Drive

Abstract

The present invention relates to a drive, in particular for a window or door sash, comprising a housing, a motor, and a gear unit housed in the housing for driving an output shaft, wherein the output shaft is configured to be connected to a force transmission element for the sash for opening and / or closing the sash. The gear unit has a torus wheel driven by the motor shaft and a curved wheel meshing with the torus wheel, wherein the torus wheel has a rolling surface with a toothing having at least one helically arranged tooth, and the curved wheel has a cylindrical rolling surface with several teeth.

Description

[0001] The present invention relates to a drive, in particular for a window or door sash, comprising a housing, a motor, and a gear unit housed in the housing for driving an output shaft, wherein the output shaft is configured to be connected to a force transmission element for the sash for opening and / or closing the sash. The invention further relates to a door or window with a pivotally mounted sash and such a drive for opening and / or closing the sash.

[0002] Drives for a sash of a window or door are generally known.

[0003] From DE 10 2015 105 623 B4, for example, an actuator for the automatic movement of locking elements for building openings, in particular for window sashes, is known. The actuator comprises a housing elongated along a longitudinal direction, a drive motor arranged in the housing, a power transmission element extendable into and out of the housing through a through-opening for transmitting an actuating force to a locking element, and a gearbox for transmitting a drive force generated by the drive motor to the power transmission element. The drive motor has an output shaft and a first gearbox element arranged on it, wherein the first gearbox element engages with a second gearbox element during power transmission from the drive motor via the gearbox to the power transmission element.The first gear element can be designed as a worm gear and the power transmission element can be designed as a power transmission chain.

[0004] In most automatic window drives, such as the drive known from DE 102015 105 623 B4, the motor movement is transmitted via a helical gear or worm gear and several spur gear stages to a chain sprocket, which drives a chain.

[0005] Due to the limited installation space of such drives, small motors with low torque are often used. This necessitates high gear ratios of approximately 300-400, which are typically achieved with four-stage gearboxes. The helical gear drive usually has very high gear ratios of around 40 or higher. However, this significantly reduces efficiency, regularly falling below 35 percent.

[0006] Ideally, the mechanisms used to operate windows or doors should not be reversible, preventing an open window or door from closing on its own. However, these mechanisms should also have the highest possible efficiency so that the window or door can be opened or closed within the required time even with a small or relatively low-powered motor.

[0007] This balancing act complicates and increases the cost of developing and manufacturing such drives and makes them susceptible to errors due to tolerance deviations.

[0008] It is therefore an object of the present invention to provide a drive for a sash of a window or door that exhibits high efficiency with a compact installation space, reduced complexity and reduced manufacturing costs. Furthermore, a corresponding window or door is to be specified.

[0009] According to the invention, this problem is solved by a drive having the features of claim 1 and by a window or door having the features of claim 10. Preferred embodiments of the drive according to the invention are described in the dependent claims, the description, and the drawings.

[0010] The drive according to the invention is characterized in that the gear unit has a torus wheel driven by the motor shaft and a bow wheel engaged with the torus wheel, wherein the torus wheel has a rolling surface with a toothing with at least one spirally arranged tooth and the bow wheel has a cylindrical rolling surface with several teeth.

[0011] In other words, in the drive according to the invention, the conventional helical gear or worm gear (in the input stage of the gear unit) is replaced by a spiral gear (also known as a planar spiral gear or torus gear). The spiral gear has the characteristic of exhibiting a high efficiency of approximately 50 percent even at high gear ratios and is simultaneously non-reverse-driven. The torus gear can also be referred to as a planar spiral gear.

[0012] If the transmission unit is designed as a three-stage gearbox, the spiral gear can achieve a very high gear ratio, namely a ratio greater than 100 or sometimes even greater than 150, by means of the aforementioned substitution. This eliminates one spur gear stage of the (usually four-stage) gearbox and simultaneously achieves high efficiency. Therefore, it may be sufficient if only two spur gear stages follow the input stage before the motion is transferred to a power transmission element, such as a chain. This saves space and costs.

[0013] If the gear unit is designed as a four-stage gearbox, the spiral gear can have a gear ratio of less than 100, and particularly advantageously less than 70. Accordingly, the diameter of the spiral wheel can be chosen to be smaller. This results in advantageous arrangement options for the further gear stages, so that even with this design, space and costs can be saved.

[0014] Due to its high efficiency, the drive according to the invention can move heavier loads and / or the window (or door) can be opened or closed faster.

[0015] The motor can be located inside the housing, or it can be located outside the housing (especially on the front). It can be connected to the housing directly or via an adapter (e.g., screwed on).

[0016] In one embodiment, the gear unit further comprises at least a first spur gear stage and a second spur gear stage. In particular, the first spur gear stage and the second spur gear stage are arranged in one plane.

[0017] Preferably, any further spur gear stages are also arranged in the aforementioned plane. Particularly preferably, the first and second spur gear stages are arranged in a plane that runs parallel to the plane of rotation of the bow wheel (and is not the same as the plane of rotation of the bow wheel) or perpendicular to an axis of rotation of the bow wheel and / or the output shaft. This arrangement offers the advantage that a comparatively large installation space can be made available for other components, especially the bow wheel. Therefore, both the size and arrangement of the bow wheel can be chosen flexibly.

[0018] In another embodiment, the curved wheel is non-rotatably connected to a pinion of the first spur gear stage.

[0019] The axis of rotation of the curved wheel is preferably the same as the axis of rotation of the pinion. This allows the first spur gear stage (consisting of the pinion and a first spur gear that meshes with the pinion) to run in a different (rotational) plane than the curved wheel.

[0020] Depending on the design of the gear unit, an embodiment is advantageous in which the curved gear essentially terminates with a first housing side and a meshing spur gear of the first spur gear stage essentially terminates with a second housing side (or vice versa), wherein the first housing side and the second housing side are opposite each other in a direction perpendicular to the longitudinal direction of the housing and perpendicular to the axis of rotation of the curved gear. Particularly preferably, in this embodiment, the curved gear does not terminate with the second housing side or is spaced apart from it, and the spur gear of the first spur gear stage does not terminate with the first housing side or is spaced apart from it.

[0021] This embodiment is particularly advantageous when the gear unit has more than two spur gear stages. For example, in the case of a four-stage gearbox with three spur gear stages, the spiral gear preferably has a gear ratio of less than 100, and more preferably less than 70, so that a curved gear with a reduced diameter is sufficient. This allows the spur gear stages to be arranged differently compared to a helical gear stage as the input stage, and in particular to be arranged much more compactly, thus requiring less overall installation space. In other words, the curved gear and the spur gear of the first spur gear stage (or their axes of rotation) can be arranged relatively far apart from each other in the direction perpendicular to the longitudinal direction of the housing and perpendicular to the axis of rotation of the curved gear, i.e., the depth direction of the drive or housing.Accordingly, the size of the housing can be quite small in the longitudinal direction of the housing.

[0022] Due to the lower gear ratio, less force is transmitted. Accordingly, the bow wheel can be made from relatively inexpensive metallic materials or even plastics. Sintered metals, polyamide (PA), or acetal resin (polyoxymethylene; POM) are particularly suitable.

[0023] In a preferred embodiment, the curved wheel substantially fills the housing in a direction perpendicular to the longitudinal direction of the housing and perpendicular to its axis of rotation.

[0024] In other words, the curved gear utilizes virtually the entire depth of the drive or housing. The circumference of the curved gear is thus maximized in this embodiment. Consequently, a very high gear ratio can be achieved, so that it may be sufficient for only two spur gear stages to follow the spiral gear before power is transmitted to the power transmission element.

[0025] In this embodiment, the bow wheel is preferably arranged centrally within the depth of the housing. More precisely, the axis of rotation of the bow wheel is located centrally within the housing in the depth direction, i.e., in the direction perpendicular to the longitudinal direction of the housing and perpendicular to its axis of rotation.

[0026] In a preferred embodiment, the torus wheel is arranged closer to the motor in the longitudinal direction of the housing than the curved wheel.

[0027] It is particularly preferred that the torus wheel is arranged on the end face of the motor shaft or connected to it.

[0028] In a further preferred embodiment, the rolling surface of the torus wheel is at least partially concave and / or the toothing of the torus wheel engages with two or more teeth of the arc wheel.

[0029] The concave rolling surface of the torus gear is particularly advantageous where it engages with the at least one helically arranged tooth. This, in conjunction with the curved gear (which has a convex rolling surface), allows for a particularly strong engagement between the two gears, thus increasing power transmission. A concave rolling surface of the helical gear can also help to keep more teeth of the curved gear (preferably two or more) engaged. If several teeth of the curved gear engage with the at least one tooth of the torus gear simultaneously (where the helically arranged tooth of the torus gear has multiple turns), the forces to be transmitted are distributed across several teeth. This allows for smaller modules and thus a higher gear ratio. Alternatively, it enables the movement of heavier loads within the installation space.

[0030] In a preferred embodiment of the drive, the teeth of the curved wheel are curved in an arc shape at least on one side.

[0031] In other words, at least one flank of the teeth of the arc wheel is curved in an arc shape. Since the toothing of the torus wheel has at least one spirally arranged tooth, the teeth of the arc wheel advantageously follow this spiral curvature. This improves the engagement of the arc wheel with the torus wheel.

[0032] The teeth of the curved gear are particularly advantageous when they are curved on both sides, with both tooth flanks being convex. In this case, forces can be absorbed by the curved gear in both directions of rotation. Depending on the drive mounting method, this can be beneficial.

[0033] In a preferred embodiment, the torus wheel has an extension which is supported in the housing via a bearing, and / or the torus wheel is connected to the motor shaft by force and / or form locking.

[0034] The bearing is preferably a ball bearing (e.g., a deep groove ball bearing or angular contact ball bearing) or a roller bearing. Other bearing types are also conceivable. The motor shaft can be connected to the torus wheel, for example, via a key or similar device. This ensures that the torus wheel is connected to the motor in a particularly efficient manner. Furthermore, this embodiment contributes to a particularly compact design of the drive.

[0035] In a further preferred embodiment, the axis of the motor shaft is arranged at an angle to the longitudinal axis of the housing, wherein the angle between the axis of the motor shaft and the longitudinal axis of the housing is at least 2°, in particular at least 4°.

[0036] This embodiment is characterized by the fact that a large or powerful motor can be used and the installation space of the drive along its longitudinal axis can still be reduced.

[0037] In a further embodiment, the drive also has a rotary output member, wherein the rotary output member is mounted non-rotatably on the output shaft and is designed to cooperate with the power transmission member.

[0038] The rotary output element is preferably a chain sprocket or a gear, and the power transmission element is preferably a rack or a chain. The chain sprocket is rotationally fixed to a spur gear, which meshes with an upstream spur gear. The two spur gears mentioned are preferably essentially the same size, or the gear ratio / reduction of this (last) spur gear stage is relatively low compared to the other gear stages in the drive. In this respect, the "penultimate" spur gear in the transmission unit primarily serves to bridge the distance, in order to create sufficient space for the chain.

[0039] In a preferred embodiment, the at least one tooth arranged spirally on the rolling surface of the torus wheel follows the path of an Archimedean spiral whose origin is located on the axis of rotation of the torus wheel. Preferably, the spiral has at least one turn, and more preferably at least two (or more) turns. This allows for a particularly effective engagement between the arc wheel and the torus wheel.

[0040] The gearing of the torus gear preferably comprises two or more helically arranged teeth whose common origin is located on the axis of rotation of the torus gear. This further improves the engagement with the arc gear.

[0041] Further developments of the invention can also be found in the dependent claims, the description and the accompanying drawings.

[0042] The invention is described below by way of example with reference to the drawings. The drawings show (schematically) Fig. 1 a perspective view of a first embodiment of the drive according to the invention, Fig. 2 a perspective view of the first embodiment of the drive according to the invention with housing cover, Fig. 3 a top view of the first embodiment of the drive according to the invention, Fig. 4 a side view of the first embodiment of the drive according to the invention, Fig. 5 a perspective view of the motor, the torus wheel and the arc wheel of the first embodiment of the drive according to the invention including an enlarged section of the rolling surface of the arc wheel, Fig. 6 a side view of a section of the rolling surface of an arc wheel of a second embodiment of the drive according to the invention, Fig. 7 a top view of a section of a third embodiment of the drive according to the invention, Fig. 8 a sectional view of a section of a fourth embodiment of the drive according to the invention, Fig.Fig. 9 a perspective view of a fifth embodiment of the drive according to the invention, Fig. 10 a top view of the fifth embodiment of the drive according to the invention, Fig. 11 a side view of the fifth embodiment of the drive according to the invention, Fig. 12 a top view of a sixth embodiment of the drive according to the invention.

[0043] Fig. 1 Figure 1 shows a perspective view of a first embodiment of the drive according to the invention. The drive is designated by reference numeral 10. The drive 10 comprises a housing 12 and a motor 14 arranged (at its end) on the housing 12. In other words, the motor 14 connects to the housing 12 in the longitudinal direction L of the housing or drive 10 (indicated by the double arrow). It is also conceivable that the motor 14 is integrated into the housing 12. The axis of the motor, or more precisely the motor shaft, is designated by reference numeral 141.

[0044] The housing 12 contains a gear unit 16 for driving a drive shaft 18, wherein the output shaft 18 is connected via a chain sprocket 20, also called rotary output link, to a chain 22, also called power transmission link, for the sash (not shown) of a window or door for opening and / or closing the sash.

[0045] In this embodiment, the gear unit 16 is designed as a three-stage assembly, with the input stage being a spiral gear. The gear unit 16 includes a torus gear 24 driven by the motor shaft. The torus gear 24 engages with the gear teeth on the rolling surface 262 of the arc gear 26 via its teeth on the rolling surface 242. The teeth of the torus gear 24 are formed by a helically arranged tooth on the rolling surface 242 of the torus gear 24, which has several turns. The teeth on the rolling surface 262 of the arc gear 26 are curved on one side and thus follow the helical shape of the tooth on the torus gear 24.

[0046] The arc wheel 26 is non-rotatably connected to a pinion (not shown), which meshes with a first spur gear 34. The pinion and the first spur gear 34 form a first spur gear stage. The first spur gear 34, in turn, meshes with a second spur gear 36, forming the second spur gear stage. The second spur gear 36 is non-rotatably connected to the output shaft 18, which is itself non-rotatably connected to a chain sprocket 20. Thus, rotation of the second spur gear 36 ultimately sets the chain sprocket 20 in motion. The chain 20, which is engaged with the chain sprocket 20, is subsequently also set in motion and can thereby move an attached window or door sash.

[0047] The first spur gear 34 and the second spur gear 36 form the second and last spur gear stages in the gear unit 16, respectively. The two spur gears are essentially the same size, and the gear ratio / reduction of this last spur gear stage is rather low compared to the other gear stages in the drive 10. Therefore, the spur gear 34 in the gear unit 16 serves to bridge the distance. This allows sufficient installation space for the chain 22.

[0048] Fig. 2 Figure 1 shows a perspective view of the first embodiment of the drive 10 according to the invention with housing cover 125. The housing cover 125 essentially covers the gear unit 16 and thus protects it from external influences such as dust or moisture. Furthermore, in Fig. 2 The chain exit of housing 12 is shown with reference numeral 220. The chain exit 220 is located on one longitudinal side of housing 12.

[0049] Fig. 3 Figure 1 shows a top view of the first embodiment of the drive 10 according to the invention. The depth direction or depth of the housing 12 is indicated by the double arrow marked with the reference sign T. Fig. 3 It can be clearly seen that the bow wheel 26 essentially occupies the entire depth of the housing 12. The axis of rotation 261 of the bow wheel is located on the longitudinal axis 121 of the housing 12, or rather, in the center of the depth of the housing 12. This results in the bow wheel 26 having the largest possible diameter. In other words, the bow wheel 26 extends from the first housing side 122 (on which the chain exit 220 is located) to the second housing side 124.

[0050] Fig. 3 It can further be seen that the axis 141 of the motor shaft does not coincide with the longitudinal axis 121 of the housing 12. Rather, the two axes are arranged at a non-zero angle to each other. In this case, the angle α between the two axes is 4.5°. In other words, in the first embodiment, the motor 14 is arranged at an angle to the housing 12 (or to its longitudinal axis 121). Due to the angled arrangement of the motor 14, the drive 10 can be shortened in the longitudinal direction L without having to use a smaller motor 14.

[0051] Fig. 4 Figure 1 shows a side view of the first embodiment of the drive 10 according to the invention. The side view clearly shows that the first spur gear stage 33 and the second spur gear stage 33 lie in a plane 123. More precisely, the pinion 32 (which is rotationally fixed to the curved gear 26), the first spur gear 34, and the second spur gear 36 are located in the plane 123 or rotate in this plane 123.

[0052] Fig. 5 Figure 1 shows a perspective view of the motor 14, the torus wheel 24 and the curved wheel 26 of the first embodiment of the drive 10 according to the invention, including an enlarged section of the rolling surface 262 of the curved wheel 26. In particular, it can be seen Fig. 5 The spiral toothing of the torus wheel 24 is shown, which has a spirally arranged tooth 243, the tooth 243 having several turns. The cylindrical rolling surface 262 of the arc wheel 26 also has several teeth. The rolling surface 262 is formed by the outer surface of the arc wheel 26 and has several arc-shaped teeth, the teeth being concave on a first flank and convex on a second flank. In the enlarged section of the arc wheel's toothing, one of the teeth is provided with the reference numeral 263, the first flank of the tooth 263 being provided with the reference numeral 263a and the second flank of the tooth with the reference numeral 263b. The first flank 263a is convexly curved, the second flank 263b is concavely curved. At least the convex curvature creates an improved engagement with the toothing of the torus wheel 24.

[0053] Fig. 6 Figure 1 shows a side view of a section of the rolling surface 262 of a curved wheel 26 of a second embodiment of the drive 10 according to the invention. In this embodiment, the rolling surface 262 has several teeth. By way of example, one of the teeth is provided with the reference numeral 263, wherein the tooth 263 has a first flank 263a with a convex curvature and a second flank 263b with a similarly convex curvature. The other teeth of the curved wheel 26 are designed in an analogous manner. Thus, the teeth of the rolling surface 262 shown are curved on both sides. Such a design has the advantage that forces can be absorbed in both directions of rotation of the curved wheel 262 by a torus wheel 24 engaged with it.

[0054] Fig. 7 Figure 1 shows a top view of a section of a third embodiment of the drive 10 according to the invention, in which a curved wheel 26 is shown in engagement with a torus wheel 24. Only a section of the torus wheel 24 is visible. In particular, the concave rolling surface 242, illustrated by the dashed arc 245, is visible. Furthermore, in this embodiment, several teeth (263, 265, 267 and 269) of the curved wheel 26 are in engagement with a tooth of the torus wheel 243, which has five turns. The concave curvature of the rolling surface 242 ensures a particularly effective power transmission between the torus wheel 24 and the curved wheel 26.

[0055] Fig. 8 shows a sectional view of a section of a fourth embodiment of the drive 10 according to the invention. Fig. 8 In particular, the motor 14 with the motor shaft 142, which is positively and force-fitted into the torus wheel 24. A reliable fit of the torus wheel 24 is ensured by the extension 248. The extension 248 forms a kind of hollow cylinder that surrounds the motor shaft 142. In this configuration, the extension 248 is supported in the housing 12 by a bearing 128. The bearing 128 is designed as a deep groove ball bearing.

[0056] Fig. 9 Figure 1 shows a perspective view of a fifth embodiment of the drive 10 according to the invention. In this embodiment, the drive 10 is designed with a four-stage gear unit 16, wherein the input stage consists of a spiral gear comprising a torus wheel 24 and a curved wheel 26, and the further stages 33, 35 and 37 are designed as spur gear stages.

[0057] The arc wheel 26 is non-rotatably connected to a pinion 32, which in the present embodiment engages with a third spur gear 38. A further pinion 39 is non-rotatably connected to the third spur gear 38 and meshes with a first spur gear 34. The first spur gear 34, in turn, meshes with the second spur gear 36, which is non-rotatably connected to a chain sprocket 20 for driving a chain (not shown). The point in the housing 12 for the chain exit is designated with the reference numeral 220.

[0058] In the present embodiment, the curved wheel 26 is comparatively small compared to the first embodiment of the drive 10, particularly with regard to its diameter. The axis of rotation 261 of the curved wheel 26 is shifted, compared to the first embodiment, towards the longitudinal side of the housing 12 on which the chain exit 220 is located. The axis of rotation 381 of the third spur gear 38 faces the opposite longitudinal side of the housing. In other words, the spur gear 38, which meshes with the pinion 32, essentially abuts the second housing side 124, and the curved wheel 26 essentially abuts the first housing side 122, with the first housing side 122 and the second housing side 124 being opposite each other in the depth direction T of the housing 12.

[0059] This order is based on Fig. 10 , which shows a top view of the fifth embodiment of the drive 10 according to the invention, even more clearly. Fig. 10 It can also be seen that in the fifth embodiment of the drive, the axis 141 of the motor shaft runs parallel to the longitudinal axis L of the housing 12. Therefore, in this embodiment, the motor 14 connects to the housing 12 without any bending.

[0060] Fig. 11 shows a side view of the fifth embodiment of the drive 10 according to the invention. Fig. 11 It is clearly evident that the three spur gear stages 33, 35 and 37 lie in a plane 123. In other words, the first spur gear 34, the second spur gear 36 and the pinion 39 lie in the plane 123 and thus provide sufficient space for the curved gear 26.

[0061] Fig. 12 Figure 1 shows a top view of a sixth embodiment of the drive 10 according to the invention. The sixth embodiment differs from the fifth embodiment in the arrangement of the motor 14 on the housing 12 and the arrangement of the spiral gear (i.e., the torus gear 24, the arc gear 26, and the pinion 32) or the third spur gear 38 in the housing 12. While in the fifth embodiment the axis 141 of the motor or the motor shaft is arranged closer to the first housing side 122 than to the second housing side 124, in the sixth embodiment it is the other way around. Accordingly, the side arrangements of the torus gear 24, arc gear 26, pinion 32, and third spur gear 38 are reversed. Bezugszeichenliste

[0062] 10 Drive 12 Housing 121 Longitudinal axis of the housing 122 First housing side 123 Plane 124 Second housing side 128 Bearing 14 Motor 141 Axis of the motor shaft 142 Motor shaft 16 Gear unit 18 Output shaft 20 Sprocket 22 Chain 220 Chain exit 24 Torus wheel 242 Rolling surface of the torus wheel 243 Tooth of the torus wheel 245 Arc 248 Extension 26 Arc wheel 262 Rolling surface of the arc wheel 261 Axis of rotation of the arc wheel 263, 265, 265, 269 Teeth of the arc wheel 263a First flank (of tooth 263) 263b Second flank (of tooth 263) 30 Pinion 32 Pinion 33 First spur gear stage 34 First spur gear 35 Second spur gear stage 36 Second spur gear 37 Third spur gear stage 38 Third spur gear 381 Axis of rotation of the third spur gear 39 Pinion L Longitudinal axis of the housing T Depth of the housing α Angle between longitudinal axis 121 of the housing and axis 141 of the motor shaft

Claims

1. Drive (10), in particular for a sash of a window or door, comprising a housing (12), a motor (14), and a gear unit (16) housed in the housing (12) for driving an output shaft (18), wherein the output shaft (18) is configured to be connected to a power transmission element for the sash for opening and / or closing the sash, characterized by the fact that the gear unit (16) comprises a torus wheel (24) driven by the motor shaft (142) and a curved wheel (26) engaged with the torus wheel (24), wherein the torus wheel (24) has a rolling surface (242) with a toothing having at least one spirally arranged tooth and the curved wheel (26) has a cylindrical rolling surface (262) with several teeth.

2. Drive (10) according to claim 1, wherein the gear unit (16) further comprises at least a first spur gear stage (33) and a second spur gear stage (35), in particular wherein the first spur gear stage (33) and the second spur gear stage (35) are arranged in one plane.

3. Drive (10) according to claim 2, wherein the curved wheel (26) is non-rotatably connected to a pinion (32) of the first spur gear stage (33).

4. Drive (10) according to claim 3, wherein the bow wheel (26) terminates substantially with a first housing side (122) and a meshing spur gear of the first spur gear stage (33) terminates substantially with a second housing side (124), wherein the first housing side (122) and the second housing side (124) are opposite each other in a direction perpendicular to the longitudinal direction of the housing (12) and perpendicular to the axis of rotation (261) of the bow wheel (26).

5. Drive (10) according to one of claims 1 to 3, wherein the curved wheel (26) substantially fills the housing (12) in a direction perpendicular to the longitudinal direction of the housing (12) and perpendicular to its axis of rotation (261).

6. Drive (10) according to one of the preceding claims, wherein the torus wheel is arranged closer to the motor (14) in the longitudinal direction of the housing (12) than the curved wheel (26).

7. Drive (10) according to one of the preceding claims, wherein the rolling surface (242) of the torus wheel (24) is at least partially concave and / or wherein the toothing of the torus wheel (24) engages with two or more teeth of the arc wheel (26).

8. Drive (10) according to one of the preceding claims, wherein the teeth of the arc wheel (26) are curved in an arc shape at least on one side.

9. Drive (10) according to one of the preceding claims, wherein the torus wheel (24) has a projection (248) which is supported in the housing (12) via a bearing (128), and / or wherein the motor shaft (142) is connected to the torus wheel (24) by friction and / or positive locking.

10. Drive (10) according to one of the preceding claims, wherein the axis (141) of the motor shaft (142) is arranged at an angle to the longitudinal axis of the housing (12), wherein the angle between the axis of the motor shaft and the longitudinal axis of the housing is at least 2°, in particular at least 4°.

11. Window or door with a pivotally mounted sash and a drive (10) according to claim 1 for opening and / or closing the sash.

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