. 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 plate carriage 106 and thus be displaced with respect to the cam disc 103.
  • the attachment stop 207 has a rectangular cross section with a cavity, seen in the x coordinate direction.
  • the attachment stop 207 can of course also be designed as a solid material block.
  • the fastening stop 207 has a section which extends in the y coordinate direction towards the plate carriage 106. The end of this section facing away from the fastening stop 207 is preferably guided in an elongated hole 113 which is formed in the plate carriage 106 and extends in the z-coordinate direction.
  • an elongated hole in an x-z plane can also be formed. I.e. the elongated hole is not formed through the plate carriage 106.
  • the tab carriage 106 preferably has a continuous surface on the outside, at least at this point.
  • a sixth variant is an in Figure 7F shown tab solution.
  • a tab 114 engages around the pressure roller 101 in a yz plane.
  • An adjusting screw 205 is preferably 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 an inner side of the side wall 1 15 and support there, which is opposite the side wall 1 15, through which the adjusting screw 205 is passed.
  • FIG. 7G shown seventh variant provided to use a journal 112 on which the pressure roller 101 is arranged.
  • a stop part 208 is preferably pushed onto the bearing pin 112 receiving the pressure roller 101 by means of a bearing sleeve.
  • the bearing pin 112 is thus freely rotatable with respect to the stop part 208.
  • the stop part 208 preferably has a bearing sleeve in which the bearing pin 112 is received.
  • the bearing sleeve preferably comprises a ball, roller, or slide bearing for the bearing journal 112.
  • Another stop part 209 in which a stop spring 210 in the form of a compression spring is accommodated, is arranged on at least one side of the link carriage 106.
  • the pressure roller 101 is urged in this direction. Due to the very strong force of the closer spring 102, the pressure roller 101 is not brought into its starting position by means of the stop spring 210 pushed back. Only when the cam cam 103 (not shown) rotates backwards does the pressure roller 101 return to its starting position due to the shape of the running surface of the cam cam 103 and the force of the closer spring 102.
  • the stop part 209 can be fixedly attached to the tab carriage 106 or, as in FIG Figure 7H shown, by means of an adjusting screw mechanism 'in the direction of the pressure roller 101 to and away from it.
  • two stop parts 209 are provided, each of which is arranged in a stationary or displaceable manner on an inner side of two opposite sides of the link carriage 106.
  • the stop parts 209 are preferably operatively connected to a stop part 208 by means of a stop spring 210 in the form of a compression spring.
  • side walls 115 of a closer spring housing 108 or side walls 110 of a closer housing 109 can also be used instead of the tab carriage 106.
  • lever arrangements shown in an adjusting device 200 according to a in Figure 8 Fourth embodiment of the invention shown the pivotally mounted point of the lever 107, which is not coupled to the connecting rod 111, preferably slidably mounted in an elongated hole 113. This location of the lever 107 is preferably received and locked as in the case of the pressure roller 101 of the embodiment described above.
  • FIG. 9A shown adjusting device 200 provided according to a fifth embodiment of the invention.
  • the surface of the closer spring housing 109 or spring stop facing away from the pressure roller 101 and facing the closer housing 109 and the inside of the side wall 115 of the closer housing 109 facing this end abut one another at least at one point. Because of the contact, the end of the closer spring housing 108 or spring stop is guided by means of the inside of the side wall 115.
  • preferably only one adjusting screw 205 is screwed into the closer spring housing 108 or the spring stop from an outside of the closer housing 109, as described above.
  • a pivoting of the arrangement is achieved by turning the adjusting screw 205.
  • the end of the closer spring housing 108 or the spring stop is as in FIG Figure 9B shown, guided in an elongated hole 1 13 formed in the closer housing 109 and can preferably be fixed by means of a locking screw 204.
  • the operative connection between closer spring 102 and pressure roller 101 is not rigid.
  • the operative connection preferably consists of a connecting rod 111 and a lever 107, which are coupled to one another in a rotationally articulated manner.
  • the connecting rod 111 and the lever 107 are coupled to the respective end facing away from the swivel joint with a spring stop or the pressure roller 101.
  • the pivot point is preferably formed by means of a bearing pin 112, which is guided and lockable in an elongated hole 113, which is not shown.
  • At least one connecting rod 111 is preferably provided.
  • the connecting rod 111 as in FIG Figure 9D shown, guide holes in the form of elongated holes 113.
  • the tab 1 14 is fixed in the elongated holes 1 13 by means of locking screws 204.
  • only a locking screw 204 is provided.
  • 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 cam disc 103.
  • Figure 10 shows a rotary vane drive 10.
  • a drive motor 11 is in rotational engagement with an output shaft 104 by means of a gear 12.
  • the drive motor 11 preferably drives the output shaft via a gear 12, preferably in the form of a worm gear.
  • gear 12 preferably in the form of a worm gear.
  • any type of rotational operative connection is possible.
  • a closer spring 102 is arranged at the end of the drive motor 11 facing away from the output shaft 104. It is preferably designed as a compression spring. The end of the closer spring 102 facing the drive motor 11 is fixed in place. The other end preferably has a mechanism for adjusting a bias of the closer spring 102, preferably in the form of an adjusting screw 205.
  • the connecting rod (s) 111 is or are coupled with a bracket 114.
  • the tab 114 is designed such that it runs past the gear 12 and the output shaft 104.
  • a pressure roller 101 is preferably fixed in place and freely rotatable at the end of the tab 114 facing away from the closer spring 102.
  • the closer spring 102 presses the pressure roller 101 over the plate carriage 106 onto the running surface of the cam disc 103.
  • the tab carriage 106 may further preferably have two guide rollers 13 that are arranged to be in relation to the tab 114 protrude and are guided in a guide 14, so that the tab carriage 106 can only be moved along a predetermined path.
  • An in Figure 1 1 shown rotary vane drive 10 according to a second embodiment of the invention comprises a plate carriage 106, which only comprises a connecting rod 111.
  • the guiding of the tab carriage 106 is achieved by means of an elongated hole 113 in the tab 114, by means of which the tab 114 engages or encloses the output shaft 104.
  • a bearing sleeve with, for example, a ball, roller or plain bearing is preferably arranged on the output shaft 104.
  • the bearing sleeve has an outer diameter that is substantially equal to an inner dimension of a cavity or a recess formed by the elongated hole 113, so that the bearing sleeve is supported in a guided manner.
  • the pressure roller 101 is preferably pivotally mounted via a lever 107.
  • Figure 12 shows a rotary vane drive 10 according to a third embodiment of the invention.
  • drive motor 11 and closer spring 102 are arranged on opposite sides of the output shaft 104, that is to say to the right and left of the output shaft 104 as seen in the y coordinate direction.
  • FIG 13 An embodiment is shown by means of which it is possible to lift the pressure roller 101 from the cam disc 103, so to speak, and thus to release it. The pressure roller 101 is then no longer pressed against the cam disc 103.
  • the fastening stop 207, the tab carriage 106 or the bearing journal 112 to which the pressure roller 101 is attached has a fastening stop 211 at one end in a direction substantially opposite to the pressing direction.
  • the attachment stop 211 is preferably designed like one of the attachment stops 207 described above.
  • a side wall 115 preferably has a through opening, preferably extending in the x-coordinate direction, for pushing and screwing a screw 212 into the fastening stop 211.
  • the pressure roller 101 is preferably displaceably arranged in a slot 113 by means of a bearing journal 112.
  • the bearing pin 112 is locked in the slot 113 by means of a fastening screw.
  • the elongated hole 1 13 can 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 more easily and precisely since there are no contact forces to be overcome which would otherwise be transmitted from the closer spring 102 to the pressure roller 101.
  • a locking device 20 is preferably also provided. Due to such a locking device 20, the screw 204, 205, 212 can be fixed in its position.
  • two guide parts 21 are provided in the locking device 20, which are preferably received and guided in an elongated hole 113.
  • This can be the elongated hole 113, in which the respective screw 204, 205, 212 may be received.
  • a mounting part 22 is placed on the guide parts 21.
  • the attachment part 22 preferably has through openings which extend in the direction of the respective guide part 21.
  • the guide parts 21 each have at least one fastening opening, preferably in the form of a threaded bore.
  • One fastening screw 23 is screwed from a side of the attachment part 22 facing away from the guide parts 21 through a through opening into a respective threaded bore.
  • any other type of non-positive and / or positive connection between the attachment part 22 and the guide parts 21 is possible.
  • the attachment part 22 has a recess on a side facing the screw 204, 205, 212 at the point where it meets the screw 204, 205, 212.
  • the recess has a shape that is complementary to the shape of the part 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 thereby achieved. Due to the screwing with the guide parts 21, the screw 204, 205, 212 is thus securely fixed in its twisted position. The screw 204, 205, 212 can still be moved in the slot 113. A movement of the pressure roller 101 due to a rotation of the cam disc 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 passed.
  • the adjusters 200 according to Figures 3 , 4th , 9A and 9B are easily on closer sections 100 according to Figures 2A - 3B applicable.
  • the adjusters 200 according to Figures 7A and 7B are with closer sections 100 according to Figures 2A-2C combinable.
  • the setting device 200 is in particular for the closer section 100 according to FIG Figures 3A and 3B suitable, while the adjusting device 200 according to Figure 7C for a closer section 100 according to Figure 2C is predestined.
  • the adjuster 200 according to Figure 9D is particularly suitable for closer sections Figures 2A and 2B suitable.
  • the spring mounting of the pressure roller 101 can be combined with the setting devices 200 and closer sections 100 described herein.
  • the locking devices 20 according to Figures 14A and 14B are applicable to all adjustment screws 205 described herein.
  • the adjusting screws 205 are not limited to the hexagon screws shown.
  • the recess of the attachment part 22 can have any complementary shape of the adjusting screw 205 used in each case. If, for example, countersunk screws are used whose heads are flush when screwed in, the attachment part 22 has a projection in the form of a complement of the head of the countersunk screw instead of a recess. For example, if it is a Phillips countersunk screw, the projection has the shape similar to the head of a Phillips screwdriver.

Landscapes

  • Power-Operated Mechanisms For Wings (AREA)
  • Transmission Devices (AREA)
  • Fixing For Electrophotography (AREA)
EP19202707.6A 2007-01-12 2007-12-11 Drehflügelantrieb Withdrawn EP3656959A2 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007002650.3A DE102007002650B4 (de) 2007-01-12 2007-01-12 Drehflügelantrieb
EP07847054.9A EP2122097B1 (de) 2007-01-12 2007-12-11 Drehflügelantrieb
PCT/EP2007/010776 WO2008083806A1 (de) 2007-01-12 2007-12-11 Drehflügelantrieb

Related Parent Applications (2)

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EP07847054.9A Division-Into EP2122097B1 (de) 2007-01-12 2007-12-11 Drehflügelantrieb
EP07847054.9A Division EP2122097B1 (de) 2007-01-12 2007-12-11 Drehflügelantrieb

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EP3656959A2 true EP3656959A2 (de) 2020-05-27

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EP19202707.6A Withdrawn EP3656959A2 (de) 2007-01-12 2007-12-11 Drehflügelantrieb
EP07847054.9A Not-in-force EP2122097B1 (de) 2007-01-12 2007-12-11 Drehflügelantrieb

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US (1) US8516912B2 (ja)
EP (2) EP3656959A2 (ja)
JP (1) JP2010515844A (ja)
CN (1) CN101573504B (ja)
DE (1) DE102007002650B4 (ja)
WO (1) WO2008083806A1 (ja)

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CH706425A1 (de) * 2012-04-23 2013-10-31 Gilgen Door Systems Ag Drehantrieb für mindestens einen Flügel, insbesondere eine Türe oder ein Fenster.
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JP2018523038A (ja) * 2015-07-23 2018-08-16 ゴットハード ３ メカトロニック ソリューションズ エージー 回転翼用駆動装置
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CA3060764C (en) 2018-10-31 2022-08-23 Pella Corporation Slide operator for fenestration unit
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CN111425099A (zh) * 2020-04-23 2020-07-17 广东万家乐燃气具有限公司 开关门系统以及开门家电
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Also Published As

Publication number Publication date
EP2122097B1 (de) 2019-11-20
US8516912B2 (en) 2013-08-27
WO2008083806A1 (de) 2008-07-17
JP2010515844A (ja) 2010-05-13
CN101573504B (zh) 2014-03-12
EP2122097A1 (de) 2009-11-25
DE102007002650A1 (de) 2008-07-17
DE102007002650B4 (de) 2020-06-04
US20100089190A1 (en) 2010-04-15
CN101573504A (zh) 2009-11-04

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