DRIVE FOR A LEAF, ESPECIALLY FOR A DOOR OR A WINDOW

Abstract

A drive (10) for a leaf of a door, window, or the like, comprising a housing (12), an output shaft (14) rotatably mounted in the housing (12) for rotating the leaf, and an energy storage device (16) which can be charged each time the leaf is opened and discharged when the leaf is closed, said energy storage device comprising a spring unit (18) in a fluid-free space, wherein a magnet system (20) is provided which, together with the spring unit (18), generates a resulting, non-linear torque curve on the output shaft (14), and for this purpose comprises a plurality of cooperating magnets (26), characterized in that a portion of the magnets (26) of the magnet system (20) is fixedly connected to a drive shaft (24) operatively connected to the spring unit (18), and a further portion of the magnets (26) of the magnet system (20) cooperating with this portion of the magnets is fixedly connected to the housing (12).

Description

[0001] The invention relates to a drive for a leaf of a door, a gate, a window, a skylight or a flap, according to the preamble of claim 1.

[0002] Drives or door closers of the type mentioned above usually have a hydraulic damping element in the form of a damping piston and a closing spring acting directly on this damping piston, which interact in a common housing.

[0003] One of the disadvantages of these conventional drives is that they require a hydraulic fluid, such as oil, to lubricate the moving parts and that they take up a relatively large amount of installation space, which is lacking, particularly in the case of an electric motor drive for its motor-gear unit.

[0004] DE 198 31 393 B4 describes a door closer whose damping device is arranged in a separate housing section in a fluid-free space.

[0005] From US 2 708 284 A, a drive for a leaf of a door or a window is known, comprising a housing and an output shaft rotatably mounted in the housing for rotating the leaf, with a spring unit and a magnet system, which together generate a resulting, non-linear torque curve on the output shaft.

[0006] The invention is based on the object of providing a drive of the type mentioned above that eliminates the aforementioned disadvantages. The drive should also operate without hydraulic fluid or lubricant, be highly efficient, and be as simple as possible in design while requiring as little space as possible for the individual components.

[0007] According to the invention, this object is achieved by a drive having the features of claim 1. Preferred embodiments of the drive according to the invention emerge from the subclaims, the present description and the drawing.

[0008] Thanks to the inventive solution, no hydraulic medium such as oil is required to lubricate the moving parts. By appropriately designing the spring unit and the magnet system, the torque required at the drive's output shaft can be generated based on the angle of rotation. Since the magnets of the magnet system do not have to touch each other, no friction losses occur in their area. Particularly with regard to an electromechanical drive, the inventive solution also offers the advantage of providing comparatively large installation space for the motor-gear unit.

[0009] Preferably, the spring unit and the magnetic system of the energy storage device act on an output shaft connected to the output shaft via a gear stage, which is preferably perpendicular to the output shaft. With a vertical output shaft, the drive shaft can thus be horizontal.

[0010] The gear stage provided between the output shaft and the input shaft can in particular comprise a crown gear drive.

[0011] According to a preferred practical embodiment of the drive according to the invention, the spring unit comprises a spiral spring. The coils of the coil spring are advantageously arranged at a distance from one another, thereby further minimizing friction losses and thus further increasing efficiency.

[0012] Such an energy storage device can generate a torque on the output shaft that drops sharply as the vane opens. With an appropriate design of the spiral spring and gear stage, wear is minimized and a very high cycle rate of the mechanical energy storage device can be achieved.

[0013] The spring unit or coil spring is preferably firmly connected to the drive shaft at one end and to the housing at the other. The spring unit is advantageously connected to the housing via a preloading device. This preloading device then allows the torque curve generated by the spring unit on the output shaft to be variably adjusted.

[0014] While the tensioned spring unit can generate an at least approximately linear torque curve on the output shaft, the magnet system can preferably generate a non-linear torque curve on the output shaft, so that the resulting total torque on this output shaft is not linear.

[0015] Preferably, the magnet system comprises a plurality of cooperating magnets.

[0016] According to a preferred practical embodiment of the drive according to the invention, a part of the magnets of the magnet system is firmly connected to the drive shaft and a further part of the magnets of the magnet system, which interacts with this part of the magnets, is firmly connected to the housing.

[0017] With each rotation of the output shaft and a corresponding rotation of the drive shaft, the interacting magnets can be moved relative to each other, resulting in the non-linear torque curve on the output shaft.

[0018] It is particularly advantageous if the magnets of the magnetic system are arranged one above the other on two pitch circles concentric to the axis of the drive shaft.

[0019] Preferably, the magnets of the magnet system arranged on the inner pitch circle are firmly connected to the drive shaft and the magnets of the magnet system arranged on the outer pitch circle are firmly connected to the housing.

[0020] The magnets of the magnet system arranged on different pitch circles can be expediently positioned in such a way that they are displaced tangentially relative to one another during each rotation of the drive shaft in order to generate a non-linear torque curve on the output shaft.

[0021] The interacting magnets of the magnetic system are preferably arranged at a distance from each other.

[0022] If both the interacting magnets of the magnetic system and the various coils of the spiral spring are spaced apart from each other, friction losses only occur in the bearings of the shafts and in the gear stage located between the input shaft and the output shaft, thus achieving very high efficiency of the energy storage system comprising the spring unit and the magnetic system. With an appropriate design of the spiral spring and the gear stage, wear is reduced to a minimum, and a very high cycle rate of the mechanical energy storage system can be achieved.

[0023] Preferably, the distance between the interacting magnets of the magnetic system is < 0.2 mm. However, a minimum distance between the interacting magnets is always maintained.

[0024] In certain cases, it is advantageous if the spring unit or spiral spring is designed in such a way that it acts over the entire angle of rotation of the drive shaft - in particular corresponding to a rotation angle range of the output shaft of approximately 180°.

[0025] The magnet system can in particular be designed in such a way that it generates its highest torque in a blade opening angle range of 0° to 4° and then, with further increasing blade opening angle, generates a torque that in particular decreases periodically.

[0026] It is particularly advantageous if the magnet system comprises at least one pair, in particular a plurality of pairs, of two magnets each interacting with each other or arranged one above the other. For example, three or four to six such pairs of two magnets each interacting with each other or arranged one above the other can be provided.

[0027] In principle, however, a different number of interacting magnets and a different arrangement of the magnets are also conceivable.

[0028] According to a suitable practical embodiment of the drive according to the invention, the closing force of the magnetic system can be variably adjusted, in particular by changing the overlap of the interacting magnets. The corresponding adjustment of the closing force of the magnetic system can also be effected, in particular, via a closing force adjustment or preloading device associated with the spring unit.

[0029] The number n Pole of poles or pairs of interacting magnets of the magnetic system depends on the comparatively highest magnetic torque M1 generated at the output shaft and the post-oscillation torques M i as can be seen from the following relationship: |Mi|=M1−M1I−1nPoles

[0030] As can be seen from this relationship, many magnetic poles increase the relatively highest magnetic moment M1, while fewer magnetic poles increase the ringing moment(s) M i reduce. For example, the magnet system can be provided with a range for three poles, a range for four to six poles, and / or a range of six poles.

[0031] In order to be able to adjust the closing torque, the spiral spring can be designed with a working angle range that is larger than the sash opening angle range of, for example, 180°.

[0032] The invention is explained in more detail below using exemplary embodiments with reference to the drawing, in which: Fig. 1 a schematic representation of the basic structure of an exemplary embodiment of a drive according to the invention, Fig. 2 a more detailed schematic longitudinal sectional view of another exemplary embodiment of a drive according to the invention, wherein the drive is designed, for example, as an overhead door closer, Fig. 3 a schematic cross-sectional view of the drive according to Fig. 2, Fig. 4 is a schematic representation of an exemplary magnet system of a drive according to the invention with a relatively higher number of magnetic poles, Fig. 5 is a schematic representation of an exemplary magnet system of a drive according to the invention with a relatively smaller number of magnetic poles, Fig. 6 is a schematic representation of the magnetic flux of the drive according to the Fig. 2 and Fig. 3 provided six-pole magnet system with six magnets provided in an inner pitch circle and six in an outer pitch circle, Fig. 7 a diagram showing an example of the curve of the spring unit of the drive according to the Fig. 2 and Fig. 3 represents the torque that can be generated on the output shaft as a function of the angle of rotation of the input shaft, and Fig. 8 a diagram showing an example of the course of the magnetic system of the drive according to the Fig. 2 and Fig. 3 represents the torque that can be generated on the output shaft as a function of the angle of rotation of the input shaft.

[0033] Fig. 1 shows in a purely schematic representation the basic structure of an exemplary embodiment of a drive 10 according to the invention for a leaf of a door, a window or the like.

[0034] The drive 10 comprises a housing 12, an output shaft 14 rotatably mounted in the housing 12, and an energy storage device 16, which can be charged with each opening of the wing and discharged when the wing is closed. The energy storage device 16 is provided as a mechanical energy storage device with at least one spring unit 18 and a magnet system 20 in a fluid-free space, which generates a resulting non-linear torque curve (cf., for example, Fig. 8) generate.

[0035] The spring unit 18 and the magnet system 20 of the energy storage device 16 act on a drive shaft 24 which is connected to the output shaft 14 via a gear stage 22 and is in particular perpendicular to the output shaft 14. In the case of a vertical output shaft 14, the drive shaft 24 can accordingly be provided as a horizontal shaft.

[0036] To generate the required closing torque, a combination of a spring unit 18 and a magnet system 20 is provided.

[0037] The drive 10 can be designed in particular as a door closer, wherein it is in the Fig. 2 and Fig. 3 is intended, for example, as an overhead door closer or as a floor door closer.

[0038] As can be seen in particular from the Fig. 2 and Fig. 3, the spring unit 18 can in particular comprise a spiral spring. Such a spring can also be arranged within the drive shaft 24, wherein the spiral spring can be connected externally to the drive shaft 24 and internally to a closing force adjustment or pretensioning device 32. In this case, the windings of this spiral spring 18 are arranged at a distance from one another (cf. in particular Fig. 3).

[0039] The spring unit or coil spring 18 can be firmly connected at one end to the drive shaft 24 and at the other end to the housing 12. The respective end can be connected to the housing 12, in particular via a pretensioning device (not shown).

[0040] With increasing wing opening angle and a corresponding rotation of the drive shaft 24, an at least approximately linearly increasing torque curve is generated on the output shaft 14 by the spring unit or spiral spring 18 (cf. Fig. 7).

[0041] In contrast, the magnet system 20 generates a non-linear torque curve on the output shaft 14 upon a corresponding rotation of the drive shaft 24 (cf. Fig. 8).

[0042] As can be seen in particular from the Fig. 3 to 6, the magnet system 20 may comprise a plurality of cooperating magnets 26.

[0043] In the present case, a part of the magnets 26 of the magnet system 20 is firmly connected to the drive shaft 24 and a further part of the magnets 26 of the magnet system 20, which interact with this part of the magnets, is firmly connected to the housing 14.

[0044] As can be seen particularly from the Fig. As can be seen from Figures 4 to 6, the magnets 26 of the magnet system 20 are arranged one above the other on two pitch circles 28, 30 concentric with the axis of the drive shaft 24. The magnets 26 of the magnet system 20 arranged on the inner pitch circle 28 are firmly connected to the drive shaft 24, and the magnets 26 of the magnet system 20 arranged on the outer pitch circle 30 are firmly connected to the housing 12.

[0045] The magnets 26 of the magnet system 20 arranged on the two pitch circles 28, 30 are positioned in such a way that they generate the non-linear torque curve on the output shaft 14 (cf. in particular Fig. 8) are displaced tangentially relative to each other.

[0046] The interacting magnets 6 of the magnet system 20 are arranged at a distance relative to each other in order to avoid corresponding friction losses.

[0047] The distance between the interacting magnets 26 of the magnet system 20 can in particular be < 0.2 mm, although a distance always remains between these interacting magnets 26 to avoid friction losses.

[0048] The spring unit or spiral spring 18 can be designed in such a way that it acts over the entire rotational angle range of the drive shaft 24, in particular corresponding to a rotational angle range of the output shaft 14 of approximately 180°. A possible course of the rotational angle generated by the spring unit or spiral spring 18 of the drive according to the Fig. 2 and Fig. 3 torque generated on the output shaft 14 as a function of the angle of rotation of the input shaft 24 is shown in the Fig. 7. In order to be able to adjust the closing torque, the spiral spring 18 in this case has a working angle range that is larger than the wing opening angle range of, for example, 0° to 180°.

[0049] In the present case, the magnet system 20 is designed, for example, in such a way that it generates its highest moment in a blade opening angle range of 0° to 4° and then, with a further increasing blade opening angle, generates a particularly periodically decreasing moment (cf. in particular Fig. 8).

[0050] The magnet system 20 can in principle comprise at least one pair of two magnets 26 which interact with each other, wherein in the present case it has a plurality of such pairs of two magnets 26 which interact with each other or are arranged one above the other.

[0051] The closing force of the magnet system 20 can be variably adjusted, in particular, by changing the overlap of the respective interacting magnets 26. This overlap of the respective interacting magnets 26 can be adjusted, for example, via a closing force adjustment or pretensioning device 32 associated with the spring unit or spiral spring 18 (cf. in particular Fig. 2) be variably adjustable.

[0052] The drive 10 can be attached to the door leaf or frame and coupled to a rod or slide rail. It can be designed, for example, as an electromechanical drive or door closer.

[0053] The gear stage 22 provided between the output shaft 14 and the input shaft 24 can in particular comprise a crown gear drive.

[0054] Fig. 4 shows an exemplary magnet system 20 of a drive 10 according to the invention with a relatively higher number of magnetic poles 34 or pairs of two interacting magnets 26, while in the Fig. 5 shows an exemplary magnet system 20 of the drive 10 according to the invention with a relatively smaller number of magnetic poles 34.

[0055] The relationship between the number of magnetic poles, the highest moment M1 on the output shaft 14, which occurs, for example, in a blade opening angle range of 0° to 4°, and the unwanted post-oscillation moments M i on the output shaft 4 results from the following relationship: |Mi|=M1−M1I−1nPoles

[0056] This shows that with a higher number of magnetic poles (cf. Fig. 4) the relatively highest magnetic moment M1 is increased and with a relatively smaller number of magnetic poles 34 the post-oscillation moments M i be reduced.

[0057] The magnet system 20 may, for example, comprise a region with three magnetic poles, a region with four to six magnetic poles and / or a region with six magnetic poles.

[0058] Fig. 6 shows the magnetic flux of the drive 10 according to the Fig. 2 and Fig.3, with six magnets 26 arranged in an inner pitch circle 28 and six in an outer pitch circle 30. This allows a comparatively high torque to be achieved in a blade opening angle range from 0° to 12°. At the same time, a comparatively high, but unwanted, post-oscillation torque is generated up to a twist angle of approximately 120°. With relatively fewer magnetic poles, the unwanted post-oscillation torque is reduced.

[0059] As can be seen from the above, the solution consists of a compromise between the highest possible initial torque acting on the output shaft 14 and the lowest possible post-oscillation torque acting on the output shaft 14.

[0060] With the drive 10 according to the invention, no fluid or oil is required to lubricate the moving parts. By appropriately designing the spring unit or coil spring 18 and, above all, the magnet system 20, a torque on the output shaft 14 that decreases sharply with increasing vane opening angle can be achieved.

[0061] Since the interacting magnets 26 do not touch each other and the turns of the spiral spring 18 are spaced apart from each other, friction losses are reduced to a minimum.

[0062] A corresponding door closer can be attached to the door leaf or frame and coupled with a rod or rail or directly to the leaf.

[0063] Since the interacting magnets 26 do not touch each other and the spiral spring 18 is advantageously provided with windings spaced apart from each other, friction losses only occur in the bearings of the shafts 14, 24 and in the gear stage 22. Thus, a very high efficiency of the energy storage device 16 can be achieved.

[0064] With a corresponding design of the spring unit or spiral spring 18 and the gear stage 22, wear is minimized, so that a very high number of cycles of the energy storage device 16 can be expected.

[0065] In connection with an electromechanical drive or door closer 10, the solution according to the invention also has the particular advantage that comparatively much installation space is available for the motor-gear unit. List of reference symbols 10 Drive 12 housings 14 Output shaft 16 fluid-free mechanical energy storage 18 Spring unit, spiral spring 20 Magnet system 22 gear stages 24 Drive shaft 26 Magnet 28 inner pitch circle 30 outer pitch circle 32 Closing force adjustment or pre-tensioning device 34 magnetic pole n Pole Number of magnetic poles

Claims

[1] Drive (10) for a leaf of a door, a window or the like, with a housing (12), an output shaft (14) rotatably mounted in the housing (12) for the rotation of the leaf, and with an energy storage device (16) which can be charged with each opening of the leaf and discharged for closing the leaf, which has a spring unit (18) in a fluid-free space, wherein a magnet system (20) is provided which, together with the spring unit (18), generates a resulting, non-linear torque curve on the output shaft (14), and for this purpose comprises a plurality of cooperating magnets (26), characterized by that a part of the magnets (26) of the magnet system (20) is firmly connected to a drive shaft (24) operatively connected to the spring unit (18) and a further part of the magnets (26) of the magnet system (20) cooperating with this part of the magnets is firmly connected to the housing (12). [2] Drive according to claim 1, characterized bythat the magnets (26) of the magnet system (20) are arranged one above the other on two partial circles (28, 30) concentric with the axis of the drive shaft (24). [3] Drive according to claim 2, characterized by that the magnets (26) of the magnet system (20) arranged on the inner pitch circle (28) are firmly connected to the drive shaft (24) and the magnets (26) of the magnet system (20) arranged on the outer pitch circle (30) are firmly connected to the housing (12). [4] Drive according to claim 2 or 3, characterized by that the magnets (26) of the magnet system (20) arranged on different pitch circles (28, 30) are positioned such that they are displaced tangentially relative to one another during a respective rotation of the drive shaft (24). [5] Drive according to at least one of the preceding claims, characterized by that the interacting magnets (26) of the magnet system (20) are arranged at a distance from one another. [6] Drive according to claim 5, characterized by that the distance between the interacting magnets (26) of the magnet system (20) is < 0.2 mm. [7] Drive according to at least one of the preceding claims, characterized by that a non-linear torque curve can be generated on the output shaft (14) by the magnet system (20). [8] Drive according to at least one of the preceding claims, characterized by that the magnet system (20) is designed such that it generates its highest moment in a blade opening angle range of 0° to 4° and then, with further increasing blade opening angle, generates a particularly periodically decreasing moment. [9] Drive according to at least one of the preceding claims, characterized by that the magnet system (20) comprises at least one pair, in particular a plurality of pairs, of two magnets (26) which interact with one another or are arranged one above the other. [10] Drive according to at least one of the preceding claims, characterized by that the closing force of the magnet system (20) is variably adjustable, in particular by changing the overlap of the respective interacting magnets (26), preferably via a closing force adjustment or pretensioning device (32) associated with the spring unit (18). [11] Drive according to at least one of the preceding claims, characterized by that the spring unit (18) comprises a spiral spring (18), the windings of which are arranged in particular at a distance from one another. [12] Drive according to at least one of the preceding claims, characterized by that the spring unit or spiral spring (18) is firmly connected at one end to the drive shaft (24) and at the other end, in particular via a pretensioning device, to the housing (12). [13] Drive according to at least one of the preceding claims, characterized bythat an at least approximately linear torque curve can be generated on the output shaft (14) by the spring unit (18). [14] Drive according to at least one of the preceding claims, characterized by that the spring unit or spiral spring (18) is designed such that it acts over the entire angle of rotation of the drive shaft (24), in particular corresponding to a rotation angle range of the output shaft (14) of approximately 180°. [15] Drive according to at least one of the preceding claims, characterized by that the spring unit (18) with the magnet system (20) of the mechanical energy storage device (16) act on the output shaft (14) via a gear stage (22). [16] Drive according to claim 15, characterized by that the gear stage (22) provided between the output shaft (14) and the input shaft (24) comprises a crown gear drive. [17] Drive according to at least one of the preceding claims, characterized bythat the drive (10) is designed as a door closer. [18] Drive according to at least one of the preceding claims, characterized by that the drive (10) is designed as an electromechanical drive.

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