EP3070246B1 - Holding device for holding a pivotable door leaf - Google Patents

Description

The invention relates to a slide rail door closer with holding device for driving and holding the closing movement of a hinged door leaf in an open position, as well as a two-leaf swing door which is equipped therewith.

The advantages of the devices according to the invention are particularly valuable on doors which have to fulfill a safety claim, in particular on fire doors with so-called panic and escape function.

Due to folds which constitute a projection of one door leaf in front of another door leaf, it is necessary for the proper closing of a double-leaf door to close the wings in the correct order. This is the case when, from the open state, the passive leaf is first brought into the closed position and only then is the active leaf. Two-leaf swing doors that have to perform a safety function, therefore, are not only provided with a drive which automatically moves the door in the closed position, but also with a device for controlling the closing sequence, which is intended to cause the two leaves automatically in the correct order getting closed.

If, when the inactive leaf is open, the active leaf also open, for example driven by a spring or hydraulics, executes a closing movement leading the inactive leaf, this closing movement is stopped by the action of the closing sequence control device at a certain opening angle until the inactive leaf in its closing movement, the power wing is sufficiently far ahead that it ensures the correct closing sequence.

In conventional slide rail door closers, a swivel arm projects from a drive unit attached to the door leaf is. The slide rail is arranged on the upper frame part of the door frame and aligned parallel thereto. With the door closed, that end of the pivot arm which is attached to the door leaf is closer to the pivot axis of the door leaf than that end of the pivot arm which is connected to the sliding block. The attached to the door drive unit exerts on the swivel arm held pivotally on her in the same direction to the opening pivot movement of the door aligned torque. As a result, the reaction torque acting on the drive and thus on the door leaf from the swivel arm drives the door leaf to be closed in the absence of other moments. During the majority of the closing pivoting movement of the door leaf, the sliding block slides in the slide rail away from the axis of rotation of the door leaf.

So far, the linear movements of the sliding blocks of the two leaves in the slide are used in most cases for controlling the closing sequence of two-leaf swing doors. When the inactive leaf is open and the movement of the active leaf is closed, the forced linear movement of the sliding block belonging to the active leaf is blocked at a locking mechanism before the active leaf is closed. Only by the associated with the closing of the inactive leaf linear displacement of the passive side sliding block releases the lock again.

This simple and robust functioning principle is according to the documents EP 0613989 A2 . DE 102012100926 A1 and AT 510907 A1 realized using fluid cylinders. The writings show two-leaf swing doors with sliding rail door closers with closing sequence control in the slide a fluid cylinder is fixedly mounted, the piston position depends on the opening angle of the passive leaf and depending on the position movement of the sliding rail door closer belonging to the active leaf sliding blocked or releases. The fluid cylinder acts directly from the slide rail on the linear movement of the sliding block along the slide rail, whereby the function is directly dependent on the direction of movement of the sliding block along the slide rail. This always results in disturbing restrictions or the requirement of unsightly or difficult settings when the associated linear movement of the associated sliding block reverses during the closing movement of a door leaf.

There are several approaches to using not the linear sliding movement of the sliding blocks in the slide for controlling the closing sequence, but the pivotal movement of the pivot arms relative to the slide rail. This pivoting movement does not change its direction of rotation during the closing pivoting movement of a door leaf.

According to the DE 3406433 A1 is already 1984 proposed to provide a hydraulic-based drive for the pivotal movement of the swing arm of the active leaf and to block the possibly required blocking pivotal movement of the pivot arm in the drive unit in response to the position of the inactive flow of hydraulic fluid. In order to establish the dependence on the position of the passive leaf, use is made of a Bowden cable which transmits movement of a part moved with the fixed leaf to a valve on the drive unit of the active leaf - which is itself fastened to the moving leaf.

According to the scriptures DE 101 22 817 A1 and AT 510971 A4 when the passive leaf is closed, the swinging arm of the inactive leaf abuts an extension which protrudes radially from a rod arranged in the sliding rail so that the rod, which is aligned parallel to the sliding rail, is also rotated about its longitudinal axis. By this rotation, the rod brings a locking part out of the path of movement of the sliding block of the active leaf rigidly anchored part, so that thus closing movement of the active leaf is released.

The EP 2 208 846 A2 proposes several embodiments of closing sequence controls in which the pivotal movement of the pivoting arm relative to the slide rail in translation of parts is translated parallel to the slide rail longitudinal direction. This is done to compensate for that linear movement of the sliding arm belonging to the sliding block, which runs during the last part of the closing movement of a door leaf to the axis of the door leaf and not away from it. The said parts are kept movably guided on the sliding block. It is further proposed by blocking movement of these parts to block pivotability of a swing arm.

In the date of the priority date of the present application not yet published Austrian patent application A60 / 2014 For the purpose of controlling the closing sequence, a special chain of translations between the swivel arms of two door leaves is proposed. On a sliding block, the rotational movement of the swivel arm rotatably mounted there is translated into movement of a part guided on the sliding block normal to the slide rail. As a result of this movement, a part which is movably guided on the slide rail is driven to move with a directional component lying normal to the slide rail longitudinal direction. The movement of the latter part is translated into movement of a guided parallel to the guide rail movable "longitudinal transmission part". The contact surface of the led on the sliding block movably held part with the guided on the slide normal to the longitudinal direction movably held part is aligned parallel to the slide rail longitudinal direction and extending in Gleitschienenlängsrichtung also appreciably. It is thereby achieved that only the pivoting position of the pivoting arm on the closing sequence control, while the longitudinal movement of the sliding block along the slide rail in a wide range has no influence. In the A60 / 2014 several designs are described in detail with which this general principle can be realized.

Of the construction according to the EP 2 208 846 A2 and the A60 / 2014 Based on the underlying task of the invention, the required optional blocking of pivotal movement of the swinging arm belonging to the moving leaf relative to the sliding block on which this pivoting arm is mounted, to improve in terms that the function even after extremely many and unfavorable working cycles still safe is given and that that opening angle by which the active leaf when opening the inactive leaf must be co-opened so that the Schließfolgesteuerung can work safely is minimal.

For solving the problem it is proposed to provide for the said switchable blocking of pivotal movement of the swinging arm belonging to the swinging arm a holding device comprising a fluid cylinder and at least one valve controlling the fluid cylinder, wherein at least the fluid cylinder is arranged in the slide, there against pivoting movement with the Swivel arm of the active leaf is supported, and optionally acts on the swing arm of the active leaf.

By the term "fluid cylinder" in this document is meant a drive unit comprising a cylinder body and a piston moveable therefrom and a fluid (liquid or gas) and, depending on the embodiment, usually referred to as either "hydraulic cylinder" or "pneumatic cylinder" becomes. For the purposes of this document, which of the two movable parts of the fluid cylinder is referred to as "cylinder body" and which is referred to as "piston" depends on which of the two parts is perceived as moving more than the other part. The less moving perceived part is referred to as a "cylinder body", which is considered more moved parts than "piston". According to the fluid cylinder is attached to the sliding block and mitbewegbar with its sliding movement along the slide rail. Contrary to expectations, this results in simpler construction conditions, as if the fluid cylinder in the slide would not be longitudinally displaceable.

In a preferred embodiment, when the pivoting movement of the pivoting arm is blocked, the movable part (piston) of the fluid cylinder projects into the path of movement of a part which is rigidly connected to the pivoting arm. Since the fluid cylinder thus acts on the pivoting arm by positive locking and not only by frictional engagement, a robustly functioning construction can be realized in which the level of the required braking or holding forces is permanently constant and predictable.

In a further preferred embodiment, that part which is rigidly connected to the swivel arm, a cam which projects radially from the stub shaft mounted on the sliding arm of the swivel arm. Thus, the required introduction of torques in the slide rail is easily accessible and all dimensions of the devices in the normal to the longitudinal direction of the slide rail level can be kept small.

Fig. 1:

zeigt in Teilschnittansicht von oben eine beispielhafte zweiflügelige Schwenktür an welcher die erfindungsgemäßen Vorrichtungen (Haltevorrichtung und Vorrichtung für das Steuern der Schließfolge) vorteilhaft anwendbar sind. Die Türflügel sind in geschlossenem Zustand dargestellt. Die Schwenkrichtungen zum Öffnen der Türflügel sind durch punktierte gekrümmte Pfeillinien angedeutet.

Fig. 2:

zeigt eine beispielhafte erfindungsgemäße Haltevorrichtung in Einbausituation bei leicht geöffnetem Gangflügel in Teilschnittansicht von oben. Soweit es für das Verständnis hilfreich ist sind einzelne verdeckte Linien strichliert eingezeichnet.

Fig. 3:

zeigt die Einbausituation von Fig. 2 in seitlicher Teilschnittansicht um 90° gedreht (In der Darstellung rechts entspricht in der Wirklichkeit unten).

Fig. 4:

zeigt die Haltevorrichtung von Fig. 2 und Fig. 3 in Einbausituation in Teilschnittansicht mit Blickrichtung parallel zur Gleitschiene.

Fig. 5:

zeigt die Haltevorrichtung von Fig. 2 und Fig. 3 zusammen mit zusätzlichen Teilen in Schrägrissansicht mit Blickrichtung von schräg oben.

Fig. 6:

zeigt in seitlicher, um 90° gedrehter Teilschnittansicht eine beispielhafte vorteilhafte standflügelseitige Vorrichtung, welche in Kombination mit einer erfindungsgemäßen Haltevorrichtung angewendet werden kann um eine erfindungsgemäße Vorrichtung für das Steuern der Schließfolge zu bilden. (In der Darstellung rechts entspricht in der Wirklichkeit unten).

Fig. 7:

zeigt in seitlicher, um 90° gedrehter Teilschnittansicht, eine weitere beispielhafte vorteilhafte standflügelseitige Vorrichtung die wie die Vorrichtung von Fig. 6 verwendet werden kann. (In der Darstellung rechts entspricht in der Wirklichkeit unten).

Fig. 8:

zeigt in seitlicher Teilschnittansicht eine vorteilhafte Ausführung von Vorrichtungsteilen im Bereich an dem zum Standflügel gehörenden Gleitstein.

In a further preferred embodiment, two cams are diametrically opposite each other from the stub shaft of the pivot arm and two fluid cylinders are used, and each of the two cams is in each case a movable part of a fluid cylinder at Blockadefall. This results in very favorable static conditions.
The invention as well as advantageous accompanying features and further developments are based on partially strongly stylized drawings, which for the most part are different from each other in scale.

Fig. 1:

shows in partial sectional view from above an exemplary double-winged swing door on which the devices according to the invention (holding device and device for controlling the closing sequence) are advantageously applicable. The door leaves are shown in closed condition. The pivoting directions for opening the door wings are indicated by dotted curved arrow lines.

Fig. 2:

shows an exemplary holding device according to the invention in installation situation with slightly open active leaf in partial section view from above. As far as it is helpful for understanding single hidden lines are drawn by dashed lines.

3:

shows the installation situation of Fig. 2 rotated by 90 ° in partial lateral section view (in the illustration on the right corresponds in reality below).

4:

shows the holding device of Fig. 2 and Fig. 3 in installation situation in partial sectional view with viewing direction parallel to the slide rail.

Fig. 5:

shows the holding device of Fig. 2 and Fig. 3 together with additional parts in oblique view with view diagonally from above.

Fig. 6:

shows in lateral, rotated by 90 ° partial sectional view of an exemplary advantageous passive side device, which can be used in combination with a holding device according to the invention to form a device according to the invention for controlling the closing sequence. (In the illustration right corresponds in reality below).

Fig. 7:

shows in lateral, rotated by 90 ° partial sectional view, another exemplary advantageous passive wing-side device as the device of Fig. 6 can be used. (In the illustration right corresponds in reality below).

Fig. 8:

shows in a side partial sectional view of an advantageous embodiment of device parts in the area of the passive leaf belonging to the sliding block.

The door of Fig. 1 has a moving leaf 1 and a passive leaf 2. The two wings overlap at the contact area, with respect to the opening direction of the active leaf 1 front. Therefore, from the closed state of both wings, the active leaf 1 must be opened in front of the inactive leaf 2, and when closing the passive leaf 2 must be closed in front of the active leaf 1.

The door of Fig. 1 is equipped with sliding rail door closers mounted on the hinge side. In Fig. 1 are of these for both doors 1, 2 common slide 3, the gangway-side pivot arm 4, the gang-wing-side drive unit 5, the stand-wing-side pivot arm 6 and the stand-wing-side drive unit 7 can be seen. "Band mutual mounting" means that the pivot axes of the door leaves 1, 2 are not on the same side of the levels of the door leaves 1, 2 as the drive units 5, 6 but on the opposite side of these levels. In this type of mounting, which is common especially when swung outwardly outward doors, the sliding direction of a sliding block during the closing pivotal movement of a door wing even at a relatively large opening angle of the door to turn.

The slide 3 is stationary fixed in the horizontal direction at the upper, horizontally extending portion of the door frame attached. The drive units 5, 7 are on the door wings 1, 2 attached. Of the drive units 5, 7 in each case a pivot arm 4, 6 projects in each case a sliding block, which is held longitudinally displaceably mounted in the slide rail 3.
The pivot arms 4, 6 are pivotable in horizontal planes; when the door panels 1, 2 closed, they are aligned approximately parallel to the door plane, wherein the sliding-stone-side end of each pivot arm 4, 6 is further away from the pivot axis 8 of the respective associated door leaf 1, 2 than that end which is located on the drive unit 5, 7 ,
Closing movements of the door leaves 1, 2 are driven by the drive units 5, 7, by exerting on the respective associated pivot arm 4, 6 a torque which "seeks" the pivot arm so that it is parallel to the plane of the associated door leaf 1, 2 is aligned.

If both door leaves 1, 2 are open, the closing movement of the active leaf 1 must be stopped in a still-open waiting position until the passive leaf 2 is completely or almost completely closed. This conditional - ie depending on conditions - blocking the closing movement of the active leaf is the central task of the holding device. An exemplary holding device 8 according to the invention, by means of which the conditional blocking of the closing movement of the active leaf 1 is accomplished as intended, is shown in the drawings Fig. 2 to Fig. 5 outlined.
Fig. 2 shows in addition to several items of the holding device 8 and the slide rail 3 and the gangway-side pivot arm. 4

The slide 3 is approximately a U-profile with downwardly open cross-sectional area. In the slide 3, the gangway-side sliding block 9 is held longitudinally displaceable. On sliding block 9, the gangway-side pivot arm 4 is pivotally supported.

In addition to its function as slidable along the slide 3 pivot bearing of the wing-side pivot arm 4, the sliding block 9 in the outlined advantageous embodiment, the function of the housing of the holding device 8. The sliding block 9 has about in the form of an elongated piece of hollow profile whose profile direction parallel is aligned with the slide rail 3 and with its profile walls comprises an elongated cavity 10 aligned parallel to the slide rail direction. For manufacturing and assembly reasons, it is advantageous that the cross-sectional area of the elongated cavity 10 is circular. From the sliding-block-side end of the pivoting arm 4, a stub shaft 11 rigidly connected to the pivoting arm 4 projects through a bore on the underside of the sliding block 9 into the oblong cavity 10 aligned parallel to the slide rail direction. In the cavity 10 protrude from the lateral surface of the stub shaft 11 two cams 12. On the lateral surface of the stub shaft 11, the two cams 12 are diametrically opposite each other. With pivotal movement of the pivot arm 4, the cams 12 are forcibly pivoted about the axis of the stub shaft 11 around.

In the cavity 10, the pistons 13, 14 of two fluid cylinders are arranged, which are aligned parallel to the slide rail 3 and opposite to each other. The cylinder cavities 15, 16 belonging to the pistons 13, 14 are delimited on their lateral surface by lateral surface sections of the cavity 10. The "fixed" part of the fluid cylinder is thus formed in each case by the sliding block 9 itself. In the example sketched, the fluid cylinders are designed as hydraulic cylinders; in the cylinder cavities 15, 16 is therefore oil 17 as working fluid.

Facing away from the cylinder cavities 15, 16, rounded end faces 18, 19 of the two pistons 13, 14 have from opposite sides to the cam 12. With extended piston 13, 14 protrude the end faces 18, 19 in the Movement path, which drive through the cam 12 during pivotal movement of the pivot arm 4, so that thereby cam 12 and end faces 18, 19 collide.

The two cylinder cavities 15, 16 are connected by a connecting channel 20, so that in them the same static oil pressure prevails. The cylinder cavity 15 is sealed at the opposite end of the piston 13 by a sealing in the cavity 10 of the sliding block 9 anchored support member 21. The cylinder cavity 16 is sealed at the opposite end of the piston 14 by a valve block 22, which is also anchored sealingly in the cavity 10 of the sliding block 9.

In the cylinder cavities 15, 16 in each case one on the slide rail parallel aligned pressure force biased elastic spring 23 is arranged. The springs 23 each act between a piston 13, 14 and the opposite end face seal of the cylinder cavity 15, 16. In the absence of other forces, the pistons 13, 14 therefore moved by the action of the springs 23 in their extended end positions.

As in Fig. 3 clearly illustrated, pass through the valve block 22 through several channels connecting the cylinder cavity 16 on one side with the fluid container 24 on the other side, wherein in the channels valves 25, 27, 28 are used.

The control valve 25 has an actuating part 26 which protrudes from a valve sleeve in the absence of other forces due to the action of a compression spring. In this state - the in Fig. 3 is outlined - the control valve 25 is locked. When the actuating member 26 is pressed into the valve sleeve, the control valve 25 is switched to flow so that oil 17 is free between the cylinder cavity 16 (which is constantly with the cylinder cavity 15 is connected) and the fluid container 24 can flow back and forth.
The check valve 27 allows flow from the fluid reservoir 24 into the cylinder cavity 16 unhindered, but blocks oppositely directed flow.
The pressure relief valve 28 allows flow from the cylinder cavity 16 into the fluid reservoir 24 when the pressure in the cylinder cavity 16 is higher by a defined threshold than in the fluid reservoir 24. Flow in the opposite direction is not possible through the pressure relief valve 28.
(Of course, there is the possibility to use instead of three valves with only one function and a smaller number of valves, which then have more than one function.) The closing movement of the active leaf 1 causes a movement of the swing arm 4 consequently the sliding block 9 and thus the whole Holding device 8 is moved along the slide rail 3 and the stub shaft 11 and with this the cam 12 are rotated about the axis of the stub shaft 11 relative to the sliding block 9.
By this rotation, in each case a cam 12 presses on in each case one end face 18, 19 of a piston 13, 14. If the inactive leaf 2 is closed, the actuating part 26 is pressed - the mechanism is explained below - so that the control valve 25 is opened and oil 17 can flow unimpeded from the cylinder cavity 16 into the fluid container 24. By the cam 12, the pistons 13, 14 are pushed back against the action of the springs 23, wherein oil 17 is forced into the fluid container 24. The pivoting movement of the swing arm 4 and thus the closing movement of the active leaf 1 is only slightly damped, but not blocked, so that the active leaf can close completely.
When the active leaf 1 is opened, the cams 12 are moved so that the pistons 13, 14 get more space and extend due to the springs 23. Oil 17 can be independent of the position of the control valve 25 flow freely from the fluid container 24 into the cylinder cavities 15, 16, since the check valve 27 always passes in this direction. Into the fluid container 24, air can flow in through the channel 29. (One could also do without channel 29 and instead provide an air cushion, which is elastically compressible, in the fluid container 24.)

By the cylinder cavity 16, the opening of the extending over the control valve 25 channel is very high, the cylinder cavity 16 is vented automatically during operation.

If from the position in which both doors 1, 2 are closed, the inactive leaf 2 is opened, due to the overlap of the door and usually also due to a driving lever, which projects from the inactive leaf 2 to the active leaf 1, the active leaf forcibly in taken an opening movement. As a result of the opening of the passive leaf, the operating part 26 can extend - the mechanics will be explained below - and the control valve 25 is closed. As already explained, oil 17 can nevertheless flow from the fluid container 24 into the cylinder cavities 15, 16 through the check valve 27 so that the pistons 13, 14 can extend and during the first part of the opening movement of the active leaf 1 with their curved end faces 18, 19 stay in contact with the cam 12.

As soon as the active leaf 1 is opened so far that the inactive leaf 2 can pass the moving leaf 1, the opening movement of the active leaf 1 stops. As a result of the action of the gangway-side drive unit 5, the active leaf 1 would come into closing motion, if not the swivel arm 4 would be rotated so that the cams 12 are pressed against the pistons 13, 14. Since the oil 17 can not escape from the cylinder cavities 15, 16, and thus the pistons 13, 14 can not be pushed into the associated cylinder cavities 15, 16, the pressure in the cylinder cavities 15, 16 increases rapidly to that on the piston 13, 14 a balance between the hydraulic force and the force caused by the drive unit 5 is produced and thus closing movement of the active leaf 1 is blocked. In the case of the opening movement of the active leaf 1 driven by the opening of the inactive leaf 2, the active leaf 1 thus remains in an open waiting position after it has come out of contact with the inactive leaf 2 already after an extremely short return spring travel. Thus, it is sufficient if the active leaf 1 is forcibly co-opened during the opening movement of the passive leaf 2 only a very small piece.

The active leaf 1 is prevented from further closing movement until either the control valve 25 is actuated - which means that the inactive leaf 2 has been closed - or until the pressure relief valve 28 responds. The pressure relief valve 28 is responsible for the overload behavior and adjusted accordingly. It speaks, for example, when trying to open the active leaf 2, the power wing 1 to close by force by pressing them manually with great force in the closing direction.

If the active leaf 1 is fully opened and then released when the fixed leaf 2 is open, the active leaf 1 is only driven by the drive unit 5 to accelerate the closing movement. After some movement meet the according to the closing movement of the active leaf pivoted cam 12 to the extended piston 13, 14. This meeting between cam 12 and piston 13, 14 takes place at a much larger opening angle of the active leaf 1, than that angle at which the active leaf. 1 must necessarily stand still so that the passive leaf 2 can still be closed past him.
As a result of the mass inertia of the active leaf 1, which is in pivoting motion, the cams 12 press with very great force against the pistons 13, 14, so that they are forcibly pushed back. As a result, oil 17 through the pressure relief valve 28 passes through the cylinder cavities 15, 16 pressed into the fluid container 24. As a result, the kinetic energy of the active leaf 1 is reduced by the flow of oil in the pressure relief valve 28. The active leaf is slowed down to the timely style level gently, vibration-free and noiseless or very quiet controlled. This is done without causing any annoying fretting on any part.

Fig. 4 shows a view with the slide rail 3 parallel viewing direction on the side of the fluid container 24 of the holding device 8. The housing of the holding device 8 is formed by the sliding block 9.

When the holding device 8 is used as intended, considerable forces are transmitted from the sliding block 9 to the slide rail 3 when the active leaf 1 is braked in the waiting position in a horizontal direction normal to the slide rail longitudinal direction. With tape - mutual mounting (as in Fig. 1 sketched) these forces are on top of that directed away from the wall on which the slide rail 3 is mounted.

So that these forces and also the torques, which are introduced from the sliding block 9 into the slide rail 3, do not cause disturbing deformation of the slide rail 3, two special measures are provided:

On the one hand, the roughly U-shaped slide rail profile on the outer side of the two lateral limbs, in each case two surface regions 31, which are facing away from the respective lateral outer surface, so that the horizontal component of its surface normal vector (which points from the surface into the environment and not in the material of the slide in) is aligned towards the center of the cross-sectional area of the slide rail profile 3 out. This makes it possible, the slide rail 3 also at its central longitudinal portions with a holder on the wall to which it is attached, to hook so that they at this Mount against movement away from the wall is positively held.
Secondly, the free ends of the two legs of the approximately U-shaped cross-sectional area of the slide rail 3 are bent inwards such that the legs each have a surface area 30 in which the horizontal component of the normal vector points away from the center of the cross-sectional area of the slide rail profile. The sliding block 9 abuts against the surfaces 30 with a counter-oriented surface. Thus, a Verhakung is formed, which causes the ends of the two legs of the slide rail profile are not bent away from each other, since they are forcibly held by the sliding block 9 at the same distance from each other.

As the actuating part 26 of the control valve 25 ( Fig. 2 . Fig. 3 ) is operated well by combining the two drawings Fig. 4 and Fig. 5 understandable:

Two elongated, parallel to the slide 3 aligned release strips 32, 33 are horizontal in the slide 3, ie parallel to the groove base of the groove formed by the slide rail profile displaced. For this they lie in the sliding rails 3 between the groove base and in each case one of the two intermediate walls 34, which project from one of the two side walls of the slide rail profile. The mobility of the release strips 32, 33 in the plane parallel to the groove bottom is limited by a slotted guide on a single track. This train is in Fig. 5 as slots 36 can be seen. The slide guide consists of a plurality of pins 35 which are anchored in the slide rail 3 and from the guide slots 36 in the release strips 32, 33, through which the pins 35 extend therethrough.

In the slide rail profile not only the two release strips 32, 33 are guided horizontally displaceable, but also an actuator 37. This is due to the two release strips 32, 33 on surfaces which are normal to the slide rail longitudinal direction. As a result, the release strips 32, 33 forcibly move the actuator 37 in the slide rail longitudinal direction. However, relative movement of the release strips 32, 33 relative to the actuator 37 is possible in the horizontal direction normal to the slide rail longitudinal direction. Since the guide slots 36 extend at an acute angle to the slide rail longitudinal direction, movement of the release strips 32, 33 in the longitudinal direction of the slide 3 forcibly also a movement of the release strips 32, 33 in the direction transverse to the longitudinal direction of the slide 3. Depending on which direction along the slide 3, the actuator 37 is displaced, the two release strips 32, 33 are moved toward the center of the cross-sectional area of the slide rail 3 or away. When they are shifted toward the center, the actuating part 26 is pressed by the release strips 32, 33; when the release strips 32, 33 are pushed away from the center, the operating member 26 is extended.

The actuator 37 is displaced over a along the slide 3 movable longitudinal transfer member with the stand-wing-side part of the device for controlling the closing sequence in conjunction and depending on whether the inactive leaf 2 is open or closed, more or less to the inactive leaf.

In the example discussed here, the actuator 37 is located at the vane-side end of the release strips 32, 33. When the actuator 37 is moved toward the inactive leaf 2, the release strips 32, 33 are crazy and thus to the profile center of the cross-sectional surface of the slide rail profile, so that the actuating member 26 is pressed is and thus the control valve 25 in the open position - as above to Fig. 3 explained. This pivotal movement of the stub shaft 11 is freely possible and thus the active leaf 1 freely closable. The actuator 37 is thus then moved within its range of motion to the inactive leaf 2, when the inactive leaf 2 is closed.

Of considerable importance is that the contact surfaces of the release strips 32, 33 are aligned with the actuating member 26 parallel to the longitudinal direction of the slide rail 3 and extending far in Gleitschienenlängsrichtung so that the actuating member 26 regardless of the sliding movement of the sliding block 9 with which he is entrained, always can be on the release strips 32, 33. Thus, the function of the operation of the operating member 26 by the release strips 32, 33 regardless of whether and where the sliding direction of the sliding block 9 of the active leaf 1 during the closing movement of the active leaf 1 reverses or not.

In Fig. 6 an exemplary device is sketched, which is mounted in the slide rail 3 and optionally translates pivotal movement of the stand-wing-side pivot arm 6 in movement of the longitudinal transmission part designed as a cable 38 along the slide rail 3. In accordance with the invention, the longitudinal transmission part is the connection between the stand-side module and the gangway-side subassembly of the closing sequence control device is shifted in the other direction. In the illustrated embodiment, the previously described actuator 37 is displaced by the movement of the cable 38 as a function of the position of the inactive leaf 2 and thus stopped or released as a result closing movement of the active leaf.

At the longitudinally slidably held in the slide 3 sliding block 39 of the associated with the inactive leaf 2 pivot arm 6 rigidly connected stub shaft 40 is pivotally mounted about a vertical axis. From the upper, lying in the slide 3 face, projecting from the stub shaft 40 two cams 41, which are symmetrical to each other with respect to the axis of the stub shaft. The cams 41 have flank surfaces which rise obliquely from the stub shaft 40.

Upon rotation of the stub shaft 40, these flank surfaces abut opposite, ie overhanging, oblique flank surfaces of cams 42, which project from the underside of a transverse transfer part 43 downwards.

The transverse transfer member 43 is slidably guided vertically guided on the sliding block 39. When the cams 41 of the stub shaft and the cams 42 of the transverse transfer member 43 abut each other as a result of rotation of the pivot arm 6 and the pivot arm 6 is pivoted further, the further pivotal movement of the pivot arm over the inclined surfaces on the cams 41, 42 into a vertical upward and thus thus translated transverse to the longitudinal direction of the slide rail 3 movement of the transverse transfer member 43 translated.

In its upward movement of the transverse transfer member 43 abuts with its upper, horizontal end face to the lower end face of a carriage 44, which is also horizontal and extends relatively long in Gleitschienenlängsrichtung, for example 10 centimeters. By further movement of the transverse transfer member 43 upwards, the carriage 44 is raised so that it is pressed against a guide block 45 rigidly anchored above the carriage 44 in the slide rail 3.

Guide block 45 and slide 44 lie against each other at three pairs of inclined surfaces 46, which are all parallel to each other and are slightly inclined relative to the slide rail. As a result, the forced lifting of the carriage 44 also forces a displacement of the carriage 44 in the longitudinal direction of the slide rail. The carriage 44 is connected via a rotatably mounted on him roller 47 with the cable 38 in conjunction, which leads to a longitudinal section to the gangway side part of the device for the control of the closing sequence - on the concrete example to the actuator 37. (The second longitudinal section of the cable 38 is adjustably anchored to the slide rail 3. The roller 47 achieves a one-to-two translation of the carriage movement onto the cable 38.)

When the swing arm 6 is pivoted in the opposite direction, the cross transfer member 43 slides on the sliding block 39 downward. The carriage 44 is no longer pressed against the guide block 45. By a - not shown - prestressed elastic spring, it is displaced against the pulling direction of the cable 38 in the slide rail 3. In this case, its movement is guided on a slotted guide which is formed by pins 48 and guide slots 49, wherein the pins 48 are anchored to the carriage 44 and project into the guide slots 49. The guide slots 49 are immovable with respect to the slide rail 3. For this purpose, the guide block 45 in view with the slide rail 3 parallel viewing direction about a U-profile in profile view represent, with the open cross-sectional area is below and the guide slots 49 extend in the side walls of the U-profile.

Of considerable importance, in turn, is that the contact surface between the transverse transfer member 43 and the carriage 44, is aligned parallel to the longitudinal direction of the slide rail and extends relatively far in Gleitschienenlängsrichtung. Thus, the movement of the carriage 44 is in a considerable range, regardless of which longitudinal coordinate of the slide 3, the sliding block 39 of the passive leaf 2 is exactly when the inactive leaf is opened or closed. Thus, the function of the operation of serving as a longitudinal transfer member rope 38 is also given regardless of whether and where the sliding direction of the sliding block 39 of the inactive leaf 2 during the closing movement of the inactive leaf 2 or not. The transmission is thus dependent only on the pivot angle of the pivot arm 6. The pivoting direction of the swing arm 6 does not reverse during the closing movement of the inactive leaf 2.

In Fig. 7 Parts of another exemplary device are sketched, which is mounted in the slide rail 3 and optionally pivotal movement of the stand-wing-side pivot arm 6 in motion of the longitudinal transmission part designed as a cable 38 translated along the slide rail 3. In Fig. 7 are those device parts that are the same as the device according to Fig. 6 can not be shown. These device parts ( Fig. 6 ) are the pivot arm 6 of the passive leaf 2, belonging to this pivot arm 6 sliding block 39 and the transverse transfer member 43rd

In the slide 3, a lever 50 is pivotally anchored in a vertical, parallel to the longitudinal direction of the slide rail 3 level. The lever 50 is very long in Gleitschienenlängsrichtung and its lower surface 51 is aligned substantially parallel to the slide rail longitudinal direction and spaced many times further from the pivot axis of the lever 50 in Gleitschienenlängsrichtung than the transverse transfer member 43 is movable in the vertical direction.

In accordance with the pivoting of the pivot arm forced movement of the transverse transfer member 43 upwards, abuts the transverse transfer member 43 from below to the surface 51 of the lever 50 and thus raises the free end of the lever. This abuts from below to a carriage 52, which is held longitudinally displaceably guided in the slide rail 3. Lever end and slide 52 lie against each other on an inclined surface 53, which is slightly inclined from the horizontal. Upward movement of the lever end forces movement of the carriage 52 in the longitudinal direction of the slide rail.

The carriage 52 is in turn attached to a roller 47, the rope 38, which as in the example according to Fig. 6 with a longitudinal portion leads to the gangway side part of the device for the Schließfolgesteuerung.

It is again important that the contact surface of the transverse transfer member 43 with the lever 50, namely the lower surface 51 of the lever is parallel to the slide rail longitudinal direction and extends itself to a certain extent in Gleitschienenlängsrichtung, since thus the function in a wide range regardless of the coordinate position of the sliding block passive leaf in the longitudinal direction of the slide rail 3.

To be able to adjust when exactly in construction according to Fig. 6 and Fig. 7 by pivotal movement of the passive leaf movement of the transverse transfer member 43 and thus subsequently the longitudinal transfer member (rope 38) begins, you can, for example, the compound of stub shaft 40 and pivot arm 6 solve the two parts to each other pivot and then fix again.

The construction principle of a more comfortable adjustment is in Fig. 8 stylized illustrates:

On sliding block 54, the pivot arm 6 of the passive leaf is rotatably mounted. At the upper end face of the pivot arm 6 belonging to the stub shaft are cams, which as on hand of Fig. 6 described interact with cams of the vertically displaceable transverse transfer member 43, so that at certain portions of the pivotal movement of the pivot arm 6 of the transverse transfer member 43 is raised relative to the sliding block 54.

Unlike the construction of Fig. 6 is in the construction of Fig. 8 the pivoting angle of the transverse transfer member 43 relative to the sliding block 54 about the axis of the stub shaft 40 of the pivot arm 6 around adjustable. For this purpose, the transverse transfer member 43 is not held vertically slidable directly on the sliding block 54 but on a guide member 55. (The guide is realized by bolts on the transverse transfer part 43, which project into bores on the guide part 55). The guide part 55, however, is adjustably and pivotably guided on the sliding block 54 about the pivot axis of the shaft stub 40. For adjusting the pivot angle of the guide member 55 relative to the sliding block 54, a threaded spindle 56 is rotatably supported on the sliding block 54, the axial direction is horizontal, transverse to the slide rail longitudinal direction. The threaded spindle 56 is in engagement with a spindle nut 57 which itself is not rotatable and projects between two fork-tine-shaped extensions of the guide part 55. When the threaded spindle 56 is rotated about its axis, shifts the spindle nut 57 linearly along the threaded spindle 56 and thereby rotates the guide member 55 and thus also the transverse transfer member 43rd

Within the inventive concept, numerous modifications of the previously described and outlined inventive devices are possible. Without claiming to be exhaustive, the following examples are mentioned:

For the gangway-side holding device not necessarily two fluid cylinder need to be provided. One can also make do with a single fluid cylinder. The advantage that fewer parts are needed is then opposite the disadvantage that the load on the stub shaft of the swing arm of the active leaf is much more asymmetrical. (The fact that due to the use of two fluid cylinders of the vane-side sliding is relatively long, is not a disadvantage, since in any case torques must be introduced via the sliding block in the slide and since this can be done with a longer sliding block with smaller forces.)

Instead of executing the or the fluid cylinder as a hydraulic cylinder you can run it as a pneumatic cylinder. Using hydraulic cylinders, however, makes it easier to build very small and to maintain consistent conditions over years and even over temperature fluctuations.

One could apply the described holding device instead of selectively blocking movement of the stub shaft of the gangway side swing arm also on the lowermost sliding block and use to translate pivotal movement of the stub shaft of the swing arm belonging to the passive arm in flow of fluid and thus subsequently the optional blocking or releasing to control the closing movement of the active leaf. The advantage of this would be that you will end up with a smaller number of different parts. Fluid cylinders are still more preferred to apply only to the active leaf, as their advantage is mainly in the controllability of large forces and because such forces only occur at the sides of the wing during normal operation and not on the wing side.

The or the fluid cylinder could instead act as shown positively on the stub shaft of the active leaf on the interposition of brake shoes or the like by friction, so purely positively acting on the stub shaft of the active leaf. While it could provide a more simple holding device, the device would be more susceptible to variations in the level of braking or blocking force.

According to the invention, arranged in the slide holding devices are also applicable to construction of Gleitschienentürschließern in which the slide rail is mounted on the door and is pivoted in the pivoting movements.

LIST OF REFERENCE NUMBERS

1

leaf

2

Fixed leaf

3

slide

4

gangway-side swivel arm

5

Wing-side drive unit

6

Wing-side swivel arm

7

Stand-wing-side drive unit

8th

holder

9

passer-side sliding block

10

cavity

11

Stub shaft (swivel arm active leaf on sliding block)

12

cam

13

piston

14

piston

15

cylinder cavity

16

cylinder cavity

17

oil

18

Front side of the piston 13

19

Front side of the piston 14

20

connecting channel

21

supporting part

22

manifold

23

feather

24

fluid container

25

control valve

26

actuating member

27

check valve

28

Pressure relief valve

29

Channel for air

30

Hooking surface sliding rail sliding block

31

Hooking surface Sliding rail wall mounting

32

initiating claw

33

initiating claw

34

partition

35

pen

36

guide slot

37

actuator

38

Rope (longitudinal transmission part)

39

Sliding block fixed leaf

40

Stub shaft (swing-wing arm on sliding block)

41

cam

42

cam

43

Cross-transmission part

44

carriage

45

guide block

46

inclined surfaces

47

role

48

pen

49

guide slot

50

Swiveling lever

51

Lower surface of the pivoting lever

52

carriage

53

inclined surfaces

54

Sliding block fixed leaf

55

guide part

56

screw

57

spindle nut

Claims (11)

1. Slide rail door closer with fixture (8) for moving and optionally blocking the closing movement of a swivelling door wing, wherein the slide rail door closer has a slide rail (3) and a swivel arm (4), which is supported on both the door wing as well as the surrounding structure eccentrically, relative to the swivel axis of the door wing, and a force acts on it that is aligned in the closing direction of the door wing, and wherein the swivel arm is held rotatably on a slide block (9), which is guided in the slide rail (3), movably in lengthwise direction, and wherein the swivel movement of the swivel arm (4) relative to the slide block (9) can be blocked optionally by the fixture (8),

   - wherein the fixture (8) is arranged in the slide rail (3) and at least comprises a fluid cylinder and a control valve (25), which regulates the flow of the fluid (17) of the fluid cylinder,

   - wherein the fluid cylinder comprises a cylinder part and a movable piston (13, 14) that is guided opposite from it, as well as a cylinder hollow space (15, 16) that is limited jointly by the cylinder part and the piston (13, 14) and contains the fluid (17),

   - wherein the cylinder part on the slide rail (3) is stabilised against swivel movements parallel to the level of the swivel arm (4) and the travel path of the piston (13, 14), which defined by the guidance on the cylinder part, leads, for the blocking of the swivel movement of the swivel arm, to the swivel arm (4) and/or to a part that is movable by force through the movement of the swivel arm (4),
   characterised in that

   - the fluid cylinder of the fixture (8) is mounted on the slide block and can be driven in lengthwise direction together with the slide block (9) in the slide rail (3).
2. Slide rail door closer with fixture (8) according to claim 1, characterised in that the relative movement of the piston (13, 14) in relation to the cylinder body can be driven by a pretensioned elastic spring (23).
3. Slide rail door closer with fixture (8) according to claim 1 or 2, characterised in that, through the swivel movement of the swivel arm (4), the relative movement of the piston (13, 14) can be driven relative to the cylinder body and the flow of the fluid (17) that can be forced by this relative movement is led through an pressure relief valve (28).
4. Fixture (8) according to claim 2 and 3, characterised in that relative movement of the piston (13, 14), in the direction in which the volume of the cylinder hollow space (15, 16) increases, can be moved by the spring (23) and the relative movement in the opposite direction can be driven by the swivel movement of the swivel arm (4).
5. Slide rail door closer with fixture (8) according to one of the claims 1 to 4, characterised in that the slide block (9) itself is the cylinder part of the fluid cylinder.
6. Slide rail door closer with fixture (8) according to claim 5, characterised in that the swivel arm (4) is connected rigidly with a shaft end (11), which is mounted swivelling on the slide block (9) and protrudes, with a longitudinal section, into the volume contained by the slide rail (3) and is exposed, on this longitudinal section, to a force that is caused by the sliding of the piston (13, 14) relative to the cylinder part.
7. Slide rail door closer with fixture (8) according to claim 6, characterised in that the travel path of the piston (13, 14) protrudes radially to the surface of a part, which is also swivelled by the swivel movement of the shaft end (11).
8. Slide rail door closer with fixture (8) according to claim 7, characterised in that the travel paths of two pistons (13, 14) protrude, from radially opposite sides, the surface of parts, which are also swivelled by the swivel movement of the shaft end (11).
9. Slide rail door closer with fixture (8) according to one of the claims 1 to 8, characterised in that, depending on the position of the control valve (25), the flow of fluid (17) from and/or into the cylinder hollow space (15, 16) can be blocked or released, and in that the control valve (25) has an operating part (26), which can be activated by a movable part (32, 33) that is guided on the slide rail (3) traversely to its lengthwise direction, and in that a contact area between the guided movable part (32, 33) and the operating part (26) is aligned parallel to the lengthwise direction of the slide rail (3) and extends over several centimetres in the lengthwise direction of the slide rail (3).
10. Two-winged swivelling door that has an underlaying, so-called inactive wing (2), and an overlaying, so-called active wing (1), wherein the door wings (1, 2) are equipped with slide rail closers, wherein the swivel movement of the swivel arm (4) belonging to the active wing (1) is blocked for blocking the closing movement of the active wing (1) with opened inactive wing (2), characterised in that the active wing (1) is equipped with a slide rail door closer with fixture (8) according to claims 1 to 9.
11. Two-winged swivelling door according to claim 10, characterised in that the swivel movement of the swivel arm (6) belonging to the inactive wing (2) can be transformed into a movement of a traverse transmission part (43), which is mounted movably and guided on the slide block on the side of the inactive wing (39, 54), wherein the movement of the traverse transmission part (43) has a direction component that is aligned normally in the lengthwise direction of the slide rail, and in that the movement of the traverse transmission part (43) can be transformed by gear parts (44, 51), which are mounted movably and guided in the slide rail (3), into a movement of a longitudinal transmission part (38) parallel to the lengthwise direction of the slide rail, and in that the control valve (25) can be activated by movement of the longitudinal transmission part (38), and in that a contact area of the traverse transmission part (43) with the gear parts (44, 51) is aligned parallel to the direction of the lengthwise direction of the slide rail and extends over several centimetres in the lengthwise direction of the slide rail.

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