EP0174432B1 - Device for holding a door closer in position - Google Patents

Abstract

A door holding device for door closers is described in which a door is held only at a predetermined angle of opening and in which the selected holding position can remain unchanged over a long period of time but can nevertheless be released by electrical means. For this purpose the switching of the door is effected, starting from a known mechanical door holding device which can be switched in and switched out, via a control unit which is biased into a door holding position by the hydraulic pressure which is in any event present in the closer and which can be released again via a magnetic valve.

Description

The invention relates to a locking device according to the preamble of claim 1.

A locking device of this type is known from DE-PS-3 151 498. This known locking device is a purely mechanical device by means of which a door can be locked at a certain opening angle and no controlled release of this locking is provided. If the determination is to be canceled in this known arrangement, then the door must be suppressed, d. H. a force is exerted in the closing direction of the door which is greater than the holding force acting in the latching position, so that the fixing is released and the door is returned to the closing position by the closer.

The invention further relates to a locking device similar to the device mentioned in the preamble of claim 9.

Such a locking device is known from FR-PS-2 343 112. The control head interacts directly with the locking unit. The disadvantage here is that even with a slight displacement of the control head, as occurs in the case of a longer hold-open time due to the inevitable pressure losses, the detection fails or the door creeps.

From DE-OS-2 523 154 a door closer with an electromagnetic hold-open device is known, in which the closer shaft is held with a locking bolt which can be actuated via the electromagnet. The locking pin is arranged on a lever which interacts with the electromagnet. The construction is relatively large.

From DE-OS-2 913 426 a hydraulic locking device for door closers is known, the locking of the door taking place in that the outflow of a hydraulic medium from a pressure chamber which increases during the opening movement and decreases during the closing movement by means of a particularly electromagnetically controlled valve is blocked. The disadvantage here is that the door at any angle, for. B. between 80 ° and 180 ° each depending on the position of the door stops when you turn on the lock, although in practice the doors should always be opened as far as possible and fixed there. A typical example of this is a wall running at right angles to the door, whereby in the normal case the opened door should always rest against this wall and should also remain there. Furthermore, in these known hydraulic locking devices, it is of considerable disadvantage that the door creeps in the closing direction even with the slightest hydraulic leakage, which can lead to the door protruding from the wall and no longer the desired, full just a few hours after the detection has taken place occupies the open position.

The object of the present invention is to provide a locking device for door closers, which enables locking in particular only at a predeterminable opening angle, maintains the selected locking position unchanged for any length of time and is electrically controllable for the purpose of releasing the locking. Furthermore, the construction volume of this locking device should be as small as possible and the power consumption of the closer should be as low as possible.

This object is achieved with a locking device with the features of claim 1 or alternatively with the features of claim 9.

It is characteristic of the solution according to the invention that a control head acting as a piston is tensioned by means of a hydraulic pressure which is present anyway in the closer and can be released again in a controlled manner via a preferably integrated solenoid valve.

Undesired creep effects due to leaks can be completely eliminated by using mechanical catches.

Preferably, in a further development of the locking device with the feature of claim 1, the control unit consists of a control sleeve which can be blocked with respect to the hollow cylinder forming the actuating member by means of at least one radially displaceable retaining pin and which cooperates with an actuating pin, and the actuating pin by means of the magnet unit in the blocking position Holding pins corresponding position is fixable.

Particularly preferred embodiments of the invention are specified in the subclaims.

• Figur 1: eine schematische Darstellung eines Ausschnitts des Dämpfungsraums eines Türschließers bei ausgeschalteter Feststellvorrichtung,
• Figur 2: eine der Figur 1 entsprechende Darstellung bei sich in Funktion befindender Feststellung,
• Figur 3: eine schematische.Darstellung einer Variante der erfindungsgemäßen Feststellvorrichtung in Verbindung mit einem Türschließer,
• Figur 4: eine mögliche Anordnung der Feststellvorrichtung nach Fig. 3 in einem Bodentürschließer und
• Figur 5: eine schematische Halb-Querschnittsdarstellung einer besonders bevorzugten Ausführungsform der Erfindung bei sich in Funktion befindender Feststellung.

The invention is explained in more detail below using exemplary embodiments with reference to the drawing; in the drawing shows:

• FIG. 1: a schematic representation of a section of the damping space of a door closer with the locking device switched off,
• FIG. 2: a representation corresponding to FIG. 1 when the determination is in operation,
• 3 shows a schematic representation of a variant of the locking device according to the invention in connection with a door closer,
• Figure 4: a possible arrangement of the locking device according to FIG. 3 in a floor closer and
• Figure 5 is a schematic half-cross-sectional view of a particularly preferred embodiment of the invention with the finding in operation.

1, a working piston 1 is arranged in the damping chamber 14 of a door closer, which is tubular at least in the region of its free end shown and moves to the right in the drawing when the associated door closes and the oil present in the damping chamber via valves (not shown) displaced the damping space. The damping space also includes all the spaces between the individual parts which are filled with oil, and it should also be pointed out that the entire cross-sectional area of the piston 1 is effective for displacing the oil.

In the interior of the working piston 1, which is displaceable in the housing 25, there is a cone 3 which is prestressed in the direction of the free end of the working piston 1 by means of a compression spring. This cone 3 interacts with locking members 2 in the form of balls, which are moved radially outwards by the cone due to the action of the compression spring 4, provided that these balls 2 are outside the working piston and not - as in the operating state according to FIG. 1 - on it be prevented by the working piston 1.

A stop element 10, which has the shape of a hollow cylinder and has an outer diameter that allows entry into the tubular part of the working piston 1, is also fixed in the housing 25 and runs coaxially to the working piston 1. The working piston end of the stop member 10 is closed by a wall through which a control tappet 5 connected to the cone 3 is guided in a sealed manner via an O-ring 6.

The stop member 10 is screwed into the housing 25 with its outer end having a larger diameter and can be left or fixed in different axial positions, as a result of which different locking opening angles can be predetermined. Between the stop member and the housing wall is approximately half the length of the stop member, a support and sealing part 13, which is also screwed to the housing wall and is sealed via O-rings on the one hand with respect to the housing wall and on the other hand with respect to the stop member 10.

In the cylindrical cavity of the stop element 10 there is a magnet unit 22 which is connected to a control head 7 and is biased in the direction of the working piston 1 by a compression spring 11. The biasing force of the spring 11 is greater than the biasing force of the spring 4 assigned to the cone 3.

The feed lines 12 for the magnet unit 22 are led out of the stop element 10 via a suitable bore.

The control head 7 is sealed with respect to the inner wall of the tubular stop member 10 via an 0-ring 8, and a further O-ring seal 9 is provided in the region of the end of the magnet unit 22 facing away from the control head 7. In the area between these two seals 8, 9 10 bores 15 are provided in the tube wall of the stop member, which lead to the pressure chamber 14.

In Fig. 1 the mechanical locking is shown in the switched-off state, which can be seen from the fact that the magnet unit 22 with the control head 7 has moved all the way to the left and the control plunger 5 has pushed the cone 3 back against the force of the spring 4. Accordingly, the cone 3 cannot exercise any spreading function with respect to the balls 2, which in turn has the consequence that even during a door opening process in which the working piston 1 is moved to the left in the drawing, the balls cannot be moved in the radial direction and therefore none Finding results.

In this operating state, which is due solely to the mechanical conditions, i.e. H. is predetermined by the ratios of the forces of the springs 4, 11, the magnet unit 22 is in the non-excited state, i. H. it is without current.

Fig. 2 shows the arrangement described in the state of detection.

The balls 2 are located after radial expansion between an end sloping surface of the working piston 1, the cone 3 and the stop member 10, whereby the selected sloping surfaces on the one hand ensures that the working piston 1 does not move out of the locking position, i. H. can run to the right in the drawing, and on the other hand it is still possible to overpress this locking position. If a sufficiently high force is applied to the determined door by hand in the closing direction, then the balls 2 are pressed radially inwards due to the effect of the front oblique surfaces of the working piston 1 with simultaneous evasive movement of the cone 2 and the working piston 1 can move in the closing direction.

The magnet unit 22 with the control head 7 is in its right end position in FIG. that is, the control head 7 is spaced with respect to the control plunger 5, which is also a prerequisite for the cone 3 to be able to perform its spreading function with respect to the balls 2.

The magnet unit 22 and the control head 7 have reached the position shown in FIG. 2 in that, starting from the position shown in FIG. 1, the associated door is opened and the working or damping piston 11 has moved to the left. The magnet unit 22 and the control head 7 remain in the position according to FIG. 1, i. H. a determination is not possible.

When the door is subsequently closed, an oil pressure builds up in the insulation space 14, which brakes the door movement. This pressure also acts through the bores 15 on the circular cross section of the magnet unit 22, which is sealed to the outside via the O-ring 9.

Since the internal pressure that is formed is higher than the external pressure and the force of the spring 11, the magnet unit 22 with the control head 7 is shifted to the right. In this case, however, this does not lead to any determination, since the door is already running in the damping chamber in the closing direction and the balls 2 are again resting against the inner wall of the piston 1.

If the magnet unit 22 is supplied with current and the magnet is excited, the magnet unit with the control head remains in the position shown in FIG. 2, since the ball valve 20 is closed via the actuating plunger 19 acted on the armature 21 and the oil from the pressure chamber 23 cannot expire. Even when the ball valve 20 is closed, the volume of the pressure chamber 23, ie. H. when the magnet unit 22 moves against the direction of the arrow 18, oil flows into this pressure chamber 23, since an intake valve 16, which seals with an O-ring 17, is formed in the control head 7. The connection to the pressure chamber 14 is created via the holes 15 and 26.

As long as the magnet unit 22 is energized and the valve 20 is closed in the operating phase shown in FIG. 2, the magnet unit 22 and the control head 7 remain in the position shown, i. H. the control plunger 5 is not actuated and the detection remains switched on.

Even if e.g. B. small leaks should occur via the valve 20, which would lead to a very slow creep of the magnet unit 22, there would be no change in the locking angle of the door. Only if the magnet unit and thus the control head 7 had moved so far that actuation of the control plunger 5 would take place that the determination would be canceled. In this case the door would have to be locked again the next time you walk on it.

It can be seen that the clamping of the magnet unit 22 with the associated control head 7 is effected by the pressure generated when the closer closes. The consequence of this is that a determination is only possible when the door is opened a second time, since the determination is only effectively switched on at this point in time and accordingly the cone 3 has moved into the position shown in FIG. 2.

The determination is released whenever the current exciting the magnet unit 22 is interrupted so that the valve 20 is opened and as a result the magnet unit 22 is moved to the left with the control head 7 and the control plunger 5 is actuated. It can be released by hand at any time, regardless of the position of the magnet unit 20, since it is only necessary to simply snap the ball 2 into place.

The embodiment of the invention according to FIG. 3 is particularly suitable for floor door closers, wherein a different locking mechanism is used compared to the variant according to FIGS. 1 and 2. However, the principle of switching the detection on and off corresponds to the principle described with reference to FIGS. 1 and 2.

According to FIG. 3, a cam disk 32 with a locking recess 27 is connected in a rotationally fixed manner to the closer axis 30. This cam disc interacts with a locking piston 29 which carries a roller at its free end and which is biased by a spring 34 against the cam disc 32. If the roller 23 engages in the cam recess 27, the closer axis 30 is locked in the predetermined position.

The biasing spring 34 is supported on an abutment 35, which also carries a guide pin 39 for the locking piston 29. This guide pin 39 simultaneously limits the axial movement of the locking piston 29.

The abutment 35 is designed as a piston and sealed against the wall guiding this piston via an O-ring. The magnet unit 22 with the control head 7 is provided on the side of the abutment 35 opposite the latching unit.

The control head 7 delimits a pressure chamber 23, and a connection chamber 36 is formed between the O-ring seals of the control head 7 and the abutment 35, into which a connecting bore 38 opens.

The design of the magnet unit 22 and control head 7 corresponds to the embodiment explained with reference to FIGS. 1 and 2.

Fig. 4 shows the placement of the arrangement of FIG. 3 in a floor closer. The blind hole for receiving the locking device runs parallel to the spring chamber 37 of the door closer filled with hydraulic fluid, in which a cam disk 31 connected to the closer axis 30 interacts with the closing spring 28 in a known manner. The connecting bore 38 extends between the spring space 37 and the connection space 36.

The closer axis 30 is acted upon in the closing direction by the cam disk 31 and the associated spring 28. For the sake of simplicity, the provided damping is not shown in the closer according to FIG. 4, but another cylinder could be provided for this purpose, for example.

The determination is effected via the locking cam 32, the roller 33 holding the closer and thus the door via the compression spring 34.

The abutment 35, which acts as a piston, can be switched via the magnet unit 22 and the control head 7. The tensioning of the abutment, ie the pressure build-up in the pressure chamber 23 is not effected in the example according to FIG. 4 by the closing damping, but the pressure build-up in the room 23 takes place during the opening process, since a pressure increase occurs in the spring chamber 37 which corresponds to the Path range "a" can correspond to a hydraulic opening damping, which can also be referred to as throwing damping.

If, starting from the latching position shown in FIGS. 3 and 4, the magnet unit 22 is excited, the valve in the control head 7 opens, the pressure in the pressure chamber 23 is reduced, the abutment 35 moves in the direction of the bottom of the blind hole, whereby the spring 34 relaxes and thus the finding is resolved. The door can now close.

The embodiment variant shown in FIG. 5 is preferably intended for floor door closers and works with a mechanical locking device which prevents any creeping effects of the closer.

Parts corresponding to the previously described embodiments are identified by the same reference symbols in the illustration according to FIG. 5.

In the end of the damping chamber of the closer, as in the arrangements already described, a unit that locks the ball lock of the mechanical lock on or off is screwed in, specifically via an adjusting sleeve 45, which is screwed to the stop element 10. All moving parts are contained in the interior of this adjusting sleeve 45 and the stop element 10. The adjustment of the sleeve 45 in the axial direction enables the setting of the required door locking angle.

In the stop member 10, a control sleeve 40 is guided axially displaceably and biased by the compression spring 11, which is supported on a rear wall of the adjusting sleeve 45. An O-ring 41 is provided between the control sleeve 40 and the stop member 10 for sealing. The control sleeve 40 can be mechanically locked relative to the stop element 10, specifically by means of retaining pins 43, which are distributed over the circumference in the region of the free end of the control sleeve 40 and are guided radially displaceably in corresponding bores in the control sleeve 40. Two or three retaining pins 43 distributed over the circumference are preferably provided. These holding pins 43 can interact with an inner inclined surface 44 on the stop element 10 and they block an axial movement of the control sleeve 40 when they bear against this stop surface 44.

The magnet unit 22 is firmly screwed into the control sleeve 40. The electrical supply lines are formed by the cables 53, which are connected to sleeves 52, into which an electrical supply cable can be inserted.

Associated with the magnet unit 22 is an adhesive bolt 46 which can be displaced in the control sleeve 40 and which is screwed to an opening bolt 47 which has at its free end a conically widening part with a footprint 49 which interacts with the holding pins 43. In the position shown, the magnet unit 22 holds the adhesive bolt 46 tight, i. H. current flows through the magnet in the position shown. A comparatively weak extension spring 50 is arranged between the adhesive bolt 46 and an inner ring shoulder of the control sleeve 40.

The arrangement described works in the following way:

In the position shown, the closer is in the locking position, since the balls 2 are pressed radially outwards via the cone 3 and the control plunger 5 is not actuated by the control sleeve 40, i. H. is not pushed to the left. The magnetic unit 22 has current flowing through it.

If the current is switched off, the compression spring 11, which acts against the support ring 48 of the control sleeve 40, presses the retaining pins 43 radially inward over the inclined surface 44, so that the mechanical blocking of the control sleeve 40 is released. This radial displacement of the retaining pins 43 is made possible by the fact that the adhesive bolt 46 is released by the magnet together with the deployment bolt 47, and thus these retaining pins 43 can no longer be held in their radially outer position via the placement surface 49.

As soon as the holding force of the holding pins 43 ceases to exist, the control sleeve 40 moves together with the parts held in it due to the force of the spring 11 to the left, as a result of which the control plunger 5 is also carried along, as a result of which the holding force of the locking balls 2 is released. The force of the spring 11 is always stronger than the force of the compression spring 4.

If the closer is to be brought back to the determination, the magnet unit 22 must be supplied with current. However, since it is only a holding magnet, it is not able to tighten the holding pin 46. This would also not be possible since the holding pins 43 are still in the narrower diameter of the stop element 10 in the switched-off position.

However, pressing the closer once creates a pressure in the piston chamber which acts on the control sleeve 40 over the cross-sectional area of the cross section sealed by the O-ring 41 and moves it back to the right against the force of the spring 11. The control sleeve 40 is pushed back due to the pressure until the compression spring 11 is on block. The holding pins 43 thus come into the larger diameter of the stop member 10 and are spread to the right by the movement of the adhesive bolt 46, specifically because of the auxiliary force of the very weak extension spring 50. This extension spring 50 brings the adhesive bolt 46 to the holding magnet and the latter now holds the adhesive bolt by its magnetic force.

The holding pins 43 now again block the control sleeve 40 against a movement to the left, i. H. the door is locked again.

• 1 Arbeitskolben (Stützorgan)
• 2 Riegelelement (Kugel)
• 3 Konus
• 4 Druckfeder
• 5 Steuerstößel
• 6 O-Ring
• 7 Steuerkopf
• 8 O-Ring
• 9 0-Ring
• 10 Anschlagorgan
• 11 Druckfeder
• 12 Anschlußleitung
• 13 Stütz- und Dichtteil
• 14 Dämpfungsraum
• 15 Bohrung
• 16 Ansaugventil
• 17 O-Ring
• 18 Pfeil
• 19 Betätigungsstößel
• 20 Kugelventil
• 21 Anker
• 22 Magneteinheit
• 23 Druckraum
• 24 Gewinde
• 25 Gehäuse
• 26 Bohrung
• 27 Rastausnehmung
• 28 Schließfeder
• 29 Rastkolben
• 30 Schließerachse
• 31 Kurvenscheibe
• 32 Rastkurvenscheibe
• 33 Rolle
• 34 Druckfeder
• 35 Widerlager
• 36 Anschlußraum
• 37 Federraum
• 38 Verbindungsbohrung
• 39 Führungszapfen
• 40 Steuerhülse
• 41 0-Ring
• 43 Haltestift
• 44 Schrägfläche
• 45 Verstellhülse
• 46 Haftbolzen
• 47 Ausstellbolzen
• 48 Stützring
• 49 Stellfläche
• 50 Ausstellfeder
• 51 Steckeraufnahme
• 52 Hülse
• 53 Kabel

This mechanical locking of the Tripping unit makes the function of the device described completely independent of any leaks, so that creeping processes are excluded with certainty.

• 1 working piston (support member)
• 2 locking element (ball)
• 3 cones
• 4 compression spring
• 5 control tappets
• 6 O-ring
• 7 control head
• 8 O-ring
• 9 0-ring
• 10 stop organ
• 11 compression spring
• 12 connecting cable
• 13 support and sealing part
• 14 damping space
• 15 hole
• 16 suction valve
• 17 O-ring
• 18 arrow
• 19 actuating plungers
• 20 ball valve
• 21 anchors
• 22 magnet unit
• 23 pressure chamber
• 24 threads
• 25 housing
• 26 hole
• 27 notch
• 28 closing spring
• 29 locking pistons
• 30 closer axis
• 31 cam
• 32 locking cam
• 33 roll
• 34 compression spring
• 35 abutments
• 36 terminal compartment
• 37 spring chamber
• 38 connecting hole
• 39 guide pins
• 40 control sleeve
• 41 0-ring
• 43 holding pin
• 44 sloping surface
• 45 adjusting sleeve
• 46 adhesive bolts
• 47 stay bolts
• 48 support ring
• 49 footprint
• 50 extension spring
• 51 connector receptacle
• 52 sleeve
• 53 cables

Claims (10)

1. A holding device for door closers comprising a support member (1), which is axially displaceably guided in a reception chamber of the housing of the door closer, which is actuated in dependence on the movement of the closer shaft and which is formed, at least in part, as a hollow cylinder; an abutment member (10) which is arranged in the reception chamber coaxial to the support member, with an oblique surface of a cone (3) facing the abutment member and with the cone being biased towards the abutment member by a spring (4) braced against the support member; and at least one locking element (2) located between the cone and the abutment member (10), with the locking element being capable of being changed over between a release position in which it is located in the hollow cylindrical section of the support member (1) and a blocking position in which it is disposed between an oblique end face of the support member (1), the cone (3) and the abutment member (10), characterized in that the support member (1) is formed as a working piston (1) which is acted on by the hydraulic pressure in the closer and moves in the reception chamber which acts as a damping chamber (14); in that the abutment member consists of a hollow cylinder (10) in which a magnetic unit (22) with a control unit (7; 40) is axially displaceably arranged and biased towards the working piston (1) by a spring (11); in that the working piston end of the hollow cylinder (10) is closed by a wall, and a control pin (5) for axially displacing the cone (3) by means of the control unit (7; 40) is guided through this wall; and in that the magnetic unit (22) with the control unit (7; 40) is displaceable by the working pressure against the force of the bias spring (11) and, under the control of the magnetic unit (22), can be held in and released from the resulting end position in which it is spaced from the control pin (5).

2. A holding device in accordance with claim 1, characterized in that the force of the bias spring (11) associated with the magnetic unit (22) is larger than the force of the bias spring (4) associated with the cone (3).

3. A holding device in accordance with claim 1, characterized in that the control pin (5) is connected with the cone (3) and extends into a pressure chamber provided in the abutment member (10), with the pressure chamber (23) being bounded at one end by the closure wall of the abutment member (10) at the working piston side and at the other end by the axially displaceable control head (7) which sealingly contacts the inner wall of the abutment member (10).

4. A holding device in accordance with claim 1, characterized in that the control unit is formed as a control head (7) in which there is provided, on the one hand, a suction valve (16) which connects the pressure chamber (23) with the damping chamber (14) when the volume of the pressure chamber (23) increases, and, on the other hand, a ball valve (20) which lies between the pressure chamber (23) and the damping chamber (14) and is controlled by the magnetic unit (22).

5. A holding device in accordance with claim 1, characterized in that the abutment member can be screwed into the housing (25) and can be fixed in different axial positions; and in that a seal (13; 42) is provided between the abutment member (10) and the region of screwed connection with the wall of the housing.

6. A holding device in accordance with claim 1, characterized in that the control unit consists of a control sleeve (40) which can be blocked relative to the hollow cylinder (10) forming the abutment member by means of at least one radially displaceable holding pin (43) which cooperates with a deployment bolt (47); and in that the deployment bolt (47) can be fixed into the position corresponding to the blocking position of the holding pins (43) by means of the magnetic unit (22).

7. A holding device in accordance with claim 6, characterized in that each holding pin (43) can be moved via an inclined surface (49) provided on the deployment bolt (47) between a release position in which its radially outer end is disposed within the peripheral contour of the control sleeve (40) and a blocking position in which its radially outer end contacts an inclined surface (44) on the inner wall of the hollow cylindrical abutment member (10).

8. A holding device in accordance with claim 7, characterized in that the magnetic unit (22) is constructed as a holding magnet and in that a weakly dimensioned spring (50) which urges the deployment bolt (47) in the deployment direction of the holding pins (43) is arranged between the control sleeve (40) and the deployment bolt (47) which acts as an adherent bolt.

9. A holding device for door closers, in particular for floor mounted door closers, comprising a latching unit (33, 29) arranged in a reception chamber of the closer housing, with the latching unit cooperating with a cam disc connected with the axle (30) of the door closer, the cam disc having at least one latch recess (27), and being hydraulically supported via a control head (7) which bounds a pressure chamber (23), and with the control head (7) being formed as a piston loaded by the hydraulic pressure of the door closer and having at least one valve (20) which is controllable by means of a magnetic unit (22) and closes or opens the pressure chamber (23), characterized in that the magnetic unit (22) together with the control head (7) is displaceable against the force of a compression spring by the hydraulic pressure in the door closer and, in the resulting end position is holdable or releasable under the control of the magnetic unit (22), with the compression spring (34) being disposed between the latching unit (33, 29) and an abutment (35) which is hydraulically supported via the control head (7).

10. A holding device in accordance with claim 9, characterized in that a connection chamber (36) which is sealed at both ends by O rings is formed between the abutment (35) and the control head (7) and is connected via a non-return valve or a suction valve in the control head (7) with the pressure chamber (23); and in that the connection chamber (36) is connected with the damping chamber of the closer, in particular with the spring chamber (37) of the closer which is filled with hydraulic fluid.

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