Drive for a door or window

Abstract

The invention relates to a drive for a door or window, comprising a housing with a longitudinal axis, an output shaft rotatably mounted in the housing, an actuating piston linearly adjustable in the housing along the longitudinal axis between a first position and a second position, which divides the interior of the housing into a first and a second space and which is coupled to the output shaft to convert a movement of the actuating piston into a rotational movement of the output shaft, and a spring accumulator, in particular a coil spring, arranged in the second space, which is pre-tensioned, in particular compressed, when the actuating piston is moved to the second position. An axial piston pump, in particular a swashplate pump, is provided for moving the actuating piston.

Description

[0001] The invention relates to a drive for a door or window. Specifically, the invention relates to a drive for a door or window with a hydraulic pump that serves to provide drive power for the drive, according to the preamble of patent claim 1.

[0002] A drive of the type mentioned above is known from WO 2006 / 066666 A1.

[0003] Hydraulic door operators are well known. Common hydraulic door operators use a gear pump to provide the drive power. Conventional gear pumps have the disadvantage that they are not designed for the high pressures, low volumes, and small installation spaces of a door operator. Furthermore, gear pumps exhibit high leakage rates, require a large amount of installation space, and are expensive to manufacture due to stringent sealing and tolerance requirements. To compensate for the high leakage rates of the gear pump, the pump and its drive motor must be larger, and their flow rate must be increased by increasing the motor speed, which leads to loud operating noise.

[0004] The door drive known from the document cited at the outset comprises a drive unit that can be coupled to the door via an output shaft and is arranged in a housing, a motor that is drivingly connected to the drive unit, and a spring energy accumulator arranged in the housing and coupled to the motor and the drive unit. The drive further comprises a hydraulic pump in the form of a proportional piston pump that is connected to the motor drive and is hydraulically connected to a first pressure chamber assigned to the drive unit and a separate second pressure chamber assigned to the spring energy accumulator. A hydraulic damping device is provided that is arranged between a receiving chamber for the drive unit and an intermediate chamber of the housing adjacent to the second pressure chamber.

[0005] KR 2007 0006391 discloses a door hinge having a wobble plate in an air chamber between two springs.

[0006] It is an object of the invention to provide a drive for a door or a window which is efficient, compact and cost-effective to produce and which also causes minimal operating noise.

[0007] The problem is solved by a drive having the features of claim 1. The drive serves to open and / or close a door or a window. The drive comprises a housing with a longitudinal axis, an output shaft rotatably mounted in the housing, and an actuating piston which is linearly adjustable in the housing along the longitudinal axis between a first position and a second position, which divides the interior of the housing into a first space and a second space and which is coupled to the output shaft in order to convert a movement of the actuating piston into a rotational movement of the output shaft. The drive also comprises a spring accumulator arranged in the second space, which can be designed as a spiral compression spring and which is preloaded, in particular compressed, when the actuating piston is adjusted to the second position.In order to overcome the disadvantages explained with regard to the commonly used gear pump, a wobble plate pump is provided to move the actuating piston.

[0008] The swash plate pump has the advantage that the door drive can be manufactured cost-effectively and compactly, yet still generates high pump pressure without significant losses due to leakage. Furthermore, the swash plate pump generates very little noise during operation.

[0009] The spring mechanism can remain preloaded during normal operation and only be used to close the door or window in exceptional circumstances, such as a fire. Alternatively, the spring mechanism can be used to always close the door after a person has passed through.

[0010] The swash plate pump is advantageously designed to move the actuating piston from the first position to the second position, counter to a restoring force of the spring-loaded actuator, preferably to open the door or window. To hold the door or window in an open position, the restoring force can be counterbalanced by a hydraulic pressure applied by the swash plate pump to the actuating piston, counter to the restoring force.

[0011] The swash plate pump has one or more pump pistons aligned parallel to one another in the axial direction. During operation, the multiple pump pistons move axially out of phase with one another between a first end position and a second end position, thereby pumping hydraulic fluid from one chamber, e.g., the second chamber, to another chamber, e.g., the first chamber.

[0012] The actuating piston forms a movable wall of the first chamber and a movable wall of the second chamber, so that the actuating piston is moved by pumping the hydraulic fluid, for example from the second chamber into the first chamber.

[0013] To ensure the drive is as compact as possible, it is advantageous if the actuating piston and the pump piston(s) move along parallel axes during operation. In other words, the pump piston(s) of the swash plate pump are preferably all mounted so that they can move in the same direction as the actuating piston.

[0014] Advantageous embodiments of the invention can be found in the dependent claims, the description and the drawing.

[0015] According to one embodiment, the swash plate pump is arranged on the side of the spring accumulator opposite the actuating piston.

[0016] The swash plate pump can have a pump housing partially or completely accommodated or arranged in the housing. The pump housing can be arranged fixedly in the housing in at least one direction. Preferably, the pump housing is arranged in the housing in a rotationally fixed manner and / or fixedly in at least one axial direction. For axial fixing, a

[0017] Retaining ring. The pump housing can also be screwed into the drive housing.

[0018] The swashplate pump has at least one, in particular at least two, in particular exactly three, pump pistons. Each pump piston is mounted in the pump housing for linear movement along the longitudinal axis between a retracted position and an extended position. If the swashplate pump has multiple pump pistons, this enables continuous pumping performance and thus continuous movement of the door or window.

[0019] The swash plate pump has a so-called swash plate that can be driven to rotate about a rotational axis for actuating the respective pump piston. The swash plate does not necessarily have to be disc-shaped. However, it is advantageous if the swash plate has a flat, in particular disc-shaped, pump piston adjustment surface. The pump piston adjustment surface is aligned obliquely to the rotational axis of the swash plate. When the swash plate rotates about its rotational axis, the oblique alignment of the pump piston adjustment surface to the rotational axis of the swash plate results in the pump piston(s) arranged eccentrically to the rotational axis of the swash plate being cyclically displaced in the axial direction and then being given space to move back towards the swash plate.

[0020] The swash plate pump also has a drive motor for driving the swash plate. This drive motor is preferably indirectly connected to the drive housing. The drive motor can be attached directly or indirectly to the drive housing. The drive motor can be indirectly connected to the drive housing, for example, via an adapter plate or a bearing housing. For example, the drive motor can be designed as a geared motor. The drive motor is preferably designed as a stepper motor. Stepper motors have the advantage that they can generate relatively high torques in a small installation space. Installation space can be saved, in particular, by omitting the otherwise usually necessary gearbox.Since the gearbox can be omitted when using a stepper motor, the use of a stepper motor as a drive motor enables not only a particularly compact design but also a compact and cost-effective construction.

[0021] Preferably, the rotational axis of the swash plate is arranged parallel to the longitudinal axis of the housing. According to one embodiment, the rotational axis of the swash plate corresponds to a central longitudinal axis of the housing.

[0022] According to a particularly cost-effective embodiment, the pump piston adjustment surface has a constant angle to the rotational axis of the swash plate. The angle between the pump piston adjustment surface and the rotational axis is preferably in the range between 80° and 85°, e.g., 83°.

[0023] According to one embodiment, the swash plate pump has a drive shaft. The swash plate is preferably connected to the drive shaft at least in a rotationally fixed manner. "At least in a rotationally fixed manner" means that the swash plate and the drive shaft can be firmly connected to one another, e.g., integrally formed, or can be connected in a rotationally fixed manner but axially displaceable relative to one another. The swash plate is preferably connected directly to the drive shaft. According to an easy-to-assemble variant, the swash plate can be integrally formed with the drive shaft. The drive shaft can advantageously be driven by the drive motor.

[0024] According to one embodiment, a motor shaft of the drive motor engages the drive shaft in a form-fitting manner. In other words, the motor shaft of the drive motor can be rotationally fixedly coupled to the drive shaft by means of a form-fitting connection.

[0025] The drive shaft can be mounted in a radial bearing, in particular a radial ball bearing. The radial bearing is preferably housed in a cover of the drive that closes the housing at the front or in a bearing housing that adjoins, in particular is coupled to, the housing at the front. The drive motor can be attached to the bearing housing. A portion of the pump housing can be arranged in the bearing housing.

[0026] According to one embodiment, the cover has an axial extension against which the pump housing rests. In other words, the cover can have an axial extension that fixes the pump housing in an axial direction.

[0027] To minimize friction, an axial bearing, in particular an axial ball bearing, an axial needle bearing, or a deep groove ball bearing, can be provided between the swash plate and the pump piston(s). The axial bearing can be equipped with at least one rotor disk, preferably two rotor disks. The axial bearing is preferably coupled to the swash plate to simplify assembly of the drive. The axial bearing can be secured to the swash plate, for example, by means of a screw.

[0028] The respective pump piston can be rounded at its end facing the swash plate, i.e. have a convex front surface.

[0029] When exposed to sunlight, the hydraulic fluid in the drive can expand, which puts particular strain on external seals. In order to design seals between the drive shaft or motor shaft and the cover or bearing housing in a cost-effective and compact manner, it is advantageous if the swash plate pump is free of hydraulic fluid in the area of ​​the swash plate. Free of hydraulic fluid means that the space containing the swash plate and / or the radial bearing is sealed off from the hydraulic fluid in the first and second spaces, so that only very small amounts of hydraulic fluid, if any, can flow into the space containing the swash plate and / or the radial bearing. For this purpose, it is advantageous if the respective pump piston is hydraulically sealed against the pump housing. For this purpose, seals can be provided on the pump piston(s) and / or on the pump housing.Preferably, at least one seal, i.e. a piston seal, is attached to the respective outer circumferential surface of the respective pump piston. Alternatively or additionally, at least one seal, i.e. a rod seal, can be provided on the inner circumferential side of a respective pump chamber in which the respective pump piston is mounted for linear movement. The at least one seal can thus be designed as a piston seal [WB2], i.e. as a seal assigned to the pump piston and moving with the pump piston, or as a rod seal, i.e. as a seal assigned to the pump housing and not moving with the pump piston. The seal can be designed, for example, as a lip seal or as a sliding ring with an O-ring. Alternatively or additionally, the at least one seal can comprise a plurality of circumferential grooves which act as a labyrinth seal.In order to further improve the tightness between the pump pistons and the pump housing, the outer circumference of the respective pump piston and the corresponding inner circumference of the pump housing can be adapted to one another in such a way that the respective pump piston is movably guided in the pump housing, but only a minimal space is formed between the respective pump piston and the pump housing, resulting in a close clearance fit which acts as a gap seal I [WB3]. Such a gap seal has the advantage that an existing rod seal or piston seal experiences less hydraulic pressure during operation, thereby reducing friction between the rod seal and the pump piston or the piston seal and the pump housing. This can further improve the efficiency of the pump.It should be noted that such an upstream gap seal can in principle be used regardless of whether the pump piston is sealed by means of a piston seal or a rod seal.

[0030] It is also advantageous if the pump piston(s) do not have an axial through-bore. However, the fact that the swashplate area is "hydraulic fluid-free" does not mean that no fluid, such as lubricant, may be present in this area. Typically, lubricant is necessary in the swashplate area, for example, to lubricate existing bearings.

[0031] According to one embodiment, the respective pump piston is preloaded toward the extended position and against the swash plate, in particular by means of a respective return spring. "Preloaded against the swash plate" means that the swash plate limits the movement of the pump piston(s) as a result of the return force of the respective return spring. However, the pump piston(s) do not have to bear directly against the swash plate. For example, the aforementioned axial bearing can be arranged between the swash plate and the pump piston(s). The respective return spring for the respective pump piston can be designed as a spiral compression spring. To achieve a particularly compact design, the respective return spring for the respective pump piston can alternatively be designed as a wave spring. The respective pump piston can have a respective axial extension that extends into the respective return spring.This allows the dead space in the respective pump chamber to be kept small, so that even if there are air inclusions in the hydraulic fluid of the drive, a sufficiently high negative pressure can be generated to suck the hydraulic fluid into the pump chamber(s).

[0032] To achieve the most uniform pumping performance possible, the pump pistons can be evenly distributed in the circumferential direction relative to the swash plate's axis of rotation. For example, if three pump pistons are provided, they are preferably arranged offset by 120° from each other around the swash plate's axis of rotation in the pump housing. The pump pistons are preferably arranged equidistant from the swash plate's axis of rotation in the radial direction.

[0033] According to one embodiment, the spring-loaded actuator is supported on the pump housing. Alternatively, a closing force adjustment mechanism arranged between the spring-loaded actuator and the pump housing can be provided, with a spring plate that is axially adjustable on a spindle, in particular by means of a worm shaft, and the spring-loaded actuator can be supported on the spring plate. The closing force adjustment mechanism preferably serves to adjust the level of the restoring force applied by the spring.

[0034] Preferably, the pump housing for the or each of the pump pistons has an inlet extending along the longitudinal axis and an outlet extending obliquely, in particular perpendicularly, to the longitudinal axis. Each inlet and each outlet can be provided with a respective, in particular pre-tensioned, check valve. The inlets can each be provided with a filter to prevent contaminants from entering the pump housing.

[0035] To easily connect the outlets, the outlets can be connected to each other via a circumferential groove formed on the circumference of the pump housing. To simplify installation of the pump housing, the pump housing is preferably designed to be rotationally symmetrical.

[0036] According to one embodiment, the inlets are connected to the second chamber, and the outlets are connected to the first chamber via an outflow channel, in particular one having a check valve. During operation of the swash plate pump, hydraulic fluid can be pumped from the second chamber into the first chamber to move the actuating piston into the second position. Advantageously, the spring accumulator is arranged in the second chamber. In such a configuration, the second chamber can also be referred to as a spring chamber.

[0037] The first chamber and the second chamber can be connected to one another via a return flow channel, in particular having a throttle valve, in order to return hydraulic fluid from the first chamber to the second chamber when the actuating piston is adjusted to the first position due to the pre-tensioned spring accumulator.

[0038] In order to hold the actuating piston in the second position and thus, for example, to keep the door or window in an open position, a check valve can be arranged in the return flow channel.

[0039] In particular, the swash plate pump defines at least one pump chamber, in particular several pump chambers, wherein a respective pump piston is mounted for linear movement in the respective pump chamber. A dead space of the respective pump chamber can be smaller than a delivery volume of the respective pump chamber. As already explained above, this allows a sufficiently high negative pressure to be generated to draw the hydraulic fluid into the respective pump chamber, even in the case of air pockets in the drive's hydraulic fluid.

[0040] Preferably, the drive motor is designed as a stepper motor and / or the respective pump piston is designed as a cylindrical pin.

[0041] To achieve a favorable closing movement of the door or window, the actuating piston can be coupled to the output shaft via a gear mechanism, for example, a rack and pinion gear or a cam-disk gear. The gear mechanism can advantageously be designed as a rack and pinion gear. The rack and pinion gear preferably comprises a rack with irregular teeth and a corresponding gear with corresponding irregular teeth.

[0042] The drive can be designed as a permanently active door closer or as a free-swing door closer. A "permanently active door closer" refers to a door closer that always returns the door to its closed position and whose restoring force can be used to open the door manually and / or mechanically. In contrast, with a free-swing door closer, the spring drive is preloaded during normal operation, allowing the door to be opened and closed without additional resistance. In an exceptional case, such as a fire, the door closer is triggered, causing the door to be closed by the door closer. The drive can also be designed for windows.

[0043] The invention also relates to the use of the drive as a continuously active door closer or as a free-wheeling door closer. The drive can preferably be designed such that the door or window connected to the drive can be manually opened and closed again by a spring drive, independent of the operation of the axial piston pump. The hydraulic drive, i.e., the axial piston pump, can only open the door when explicitly requested, for example, by operating a switch.

[0044] The invention is described below using purely exemplary embodiments with reference to the accompanying drawings. They show: Fig. 1 a side sectional view of a drive according to the invention; Fig. 2 the drive of Fig. 1 with a schematic representation of channels used to operate the drive and their valves; Fig. 3A a section of the drive showing a wobble plate pump of Fig. 1 in a first pumping position; Fig. 3B the section of the drive showing the swash plate pump of Fig. 1 in a second pumping position; Fig. 4 shows a detailed view of a swash plate pump of a drive according to a second variant; Fig. 5 shows a detailed view of a swash plate pump of a drive according to a third variant; Fig. 6 shows a detailed view of a swash plate pump of a drive according to a fourth variant; Fig. 7 shows a detailed view of a swash plate pump of a drive according to a fifth variant; Fig. 8 shows a detailed view of a swash plate pump of a drive according to a sixth variant; Fig. 9 shows a detailed view of a swash plate pump of a drive according to a seventh variant; Fig. 10A shows a first perspective view of the swash plate pump according to the third variant; Fig. 10B shows a second perspective view of the swash plate pump according to the third variant; Fig. 11A shows a first perspective view of a pump housing; Fig. 11B shows a second perspective view of the pump housing; Fig. 11C shows a sectional view of the pump housing; and Fig.12A perspective sectional view of a swash plate mounted in a cover.

[0045] The Figuren 1 and 2show a side sectional view of a drive 10 according to the invention. The drive 10 has a housing 12 which extends along a longitudinal axis L of the drive 10. The housing 12 defines an inner circumferential surface 14 defining an interior of the housing 12. An actuating piston 16 is mounted such that it can move in the direction of the longitudinal axis L along the inner circumferential surface 14. A rack and pinion gear 18 converts a linear movement of the actuating piston 16 into a rotational movement of an output shaft 20. For this purpose, a rack 18a of the rack and pinion gear 18 is formed on an inner side of the actuating piston 16. The rack 18a meshes with a gear 18b of the rack and pinion gear 18 which is connected in a rotationally fixed manner to the output shaft 20. The rack 18a and the gear 18b each have asymmetrical teeth in order to achieve an advantageous speed profile of the door or window sash when closing the door or window.

[0046] The actuating piston 16 is subjected to a restoring force by a spring accumulator 22, which holds the actuating piston 16 in a first position (see Fig. 1 ). Against the restoring force, the actuating piston 16 can be moved along the longitudinal axis L from the first position to a second position. In order to move the actuating piston 16 along the longitudinal axis L, an axial piston pump 24 in the form of a swash plate pump is provided. The swash plate pump 24 serves to discharge hydraulic fluid, which is located in a second chamber 28 extending between the actuating piston 16 and a pump housing 26 of the swash plate pump 24, via an outflow channel 30 (see Fig. 2 ) into a first chamber 32. The hydraulic fluid pumped into the first chamber 32 displaces the actuating piston 16 delimiting the first chamber 32, so that it moves against the restoring force of the spring accumulator 22, here a spiral compression spring, in the direction of the swash plate pump 24. In order to drain the hydraulic fluid from the first chamber 32 into the second chamber 28, a return flow channel 34 (see Fig. 2 ) is provided. A throttle valve 36 is arranged in the return flow channel 34 in order to limit the return flow speed of the hydraulic fluid and thus ensure that, for example, a door connected to the drive 10 closes slowly and in a controlled manner. In order to hold such a door connected to the drive 10 in an open position without having to continuously apply pumping power, an electrically switchable shut-off valve 38 is provided in the return flow channel 34. In addition, a check valve 40 is provided in the outflow channel 30 in order to prevent hydraulic fluid from flowing back from the first chamber 32 into the second chamber 28 along the outflow channel 30. When the shut-off valve 38 is closed, the hydraulic fluid in the first chamber 32 cannot escape and, due to its incompressibility, prevents the actuating piston 16 from moving into the Fig. 1 and 2 to return to the first position shown.

[0047] In the following, with regard to the Figuren 3A und 3B The design and operation of the swash plate pump 24 will be discussed in more detail. The pump housing 26 defines several, as shown, for example, two, pump chambers 42a, 42b, which are delimited on one side by pump pistons 44a, 44b movably mounted along the longitudinal axis L. Each pump chamber 42a, 42b has an inlet 46a, 46b, which connects the second chamber 28 with the respective pump chamber 42a, 42b. The inlets 46a, 46b are each formed on the end faces of the pump chambers 42a, 42b. In addition, each pump chamber 42a, 42b has an outlet 48a, 48b, which connects the respective pump chamber 42a, 42b with the outflow channel 30 (see Fig. 2 ). The outlets 48a, 48b are each arranged circumferentially of the respective pump chamber 42a, 42b. The inlets 46a, 46b are each equipped with an inlet check valve 50a, 50b to prevent the hydraulic fluid from flowing directly back from the pump chamber 42a, 42b into the second chamber 28. Similarly, the outlets 48a, 48b are each equipped with an outlet check valve 52a, 52b to prevent the hydraulic fluid from flowing directly back from the outflow channel 30 into the pump chamber 42a, 42b.

[0048] When one of the pump pistons 44a, 44b is moved along its axial direction, i.e., along the longitudinal axis L, hydraulic fluid is sucked from the second chamber 28 into the respective pump chamber 42a, 42b during a movement from a retracted position to an extended position, i.e., from left to right in the figures. When the pump piston 44a, 44b is then moved back from the extended position to the retracted position, i.e., from right to left in the figures, the hydraulic fluid is pressed by the pump piston 44a, 44b out of the pump chamber 42a, 42b into the discharge channel 30.

[0049] To keep the pumping performance as constant as possible, the pump pistons 44a, 44b move out of phase with one another. To achieve this, the swashplate pump 24 has a swashplate 54. The swashplate 54 forms a pump piston adjustment surface 56, which is arranged obliquely to a rotational axis D of a drive shaft 58 formed integrally with the swashplate 54. The pump pistons 44a, 44b are preloaded in the direction of the swashplate 54 by return springs 60a, 60b. To minimize friction, an axial bearing 62 in the form of an axial needle bearing is arranged between the end surfaces of the pump pistons 44 facing the swashplate 54 and, in this case, convex, and the pump piston adjustment surface 56.

[0050] During operation of the swash plate pump 24, the swash plate 54 is set in rotation by a drive motor 63. Due to the rotational movement of the swash plate 54, the pump pistons 44a, 44b are moved out of phase with each other against the restoring force of the return spring 60a, 60b into the retracted position (pump piston 44a in Fig. 3A ) and then again by the respective return spring 60a, 60b into the extended position (pump piston 44b in Fig. 3A ) is pushed back. Thus, with each complete revolution of the swash plate 54 about the axis of rotation D, the pump pistons 44 perform a complete pumping movement, for example from the retracted position to the extended position and back again to the retracted position.

[0051] In Fig. 4 an alternative embodiment of the drive 10' is shown. In comparison to drive 10, in which an axial fixation of the pump housing 26 and thus a support of the restoring force of the spring accumulator 22 is achieved by a retaining ring 64, which is inserted into a retaining groove 66 formed circumferentially in the housing 12 (see Fig. 3B ) is used, is in the Fig. 4 In the embodiment shown, an axial extension 64' is provided on a cover 68 supporting the drive shaft 58, wherein the extension 64' serves to axially fix the pump housing 26 and thus to support the restoring force of the spring accumulator 22.

[0052] Another separate difference in Fig. 4 The embodiment shown is that the inlet check valves 50a', 50b' and the outlet check valves 52a', 52b' are spring-loaded to shorten the reaction time of the valves 50a', 50b', 52a', 52b'.

[0053] Another, also separate, difference in Fig. 4 The embodiment shown is that the axial bearing 62' is fixed to the swash plate 54' in the axial direction by means of a screw 70'.

[0054] One aspect that the various variants have in common is that the pump pistons 44 are sealed against the pump housing 26 by means of seals 45. While in the variants shown the seals 45 are attached to the pump pistons 44, the seals 45 can alternatively be attached to the pump housing 26. The seals 45 prevent the hydraulic fluid from penetrating a space 47 surrounding the swash plate 54. This allows the seals 94, 96 used to seal the space 47 to be designed more simply and thus more cost-effectively.

[0055] While in the embodiments of the Fig. 1 bis 4 the cover 68 serves to support the drive shaft 58 and to close the housing 12 on the end face adjacent to the axial piston pump 24, serves in the Fig. 5 In the embodiment shown, the pump housing 26" serves to close the housing 12" at the front. In addition, in the Fig. 5 In the embodiment shown, a bearing housing 72" is provided to support the drive shaft 58". The drive motor 63" is fastened to the front of the bearing housing 72". As can be seen in Figures 6A and 6B, the bearing housing 72" is connected to the housing 12" at the front by means of a flange 74" and screws 76". The drive motor 63" is in turn fastened to the bearing housing 72" by means of screws 78".

[0056] The design of the Fig. 5 also has a closing force adjustment 80" for setting the level of the restoring force of the spring accumulator 22". The closing force adjustment 80" comprises a spring plate 82" which is mounted in the housing 12" in a rotationally fixed but axially displaceable manner and which supports the spring accumulator 22" at the front. The spring plate 82" is adjustable in the longitudinal direction L by means of a spindle 84" in order to either preload or relax the spring accumulator 22" depending on the direction of rotation of the spindle 84". The spindle 84" is in turn driven by a worm gear, of which Fig. 5 a part of the worm wheel 86" can be seen, can be set in rotation. The worm wheel 86" can be rotated via a worm shaft 88", which, as in Fig. 10A shown, is accessible from the outside.

[0057] Fig. 6 shows a further, particularly robust embodiment of a swash plate pump 24‴ for a drive 10‴. In this embodiment, the return springs 60a‴ and 60b‴ are designed as wave springs. The wave springs 60a‴ and 60b‴ are adapted in terms of their outer diameter to the cross-sectional area of ​​the respective pump chambers 42a‴ and 42b‴. In addition, the pump pistons 44a‴ and 44b‴ are designed such that they are in the position maximally displaced by the swash plate (see pump piston 44a‴ in Fig. 6 ) essentially completely occupy the pump chamber 42a‴ except for a structurally necessary free space for the wave spring 60a‴ and 60b‴. For this purpose, the pump pistons 44a‴ and 44b‴ have an axial extension 104a‴ and 104b"', which extends into the respective wave spring 60a‴ and 60b‴ and occupies a large part of an interior space of the respective wave spring 60a‴ and 60b‴. This embodiment has the advantage that a dead space 106‴ of the respective pump chamber 42a‴ and 42b‴, i.e. a space section of the respective pump chamber 42a‴ and 42b‴ in which the pump piston 44a or 44b is never located, can be kept small and yet a long guide surface of the pump pistons 44a‴ and 44b‴ in the pump housing 26 is made possible with a small overall length. This allows a sufficiently high negative pressure to be achieved even in the case of air inclusions in the hydraulic fluid of the drive 10. Suction of the hydraulic fluid into the pump chambers 42a‴ and 42b‴.

[0058] Fig. 7 shows a further embodiment of a wobble plate pump 24 IV< for a drive 10 IV< . In this embodiment, the seal 45 IV< between the pump pistons 44a IV< and 44b IV< and the pump housing 26 IV< is designed as a lip seal or grooved ring. The lip seals or grooved rings 45 IV< are arranged on their respective pump pistons 44a IV< and 44b IV<. Due to their design, such a lip seal or grooved ring 45 IV< generates particularly low frictional forces. As a result, the wobble plate pump 24 IV< can achieve high levels of efficiency and the drive motor 63 IV< can be made smaller and more cost-effective. The return springs 60a IV< and 60b IV< are designed as helical compression springs. The helical compression springs 60a IV< and 60b IV< extend along a recess in the respective pump piston 44a IV< and 44b IV< through the pump chamber 42a IV< and 42b IV< into the respective inlet 46a IV< and 46b v< .As a result, the helical compression springs 60a IV< and 60b IV< are supported at both their ends in the radial direction.

[0059] Fig. 8 shows a particularly cost-effectively manufactured embodiment of a 24 V< wobble plate pump for a 10 V< drive. In this embodiment, the seal 45 V< between the pump pistons 44a V< and 44b V< and the pump housing 26 V< is realized by a seal, specifically a rod seal, in the pump housing 26 V<. This makes it possible to use a standardized cylindrical pin as the pump piston 44a V< and 44b V<. Such cylindrical pins 44a V< and 44b V< are particularly cost-effective to obtain and yet maintain high quality standards. In this embodiment too, the return springs 60a V< and 60b V< - as shown - can be designed as wave springs [WB5]. Alternatively, the return springs can be designed, for example, as helical compression springs. In this case, a wave spring 60a V< , 60b V< is arranged in each of the pump chambers 42a V< and 42b V< between the pump housing 26 V< and the respective pump piston 44a V< and 44b V<.The rod seal 45 V< can be designed as a lip seal or as a sliding ring with an O-ring, for example. This results in a compact and particularly cost-effective design. The pressure in the pump chamber drops significantly until it reaches the seal 45 V< due to a favorable fit, i.e. the narrow gap, between the respective cylindrical pin 44a V< and 44b V< and the pump housing 26 V< and the gap seal [WB6] created in this way. This means that less pressure acts on the seal, which causes significantly less friction during dynamic operation. This in turn means that the swash plate pump 24 V< can achieve particularly high levels of efficiency and the drive motor 63 V< can be made smaller and more cost-effective. The gap seal described above can basically be provided for all variants described, regardless of whether a piston seal or a rod seal is used.

[0060] Fig. 9 shows a particularly low-friction embodiment of a wobble plate pump 24 VI< for a drive 10 VI< . In this embodiment, radially circumferential recesses, i.e. grooves 108 VI< , are provided in the outer circumferential surface of the pump pistons 44a VI< and 44b VI<, which create a sealing effect between the outer circumferential surface of the pump pistons 44a VI< and 44b VI< and the pump housing 26 VI< in the manner of a labyrinth seal. The hydraulic pressure in the respective pump chamber 42a VI< and 42b VI< drops sharply through the labyrinth seal created by the grooves 108 between the pump pistons 44a VI< and 44b VI< and the pump housing 26 VI< down to the seal 45 VI<, whereby frictional forces on the seal 45 VI< are reduced. As a result, the wobble plate pump 24 VI< can achieve particularly high levels of efficiency and the drive motor 63 VI< can be made smaller and more cost-effective.

[0061] The Figuren 11A, 11B und 11C show different views of a pump housing 26. In Fig. 11A The front inlets 46a, 46b, 46c and one of the circumferentially arranged outlets 48b can be seen. The outlets 48 are connected to each other via a circumferential groove 90. The groove 90 is sealed by two seals 91a, 91b running parallel to the groove 90. As can be seen from the Fig. 11B und 11C As can be seen, three pump chambers 42a, 42b, 42c for three pump pistons 44a, 44b, 44c are formed in the pump housing 26. The pump pistons are each arranged offset by 120° from one another around a central axis of the pump housing 26. If the swash plate pump 24 is equipped with exactly three pump pistons 44a, 44b, 44c, a good compromise is achieved between compact design and homogeneous pumping performance.

[0062] In Fig. 12 A detailed view of the cover 68 and the drive shaft 58 mounted in the cover 68 is shown. Here, it can be seen that the drive shaft 58 is formed integrally with the swash plate 54. The drive shaft 58 is rotatably mounted in the cover 68 by means of the radial bearing 92, here a radial ball bearing. The drive shaft 58 has a rotationally asymmetrical opening at its front end to allow the insertion of an asymmetrical motor shaft 98 of the drive motor 63 into the drive shaft 58 at its front end.

[0063] In addition, Fig. 12 The axial bearing 62 is shown in detail. The axial bearing is an axial needle bearing 62 with runner plates 100. A first runner plate 100a, facing the pump piston adjustment surface 56, rotates with the pump piston adjustment surface 56. A second runner plate 100b, facing the pump piston 44, does not rotate with the swash plate 54, just like the pump piston 44.

[0064] The cover 68 is - as well as the pump housing 26" made of Fig. 5 - can be screwed into the housing 12. For this purpose, the cover 68 has an external thread 102, which can be screwed into a corresponding internal thread formed on the inner circumferential surface 14 of the housing 12.

[0065] The drive 10 is suitable for various applications. When the check valve 38 is open, the actuating piston 16 can be adjusted by manually opening and closing a door or window coupled to the drive 10. As a result, the drive 10 is designed to close a manually opened door or window solely through the restoring force of the spring-loaded mechanism 22. Additionally, the drive 10 can be used to open a door or window coupled to the drive 10 using the drive power of the drive motor 63, hold it open by means of the closed check valve 38, and then close it again by opening the check valve 38. The drive 10 can also serve as a free-wheel door closer drive. The spring-loaded mechanism 22 is preloaded by adjusting the actuating piston 16 using the wobble plate pump 24.The door or window coupled to the drive 10 can then be opened and closed without moving the actuating piston 16. In a special case, for example, in the event of a fire alarm, a signal is sent to the shut-off valve 38 to open it. This causes the actuating piston 16 to be returned to its first position by the restoring force of the spring-loaded actuator 22, which ensures that the door or window is closed. List of reference symbols

[0066] 10Drive 12Housing 14Inner peripheral surface 16Adjusting piston 18Rack and pinion gear 18aRack 18bGear 20Output shaft 22Spring accumulator 24Axial piston pump / swash plate pump 26Pump housing 28Second chamber 30Outflow channel 32First chamber 34Return channel 36Throttle valve 38Locking valve 40Check valve 42Pump chamber 44Pump piston 45Seal 46Inlet 47Chamber 48Outlet 50Inlet check valve 52Outlet check valve 54Swash plate 56Pump piston adjustment surface 58Drive shaft 60Return spring 62Axial bearing 63Drive motor 64Retaining ring 64Axial extension 66Retaining groove 68Cover 70Screw 72Bearing housing 74Flange 76Screw 78Screw 80Closing force adjustment 82Spring plate 84Spindle 86Worm wheel 88Worm shaft 90Groove 92Radial bearing 91Seal 94Seal 96Seal 98Motor shaft 100Running disk 102External thread 104Extension 106Dead space 108Groove DRotation axis LLongitudinal axis

Claims

1. Drive (10) for a door or a window, comprising a housing (12) with a longitudinal axis (L), an output shaft (20) which is mounted rotatably in the housing (12), an actuating piston (16) which can be adjusted in the housing (12) in a linear manner along the longitudinal axis (L) between a first position and a second position, divides the interior space of the housing (12) into a first space (32) and a second space (28), and is coupled to the output shaft (20), in order to convert a movement of the actuating piston (16) into a rotational movement of the drive shaft (20), and a spring force accumulator (22), in particular a spiral compression spring, which is arranged in the second space (28) and is preloaded, in particular compressed, in the case of an adjustment of the actuating piston (16) into the second position, characterized in that a swash plate pump (24) is provided to move the actuating piston (16); wherein the swash plate pump (24) has: a pump housing (26) which is received partially or completely in the housing (12) and is arranged in the housing (12) in a fixed manner, at least one pump piston (44a, 44b, 44c), wherein the pump piston (44a, 44b, 44c) is mounted such that it can be moved in a linear manner in the pump housing (26) along the longitudinal axis (L) between a retracted position and an extended position, a swash plate (54) which can be driven rotatably about a rotational axis (D) for actuating the pump piston (44), wherein the swash plate (54) has a pump piston adjusting surface (56) which is oriented obliquely with respect to the rotational axis (D) of the swash plate (54), and a drive motor (63) for driving the swash plate (54).

2. Drive (10) according to Claim 1, characterized in that the swash plate pump (24) is arranged on that side of the spring force accumulator (22) which lies opposite the actuating piston (16).

3. Drive (10) according to Claim 1 or 2, characterized in that the swash plate pump (24) has at least two pump pistons (44a, 44b, 44c), wherein the swash plate (54) actuates the at least two pump pistons (44).

4. Drive (10) according to one of Claims 1 to 3, characterized in that the rotational axis (D) of the swash plate (54) corresponds to the longitudinal axis (L) of the housing (12), and / or in that the pump piston adjusting surface (56) has a constant angle with respect to the rotational axis (D) of the swash plate (54).

5. Drive (10) according to one of Claims 1 to 4, characterized in that the swash plate pump (24) has a drive shaft (58), to which the swash plate (54) is connected at least fixedly for conjoint rotation and which can be driven by the drive motor (63).

6. Drive (10) according to Claim 5, characterized in that the swash plate (54) is configured in one piece with the drive shaft (58), and / or in that a motor shaft (98) of the drive motor (63) engages into the drive shaft (58) in a positively locking manner.

7. Drive (10) according to Claim 5 or 6, characterized in that the drive shaft (58) is mounted in a radial bearing (92) which is received in a cover (68), which closes the housing (12) on the end side, of the driver (10) or in a bearing housing (72") which adjoins, in particular is coupled to, the housing (12") on the end side.

8. Drive (10) according to Claim 7, characterized in that the cover (68') has an axial projection (64'), against which the pump housing (26) is supported, and / or in that the drive motor (63") is fastened to the bearing housing (72") .

9. Drive (10) according to at least one of Claims 1 to 8, characterized in that an axial bearing (62), in particular an axial ball bearing, an axial needle bearing or a deep groove ball bearing, preferably with races (100), is provided between the swash plate (54) and the pump piston or pistons (44), wherein the axial bearing (62) is preferably secured by means of a screw (70) on the swash plate (54).

10. Drive (10) according to at least one of Claims 1 to 9, characterized in that the respective pump piston (44) is rounded at its end which faces the swash plate (54).

11. Drive (10) according to at least one of Claims 1 to 10, characterized in that the respective pump piston (44) is sealed hydraulically with respect to the pump housing (26), with the result that the swash plate pump (24) is free from hydraulic fluid in the region of the swash plate (54).

12. Drive (10) according to Claim 11, characterized in that the respective pump piston (44) is sealed hydraulically with respect to the pump housing (26) by means of a gap seal and / or a piston seal (45; 45'; 45"; 45‴; 45IV) or rod seal (45V, 45VI), in particular a lip seal or a sliding ring with an 0-ring.

13. Drive (10) according to at least one of Claims 1 to 12, characterized in that the respective pump piston (44) is preloaded in the direction of the extended position and against the swash plate (54), in particular by means of a respective restoring spring (60).

14. Drive (10) according to Claim 13, characterized in that the respective restoring spring (60) is configured as a spiral compression spring or a zigzag spring, and / or in that the respective pump piston (44) has an axial projection (104) which extends into the respective restoring spring (60).

15. Drive (10) according to at least one of Claims 1 to 14, characterized in that the pump pistons (44) are arranged distributed homogeneously in the circumferential direction with regard to the rotational axis (D) of the swash plate (54) .

16. Drive (10) according to at least one of Claims 1 to 15, characterized in that the spring force accumulator (22) is supported on the pump housing (26), or in that a closing force adjustment means (80") which is arranged between the spring force accumulator (22'') and the pump housing (26") and has a spring collar (82") which can be adjusted axially on a spindle (84"), in particular by means of a worm shaft (88"), is provided, and the spring force accumulator (22'') is supported on the spring collar (82").

17. Drive (10) according to at least one of Claims 1 to 16, characterized in that the pump housing (26) has, for the or each of the pump pistons (44), an inlet (46), which runs along the longitudinal axis (L), and an outlet (48) which runs obliquely, in particular perpendicularly, with respect to the longitudinal axis (L).

18. Drive (10) according to Claim 17, characterized in that each inlet (46) and each outlet (48) is provided with the respective (in particular, preloaded) check valve (50, 52), and / or in that the inlets (46) are each provided with a filter.

19. Drive (10) according to Claim 17 or 18, characterized in that the outlets (48) are connected to one another via a peripheral groove (90) which is configured on the peripheral side of the pump housing (26).

20. Drive (10) according to at least one of Claims 17 to 19, characterized in that the inlets (46) are connected to the second space (28) and the outlets (48) are connected via an outflow channel (30), in particular having a check valve (40), to the first space (32), wherein, during operation of the swash plate pump (24), hydraulic fluid is pumped from the second space (28) into the first space (32), in order to adjust the actuating piston (16) into the second position.

21. Drive (10) according to at least one of the preceding claims, characterized in that the first space (32) and the second space (28) are connected to one another via a return flow channel (34) which has, in particular, a throttle valve (36), in order to return hydraulic fluid from the first space (32) into the second space (28) in the case of an adjustment of the actuating piston (16) into the first position on account of the preloaded spring force accumulator (22).

22. Drive (10) according to Claim 21, characterized in that a shut-off valve (38) is arranged in the return flow channel (34), in order to hold the actuating piston (16) in the second position.

23. Drive (10) according to at least one of Claims 1 to 22, characterized in that the swash plate pump (24) defines at least one pump space (42), in particular a plurality of pump spaces (42), wherein a respective pump piston (44) is mounted in a linearly movable manner in the respective pump space (42), in particular wherein a dead space (106) of the respective pump space (42) is smaller than a delivery volume of the respective pump space (42).

24. Drive (10) according to at least one of Claims 1 to 23, characterized in that the drive motor (63) is configured as a stepping motor.

25. Drive (10) according to at least one of Claims 1 to 24, characterized in that the respective pump piston (44) is configured as a cylindrical pin.

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