WO2000042282A1 - Drive - Google Patents

Abstract

The invention relates to a drive which is configured to be as narrow as possible, especially a door closer (1) for concealed installation in a door leaf or a door frame. The inventive door closer (1) has a closer shaft (2) on which two lifting curve plates (22a, 22b) are arranged in such a way that they are offset from each other. Two spring cylinders (3a, 3b) with closer springs (4a, 4b) are situated on opposite sides of the closer shaft (2) respectively, said spring cylinders also being vertically offset from each other. Each spring cylinder interacts (3a, 3b) with a lifting curve plate (22a, 22b). Two damping cylinders (5a, 5b) with a small diameter are located opposite the spring cylinders (3a, 3b), respectively, said damping cylinders also interacting with the lifting curve plates (22a, 22b).

Description

 drive

The invention relates to a drive, e.g. Door closer, for a wing of a door, a window or the like.

The drive housing is preferably provided for concealed installation in a door leaf or in a door frame. At least two closer springs are arranged in the drive housing, which are acted upon when opening or closing the leaf and are designed as energy stores for automatically closing or opening the leaf, with each closer spring being supported on a separate piston, known as a spring piston, guided in the drive housing . In addition, a preferably hydraulic damping device for damping the closing and / or opening movement of the wing is arranged in the drive housing. In the drive housing there is mounted an output member, preferably designed as a closer shaft, which cooperates with the closer springs and / or with the damping device via a gear and is coupled to a force-transmitting linkage. DE 195 26 061 A1 describes a particularly narrow door closer for concealed installation in a door leaf or door frame. The door closer has a piston system with two pistons working in opposite directions and two separate closer springs. The two pistons are coupled to the closer shaft via a crank mechanism arranged on an eccentric disc. Compared to conventional door closers with only one piston and one closer spring, the piston system allows the use of particularly narrow springs. However, the design of the crank mechanism is relatively complex. In an alternative embodiment, in which the pistons are coupled via two lifting discs, on the other hand, a separately designed damping device is required, which in turn takes up more installation space.

DE-PS 61 34 44 describes a door closer with two separate closer springs, which interact in opposite directions via a pinion with a pinion arranged on the closer shaft. The two closer springs are arranged in one plane on opposite sides of the closer shaft. Below the closer springs, a common damping device is accommodated in the door closer housing, which interacts with the closer shaft. The Schiießergehäuse has a relatively large height.

In US 2,460,369 two piston devices with a total of two closer springs are arranged one above the other in the closer housing. A continuously formed pinion on the closer shaft interacts with toothed drives, which are each formed in a recess in the pistons. This door closer also has a large overall height due to the superimposed closer springs.

The object of the invention is to construct a particularly narrow door closer with a damping device, which is also of particularly compact construction. The object is achieved according to the invention by the subject matter of claim 1.

The at least two spring piston chambers formed in the door closer housing are offset parallel to one another in the direction of the closer axis = closer shaft and / or in the direction parallel to the door plane. Alternatively or additionally, the at least two spring piston chambers are arranged on opposite sides of the closer shaft.

In general: When using several separate spring pistons with separate closer springs, the diameters of the individual closer springs are reduced, but at the same time a high closing force is achieved. Even with door closers with two separate closer springs, installation depths of the door closer, i.e. Extends of the door closer housing perpendicular to the door plane, in the range from 30 mm to 25 mm, in particular 28 mm, can be realized.

In versions in which the closer springs with spring pistons are arranged offset to one another in the direction of the closer axis, the closer springs can be arranged in a plane arranged parallel to the door plane - i.e. parallel to the plane in which the door closer housing is mounted on or in the door leaf or on or in the door frame - be arranged one above the other.

In versions in which the closer springs with spring pistons are arranged offset parallel to one another in a direction parallel to the door plane, the closer springs and spring pistons lie in two planes arranged parallel to one another at a distance and parallel to the door plane. With this arrangement, a particularly low construction of the door closer housing can be achieved, i.e. the extent of the door closer housing in the direction of the closer axis arranged parallel to the door plane is reduced.

In versions in which the closer springs with spring pistons are arranged on opposite sides of the closer shaft, the closer springs can both lie in one plane parallel to the door plane. Through the two arrangement, the closer springs can be axially aligned with one another or more or less offset from one another, whereby the overall height can also be reduced

If the spring piston chambers are arranged on opposite sides of the closer shaft, a particularly significant reduction in the overall height can be achieved; for this purpose the offset between the central axes of the piston spaces is made smaller than their diameter, i.e. When viewed in the axial direction of the housing, the cross sections of the piston chambers partially overlap.

Due to the fact that the spring piston chambers are arranged on opposite sides of the closer shaft and at the same time offset in height and the damping piston chambers have a smaller diameter than the spring piston chambers, this "nesting" of the piston chambers allows installation heights, i.e. extensions of the door closer housing in the direction of the closer axis, at the same time A range of 40 mm to 50 mm can be achieved, which makes door closers of this type particularly suitable for installation integrated in the door leaf or in the door frame.

The overall lengths are 250 mm to 350 mm for arrangements with closer springs on one side of the closer shaft and 350 mm to 550 mm for arrangements with closer springs arranged opposite the closer shaft.

The two closer springs can be of identical design or can also have different lengths, diameters or spring constants. At least one of the closer springs can interact with a device for adjusting the spring force, with which the bias of the closer spring can be varied.

In addition to the two piston chambers for receiving the spring pistons, two further piston chambers with a smaller diameter can advantageously be formed in the housing for receiving two damping pistons. Here are because a spring piston chamber and a damping piston chamber, at the same height on opposite sides of the closer shaft. The damping piston chambers are also designed to be shorter than the spring piston chambers, so that there is free space in the housing for accommodating further assemblies following the damping piston chambers. Such assemblies can be, for example, an electromagnetic valve actuation and / or the valve itself, a locking device, a sensor element, a hydraulically connectable additional spring or the like.

Two or more cam disks can be arranged one above the other on the closer shaft, the cam disks being mirror-symmetrical to their longitudinal axis. In particularly advantageous embodiments, the cam disc is heart-shaped, so that the ratio between the spring piston and the closer shaft changes depending on the angular position of the closer shaft; It is hereby achieved that the torque on the closer shaft remains almost constant or slightly decreases with increasing opening angle despite increasing spring force - there is therefore a reduction ratio with the opening angle - so that when using a sliding arm linkage when opening the The door gives a drastically decreasing torque towards larger opening angles.

The gearbox can be used as a pinion, e.g. with a pinion on the closer shaft side and a rack on the piston side. Here, the pitch curve of the pinion can be designed such that the effective lever arm of the pinion becomes smaller as the opening angle increases; here too there is a transmission ratio that decreases with the opening angle.

One spring piston and one damping piston each interact with the same lifting disc. The interaction preferably takes place via a force transmission roller or damping roller, which are mounted on an axle bolt at the front end of the respective piston.

In alternative designs, pinions and pinions can also be provided for coupling between the piston and the closer shaft. It is also possible to interpose a preferably hydraulic transmission between the spring piston and the cam plate or pinion or between the damping piston and the cam plate or pinion.

In a further embodiment, the closer shaft can be formed in two parts within the housing into two axially connected sections, the interaction of the two closer shaft sections taking place via a gear. In this way, the rotary movement of the closer shaft can be reduced or translated, which enables the use of differently designed closer springs.

In a preferred embodiment, the pressure-side piston chambers of the two damping pistons are coupled to one another via one or more hydraulic channels. The pressureless piston chambers of the two damping pistons are also hydraulically connected to one another via the receiving chamber of the closer shaft. This makes it possible to provide only one valve for adjusting the damping and only one valve for adjusting the end stop for both damping pistons. The valves are easily accessible on the top of the housing.

As a further advantage of the hydraulic coupling between the two damping pistons, it is possible to form a check valve in one damping piston and to form a pressure relief valve in the other damping piston. It is not necessary to provide these valves in every piston.

In a preferred embodiment, the door closer has a locking device in the open position of the door. For this purpose, the damping pistons can be hydraulically locked in the open position of the door, e.g. operated by an electromagnetic valve.

Another variant provides a free-wheel function for the door closer. This freewheeling function is achieved by locking the closer springs in the tensioned state. In addition, the damping is switched off hydraulically. The Spring pistons can then be moved freely by the closer springs without restoring forces.

Versions with a freewheel function can have a locking device for the closer spring, e.g. hydraulic valve, and have a freewheel in the area of the closer shaft or a force-transmitting linkage connected to it.

In addition to this basic version with two spring pistons and two damping pistons, other variants are possible, e.g. with two spring pistons and one damping piston, with three spring pistons and one or more damping pistons, and with more than three spring pistons. The arrangement of the spring pistons is preferably offset in order to reduce the overall height. In applications in which the overall height is not critical, however, all spring pistons can also be arranged on one side of the closer shaft and all damping pistons on the other side. Such systems can also have a modular design, which results in a free arrangement of the various pistons.

Another advantageous embodiment is that the drive is modular. Different, universally combinable modules can be provided, e.g. Spring and damping components, spring components, damping components, locking components or drive components; e.g. the required closing force can be achieved by the preferably axial alignment of spring components. There are also various options for coupling the output shafts, e.g. coupling via belt, pull rope, chain or push rod.

In a modified version, the door closer can also be provided for use on swing doors, with the door leaf opening in both directions. As an alternative, however, an overlying installation of such door closers is also possible, with optical advantages resulting from the small structural depth.

Another possible use of such a door closer is that the door closer is sunk in the floor area near the door axis of rotation. The closer shaft, which is arranged parallel to the floor level, is then connected to an angular gear with the door rotation axis or to a sliding arm arranged in the lower door area. The angular gear can be designed as a module which can be connected to the door closer housing. An advantage of this application of the door closer is that, due to the small overall depth (height of the tilted door closer), only a relatively flat recess is required for the recessed installation of the door closer in the floor. In many cases, retrofitting of doors that have not been equipped with a floor closer is possible.

The invention is explained in more detail in the figures. It shows:

Figure 1a is a schematic front view of a door equipped with a door closer in the closed position;

1 shows a longitudinal section through a door closer according to the invention with two spring pistons and two damping pistons;

Figure 2 is an enlarged view of Figure 1 in the area of the closer shaft;

FIG. 3 shows a detailed view of the damping piston in FIG. 1;

Figure 4 shows a longitudinal section through a door closer according to the invention of a modified embodiment with two spring pistons and two damping pistons;

5 shows a longitudinal section through a door closer according to the invention of a modified embodiment with two spring pistons and a damping piston; FIG. 6 shows a longitudinal section through a door closer according to the invention of a modified exemplary embodiment with two spring pistons and a damping piston with a larger diameter;

Figure 7 shows a longitudinal section through a combinable door closer according to the invention, consisting of two spring and damping components;

Figure 8 shows a longitudinal section through a combinable door closer according to the invention, each consisting of a spring and damping component and a spring component;

FIG. 9 shows a longitudinal section through a combinable door closer according to the invention, each consisting of a spring and damping component and a larger spring component;

FIG. 10 shows a longitudinal section through a door closer according to the invention, each consisting of a damping component and a spring component with coupling via toothed belts;

FIG. 11 shows a sectional end view of the exemplary embodiment from FIG. 10;

FIG. 12 shows a sectional end view of an exemplary embodiment with closer springs which are offset parallel to one another in the direction of the closer axis;

FIG. 13 shows a sectional end view of an exemplary embodiment with closer springs offset parallel to one another in a direction to the door plane;

FIG. 14 shows a sectional end view of an exemplary embodiment with closer springs arranged on opposite sides of the closer shaft.

Figure 1a shows a door leaf 101 of a revolving door, which is pivotally mounted on a stationary door frame by means of door hinges. The door leaf 101 has in its upper area a door closer 1, the housing 11 of the door closer 1 being arranged integrated in the profile of the door leaf 101. The door closer 1 has a closer shaft 2 emerging upwards from the housing 11. The closer shaft 2 is non-rotatably coupled to a slide arm linkage 95, which at its other end is slidably guided in a fixedly mounted slide rail 96 by means of a slide 97. The slide rail is preferably arranged integrated in the profile of the stationary door frame, so that the door closing device 1, 95, 96, 97 is arranged invisible to the viewer when the door leaf 101 is closed.

FIG. 1 shows a longitudinal section through a door closer 1 according to the invention for concealed installation in door leaves or door frames. For this purpose, the door closer 1 is received in a recess which is milled in the area of the upper edge of the door leaf or the lower edge of the door frame. The door closer 1 is a hydraulic door closer 1. The door closer has two separate closer springs 4a, 4b arranged in the door closer housing 11. The closer springs 4a, 4b are compressed when the wing is opened and serve as an energy store for the automatic closing of the wing. The closing process takes place under the action of a damping device which has two damping pistons 5a, 5b.

A closer shaft 2 is mounted approximately in the middle in the door closer housing 11. The closer shaft 2 is mounted in a bearing and the top 21 a and on the bottom 21 b of the door closer housing 11. The closer shaft 2 protrudes from the top of the housing 11. There, the closer shaft 2 is coupled to a force-transmitting linkage, the free end of which is supported in a rotary or sliding bearing which is fixed on the door frame or on the door leaf. A sliding arm linkage is preferably used as the force-transmitting linkage. It consists of a sliding arm that can be coupled in a rotationally fixed manner to the closer shaft and that is articulated with its free end to a slider that is guided in a sliding rail. The slide rail is in the concealed installation of the door closer in the upper lintel of the door frame or in Door leaf arranged concealed. The slide arm extends through the rebate area between the door leaf and frame.

Two cam disks 22a, 22b are non-positively or positively connected to the closer shaft 2. These cam disks 22a, 22b have symmetrically designed cam tracks in order to be able to use the door closer 1 in both right-hand and left-hand assembly. The two cam disks 22a, 22b are arranged offset from one another on the closer shaft 2. One Hubkun disc 22a, 22b is arranged in the upper region of the closer shaft 2 and the other cam disc 22a, 22b in the lower region of the closer shaft 2nd

In the embodiment shown, the housing of the door closer 1 has two piston chambers 12a, 12b of larger diameter and two piston chambers 13a, 13b of smaller diameter. One of the two larger piston chambers 12a is formed on the left side of the closer shaft 2 and the other piston chamber 12b is formed on the right side on the closer shaft 2. The left-side piston chamber 12a is formed in the upper housing area and the right-hand piston chamber 12b is formed in the lower housing area. The same applies in mirror image to the two smaller piston spaces 13a, 13b, so that a larger and a smaller piston space on the left and right of the closer shaft 2 face each other. All piston spaces 12a, 12b, 13a, 13b are arranged in the same sectional plane shown in FIG. 1 in the housing.

A spring piston 3a, 3b and a closer spring 4a, 4b and a device for adjusting the closing force 6a, 6b are accommodated in each of the two larger piston chambers 12a, 12b. The spring piston 3a, 3b is sealingly guided in the piston chamber 12a, 12b. As can be seen in FIG. 2, on the side of each spring piston 3a, 3b facing the closer shaft 2, a force transmission roller 31a, 31b is rotatably mounted on an axle bolt 32a, 32b and cooperates with one of the cam disks 22a, 22b. The two larger piston spaces 12a, 12b have a greater axial length than the two smaller piston spaces 13a, 13b. The resulting installation space 9a, 9b in connection with the two smaller piston spaces 13a, 13b can optionally also be used for the installation of additional devices. Such devices can be, for example, a locking device, an electromagnetic valve, a sensor device or the like. The installation space 9a, 9b can also be used for the installation of an additional spring piston with a closer spring, which can be hydraulically connected to one of the two larger piston spaces 12a, 12b.

In each of the two smaller piston spaces 13a, 13b, a sealingly guided damping piston 5a, 5b is received, which is acted upon by a return spring 55a, 55b in the direction of the closer shaft. On the side of the closing shaft 2 facing each damping piston 5a, 5b, a damping roller 51a, 51b is rotatably mounted on an axle bolt 52a, 52b (FIG. 3), which also interacts with one of the cam disks 22a, 22b. The rollers 31a, 31b, 51a, 51b each have a spring piston 3a, 3b and a damping piston 5a, 5b cooperate with the same lifting disc 22a, 22b. As with a conventional door closer 1, the closer springs 4a, 4b are tensioned when the door is opened manually and then cause the door to close hydraulically and damped. The bias of the closer springs 4a, 4b can be changed in the idle state via the closing force setting 6a, 6b. Such a device for setting the closing force 6a, 6b is described, for example, in DE 93 08 568.

In order to prevent the spring piston 3a, 3b from rotating and the resultant tilting of the force transmission roller 31a, 31b and the lifting disc 22a, 22b during the opening and closing process, the spring piston 3a, 3b has an anti-rotation device. For this purpose, the spring piston 3a, 3b and the piston chamber 12a, 12b are designed in two stages. The piston area of the spring piston 3a, 3b facing away from the closer shaft 2 has a larger diameter than the inner area facing the closer shaft 2. The piston chamber 12a, 12b is correspondingly complementary. However, the centers of the piston areas of larger diameter and smaller diameter are not concentric, but slightly offset from one another. The result of this is that the piston 3a, 3b can only be guided in the piston chamber 12a, 12b in a defined vertical orientation and that rotation is no longer possible.

Alternatively or additionally, a radial guide lug can also be formed on the piston as an anti-rotation lock and engage in a corresponding groove which extends axially in the cylinder wall. Or a piston rod can be attached to the piston as a guide rod, e.g. as a polygonal rod, which is positively guided in a corresponding complementary arrangement in the housing. Or the piston can be slidably guided on such a guide rod that is fixed in the housing.

The piston can also be designed with a non-circular cross-section and the cylinder interior in which the piston is guided is correspondingly complementary, e.g. oval or polygonal, e.g. have a triangular cross section.

As shown in FIGS. 2 and 3, the two smaller piston spaces 13a, 13b are hydraulically coupled to one another. The hydraulic flow takes place via an inlet 7e in the lower left pressure-side piston chamber 13b and a horizontal channel 7a into an annular groove 71 in the cover of the lower bearing 22b of the closer shaft 2. In the annular groove 71, the hydraulic fluid is passed around the closer shaft 2 and opens on the opposite side of the bearing 22b in the continuation of the horizontal channel 7b. The hydraulic fluid then reaches an upper horizontal channel 7d via a vertical channel 7c which is not in the sectional plane and opens into the upper pressure-side piston chamber 13a for an inlet 7g.

As can be seen from FIG. 3, a damping valve 81 and an end stop valve 82 are arranged in the upper horizontal channel 7d. Via the inlet 7g, the damping valve 81 and the horizontal channel 7d is the pressure side part of the Piston chamber 13a connected to the unpressurized part of the piston chamber 13a. The unpressurized part of the piston chamber 13a is open towards the receiving chamber of the closer shaft 2, in which the horizontal channel 7d opens in the area of the upper bearing 21a.

When the door is opened, the upper spring piston and the upper damping piston 5a move to the left and the lower spring piston and the lower damping piston 5b to the right. The damping pistons 5a, 5 are acted upon by the return springs 55a, 55b. Hydraulic fluid is exchanged directly between unpressurized and pressure-side piston chamber 13a via the check valve 83 arranged in the upper damping piston 5a. Upper and lower damping pistons 5a, 5b are in fluid exchange on the one hand via the hydraulic line 7a, 7b, 7c, 7d and also on the receiving space of the closer shaft.

When the door is closed, the upper spring piston and the upper damping piston 5a move to the right and the lower spring piston and the lower damping piston 5b to the left. Hydraulic fluid is exchanged via the inlet 7g, the damping valve 81 and the horizontal channel 7d between the pressure-side part of the piston chamber 13a and the unpressurized part of the piston chamber 13a. The closing movement of the door is hydraulically damped by the damping valve 81, and the return springs 55a, 55b are compressed. At a certain closing angle of the door, the inlet 7f connected to the end stop valve 82 comes into connection with an annular groove 53 in the damping piston 5a. Hydraulic fluid then flows via a control bore 54 in the damping piston 5a bypassing the damping valve 81 via the end stop valve 82 from the pressure-side piston chamber 13a into the unpressurized piston chamber 13b. The door then carries out the so-called end stop.

Due to the hydraulic coupling of the upper and lower piston chambers 13a, 13b, there is only one valve for adjusting the damping pistons Damping 81 and only one valve required to set the end stop 82. Instead of the check valve 83 arranged in the upper damping piston, a pressure relief valve, not shown, is arranged in the lower damping piston. The pressure relief valve prevents damage to the hydraulic system when the door is forced to close manually.

Figures 4 to 6 show a door closer modified compared to the previous embodiment. The damping pistons 5a, 5b are arranged coaxially on the same side of the closer shaft 2 as the respectively associated spring pistons 3a, 3b, spring pistons 3a, 3b and damping pistons 5a, 5b each being guided in separate piston chambers 12a, 12b, 13a, 13b which are sealed off from one another the spring piston 3a, 3b are each connected to the damping piston 5a, 5b by means of a piston rod 10a, 10b. The central axes of the piston chambers 12a, 12b, of the spring pistons 3a, 3b lie vertically one above the other. The piston rod 10a, 10b is sealingly guided between the spring piston chamber 12a, 12b and the damping piston chamber 113a, 13b. A slide 33a, 33b is mounted on the spring piston 3a, 3b, which carries two power transmission rollers 31a, 31b, 31c, 31d; the cam disc 22a, 32b is arranged between two power transmission rollers 31 a, 31 b, 31c, 31 d. In Figure 4, the door closer is constructed symmetrically. The exemplary embodiment according to FIG. 5 differs from this in that there is only one damping piston 5a, which dampens the movement of both spring pistons 3a, 3b. In the exemplary embodiment according to FIG. 6, the damping piston has a larger diameter.

The exemplary embodiments in FIGS. 7 to 9 are modified in that the central axes of the piston spaces 12a, 12b, 13a, 13b are collinear. Furthermore, separate housings 11a, 11b, 11c are coupled to one another, the end faces of the housings 11a, 11b, 11c to be coupled to one another each being open. The closer shaft 2a, 2b carries above the cam disc 22a, 22b a gear 17a, 17b which meshes with a central gear 19 mounted on a shaft 18 in the housing 11c. The shaft 18 is mounted in the middle housing 11 c by means of a bearing 20. The linkage, not shown here, is ner of the closer shafts 2a, 2b attachable. A rotation of the one closer shaft 2a, 2b during the opening movement of the door leaf causes the other closer shaft 2b, 2a to rotate in the same direction via the toothed wheels 17a, 17b, 19.

In FIG. 7, two identical spring and damping components 40 are connected to one another. The spring and damping components 40 each represent a separately functioning, hydraulically damped door closer. In FIGS. 8 and 9, a spring and damping component 40 is coupled to a spring component 42, the spring component 42 in FIG. 9 being longer than the spring component 42 shown in FIG. 8 is trained. The spring component has no hydraulic damping, so that the damping device of the spring and damping component 40 is associated with the damping of the closing movement of all closer springs 4a, 4b.

The exemplary embodiments in FIGS. 10 and 11 show a further modular door closer 1. The spring component 42 has two spring piston chambers 12a, 12b, which are offset parallel to one another in the direction of the closer axis 2a and in which - not shown here - each a spring piston with a closer spring supported thereon is. The arrangement of the spring piston chambers 12a, 12b and the associated lifting disc 22a, 22b arranged on the closer shaft 2a corresponds to the arrangement shown in FIGS. 1 and 2. A damping component 41 is then arranged axially on the end face of the housing 11a of the spring component 42, the housing 11b of which preferably has the same cross section as the housing 11a of the spring component 42. A further closer shaft 2b is rotatably mounted in the housing 11b of the damping component 41. On the further closer shaft 2b, a cam disc 22c is fastened in a rotationally fixed manner, a damping piston, not shown here, which is guided in the damping piston chamber 13 of the housing 11b of the damping component 41 cooperating with the cam disc 22c, as shown in FIGS. 1 and 2. A toothed belt 69 is provided as a gear for coupling the components 41, 42, the toothed belt 69 interacting with pulleys 70 mounted on the closer shafts 2a, 2b and the rod 73 with gear wheels 17a, 17b mounted on the closer shafts 2a, 2b. The toothed belt 69 is thus guided above the housing 11 a, 11 b, the toothed belt 69 being guided within the housing 11 a, 11 b in corresponding housing channels 72.

FIGS. 12 to 14 show sectional end views of door closers 1, each with two closer springs arranged in separate spring piston chambers 12a, 12b, each with a different arrangement of the spring piston chambers 12a, 12b from one another. A closer shaft 2 is rotatably supported in the door closer housing 11. The transmission between the closer shaft and the spring piston is designed as described in the previous exemplary embodiments and, like the closer springs and spring pistons, is not shown here. FIG. 12 shows a sectional front view of a door closer with closer springs offset parallel to one another in the direction of the closer axis. FIG. 13 shows a sectional front view of a door closer with closer springs offset parallel to one another in one direction to the door plane. FIG. 14 shows a sectional front view of a door closer with closer springs arranged on opposite sides of the closer shaft.

Other exemplary embodiments - not shown here - can alternatively or additionally provide for the coupling of further components, for example fixing or drive components, and the universal combination of the components; For example, the required closing force can be achieved by the preferably axial alignment of spring components. There are also various possibilities with regard to the coupling of the output shafts, for example coupling via a pull rope, chain or push rod. List of reference numbers

Door closer 13 damping piston chamber

Closer shaft 13a damping piston chamber a closer shaft 13b damping piston chamber b closer shaft 16a bearing a spring piston 16b bearing b spring piston 17a gear wheel a closer spring 17b gear wheel b closer spring 18 shaft a damping piston 19 gear wheel b damping piston 20 bearing a closing force setting 21a upper bearing b closing channel horizontal 21 bearing force setting b Stroke cam b horizontal hydraulic channel 22b lifting disc c vertical hydraulic channel 22c lifting disc d horizontal hydraulic channel 31a power transmission roller e inlet bore 31b power transmission roller f inlet bore 31 c power transmission roller le g inlet bore 31 d power transmission roller le a installation space 32a axle pin b installation space 32b piston rod 0b 33b slide 1 door closer housing 40 spring and damping component 1a door closer housing

41 Damping component 1 b door closer housing 2a 42 spring component

Spring piston chamber 2b 51a damping roller

Spring piston chamber b Damping roller 81 b Damping valve a Axle pin 82 End stop valve b Axle pin 83 Check valve

Ring groove 83a check valve

Control bore 83b check valve a return spring 95 slide arm b return spring 96 slide rail

Ring channel 97 slider

Housing channel 101 door leaf

Damping valve a damping valve

Claims

Expectations 1. Drive (1) for a wing of a door, a window or the like, with a drive housing (11), preferably for concealed installation in a door leaf (101) or in a door frame, with at least two arranged in the drive housing (11) Normally open springs (4a, 4b), which are acted upon when opening or closing the leaf (101) and are designed as energy stores for automatically closing or opening the leaf (101), each of the at least two closer springs (4a, 4b) on a separate one spring piston (3a, 3b) arranged in the drive housing (11) is supported with a damping device (5a, 5b, 6a, 6b, 7a, 7b, 7c, 7d, 7e, 7f, 7g, 13) arranged in the drive housing (11) 13a, 13b) for damping the closing and / or opening movement of the leaf (101), preferably hydraulic damping device (5a, 5b, 6a, 6b, 7a, 7b, 7c, 7d, 7e, 7f, 7g, 13, 13a, 13b ), with an A arranged in the drive housing (11) drive element, preferably closer shaft (2), which with the energy store (4a, 4b) and / or with the damping device (5a, 5b, 6a, 6b, 7a, 7b, 7c, 7d, 7e, 7f, 7g, 13, 13a, 13b) cooperates, preferably with a force-transmitting linkage (95), which is supported on the one hand in a rotary or sliding bearing (97) and on the other hand is connected to the output member (2), for example as a slide arm linkage (95) or as a scissor arm linkage or as Telescopic arm linkage formed, the output member (2) preferably interacts via a gear with the at least two spring pistons (3a, 3b) arranged in the housing (11), the gear as a cam disc (22a, 22b) and / or pinion and / or crankshaft drive and / or hydraulic Gear is formed, and it is provided that two or more spring pistons (3a, 3b), on each of which at least one of the closer springs (4a, 4b) is supported, in the direction of the closer axis (2) and / or in a direction parallel to Door plane are arranged offset parallel to each other and / or that two or more spring pistons (3a, 3b), on each of which at least one of the closer springs (4a, 4b) is supported, are arranged on opposite sides of the closer shaft (2). 2. Drive according to claim 1, so that the offset in the direction of the closer axis (2) between the spring pistons (3a, 3b) is smaller than the diameter of the associated piston chambers (12a, 12b). 3. Drive according to claim 1 or 2, so that the spring cams (3a, 3b) interact with closer springs (4a, 4b) of different diameters and / or different lengths and / or different spring constants. 4. Drive according to claim 3, so that at least one closer spring (4a, 4b) interacts with a device (6a, 6b) for adjusting the spring force. Drive according to one of claims 3 or 4, so that the closer spring (4a, 4b) and / or the spring piston (3a, 3b) can preferably be hydraulically locked in an open position of the door (101) . 6. Drive according to one of the preceding claims, so that at least one, preferably two or more damping pistons (5a, 5b) are formed separately from the spring pistons (3a, 3b). 7. Drive according to claim 6, so that the spring piston (3a, 3b) has a different, preferably larger diameter than the damping piston (5a, 5b). 8. Drive according to one of claims 6 or 7, so that the piston chamber (12a, 12b) of the spring piston (3a, 3b) has a different, preferably greater axial length than the piston chamber (13a , 13b) of the damping piston (5a, 5b). 9. Drive according to one of claims 6 to 8, so that at least one spring piston (3a, 3b) and at least one damping piston (5a, 5b) are arranged on opposite sides of the closer shaft (2) are. 10. Drive according to one of claims 6 to 9, so that at least one spring piston (3a, 3b) and at least one damping piston (5a, 5b) are each on the same side of the closer shaft (2). are preferably nested and / or interlocking. 11. Drive according to one of claims 6 to 10, so that the damping piston (5a, 5b) is designed to be hydraulically lockable. 12. Drive according to one of claims 6 to 11, so that the piston chambers (13a, 13b, 12a, 12b) of the damping pistons (5a, 5b) and / or spring pistons (3a, 3b) are hydraulically coupled via hydraulic channels (7a, 7b, 7c, 7d, 71). 13. Drive according to one of claims 6 to 12, so that to adjust the damping and / or the hydraulic end stop for several damping pistons (5a, 5b) and / or spring pistons (3a, 3b) only one valve (81, 82) is provided in each case. 14. Drive according to one of claims 6 to 13, so that a damping piston (5a) has a check valve (83) and another damping piston (5b) has a pressure relief valve (84). 15. Drive according to one of claims 6 to 14, so that for the hydraulic coupling of damping pistons (5a, 5b) arranged on both sides of the closer shaft (2), an annular channel (71) in the bottom bearing (21b ) of the closer shaft (2), preferably in a housing cover accommodating the bearing (21b). 16. Drive according to one of the preceding claims, d a d u rch g e ke n nze i ch n et that on the closer shaft (2) two or more cam disks (22a, 22b) are arranged one above the other. 17. Drive according to claim 16, so that the cam disks (22a, 22b) are designed to be mirror-symmetrical to their longitudinal axis. 18. Drive according to claim 16 or 17, so that at least two cam disks (22a, 22b) are of identical design. 19. Drive according to one of the preceding claims, dadu rch ge ke n nze i ch n et that on the closer shaft (2) two or more pinions are arranged one above the other. 20. Drive according to one of the preceding claims, d a d u rch g e k n nze i ch n e t that at least one pinion (17a, 17b) and at least one cam disc (22a, 22b) are arranged one above the other on the closer shaft (2). 21. Drive according to one of claims 16 to 20, so that the cam disc (22a, 22b) and / or the pinion (17a, 17b) is designed so that there is an increasing opening angle the closer shaft (2) decreases the transmission ratio between the movement of the spring piston (3a, 3b) and the rotation of the closer shaft (2). 22. Drive according to one of the preceding claims, that the closer shaft (2) is formed axially in two parts within the housing (11). 23. Drive according to one of claims 16 to 22, so that a spring piston (3a, 3b) and a damping piston (5a, 5b) interact with the same cam disc (22a, 22b), wherein the interaction preferably takes place via a force transmission roller (31a, 31b) or damping roller (51a, 51b). 24. Drive according to claim 23, thus ensuring that between the spring piston (3a, 3b) and the cam disc (22a, 22b) and / or between the damping piston (5a, 5b) and the cam disc (22a, 22b) and / or a transmission gear is arranged between the two cam discs (22a, 22b). 25. Drive according to claim 24, so that the transmission gear is designed as a gear transmission and / or as a hydraulic transmission. 26. Drive according to one of the preceding claims, so that the drive housing (11) is designed as a multi-part housing, the drive housing (11) having at least one basic housing body in which the closer shaft (2) is mounted is, and at least one further housing component, for example is designed as a spring housing. 27. Drive according to the preamble of claim 1, so that the spring piston (3a, 3b) and the damping piston (5a, 5b) are connected to one another, preferably by a piston rod (10, 10a, 10b ) or the like, the spring piston (3a, 3b) and the damping piston (5a, 5b) moving in the same direction when the closer shaft (2, 2a, 2b) rotates. 28. Drive according to claim 27, so that the spring piston (3a, 3b) and the damping piston (5a, 5b) in separate piston chambers (12a, 12b, 13a, 13b), preferably sealed against one another are guided, the piston rod being guided between the piston chambers (12a, 12b, 13a, 13b) by means of a preferably sealing guide (16a, 16b). 29. Drive according to the preamble of claim 1, so that the force transmission rollers (31a, 31b, 31c, 31d) are mounted on the slide (33a, 33b) in such a way that the cam disc (22a , 22b, 22c) is arranged between at least two opposing force transmission rollers (31a, 31b, 31c, 31 d), the opposing force transmission rollers (31a, 31b, 31c, 31 d) being in each rotational position of the cam disc (22a, 22b, 22c) are in contact with the lifting disc (22a, 22b, 22c).