WO2023143999A1

WO2023143999A1 - Drive for a door or window

Info

Publication number: WO2023143999A1
Application number: PCT/EP2023/051207
Authority: WO
Inventors: Benjamin Wörner
Original assignee: Geze Gmbh
Priority date: 2022-01-28
Filing date: 2023-01-19
Publication date: 2023-08-03
Also published as: DE102022200954B4; EP4314459A1; DE102022200954A1

Abstract

The application relates to a drive for a door or a window, comprising a housing, an output shaft mounted rotatably on the housing and comprising a cam disc, an electric motor comprising a transmission for driving the output shaft from a closed position in an opening direction in order to open the door or the window, a roller rolling over the rotating cam disc during operation, a pivot lever, which is hinged to the housing so as to be pivotable about a pivot axis, the roller being arranged rotatably on the pivot lever, and an energy storage unit for driving the output shaft from an open position in a closing direction in order to close the door or the window, the energy storage unit comprising an energy store having a longitudinal axis and movable first abutment facing the roller, and a second abutment, which faces away from the roller, on which abutments the energy store is supported, the roller acting in a force-transmitting manner between the cam disc and the movable first abutment of the energy storage unit, the cam disc and the energy storage unit being arranged on mutually opposed sides with respect to the pivot lever, and the movable first abutment of the energy storage unit being coupled rotatably and non-displaceably to the pivot lever at a coupling point and thus being guided on a circular path by the pivot lever.

Description

Drive for a door or a window

The invention relates to a drive for a door or a window and in particular to a motor-operated drive for a door or a window.

Such motor-operated drives, which can also be referred to as automatic drives, transmit at least part of the drive power of the drive motor, usually via a linkage, to a door or window sash in order to pivot it. A second part of the drive power can be transmitted to an energy store, which can be designed as a compression spring, via a cam disk mechanism. The cam disk mechanism comprises a cam disk located in a so-called cage. The cage is connected to a roller and the roller is arranged in such a way that the roller rolls on a peripheral surface of the cam disk. The cage is in turn connected to a tie rod and the tie rod is connected to the compression spring via a piston. When the door is opened using the drive, the cam disk is rotated. This moves the cage connected to the roller, the pull rod and the piston and consequently tensions the compression spring.

Due to the space required by the cage and the pull rod, the constructive connection of the motor-transmission unit is complex and other components, such as a bearing for the cage and the piston, have little installation space. Thus, there is the difficulty that either a more compact bearing has to be used, which leads to higher friction and thus to a less powerful drive, or the entire drive has to be built larger and requires more installation space. In addition, in the drive described above, the central axis of the output shaft is not aligned with the compression spring, so that bending moments act on the cage and the pull rod, which means that a particularly complex and cost-intensive construction is required to absorb the bending forces.

A further disadvantage of this design is that the design of the cage, its mounting and the connection of the pull rod to the cage and the piston are complex, which has a negative effect on the manufacturing costs of the drive.

In general, the numerous bearing points generate a lot of friction, which means that the efficiency of the drive needs to be improved. In addition, the high level of friction creates wear and, due to the higher drive torques required, means that larger and more expensive drive motors are required.

It is therefore an object of the present invention to provide a drive that is powerful, inexpensive and compact.

The object is achieved by a drive with the features of claim 1 and in particular in that the drive has a pivoted lever which is pivoted about a pivot axis on a housing, the roller being rotatably arranged on the pivoted lever that an energy storage unit is provided for driving the output shaft from an open position in a closing direction in order to close the door or the window, the energy storage unit having an energy storage device having a longitudinal axis and a movable first abutment facing the roller and a second abutment facing away from the roller, on which the energy store is supported, has that the roller acts in a force-transmitting manner between the cam disk and the movable first abutment of the energy store unit, that the cam disk and the energy storage unit are arranged on opposite sides of the pivoting lever, and that the movable first abutment of the energy storage unit is coupled to the pivoting lever at a coupling point in a rotatable and non-displaceable manner and is thereby guided by the pivoting lever on a circular path.

Coupled in a non-displaceable manner means that the first abutment cannot perform any linear movement relative to the pivoting lever.

A drive with these features has a simple structure with few friction losses, since only a few bearing points are required, since the first abutment can be guided and supported exclusively by the pivoting lever. In addition, the force of the energy store can be transmitted directly to the cam disk without the first abutment or the energy store coming into contact with the housing and causing friction losses. As a result, the drive can be operated with a high level of efficiency, which in turn means that the drive can be dimensioned to be compact and can be produced inexpensively

The cam disk can be coupled to the output shaft in a rotationally fixed manner or can be formed in one piece with the output shaft. The cam disk can also be referred to as a cam disk or heart cam disk. The cam disk can have a symmetrical or asymmetrical outer contour, depending on the desired drive torque curve. The output shaft can be rotated from a rest position in both directions of rotation to ensure different types of installation.

Advantageous developments of the invention can be found in the dependent claims, the description and the drawing. In general, a drive motor of the drive can be coupled to the output shaft via a gear. The gear can be designed as a spur gear, as a combination of worm gear and spur gear, as a combination of curved or spiral bevel gear and spur gear, or as a combination of hypoid gear or hypoid bevel gear and spur gear.

According to a particularly compact embodiment, the gear comprises a worm gear and a spur gear.

According to a further embodiment, the electric motor and the energy storage unit are arranged on opposite sides with respect to the output world. This enables a modular design of the drive in a particularly simple manner. For example, the drive can have a modular design, in that the pivoted lever and the energy storage unit are part of an energy storage module and are arranged in a first housing section and the output shaft and/or the electric motor are part of a drive module and in a separate and with the first housing connectable second housing section is arranged. Such a modular design has the advantage that the drive can also be used without an energy storage module. Furthermore, the transmission and the energy storage unit can be designed particularly simply and cost-effectively due to the opposing arrangement, without components having to be nested/engaged in one another for reasons of space. According to one embodiment, the roller and the movable first abutment are mounted on the pivoting lever such that they can rotate about the same axis. This has the advantage that the drive can be manufactured more cost-effectively and the power transmission of the drive power to the energy store and vice versa is optimized when closing. According to one embodiment, the pivoting lever has a fork-shaped extension, in the free space of which extends a pin on which the movable first abutment is rotatably mounted. As a result, the pivoting lever can be coupled to the movable first abutment in a simple manner and with little friction. The pin can be rotatably mounted on the forked extension, in particular by means of a ball bearing, cylindrical roller bearing, needle bearing or slide bearing.

According to one embodiment, the movable first abutment has a receptacle for the roller, formed in particular by a fork-shaped extension. The roller can be arranged rotatably in the receptacle, in particular on the aforementioned pin. The roller is preferably rotatably mounted by means of a needle bearing or plain bearing.

According to one embodiment, in the closed position, ie in a position of the drive in which the door or window is closed, the pivot axis of the pivot lever is further away from the output shaft or its central axis as seen in the direction of a longitudinal extension of the energy store arranged as the coupling point between the pivoted lever and the movable first abutment. The pivoting axis of the pivoting lever is preferably offset by about half the distance, viewed in the direction of the longitudinal extension of the energy storage device, which the first abutment covers when the door or window is fully opened in the direction of the longitudinal extension of the energy storage device. This ensures that the transverse offset of the coupling point between the pivoted lever and the movable first abutment is as small as possible when the pivoted lever is pivoted. Transverse offset here means a movement of the coupling point transverse to the direction of the longitudinal extension of the energy store. In particular, when the output shaft moves from the closed position to the open position and vice versa, a deflection of the coupling point between the pivoted lever and the movable first abutment perpendicular to the longitudinal axis of the energy store passes through a reversal point. In other words, the coupling point between the pivoted lever and the movable first abutment initially moves away from an imaginary line and then back towards the line during opening or closing, the imaginary line corresponding to the longitudinal axis of the energy store in the closed position.

According to one embodiment, the pivoting lever is curved. This enables a more compact design of the first abutment and of the drive, with a force absorption surface of the first abutment being able to dip into the curvature of the pivoting lever.

According to one embodiment, the energy store is designed as a spring, in particular a compression spring, in particular a spiral compression spring. Alternatively, the energy store can be designed, for example, as a set of disk springs or the like.

According to one embodiment, a diameter of the spring is greater than 60% of a housing diameter, preferably greater than 80% of the housing diameter, specifically the housing section surrounding the spring. The housing inner diameter or the housing outer diameter can be regarded as the housing diameter. As a result, a high level of buckling stability is achieved using as little installation space as possible.

It has been shown that a ratio of the unstressed length of the spring to the diameter of the spring of less than 3 is preferred for the present application. There are particular advantages if the ratio of the unstressed length of the spring to the diameter of the spring is less than or equal to 2. This further improves the buckling stability of the spring. According to one embodiment, a total number of coils of the spring is in the range from X.3 to X.7. The X stands for a natural number. In other words, the beginning of the coils of the spring is offset in the circumferential direction to the end of the coils of the spring. The beginning of the coils of the spring and the end of the coils of the spring are preferably at a maximum distance from one another, as seen in the circumferential direction. In this case, the total number of coils in the spring is X.5.

According to one embodiment, the ends of the spring are applied and/or ground. The ends can be offset 180° from one another, as is the case with a total number of spring coils of X.5

According to one embodiment, the spring is held by the two abutments only in its end regions. In other words, the spring is only held in its end areas and thus does not rest on any part in its middle area.

According to one embodiment, the movable first abutment is designed as a spring plate. The spring plate preferably has a front contact surface, i.e. a force absorption surface, for the spring and a holding section which extends into the spring and which can also be referred to as a fixing section.

In general, a force delivered by the energy store for closing the door can be adjustable. A closing force adjustment device is preferably provided, by means of which a prestressing force of the energy store can be adjusted. A distance between the movable first abutment and the second abutment is preferably set by means of the closing force adjustment device which the energy storage is supported, adjustable. The closing force adjustment device can preferably be operated manually, for example by means of a tool or without tools using an adjustment element. According to one embodiment, the closing force adjustment device comprises a spindle and a spring plate that can be moved along the spindle by rotating the spindle and forms the second abutment for the energy store. The spring plate is preferably mounted in the housing in a rotationally fixed but axially displaceable manner.

According to one embodiment, the spindle can be driven either directly or via a worm wheel which is rotated by a worm.

The spindle is preferably mounted in the housing such that it can pivot over a defined angular range, preferably by means of a ball joint. This prevents the spindle from jamming when it is rotated in the housing if, due to dimensional deviations occurring during the manufacture of the components, the spring plate and the spindle are arranged at a slight angle to the housing when assembled.

According to one embodiment, the cam disk is arranged at least partially in line with the energy store. In particular, the cam disk can be arranged at least partially in alignment with the energy store when the output shaft is in the closed position. The cam disk is preferably arranged with more than 60% of its surface in line with the energy store when the output shaft is in the closed position. As a result, the force can be transmitted directly from the energy store to the cam disk without generating unwanted moments. According to one embodiment, the central axis of the output shaft is arranged in alignment with the longitudinal axis of the energy store in the closed position. As an alternative to this, the central axis of the output shaft in the closed position can be offset from the longitudinal axis of the energy store by at most the diameter of the roller or the drive shaft. The longitudinal axis of the energy store can intersect the output shaft, preferably a central axis of the output shaft. A central axis, in particular an axis of symmetry, of the cam disk can be positioned parallel to or in the longitudinal axis of the energy store. As an alternative to this, the central axis of the cam disk can run at an angle to the longitudinal axis of the energy store.

According to one embodiment, the pivoted lever is mounted on the housing by means of a ball bearing, a cylindrical roller bearing, a needle bearing or a sliding bearing.

The invention is described below using purely exemplary embodiments with reference to the accompanying drawings. Show it:

1 shows a side view of a door drive according to the invention with the housing open;

FIG. 2 shows a perspective view of the door drive from FIG. 1 ;

3A shows the door drive from FIG. 1 in a closed position of the output shaft

sectional view;

FIG. 3B shows the door drive from FIG. 1 in an open position of the output shaft in a sectional view; FIG.

4 shows a door drive according to a second variant in a closed position of the output shaft in a sectional view;

FIG. 5A shows a sectional illustration of the door operator from FIG. 1 ;

FIG. 5B shows a view of a first end of the compression spring of the door drive from FIG. 1 ; FIG. 5C shows a view of a second end of the compression spring of the door drive from FIG. 1 ;

6A shows a perspective view of a coupling element between pivoting lever and movable first abutment according to a first variant;

6B shows a perspective view of a coupling point between the pivoting lever and the movable first abutment according to a second variant;

Fig. 7A is a sectional view of a movable first abutment; and

7B is a sectional view of a second abutment.

1 and 2 show an exemplary embodiment of a door drive 10 according to the invention. The door drive 10 comprises an electric motor 18 which is coupled to an output shaft 14 via a gearbox 20, so that a drive torque generated by the electric motor 18 is applied to the output shaft 14 is transmitted in order to pivot a linkage (not shown) coupled to the output shaft 14 in such a way that a door leaf coupled to the linkage is transferred from a closed position to an open position. The gear 20 is designed as a reduction gear, i.e. the torque provided by the electric motor 18 is increased by the gear 20, while the speed provided by the electric motor 18 is reduced by the gear 20. For this purpose, the transmission 20 includes a worm gear 40 and several, here two, spur gear 42 wheels with preferably helical spur gears.

The output shaft 14 is non-rotatably connected to a cam disk 16, in the present example a symmetrical cam disk 16. An outer peripheral surface 16a (see FIG. 2) of the cam disk 16 rests against an outer peripheral surface 22a of a roller 22, so that the roller 22 can roll on the outer peripheral surface 16a of the cam disk 16 during operation. The roller 22 is rotatably attached to a pivot lever 24 . The pivoting lever 24, which is curved due to the installation space, is in turn attached to a housing 12 of the door drive 10 so that it can pivot about a pivot axis 26. In addition to the roller 22, a first abutment 34 for an energy store 32 in the form of a spiral compression spring is also attached to the pivoting lever 24, more precisely at a coupling point 38 between the pivoting lever 24 and the roller 22. The first abutment 34 is mounted on the pivoting lever 24 such that it can pivot about an axis 44 which is also the central axis of the roller 22 . In addition, the door drive 10 has a second abutment 36 for the compression spring 32 . The compression spring 32 is thus arranged between the first abutment 34 and the second abutment 36 . While the first abutment 34, guided by the pivot lever 24, can be pivoted about the pivot axis 26, the second abutment 36 is connected to the housing 12 in a stationary manner, with the exception of a small compensating movement, which will be explained below, so that the second abutment 36 can support a clamping force applied by the first abutment 34 to the compression spring 32 in order to clamp the compression spring 32 . In order to be able to set the magnitude of the tensioning force absorbed by the compression spring 32 during the opening of the door, a closing force adjustment device 52 is provided, which is described in more detail with reference to FIG. 7B.

As can be seen in Fig. 1, the motor 18 and the transmission 20 are arranged on one side of the output shaft 14 and an energy storage unit 28, the first abutment 34, the energy storage 32, the second abutment 36 and - if present - the closing force adjustment device 52 is arranged on a side of the output shaft 14 opposite the motor 18 and the transmission 20 . This simplifies the design and manufacture of the door operator 10 and allows for a modular design so that the door operator 10 can also be manufactured and sold without the energy storage unit 28 . FIGS. 3A and 3B show how the energy storage unit 28 is activated, ie how the energy storage 32 is charged. The door operator 10 is shown in its closed position S in FIG. 3A. The roller 22 is in contact with a concave area 17 of the cam disk 16 which is at a relatively short distance from a central axis 64 of the output shaft 14 . The closing force adjustment device 52 is usually adjusted in such a way that the energy store 32 presses on the roller 22 in the closed position S with a relatively small force and thus holds the roller 22 in the concave area 17 of the cam disk 16

When the electric motor 18 drives the output shaft 14 to open the door leaf, the cam disk 16 is rotated relative to the housing 12 (see arrow in FIG. 3B). Since the effective distance between the central axis 64 and the peripheral surface 16a of the cam disk 16 increases as a result of the rotation of the cam disk 16, the roller 22 is displaced by the cam disk 16 while it rolls on the peripheral surface 16a, i.e. by the Central axis 64 of the cam 16 pushed away.

Since the roller 22 is attached to the pivot lever 24 so that it can pivot about the pivot axis 26 , the roller 22 moves along a circular path while the roller 22 is displaced by the cam disk 16 . Together with the roller 22, the first abutment 34 also moves on the circular path away from the central axis 64 of the output shaft 14 and towards the second abutment 36. As a result, the energy store 32 designed as a compression spring is compressed and thus tensioned. In order to avoid buckling of the compression spring 32, this has a ratio between the unstressed length of the compression spring and the diameter of the compression spring of less than 2. In addition, the pivot axis 26 of the pivot lever 24 is offset relative to the position of the coupling point 38 between the pivot lever 24 and the first abutment 34 in the closed position S in the direction of the second abutment 36, ie to the right in the figures The result is that the coupling point 38 initially moves away from the central axis 30 of the energy store 32 formed in the closed position S during the pivoting of the pivot lever 24, but approaches it again after a vertex of the central axis 30 has been exceeded, so that the first abutment 34 overall, the smallest possible displacement in the transverse direction, ie away from the central axis 30, experiences. In addition, the pivot axis 26 is arranged as far away as possible from the central axis 30 in the housing 12 in order to obtain the largest possible pivot radius and thus a small offset in the transverse direction.

The potential energy stored by the energy store 32 can be used to close the door leaf coupled to the door drive 10, for example in the event of a fire. In order to move the door drive from its open position O (Fig. 3B) back to the closed position S (Fig. 3A), the energy accumulator 32 presses on the first abutment 36, from which the force is applied directly via the roller 22 to the cam disk 16 is transferred. The roller 22 presses on the cam disk 16, as a result of which the cam disk 16 is set in rotation and a torque is thus generated on the output shaft 14 in order to pivot the door leaf.

While in the exemplary embodiment in FIGS. 3A and 3B the central axis 64 of the output shaft 14 in the closed position S is aligned with the central axis 30 of the energy store 32, with the result that depending on the direction of rotation of the output shaft 14, different torque curves for the door drive 10 As a result, in the alternative exemplary embodiment shown in FIG. 4, the center axis 64' of the output shaft 14' in the closed position S is offset from the center axis 30' of the energy store 32'. In addition, the cam disk 16* is aligned in such a way that its axis of symmetry 66' is arranged at an angle to the central axis 30' of the energy store 32'. This exemplary embodiment has the advantage that almost identical torque curves result in the different directions of rotation. FIG. 5A shows a further sectional view of the door drive 10, the door drive 10 being shown in section along the central axis 30 of FIG. 3A and perpendicular to the sectional plane according to FIG. 3A. It can be seen in FIG. 5A, among other things, that a pin 48 is provided for coupling the roller 22 to the first abutment 34 and the pivoting lever 26 . This sectional view also shows that the roller 22 is rotatably mounted on the pin 48 by means of a needle bearing 68 . In connection with FIGS. 5B and 5C, which show the two end faces of the compression spring 32, it can also be seen that the ends of the compression spring 32 are applied and ground and are offset by 180° from one another. In other words, the total number of turns of the compression spring 32 is not an integer, but ends at approximately X.5 turns, where X is a natural number.

Two different exemplary embodiments for the coupling point 38 between the rocker arm 24, the roller 22 and the first abutment 34 are shown in FIGS. 6A and 6B. The two exemplary embodiments have in common that the pivoting lever 24 has a fork-shaped extension 46, in the intermediate space of which the roller 22 is arranged. The pin 48 for mounting the roller 22 extends parallel to the pivot axis 26 of the pivot lever 24 from one section of the fork-shaped extension 46 to the other section of the fork-shaped extension 46. The two different exemplary embodiments differ, among other things, in how a receptacle 50 of the first abutment 34 is configured. While in the exemplary embodiment according to FIG. 6A the receptacle 50 is formed by a fork-shaped section with two separate holding plates, the receptacle 50 in the exemplary embodiment according to FIG. 6B is formed by a receptacle 50 enclosing the roller 22 from four sides. FIG. 7A shows a detailed view of the coupling point 38 and the first abutment 34 from FIG. 5A. With regard to the coupling point 38, it can be seen here that the pin 48 is rotatably mounted on the pivoting lever 26 via a roller bearing 69, for example a needle bearing. As an alternative to the roller bearing 69, a plain bearing can be provided. It can also be seen in FIG. 7A that the first abutment 34 has, in addition to the receptacle 50 for coupling the abutment 34 to the pin 48 , a force absorption surface 70 on the end face and a radial fixing section 72 . The radial fixing section 72 engages in the compression spring 32 on the front side in order to support the compression spring 32 radially.

7B shows a detailed view of the second abutment 36 and the closing force adjustment device 52 connected to the second abutment 36. The second abutment 36 has—a mirror image of the first abutment 34—a frontal force absorption surface 74 and a radial fixing section 76. In addition, the second abutment 36 has two opposite extensions 78 (see FIG. 2) which engage in corresponding recesses in the housing 12 such that the second abutment 36 is arranged in the housing 12 secured against rotation. The second abutment 36 also has a threaded opening 80 whose internal thread meshes with a spindle 54 . The spindle 54 is in turn connected in a rotationally fixed manner to a worm wheel 58 which can be rotated from the outside via a worm 60 (cf. FIG. 2). The second abutment 36 can be displaced axially by rotating the spindle 54 so that the compression spring 32 can be tensioned or released. So that the second abutment 36, while the first abutment 34 moves along the circular path, can carry out a compensating movement, ie can adapt to the slightly changing axial alignment of the compression spring 32, the spindle 54 can be pivoted by means of a ball joint 62 on the Housing 12, here a housing cover 12a stored. The ball joint 62 is therefore used to automatically align the spindle 54 in the direction of the central axis 30 of the compression spring. and as a result the compression spring 32 is always held securely between the two abutments 34, 36, without having to provide additional storage for the compression spring 32. The ball joint 62 can also serve to compensate for manufacturing tolerances. If no closing force adjustment device is provided, the second abutment 36 can nevertheless be arranged in the housing such that it can pivot over an angular range, for example via a ball joint.

Overall, it is noticeable in the present design that the first abutment 34 is mounted guided exclusively by the pivoted lever 24 and thus without

linear bearing manages. It is also noticeable that the compression spring 32 is only held in position by the two abutments 34, 36 and is therefore built into the door drive 10 so to speak “floating”. As a result, particularly little friction is generated during operation of the door drive 10, which makes the door drive 10 efficient and low-maintenance.

Reference List

10 drive

12 housing

12a housing cover

14 downforce worlds

16 cam disc

16a outer peripheral surface

17 concave area

18 electric motor

20 gears

22 roller

22a outer peripheral surface

24 swing levers

26 pivot axis

28 energy storage unit

30 longitudinal axis

32 energy storage

34 first abutment

36 second abutment

38 coupling point

40 worm gears

42 spur gears

44 axis

46 fork-shaped extension (pivoting lever)

48 pin

50 recording

52 closing force adjustment device

54 spindle

58 worm wheel 60 snail

62 ball joint

64 central axis

66 axis of symmetry 68 needle bearing

69 rolling bearings

70 force receiving surface

72 fixing section

74 force receiving surface 76 fixing section

78 extension

80 thread opening

S closed position

O open position

Claims

Claims Drive (10) for a door or a window, comprising a housing (12), an output shaft (14) rotatably mounted on the housing (12) and having a cam disk (16), an electric motor (18) with a gear (20) for driving the output shaft (14) from a closed position (S) in an opening direction in order to open the door or the window, a roller (22) rolling on the rotating cam disk (16) during operation, a pivoting lever (24), which is pivoted about a pivot axis (26) on the housing (12), wherein the roller (22) is rotatably arranged on the pivot lever (24), and an energy storage unit (28) for driving the output shaft (14) from an open position ( 0) in a closing direction in order to close the door or the window, the energy storage unit (28) having an energy storage device (32) having a longitudinal axis (30) and a movable first abutment (34 ) and a second abutment (36) facing away from the roller (22) and on which the energy storage device (32) is supported, the roller (22) transmitting force between the cam disk (16) and the movable first abutment (34 ) of the energy storage unit (28), the cam disc (16) and the energy storage unit (28) being arranged on opposite sides with respect to the pivoting lever (24), and the movable first abutment (34) of the energy storage unit (28) being rotatably and non-displaceably coupled to the pivoted lever (24) at a coupling point (38) and thereby guided by the pivoted lever (24) on a circular path. Drive (10) according to claim 1, characterized in that the gear (20) comprises a worm gear (40) and a spur gear (42). Drive (10) according to claim 1 or 2, characterized in that the electric motor (18) and the energy storage unit (32) are arranged on opposite sides with respect to the output shaft (14). Drive (10) according to one of the preceding claims, characterized in that the roller (22) and the movable first abutment (34) are mounted on the pivoting lever (24) so as to be rotatable about the same axis (44). Drive (10) according to one of the preceding claims, characterized in that the pivoting lever (24) has a fork-shaped extension (46) into whose free space extends a pin (48) on which the movable first abutment (34) is rotatably mounted . Drive (10) according to one of the preceding claims, characterized in that the movable first abutment (34) has a receptacle (50), formed in particular by a fork-shaped extension, for the roller (22) and the roller (22) is rotatably arranged in the receptacle (50). Drive (10) according to one of the preceding claims, characterized in that in the closed position (S) the pivot axis (26) of the pivot lever (24) viewed in the direction of a longitudinal extent of the energy store (28) is further away from the output shaft (14). is arranged as the coupling point (38) between the pivoting lever (24) and the movable first abutment (34). Drive (10) according to one of the preceding claims, characterized in that when the output shaft (14) moves from the closed position (S) to the open position (O) and vice versa, a deflection of the coupling point (38) between the pivoted lever (24) and the movable first abutment (34) perpendicular to the longitudinal axis (30) of the energy store (32) through a reversal point. Drive (10) according to one of the preceding claims, characterized in that the pivoting lever (24) is curved. Drive (10) according to one of the preceding claims, characterized in that the energy store (32) is designed as a spring, in particular a compression spring, in particular a spiral compression spring. Drive (10) according to Claim 10, characterized in that a diameter of the spring (32) is greater than 60% of a housing diameter, preferably greater than 80% of the housing diameter. Drive (10) according to Claim 10 or 11, characterized in that a ratio of the unstressed length of the spring to the diameter of the spring is less than 3, in particular less than 2. Drive (10) according to at least one of claims 10 to 12, characterized in that a total number of coils of the spring is in the range between X.3 and X.7, in particular is X.5, where X is a natural number. Drive (10) according to at least one of Claims 10 to 13, characterized in that the ends of the spring (32) are applied and/or ground and/or offset by 180° with respect to one another. Drive (10) according to at least one of Claims 10 to 14, characterized in that the spring (32) is held by the two abutments (34, 36) exclusively in its end regions. Drive (10) according to at least one of Claims 10 to 15, characterized in that the movable first abutment (34) is designed as a spring plate. Drive (10) according to one of the preceding claims, characterized in that a closing force adjustment device (52) is provided, by means of which a prestressing force of the energy store (32) can be adjusted. Drive (10) according to Claim 17, characterized in that the closing force adjustment device (52) comprises a spindle (54) and a spring plate which can be moved along the spindle (54) by rotation of the spindle (54) and which the second abutment (36) for the energy store (32). Drive (10) according to Claim 18, characterized in that the spindle (54) can be driven either directly or via a worm wheel (58) which is rotated by a worm (60). Drive (10) according to Claim 18 or 19, characterized in that the spindle (54) is mounted in the housing (12) so that it can pivot over a defined angular range, in particular by means of a ball joint (60). Drive (10) according to one of the preceding claims, characterized in that the cam disc (16) is at least partially arranged in alignment with the energy store (32). Drive (10) according to one of the preceding claims, characterized in that in the closed position (S) the central axis (64) of the output shaft (14) is arranged in alignment with the longitudinal axis (30) of the energy store (32) or that in the closed position (S) the central axis (64) of the output shaft (14) is arranged offset to the longitudinal axis (30) of the energy store (32) by at most the diameter of the roller (22) or drive shaft (14). Drive (10) according to one of the preceding claims, characterized in that the pivoted lever (24) is mounted on the housing (12) by means of a ball bearing, a needle bearing or a sliding bearing.