EP0863286B1 - Closer for a door or the like - Google Patents

Description

The invention relates to a closer between a fixed frame and a door or the like, which can be pivoted relative to this, with a locking mechanism which has at least one drive slide, at least one control slide and at least one control lever, via which the drive and control slide are in drive connection with one another , comprises, the drive slide on the wing or on the frame in the direction of the wing or the main plane of the frame and a transverse to the wing or the frame main plane of the wing or frame end face against the action of a restoring force from a starting position assigned to the closed position of the wing is displaceable in an opening position assigned to the wing and the control slide on the wing or on the frame is displaceably guided in the direction of the wing or frame main plane and transversely to the wing or the frame end face and is supported on the frame or on the wing in the direction of displacement is.

Devices of this type are used, for example, in the form of folding door closers. For example, for aesthetic reasons, the components of the closer or the locking mechanism are recessed into the sash or the fixed frame from the outside.

From US-A-1,952,070 a door closer of the above type is known, the locking mechanism of which comprises a drive slide in the form of a piston rod which is guided in a vertical direction in an assembly chamber of the door leaf and a control slide which can also be displaced transversely to the direction of movement of the piston rod and is designed as a slide piece , The slider and piston rod are connected to one another via an angle lever that takes over the function of a control lever, which, in addition to the articulation points connecting it to the slider and the piston rod, is pivotably articulated on the door leaf or the closer housing integrated in the door leaf about an axis running transversely to the main plane of the leaf is. The slider has a guide slot running transversely to its direction of displacement, which slits the slider with the Joint axis connecting joint lever slidably receives in the longitudinal slot direction. Overall, a locking mechanism with a relatively complicated configuration results on the previously known closer.

To remedy this disadvantage, the present invention has set itself the goal.

According to the invention, the stated object is achieved in that the control lever is articulated on a closer of the type mentioned at the outset exclusively to the drive slide and to the control slide, and in this case can only be pivoted about an axis running transversely to the sash or the main plane of the frame. In the case of the locking gear part described, designed in the manner of a toggle lever, the number of articulation points required for mounting the control lever or the control lever is minimized; the bearing type selected for the control lever (s) is limited to pure swivel mounting.

In the sense of a defined guidance of the control slide and thus the articulation point provided for the control lever, it is provided in an expedient development of the invention that the control slide is displaceable between the legs of a guide bracket sunk into the wing or into the frame from the wing or from the frame end face is led. The leg surfaces of the guide bracket give the movement path of the control spool in front and support it safely to avoid undesired tilting movements, for example.

A further perfection of the guidance of the control slide serves that, in the case of a further variant of the closer according to the invention, at least one guide projection protruding transversely to the direction of displacement and at least one leg of the guide bracket has a guide slot running in the direction of displacement of the control slide for receiving the assigned guide approach of the control slide Control spool is provided.

If the control slide is slidably attached to the sash, it must be supported on the frame in the direction of displacement. When the control spool is movably mounted on the frame, the wing must be supported accordingly. In both cases, the support is carried out at a bearing point remote from the pivot axis of the wing, since only under this condition is a shifting movement of the control slide transverse to the wing or frame end face associated with the pivoting movement of the wing. Due to the described storage conditions, there is also a movement of the control slide parallel to itself perpendicular to the wing or the main frame plane parallel to itself relative to the position of its support on the frame or on the wing. In order that this relative movement can be carried out without bending stress or deformation of the closing gear parts involved, is in a further expedient embodiment the invention of the control slide on the frame or on the wing supported by at least one connecting arm which is pivotally mounted on the one hand on the control slide and on the other hand on the frame or on the wing about an axis extending in the direction of the wing or the main frame plane.

The above-described configuration of the closing mechanism according to the invention makes it possible to make not only the storage of the control lever but also the control lever itself extremely simple. A corresponding advantage is characterized by an embodiment of the closer according to the invention, whose at least one control lever is designed in the manner of a tab.

A variant of the invention, in the case of which the drive slide can be supported against the direction of its movement in the open position on the wing or on the frame and is acted upon by a closing spring which produces the restoring force acting thereon and is supported on the wing or on the frame, for which An adjusting device for adjusting the spring preload is provided, characterized in that the adjusting device for adjusting the spring preload has an adjusting spindle which runs with its axis in the direction of action of the restoring force and can be driven to rotate about said axis, and an adjusting spindle which can be moved thereon by rotating the adjusting spindle in the axial direction of the adjusting spindle Set nut includes, the adjusting spindle on the drive slide and the adjusting nut on the support on the Wing or on the frame opposite side of the closing spring is supported. The amount of the restoring force acting on the drive slide for closing the wing can be set on such a closer with structurally simple and robust, permanently functional technical means in operation. A change in the closing force by varying the closing spring preload must be carried out in particular to adapt the effective restoring or closing force to different door widths. With a kinematic reversal of the movement sequences resulting for the individual parts of the aforementioned adjusting device, in deviation from the constructive solution described above, the adjusting spindle can also be rotatably fixed and the adjusting nut arranged thereon can be rotatably mounted.

In a further development of the invention, the rotary drive of the adjusting spindle is accomplished by means of a lockable bevel spur gear, which comprises a first bevel spur gear arranged coaxially with the adjusting spindle and non-rotatably connected to the adjusting spindle as well as a second bevel spur gear connected to the drive, which is oriented about an axis transverse to the axis of the first bevel spur gear is rotatably accessible from the wing or the frame end face for a drive device. On the basis of the described structural features, the actuating device in question can be actuated in a few simple steps with the sash open. A manual setting is preferred, which is made possible by the fact that the second bevel gear with a is easily accessible intervention for a hand-operated tool.

On a closer according to the invention with a damping device for the drive slide moving from an open position in the direction of the starting position, with a damping cylinder containing a damping medium and with a damping piston which can be displaced relative to the damping cylinder when the drive slide moves, the damping cylinder or the damping piston with the drive slide is motion-connected and in the damping cylinder in the direction of the relative movement of the damping cylinder and damping piston on both sides of the damping piston when the drive slide moves toward the starting position via at least one overflow channel for damping medium interconnectable cylinder spaces are provided, the effective flow cross section of the overflow channel is adjustable. As is known, the damping device ensures that the wing pivoted in the open position is transferred to the closed position under the action of the restoring force exerted on the drive slide. In the course of the closing movement of the wing, damping medium which is present in the cylinder space on one side of the damping piston is displaced as a result of the relative movement of the damping cylinder and damping piston through the overflow channel into the cylinder space located on the opposite side of the damping piston. The mass flow of this displacement determines the amount of speed at which the wing moves to the closed position. Against this background, the adjustability of the effective flow cross-section of the overflow channel according to the invention offers the possibility of influencing the mass flow mentioned and thereby specifying the closing speed of the wing in a manner which is tailored to the individual case.

In cases in which the damping cylinder is motionally connected to the drive slide, in a further development of the invention the damping piston is held on the wing or on the frame via at least one piston rod, on which at least part of the overflow channel is provided for damping medium and on which at least one in Different shift positions lockable valve rod is guided displaceably relative to the piston rod, the overflow channel having a control surface or edge limiting its effective flow cross-section, against which the valve rod can be adjusted with a control counter surface or counter edge by displacement relative to the piston rod. The described positioning of the valve rod with respect to the piston rod allows the relative position of the control surface or edge on the piston rod side and of the control counter surface or counter edge on the valve rod side to be varied. A change in the effective flow cross section of the overflow channel is associated with the change in relative position described. By shifting the valve stem relative to the piston rod Accordingly, the above-mentioned setting of the closing speed of the wing can be carried out.

In order to accommodate the closer components in question in a space-saving manner, a further embodiment of the closer according to the invention provides that the piston rod is hollow, with a free inner cross section, and the valve rod can be displaced in the free inner cross section of the piston rod relative to the latter in the axial direction.

The adjustability of the valve rod relative to the piston rod is made possible in a further development of the invention in that the valve rod is supported on the wing or on the frame so as to be displaceable in the axial direction relative to the piston rod via a positioning eccentric.

So that, for example, the latchbolt of a lock attached to a door leaf can be automatically and securely engaged with an assigned bolt latch on the fixed frame by means of a closer that is effective between the door leaf and the fixed door frame, the leaf should move at a relatively high rate in the final phase of its closing movement Move closing speed. For this purpose, according to the invention, at least one bypass channel for damping medium is provided, via which the cylinder spaces are connected to one another on both sides of the damping piston when the damping piston is relative to the damping cylinder assumes a position assigned to a position of the drive slide close to the starting position. When the bypass channel cross section becomes effective, the flow cross section available for displacing the damping medium from one side of the damping piston to its opposite side increases. This reduces the force exerted by the damping device and counteracts the closing movement of the leaf, so that the leaf can cover the last part of its closing pivoting movement at a relatively high speed.

An embodiment of the closer according to the invention is distinguished by manufacturing advantages, in which the bypass channel is formed by a radial widening on the inner wall of the damping cylinder facing the damping piston, the extent of which in the axial direction of the damping cylinder exceeds the corresponding extent of the damping piston. Such a bypass channel can be incorporated into the inner wall of the damping cylinder with little effort.

In the sense of the invention, the cross section of the bypass channel, via which damping medium is displaced from one cylinder space into the other cylinder space arranged on the opposite side of the damping piston during the final closing movement of the wing, can be constant. In the case of a preferred variant of the closer according to the invention, however, the cross section increases the radial widening on the inner wall of the damping cylinder in the direction of movement of the damping piston relative to the damping cylinder associated with the movement of the drive slide in the direction of its starting position. This results in a progressive closing speed curve in the final phase of the wing closing movement.

Are on a closer, the damping device has a bypass channel of the type described, the damping piston and the damping cylinder in the axial direction relative to each other, as is also possible according to the invention, can be adjusted by such an adjustment, the size of the closing movement of the wing specify the remaining opening angle at which the acceleration of the closing movement begins. Depending on the basic setting of the damping piston relative to the damping cylinder, the bypass connection between the cylinder spaces present on the two sides of the damping piston is made with a larger or smaller residual opening angle of the wing. There is the described possibility of setting the wing acceleration time regardless of whether the bypass channel has a constant or a changing cross section. If a radial extension provided with a variable cross-section on the inner wall of the damping cylinder, as described above, is used as the bypass channel, the set relative position of the damping piston and damping cylinder also has an effect the attainable final wing speed. Depending on the setting of the damping piston relative to the damping cylinder, a more or less large bypass channel cross section is available at the time the wing closes to displace the damping medium.

The axial adjustment of the damping piston relative to the damping cylinder can be carried out in a few simple steps and using structurally simple means if - as provided in the case of a preferred embodiment of the invention - the damping piston is adjustable in the axial direction relative to the damping cylinder via at least one piston rod and in the assumed position is supported on the wing or on the frame.

Fig. 1:

einen Falztürschließer in Einbaulage an einer Tür mit geschlossenem Flügel,

Fig. 2:

eine Schnittdarstellung zu dem Falztürschließer gemäß Figur 1 mit einer parallel zu der Flügelhauptebene verlaufenden Schnittebene,

Fig. 3:

den Falztürschließer gemäß den Figuren 1 und 2 bei geöffnetem Flügel mit einem Flügelöffnungswinkel von 90°,

Fig. 4:

eine Schnittdarstellung des Falztürschließers gemäß Figur 3 mit einer parallel zu der Flügelhauptebene verlaufenden Schnittebene,

Fign. 5a und 5b:

vergrößerte Darstellungen zu dem Ausschnitt V von Figur 2 und

Fign. 6a bis 6g:

vergrößerte Darstellungen zu dem Ausschnitt VI von Figur 2.

The invention is explained in more detail below with reference to schematic representations of an exemplary embodiment. Show it:

Fig. 1:

a rebate door closer in the installed position on a door with a closed leaf,

Fig. 2:

2 shows a sectional view of the rebate door closer according to FIG. 1 with a sectional plane running parallel to the main wing plane,

Fig. 3:

the rebate door closer according to Figures 1 and 2 with the sash open with a sash opening angle of 90 °,

Fig. 4:

3 shows a sectional view of the rebate door closer according to FIG. 3 with a sectional plane running parallel to the main wing plane,

FIGS. 5a and 5b:

enlarged representations of the section V of Figure 2 and

FIGS. 6a to 6g:

enlarged representations of section VI of Figure 2.

The illustrations relate to a folding door closer 1, which is arranged between a fixed frame 2 and a wing 4 pivotally mounted thereon about a pivot axis 3. As can be seen in particular from FIGS. 1 and 3, the folding door closer 1 is installed, for aesthetic reasons, in a recessed manner in a wing face 5 running perpendicular to the main wing plane. A frame insert 6 in the form of a bearing block is screwed to the fixed frame 2.

A housing 7 of the folding door closer 1 consists essentially of two housing parts running at right angles to one another, the horizontal housing part being formed by a guide bracket 8 and the vertical housing part being formed by a housing box 10 connected to the wing 4 on a screw-on plate 9.

As shown in particular in FIGS. 2 to 4, a control slide 13 is guided between legs 11, 12 of the guide bracket 8 so as to be displaceable perpendicular to the wing end face 5 in the direction of a double arrow 14. For the purpose of defined guidance, the control slide 13 is provided with guide projections 15 projecting transversely to the direction of displacement 14. The guide lugs 15 are formed by the free ends of two notches fitted in the control slide 13. To accommodate the guide lugs 15, guide slots 16 on the legs 11, 12 of the guide bracket 8 are used in the displacement direction 14 of the control slide 13. At the end of the control slide 13 facing the wing end face 5, a connecting arm 17 is articulated, via which the control slide 13 with the frame insert 6 is connected to the fixed frame 2. The connecting arm 17 is pivotably mounted on the control slide 13 about an axis 18 running in the direction of the main wing plane, and on the frame insert 6 about an axis 19 parallel to the axis 18. The axis 19 extends laterally offset with respect to the pivot axis 3 of the wing 4.

On the side of the control slide 13 facing away from the wing end face 5, two tab-like control levers 20 which are arranged parallel to one another are pivotably articulated about an axis 21 running perpendicular to the main wing plane. With their opposite ends, the control levers 20 are mounted on a drive slide 23 so as to be pivotable about an axis 22 likewise oriented perpendicular to the main wing plane. The drive slide 23 is slidably guided in the housing box 10 in the direction of a double arrow 24.

In correspondingly designed recesses, the drive slide 23 receives a first bevel gear 25 and a second bevel gear 26 meshing therewith. The first bevel spur gear 25 is arranged coaxially with an adjusting spindle 27 and riveted to the latter with rotation about an axis of rotation 28. The second bevel gear 26 is rotatably mounted on the drive slide 23 about an axis of rotation 29 running perpendicular to the axis of rotation 28 and is provided with a hexagon socket 30 as an engagement for a corresponding actuating tool.

With its external thread, the adjusting spindle 27 engages in the internal thread of an adjusting nut 31, which is designed as an adjusting plate and is held in the housing box 10 so as to be displaceable against rotation with the adjusting spindle 27 about the axis of rotation 28 and on the adjusting spindle 27 in the direction of the double arrow 24.

On its underside, the adjusting nut 31 supports a closing spring 32 designed as a helical compression spring and pretensioned in its starting position according to FIG. 2. At its end opposite the adjusting nut 31, the closing spring 32 is supported on two rivet pins 33 arranged parallel to one another, of which in FIGS 4 only one can be seen and which are connected to the wing 4 via the housing box 10. The interior of the housing box 10 is accessible via a bore 34 in the screw-on plate 9.

The closing spring 32 surrounds a damping cylinder 35 aligned coaxially with it, which, like a damping piston 36 which is displaceably guided in the interior thereof in the direction of the double arrow 24, is an integral part of a damping device for the drive slide 23. At its end facing the drive slide 23, the damping cylinder 35 is firmly connected to an extension of the adjusting spindle 27.

At the opposite end, the damping cylinder 35 is closed with a cylinder cover 37. The latter is provided with a passage with a circular cross section for a piston rod 38, via which the damping piston 36 is supported on an adjusting bracket 39. The piston rod 38 is screwed with a threaded end into a threaded bore 43 of the adjusting block 39, which is also shown in FIG. 6. The adjustment bracket 39 can be implemented in the interior of the housing box 10 in the direction of the double arrow 24 and can be fixed in the position assumed in each case by means of a clamping screw 41 which passes through the screw-on plate 9 of the housing box 10 at an elongated hole 42 running in the direction of the piston rod 38 and engages with its external thread in a threaded bore 40 of the adjusting block 39 (inter alia FIG. 6a).

As shown in FIGS. 5a and 5b in an enlarged representation, a radial extension 44 is worked into the inner wall of the damping cylinder 35 near the cylinder cover 37, which has the shape of a groove widening in a wedge shape towards the lower end of the damping cylinder 35. The inside of the damping piston 36 is provided with passages 45, via which a cylinder space 46 formed on one side of the damping piston 36 can be connected to a cylinder space 47 on the opposite side of the damping piston 36. In front of the openings of the passages 45 into the lower cylinder space 46, a valve ring 48 is attached to the piston rod 38, which is displaceable in the axial direction of the piston rod 38 and is underpinned on the side facing away from the damping piston 36 by means of a circlip.

The piston rod 38 is also provided with an external thread at its end assigned to the damping piston 36. By means of this external thread, the relevant piston rod end is screwed into a corresponding internal thread of the damping piston 36.

The piston rod 38 is hollow to form a free inner cross section and accommodates a valve rod 49 arranged concentrically with it inside. The latter has a stepped outer diameter, a section 50 of smaller diameter ending in a conical tip 51. An annular space 52 remains between the inner wall of the piston rod 38 and the outer wall of the section 50 of the valve rod 49. A wall bore 53 of the piston rod 38 opens into this annular space. An annular gap 54 adjoins the annular space 52 and leads to the cylinder space 47 Conical surface 55 of the conical tip 51 of the valve rod 49 and a counter surface 56 opposite this remains on the damping piston 36. Finally, the annular gap 54 widens to form an inner cone 57 of the damping piston 36 opening into the cylinder space 47.

The cylinder spaces 46 and 47 contain damping medium, in the case shown hydraulic oil. The wall bore 53, the annular space 52, the annular gap 54 and the inner cone 57 of the damping piston 36 form an overflow channel connecting the cylinder spaces 46, 47, the effective flow cross section of which in the area of the annular gap 54 through the conical surface 55 of the valve rod 49 and the opposing surface 56 of the damping piston 36 is limited. The counter surface 56 on the damping piston 36 serves as a control surface, the conical surface 55 on the valve rod 49 as a control counter surface, the conical surface 55 by displacing the valve rod 49 relative to the piston rod 38 is deliverable in the axial direction relative to the counter surface 56.

The described displacement of the valve rod 49 with respect to the piston rod 38 is accomplished by means of constructive measures, which can be seen in particular from FIGS. 2 and 4 in connection with FIGS. 6a to 6g.

Accordingly, an adjusting ring 58 is attached to the lower end of the valve rod 49 (FIGS. 6f and 6g). In the installed position, the adjusting ring 58 is penetrated by an adjusting eccentric 59 (FIGS. 6d and 6e), an eccentric cylinder section 60 of the adjusting eccentric 59 being supported on the inner wall of the adjusting ring 58 located above. A clip 61 (FIG. 6c) made of sufficiently elastic plastic is clipped axially adjacent to the eccentric cylinder section 60 onto central cylinder sections 62 of the positioning eccentric 59. The positioning eccentric 59 is rotatably supported in each case in a bearing opening 63 of the clips 61 via the central cylinder sections 62. Hook-like arms 64 of the clips 61 surround the adjusting bracket 39 and thus create a connection between the assembly consisting of the adjusting eccentric 59 and the valve rod 49 and the housing box 10 and thereby the wing 4.

If the wing 4 is pivoted in the opening direction from its closed position shown in FIGS. 1 and 2, the lateral offset of the axis 19 of the connecting arm 17 relative to the pivot axis 3 of the wing leads to a translatory movement of the connecting arm 17 relative to the wing 4 The connecting arm 17 moves in the direction of an arrow 14a and takes the control slide 13 mounted on the guide bracket 8 with it.

The translational movement of the control slide 13 transversely to the wing end face 5 is transmitted via the control lever 20 to the drive slide 23 and causes its displacement inside the housing box 10 in the direction of an arrow 24a parallel to the wing end face 5. The prerequisite for the kinematics described is the existence of a angle α of more than 0 ° and less than 90 ° between the direction of movement 14a of the control slide 13 and the connecting path of the axes 21 and 22 of the control levers 20 when the wing 4 is in the closed position.

When it is displaced in the direction of movement 24a, the drive slide 23 acts on the damping cylinder 35 in the same direction via the adjusting spindle 27 supported on it. As a result, there is a displacement of the damping cylinder 35 with respect to the damping piston 36, which is mounted in a wing-fixed manner via the piston rod 38, the adjusting bracket 39 and the clamping screw 41 cooperating with the latter. As a result of this relative movement Damping medium from damping cylinder 35 and damping piston 36 is present in the cylinder space 47 of the damping cylinder 35 via the passages 45 of the damping piston 36 and through the overflow channel, which is provided by the inner cone 57 of the damping piston 36, the annular gap 54, the annular space 52 and the wall bore 53 of the piston rod 38 is formed, displaced into the cylinder chamber 46 of the damping cylinder 35. A relatively large flow cross-section is available to the damping medium, so that the displacement movement of the damping cylinder 35 in the direction of movement 24a is at best counteracted by a slight hydraulic resistance.

A restoring force is exerted on the drive slide 23 by the closing spring 32. This is acted upon by the drive slide 23 via the adjusting nut 31 seated on the adjusting spindle 27 supported on the drive slide 23. After the closing spring 32 is mounted in a wing-fixed manner at its end opposite the drive slide 23, namely on the rivet pins 33, this action by the drive slide 23 leads to a spring compression. Since the closing spring 32 is a spring with a progressive characteristic curve, the amount of the reaction force exerted by the closing spring 32 on the drive slide 23 during its movement in the direction of arrow 24a increases with the amount of said movement of the drive slide 23. As a result, when opening the wing 4 itself to overcome a counterforce increasing with the wing opening angle.

Such an opening force profile, which is unsuitable for practical door closers, can be avoided by the toggle-like coupling of the control slide 13, the control lever 20 and the drive slide 23. An acute angle δ between the axis of movement of the drive slide 23 and the connecting path of the axes 21, 22 of the control levers 20 thus decreases with increasing door opening angle. In accordance with the known force relationships on toggle lever mechanisms, the reduction in the angle δ is associated with an increase in the amount of the component of the force applied by the user of the door acting in the axial direction of the movement of the drive slide 23. This increase in force overcompensates for the increase in the counterforce exerted by the closing spring 32 on the drive slide 23 against its direction of movement 24a, so that overall, with increasing door opening angle, there is a degressive course of the amount of the opening force to be initiated by the user of the door into the wing 4.

With an opening angle of the wing 4 of 90 °, the components of the door closer gear shown take up the position shown in FIG. 4 relative to one another. The second bevel spur gear 26, which is rotatably mounted on the drive slide 23 about its axis of rotation 29, lies with its hexagon socket 30 at the level of the bore 34 the screw-on plate 9 of the housing box 10. If the pretensioning of the closing spring 32 and thus the force exerted by the latter when opening and closing the leaf 4 are to be changed, a corresponding actuating tool can now be used from the end face 5 of the wing through the bore 34 into the hexagon socket 30 of the second bevel gear 26 are introduced. By subsequently rotating the second bevel spur gear 26 when the wing 4 is fixed in the assumed open position, the adjusting spindle 27 can also be rotated via the first bevel spur gear 25. This is associated with a translational change in position of the adjusting nut 31 on the adjusting spindle 27. This in turn changes the length of the closing spring 32 supported on the wing-fixed rivet pins 33 on the opposite side and thus the pretension thereof.

If the sash 4, which is arranged with an opening angle of 90 ° relative to the fixed frame 2, is released, the closing spring 32 compressed according to FIG. 4 lengthens and thereby displaces the drive slide 23 via the adjusting nut 31 and the adjusting spindle 27 in the direction of an arrow 24b and thus in Direction to the starting position of the drive slide 23 according to Figure 2. The translational movement of the drive slide 23 in the direction of arrow 24b is transmitted via the control lever 20 to the control slide 13 and causes the latter to move in the direction of an arrow 14b and thus also in the direction of his Starting position shifts according to Figure 2. This is a prerequisite for this kinematics There is an angle β of more than 0 ° and less than 90 ° included by the direction of movement 24b of the drive slide 23 and the connecting path of the axes 21, 22 of the control levers 20. With the displacement of the control slide 13 in the direction of arrow 14b, the wing 4 is closed by the connecting arm 17.

The damping cylinder 35 is carried by the drive slide 23 in the direction of movement 24b, which accordingly moves in the corresponding axial direction relative to the wing-fixed damping piston 36. As a result, damping medium present in the cylinder space 46 of the damping cylinder 35 is displaced into the cylinder space 47 of the damping cylinder 35. However, only the overflow channel, consisting of the wall bore 53 of the piston rod 38, the annular space 52, the annular gap 54 and the inner cone 57 of the damping piston 36, is available as the flow path for the damping medium. The openings of the passages 45 of the damping piston 36 into the cylinder space 46 are closed by the valve ring 48, which is not shown in FIGS. 5a and 5b. The latter was carried along by the damping medium which flowed out of the cylinder space 46 under the effect of the excess pressure built up in the cylinder space 46 as a result of the relative movement of the damping cylinder 35 and the damping piston 36. The valve ring 48 was shifted upward from its initial position shown in FIG. 5a and has since covered the mouths of the passages 45 in a sealing manner. One of the damping medium Flowable area was available on the underside of the valve ring 48, since the circlip bearing the valve ring 48 does not completely cover the surface of the valve ring 48 facing it in the starting position.

Since the damping medium flowing out of the cylinder chamber 46 of the damping cylinder 35 into the cylinder chamber 47 has only a relatively small flow cross-section, the return movement of the damping cylinder 35 or the drive slide 23 caused by the closing spring 32 is opposed by a relatively large hydraulic resistance.

The extent of the resulting damping of the return movement of the drive slide 23 can be varied by axially adjusting the valve rod 49 arranged inside the hollow piston rod 38. For this purpose, the eccentric 59 accessible from the wing end face 5 and provided with an engagement for a Phillips screwdriver is to be rotated about the axis of its central cylindrical sections 62. Via the eccentric cylinder section 60, which is supported on the inner wall of the adjusting ring 58 provided at the lower end of the valve rod 49, the valve rod 49 is displaced in the axial direction of the piston rod 38 when the actuating eccentric 59 is rotated. With the displacement of the valve rod 49 in the interior of the piston rod 38, a feed movement of the conical surface provided on the conical tip 51 of the valve rod 49 is connected 55 relative to the mating surface 56 of the damping piston 36 assigned to it. This infeed movement in turn, depending on the infeed direction, requires an expansion or a narrowing of the annular gap 54 between the valve rod 49 and the damping piston 36 and thus a variation of the flow cross section for that from the cylinder space 46 into the cylinder space 47 displaced damping medium.

When the wing 4, actuated by the closing spring 32, approaches its starting closed position, the damping piston 36 reaches the area of the radial extension 44 on the inner wall of the damping cylinder 35. Since the axial extension of the radial extension 44 of the damping cylinder 35 is greater than that Axial extension of the damping piston 36, a bypass connection bypassing the damping piston 36 can be established between the cylinder spaces 46, 47 of the damping cylinder 35 via the radial extension 44 of the damping cylinder 35 as soon as the axial start. the radial extension 44 on the inner wall of the damping cylinder 35 which has passed through the upper end face of the damping piston 36 in the direction of arrow 24b in the figures. Due to the radial expansion 44 of the damping cylinder 35, a bypass channel is now formed in cooperation with the assigned area of the axial lateral surface of the damping piston 36, due to which the flow cross-section for the damping medium displaced from the cylinder space 46 into the cylinder space 47 is considerable increased. When this bypass channel begins to be used as an outflow path for damping medium from the cylinder space 46, the hydraulic resistance to the displacement of the damping cylinder 35 with respect to the damping piston 36 in the direction of arrow 24b decreases. This is equivalent to an acceleration of the movement of the drive slide 23 in the direction of movement 24b, which in turn is converted into an acceleration of the wing 4 via the control lever 20, the control slide 13 and the connecting arm 17. After the bypass channel remains open until the leaf 4 reaches the closed position, it is ensured that even a relatively difficult latch bolt of a lock attached to the leaf 4 is automatically brought into engagement with an associated bolt latch on the fixed frame 2.

The closing-end movement of the wing 4, referred to as the "door slam", can be influenced by axially adjusting the damping piston 36 relative to the damping cylinder 35. The basic axial setting of the damping piston 36 and the damping cylinder 35 thus determines the opening angle of the wing 4 at which the bypass connection between the cylinder spaces 46, 47 of the damping cylinder 35 is established via its radial extension 44. Given the wedge shape of the radial extension 44 in the axial direction of the damping cylinder 35, the basic axial setting of the damping piston 36 relative to the damping cylinder 35 also determines the size of the cross section of the effective bypass connection and thus the extent of the reduction in hydraulic Resistance to the displacement of the damping cylinder 35 relative to the damping piston 36 in the direction of movement 24b.

If the damping piston 36 is displaced axially relatively far upward in the figures relative to the damping cylinder 35, for example, when the wing 4 is pivoted into its closed starting position, the bypass connection between the cylinder spaces 46 and 47 via the radial extension 44 of the damping cylinder 35 is only at one relatively small door opening angle. At the same time, the radial enlargement 44 on the inner wall of the damping cylinder 35 moves only over a relatively small axial length along the upper end face of the damping piston 36 in the course of the accelerated closing-end movement of the wing 4. The height of the upper end face of the damping piston 36 therefore stands only a relatively small bypass channel cross section is available.

The adjustment of the axial relative position of damping piston 36 and damping cylinder 35 is accomplished by moving the adjusting bracket 39. For this purpose, given the relative arrangement of damping piston 36 and damping cylinder 35, the clamping screw 41 must first be loosened from the wing end face 5. Subsequently, the clamping screw 41 can be displaced in the slot 42 of the screw-on plate 9 with the adjusting bracket 39 held on it in the vertical direction and fixed again in the desired position. With the displacement of the adjustment bracket 39 a corresponding displacement of the damping piston 36 held on the adjusting bracket 39 via the piston rod 38 is connected inside the damping cylinder 35. The adjusting eccentric 59, which is held there by the clips 61, is carried along with the valve rod 49 supported thereon of the adjusting bracket 39, the relative position of the valve rod 49 and the piston rod 38 remains unchanged, the wing flap can be adjusted independently of the damping setting.

Claims (16)

1. Closure device between a fixed frame (2) and a leaf (4) of a door or the like, which leaf can be pivoted relative thereto, having a closure mechanism which comprises at least one driving sliding member (23), at least one control sliding member (13) and at least one control lever (20), by means of which the driving sliding member (23) and the control sliding member (13) are drivingly connected to each other, the driving sliding member (23) being able to be displaced on the leaf (4) or on the frame (2), in the direction of the main plane of the leaf or frame and an end face (5) of the leaf or frame, which face extends transversely to the main plane of the leaf or frame, counter to the effect of a restoring force, from a starting position which is associated with the closed position of the leaf (4) into an open position which is associated with an open position of the leaf (4), and the control sliding member (13) being guided in a displaceable manner on the leaf (4) or on the frame (2) in the direction of the main plane of the leaf or frame and transversely to the end face (5) of the leaf or frame and being supported on the frame (2) or on the leaf (4) in the direction (14) of displacement, characterised in that the control lever (20) is articulated exclusively to the driving sliding member (23) and the control sliding member (13) and can be pivoted in each case only about an axis (21, 22) which extends transversely to the main plane of the leaf or frame.
2. Closure device according to claim 1, characterised in that the control sliding member (13) is guided in a displaceable manner between members (11, 12) of a guiding bar (8) which is recessed into the leaf (4) or into the frame (2) from the end face (5) of the leaf or frame.
3. Closure device according to either of the preceding claims, characterised in that there are provided, on the control sliding member (13), at least one guiding projection (15) which protrudes transversely to the displacement direction (14) and, on at least one member (11, 12) of the guiding bar (8), a guiding slot (16), which extends in the displacement direction (14) of the control sliding member (13), for receiving the associated guiding projection (15) of the control sliding member (13).
4. Closure device according to any one of the preceding claims, characterised in that the control sliding member (13) is supported on the frame (2) or on the leaf (4) by way of at least one connecting arm (17) which is pivotably supported, at one side, on the control sliding member (13) and, at the other side, on the frame (2) or on the leaf (4), about an axle (18, 19) which extends in the direction of the main plane of the leaf or frame.
5. Closure device according to any one of the preceding claims, characterised in that the at least one control lever (20) is in the form of a bracket.
6. Closure device according to any one of the preceding claims, the driving sliding member (23) being able to be supported, counter to the direction (24a) of the movement thereof, in the open position on the leaf (4) or on the frame (2), and being acted upon by a closure spring (32) which produces the restoring force acting thereon and which is supported on the leaf (4) or on the frame (2) and for which a control device is provided for adjusting the spring bias, characterised in that the control device for adjusting the spring bias comprises an adjusting spindle (27), which extends with the axis (28) thereof in the effective direction of the restoring force and which can be rotatingly driven about said axis (28), and an adjusting nut (31) which can be moved thereon by the adjusting spindle (27) being rotated in the axial direction of the adjusting spindle (27), the adjusting spindle (27) being supported on the driving sliding member (23) and the adjusting nut (31) being supported at the side of the closure spring (32) that is opposite the support on the leaf (4) or on the frame (2).
7. Closure device according to claim 6, characterised in that the adjusting spindle (27) can be rotatingly driven by means of a lockable tapered spur wheel gear which comprises a first tapered spur wheel (25), which is arranged coaxially with the adjusting spindle (27) and which is connected in a rotationally secure manner to the adjusting spindle (27), and a second tapered spur wheel (26) which is drivingly connected to the first tapered spur wheel and which, being rotatable about an axis (29) which is orientated transversely to the axis (28) of the first tapered spur wheel (25), is accessible relative to a drive device from the end face (5) of the leaf or frame.
8. Closure device according to any one of the preceding claims, having a damping device for the driving sliding member (23) which moves from an open position in the direction towards the starting position, and having a damping cylinder (35), which contains a damping medium, and a damping piston (36) which can be displaced relative to the damping cylinder (35) when the driving sliding member (23) is moved in the damping cylinder (35), the damping cylinder (35) or the damping piston (36) being connected to the driving sliding member (23) in terms of movement, and cylinder spaces (46, 47), which can be connected to each other via at least one overflow channel (52, 53, 54, 57) for damping medium, being provided in the damping cylinder (35), in the direction (24) of the relative movement of the damping cylinder (35) and the damping piston (36), at both sides of the damping piston (36), when the driving sliding member (23) is moved in the direction towards the starting position, characterised in that the effective cross-section of flow of the overflow channel (52, 53, 54, 57) can be adjusted.
9. Closure device according to claim 8, the damping cylinder (35) being connected to the driving sliding member (23) in terms of movement, characterised in that the damping piston (36) is held on the leaf (4) or on the frame (2) by means of at least one piston rod (38), on which at least a portion of the overflow channel (52, 53, 54, 57) for damping medium is provided and on which at least one valve rod (49), which can be stopped in various displacement positions, is guided in a displaceable manner relative to the piston rod (38), the overflow channel (52, 53, 54, 57) having a control face or control edge (56) which delimits the effective cross-section of flow thereof and relative to which the valve rod (49) can be adjusted with a control counter-face or control counter-edge (55) by being displaced relative to the piston rod (38).
10. Closure device according to claim 8, characterised in that the piston rod (38) is formed so as to be hollow with a free inner cross-section being formed, and the valve rod (49) can be displaced in an axial direction in the free inner cross-section of the piston rod (38) relative thereto.
11. Closure device according to claim 9 or 10, characterised in that the valve rod (49) is supported on the leaf (4) or on the frame (2) in a displaceable manner in an axial direction relative to the piston rod (38) by means of a positioning cam (59).
12. Closure device according to any one of claims 8 to 11, characterised in that at least one bypass channel for damping medium is provided, via which channel the cylinder spaces (46, 47) at both sides of the damping piston (36) are connected to each other when the damping piston (36) assumes, relative to the damping cylinder (35), a position associated with a position of the driving sliding member (23) that is close to the starting position.
13. Closure device according to claim 12, characterised in that the bypass channel is formed by a radial widening (44) at the inner wall of the damping cylinder (35) that faces the damping piston (36), the extent of which radial widening in an axial direction of the damping cylinder (35) exceeds the corresponding extent of the damping piston (36).
14. Closure device according to claim 13, characterised in that the cross-section of the radial widening (44) at the inner wall of the damping cylinder (35) increases relative to the damping cylinder (35) in the movement direction of the damping piston (36) that is associated with the movement of the driving sliding member (23) in the direction towards the starting position thereof.
15. Closure device according to any one of claims 8 to 14, characterised in that the damping piston (36) and the damping cylinder (35) can be adjusted relative to each other in an axial direction.
16. Closure device according to any one of claims 8 to 15, characterised in that the damping piston (36) can be adjusted relative to the damping cylinder (35) in an axial direction by means of at least one piston rod (38) and is supported in the assumed position so as to be able to be fixed on the leaf (4) or on the frame (2).