EP2725176A2 - Door closer - Google Patents

Abstract

The closer (100) has a pinion shaft (104) on which a cam disk (103) is arranged in a rotationally fixed manner and a pressure roller (101). A closing spring (102) forces the pressure roller against a roll-off surface of the cam disk by an operative connection (106, 111, 107). The roller is arranged relative to an axial centre of the pinion shaft in such a way the pressure roller, when a door leaf of a conventional door coupled to the pinion shaft is opened or closed, is moved along a trajectory. The trajectory runs past the axial centre of the pinion shaft and the run-off surface of the disk.

Description

The invention relates to a cam mechanism based on a door closer.

Door closers with cam mechanism typically have a Hubkurvenscheibe rotatably mounted on an output shaft, which has a drainage surface on which a pressure roller unrolled pressed due to a closing spring.

Due to the shape of the drainage surface, the course of the torque applied to the driven rotary vane during a closing movement, i. H. the resulting torque curve is determined.

The Hubkurvenscheibe seen in the direction of a longitudinal extension of the output shaft of the door closer may have a symmetrical or asymmetrical cross-sectional shape.

The pressure roller is mounted so that it can move on the Hubkurvenscheibe to and from her. The movement takes place in the direction of the axis of rotation of the output shaft and away from it.

The torque curve is determined by the shape of the respective running surface of the Hubkurvenscheibe. This means that the cam disc must be specially designed, ie designed, for each application.

In cross-section symmetrically shaped Hubkurvenscheiben cause slide rail operation a different torque curve than in a normal or scissor linkage both in magnitude and in the course.

However, in order to use one and the same door closer for both modes of operation, the torque curves must be substantially the same.

For this purpose, asymmetric cam discs have been developed whose two drainage surface halves are designed for one operating mode. The course of the respective torque curve defined by the shape of the run-off surfaces can not be changed.

If now a door provided with a door closer door are provided with a fire protection function, are in a predetermined first opening angle range (about 0 ° - 4 °) of a rotary wing and in a predetermined second opening angle range (about 88 ° - 92 °) of the rotary vane torques permitted only within predetermined limits. In addition, there is a minimum torque that must not be exceeded over the entire opening angle range of the rotary wing.

The only known way to change the torque on the rotary wing are mechanisms for adjusting the bias of the closing spring. Such mechanisms usually comprise an adjusting screw by means of which the position of a closer spring stop can be changed. Thus, the size of the torque can be changed in a substantially constant ratio. The shape of the torque curve remains unchanged.

Are a torque at an opening angle of 0 °, d. h, with the revolving wing closed, too high and a final torque, d. H. a torque at a maximum opening angle of for example 90-100 °, only slightly larger than a permissible minimum torque, could be reduced by means of an adjustment of the closing spring bias while the torque at an opening angle of 0 °, but at the same time the final torque below the allowable minimal torque fall. Switching to a fire protection function would therefore be impossible. Replacing a door closer with a completely new one adds up to enormous costs.

The object of the invention is to provide a door closer, which can be manufactured inexpensively adapted to the particular application or even adapted or converted in the assembled state to the particular application.

The object is solved by the subject matter of patent claim 1. Advantageous developments are specified in the subclaims.

According to the invention, a door closer has a pressure roller, which rolls pressed against a cam disc of the door closer. The Hubkurvenscheibe is arranged rotatably on an output shaft. The pressure roller is arranged with respect to an axial center of the output shaft so that the pressure roller is moved along a path upon opening or closing of a coupled with the output shaft rotary vane. Characterized in that the web passes by the axial center of the output shaft, and due to the design of the running surface of Hubkurvenscheibe is at a respective opening angle of the rotary vane at different modes of the door closer to the output shaft in each case a very similar or identical torque. Ie. in one mode a curve of a voltage applied to the rotary vane, dependent on the opening angle of the rotary vane torque curve is achieved, which is identical or very similar to a torque curve in another mode.

The torque curve is a characteristic of a voltage applied to the output shaft of the door closer torque in dependence on the opening angle of the rotary wing.

The advantage is that not only is the torque variable in proportion, but it is also possible to change the shape of the torque curve during a movement, i. H. a closing movement of a rotary wing, despite using a Hubkurvenscheibe with one and the same shape to adapt to the particular application.

As a result, a single door closer can be used in different modes. According to the invention, these operating modes include slide rail operation and normal or scissors linkage operation, and preferably additionally parallel linkage operation.

It has been shown that due to the rearrangement of the pressure roller, the torque curves in slide rail operation and normal rod operation, especially when using a symmetrically designed Hubkurvenscheibe can be matched to each other.

The described torque curve approximation results in particular in a lintel mounting of the door closer according to the invention in slide rail operation on a tape opposite side or in normal linkage operation on a hinge side. The same effect results in particular in a door leaf assembly of the door closer according to the invention Sliding rail operation on the belt side or in normal linkage operation on the opposite side of the belt.

In addition, adaptation to different EN classes is possible. Ie. one and the same door closer can be used for various closing scenarios and with different blade weights, which requires less diversely designed door closers. This leads to a reduction in manufacturing costs.

In addition, it is possible to change not only the degree of torque increase but possibly even to change the increase so that the torque, for example, does not drop at the beginning but increases (from a lower torque at an opening angle of 0 °).

In addition, can be done by such an adjustment, a fall compensation, so that a mounting on both the hinge side and on the opposite hinge side is possible. Furthermore, such trained door closers can be used with different door geometries.

Are the output shaft and the housing of the door closer according to the invention designed so that the output shaft can be operatively connected at both ends with a rotary wing, the door closer is also applicable to both DIN-right and DIN-left swing doors. For this purpose, the housing in the region of the drive shaft ends in each case has a passage opening, which is optionally provided by means of a cover cap, so that the unused end of the output shaft is concealed to the outside.

Furthermore, it can be provided that the pressure roller is not fixed in relation to the Hubkurvenscheibe in their position. Ie. during a rotation of the Hubkurvenscheibe this moves the pressure roller to a predetermined position. The position reached then corresponds to the position at which the desired torque curve is achieved. Preferably, the adjustment takes place in a symmetrical Hubkurvenscheibe with respect to the axis of symmetry. This can be done by the pressure roller is arranged displaceably in a direction transversely or at an angle between 0 ° and less than 90 ° to the above-described movement path of the pressure roller.

In addition, the invention provides, vorzuverdrehen the Hubkurvenscheibe. This makes it possible to match the torque at an opening angle of 0 ° in the aforementioned modes to each other.

In addition, it has proven to be advantageous in the normal linkage to vary the distance of the axial center of the output shaft of the door closer to the rotation point of a rotary wing and / or the distance of the axial center of the output shaft of the door closer to the articulation point of the normal linkage on the rotary wing. With increasing distance to the rotation point of the rotary wing, the maximum opening angle and the leverage change. Due to these variations, it is possible to change the torques in a predetermined ratio. For example, the ratio of torque at an opening angle of 0 ° to end torque and due to the adjustment of the maximum opening angle, the torque curve can be changed. It has proved particularly advantageous if the distance to the articulation point of the normal linkage is equal to or greater than the distance to the rotation point of the rotary vane.

According to the Hubkurvenscheibe is symmetrical and preferably has a heart-shaped cross-sectional area. This has cost advantages compared to an asymmetric cam disc. On the one hand, the shape of only one half of the running surface of the Hubkurvenscheibe to calculate and thus construct. Furthermore, fewer different drain surface shapes are required, which reduces the variety of Hubkurvenscheiben to be used and thus to manufacturing tools.

Alternatively or additionally, the door closer according to the invention is designed so that the direction of the movement path of the pressure roller in the assembled state of the door closer can be adjusted. This makes it possible, the door closer in the assembled state, d. H. on site, still to adapt to any peculiarities of the opening or closing process. In addition, this makes it possible to provide the door closer with a new function in retrospect or, for example, switch from slide rail operation to normal linkage or parallel linkage operation or vice versa.

Ie. one and the same door closer is universally applicable. The manufacturing costs are reduced because with fewer types of door closers, a variety of automatic functions, such as fire protection function, can be realized.

Alternatively or additionally, it is provided to mount the arrangement consisting of at least one pressure roller and a closing spring rotatable and lockable, wherein the rotation point is not the axial center of the output shaft of the door closer.

In addition or instead of the rotary bearing arrangement, the arrangement can be mounted as a whole displaceable.

Further features and advantages of the invention will become apparent from the following description of preferred embodiments.

Figur 1A:

ein Diagramm, das den Verlauf eines Kraftübersetzungsverhältnisses einer Hubkurvenscheibe bei einem herkömmlichen Nockenmechanismus in Abhängigkeit von einem Öffnungswinkel zeigt,

Figur 1B:

zwei Diagramme, die den Verlauf des Kraftübersetzungsverhältnisses bzw. eines Drehmoments in Abhängigkeit vom Öffnungswinkel bei einem herkömmlichen Nockenmechanismus im Gleitschienen-Betrieb zeigen,

Figur 1C:

zwei Diagramme, die den Verlauf des Kraftübersetzungsverhältnisses bzw. des Drehmoments in Abhängigkeit vom Öffnungswinkel bei einem herkömmlichen Nockenmechanismus im Normalgestänge-Betrieb zeigen,

Figur 1D:

zwei Diagramme, die Drehmomentverläufe beim Öffnen und Schließen eines Drehflügels bei einem herkömmlichen Nockenmechanismus zeigen,

Figur 1E:

zwei Diagramme, die Drehmomentverläufe beim Öffnen und Schließen eines Drehflügels bei einem Nockenmechanismus zeigen, wobei die Andrückrolle erfindunggemäß versetzt ist,

Figur 1F:

ein Diagramm, das Verläufe von Drehmomenten in Abhängigkeit vom Öffnungswinkel bei einem Nockenmechanismus im Normalgestänge-Betrieb bei verschiedenen Positionen der Andrückrolle zeigt,

Figuren 2A - 2C:

einen Türschließer mit einer Hubkurvenscheiben-Anordnung gemäß einer ersten Ausführungsform der Erfindung in verschiedenen Varianten,

Figuren 3A, 3B:

einen Türschließer mit einer Hubkurvenscheiben-Anordnung gemäß einer zweiten Ausführungsform der Erfindung in verschiedenen Varianten,

Figur 4:

einen Türschließer mit einer Hubkurvenscheiben-Anordnung gemäß einer dritten Ausführungsform der Erfindung,

Figur 5:

einen Türschließer mit einer Hubkurvenscheiben-Anordnung gemäß einer vierten Ausführungsform der Erfindung,

Figur 6:

eine Vorrichtung zun Einstellen der Bewegungsrichtung einer Andrückrolle in Bezug auf eine Hubkurvenscheibe gemäß einer ersten Ausführungsform der Erfindung,

Figuren 7A - 71:

eine Vorrichtung zum Einstellen der Bewegungsrichtung einer Andrückrolle in Bezug auf eine Hubkurvenscheibe gemäß einer zweiten Ausführungsform der Erfindung in verschiedenen Varianten,

Figur 8:

eine Vorrichtung zum Einstellen der Bewegungsrichtung einer Andrückrolle in Bezug auf eine Hubkurvenscheibe gemäß einer vierten Ausführungsform der Erfindung,

Figuren 9A - 9D:

eine Vorrichtung zum Einstellen der Bewegungsrichtung einer Andrückrolle in Bezug auf eine Hubkurvenscheibe gemäß einer fünften Ausführungsform der Erfindung in verschiedenen Varianten,

Figur 10:

einen Mechanismus zum Lösen einer Andrückrolle von einer Hubkurvenscheibe gemäß einer Ausführungsform der Erfindung und

Figuren 11A, 11B:

Vorrichtungen zum Arretieren einer Einstellschraube gemäß einer Ausführungsform der Erfindung.

Show it:

FIG. 1A

a diagram showing the curve of a power transmission ratio of a Hubkurvenscheibe in a conventional cam mechanism in response to an opening angle,

FIG. 1B

two diagrams showing the course of the power transmission ratio or a torque as a function of the opening angle in a conventional cam mechanism in slide rail operation,

FIG. 1C:

two diagrams showing the course of the power transmission ratio or the torque as a function of the opening angle in a conventional cam mechanism in the normal rod operation,

FIG. 1D:

two diagrams showing torque curves when opening and closing a rotary vane in a conventional cam mechanism,

FIG. 1E:

two diagrams showing torque curves when opening and closing a rotary vane in a cam mechanism, wherein the pressure roller is offset according to the invention,

FIG. 1F:

a diagram showing curves of torques as a function of the opening angle in a cam mechanism in normal linkage operation at different positions of the pressure roller,

FIGS. 2A-2C:

a door closer with a Hubkurvenscheiben arrangement according to a first embodiment of the invention in different variants,

FIGS. 3A, 3B:

a door closer with a Hubkurvenscheiben arrangement according to a second embodiment of the invention in different variants,

FIG. 4:

a door closer with a Hubkurvenscheiben arrangement according to a third embodiment of the invention,

FIG. 5:

a door closer with a Hubkurvenscheiben arrangement according to a fourth embodiment of the invention,

FIG. 6:

a device for adjusting the direction of movement of a pressure roller with respect to a Hubkurvenscheibe according to a first embodiment of the invention,

FIGS. 7A-71:

a device for adjusting the direction of movement of a pressure roller with respect to a Hubkurvenscheibe according to a second embodiment of the invention in various variants,

FIG. 8:

a device for adjusting the direction of movement of a pressure roller with respect to a Hubkurvenscheibe according to a fourth embodiment of the invention,

FIGS. 9A-9D:

a device for adjusting the direction of movement of a pressure roller with respect to a Hubkurvenscheibe according to a fifth embodiment of the invention in various variants,

FIG. 10:

a mechanism for releasing a pressure roller from a Hubkurvenscheibe according to an embodiment of the invention and

FIGS. 11A, 11B:

Devices for locking an adjusting screw according to an embodiment of the invention.

In Figure 1A is schematically illustrated, which course has a force translation i _cam in a symmetrically shaped Hubkurvenscheibe a conventional cam mechanism 'in response to an opening angle φ of a rotary wing. At an opening angle φ of 0 ° is the force transmission ratio i _cam is substantially equal to 1, after which the force transmission ratio i _cam falls within a relatively small opening angle range relatively steeply to a lower minimum value and then rises again.

When such a cam mechanism is combined with a slide rail, a power transmission curve according to the left-hand diagram in FIG FIG. 1B , At an opening angle φ of 0 °, the force transmission i _{cam is} about 1.5 and then falls initially similar to a downwardly open Parabola off. At an opening angle φ of 0 °, the negative slope of the curve is initially relatively small and increases with increasing opening angle φ. In an opening angle range of about 80-90 °, the power transmission curve has the largest drop, ie the largest negative increase. After that, this negative increase decreases. The resulting torque curve is right in FIG. 1B shown. It has a similar course to the force transmission curve,

If the same cam mechanism is combined with a normal linkage, a force transmission curve according to the left-hand diagram in FIG Figure 1C , Unlike the in FIG. 1B shown power transmission curve is the force transmission i _cam here at an opening angle φ of 0 ° much higher, it may have a value between 3-7 or even tend to near infinity. After that, the force transmission i _cam falls off similar to an upwardly open parabola. The negative increase in the power transmission curve is steadily decreasing. The resulting torque curve is right in Figure 1C shown. The torque M is at the beginning, ie at an opening angle φ of 0 °, relatively high and is about 3 - 4 Nm. Thereafter, the torque falls very sharply within a very small opening angle range and approaches a lower, minimum value. The setting of a door rest position (opening angle φ in a range of about 0 °) is thereby extremely difficult. Small changes in the opening angle φ cause a large change in the torque M.

In order to achieve that the torque curves in slide rail operation and normal rod operation with one and the same cam disc are substantially equal or similar and preferably substantially correspond to the torque curve in slide rail operation, it is provided to arrange the pressure roller off-center. This means, in that the pressure roller is movable with respect to the cam disc along a path in which a direction of movement of the pressure roller does not intersect at any point of the track the axial center of the cam disc.

In FIG. 1D two diagrams are shown, indicating the torque curves for a cam mechanism with conventionally arranged pressure roller in Gleitschienen- or normal rod operation. The respective upper characteristic curve indicates the torque curve during an opening process, and the lower characteristic curve shows the torque curve during a closing operation. The differences between these characteristics are due to the fact that the opening takes place against the force of a closing spring. As can be seen, the torque M at an opening angle φ of 0 ° when opening in normal linkage operation is much higher (about 162 Nm) than in slide rail operation (about 111 Nm). When closing the torque M is at an opening angle φ of 0 ° in normal linkage operation about 81 Nm and at Gleitschienen-operation about 55 Nm. The differences of the torques M in the two operating modes to each other consequently amount to about 51 Nm or 26 Nm. Furthermore, the torque curve at normal start-up operation falls significantly steeper at the beginning than the torque curve at slide rail operation. The torque curves thus have different gradients.

Figure 1E shows torque curves, which are achieved when a pressure roller is arranged according to the invention. In normal linkage operation, the torque M at an opening angle φ of 0 ° when opening is about 142 Nm and when closing about 70 Nm. In slide rail operation, the torque M at an opening angle φ of 0 ° when opening is about 143 Nm and when closing about 71 Nm. The differences of the torques M in the two operating modes to each other are only about 1 Nm, thus are in a range between 0.7% and 1.5% with respect to a respective reference torque in one mode. In addition, it can be seen that the torque curve in normal rod operation at an opening angle φ of 0 ° does not drop as steep as in Figure 1E , Rather, the shapes of the torque curves, so the torque curves in the two modes are approximated.

As a result, the torques M in the mentioned modes are identical or very similar at a respective opening angle φ. The difference of the torque values at a respective opening angle φ in the operating modes relative to one another preferably lies in a range of at most 10%, preferably 5% or less with respect to one of the applied torques in one of the operating modes. By matching the torque curves, it is also achieved that the force required to open a rotary vane in the operating modes is approximately the same.

As exemplified in Figure 1F shown, due to the displacement of the pressure roller 101, the torque M at an opening angle φ of 0 ° can not only be increased. It is also possible to make the torque M at an opening angle φ of 0 ° lower than the average torque applied during a moving operation of a rotary vane.

In a conventional arrangement of a pressure roller 101, as in the lower left in Figure 1F 1, a torque curve shown in the diagram by means of a solid line is achieved, in both directions of rotation of a cam disc 103 indicated on the bottom left. The pressure roller 101 is arranged in such a way that it can move through a direction of movement R _B defined trajectory of the pressure roller 101, the axial center of an output shaft 104 intersects. The pressure roller is thus centric with respect to the output shaft 104, a so-called eccentricity e is equal to 0.

An offset of the pressure roller, as in the middle below in Figure 1F shown causes when rotating the Hubkurvenscheibe 103 along a first, according to Figure 1F upper run-surface section of Hubkurvenscheibe 103 in a direction which is indicated by a dashed arrow, a torque curve according to the dashed line in the graph shown characteristic. In the case, a torque M is increased at an opening angle φ of 0 °. A displacement amount of the pressure roller 101 according to FIG Figure 1F with respect to this direction of rotation of Hubkurvenscheibe 103 represents a so-called positive eccentricity (e> 0). Rotation direction is preferably used in slide rail operation.

When rotating the Hubkurvenscheibe 103 along the other, according to Figure 1F bottom running surface portion of the Hubkurvenscheibe 103 in a direction indicated by an arrow, which is represented by a dash-dotted line, a torque curve is achieved according to the characteristic in the diagram, which is represented by a dash-dot line. In the case, the torque M is reduced at an opening angle φ of 0 °. The displacement amount of the pressure roller 101 according to Figure 1F with respect to this direction of rotation represents a so-called negative eccentricity (e <0).

A door closer 100 according to a first embodiment of the invention has, as in FIGS. 2A-2C shown, a pressure roller 101, which is pressed by means of a closing spring 102 against a Hubkurvenscheibe 103 is arranged rotationally fixed on an output shaft 104 of the door closer 100.

The pressure roller 101 is arranged so that a line defined by its substantially translational movement passes the axial center of the output shaft 104.

As in FIG. 2A shown, the shutter spring 102 is disposed on one side of the Hubkurvenscheibe 103, on which the pressure roller 101 is arranged. The closing spring 102 presses the pressure roller 101 against the Hubkurvenscheibe 103 via an operative connection in the form of a connecting rod 111. The connecting rod 111 is guided in a guide 105 so that it is only translationally on the Hubkurvenscheibe 103 to or away from it. A force of the closing spring 102 thus acts in the + x coordinate direction.

Alternatively, the shutter spring 102, as in FIG. 2B shown to be disposed on a side of Hubkurvenscheibe 103, which is opposite to the side on which the pressure roller 101 is arranged. The closer spring 102 is coupled to the pressure roller 101 facing the end with a flap carriage 106. The flap carriage 106 has at least one connecting rod 111 and a tab 114 and extends in the x-coordinate direction. The flap truck 106 passes the Hubkurvenscheibe 103 at a predetermined distance. The pressure roller 101 is mounted freely rotatably in the tab 114. The force of the closing spring 102 acts in the -x coordinate direction. The pressure roller 101 is analogous with respect to the Hubkurvenscheibe 103 FIG. 2A arranged.

The flap truck 106 may also, as in Figure 2C shown to be designed so that the at least one connecting rod 111 in an xz plane When viewed in the x-coordinate direction, the cam disk 103 passes laterally. The pressure roller 101 is analogous with respect to the Hubkurvenscheibe 103 FIG. 2A arranged.

At an in FIG. 3A shown door closer 100 according to a second embodiment of the invention, the closing spring 102 is operatively connected by means of a transmission gear, preferably in the form of a lever assembly with a pressure roller 101. The closing spring 102 pulls the pressure roller 101 via a lever 107 in the direction Hubkurvenscheibe 103, so acts in -x coordinate direction. Even if the trajectory of the pressure roller 101 describes a circle, it passes over the entire path of movement past the axial center of the output shaft 104.

An alternative lever arrangement is in FIG. 3B shown. In contrast to FIG. 3A Here, the closing spring 102 presses the pressure roller 101 via a lever 107 against the Hubkurvenscheibe 103, ie in the + x coordinate direction. Here, with respect to the pressure roller 101, the same applies as regards FIG. 3A ,

At an in FIG. 4 shown door closer 100 according to a third embodiment of the invention is provided, the arrangement of closing spring 102 and its operative connection with the pressure roller 101 (for example, the lever 107) rotated by one point, ie at an angle α, to arrange, which point, not the axial Center of an output shaft 104 of the door closer 100 corresponds.

An in FIG. 5 shown door closer 100 according to a fourth embodiment of the invention has a Hubkurvenscheibe 103, the receptacle for the output shaft 104 is arranged off-center. Ie. the Receiving for the output shaft 104 is arranged in a direction along an axial extension of the output shaft 104 adjacent to a connection line between the pressure roller 101 and the axial center of a conventionally arranged output shaft.

In addition, it may be provided that the pressure roller 101 with respect to their direction of movement in an assembled state of the door closer 100, d. H. when assembled, adjustable to train.

A device 200 according to a first embodiment of the invention for adjusting the position of a pressure roller 101 with respect to a cam disc 103 in the assembled state of the door closer 100 is shown in FIG FIG. 6 shown. A closer spring housing 108 receiving the closer spring housing 108 is freely pivotably mounted at one point. At another point, the closer spring housing 108 is mounted lockable in a slot 113. The locking is preferably carried out by means of a locking screw 204. The slot 113 is formed in accordance with the movement path which passes through the locking screw 204 upon pivoting of the closing spring 102. Instead of a closer spring housing 108, a spring stop of the closing spring 102 can be used.

The pressure roller 101 is operatively connected to the closing spring 102, preferably by means of a connecting rod 111. The connecting rod 111 is mounted in a guide 105 translationally on the closing spring 102 to or away from it.

Alternatively, the connecting rod 111 is guided into the closing spring 102 and is guided translationally by means of the closing spring 102. In that case, a closer spring housing 108 can be omitted.

The pressure roller 101 is mounted freely rotatably on the end of the connecting rod 111 facing away from the closing spring 102.

Instead of pivoting said arrangement is as in FIGS. 7A-7I shown, provided in a setting device according to a second embodiment of the invention, a translational displacement.

According to a first, in FIG. 7A illustrated variant, the above-described arrangement is moved altogether. The position of the closer spring housing 108 of the closer spring 102 is fixed by means of adjusting screws 205. The adjusting screws 205 are freely rotatably mounted on one side of the closer housing 109 in such a way that they maintain their position with respect to the closer housing 109 in the direction of their longitudinal extent, ie in the y-coordinate direction in FIG FIG. 7A , do not change. By turning the adjusting screws 205, the closer spring housing 108 and thus the entire arrangement can be moved in the y-coordinate direction, so that a displacement of the arrangement according to FIG. 2A is reached.

If only one adjusting screw 205 is rotated, a pivoting of the arrangement is possible to a certain extent.

Two independently rotatable adjusting screws 205 may cause a jamming under circumstances, so that an adjustment of the arrangement is no longer possible.

For this reason, according to a second, in FIG. 7B variant shown only one adjustment screw 205 is provided. On an inner side of at least one side wall 115 of the closer housing 109 is a part of a guide 201, preferably in the form of a guide projection 202, furthermore preferably as part of a dovetail guide. The other, preferably in the form of a groove 203 formed part of the guide 201 is formed on a side wall 115 of the closer spring housing 109. Advantageously, two, provided on two different side walls 110, 115 guides 201 are formed so that tilting is avoided. The only one adjusting screw 205 is preferably as in the embodiment according to FIG. 7A educated.

If the pressure roller 101 is received in a flap truck 106, as in FIGS. 2B and 2C is shown, the pressure roller 101 according to an in FIG. 7C shown third variant of this embodiment of the invention slidably received in an elongated hole 113 formed in the flap carriage 106. The pressure roller 101 is preferably arranged freely rotatable on a bearing journal 112. The bearing pin 112 in turn is received in the slot 113 and lockable by means of a locking screw 204 in the slot. Ie. not the entire assembly but only the pressure roller 101 itself is changed in position.

According to Figure 7D is in a fourth variant, the pressure roller 101 of the door closer 100 instead of attached to a flap truck 106 on a mounting stop 207 stationary and freely rotatable. The mounting stop 207 is guided in the flap carriage 106, preferably in a slot 113 movable. The attachment stop 207 has a locking stop 206, which has a threaded bore extending toward the tab carriage 106. The flap carriage 106 has a passage opening in such a way that a locking screw 204 passes from an outer side of the flap carriage 106 through the passage opening into the threaded bore of the arresting stop 206 screwed into it. Due to a rotation of the locking screw 204 of the mounting stop 207 and thus the pressure roller 101 can be moved to the flap carriage 106 to or away from it and thus be moved with respect to the Hubkurvenscheibe 103.

A fifth variant is in Figure 7E shown. The attachment stop 207 has a rectangular cross section with a cavity as seen in the x-coordinate direction. The mounting stop 207 can of course also be designed as a solid block. The attachment stop 207 has a section extending in the y-coordinate direction toward the flap carriage 106. The fastening stop 207 facing away from the end of this section is preferably guided in a slot 113 which is formed in the flap carriage 106 and extending in the z-coordinate direction.

Alternatively, instead of a slot 113 on the inside of the flap truck 106 may also be formed in an x-z plane slot-shaped recess. Ie. the slot is not formed by the flap carriage 106 through. The flap carriage 106 preferably has a continuous surface on the outside at least at this point.

A sixth variant is an in FIG. 7F illustrated strap solution. A tab 114 engages in a yz plane, the pressure roller 101. Preferably, in an xz plane in which the pressure roller 101 is located, an adjusting screw 205 is arranged.

In order to ensure a secure adjustment, can also be provided, the adjusting screw 205 in the in Figures 7D - 7F shown variants continue to an inner side of the side wall 115 and support there, which is opposite to the side wall 115, through which the adjusting screw 205 is guided.

Alternatively or additionally, according to an in FIG. 7G illustrated seventh variant provided to use a bearing pin 112, on which the pressure roller 101 is arranged. A stop member 208 is preferably pushed by means of a bearing sleeve on which the pressure roller 101 receiving bearing pin 112. The bearing pin 112 is thus freely rotatable with respect to the stop member 208. The stop member 208 preferably has a bearing sleeve in which the bearing pin 112 is received. The bearing sleeve preferably comprises a ball, roller or sliding bearing for the bearing journal 112.

On at least one side of the flap carriage 106 another stop member 209 is arranged, in which a stop spring 210 is received in the form of a compression spring. Upon rotation of the Hubkurvenscheibe 103 in the direction of stop member 209, the pressure roller 101 is urged in this direction. Due to the very strong force of the closing spring 102, the pressure roller 101 is not pushed back by means of the stopper spring 210 to its original position. Only with a reverse rotation of the Hubkurvenscheibe 103, not shown, the pressure roller 101 passes due to the shape of the drain surface of the Hubkurvenscheibe 103 and the force of the closer spring 102 back to its original position.

The stop member 209 may be fixedly attached to the flap truck 106 or, as in FIG. 7H represented by means of a Einstellschrauben mechanism 'in the direction of the pressure roller 101 to be movable away from and to.

According to a in FIG. 7I illustrated variant, two stop members 209 are provided, which are arranged fixed or displaceable on each of an inner side of two oppositely disposed sides of the flap carriage 106. The stop members 209 are preferably operatively connected by means of a respective stop spring 210 in the form of a compression spring with a stop member 208.

For attaching or supporting the adjusting screws 205 and locking stops 206, side walls 115 of a closer spring housing 108 or side walls 110 of a closer housing 109 may be used instead of the flap carriage 106.

Regarding the in FIGS. 3A and 3B shown lever assemblies is in an adjustment 200 according to a in FIG. 8 illustrated fourth embodiment of the invention, the pivotally mounted point of the lever 107, which is not coupled to the connecting rod 111, preferably slidably mounted in a slot 113. The recording and locking of this position of the lever 107 is preferably carried out as in the pressure roller 101 of the embodiment described above.

In order to pivot the arrangement according to FIG. 4 to reach is one in Figure 9A shown adjusting device 200 according to a fifth embodiment of the invention. Facing away from the pressure roller 101 and the closer spring housing 108 facing surface of a closer housing 109 or spring stop and the end facing the inside of the side wall 115 of the closer housing 109 are at least at one point to each other. Due to the concern, the end of the closer spring housing 108 or spring stop is guided by means of the inside of the side wall 115. Preferably again only one adjusting screw 205 is analogous to the above description of an outer side of the closer housing 109 is screwed into the closer spring housing 108 or the spring stop. By rotating the adjusting screw 205, a pivoting of the arrangement is achieved.

Alternatively, the end of the closer spring housing 108 or the spring stop, as in FIG. 9B shown guided in a formed in the closer housing 109 slot 113 and can be set by means of preferably a locking screw 204.

Alternatively, as in FIG. 9C shown, the operative connection between the closing spring 102 and pressure roller 101 is not rigid. Preferably, the operative connection consists of a connecting rod 111 and a lever 107, which are pivotally coupled together. The connecting rod 111 and the lever 107 are coupled to the respective end facing away from the pivot with a spring stop or the pressure roller 101. The pivot point is preferably formed by means of a guided and lockable in a slot 113 bearing pin 112.

In a flap truck 106, at least one connecting rod 111 is preferably provided. According to another variant of the fifth embodiment of the invention, the connecting rod 111, as in FIG FIG. 9D shown, guide holes in the form of slots 113. In the oblong holes 113, the tab 114 is fixed by means of locking screws 204. The shapes of the guide holes determine the displacement path for the tab 114 and thus the displacement of the pressure roller 101 with respect to the Hubkurvenscheibe 103th

The flap truck 106 may also include only one connecting rod 111. A guide of the flap carriage 106 is by means of a slot reached in the tab 114, by means of which the tab surrounds the output shaft 104 or encloses. On the output shaft 104, a bearing sleeve is preferably arranged with, for example, a ball, roller or sliding bearing. The bearing sleeve has an outer diameter which is substantially equal to an inner dimension of a cavity formed by the slot 113 or a recess, so that the bearing sleeve is guided guided.

In FIG. 10 an embodiment is shown, by means of which it is possible, so to speak, to release the pressure roller 101 from the Hubkurvenscheibe 103 and thus to solve. The pressure roller 101 is then no longer pressed against the Hubkurvenscheibe 103. For this purpose, the attachment stopper 207, the tab carriage 106 or the journal 112 to which the pressure roller 101 is attached has a mounting stopper 211 at one end in a direction substantially opposite to the pressing direction. The attachment stop 211 is preferably designed like one of the attachment stops 207 described above. Preferably, a side wall 115 has a preferably in the x-coordinate direction extending through hole for pushing through and screwing a screw 212 into the mounting stop 211 on. The pressure roller 101 is preferably arranged displaceably in a slot 113 by means of a bearing journal 112. By means of a fastening screw of the bearing pin 112 is locked in the slot 113. The slot 113 may have any shape. It is not limited to a straight design and thus to a purely translational displacement of the pressure roller 101.

The pressure roller 101 can thus be positioned easier and more precise, since no contact forces are to be overcome, which would otherwise be transmitted from the closing spring 102 to the pressure roller 101.

If the desired position of a screw 204, 205, 212 is reached, a locking device 20 is also preferably provided. Because of such a locking device 20, the screw 204, 205, 212 can be fixed in position.

As in Figure 11A Shown in the locking device 20 preferably two guide members 21 are provided, which are preferably received and guided in a slot 113. This may be the slot 113, in which under certain circumstances, the respective screw 204, 205, 212 is added. On the guide parts 21, a placement part 22 is placed. For attachment, the attachment part 22 preferably has passage openings which extend in the direction of the respective guide part 21. The guide parts 21 each have at least one attachment opening, preferably in the form of a threaded bore. In each case a fastening screw 23 is screwed from a guide parts 21 facing away from the side of the Aufsetzteils 22 through a through hole into a respective threaded hole. It is of course any other type of non-positive and / or positive connection between Aufsetzteil 22 and guide members 21 possible.

The Aufsetzteil 22 has on a screw 204, 205, 212 facing side at the point where it meets the screw 204, 205, 212, a recess. The recess has a shape that is complementary to the shape of the portion of the screw 204, 205, 212 that is received by the recess. As a result, a positive connection between screw 204, 205, 212 and attachment part 22 is achieved. Due to the screwing with the guide parts 21 thus the screw 204, 205, 212 is securely fixed in its rotational position. The screw 204, 205, 212 is further displaceable in the slot 113. A Movement of the pressure roller 101 due to a rotation of the Hubkurvenscheibe 103 is thus still guaranteed.

Due to the rotation of the screw 204, 205, 212 is in the in Figure 11A shown variant may not always ensure that the attachment part 22 can always be placed on the screw 204, 205, 212. In order to avoid this problem, in the attachment part 22 according to a in FIG. 11B shown second variant instead of passage openings preferably arcuate slots 24 are formed. This makes it possible, the Aufsetzteil 22 with respect to the guide members 21 at an angle β <> 0 ° to arrange and still achieve a positive connection between Aufsetzteil 22 and screw 204, 205, 212.

If the screw 204, 205, 212 is not received in an oblong hole, the guide parts 21 are omitted. Instead, the fastening screws are screwed into the respective wall, through which the screw 204, 205, 212 is guided.

The adjusting devices 200 according to Figures 3 . 4 . 9A and 9B are readily according to door closer 100 according to FIGS. 2A-3B applicable.

The adjusting devices 200 according to FIGS. 7A and 7B are with a door closer 100 according to FIGS. 2A-2C combined.

The adjusting device 200 is in particular for door closer 100 according to FIGS. 3A and 3B suitable while the adjusting 200 according to FIG. 7C for a door closer 100 according to Figure 2C is predestined.

The adjusting device 200 according to FIG. 9D is especially for door closers according to FIGS. 2A and 2B suitable.

The spring mounting of the pressure roller 101 can be combined with the adjustment devices 200 and door closers 100 described herein.

In the FIG. 10 Apparatus for releasing the pressure roller 101 shown is applicable to each door closer 100 described herein.

The locking devices 10 according to Figures 11A and 11B are applicable to all adjustment screws 205 described herein.

The adjusting screws 205 are not limited to the illustrated hexagon screws.

The recess of the Aufsetzteils 12 may have any complementary shape of the adjusting screw 205 used in each case. If countersunk screws are used, for example, whose heads are flush in the screw-in state, the mounting part 12 has a projection in complementary form of the head of the countersunk screw instead of a recess. For example, if it is a Phillips countersunk screw, the protrusion has the shape similar to the head of a Phillips screwdriver.

LIST OF REFERENCE NUMBERS

20

locking device

21

guide part

22

footpad

23

fixing screw

24

Long hole

100

door closers

101

capstan

102

closer spring

103

cam disc

104

output shaft

105

guide

106

cam plate

107

lever

108

Closer spring housing

109

closer housing

110

Side wall

111

connecting rod

112

pivot

113

Long hole

114

flap

115

Side wall

200

adjustment

201

guide

202

head Start

203

groove

204

locking screw

205

adjustment

206

arresting stop

207

fastening stopper

208

stop part

209

stop part

210

stop spring

211

fastening stopper

212

screw

i _cam

Power ratio of Hubkurvenscheibe

M

torque

α

angle

β

angle

φ

Rotary blade angle

e

eccentricity

R _B

Direction of movement of the pressure roller

x

coordinate direction

y

coordinate direction

z

coordinate direction

Claims (17)

Door closer (100), comprising an output shaft (104) on which a Hubkurvenscheibe (103) is arranged rotationally fixed, and a pressure roller (101), wherein a closing spring (102) by means of an operative connection (106, 111, 107), the pressure roller (101 ) against a running surface of the Hubkurvenscheibe (103) presses, wherein the pressure roller (101) with respect to an axial center of the output shaft (104) is arranged so that the pressure roller (101) at an opening or closing with the output shaft (104) Coupled rotary vane is moved along a path, wherein the fact that the web at the axial center of the output shaft (104) passes, and due to a design of the running surface of the Hubkurvenscheibe (103) at a respective opening angle of the rotary vane in Verdissenen modes of the door closer (100 ) is applied to the output shaft (104) in each case a very similar or identical torque, ■ wherein the modes include operation of the door closer (100) with a slide rail and operation of the door closer (100) with a normal or scissors linkage, and Wherein the rotary vane drive (10) is mounted on a hinge side in a slide rail operation and on a belt opposite side during normal linkage operation, or wherein the rotary vane drive (10) is mounted on a belt side in slide rail operation and on a belt side in normal linkage operation, The Hubkurvenscheibe (103) in a first direction (± y) parallel to a longitudinal extent of the output shaft (104) seen as having a symmetrical cross-sectional area, ■ wherein the passage of the path of the pressure roller (101) is designed so that the door closer (100) on a first portion of the running surface of the Hubkurvenscheibe (103) for GleitschienenBetrieb and on a second portion of the running surface of the Hubkurvenscheibe (103) is designed for normal linkage operation, wherein a start of the portions of the running surface of the Hubkurvenscheibe (103) is a point of the running surface of the Hubkurvenscheibe (103) against which the pressure roller (101) when the rotary wing is closed, ■ wherein an arrangement consisting of at least the closing spring (102), the pressure roller (101) and the operative connection (106) between them in a first plane (x, z) is arranged transversely to the longitudinal extent of the output shaft (104) rotatable, wherein a rotation point the arrangement to the axial center of the Hubkurvenscheibe (103) in the first plane (x, z) has a distance, or in the first plane (x, z) at an angle (α) to a line connecting the pressure roller (101) and axial Center of Hubkurvenscheibe (103) is displaceable and each is arranged lockable. A door closer (100) according to any one of the preceding claims, wherein the rotary wing drive (10) is mounted on a lintel or upper portion of a door frame or frame on which the louver is suspended, or on the louver itself. The door closer (100) of any of claims 1 to 2, wherein the modes further include operating the door closer (100) with a parallel linkage. Door closer (100) according to one of the preceding claims, wherein the operative connection comprises at least one rigid part (106, 111). Door closer (100) according to one of the preceding claims, wherein the operative connection is a lever mechanism. Door closer (100) according to claim 1, wherein the cross-sectional area is heart-shaped. The door closer (100) according to claim 1 or 6, wherein the rotation point of the cam disc (103) is arranged in the first direction (± y) adjacent to a symmetry line of the symmetrical cross-sectional area. Door closer (100) according to one of the preceding claims, wherein a housing of the door closer (100) at least in areas in which the ends of the output shaft (104) are arranged in a respective side wall (115) has a through opening, wherein the ends of the output shaft (104) are designed to be coupled with a rotary wing. A door closer (100) according to any one of the preceding claims, further comprising adjustment means (200) for adjusting a distance of the pressure roller (101) with respect to its path in a mounting state of the door closer (100). A door closer (100) according to claim 9, wherein the adjustment means (200) comprises a mounting stop (207) on which the pressure roller (101) is fixed and freely rotatable, the mounting stop (207) having a threaded bore extending into a second Direction (± z) transverse to a longitudinal extent of the output shaft (104) and extends transversely to a longitudinal extent of the door closer (100), wherein a side wall (115) of the door closer (100) has a passage opening such that from an outer side of the side wall (115) forth a screw (205) is screwed into the threaded bore, wherein the attachment stop (207) is guided guided in a guide of a connecting member (106) connected to the Closing spring (102) is coupled. Door closer (100) according to claim 10 and according to claim 5, wherein a point of rotation of a lever (107) of the lever mechanism is slidably mounted. Door closer (100) according to claim 9 or 10, further comprising means for releasing the pressure roller (101) from the Hubkurvenscheibe (103) in the assembled state of the door closer (100). The door closer (100) according to claim 12, wherein the means comprises a mounting stop (211) on which the pressure roller (101) is fixed and freely rotatable, the mounting stop (211) having a threaded bore extending in a third direction (± x) extends parallel to a longitudinal extent of the door closer (100), wherein a side wall (115) of the door closer (100) has a through opening such that from an outer side of the side wall (115) a screw (212) is screwed into the threaded bore. Door closer (100) according to one of the preceding claims, wherein the pressure roller (101) is arranged so that it is moved during rotation of the Hubkurvenscheibe (103) by means of the Hubkurvenscheibe (103) in a position in which the web of the pressure roller (101 ) passes the axial center of the output shaft (104). The door closer (100) according to any one of the preceding claims, wherein the cam disc (103) is pre-twisted in a position in which the rotary wing is closed. Door closer (100) according to one of the preceding claims, further comprising at least one device (10), arranged to lock at least one screw (205) against rotation. A door closer (100) according to claim 15, wherein the apparatus comprises a seating member (12) which, when placed on the screw (205), rotates with a head of the screw and is lockably disposed.

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