Drive for a door or window with improved operating wheel

Abstract

The invention relates to a drive for operating a movable leaf, in particular a door or a window, comprising a housing with a longitudinal axis, wherein the housing has a first housing side running along the longitudinal axis and a second housing side running along the longitudinal axis, wherein the first housing side is designed to be arranged facing the leaf and the second housing side is designed to be arranged facing away from the leaf, a motor, a gear unit comprising a helical gear stage with a worm and a helical gear, wherein the worm and the helical gear are meshingly engaged, a first spur gear stage with a first spur gear and a second spur gear stage with a second spur gear, for driving an output shaft, and an energy storage device, wherein the motor and the energy storage device are arranged in the housing in such a way thatthat they are located along the longitudinal axis of the housing on opposite sides of the output shaft. A first straight line, which intersects the longitudinal axis of the output shaft and runs parallel to the longitudinal axis of the housing, is arranged between the longitudinal axis of the worm gear and a second straight line, which intersects the longitudinal axis of the helical gear and runs parallel to the longitudinal axis of the housing.

Description

[0001] The invention relates to a drive for operating a movable leaf, in particular a door or a window according to the preamble of claim 1.

[0002] (Automatic) door drives usually transmit the motor movement to the drive's output shaft via a worm or helical gear and several spur gear stages. When the door is opened, an energy storage device is energized. This storage device is often arranged parallel to the motor or gear in the depth of the drive, i.e., when viewed from above, it is arranged in front of or behind the motor. This limits the installation space for the gear, which has an impact on the design of the drive. Due to the limited installation space, worm or helical gear stages usually have a few gears and small helical gears in order to allow for a more compact design. However, this generally results in very low drive efficiency.

[0003] Often, drives also have a very long installation space, i.e. they are very wide when viewed from above when mounted on the door.

[0004] Due to the space required by the energy storage device, the structural connection of the motor gearbox is often complex and other components such as the bearings have less space available, which means that the drive system as a whole becomes less powerful or requires more space.

[0005] Furthermore, the output shaft and energy storage unit are usually offset from each other, which causes bending moments to act on the cage or housing and the drive's tie rod. Accordingly, a particularly complex and costly drive design is often required to absorb these forces.

[0006] Furthermore, the worm gear stage often has a high gear ratio (ratio greater than 8), which results in very high forces acting on the helical gear that connects to the worm gear. Accordingly, expensive materials often have to be used for these components.

[0007] The first two gear stages, i.e. the worm stage and the spur gear stage, together also usually have a high gear ratio (gear ratio greater than 35), or the second spur gear stage often has a gear ratio greater than 5. Therefore, the forces acting on the spur gear are also very high, so that expensive materials often have to be used for the spur gear as well.

[0008] If the door is opened by the drive, in automatic drives the energy storage device closes the door again after the opening process. The (de-energized) motor is moved via the gear box. Motors have a cogging torque, i.e. a torsional resistance, which is ultimately caused by the permanent magnets in the motor. In other words, the cogging torque, also known as the holding torque, is the torque required to hold the motor in a certain position when it is not actively working. The higher the cogging torque, the more resistance occurs when the door is closed (against the energy storage device) and the lower the efficiency of the mechanical system. Therefore, there is a need for better designed drives to reduce the resistance against the energy storage device and increase the efficiency of the drive.

[0009] EP 3 309 339 B1 discloses a drive device in the form of a rotary drive for a leaf of a door or window, comprising a housing, an output shaft for actuating a lever mechanism arranged between the frame and leaf, and a mechanical energy storage device by means of which the output shaft can be driven. In the drive shown in the figures, the electric motor and the energy storage device are arranged on opposite sides of the gear mechanism.

[0010] Due to its design, the drive known from EP 3 309 339 B1 has an efficiency that can be increased.

[0011] The invention is based on the object of creating a drive for a door or window that offers improved efficiency. The drive should be designed in such a way that, despite its high efficiency, it is particularly compact and inexpensive.

[0012] The problem is solved by the features of claim 1.

[0013] Preferred embodiments of the drive according to the invention emerge from the subclaims, the present description and the drawings.

[0014] The drive according to the invention comprises a housing with a longitudinal axis, wherein the housing has a first housing side running along the longitudinal axis and a second housing side running along the longitudinal axis, wherein the first housing side is designed to be arranged facing the blade and the second housing side is designed to be arranged facing away from the blade, a motor, a gear unit having a helical gear stage with a worm and a helical gear, wherein the worm and the helical gear are in meshing engagement, a first spur gear stage with a first spur gear and a second spur gear stage with a second spur gear, for driving an output shaft, and an energy storage device. The motor and the energy storage device are arranged in the housing such that they are located on opposite sides of the output shaft along the longitudinal axis of the housing.A first straight line, which intersects the longitudinal axis of the output shaft and runs parallel to the longitudinal axis of the housing, is arranged between the longitudinal axis of the worm and a second straight line, which intersects the longitudinal axis of the helical gear and runs parallel to the longitudinal axis of the housing.

[0015] The solution according to the invention solves all of the above-mentioned problems with a powerful, cost-effective and compact drive.

[0016] The drive has a particularly simple, separate design, in which the energy storage device is located on one side of the output shaft and the motor and large parts of the gear unit are located opposite the output shaft. This means that the gearbox (or gear unit) and the energy storage device can be designed particularly simply and separately from one another. The installation space for the helical gear in the depth of the drive (i.e. between the first housing side and the second housing side) can therefore be optimally utilised. In this respect, a relatively large helical gear can be selected. In particular, the arrangement of the motor orThe worm gear and a gear structure such that a first straight line, which intersects the longitudinal axis of the output shaft and runs parallel to the longitudinal axis of the housing, is arranged between the longitudinal axis of the worm gear and a second straight line, which intersects the longitudinal axis of the helical gear and runs parallel to the longitudinal axis of the housing, enables a drive whose components do not have to be nested or intermesh due to space constraints. The helical gear can be selected to be as large as possible and arranged in the housing such that it is largely flush with the first or second housing side.

[0017] In this respect, the arrangement of the individual components of the drive within the housing (and relative to each other) is crucial in the present invention. The chosen arrangement ensures, in particular, that the components of the gear unit (i.e., worm gear, helical gear, and spur gears) can be designed as large as possible without resorting to complex mechanics.

[0018] Usually, in particular in the drive known from EP 3 309 339 B1, the longitudinal axis of the screw is arranged between the first straight line and the second straight line.

[0019] The drive according to the invention is designed to be mounted on the door frame as standard. The drive's output shaft is designed to accommodate a rod that connects the drive to the door leaf. The door can thus be opened or closed by rotating the output shaft. The energy storage unit is designed to be charged when the door is opened and to ensure safe closing in the event of a power failure.

[0020] The motor is ideally located on the side of the drive housing facing away from the frame / door leaf to improve accessibility for maintenance and installation. However, other mounting options are also conceivable.

[0021] In a preferred embodiment, the motor is arranged in the housing such that it is substantially flush with the first housing side or the second housing side, and the worm is arranged in the housing such that the longitudinal axis of the worm is arranged between the housing side flush with the motor and the first straight line.

[0022] In other words, the motor is arranged in the housing such that it is as close as possible to the first or second side of the housing or is adjacent to one of these sides. Since the axis of the motor or its output shaft coincides with the longitudinal axis of the adjoining worm (or straight lines along the axes are congruent), this arrangement ensures that the worm is also arranged as close as possible to the same side of the housing as the motor. A worm that is close to the housing side, i.e. a worm on the edge, in turn offers the greatest possible space in the depth of the drive for the helical gear that meshes with the worm. In this respect, the installation space of the helical gear can be optimally used in terms of depth and the helical gear can be made as large as possible.

[0023] Minor gaps between the motor and the housing side are also considered to be "contact with" or "terminating with" the housing side.

[0024] Preferably, the first spur gear and / or the second spur gear essentially end with the same housing side as the motor.

[0025] Slight gaps between the spur gears and the housing side are also considered to be "contacting" or "sealing" the housing side. This arrangement allows the drive to be designed particularly compactly and short (along its longitudinal axis). This allows the individual gears or individual gear stages to have as much space as possible in depth, eliminating the need to relocate the gears, which would require a larger installation space lengthwise.

[0026] Advantageously, the helical gear essentially ends with the housing side opposite the housing side with which the motor ends.

[0027] In other words, the diameter of the helical gear is selected so that the helical gear is positioned as close as possible to the housing side. This ensures that the helical gear's installation space is optimally utilized in depth. In other words, the helical gear can be designed to its maximum size, as the installation space between the worm gear and the housing side opposite the motor is fully utilized in depth. Slight gaps between the helical gear and the housing side are also considered to be "adjacent to" or "seal with" the housing side.

[0028] According to a preferred embodiment, the worm has at least four threads. Additionally or alternatively, the worm has a toothing with a pitch angle of at least 25°, preferably at least 30°.

[0029] Typically, the number of threads in worm gears in door drives is 2, with a maximum of 3. A higher thread number offers a wider range of gear ratios. In particular, the higher the number of threads, the lower the gear ratio—that is, the ratio of the number of teeth on the helical gear to the number of threads on the worm gear—can be. The fine-tuning of the gear ratio can also be improved if the worm gear has more threads. Furthermore, using multiple threads allows for better distribution of the load across the individual tooth flanks, which can reduce wear.

[0030] A pitch angle of 25° or more on the worm gearing, or such a pitch angle of the tooth flanks, is significantly greater than that of worm gears in conventional drives. Indeed, the pitch angle of worm gears in conventional drives for doors and the like is 10° to 20°. The larger the pitch angle, the lower the risk of tooth breakage. This applies to both the worm gear and the helical gear meshing with the worm gear, whose gearing preferably has the same or at least a similar pitch angle.

[0031] Due to the larger pitch angle, the efficiency of a driven worm can be significantly increased from the usual 60% to 70% with a usual gear ratio of 5 to 15, to approx. 80%.

[0032] In an advantageous embodiment, the transmission ratio of the helical gear stage is at most 7.5, preferably at most 7.

[0033] Such a low gear ratio of the helical gear stage allows forces between the worm and the worm wheel to be reduced. This results in less wear. Furthermore, reducing the acting forces allows a wider range of possible materials to be used to manufacture the helical gear stage components.

[0034] Advantageously, the helical gear has a diameter of at least 55 mm, preferably at least 60 mm.

[0035] This makes the helical gear significantly larger than existing, comparable drives. Since a larger diameter also entails a larger circumference, the gear teeth can be adjusted accordingly. In particular, the gear module, i.e., the ratio of diameter to number of teeth on the helical gear, can be increased by increasing the diameter, thus preventing wear. The risk of tooth breakage can also be reduced.

[0036] In a further advantageous embodiment, the transmission ratio of the first spur gear stage is at most 5 and / or the transmission ratio of the second spur gear stage is at least 4.5.

[0037] The gear ratio of the first spur gear stage is preferably at most 4.6. If the gear ratio of the helical gear stage is at most 7 and the gear ratio of the first spur gear stage is at most 5, the gear ratio of both stages together is at most 35. Advantageously, the gear ratio of the two stages together is at most 33. The gear ratio of the second spur gear stage is preferably at least 5. Overall, this allows for a sufficient overall gear ratio of the transmission and a sufficiently high output torque of the drive.

[0038] In general, a smaller gear ratio offers several advantages over a larger gear ratio. A smaller gear ratio enables higher torque and power transmission. Overall, efficiency is higher; therefore, less energy is lost in the transmission. Since a smaller gear ratio generally also results in lower speeds at the individual gear wheels (helical gear, spur gears), lower loads and less wear can be expected, which can increase the service life of the transmission unit.

[0039] In an expedient embodiment, the helical gear is made of a, preferably unreinforced, plastic, in particular polyamide, PA, or polyoxymethylene, POM, and / or the first spur gear and / or the second spur gear is made of one of unalloyed steel, low-alloy steel, or sintered metal.

[0040] As mentioned above, the forces acting there are relatively low, especially when the gear ratios of helical and spur gear stages are relatively small. Accordingly, inexpensive, preferably unreinforced, plastics can be used for the helical gear, while cheaper metals can be used for the spur gear. For example, the spur gear can advantageously be manufactured from inexpensive steel or from a cost-effective sintered metal using a sintering process. This can save costs. This is especially true when the aforementioned components can be manufactured using injection molding. Using unreinforced plastics can also increase the service life of the injection molding tool.

[0041] In another embodiment, a third straight line can be arranged so that it can be arranged between the longitudinal axis of the worm and the first straight line, intersecting the longitudinal axis of the first spur gear and running parallel to the longitudinal axis of the housing.

[0042] According to a preferred embodiment, the energy store is designed as a spring, wherein the spring is accommodated in a spring receptacle and is designed to be subjected to a compressive force and / or tensile force via a rocker and the spring receptacle, wherein the rocker and the spring receptacle are arranged in the housing such that, when viewed along the longitudinal axis of the housing, the output shaft is located between the motor on one side and the rocker and the spring receptacle on another side, and / or wherein the spring is arranged in the housing such that its longitudinal axis runs parallel to the longitudinal axis of the housing.

[0043] By designing the energy storage device as a spring (storage device), a structurally simple and at the same time reliable energy storage device is created.

[0044] In addition to the aforementioned components, the drive advantageously also includes control electronics for controlling, in particular for automatically opening and / or closing, the sash. The control electronics can be designed as a standalone module. It can be permanently mounted on the drive, in particular in the housing.

[0045] The invention is explained in more detail below using exemplary embodiments with reference to the drawings. Elements with the same function and mode of operation are provided with the same reference numerals in the figures. They show: Fig. 1 schematically shows a first embodiment of the drive according to the invention in a plan view; Fig. 2 schematically shows a second embodiment of the drive according to the invention in a plan view; Fig. 3 schematically shows the first embodiment of the drive according to the invention in a bottom view; Fig. 4 an excerpt from Fig. 1 including a side view of an enlarged section of the drive 10; Fig. 5 schematically shows a third embodiment of the drive according to the invention in a perspective view as well as an enlarged section of the drive; and Fig. 6 schematically the first embodiment of the drive according to the invention in a further bottom view.

[0046] Fig. 1 shows a schematic plan view of a first embodiment of the drive according to the invention. The drive is designated in its entirety by reference numeral 10.

[0047] In order to protect the motor 14, the gear unit 16 and the energy storage device 20 from external influences, the drive 10 has a housing 12 which encloses the aforementioned components. The housing side, which would block the view of the aforementioned components in plan view, is Fig. 1 omitted. More precisely, however, are a first housing side 121 and a second housing side 122. The depth of the drive 10 is defined by the distance between the two housing sides 121 and 122 and is in Fig. 1 represented by a double arrow.

[0048] The two housing sides 121 and 122 are longer than the other sides of the housing 12. Therefore, the longitudinal axis of the housing 12 runs along the housing sides 121 and 122, although this axis is not shown. The width of the housing is also not shown, but runs parallel to the longitudinal axis.

[0049] The first housing side 121 is configured to be arranged facing the leaf (e.g., a door). In particular, the first housing side 121 can be configured to be attached to a door leaf, a window leaf, or the like, or to a door frame, a window frame, or the like. For this purpose, the first housing side 121 preferably has fastening means or fastening aids, for example, through holes for receiving screws.

[0050] The second housing side 122 is designed to be positioned facing away from the door. Therefore, the second housing side 122 is generally visible when the drive is installed, while the first housing side 121 is concealed by the drive 10.

[0051] Housing sides 121 and 122 face each other, with the motor 14, gear unit 16, and energy storage device 20 arranged between the two housing sides 121 and 122. The gear unit 16 has a worm gear 162, a helical gear 164, a first spur gear 166, and a second spur gear. The worm gear 162 and the helical gear 164 form the helical gear stage. The first spur gear 166 is part of the first spur gear stage, and the second spur gear 168 is part of the second spur gear stage. The gear unit 16 is configured to drive the output shaft 18.

[0052] The gear unit 16 is located (as viewed along the longitudinal axis of the drive 10) between the motor 14 and the energy storage device 20. In this embodiment, the motor 14 is arranged in the housing 12 such that it is flush with the first housing side 121. In other words, the motor 14 rests against the housing side 121. However, there is a greater distance to the second housing side 122. Due to the position of the motor 14, the worm 162 is also arranged closer to the first housing side 121 than to the second housing side 122. In fact, the worm 162 is arranged in the housing such that, for the given size of the motor 14, it occupies a minimal distance from the housing side 121. Accordingly, the helical gear 164, with which the worm engages, is provided with the greatest possible space, since the space up to the second housing side 122 is maximized.The helical gear 164 is therefore relatively large compared to other helical gears of comparable drives (particularly in terms of diameter). Furthermore, the arrangement shown allows for relatively large spur gears 166 and 168. Thus, in the illustrated embodiment, the space toward the first housing side 121 is maximized by both the first spur gear 166 and the second spur gear 168, since both spur gears 166 and 168 extend to the first housing side 121 or rest against it (with their peripheral edge).

[0053] Overall, the aforementioned components in the drive 10 according to the first embodiment shown are arranged such that a first straight line 1 is arranged between the longitudinal axis 3 of the worm 162 and a second straight line 2. The first straight line 1 is defined by the fact that it intersects the longitudinal axis of the output shaft 18 on the one hand and runs parallel to the longitudinal axis of the housing 12 on the other. In this respect, the first straight line 1 runs parallel to the longitudinal axis 3 of the worm 162. However, the straight line 1 is arranged closer to the second housing side 122 than the longitudinal axis 3 of the worm 162. The second straight line 2 is defined by the fact that it intersects the longitudinal axis of the helical gear 164 and runs parallel to the longitudinal axis of the housing 12. In this respect, the second straight line 2 runs parallel to the first straight line 1 and parallel to the longitudinal axis 3 of the worm. However, the second straight line 2 is arranged even closer to the second housing side 122 than the first straight line 1.

[0054] The first embodiment is further characterized in that a third straight line 4, which intersects the longitudinal axis of the first spur gear 166 and runs parallel to the longitudinal axis of the housing 12, is arranged between the longitudinal axis 3 of the worm 162 and the first straight line 1. The third straight line 4 also runs parallel to the first straight line 1, the second straight line 2, and the longitudinal axis 3 of the worm 162.

[0055] This arrangement ensures that the individual components, in particular the helical gear 164 and the spur gears 166 and 168, have as much installation space as possible. By utilizing the installation space, particularly in depth, the gearing module, in particular the helical gearing module, can be increased compared to existing drives. Overall, the drive 10 according to the first embodiment creates a drive that is less susceptible to wear, has increased efficiency, and is compact.

[0056] Fig. 2 shows schematically a second embodiment of the drive 10 according to the invention in a plan view.

[0057] The components used in the drive 10 according to the second embodiment are the same as in the first embodiment. In contrast to the first embodiment, the motor 14 in the second embodiment is not arranged adjacent to the first housing side 121, but rather adjacent to the second housing side 122. Consequently, the worm 162 is not located closer to the first housing side 121 than to the second housing side 122, but vice versa. In fact, the distance between the longitudinal axis 3 of the worm 162 and the second housing side 122 is minimal for the given size of the motor 14. This provides the helical gear 164 with the largest possible installation space towards the first housing side 121. As shown in Fig. 2 As shown, the installation space created by the helical gear 164 is also fully utilized. In fact, the helical gear 164 extends to the first housing side 121. The helical gear 164, or its peripheral edge, rests particularly against the first housing side 121.

[0058] Overall, the above-mentioned components in the drive 10 according to the second embodiment shown are arranged such that, as in the first embodiment, the first straight line 1 is arranged between the longitudinal axis 3 of the worm 162 and the second straight line, wherein the first straight line 1 intersects the longitudinal axis of the output shaft 18 and runs parallel to the longitudinal axis of the housing 12, and wherein the second straight line 2 intersects the longitudinal axis of the helical gear 164 and runs parallel to the longitudinal axis of the housing 12. In contrast to the first embodiment, in the second embodiment the longitudinal axis 3 of the worm 162 is arranged closer to the second housing side than the second straight line 2. Furthermore, a third straight line 4,which intersects the longitudinal axis of the first spur gear 166 and runs parallel to the longitudinal axis of the housing 12, between the longitudinal axis 3 of the worm 162 and the first straight line 1. The third straight line 4 runs parallel to the first straight line 1, the second straight line 2, and the longitudinal axis 3 of the worm 162.

[0059] Fig. 3 shows schematically the first embodiment of the drive 10 according to the invention in a bottom view. In contrast to Fig. 1 Further parts of the housing 12 are shown. These housing parts can accommodate, in particular, control electronics for the drive 10.

[0060] Fig. 4 shows an excerpt from Fig. 1 including a side view of an enlarged section of the drive 10. In the section and in the side view of the enlarged section, the worm 162 and the helical gear 164 of the drive 10 according to the first embodiment are shown in particular. The enlarged section shown is a view from the first housing side 121. In the enlarged section, it is clearly visible that the worm 162 in the first embodiment of the drive 10 has four gears 1621, 1622, 1623 and 1624. These mesh with the helical gear 164 located behind it in this view. The pitch angle α (of the side flanks) of the gears or the pitch angle α of the gearing is 30° in the present case. An even larger pitch angle is also conceivable.In general, a larger pitch angle can contribute to the worm generating a greater axial displacement per revolution, thus rotating the helical gear further, than with a smaller pitch angle. To ensure smooth and efficient operation of the gear unit 16, the angle of the teeth of the helical gear 164 is preferably the same as the angle of the teeth of the worm 162.

[0061] Fig. 5 shows schematically a third embodiment of the drive 10 according to the invention in a perspective view as well as an enlarged section of the drive 10.

[0062] The housing 12 is in Fig. 5 Not shown. The enlarged section shows a side view of the helical gear 164 and the worm 162. Also shown is the longitudinal axis 1642 of the helical gear 164, i.e., the axis around which the helical gear 164 rotates, as well as the pitch angle β of the toothing of the helical gear 164. The pitch angle β is 30° in the third embodiment shown. The angle of the toothing of the worm 162 is preferably the same size.

[0063] Fig. 6 shows schematically the first embodiment of the drive 10 according to the invention in a bottom view. In contrast to Fig. 3 no further parts of the housing 12 are shown. The gear unit 16 as well as the energy storage 20 and other components of the drive 10 are shown in comparison to Fig. 3 shown in more detail.

[0064] In Fig. 6 It is clearly visible that in the first embodiment of the drive 10, the energy storage device 20 is designed as a spring 200. The spring 200 is accommodated in a spring receptacle 202, which in turn is operatively connected to a rocker arm 204. In particular, a tensile and / or compressive force can be exerted on the spring via the rocker arm 204 and the spring receptacle 202. While tensioning the spring when the drive is operatively connected to a leaf (e.g., a door) is accompanied by the opening of the leaf, relaxing the spring is accompanied by the closing of the door. When the second spur gear 168 rotates, the cam disk 170, which is firmly connected to the second spur gear 168, also rotates. Rotation of the cam disk 170, in turn, causes a displacement of the rocker arm 204 or a rotation of the rocker arm 204 about its axis of rotation 2042.The operative connection between the rocker 204 and the spring holder 202 results in a displacement of the spring holder 202 along the longitudinal axis of the drive 10. Depending on the direction of displacement of the spring holder 202, the spring 200 is tensioned or can be relaxed.

[0065] The spring retainer 202 and the rocker 204 are arranged in the housing 12 such that they are on the same side of the output shaft 18 as the spring 200. In other words, when viewed along the longitudinal axis of the housing 12, the spring retainer 202 and the rocker 204 are located on a different side of the output shaft 18 than the motor 14. Furthermore, in the first embodiment of the drive 10, the spring 200 is arranged in the housing 12 such that the longitudinal axis of the spring 200 runs parallel to the longitudinal axis of the housing 12. Thus, the spring 200 can be optimally tensioned or relaxed via the spring retainer 202 and the rocker 204. Bezugszeichenliste

[0066] 1First straight line 2Second straight line 3Longitudinal axis (of the worm) 4Third straight line 10Drive 12Housing 121First housing side 122Second housing side 14Motor 16Gear unit 162Worm 1621Gear 1622Gear 1623Gear 1624Gear 164Screw gear 1642Longitudinal axis (of the worm gear) 166First spur gear 168Second spur gear 170Cam disc 18Output shaft 20Energy storage device 200Spring 202Spring holder 204Swing arm 2042Rotation axis

Claims

1. A drive (10) for actuating a movable leaf, in particular a door or a window, comprising a housing (12) with a longitudinal axis, wherein the housing has a first housing side (121) running along the longitudinal axis and a second housing side (122) running along the longitudinal axis, wherein the first housing side (121) is configured to be arranged facing the leaf and the second housing side (122) is configured to be arranged facing away from the leaf, a motor (14), a gear unit (16) comprising a helical gear stage with a worm (162) and a helical gear (164), wherein the worm and the helical gear are meshingly engaged, a first spur gear stage with a first spur gear (166) and a second spur gear stage with a second spur gear (168) for driving an output shaft (18), and an energy storage device (20), wherein the motor (14) and the energy storage device (20) are arranged in the housing in such a way thatthat they are located along the longitudinal axis of the housing (12) on opposite sides of the output shaft (18), , characterized in that a first straight line (1), which intersects the longitudinal axis of the output shaft (18) and runs parallel to the longitudinal axis of the housing (12), is arranged between the longitudinal axis (3) of the worm (162) and a second straight line (2), which intersects the longitudinal axis of the helical gear (164) and runs parallel to the longitudinal axis of the housing (12).

2. Drive (10) according to claim 1, wherein the motor (14) is substantially flush with the first housing side (121) or the second housing side (122) and wherein the longitudinal axis (3) of the worm (162) is arranged between the housing side flush with the motor (14) and the first straight line (1).

3. Drive (10) according to claim 2, wherein the first spur gear (166) and / or the second spur gear (168) terminate substantially at the same housing side as the motor (14).

4. Drive (10) according to claim 2 or 3, wherein the helical gear (164) is substantially flush with the housing side opposite the housing side with which the motor (14) is flush.

5. Drive (10) according to one of claims 1 to 4, wherein the worm (162) has at least four threads (1621, 1622, 1623, 1624) and / or wherein the worm (162) has a toothing with a pitch angle of at least 25°, preferably at least 30°.

6. Drive (10) according to one of claims 1 to 5, wherein the transmission ratio of the helical gear stage is at most 7.5, preferably at most 7.

7. Drive (10) according to one of claims 1 to 6, wherein the helical gear (164) has a diameter (5) of at least 55mm, preferably at least 60mm.

8. Drive (10) according to one of claims 1 to 7, wherein the gear ratio of the first spur gear stage is at most 5 and / or wherein the gear ratio of the second spur gear stage is at least 4.

5.

9. Drive (10) according to one of claims 1 to 8, wherein the helical gear (164) is made of a, preferably unreinforced, plastic, in particular polyamide, PA, or polyoxymethylene, POM, and / or wherein the first spur gear (166) and / or the second spur gear (168) is made of one of unalloyed steel, low-alloy steel, or sintered metal.

10. Drive (10) according to one of claims 1 to 9, wherein a third straight line (4), which intersects the longitudinal axis of the first spur gear (166) and runs parallel to the longitudinal axis of the housing (12), is arranged between the longitudinal axis (3) of the worm (162) and the first straight line (1).

11. Drive (10) according to one of claims 1 to 10, wherein the energy storage device (20) is designed as a spring (200), wherein the spring (200) is received in a spring receptacle (202) and is configured to be subjected to a compressive force and / or tensile force via a rocker arm (204) and the spring receptacle (202), wherein the rocker arm (204) and the spring receptacle (202) are arranged in the housing (12) such that, when viewed along the longitudinal axis of the housing (12), the output shaft (18) is located between the motor (14) on one side and the rocker arm (204) and the spring receptacle (202) on another side, and / or wherein the spring (200) is arranged in the housing (12) such that its longitudinal axis runs parallel to the longitudinal axis of the housing (12).

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