DE102019206733A1 - DRIVE FOR A LEAF, IN PARTICULAR FOR A DOOR OR WINDOW - Google Patents

Abstract

A drive for a wing of a door, a window or the like comprises a housing, an output shaft rotatably mounted in the housing for rotating the wing, and an energy storage device that can be charged with each opening of the wing and discharged for closing the wing, which has a spring unit in a fluid-free space, as well as a magnet system which, together with the spring unit, generates a resulting, non-linear torque curve on the output shaft, and for this purpose comprises a plurality of interacting magnets, part of the magnets of the magnet system being firmly connected to one that is operatively connected to the spring unit Drive shaft, and a further part of the magnets of the magnet system which cooperates with this part of the magnets is firmly connected to the housing.

Description

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

Drives or door closers of the type mentioned at the beginning usually have a hydraulic damping element in the form of a damping piston and a closing spring which acts directly on this damping piston and which interact in a common housing.

A disadvantage of these conventional drives is, among other things, that they require a hydraulic fluid, such as oil in particular, to lubricate the moving parts and take up a relatively large amount of installation space, which is particularly lacking in an electric motor drive for its motor-gear unit.

In the DE 198 31 393 B4 describes a door closer, the damping device of which is arranged in a separate housing section in a fluid-free space.

The invention is based on the object of specifying a drive of the type mentioned at the outset, in which the aforementioned disadvantages are eliminated. The drive should also manage without hydraulic fluid or lubricant and should have a high degree of efficiency and should be kept as simple as possible in construction with as little space as possible for the individual components.

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

Due to the solution according to the invention, no hydraulic medium such as oil is required to lubricate the moving parts. With an appropriate design of the spring unit and the magnet system, the torque required in each case via the angle of rotation can be generated on the output shaft of the drive. Since the magnets of the magnet system do not have to touch each other, there are no friction losses in their area. In particular with regard to an electromechanical drive, the solution according to the invention also has the advantage that a comparatively large amount of installation space is available for the motor-gear unit.

The spring unit and the magnet system of the energy store preferably act on an output shaft connected to the output shaft via a gear stage and in particular perpendicular to the output shaft. In the case of a vertical output shaft, the drive shaft can thus in particular be horizontal.

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

According to a preferred practical embodiment of the drive according to the invention, the spring unit comprises a spiral spring. Their turns are advantageously arranged at a distance from one another, as a result of which the friction losses are further minimized and thus the efficiency is additionally increased.

By means of such an energy storage device, a torque that drops sharply as the wing opens can be generated on the output shaft. With an appropriate design of the spiral spring and the gear stage, the wear is reduced to a minimum and a very high number of cycles of the mechanical energy store can be achieved.

The spring unit or spiral spring is expediently firmly connected at one end to the drive shaft and at the other end to the housing. The spring unit is advantageously connected to the housing via a pretensioning device. The torque curve generated by the spring unit on the output shaft can then be variably adjusted via such a pretensioning device.

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.

The magnet system preferably comprises a plurality of interacting magnets.

According to a preferred practical embodiment of the drive according to the invention, some of the magnets of the magnet system are firmly connected to the drive shaft and a further part of the magnets of the magnet system that interacts with this part of the magnets is firmly connected to the housing.

With a respective rotation of the output shaft and an associated respective rotation of the drive shaft, the interacting magnets can be displaced relative to one another, which results in the non-linear torque curve on the output shaft.

It is particularly advantageous if the magnets of the magnet system are arranged one above the other on two partial circles concentric to the axis of the drive shaft.

The magnets of the magnet system arranged on the inner pitch circle are preferably fixedly connected to the drive shaft and the magnets of the magnet system arranged on the outer pitch circle are fixedly connected to the housing.

The magnets of the magnet system, which are arranged on different pitch circles, can expediently be positioned in such a way that they are displaced tangentially relative to one another with a respective rotation of the drive shaft to generate a non-linear torque curve on the output shaft.

The respectively interacting magnets of the magnet system are preferably arranged at a distance relative to one another.

If both the interacting magnets of the magnet system and the various turns of the spiral spring are arranged at a distance from one another, friction losses occur only in the bearing points of the shafts and in the gear stage provided between the drive shaft and the output shaft, which results in a very good efficiency of the spring unit and the magnet system comprehensive energy storage is achieved. With an appropriate design of the spiral spring and the gear stage, wear is reduced to a minimum and a very high number of mechanical energy storage cycles can be achieved.

The distance between the respectively interacting magnets of the magnet system is preferably <0.2 mm. Preferably, however, there is always a minimal distance between the interacting magnets.

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 range of the drive shaft, in particular corresponding to a rotation angle range of the output shaft of approximately 180 °.

The magnet system can in particular be designed in such a way that it generates its highest moment in a vane opening angle range from 0 ° to 4 ° and then, as the vane opening angle continues to increase, an in particular periodically decreasing moment.

It is particularly advantageous if the magnet system comprises at least one pair, in particular a plurality of pairs of two magnets that interact with one another or are arranged one above the other. For example, three or four to six such pairs of two magnets interacting with one another or arranged one above the other can be provided. In principle, however, a different number of interacting magnets and a different arrangement of the magnets is also conceivable.

According to an expedient practical embodiment of the drive according to the invention, the closing force of the magnet system can be variably adjusted in particular by changing the overlap of the magnets that interact with one another. The corresponding adjustment of the closing force of the magnet system can in particular also take place via a closing force adjustment or pretensioning device assigned to the spring unit.

The number n _poles of poles or pairs of mutually interacting magnets of the magnet system is related to the comparatively highest magnetic torque M ₁ generated on the output shaft and the post-oscillation moments M _i generated on the output shaft, as can be seen from the following relationship: $$\left|{\text{M.}}_{\text{i}}\right|={\text{M.}}_1-{\text{M.}}_1\frac{\text{l}-1}{{\text{n}}_{\text{Pole}}}$$

As can be seen from this relationship, many magnetic poles increase the relatively highest magnetic moment M ₁ , while fewer magnetic poles reduce the post-oscillation moment or moments M _i . The magnet system can for example be provided with an area for three poles, with an area for four to six poles and / or with an area of six poles.

In order to be able to set the closing moment, the spiral spring can be designed with a working angle range that is larger than the blade opening angle range of 180 °, for example.

• 1 eine schematische Darstellung des Grundaufbaus einer beispielhaften Ausführungsform eines erfindungsgemäßen Antriebs,
• 2 eine detailliertere schematische Längsschnittdarstellung einer weiteren beispielhaften Ausführungsform eines erfindungsgemäßen Antriebs, wobei der Antrieb beispielsweise als obenliegender Türschließer ausgeführt ist,
• 3 eine nur schematische Querschnittsdarstellung des Antriebs gemäß 2,
• 4 eine nur schematische Darstellung eines beispielhaften Magnetsystems eines erfindungsgemäßen Antriebs mit einer relativ höheren Anzahl von Magnetpolen,
• 5 eine nur schematische Darstellung eines beispielhaften Magnetsystems eines erfindungsgemäßen Antriebs mit einer relativ geringeren Anzahl von Magnetpolen,
• 6 eine nur schematische Darstellung des magnetischen Flusses des bei dem Antrieb gemäß den 2 und 3 vorgesehenen sechspoligen Magnetsystems mit sechs in einem inneren Teilkreis vorgesehenen und sechs in einem äußeren Teilkreis vorgesehenen Magneten,
• 7 ein Diagramm, das einen beispielhaften Verlauf des durch die Federeinheit des Antriebs gemäß den 2 und 3 an der Abtriebswelle erzeugbaren Moments in Abhängigkeit vom Drehwinkel der Antriebswelle wiedergibt, und
• 8 ein Diagramm, das einen beispielhaften Verlauf des durch das Magnetsystem des Antriebs gemäß den 2 und 3 an der Abtriebswelle erzeugbaren Moments in Abhängigkeit vom Drehwinkel der Antriebswelle wiedergibt.

The invention is explained in more detail below using exemplary embodiments with reference to the drawing; in this show:

• 1 a schematic representation of the basic structure of an exemplary embodiment of a drive according to the invention,
• 2 a more detailed schematic longitudinal sectional view of a further exemplary embodiment of a drive according to the invention, the drive being designed, for example, as an overhead door closer,
• 3 a schematic cross-sectional view of the drive according to FIG 2 ,
• 4th a schematic representation of an exemplary magnet system of a drive according to the invention with a relatively higher number of magnetic poles,
• 5 a schematic representation of an exemplary magnet system of a drive according to the invention with a relatively smaller number of magnet poles,
• 6th a schematic representation of the magnetic flux of the drive according to the 2 and 3 provided six-pole magnet system with six magnets provided in an inner pitch circle and six magnets provided in an outer pitch circle,
• 7th a diagram showing an exemplary course of the by the spring unit of the drive according to the 2 and 3 reproduces the torque that can be generated on the output shaft as a function of the angle of rotation of the drive shaft, and
• 8th a diagram showing an exemplary course of the by the magnet system of the drive according to the 2 and 3 reproduces the torque that can be generated on the output shaft as a function of the angle of rotation of the drive shaft.

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

The drive 10 includes a housing 12 , one rotatable in the housing 12 output shaft with bearings 14th and an energy store 16 , which can be charged with each opening of the wing and can be discharged for closing the wing. Here is the energy store 16 as a mechanical energy store with at least one spring unit 18th and a magnet system 20th provided in a fluid-free space on the output shaft 14th a resulting non-linear torque curve (see for example 8th ) produce.

The spring unit 18th and the magnet system 20th of the energy storage 16 act on one via one gear stage 22nd with the output shaft 14th connected to the output shaft 14th especially vertical drive shaft 24 . With a vertical output shaft 14th can the drive shaft 24 be provided accordingly as a horizontal shaft.

A combination of a spring unit is therefore required to generate the required closing torque 18th and a magnet system 20th intended.

The drive 10 can in particular be designed as a door closer, where it is in the 2 and 3 illustrated embodiment is provided for example as an overhead door closer or as a floor spring.

As in particular using the in the 2 and 3 shown embodiment, the spring unit 18th in particular comprise a spiral spring. Such can also be inside the drive shaft 24 be arranged, the spiral spring outside with the drive shaft 24 and inside with a clamping force adjustment or pretensioning device 32 can be connected. Here are the turns of this spiral spring 18th in the present case arranged at a distance from one another (cf. in particular 3 ).

The spring unit or spiral spring 18th can with one end to the drive shaft 24 and the other end to the housing 12 be firmly connected. The end in question can be connected to the housing in particular via a prestressing device (not shown) 12 be connected accordingly.

With increasing blade opening angle and a corresponding rotation of the drive shaft 24 is made by the spring unit or spiral spring 18th an at least approximately linearly increasing torque curve on the output shaft 14th generated (cf. 7th ).
In contrast, the magnet system generates 20th with a corresponding rotation of the drive shaft 24 a non-linear torque curve on the output shaft 14th (see. 8th ).

As in particular from the 3 to 6th can be seen, the magnet system 20th a plurality of cooperating magnets 26th include.

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

As is evident from the 4th to 6th can be seen are the magnets 26th of the magnet system 20th while on two to the axis of the drive shaft 24 concentric pitch circles 28 , 30th arranged one above the other. Here are those on the inner pitch circle 28 arranged magnets 26th of the magnet system 20th firmly to the drive shaft 24 and the one on the outer pitch circle 30th arranged magnets 26th of the magnet system 20th firmly to the housing 12 connected.

The ones on the two partial circles 28 , 30th arranged magnets 26th of the magnet system 20th are like that positioned that they are with a respective rotation of the drive shaft 24 for generating the non-linear torque curve on the output shaft 14th (see in particular 8th ) are displaced tangentially relative to each other.

The magnets interacting in each case 6th of the magnet system 20th are arranged at a distance from one another in order to avoid corresponding friction losses.

The distance between the respectively interacting magnets 26th of the magnet system 20th in particular <0.2 mm, with a distance between these interacting magnets, however, to avoid friction losses 26th persists.

The spring unit or spiral spring 18th can be designed so that they over the entire, in particular one angle of rotation range of the output shaft 14th of approximately 180 ° corresponding, angle of rotation range of the drive shaft 24 works. A possible course of the through the spring unit or spiral spring 18th of the drive according to the 2 and 3 on the output shaft 14th generated torque depending on the angle of rotation of the drive shaft 24 is in the 7th reproduced. In order to be able to adjust the closing moment, the spiral spring has 18th in the present case a working angle range which is greater than the blade opening angle range of, for example, 0 ° to 180 °.

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

The magnet system 20th can basically at least one pair of two interacting magnets 26th comprise, wherein in the present case there is a plurality of such pairs of two magnets that interact with one another or are arranged one above the other 26th having.

The closing force of the magnet system 20th can in particular by changing the overlap of the magnets that interact with one another 26th be variably adjustable. This overlap of the magnets interacting with each other 26th can for example via one of the spring unit or spiral spring 18th associated clamping force adjustment or pretensioning device 32 (see in particular 2 ) be variably adjustable.

The drive 10 can be attached to the door leaf or frame and coupled with a linkage or slide rail. It can for example be designed as an electromechanical drive or door closer.

The one between the output shaft 14th and the drive shaft 24 intended gear stage 22nd can in particular comprise a crown gear drive.

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

The relationship between the number of magnetic poles, the highest torque M _i occurring on the output shaft, for example in a blade opening angle range of 0 ° to 4 ° 14th and the unwanted post-oscillation moments M _i on the output shaft 4th results from the following relationship: $$\left|{\text{M.}}_{\text{i}}\right|={\text{M.}}_1-{\text{M.}}_1\frac{\text{l}-1}{{\text{n}}_{\text{Pole}}}$$

It can be seen from this that with a higher number of magnetic poles (cf. 4th ) the relatively highest magnetic torque M _{1 is} increased and with a relatively smaller number of magnetic poles 34 the post-oscillation moments M _{i are} reduced.

The magnet system 20th may, for example, include an area with three magnetic poles, an area with four to six magnetic poles and / or an area with six magnetic poles.

6th shows the magnetic flux of the drive 10 according to the 2 and 3 provided six-pole magnet system 20th with six in an inner pitch circle 28 provided and six in an outer pitch circle 30th provided magnets 26th . In this way, a comparatively high torque can be achieved in a wing opening angle range of 0 ° to 12 °. At the same time, up to a twist angle of up to about 120 °, a comparatively high, but undesired, post-oscillation moment arises. The unwanted post-oscillation moments are reduced with relatively fewer magnetic poles.

As can be seen from the foregoing, the solution consists of a compromise between an initial as high as possible, on the output shaft 14th acting torque and the lowest possible on the output shaft 14th acting post-oscillation moments.

In the drive according to the invention 10 no fluid or oil is required to lubricate the moving parts. By appropriate design of the spring unit or spiral spring 18th and above all the magnet system 20th a torque on the output shaft that decreases sharply with increasing blade opening angle can occur 14th can be achieved.

Because the interacting magnets 26th do not touch and the coils of the coil spring 18th are provided at a respective distance from each other, the friction losses are reduced to a minimum.

A corresponding door closer can be attached to the door leaf or the frame and directly coupled with a linkage or a rail or the leaf.

Because the interacting magnets 26th do not touch and the coil spring 18th is advantageously provided with a respective distance from one another having turns, arise only in the bearing points of the shafts 14th , 24 as well as in the gear stage 22nd Frictional losses. It can therefore have a very good efficiency of the energy store 16 can be achieved.

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

In connection with an electromechanical drive or door closer 10 the solution according to the invention also has the particular advantage that a comparatively large amount of installation space is available for the motor-gear unit.

List of reference symbols

10

drive

12

casing

14th

Output shaft

16

fluid-free mechanical energy storage

18th

Spring unit, spiral spring

20th

Magnet system

22nd

Gear stage

24

drive shaft

26th

magnet

28

inner pitch circle

30th

outer pitch circle

32

Closing force adjustment or pre-tensioning device

34

Magnetic pole

n _poles

Number of magnetic poles

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 19831393 B4 [0004]

Claims (18)

Drive (10) for a wing 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 wing, and with an energy store (16), which is connected to each opening of the wing can be charged and discharged for closing the wing, which has a spring unit (18) in a fluid-free space, characterized in that a magnet system (20) is provided which, together with the spring unit (18), is attached to the output shaft ( 14) generates a resulting, non-linear torque curve, and for this purpose comprises a plurality of interacting magnets (26), some of the magnets (26) of the magnet system (20) fixed to a drive shaft (24) that is operatively connected to the spring unit (18) and a with this part of the magnets cooperating further part of the magnets (26) of the magnet system (20) is firmly connected to the housing (12). Drive after Claim 1 , characterized in that the magnets (26) of the magnet system (20) are arranged one above the other on two partial circles (28, 30) concentric to the axis of the drive shaft (24). Drive after Claim 2 , characterized in that the magnets (26) of the magnet system (20) arranged on the inner pitch circle (28) are fixed to the drive shaft (24) and the magnets (26) of the magnet system (20) arranged on the outer pitch circle (30) are fixed are connected to the housing (12). Drive after Claim 2 or 3 , characterized in that the magnets (26) of the magnet system (20) arranged on different pitch circles (28, 30) are positioned in such a way that they are displaced tangentially relative to one another with a respective rotation of the drive shaft (24). Drive according to at least one of the preceding claims, characterized in that the respectively interacting magnets (26) of the magnet system (20) are arranged at a distance from one another. Drive after Claim 5 , characterized in that the distance between the respectively interacting magnets (26) of the magnet system (20) is <0.2 mm. Drive according to at least one of the preceding claims, characterized in that the magnet system (20) can produce a non-linear torque curve on the output shaft (14). Drive according to at least one of the preceding claims, characterized in that the magnet system (20) is designed in such a way that it generates its highest moment in a vane opening angle range of 0 ° to 4 ° and thereupon a periodically decreasing moment as the vane opening angle continues to increase. Drive according to at least one of the preceding claims, characterized in 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. Drive according to at least one of the preceding claims, characterized in that the closing force of the magnet system (20) in particular by changing the overlap of the respectively interacting magnets (26), preferably via a closing force adjustment or pretensioning device (32) assigned to the spring unit (18), is variably adjustable. Drive according to at least one of the preceding claims, characterized in that the spring unit (18) comprises a spiral spring (18), the turns of which are arranged in particular at a distance from one another. Drive according to at least one of the preceding claims, characterized in 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). Drive according to at least one of the preceding claims, characterized in that the spring unit (18) can generate an at least approximately linear torque curve on the output shaft (14). Drive according to at least one of the preceding claims, characterized in that the spring unit or spiral spring (18) is designed in such a way that it over the entire, in particular a rotational angle range of the output shaft (14) corresponding to approximately 180 °, the rotational angle range of the drive shaft (24) works. Drive according to at least one of the preceding claims, characterized in that the spring unit (18) with the magnet system (20) of the mechanical energy store (16) act on the output shaft (14) via a gear stage (22). Drive after Claim 15 , characterized in that the between the output shaft (14) and the gear stage (22) provided for the drive shaft (24) comprises a crown gear drive. Drive according to at least one of the preceding claims, characterized in that the drive (10) is designed as a door closer. Drive according to at least one of the preceding claims, characterized in that the drive (10) is designed as an electromechanical drive.

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