WO2009140705A2

WO2009140705A2 - Device for the independent adjustment of a leaf of a window or of a door with a spring-load device

Info

Publication number: WO2009140705A2
Application number: PCT/AT2009/000096
Authority: WO
Inventors: Helmut Katherl
Original assignee: Helmut Katherl
Priority date: 2008-05-19
Filing date: 2009-03-10
Publication date: 2009-11-26
Also published as: WO2009140705A3; EP2304149B1; EP2304149A2

Abstract

The invention relates to a component (201), in particular a window or door with a pivoted leaf, a top-hung window, pivoted window or sash window, comprising a frame (103, 203) and a leaf (102, 204) which may be pivoted about an essentially horizontal pivot axis (209) or moved in a sliding manner relative to the frame (103, 203), a closing device (1, 101, 217) for the delayed or retarded independent closing of the leaf (102, 204) and a locking system (169, 239) for locking the leaf (102, 204) in the closed position on the frame (103, 203). On closing the leaf (102, 204) the locking system has an independent self-locking design and comprises a locking element (170, 240) with a locking surface (174, 249) which may be fixed to the frame (103, 203) and a locking device (171, 241) which may be fixed to the leaf (102, 204) with a locking body (176, 248) cooperating with the locking surface (174, 249).

Description

Device for automatically adjusting a wing of a window or a door with a spring accumulator

The invention relates to a component, in particular window or door according to the preamble of claim 1 and a locking device for the time-delayed or slowed independent closing a wing of a window or a door.

In order to be able to advantageously ventilate a room via an open window or an open door, without having to accept excessive heat loss in the cold season, for example, the window or the door must be closed after a suitable ventilation period. So that this closing process can proceed independently, has already been proposed (DE 195 41 198 Al) to stretch when opening the window or door leaf spring, with its energy an actuator can be acted upon to close the wing, when the spring-loaded in the clamping position is unlocked after expiration of a wound up at the same time with the tensioning of the spring accumulator clockwork. A disadvantage of this known closure device for independently closing a window or door leaf, however, is the effort associated with the locking of the spring store and the time required for unlocking the clockwork.

For the independent closing of sliding doors, it is also known (DE 195 13 742 Al) to load the sliding door via a cable with a weight that is guided in a vertical tube. In order to achieve a braked closing movement, the weight in the bottom airtight tube sealed airtight, so that the weight is supported during gravity lowering on a Lustpolster that can be reduced only delayed by a throttle valve. An air inlet valve designed as a check valve ensures, when the door is opened, that it is not possible to build up any negative pressure in the pipe that makes lifting the weight difficult. However, the delayed with such a deceleration of the weight closing movement is not sufficient for a good room ventilation during the closing movement of the sliding door, especially up to the construction of a falling movement of the weight effectively delaying pressure pad, the sliding door already covers a considerable part of the closing path. A generic component is known for example from DE 44 45 366 Al, which discloses a window with a window frame and a window sash, in which the window sash by means of a window handle to manually lock and open but also automatically by a control unit to close and lock , The closing can also be triggered independently by tensioning a spring or a biasing mechanism or a prestressed spring drum by a timer. The control unit with a closing device is designed so that both in an open window as well as a tilted window, the independent closing takes place and by means of a coupled with the window handle locking mechanism, a locking of the closed sash relative to the frame. Between the control unit and the window handle a traction means is provided for this purpose and a tensile force occurring in the traction means, caused by the control unit is converted into a rotation of the window handle and thereby actuates the locking mechanism.

The comfortable closing of a tilted window after a certain period of time, which is comfortable for a user in such a system, is, however, in practice disturbed by the fact that a window opened about the vertical axis of rotation also automatically closes after a certain time interval in such an arrangement, however This closing process is often undesirable or not necessary, since a fully open window is open only in rare cases for a long time without supervision, as this naturally entails a high risk of burglary or, for example, a risk of falling for children. Furthermore, by this coupling of the control unit with the locking mechanism of the window handle, the usability of such a control unit on the embodiment of the locking mechanism is highly dependent and the installation of such a control unit can sometimes be very difficult or impair the function of the locking mechanism.

The object of the invention is to provide a component, in particular a window or a door, with a frame and a wing hinged to the frame with an automatic locking device which avoids the known from the prior art disadvantages and is characterized by a high level of user friendliness and a comfortable operation. The invention is further based on the object, a closing device of the type described for time-independent adjustment, especially for closing a wing of a window or a door so that without the use of a spring-loaded clockwork sufficient for example, a room ventilation open position by the time-delayed Closing the sash can be ensured with simple structural means.

The object of the invention is achieved by a component having the features of the characterizing part of claim 1, according to which a locking system between a fixed frame and adjustable wing when closing the wing automatically locking system acting on the frame or on the wing, a locking surface exhibiting locking element and a on the wing or the frame attached locking device with a cooperating with the locking surface locking member summarized.

By such a locking system, the advantageous automatic closing function is extended by a locking function which automatically takes effect when closing, which, like the closing function, also has no external energy source, like e.g. required for an electric drive, can be operated. Since the closing by the closing device of a window or a door normally occurring manual locking operation with time-delayed self-closing is not possible or should be saved, the locking system forms a high security gain, since the window or the door after the time-delay closing in the Closed position is locked and can not be easily opened by pressure from the outside. Such a device thus simultaneously offers a comfortable way to save energy, since a hold open the wing about in the winter can be limited in time and following the preselected ventilation time without user intervention and without supply of external energy independent closing and locking of the device.

An advantageous function of the locking system is achieved when the locking member is biased by a spring element in the reverse direction, ie in engagement with the Verrieglungsfläche and is adjustable by means of an actuating member in a non-engaged with the locking surface release position. As a result, the blocking effect of the locking system can only be canceled by active actuation of the actuator and the locking function is made by the spring element in a reliable manner.

If the actuating member is formed by a traction means, the operation can be moved with simple means and cost of the possibly difficult to reach locking device in an easily accessible handling area.

In particular, the traction means may be guided by guide means or deflection means on the closing device for closing the wing to a handling area. If in this case an operation by pulling the traction means, the locking member is brought out of engagement with the locking element in a first phase and and the locking effect or released locking action. Upon further pulling the traction means this can be simultaneously used in consequence to spend the wing of the door or the window from the closed position to the open position, whereby the spring accumulator is tensioned. Since the traction is initiated where it is needed by this leadership of the traction device, namely in the region of the closing device, the biasing of the spring accumulator can be done by opening the wing with relatively little effort.

In addition, the traction means can also be used for triggering or activating further additional functions, that is to say for switching functions, further adjusting movements on further movable components of the component and similar additional functions.

One possible additional function which can advantageously be activated with the actuator on a window used for ventilation is the activation of a fragrance dispenser which can neutralize or mask unpleasant odors in a room. When opening a wing for ventilation, the effect of the air exchange with the outside air sets in after a period of several minutes, so that especially in the phase at the beginning of the airing, the additional effect of a fragrance dispenser can be very pleasant. Thus, for example, the tensile force exerted on the tension element can be used to trigger a spray impulse in a compressed air-filled fragrance dispenser of a commercially available design, for example by the fragrance dispenser being fastened between the free end of the tension element gripped by the user and a fixed abutment point of the tension element Tensile means occurring tension actuated a spray button. The attachment of the fragrance dispenser can take place on the wing, but advantageously also on the traction means alone. So z. B. the tension element in the form of a Perlonschnur Überlenkpunlcte on the air freshener or a holder receiving this looped, wherein a deflection point is connected to the Duftspendergehäuse or the holder and another deflection point is connected to the release button, and when a tensile stress in the tension element

Unlocking and opening the wing, the two spaced apart deflection points are approximated.

A very stable and mechanically heavy-duty embodiment of the locking system is achieved when the arranged on the frame locking element has at least one Sperrauf- perception and arranged on the wing locking means comprises a locking member in the form of at least one, preferably in or out of the locking recess displaceable hook member or locking bolt. In a locking bolt, which is guided with a small clearance in the locking device and engages in a locking recess of the locking element, considerable shear forces for overcoming the locking are required even for small bolt cross sections, and can at a sufficient anchoring of the locking element in the frame or the locking device on Wing oppose a violent opening of such a device, a high resistance. Furthermore, a simple rectilinear unlocking is given in locking members in the form of locking bolts, which can be easily initiated by means of an actuator, such as by a pulling movement.

A further advantageous structural solution of the locking system is that it comprises at least one locking member in the form of an adjustable Exzenterklemmelements, in particular a Exzenterklemmrolle, and a support member for supporting the act of the Exzent- terbemmelement on the locking surface locking element. During the closing movement of the wing, the locking surface and the Exzenterklemmelement come into contact with the Exzenterklemmelement allows closing of the wing, but in the opposite direction self-locking between Exzenterklemmelement and Verrie- gelungsfläche is effective, whereby the locking element is clamped between Exzenterklemmelement and support member and a movement of the Wing is suppressed in the direction of the open position. In order to support the achievement of the required self-locking and the necessary frictional forces, at the locking surface, the effective surface be attached to the Exzenterklemmelement and on the support member friction materials, such as rubber elements.

Another possible embodiment of the locking device is that the locking element on the locking surface has a locking toothing and the locking member comprises a locking engagement with the form-fitting cooperating, likewise a locking tooth exhibiting locking element. This is a proven in other applications possibility to lock the movement of the wing unidirectional can. The wing is thereby fixed in the maximum approximation to the fixed frame. A possible movement in the direction of the open position is due only to the tooth width of the locking toothing, but with tooth widths of about 0.5 mm to about 2 mm, in particular about 1.0 mm cause sufficient locking strength and such a small movement in the direction the open position can normally be disregarded.

Since the engagement movement between the latching toothing on the latching element and the latching toothing on the latching element for certain application cases in quiet zones such as bedrooms or hospital rooms could cause disturbing noises, it may be advantageous if a sliding element can be used on the latching toothing of the locking element, which is the locking surface considered in the form of locking teeth in the closing direction in a sliding portion without engagement of the locking teeth of the locking element and an adjoining latching portion with engagement of the locking teeth of the locking element divided. By the sliding element, the two locking teeth are slightly lifted from each other, whereby the ratchet-like Einrastgeräusch can be largely prevented by the sliding portion is carried out as long as possible.

Since the locking element advantageously has a length with which windows or doors with thicker frame thicknesses by means of the locking device should be lockable, the length is chosen to be relatively large. For wings with a small frame thickness, this would cause a very long Einrastweg, which is why it is advantageous if the sliding element, viewed in the direction of movement of the locking element, can be fixed in at least two different positions on the locking teeth. Thereby, the locking position of the locking element on the locking element can be optimally adjusted and by the positioning the sliding element the ratchet-like Einrastgeräusch be largely avoided even with different frame thicknesses.

The locking system can be functionally and / or structurally independent and not operatively connected to it, in particular by a manually or motor-operated locking fitting of the wing, as a result of which, as already described above, a deactivation of a conventional locking fitting by the tilting position of the window handle becomes automatically effective Locking system is compensated after the independent closing of the wing. The structural independence of the locking fitting also has the effect that such a locking system without having to pay particular attention to structural conditions of the locking fitting, can also be retrofitted and thus retrofitting a safety-relevant locking system is easily possible.

Alternatively, the locking system automatically becoming effective when closing can also be realized by a special locking fitting with an operating handle, which is locked next to a basic position or locking position in which the wing is locked in the closed position on the frame and an open position in which the wing opposite the Frame by turning, swiveling, folding, pushing or tilting is adjustable, can also take a position in which an adjustable locking member on the wing

Closing the same automatically interacts with a locking element on the frame, e.g. snaps and locks the wing in the closed position and can also take a position in which the automatic locking can be actively unlocked again. Thus, with such a locking fitting, a user can deliberately activate an interlock which automatically takes effect when the wing is closed and which can only be actively unlocked by the user.

These additional functions compared to a conventional window or door fitting offer a user the advantage that can be actively opened by a single actuation on the component of the wing and without further intervention by the user and without the supply of external energy after a presettable time of the wings the locking device can be returned to the closed initial state and can be largely secured in this by the locking system against unauthorized opening. For components in which there is sufficient space between the fold of the frame and the fold of the wing, it is advantageous if the locking system with the wing closed between the fold of the wing and the fold of the frame is arranged and the locking system in a front view of the device not is visible. Since such an embodiment of the locking system, the overall visual impression is not changed, such a system can also be advantageously used for retrofitting to existing components. For this purpose, the locking system advantageously has dimensions which are as small as possible, and permit, for example, installation on components with a so-called Eurofalz with a rebate height of approximately 12 mm.

The actuating member for unlocking the locking member may advantageously be designed in particular as a tension element, such as a pull cord, whereby the actuator with simple means, such as pulleys or guide sleeves in a simple way from the locking system to an ergonomically favorable for the user operating area or relocated can. Particularly in the case of a locking system concealed in the rebate area, it is advantageous if the traction element is guided by the locking system through a passage in the wing to the wing front side. In this case, the tension element can be approached approximately horizontally from the locking system on the upper frame part of the window sash, within the frame part to the subsequent vertical frame part, and be led out in this area through a grommet to the wing front side, whereby only a small amount is achieved in the case of a passage with rounded edges Friction resistance for the actuator or tension element is caused.

If the implementation for the tension element of the locking system has a vertical distance from the horizontal pivot axis of at least two-thirds of the height of the sash, with a force exerted on the tension element pulling the lock system can be unlocked and subsequently also the wing in tilted position, with by a high force application point of the traction means favorable leverage ratios are given, which facilitate a biasing of the spring accumulator of the locking device. This high force application point of the tension element is also advantageous in the case of a non-integrated locking system, since the opening process is thereby also facilitated here. A practical design of the component with the least possible actuation forces is provided if the horizontal pivot axis in the region of the lower horizontal frame part of the wing and the passage of the tension element or the force application point of the drawn by the user pulling element arranged on the upper horizontal frame part of the wing is.

An advantageous embodiment of a component with a locking system can be achieved in that the adjustment for the locking member or the actuator in the direction of the release position or unlocking position by a stop element or a defined fixed point on the locking system or on the wing is limited and by the actuator in the form the pulling element is formed a handle for tilting the wing about the horizontal pivot axis against the tensile force of the spring accumulator of the closing device. This ensures that the pulling force required for tilting the wing is reliably introduced into the window wing without damaging the locking system, after unlocking of the locking system takes place in a first phase with a relatively low tensile force and tilting only in a second phase of the grand piano.

The object of the invention is further achieved by a locking device according to patent claim 16, according to which the actuating drive has an actuating cylinder with a first end position corresponding to the initial position and a second end position corresponding to the pretensioning position, and connected to the wing comprising actuating piston operatively connected to the spring accumulator which, together with the cylinder inner surface, delimits at least one variable working space receiving a fluid, and a first flow path for the fluid opens into the working space, in which a check valve is arranged, the adjustment being effected by the vane actuation of the actuating piston from the first end position to the second end position in the open position, and a second flow path for the fluid opens, in which a delay element in the form of a time-controlled shut-off valve or a throttle valve is arranged, da s in the caused by the relaxation of the spring accumulator adjustment of

Adjusting piston from the second end position in the first end position is flow-inhibiting effect and that at least one opening into the working space Ausgleichsfließweg is effective in the adjustment of the actuating piston from the second end position to the first end position. By this embodiment of the actuator is achieved that for actuating the wing from the initial position in the biasing position substantially only required for biasing the spring force is required because the adjustment of the actuating piston from the first end position to the second end position without back pressure from the working space takes place, since the check valve is in the open position and therefore the fluid displaced by the first flow path with little resistance from the working space or low resistance can flow into the working space. Following this actuation of the blade for biasing the spring accumulator, the phase of the independent Versteilens of the wing begins by relaxation of the spring accumulator, wherein the volume change of the working space and thus the. By the delay element in the form of timed shut-off valve or in the form of flow-restrictive effective throttle valve Adjustment speed of the actuating piston is prevented for a defined period of time or is very low. This can be erzieit the desired time delay of the adjustment of the wing.

Subsequent to this first, braked by the delay element adjustment follows a second relatively fast expiring adjustment phase, as between the second end position and the first end position of the actuating piston of the low-resistance fluid-permeable Ausgleichsfließweg is effective and the flow of fluid is no longer subject to the influence of the delay element. Due to the greatly increased volume flow from or into the working space a fast pressure equalization takes place in the working space with the environment or the back of the actuating piston, whereby the actuating piston is essentially only subjected to force by the spring accumulator and by the lack of braking action of the working space, the adjustment of the Wing can take place much more quickly from the effectiveness of the Ausgleichsfließweges.

In addition to the first time-delayed or in the VersteÜgeschwindigkeit greatly reduced set first adjustment phase in which can be done by temporarily remaining in the open position wing of the window or the door air exchange between the room interior and the outside, is by the second adjustment phase with fast adjustment a reliable Adjusting, in particular closing the wing caused by the spring accumulator. The movement connection between the wing and actuator piston can be done in any way, for example. By mechanical fasteners such as rods or relatively flexible traction means, but it is also a fluidic motion transmission by means of a hydraulic line and an actuator on the wing conceivable.

A structurally simple and cost-effective design of the spring accumulator is to form this by a mechanical spring, in particular a tension spring. In the case of a mechanical spring, the spring accumulator can also be referred to as a storage spring, which may have a linear spring characteristic, but deviating or progressive spring characteristic curves are also conceivable. As mechanical springs come further springs with rectilinear operation but also by angular displacement adjustable springs so torsion springs in question. An advantage of mechanical springs in the form of cylindrical springs is that the actuating cylinders can also be arranged in its interior, whereby shorter overall lengths can be realized, as in a series connection of spring and actuator piston with piston rod or traction means for piston movement.

Another way to form the spring accumulator is to form this by a gas spring with variable gas volume. The closing force is effected by a compressed gas in the gas spring, wherein the compression when adjusting the wing from the initial position takes place in the biasing position, in particular using a force acting between the frame and wing traction means, the movement in an adjustment of a piston in the Gas spring is converted. The actuator with the gas spring includes in addition to the pure gas spring function of the compressible gas volume also has a delay function for the relaxation movement, which is effected by the delay element. The delay element may, as mentioned above, comprise a timer element and / or a throttle element with which the speed of the expansion movement can be greatly reduced.

In particular, it is possible to use gas spring / damper combinations which are sufficiently known from the prior art and, in addition to a gas spring arrangement, also comprise a structurally combined or structurally separate linear or rotational damping arrangement. The gas volume can be enclosed, for example, in the actuating cylinder by a separating piston and the mechanical spring force is transmitted mechanically or fluidically to the actuating piston. The advantage of a spring accumulator in the form of a gas spring is that a high energy density for the actuation of heavy wings can be achieved by choosing a high Fülldracks even with small physical dimensions of the gas spring. The achievable by a gas spring high actuation forces, it is also possible to convert a relatively short piston rod movement by means of a deflection in a relatively long wing movement, such as by using a traction device for transmitting motion to the wing, the traction means is attached to a fixed point and by means of a The piston rod of the gas spring connected pulley the free end of the traction device when looping the pulley by 180 ° twice the distance travels, according to the reversal of the principle of operation of a pulley. The possible small design of the closing device with a gas spring, in particular in connection with the use of a traction device for transmitting power to the wing, offers a variety of possible applications, such as the automatic closing of windows or doors of all kinds, such as tilt and turn windows, swing windows, sliding windows etc.

Structurally simple solutions for the actuator can be achieved by using a gas, in particular air, as the fluid. The use of air makes it possible to dispense with closed fluid circuits, since an exchange between the working space and the ambient air is structurally easier to solve than the formation of closed circuits. Another advantage of using a fluid in the form of gas is that there is no risk of contamination of the environment of the closure device in the event of leakage.

Another possible embodiment of the closure device is that a fluid, in particular a hydraulic oil with a viscosity index with a value of at least 100, preferably at least 120 according to ISO 2909 and a service temperature with a lower limit of less than 10 ° C is used as the fluid. The use of largely incompressible liquids, in particular hydraulic oils, enables the transmission of high forces with small paths and therefore small physical dimensions. Furthermore, standardized and readily available components can be used for the required components such as return valve and throttle. The high viscosity index with low Changes in viscosity with changes in the temperature of the hydraulic oil causes the adjustment speeds and the actuating forces to remain largely uninfluenced by the operating temperature during the temperature changes occurring in the adjustment drive.

Due to small structural dimensions, it is possible in particular, the actuator of the

Integrate locking device inside a wing or a fixed window or door frame, whereby the locking device does not affect the overall appearance of a window or a door.

For the practical function of the actuator, it is advantageous if the working space in the second end position of the end piston has a smaller, preferably very small volume than in the first end position of the actuating piston and the working space thereby acts as a vacuum chamber. By definition, the second end position of the actuating piston forms the starting point for the automatic relaxation of the spring accumulator, wherein at a small volume of the working space in the second end position after a short adjustment sufficient vacuum in the working space is established and effective, which counteracts the force of the spring accumulator and Therefore, the adjustment of the actuating piston caused by this is slowed down to the desired level immediately after leaving the second end position.

If, on the other hand, the working chamber in the second end position of the actuating piston has a larger volume than in the first end position of the actuating piston, the working chamber acts as a pressure chamber, which can also slow down the adjusting speed of the actuating piston caused by the spring accumulator, but already to build up the required overpressure in the working space a considerable proportion of the independent adjustment of the actuating piston is required. However, this disadvantage of the formation of the working space as a pressure chamber is effective only when using a fluid in the form of a gas, as when using an incompressible liquid also shortly after leaving the second end position of the actuating piston an opposite to the force of the spring accumulator effective pressure on the actuator piston can be effective.

In order to influence the fluid volume flow from or into the working space and thereby also the speed of the effect caused by the spring-loaded automatic adjustment of the It is advantageous if the time-controlled shut-off valve or the throttle valve has an adjustable flow cross-section. The adjustment of the flow cross-section can be done for example by using different constant restrictors with different flow cross-sections; for a sensitive adjustment of Ent-tensioning speed, however, it is advantageous if the throttle valve comprises continuously adjustable throttle elements.

In order to be able to influence the adjustment speed of the control piston and of the blade even in the movement phase after the compensation fluid path has taken effect, it is advantageous if it has an adjustable flow cross section. This can also be done by throttle valves - but here with a larger flow cross section.

Since the check valve and / or the delay element should be as easy as possible to exchange or to adjust the flow cross-section or the delay time, it is advantageous in many cases if they are arranged accessible from the outside on the actuating cylinder; In some cases, however, it may be structurally advantageous if the first flow path with the check valve and / or the second flow path with the delay element extends through the control piston. As a result, the fluid outlet or fluid flow through the adjusting piston takes place in the adjusting cylinder space located behind the adjusting piston. The actuating piston can thus also define two effective working spaces between two opposite end faces of the actuating cylinder, it being advantageous to pass the first flow path or the second flow path through the actuating piston.

In order to have more possibilities for mounting the closing device on a frame or a wing, it is advantageous if the movement connection between actuating piston and wing comprises a traction means fastened to the adjusting piston, with which the actuating piston counteracts the action of the spring accumulator on the first End position is adjustable in the second end position. In particular in the case of a slightly rigid traction means, a deflection of the force directions is possible and therefore deviations in direction between the adjustment direction of the adjusting piston in the adjusting cylinder and the adjustment direction of the vane with respect to the fixed frame are easily possible. Thus, the actuating cylinder can be mounted approximately parallel to the wing surface, while the traction means extends approximately at right angles to the wing surface from the wing to the fixed frame. For variants of the closing device in which the working space acts as a vacuum chamber, it is advantageous if the traction means passes axially through the working space and is led out of the adjusting cylinder in a sealed manner by a sealing arrangement. By caused by the manual wing operation from the initial position in the biasing position, pulling movement on the actuator piston while the working space is reduced in volume and the fluid pushed out of this. A remaining at the end of this displacement when reaching the second end position by the actuating piston, the smallest possible residual volume of the working space forms a good condition for a rapid construction of the required subdrack.

Furthermore, a deflecting element, for example in the form of a deflection roller, can be arranged on the end side of the closing device with which the traction means can be deflected in any direction, in particular approximately at right angles, in the direction of the fixed frame or the wing, starting from the axial direction of the setting cylinder the outgoing from the spring memory of the closing device closing force can be transmitted with low losses.

In particular, the deflecting element, for instance the bearing block carrying the deflection roller, can be rotatable with respect to the axial direction of the adjusting cylinder, whereby the closing device can be adapted to different mounting situations with little effort.

A further structural simplification can take place in that the check valve is formed by the traction means with circular cross-section and smooth surface and a cooperating with this, on the actuating cylinder frontally mounted sealing arrangement. A separate flow path with its own non-return valve can be saved by this design.

The sealing arrangement may advantageously comprise at least one O-ring, one X-ring or the like, which constitutes an easily available and proven sealing means.

A reliable function of a seal assembly as part of a check valve is provided when the seal assembly is mounted axially displaceable or axially deformable in a seal seat on the actuating cylinder and in the adjustment of the actuating piston from the first end position to the second end position the traction means itself and by the actuation tion of the traction means caused pressure differences on the opposite sides of the seals, the seal assembly in an axial position or cause axial deformation, are effective in the recesses in the seal seat, which form the low-resistance first flow path. The seal assembly thereby has an equivalent function, such as a ball seat member in a conventional check valve.

Another possibility to influence the adjustment speed of the actuating piston and thus also of the wing is that the spring-loaded is adjustable in its bias, for example by in the axial direction staggered suspension points for a Zugfe-.

A structurally simple solution, which is particularly suitable when using gases as fluid, is that the Ausgleichsfließweg at least one arranged on the cylinder jacket of the actuating cylinder, in particular by a cover in its throttle cross-section changeable, pressure compensation opening comprises. The exchange of air between the working space and the ambient air through the structurally simple pressure equalization opening represents the simplest form of a Ausgleichsfließweges.

Another possibility to influence the movement of the actuating piston in the actuating cylinder is that the working space of the actuating cylinder is fluid-connected to a pilot control device by means of which the check valve from the blocking position is adjustable in the open position. This unlocking of the check valve works around the first flow path leading to the check valve to Ausgleichsfließweg, through which the rapid pressure equalization can take place in the working space. The unlocking of the non-return valve can be done in particular by a control piston, which is guided in a pilot cylinder.

An advantageous development of the invention is that the actuating cylinder along its longitudinal axis has a variable, in particular conically extending cylinder cross-section, wherein the cylinder cross section, starting from the region of the second Endstel- ment of the actuating piston in the direction of the first end position of the actuating piston increases. Such a conical design of the actuating cylinder causes the working space is better sealed in the region of the second end position of the actuating piston and thus leakage through fluid escaping between the actuating piston and cylinder inner wall are avoided. Furthermore, The conical execution of the actuating cylinder can be helpful for the demolding during production in an injection molding process, since an axially tapered inner core is easier entfoπnbar.

To achieve an anti-rotation for the actuating piston in the actuating cylinder to the cylinder longitudinal axis, it is also possible not circular but non-circular, in particular oval perform the cylinder cross-section, as this means especially when using Spritzgieß- components no extra effort for the production and still used as a piston seal simple sealing rings can be.

The invention further solves this problem by providing that the actuating drive comprises an actuating cylinder with a piston loaded by a storage spring, between which and a cylinder bottom of the cylinder forms a negative pressure space acting on the piston in opposite directions to the accumulator spring, in at least one of the two through the cylinder bottom and the piston resulting end faces of the vacuum chamber on the one hand an air outlet valve in the form of a check valve and on the other hand, a throttle performing air inlet valve and that the piston controls a vent valve for the vacuum chamber of the cylinder in response to a predetermined relaxation path of the storage spring.

By the measure to oppose the force of the accumulator spring a negative pressure of the piston can be ensured in a simple manner that already in the clamping position of the spring accumulator corresponding open position of the wing whose closing movement is effectively braked, although the actuator with the largest available spring force is acted upon, because when striking the piston to the Zy- linderboden in the clamping position of the spring accumulator, the piston can be moved away from the cylinder bottom due to its spring load only to form a substantial, co-determined by the throttling action of the air inlet valve vacuum. This, however, fulfills the prerequisites for a closing movement of the wing delayed by the spring-loaded actuating drive, even over a relatively long period of time, so that, given a sufficient opening width of the wing over a reasonable period of time, good ventilation of the room can be ensured. However, with the high negative pressure of the piston from its stop-limited starting position effective delay the closing movement brings with it the risk that at the end of the closing movement of the then already largely relaxed spring accumulator can not melir provide the required for locking the wing in the closed position closing force available, especially in the sense of a strong delay of the closing movement, the force of the accumulator spring should remain limited. In order to meet these partly conflicting requirements, according to the invention for the resulting between the cylinder bottom and the piston vacuum chamber of the cylinder B a ventilation valve provided which is actuated in response to the stroke of the piston. As the negative pressure is vented rapidly with the ventilation of the vacuum chamber, the spring force of the spring accumulator fully comes into effect, which leads to a corresponding acceleration of the closing movement of the wing with the effect that the mass inertia forces of the accelerated wing lead to its secure locking, and even when using comparatively soft memory springs, which are well suited for longer suspension travel. With the aid of a closing device according to the invention, however, a wing can not only be closed, but also opened with a time delay, in order, for example, to ventilate a heat cabin after a predetermined period of time via a wing which is to be opened.

The accumulator spring can be designed as a pressure or as a tension spring, since it is only important to pressurize the piston by the spring in the sense of increasing the negative pressure space. Particularly simple construction conditions arise, however, when the accumulator spring is designed as a tension spring and attacks on the vacuum side facing away from the ventilated side of the cylinder on the piston, because in this case the memory spring can be accommodated protected in the cylinder with a small overall length. In order to adjust the closing force provided by the spring accumulator available to the respective closing resistors, the accumulator spring can be made adjustable in their bias.

The vacuum space between the cylinder bottom and the piston is to be ventilated via the air outlet valve while the accumulator spring is being tensioned. This to be formed as a check valve air outlet valve can therefore be provided either in the piston or in the cylinder bottom. Simpler design conditions, however, result in an arrangement in the cylinder bottom, because then this air outlet valve remains easily accessible. The same applies to the air inlet valve, which ensures when relaxing the accumulator spring for a metered due to the throttling effect of air access to the vacuum space imd thereby brakes the adjusting movement of the piston according to its spring loading accordingly. With a adjustable throttle cross-section of this air intake valve can therefore be influenced on the time delay of the closing movement of the wing.

The ventilation valve for the vacuum chamber, which is provided for releasing the piston after a braked adjusting movement, can preferably be designed as a passage opening in the cylinder jacket, which, however, is not mandatory. This arrangement of at least one passage opening in the cylinder jacket has the advantage that no additional measures are required for the control of this ventilation valve, because the passing past this passage opening piston initiates the ventilation of the vacuum chamber after a constructively determined by the axial position of the passage opening travel. To adapt this travel to different closing conditions, at least two selectively coverable passage openings can be provided at a mutual distance in the direction of the cylinder axis.

By the measures a) optional covering offset in the direction of the cylinder axis passages b) adjustable throttle cross section c) Ausgleichsfließweg with adjustable throttle cross-section of the pressure compensation opening d) adjustable bias of the spring accumulator consist of adapting the individual measures or the appropriate choice of combinations of diverse possibilities for setting the Closing characteristic and adaptation to a wide variety of applications.

In particular, a switching function between summer and winter operation of the closing device can be provided with different periods of ventilation periods, such as two flow paths are provided with throttle valves, which can be used for the slow, first part of the closing movement alternatively or combined, whereby two or possibly three or several different closing delays can be preselected.

The invention will be explained in more detail below with reference to the exemplary embodiments illustrated in the drawings.

Each shows in a simplified schematic representation: 1 shows a closing system for a window sash with a closing device for closing a window sash;

Fig. 2 shows a further embodiment of the closing device with a working space which acts as a pressure chamber;

3 shows a further embodiment of the closing device with a pilot control;

4 shows a further embodiment of the closing device with closed fluid circuits, in particular for the use of hydraulic fluid as fluid;

Fig. 5 shows an embodiment of the closure device with a spring accumulator in the form of a gas spring element and use of hydraulic fluid as the fluid

Achieving the delay effect;

Fig. 6 shows a further embodiment of the locking device with a spring accumulator in

Shape of a gas spring and use of hydraulic oil as a fluid to achieve the retarding effect;

FIG. 7 shows a partial view of a cylinder jacket of a gaseous fluid actuating cylinder; FIG.

FIG. 8 is a fragmentary view of another embodiment of a gaseous fluid actuator cylinder; FIG.

9 shows a partial section through a further embodiment of a closing device with a special form of the check valve.

10 shows a component with a closing device for closing a wing and a locking system for the wing;

11 shows an example of a locking system according to FIG. 10 in a sectional view; FIG. 12 a further embodiment of a locking system according to FIG. 10 in an exploded view; FIG.

13 shows a further embodiment of the closing device in a sectional view;

Fig. 14 is a closing device in exploded view.

15 shows a view of a further embodiment of a component in the form of a window with tilt and turn wings with a locking device for the tilted wing and a concealed locking system;

FIG. 16 shows a plan view of the component according to FIG. 5 in the direction of the arrow XVI in FIG. 15 with closed wing; FIG.

Fig. 17 is a plan view of a concealed locking system for the device;

Fig. 18 shows a possible arrangement for actuating the locking system;

By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same Bauteilbezeiclinungen, the revelations contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or identical component names. Also, the location information chosen in the description, such as above, below, laterally, etc. related to the directly described and illustrated figure and are mutatis mutandis to transfer to a new position to the new situation. Furthermore, individual features or combinations of features from the different exemplary embodiments shown and described can also represent independent, inventive or inventive solutions.

All statements on ranges of values in objective description are to be understood as including any and all sub-ranges thereof, eg the indication 1 to 10 should be understood as meaning that all sub-ranges, starting from the lower limit 1 and the 1 upper limit 10 are included, ie all sub-areas begin with a lower limit of 1 or greater and end at an upper limit of 10 or less, eg 1 to 1.7, or 3.2 to 8.1 or 5.5 to 10 ,

FIG. 1 shows a component with a closing device 101 for the time-delayed self-adjusting of a vane 102 of the component, in the form of a window or a door, relative to a fixed frame 103. The vane 102 is between an initial position shown in phantom 104, which corresponds to the closed position and a likewise shown in phantom bias position 105 adjustably mounted on the frame 103, wherein the bias position 105 corresponds to the open position of the wing 102.

The function of the closing device 101 is that after a manual wing operation 106 represented by a line arrow 106 from the initial position 104 into the pretensioning position 105, the vane 102 is moved back into the initial position 104 by the closing device 101 in a time-delayed independent adjustment 107 ,

The closing device 101 comprises a Stellzy cylinder 108 in which an actuating piston 109 is adjustably mounted, which is connected to the wing 102, approximately as shown in Fig. 1, by a traction means in the form of a string 110 with the wing 102 and further connected with a Spring accumulator 111 is operatively connected. The actuating piston 109 is adjustably mounted in the actuating cylinder 108 between a first adjustment 112 indicated by dashed lines and a second end position 113 also shown in dashed lines and operatively connected to the spring accumulator 111, here in the form of a mechanical spring 114, in particular a tension spring 115. Control piston 109 and spring accumulator 111 are arranged so that an adjustment of the actuating piston 109 from the first end position 112 in the second end position 113, the voltage in the spring memory 111 increases, so this is biased by the movement and in turn by an adjustment of the actuating piston 109 is relaxed from the second end position 113 in the first end position 112 of the spring 111, so its voltage is reduced.

Due to the movement connection between the wing 102 and the actuating piston 109 via the cord 110, a direct relationship between the first end position 112 of the actuating piston Bens 109 and the starting position 104 of the wing 102 given; Similarly, the second end position 113 of the actuating piston 109 corresponds to the biasing position 105 of the wing 102nd

In order to let the independent adjustment 107 of the vane 102 time-delayed or slowed down, it must be prevented that the spring force exerted by the spring accumulator 111 on the adjusting piston 109 is converted directly into a movement of the system adjusting piston 109 - vane 102, ie the adjustment of the adjusting piston 109 from the second end position 113 in the first end position 112 is substantially unrestrained and at full speed.

For this purpose, the actuating piston 109, together with the cylinder inner wall 116, delimits an at least approximately hermetically sealed working space 117 which extends between the cylinder end face 118 and the actuating piston surface 119. In order to counteract the spring force exerted by the spring accumulator 111 on the actuating piston 109, a negative pressure or an overpressure in the working space 117 is produced by measures described in consequence, which counteracts the spring force exerted by the spring accumulator 111.

Since in Fig. 1, the spring accumulator 111 is formed approximately as a tension spring 115, the spring force acts in the drawing to the right; the pressure force exerted on the actuating piston surface 119 by the working space 117 must therefore act to the left in order to counteract the spring force acting to the right. For clarification, the spring force acting on the actuating piston 109 from the spring accumulator 111 is indicated by an arrow in solid line as spring force 120, while the force exerted by the working chamber 117 on the actuating piston 109 pressure force is indicated by a dashed arrow as a left-acting pressure 121. The pressure force 121 exerted on the actuating piston 109 by the working chamber 117 results as a resultant pressure force from the pressures acting on the opposing piston surfaces - in the illustrated embodiment this is a pressure force 121 to the left since the ambient air pressure is higher than the vacuum prevailing in the working space 117.

In the embodiment of FIG. 1 is located in the working space 117, a fluid 118 which is formed in the simplest case by air. Actuating cylinder 108 and actuator piston 109 are thus components of an actuator 123 for the independent adjustment 107 of the wing 102, the mode of action is described as a result.

In the case of the manual wing actuation 106 of the wing 102, the actuating piston 109 is pulled out of the first setting 112 into the second end position 113 via the traction means or the cord 110. The relatively large output volume of the working space 117 is thereby reduced to a relatively small residual volume, and the fluid in the form of air contained in the working space 117 leaves the working space 117 via a first flow path 124 and is discharged to the outside environment. The first flow path 124 is designed so that the fluid can pass without any significant flow resistance. Therefore, no appreciable force is required for the displacement of the fluid from the working space 117, and the force required for the leaf actuation 106 is essentially caused by the tensioning of the spring accumulator 111.

At the end of the wing actuator 106 is the wing 102 in the biasing position 105 and the actuator piston 109 in the dashed line in Fig. 1 indicated, left second end position 113. Starting from this position would by the tensioned spring 111 of the actuating piston 109 again directly into the right first End position 112 are spent and thereby also the wing 102 are moved to the closed starting position 104. In order to achieve the desired delay of this process, located in the first flow path 124, a check valve 125, which prevents an influx of air into the working space 117, ie during the movement of the actuating piston 109 from the second end position 113 in the first end position 112 in Locking position is, while it is in the movement of the Stellkol- bens 109 to the left from the first end position 112 in the second end position 113 in the open position and therefore the fluid can be displaced without appreciable resistance via the flow path 124 from the working space 117.

Since during the expansion movement of the actuating piston 109 to the right through the first flow path 124 due to the closed check valve 125 no air can flow, builds up immediately at the beginning of this relaxation movement in the working space 117, a negative pressure, which together with the effective on the right side of the piston ambient pressure causes a resultant compressive force 121 to the left, which increases with increasing piston away increases until it is in force equilibrium with the force acting to the right from the spring 111 and decreasing with increasing piston travel spring force 120. If only a small residual volume of fluid is contained in the working space 117 in the left second end position 113, the required negative pressure already arises after a very small piston travel and the independent adjustment 107 of the vane 102 comes to a standstill after a negligible short path.

However, since the vane 102 is to be displaced by the actuating drive 123 into the starting position 104 after an intended delay time, this further comprises a second flow path 126, via which the fluid in the form of air can be supplied to the working space 117. In order to obtain the necessary control over the fluid supply, a delay element 127 is arranged in the second flow path 126, with which the supply of fluid over a defined period of time is completely suppressed or lowered to a defined low level. Delay element 127 includes either a timed shut-off valve 128 or a throttle valve 129. Timed shut-off valve 128 releases second flow path 126 after a predefined period of time and is connected to an arbitrary timer member.

The throttle valve 129 has in relation to the first flow path 124 a significantly higher flow resistance for the fluid, whereby it can flow much slower into the working space 117 during the relaxation movement of the actuating piston 109 from the second end position 113 into the first end position 112 and through this high Flow resistance significantly slows down this movement.

The time-controlled shut-off valve 128 is set so that it releases the second flow path 126 after the delay time, but itself also has a throttling effect, since an unrestrained relaxation movement of the actuating piston 109 by the spring 111 cause a violent slamming of the wing 102 against the fixed frame 103 would, which is generally undesirable.

In order to further influence the independent adjustment 107 of the wing 102, it is provided that, after the first part of the adjustment path influenced by the delay element 127, a compensation flow path 130 which opens into the working space 117 and becomes effective in the Adjustment of the actuating piston 109 from the second end position 113 in the first end position 112 is effective. By this Ausgleichsfließweg 130 existing in the working space 117 working pressure is compensated in a short time with the environment and the actuator piston 109 spent from the spring memory 111 at an increased speed in the first end position 112. The last phase of the independent adjustment 107 of the wing 102 can thus take place at an increased speed.

The Ausgleichsfließweg 130 is formed in the exemplary embodiment of FIG. 1 by a simple pressure equalization port 131 in the cylinder jacket of the Stellzy Linders 108, wherein the position along the cylinder axis the time of switching from the through

Delay element 127 certain lower closing speed to the caused solely by the spring memory 111 higher closing speed.

By combining the Ausgleichsfließweg 130 with the delay element 127 in the form of the throttle valve 129 can thus be achieved by positioning the Ausgleichsfließ away 130 the same effect as a delay element 127 in the form of a timed shut-off valve 128, so also a delayed independent adjustment 107 of the wing 102nd ,

In the embodiment of the closure device 101 according to FIG. 1, the check valve 125 corresponds to an air outlet valve, the throttle valve 129 corresponds to an air inlet valve, and the pressure equalization opening 131 corresponds to a ventilation valve.

2 shows a further embodiment of a closing device 101 with an actuating drive 123, comprising an actuating cylinder 108 with an adjusting piston 109 adjustable between a first end position 112 and a second end position 113. The adjustment of the actuating piston 109 from the first end position 112 into the second end position 113 takes place in this embodiment also by a traction means in the form of a string 110, against the biasing force of the spring accumulator 111. This is formed in the embodiment of FIG. 2 by a compression spring 132, the spring force 120 acts in this case to the right and the working space 117 arranged to the right of the actuating piston 109. Thus, for the delayed adjustment of the actuating piston 109 from the second end position 113 in the first end position 112 on the actuating piston 109, a resultant pressure force 121 can act, which counteracts the spring force 120 acts, the pressure force 121 must act to the left, ie the working space 117 is effective in this embodiment as a pressure chamber.

Starting from the first setting 112 with a very small volume of the working space 117, the adjusting piston 109 is pulled to the left against the spring force 120 of the spring accumulator 111 by means of the cord 110, as a result of which the volume of the working space 117 increases. The supply of fluid takes place in this exemplary embodiment by a first flow path 124, which passes through the actuating piston 109 and can flow through the fluid in the form of air from the environment to the left of the actuating piston 109 into the working space 117. This inflow is possible because the non-return valve 125 arranged in the flow path 124 is oriented such that it is in the open position when adjusting the actuating piston 109 from the first end position 112 to the second end position 113, ie when the actuating piston 109 moves to the left allows air to flow in the working space 117 to the right, but blocks outflow of air from the working space 117.

In the left second end position 113 of the actuating piston 109 of the working space 117 has its largest working volume and is filled with air, which is located approximately at the pressure level of the ambient air. In this left second setting 113 thus acts on the actuating piston 109 no resultant pressure force 121, since the actuating piston 109 is acted upon by both sides with air at ambient pressure. There is therefore by the spring memory 111 in the form of the compressed compression spring 132 a relaxation movement of the actuating piston 109 to the right in the direction of the first end position 112. The check valve 125 is closed during this movement, which is why the air contained in the working space 117 is compressed during this movement until has formed a compression force 121 by the compression, which stands with the spring force 120 in the balance of power.

In this embodiment, with a pressure chamber acting as a working space 117 is thus at the beginning of the independent adjustment 107 a phase of rapid movement, which is slowed down by the pressure build-up in the working space 117. The further displacement movement is determined by the outflow of air through the second flow path 126, in which the delay element 127 is arranged in the form of a throttle valve 129. The second flow path 126 leads in this embodiment, as well as the first flow path 124 through the actuating piston 109 through to the piston rear side, which passes through a on the second cylinder end face 133 provided vent 134 is subjected to ambient air pressure. The adjustment of the actuating piston 109 takes place in this phase due to the controlled, delayed fluid drainage from the working space 117 through the throttle valve 129. The end of the adjustment is again carried out at increased speed as in the first embodiment by a Ausgleichsfließweg 130, here in Form of a bypass line 135, opens, which brings about in the last part of the adjustment a pressure equalization between the two piston surfaces, whereby the further relaxation of the spring memory 111 without inhibiting compressive force 121 and therefore the adjustment speed of the wing 102 is increased in the last movement section.

In Fig. 3, a further exemplary embodiment of a closing device 101 is shown schematically, in which between the actuating piston 109 and second end position 113 - dashed lines in Fig. 3 indicated by dashed lines - located working space 117 acts again as a vacuum chamber and the fluid is again formed by air. The corresponding with the wing actuator 106

Adjustment of the actuating piston 109 from the right, first end position 112 in the left, second end position 113 is again here by a traction means in the form of a string 110, and in this piston movement in the working space 117 contained air is discharged through the first flow path 124. The first flow path 124 has in its course again a check valve 125, which allows this air discharge largely unhindered.

However, in this embodiment, the displaced air is not discharged directly into the ambient air, but is directed into a pilot control 136, comprising a pilot cylinder 137 and a pilot piston 138 displaceably mounted therein. In this pilot cylinder 137, a pilot control chamber 139 is delimited by the spring-mounted pilot piston 138, in which an excess pressure cushion is formed by the air flowing over from the working chamber 117, which displaces the pilot piston 138 counter to the spring force to the right. This pressure cushion reached in the left second end position 113 of the actuating piston 109 its largest volume and a maximum pressure would hold the pilot piston 138 in the maximally deflected to the right position without further action.

Likewise, the actuating piston 109 would be by the in the working space 117 after a brief relaxation movement to the right caused suppression - an entry of air is through the immediately closing check valve 125 yes prevented - stop in the second end position 113.

In order to again achieve a controlled adjusting movement of the actuating piston 109 and of the vane 102, air is controlled from the pilot cylinder 137 by means of a pilot throttle 140, whereby the pilot piston 138 is slowly moved to the left again by the spring bias. The pilot piston 138 is designed so that it at the end indicated by dashed lines this, the desired delay causing movement to the left unlock the check valve 125, whereby the negative pressure existing in the working space 117 abruptly transmits to the pilot chamber 139.

The pilot control chamber 139 can compensate for this negative pressure via a pilot control check valve 141, in that it passes into the open position at negative pressure and air can flow into the pilot control chamber 139 substantially unhindered. As a result of this and by the check valve 125 opened by the pilot piston 138, the negative pressure in the working chamber 117 is not maintained by air flowing in from the pilot control chamber 139 and the adjusting movement of the vane 102 takes place at an increased speed.

The first flow path 124, the second flow path 126 and the Ausgleichsfließweg 130 coincide in this embodiment in the area between actuator cylinder 108 and pilot cylinder 137 together, which of course may be the case in other embodiments, at least in sections.

The embodiment of FIG. 3 further shows a slightly conical design of the actuating cylinder 108, which has a larger inner cylinder diameter in the region of the first end position 112, that is in Fig.3 right than in the second end position 113 in Fig. 3 left. The actuating piston 109 thus has in the region of the second end position 113 a stricter seat in the actuating cylinder 108, which means a good seal against leakage, which could cause an unintentional pressure equalization in the working chamber 117. Furthermore, the adjusting piston 109 has a less tight fit in the region of the first end position 112 and can therefore be moved more easily by the spring accumulator 111 due to lower frictional losses. To compensate for this variable cylinder bore of the actuating piston 109 is equipped with a piston seal 142, which by at least one sealing ring, in the dar- exemplary embodiment are formed by two O-rings made of an elastomer. The use of such a piston seal is of course also possible in other embodiments advantageous.

The conical design of the adjusting cylinder 108 is advantageous in a production thereof with an injection molding process, since the inner core forming the cylinder interior can be demoulded more easily.

FIG. 4 shows a further embodiment of the locking device 101, which is separate and independent of itself, again using the same reference numerals or component designations for the same parts as in the preceding FIGS. To avoid unnecessary repetition, reference is made to the detailed description in the preceding figures. Therefore, it is only mentioned at this point that in this exemplary embodiment the flow paths 124, 126 and the compensating flow path 130 are guided in closed circuits, which is why this embodiment is also particularly suitable for a fluid in the form of an incompressible fluid, preferably hydraulic oil.

Of course, the compensation flow path 130 can also have a variable flow cross section in this embodiment.

The fluid exchange in Stellzy cylinder takes place between the working space 117 and lying on the other side of the actuating piston 109 compensating chamber 143, which can be used with an appropriate routing and orientation of the check valves as additional working space.

Since the hydraulic fluid used here is to be regarded as incompressible, in the adjusting cylinder 108, here in the compensation chamber 143, a compressible compensating element 144, for example made of a closed-cell, foamed elastomer, is arranged, which by displacement reduces the displacement of hydraulic fluid by means of an actuating piston 109 connected traction means or the cord 110 can compensate. FIG. 5 shows a further independent embodiment or development of the closing device 101 in the form of a gas spring damping element, wherein the same reference numerals or component designations are again used for the same parts as in the preceding FIGS. To avoid unnecessary repetition, reference is made to the detailed description in the preceding figures.

The spring accumulator 111 is formed in this embodiment with closed circuit for the use of a hydraulic oil by a hermetically enclosed, compressible gas 145 which is sealed from the working space 117 by a movable separating piston 146. In the wing operation 106, so compressing the gas 145 of the actuating piston 109 is pushed by a piston rod 147 to the left in the actuating cylinder 108, wherein the displaced by the piston rod 147 hydraulic oil causes an equal volume reduction of the gas 145, whereby in this pressure increases and the spring accumulator 111 is biased.

However, since the diameter of the actuating piston 109 is greater than the diameter of the piston rod 147, additional hydraulic oil must be displaced from the working space 117. This is done by the actuating piston 109, both the first flow path 124 with the check valve 125 and the Ausgleichsfließweg 130 in the piston rod side working cavities 148 lead over which a corresponding amount of hydraulic oil can be displaced.

In the dashed left second end position 113 of the actuating piston 109 of Ausgleichsfließweg 130, which is formed by a running in the cylinder longitudinal bore in the actuating piston 109 is largely tightly closed by a separating piston 146 arranged coaxially to the passage bore stopper 149, which shortly before reaching this Position a hydraulic oil drain from the working space 117 can only be done via the check valve 125, which, however, the wing operation is not noticeably influenced.

Falls now in the preloaded second end position 113 of the actuating piston 109, the actuating force away, acts on the left piston surface 118 of the same pressure as on the right piston ring surface 150, and that the pressure of the compressed gas 145 acts, since this pressure on both Sides of the separating piston 146 at least approximately at the same height acts. However, since the right piston ring surface 150 is smaller by the piston rod cross section than the left piston surface 118 acts on the actuating piston 109, a rightward pressure force that can adjust the actuator piston 109 back to the right, first end position 112. For this adjustment, however, it is necessary for hydraulic oil to be displaced from the right-hand second working space 148 into the left-hand first working space 117. However, since the first flow path 124 through the check valve 125 and the Ausgleichsfließweg 130 are closed by the stopper 149, this displacement of the hydraulic oil from the right working chamber 148 in the left working space 117 through the second flow path 126, which in this embodiment by the actuating piston 109th and which leads to this subsequent hollow piston rod 147. In this second flow path 126, a delay device 127 in the form of a throttle valve 129 is again arranged. This throttle valve 129 comprises an axially adjustable in the piston rod 147 valve needle 151 with, for example, conical tip, which limits a flow cross section of the hollow piston rod 147 in a second working space 148 opening transverse bore. Due to the volume flow limited by the throttle valve 129, the actuating piston moves only very slowly in the first movement phase and is thus again brought about the desired time delay of the wing adjustment.

As soon as the distance between the actuating piston 109 and the separating piston 146 increases in this relaxation movement to the right and the stopper plug 149 again from the

Through hole in the actuating piston 109 is pulled out, the hydraulic oil can also flow back over the Ausgleichsfließ away 130 in the form of the through hole from the right second working chamber 148 in the left first working space 117, whereby in the second phase of the independent adjustment 107 this again with the desired higher speed - done.

As a result of the illustrated guidance of the traction means or the cord 110 from an articulation point 153 fixed with respect to the adjusting cylinder 108 via a deflection roller 154 connected to the piston rod 147, the adjustment travel of the actuating piston 109 is translated into a travel path of the wing 102 that is twice as large, as a result of which Design short lengths of the actuator 123 allows. Notwithstanding the embodiment of FIG. 5 and simpler variants of commercially available gas spring elements for the locking device 101 are used, the delay of the relaxation movement can be effected by a damping element in the form of a linear damper or a rotary damper.

FIG. 6 shows a similar embodiment of the closing device 101 with a gas spring element, in which the gas 145 serving as a spring accumulator 111 is enclosed in an outer cylinder 155 enclosing the actual adjusting cylinder 108 on the outside and is again separated from the hydraulic oil by a displaceable separating piston 146 located in the second working space 148, which is formed by the outer cylinder 155, the separating piston 146 and a cylinder head 156 which closes the end face of the adjusting cylinder 108. The first flow path 124 with the check valve 125, the second flow path 126 with the delay element 127 in the form of a throttle valve 129 or a timed shut-off valve 128 and the Ausgleichsfließweg 130 are arranged in this embodiment in the cylinder head 156 and therefore easily accessible and easily replaceable. The increase of the piston speed in the second phase of the expansion movement is also effected here by the release of the compensation flow path 130 by a stopper plug 149 arranged here on the actuating piston 109.

7 shows a partial view of the adjusting cylinder 108 with a plurality of pressure equalization openings 131 arranged at a small distance along a circumferential line. These pressure compensation openings 131 form the equalizing flow path 130 and can be covered by a displaceable covering element 157 with a preferably wedge-shaped recess 158 in various numbers as required are exposed, whereby the free flow cross section of the Ausgleichsfließweges 130 can be adjusted in a simple manner, whereby the adjustment speed of the wing 102 can be adjusted in the second, accelerated movement phase.

Fig. 8 shows a similar embodiment of the Ausgleichsfließweges 130 with a plurality of arranged on the lateral surface of the adjusting cylinder 108 pressure compensation openings 131 and a displaceable in the axial direction cover 157. The adjustment of the free flow cross section of Ausgleichsfließ wegs 130 takes place again by covering or exposing the pressure equalization openings 131 means the cover element 157. In the filling stalls according to FIG. 7 and FIG. 8, it is also conceivable that instead of a plurality of pressure compensation openings 131 only one pressure equalization opening, for example in the form of a long. Is formed hole that can be covered by the cover more or less.

However, the axial arrangement of the pressure compensation openings 131 can also be used to influence the timing of the transition from the slow, caused by the throttle valve 129 adjustment speed on the faster, away from the equalizing flow 130 Verstellgeschwindigkeit by about exactly by individual cover elements the pressure compensation opening, the the effect of switching the speed should not be covered. Thus, the duration of the delay of the closing process can be changed in a simple manner.

Fig. 9 shows a possible embodiment of the check valve 125, which is characterized by a simple structure. The check valve 125 in this case comprises an actuating piston 109 acting on traction means 159 with circular cross-section and smooth surface and a cooperating with this, at the Stellzy cylinder 108 frontally mounted seal assembly 160. The seal assembly comprises in a simple embodiment, at least one O-ring 161, the inner diameter slightly smaller is, as the outer diameter of the traction means 159 and thereby a fluid passage between the O-ring 161 and traction means 159 is prevented.

In the case of the end-side passage of the traction means 159 out of the working space 117 of the actuating cylinder 108, a sealing seat 162 is formed in the form of an approximately cylindrical bore, in which the sealing arrangement 160, here in the form of the O-ring 161, extends axially by a short distance is movable or deformable and has at least one or more axially extending recesses 163 through which fluid can flow in the axial direction at the outer periphery of the seal assembly 160 when the seal assembly 160 is not sealingly abutting an end face 164 of the seal seat 162. This situation is in Fig. 9 with the O-ring 161 in the left, shown in solid lines the case, since here of the outer recesses 163 on the left end face 164 still radial channels 165 lead to the feedthrough hole 166 for the traction means 159. Furthermore, the recess 163 itself may be guided to the outside. By a movement of the traction means 159 to the left, the seal assembly 160 therefore can not be effective, and a fluid passage from the Arbeitsräum to the outside is possible. In contrast, in the movement of the traction means 159 to the right, the seal assembly 160 sealingly abut the right end face 164 of the seal seat 162 and a passage of fluid from the outside into the working space (not shown, right) is prevented, whereby a check valve 125 is formed.

For clarification, the flow path for the fluid which is possible in the left-hand position of the sealing arrangement 160 is also shown by an arrow 167 in FIG. 9.

Fig. 10 shows a locking system 168 for the time-delayed self-closing and locking a wing 102 of a window or door from an open position to a closed position comprising a closing device 101 for the time-delayed closing of the wing 102 and a between fixed frame 103 and adjustable wing 102 unidirectionally blocking acting Locking system 169. In the illustrated embodiment, this comprises a locking element 170 fastened to the frame 103 and a locking device 171 fastened to the wing 102.

Of the locking device 171 leads in approximately horizontal direction an Betätigungsorg- gan 172 in the form of a pull cord 173 to the locking device 101, which is attached to the upper right corner of the window sash is guided by this and deflected in the region of the window frame down. The pull cord 173 thereby does not hang simply in the middle of the window but laterally downwards and, when pulled, causes the locking device 171 to be actuated on the one hand and the pulling force required to open the sash 102 to be introduced into the sash 101 in the window sash on the other hand. where also the force for biasing the spring accumulator between locking device 101 and Fensterrahmenl03 is transmitted.

A section through an embodiment of the locking system 169 is shown in FIG. 11. The attached to the frame 103 locking member 170 projects from the frame approximately at right angles horizontally and is formed, for example, strip-shaped. On its underside it has a locking surface 174 which cooperates with the locking device 171 attached to the wing 102 and protruding above it, by gelungselement 170 is inserted when closing the wing 102 in an insertion opening 175 formed in this and is locked in this by a locking member 176 unidirectional, ie a closing of the wing 102 to the left is possible, but not opening to the right, as pulling out of the locking element 170 from the Einführöff- 175 175 by the locking member 176 is prevented.

The locking member is formed here by an eccentric clamping element 177 in the form of an eccentric clamping roller 178, which cooperates with the locking element 170 such that it is clamped between the eccentric clamping roller 178 and a support member 179 by self-locking frictional forces. For this purpose, the eccentric clamping roller 178 is mounted on a horizontal pivot axis 180 in locking device 171, wherein the roller axis 181 is positioned to the right of the pivot axis 180 by a small eccentricity. Frictional forces between the locking surface 174 on the locking element 170 and the eccentric clamping roller 178 pivot it to the left about the eccentric pivot axis 180 when the locking element 170 is withdrawn, as a result of which the clamping gap in the insertion opening 175 extending between the eccentric clamping roller 178 and the supporting element 179 becomes narrower and the locking occurs due to the self-locking strong rising clamping forces.

Upon a movement of the locking element 170 in the Einführöffhung to the right by reversing the effect described above, the clamping is released.

The Exzenterklemmelement 177 is biased by a biasing spring 182 so that in the nip upon movement of the locking member 170 to the left for the onset of self-locking required contact forces between the locking surface 174 and Exzenterklemmelement 177 act. To release the lock before opening the wing 102, the eccentric clamping element 177 is unlocked by means of the actuating member 172. In the exemplary embodiment, this is done by pulling on the pull cord 173 downwards, which is fixed to the right of the roller axis 181, ie approximately with respect to the pivot axis 180 with respect to the pivot axis 181 on the eccentric clamping roller 178. The nip is thereby increased and released the lock. 12 shows an exploded view of a further embodiment of the locking system 169 with a locking element 170 and a unidirectionally locking locking device 171. The locking element 170 has for this purpose a locking surface 174, which is provided with a locking toothing 183. The locking member 176 cooperating with the locking element 170 in the locking device 171 has a locking toothing 184 which cooperates therewith. As in the example of Fig. 11, the locking member 170 is inserted when closing the wing 102 in an insertion opening 175 on the locking device 171 and supported therein by a support member 179 against a deviation upwards.

Since the latching teeth 183, 184 can cause a sometimes disturbing noise when they engage each other, a sliding element 185 is provided which can be used on the locking element 170 on the locking surface 174, extends to the front edge 186 of the locking element 170 and projects slightly beyond the latching toothing 183. The locking teeth 184 on the locking member 176 can therefore not engage in the region over which the sliding member 185 extends into the locking teeth 183 on the locking element, whereby this relative movement can take place almost silently. The sliding member 185 is strip-shaped and can be inserted into a corresponding groove in the locking teeth 183, wherein the length of the sliding member 185 is selected so that engagement of the locking teeth 183, 184 takes place only in the closed position of the wing 102.

FIG. 13 shows a further exemplary embodiment of a closing device for the time-delayed independent closing of a wing of a window or a door in a schematic axial section.

The locking device shown has an actuating drive 1 for the not shown wing of a window or a door, said actuator 1 comprises a control cylinder 2 with a piston 3, which is loaded by a storage spring 4. This accumulator spring 4 is designed according to the illustrated embodiment as a helical tension spring 5, which acts on the one hand on the piston 3 and on the other hand is struck on a cover 6 of the cylinder 2, to an anchor bolt 7, the more to adjust the bias of the tension spring 5 Has attachment points 8. On the memory spring 4 opposite side is an airtight guided by the cylinder bottom 9 traction means 10 hinged to the piston 3, via which the actuator 1 is drivingly connected to the wing. It probably does not need to be emphasized that the drive connection of the actuator 1 with the independently to be adjusted wings does not have to be done via a guided through the cylinder bottom 9 traction means 10, but z. B. also be guided by a guided through the lid 6 piston rod.

In the cylinder bottom 9 on the one hand designed as a check valve air outlet valve 11 and on the other hand, an air inlet valve 12 is provided, which is present in the exemplary embodiment in the form of a needle valve whose schraubverstellbare needle 13 an adjustable throttle for the in the vacuum chamber 14 between the cylinder bottom 9 and the piston 3 incoming air forms. With an axial distance from the cylinder bottom 9 a plurality of passage openings 15 are provided in the cylinder 2, which form controllable by the piston 3 ventilation valves 16 for the vacuum chamber 14. These vent valves 16 can be selected by means of a slide 17 which closes the unnecessary openings 15, so that the ventilation of the vacuum chamber 14 takes place only when the piston 3, the first not covered by the slide 17 passage opening 15 for the inflow of air in the Vacuum space 14 releases.

If the connected via the traction means 10 with the actuator 1 wing of a window or a door is opened, the piston 3 is pulled under a tension of the accumulator spring 4 against the piston head 9, wherein in the vacuum chamber 14 between the cylinder bottom 9 and the piston 3 existing Air escapes through the air outlet valve 11. In the clamping position of the accumulator spring 4, the piston 3 strikes the cylinder bottom 9, so that the piston 3 can be lifted off the cylinder base 9 only by forming a corresponding vacuum. The resulting negative pressure in the vacuum chamber 14 thus depends on the one hand on the throttle effect of the air inlet valve 12 and on the other hand on the tensile force of the accumulator spring 4. The vacuum building up in the vacuum chamber 14 brakes the piston movement as a result of the action of the accumulator spring 4 until the piston 3 slides past the respectively set ventilation valve 16 and thus releases the ventilation of the vacuum chamber 14, with the consequence that the piston 3 passes through the tension spring without counterforce a Unterdruckbeaiifschlagung is moved to the closed position. This unrestrained piston movement causes an acceleration of the shooting movement of the wing, ensure the associated inertia forces for a safe closing and locking of the wing in the closed position.

In Fig. 14 is an exploded view of a closing device 101 according to. of the embodiment described with reference to FIG. 13, wherein in turn the same reference numerals or component designations are used for the same parts as in the preceding FIG. To avoid unnecessary repetition, reference is made to the detailed description in the preceding figures. FIG. 14 further shows features of the embodiments described with reference to FIGS. 1 and 7.

FIGS. 15 and 16 show a component 201 in the form of a window 202, which encloses a stationary frame or frame 203 which can be installed in a masonry or a façade of a building, as well as a wing 204 adjustably mounted thereon. The wing 204 is designed as a tilting turn-wing 205 and can be displaced by means of a fitting arrangement 206, which comprises a plurality of hinges 207, between a frame 203 and tilt wing 204, optionally about a vertical axis of rotation 208 or about a horizontal pivot axis 209 relative to the fixed frame 203.

In this case, by means of an actuating handle 210, the fitting arrangement 206 can be adjusted so that the rotary tilting wing 205, starting from a closed, on the frame

203 adjacent home position optionally about the vertical axis of rotation 208 in the region of a lateral edge of the wing 204 can be opened or to the horizontal

Pivot axis 209 in the region of a lower edge of the wing 204 preferably in the

Room interior can be pivoted or tilted. The possible rotation angle for the opening of the Drehkippflügels 205 about the vertical axis of rotation 208 and the tilting with respect to the horizontal pivot axis 209 may be limited by the subsequent masonry or the subsequent facade, in particular by a window reveal, or in the case of tilting through in the Beschlaganordnung 206 provided Wegbegrenzungen in

Shape of fittings scissors.

In the conventional fitting arrangements 206, the setting of the fitting functions is carried out by pivoting the actuating handle 210, starting from a generally downward-pointing basic position 211 shown in solid lines into a dashed line. horizontal opening position 212 for opening the Drehkippflügels 205 about the vertical axis of rotation 208 and an adjustment of the actuating handle 210 in an approximately vertically oriented upward in dashed lines shown tilting position 213 to tilt the Drehkippflügel 205 about the horizontal pivot axis 209 can. Depending on the position of the actuating handle 210, different hinges 207 or locking mechanisms (not shown) of the fitting arrangement 206 are therefore activated or deactivated. The positions 212 and 213 of the operating handle 210 are common, but can also be exactly reversed acting.

Fig. 15 shows the Drehkippflügel 205 in the closed position, with the operating handle 210 in the basic position 211, and Fig. 16, the device 201 in a plan view according to the arrow XVI in Fig. 15 with the wing in the closed position. The opening and closing movement 214 with respect to the vertical axis of rotation 208, the tilting movement 215 and the closing movement 216 with respect to the horizontal pivot axis 209 are indicated by arrows in FIG. 16.

In the case of the component 201 according to the invention, a closing device 217 is provided, which is fastened to the upper frame element of the wing 204 in the illustrated embodiment and which, starting from a tilted position of the tilting turnout 205, not shown, causes the closing movement 216 of the tilting turntable 205 and places it in a frame 203, So closed position, spend. The closing movement 216 takes place independently, with a time delay and / or slowed down, for which the closing device 217 comprises a spring accumulator 218, which is tensioned during the tilting movement 215 of the tilting turntable 205 and provides the required closing force during the closing movement 216. The closing force is transmitted from the spring accumulator 218 via a traction mechanism 219, for example in the form of a traction cable 220 between tilting turntable 205 and frame 203, wherein the traction means 219 emanating from the closing device 217 is a deflection element 222, here in the form of a deflection roller 223 is deflected towards the frame 203. The pull cable 220 can be formed, for example, by a thin steel cable, preferably with plastic casing or a monofilament plastic cable, for example made of nylon or polymers with similar mechanical properties. As an example of an advantageous traction means, a monofilament polyamide cord with a diameter of about 1.20 mm and a load-bearing capacity of about 750 N should be used at this location. at maximum load has an elongation at break of, for example, about 30% and at a load of 100 N has an elongation of less than 5%. The traction means 219 can advantageously also consist of approximately transparent material, whereby it visually hardly stands out from the frame of the component 201.

FIG. 15 further shows a locking system 239 comprising a locking element 240 attached to the upper horizontal frame part of the frame 203, and a locking device 241 attached to the upper horizontal part of the wing 4, and which after a manual closing operation of the opened or tilted wing 204 or the independent, time-delayed and / or slowed closing of the tilted wing 204 is automatically effective. The wing 204, which has been moved to a closed position by the closing device 217, with the actuating handle 210 in the tilted position 213 can not thereby be pressed easily from the outside of the component 201, thereby making it difficult for the component 201 to be intruded from outside by the opening process generates a higher noise or forms a higher mechanical resistance, as in a device 1, which is not equipped with this locking system 239.

The locking system 239 is not operatively connected to the locking device 217 in the sense that a mechanical connection for transmitting forces or movements is provided between the locking device 217 and the locking system 239, whereby locking device 217 and locking system 239 are to be considered independent of each other ; A dependency can only be seen in the fact that the closing of the rotary tilting wing 205 effected by the closing device 217 causes the automatic locking by means of the locking system 239. To open the tilt and turn wing 205 from the closed, locked position, the locking system 239 includes an actuator 235, here in the form of a tension member 236, such as a pull cord, with which a user can manually unlock the locking system 239 and then tilt or open the wing 204. The locking system 239 is furthermore independent of the fitting arrangement 206, which in most cases has a locking function coupled to the actuating handle 210. The fitting arrangement 206 is thus formed in most cases by a locking fitting 237, in which the function of the hinges 207 is coupled to a locking function. The activation or deactivation of the locking function of the locking fitting 237 can be done via the operating handle 210, ie manually, but alternatively also by motor.

Since the locking system 239 is also independent of the locking fitting 237 or its locking function, both the locking fitting 237 and the locking system 239 must be unlocked by the user to open or tilt the wing 204. The additional locking system 239 in this case provides increased resistance to external intrusion by the device 201, and also reduces the likelihood of unwanted opening of the wing 204 by unattended infants with the consequent risk of falling, as a toddler is often confined in the It is able to deactivate a locking fitting 237 by moving the actuating handle 210 in the open position 212, but the probability of a simultaneous unlocking of the locking system 239 is significantly lower. 15 and 16, the actuating handle 210 is simultaneously marked as a locking fitting 237, wherein its components such as tie rods, push rods or connecting rods continue from the operating handle 210 mostly along the sash and cooperate with locks, not shown, on the frame 203. Since such a locking fitting 237 can be embodied in many different ways, it is furthermore advantageous that the locking system 239 is functionally and / or structurally independent of this and is not bidirectionally operatively connected thereto, thus subsequently also providing a component 201 with a locking system 239 which causes an additional increase in safety, can be retrofitted without the structural design of the locking fitting 237 would have to be considered.

The locking system 239 is designed to be unidirectionally locking and comprises the locking element 240 which can be fastened to the frame 203 and has at least one locking surface and the locking device 241 secured to the wing 204 with at least one locking element cooperating with the locking surface.

The locking system 239 is preferably located at the upper end portion of the wing 204 because its lower end portion has sufficient mechanical resistance to penetration through the hinges 207 of the fitting assembly 206 and through the locking fitting 237, respectively, even though the operating handle 210 is in the tilted position 213. should and by the additional locking system 239 and the upper end portion of the wing 204 is secured against forced entry by pressing the wing 204.

The actuator 235 in the form of the tension element 236, with the unlocking of the locking system 239, can advantageously be used in this arrangement simultaneously to initiate the force required for tilting in the wing 204, since when tilting the force transmitted by the traction means 219 of the spring accumulator 218 must be overcome and in the case of the tilting movement occurring about the horizontal pivot axis 209, the introduction of the force at the upper end portion of the wing 204 causes a better lever ratio than the initiation of the force required for tilting via the actuating handle 210, which is normally approximately halfway Height of the wing 204 is located. After the operating handle 210 in conventional locking fittings 237 must be spent for tilting the wing 204 in vertically upwardly tilted position 213, the tilting of the wing 204 can be carried out comfortably by means of the Betätigungsorgangs 235, since by pulling the actuator 235 first the locking system 239 is deactivated and then the applied via the actuator 235 in the form of the tension member 236 tensile force for tilting the wing 204 against the force exerted by the closure device 217 with the spring 218 force can be used.

FIGS. 15 and 16 show the locking system 239, which effects a locking function which is independent of the locking device 217 and not operatively connected thereto after the wing 204 has been closed. The locking system 239 is functionally independent of a possibly present locking fitting such that it can become effective even without manual actuation of the locking fitting and can only be deactivated by manual unlocking. The difference to the locking system 169 of FIG. 10 is that the locking system 239 is arranged with the wing closed 204 between the fold of the wing 204 and the fold of the frame 203. The locking system 239, which comprises a locking element 240 attached to the frame 203 and a locking device 241 attached to the wing 204, is therefore not or only slightly visible in frontal view of the component 201, whereby the overall visual impression of such a component 201 by the locking system 239 is not is impaired. The locking system 239 comprises for manual de Activation of the automatic locking function also an actuator 235, here in the form of a tension member 236, which extends from the locking device 241 first in the rebate of the wing 204 and then passed through a passage 242 in the wing 204 to the wing front side 243 and from there to a Operating range, which is easily accessible to the user, leads or hangs down.

The passage 242 may be formed for the traction means 219 by a simple bore in the wing 204, but preferably be designed as a separate component which is inserted into a through hole in the wing 204 and has rounded portions at the through hole to the friction of the tension member 236 in the Implementation by the wing 204 to reduce.

The concealed locking system 239 can also be used in the case of a blunt wing 204 striking in the frame 203, where it is likewise concealed in the fold of the frame 203 arranged by the wing 204 in a frontal view of the closed component 201.

17 shows an advantageous embodiment of the locking system 239, which is arranged concealed in the component 201 between a fold 244 of the sash frame and a fold 245 of the frame 203. As already described with reference to FIGS. 15 and 16, the locking system 239 comprises the locking element 240 fastened in the rebate 245 of the frame 203 and the locking device 241 fastened in the rebate 244 of the sash frame which, when the sash 204 or tilting sash 205 approaches, enters the Closed position causes a unidirectional independent locking of the wing 204 in the closed state relative to the frame 203. The basic form of the locking element 240 is in the illustrated embodiment, for example, a block-shaped block whose longitudinal axis is approximately parallel to the window plane and its opposite end faces 246 recesses 247 which are adapted to engage the locking device 241 adjustably mounted locking members 248, whereby the locking effect is achieved. In the locking recesses 247 are oriented approximately parallel to the window surface oriented locking surfaces 249, which are engaged behind by the locking members 248 in the closed and locked state. The locking device 241 has a basic shape similar to a U, which surrounds the cuboid locking element 240 laterally in the closed state of the wing 204. 17 shows the locking system 239 in the locked position, that is to say with the locking members 248, in engagement with the locking surfaces 249. The locking members 248 are designed in the form of locking bolts 250, which have a collar 251 in their rear end section, which is remote from the locking element 240. with which they are as well as with the locking element 240 facing shaft part in a base housing 252 of the locking device 241 are adjustably mounted. In this case, spring elements 253, here in the form of cylindrical compression springs 254, are arranged in extension of the locking bolts 250, which are each supported with one end on the collar 251 of a locking bolt 250 and with the other end on the base housing 252 of the locking device 241. The basic prestressing of the spring elements 253 causes the locking members 248 and the locking bolts 250 to be pressed into the locking position, that is to say into engagement with the locking recesses 247 or the locking surfaces 249. In order to bring the locking device 241 into the blocking position with the locking element 240, the projecting ends of the locking pins 250 and / or the corners of the locking element 240 have chamfers 255 which, as the locking device 241 approaches the locking element 240, automatically push back the locking bolts 250 in the axial direction allow against the action of the spring elements 253.

In order to enable unlocking of the locking system 239, the locking device 241 comprises two locking elements 250 associated unlocking elements 256 which are rotatably mounted in the locking device 241 and its base housing 252 and whose axes of rotation approximately at right angles to the adjustment direction of the locking bolt 250. The unlocking elements 256 have an approximately circular cylindrical shape and have on their the locking pin 250 facing end faces eccentric pin 257, which abut respectively on the locking element 240 facing surface of the collar 251 on the locking pin 250. As a result, the eccentric pins 257 rest on the collar 251 in relation to the spring elements 253 in the form of the compression springs 254. As a result, a rotation of the unlocking elements 256 via the eccentric pin 257 lying on the collar 251 causes a displacement of the locking bolt 250 against the spring force of the compression springs 254 in an unlocking position in which the locking bolt 250, the locking surfaces 249 of the locking recesses 247 on the locking element 240 does not engage behind and thereby the Drehkippflügel 205 can be opened or tilted. The adjustment direction of the locking bolt 250 is indicated in FIG. 17 by the reference numeral 258.

The fastening of the locking device 241 in the rebate 244 of the wing 204 of the casement is effected by means of screws 259, with which the locking device 241 is fixed in the fold 244 in the vertical or in the horizontal direction. Preferably, the locking device 241 is fixed in both the vertical and in the horizontal direction. However, the locking device 241 can also be pressed with a fitting part or hung in it. The attachment of the locking element 240 in fold 245 of the frame

203 also takes place with screws 259, wherein the locking element 240 may be slightly adjustable in its mounting position by the fixing holes are formed by elongated holes 260 on the cuboid locking element 240 which allow an adjustment of the locking element 240 approximately at right angles to the window surface, whereby tolerances in the folding distance between Fensterfalz 244 and frame rebate 245 can be compensated.

In order to prevent a change in position of the locking element 240 in the fold 245 of the frame 203 in the assembled state, particularly prong-shaped projections may be provided on the mounting surface, which penetrate slightly into the material of the frame 203 and the non-positive connection between locking element 240 and frame 203 through support the screws 259 by an additional positive locking effect. The material of the locking element 240 as well as the housing 252 of the locking device 241 is preferably suitable for production by injection molding or die casting and therefore advantageously formed by a suitable metal or plastic, which are characterized by high mechanical strength and good processing capabilities with injection molding, In particular, high strength polyamide with glass fiber reinforcement can be used advantageously.

In order to facilitate the assembly of the locking system 239, in particular the mutual positioning in the attachment of the locking device 241 in the rebate 244 of the wing

204 and the locking member 240 in the fold 245 of the frame 203, the following assembly method is provided. First, the locking element 240 is locked in locking position brought to the locking device 241; Subsequently, the locking system 239 is positioned in the fold 244 of the wing 204 and fastened by means of screws 259. Subsequently, the wing 204 is moved in the closed position with respect to the frame 203 and marks the resulting position of the locking element 240 to the fold 245 of the frame 203. In order to facilitate the marking of this position, a marking plate 261 may be arranged on the front edge of the locking element 240, which, as indicated in FIG. 15, projects upwards relative to the locking element 240 and projects slightly above its upper edge 262 in the closed state of the wing 204. This position can be easily retained on the frame 203 and, accordingly, fastening holes for positionally correct screwing of the locking element 240 can be introduced into the fold 245 of the frame 203. Alternatively, it would also be possible to provide a marking mandrel 263 on the rear side of the locking element 240, which when approaching the wing 204 with the locking system 239 mounted when approaching the frame 203 leaves a small, non-irritating marking in the fold 245 of the frame 203 and This also represents an aid to the positioning of the mounting holes. The marking mandrel 263 can be designed as a separate component which is used for the assembly process in the locking element 240, so be injection molded in the manner of a bolt-shaped grain or on the locking element 240 and after marking, if necessary, be shortened. To set the correct position of the locking element 241 in the direction of the horizontal rebate depth, so to determine a distance of the locking element 241 to the vertical rebate surface 245, after marking the lateral position by means of the marking mandrel 263 at the marked position a hole in the rebate 245 can be introduced , which has a press fit with the marking mandrel. After closing and subsequent unlocking and opening of the wing 204, the locking element 240 remains in the correct position by means of the marking mandrel 263 inserted in the bore, in which the wing bears against the usually existing sealing surface at normal closing force and the locking member or the locking members also Engage locking surface or the locking surfaces behind.

In order to effect the rotation of the unlocking elements 256 required for an unlocking operation, as shown in FIGS. 17 and 18, these are connected in a special way to the actuating member 235 in the form of the tension element 236. The tension member 236 is Here, as shown in Fig. 18 by two unlocking elements 256 in the radial direction, ie in the diameter direction, threaded through and fixed tensile strength at one end to a fixed point 264. If a pulling movement is now performed with the free end of the tension element 236, the tensioned tension element 236 can follow this movement only by shortening its length between a force application point 265 at the free end and the fix point 264, this shortening being a rotational movement the unlocking 256 causes. For this purpose, the tension element 236 in the locked position, which can also be referred to as the starting position, laid approximately loop-shaped, and formed by the threading through the Entriegelungselemente 256 bays cause a longer arc length of the tension member 236. Will now be a tensile force on the free end of the tension element 236, which preferably has only a very low longitudinal elasticity exerted, the tension element 236 between force application point 265 and fixed point 264 shorten its arc length as much as possible, and reduce the existing in the unlocking 256 bays as much as possible, whereby a resulting rotational movement of the Ent - Locking elements 256 is effected and by means of the eccentric pin 257, an unlocking of the locking pin 250 is carried out. The tension element 236, which may also be referred to as a pull cord or unlocking cord, is advantageously guided, at least in sections, in a feedthrough channel 266 on the underside 267 of the locking device 241. The fixed point 264 can be formed in a simple manner in that in the loose end of the tension element 236, a node is formed, which is greater than the clear cross section of the feedthrough channel 266. In this way, in a further development of the embodiment of FIG Tensile element 236 and a plurality of locking systems 239 parallel or successively serially coupled and unlocked via a train on the tension element 236, which provides even greater security against forcible opening of the wing 204 with nevertheless easier and more comfortable unlocking with only one unlocking movement. For this purpose, for example, the tension element 236 can be threaded starting from a fixed point 264 by a plurality of locking devices 241, whereby pulling on the free end of the tension element 236 or between two locking systems 239 all locking devices 241 are unlocked simultaneously.

As a security measure, in order to be able to make an unlocking of the locking system 239 even in the case of a possible tearing of the tension element 236, the unlocking elements 256 have actuating holes 268 or abutment surfaces which are intended for receiving or Attachment of an elongated tool are suitable, which can be introduced between the frame 203 and window rebate 244 in the region of the window seal in the actuating holes 268 or attached to the shoulder surfaces and can be used to rotate the unlocking elements 256. The actuating holes 268 extend approximately at the top of the unlocking 256 in the radial direction and can also be designed as slots or approach surfaces for radial pressure for rotating the unlocking 256.

14 also shows a deflecting element 222, which is arranged on the front side on the closing device 1, 101, 217, here in the form of a deflection roller 223, with which the traction means 10, 110, 159, 219 extend in any direction from the axial direction of the adjusting cylinder 108, in particular approximately at right angles, can be deflected in the direction of the fixed frame or the wing. In particular, the deflecting element 222, such as the bearing block 223 bearing the bearing roller with respect to the axial direction of the actuating cylinder 108 may be rotatable, whereby the closing device 1, 101, 217 can be adapted with little effort to different mounting situations.

Fig. 15 further illustrates the ease of gripping the tension member 236 which may be used for unlocking the locking system 239 and tilting the tilt and turn wing 5 at the free end of which is attached a pull button 269. At Zugkopf 269 a sleeve 270 is further formed, through which the tension element 236 is performed. This sleeve 270 may be integrally connected to the pull knob 269 or formed as a separate component by injection molding and prevents that when pulling the pull knob 269, the tension element, which is formed for example by a white Perlonschnur, can be contaminated.

The variants of the component or the closure device illustrated with reference to the embodiments are also usable with the same advantageous effects for windows and doors with sliding sashes, as they are often used in certain countries or swinging wings, such as roof windows.

The exemplary embodiments show possible embodiments of the closing device 10I ₅ 217 for adjusting a wing and the device 201, wherein at this point It should be noted that the invention is not limited to the specifically illustrated embodiments of the same, but also various combinations of the individual variants with each other are possible and this possibility of variation due to the doctrine of technical action by objective invention in the skill of those working in this technical field. So are all conceivable embodiments, which are possible by combinations of individual details of the illustrated and described embodiment variant, includes the scope of protection.

For the sake of order, it should finally be pointed out that for a better understanding of the construction of the closing device 101 or of the component 201, these or their components have been shown partially unevenly and / or enlarged and / or reduced in size.

The task underlying the independent inventive solutions can be taken from the description.

Above all, the individual in Figs. 1; 2; 3; 4; 5; 6; 7; 8th; 9; 10; 11; 12; 13; 14; 15, 16, 17 and 18 show the subject matter of independent solutions according to the invention. The relevant objects and solutions according to the invention can be found in the detailed descriptions of these figures.

REFERENCE NUMBERS

1 actuator 2 actuator cylinder

3 pistons

4 memory spring 41

5 tension spring 42 43

6 lid 44

7 anchor bolts 45

8 lifting point

9 cylinder bottom 46

10 traction devices 47 48

11 air outlet valve 49

12 air intake valve 50

13 needle

14 vacuum chamber 51

15 passage 52 53

16 ventilation valve 54

17 pushers 55

18

19 56

20 57 58

21 59

22 60

23

24 61

25 62 63

26 64

27 65

28

29 66

30 67 68

31 69

32 70

33

34 71

35 72 73

36 74

37 75

38

39

40 81 123. Actuator

82 124. First flow path

83 125. Check valve

84 126. Second flow away

85 127. Delay element

128. Timed shut-off valve

86 129. Throttle valve

87 130. Balancing flow away

88

89 131. Pressure equalization opening

90 132. Compression spring

133. Cylinder front side

91 134. Ventilation opening

92 135. Bypass line

93

94 136. Feedforward control

95 137. Pre-tax cylinder

138. pilot spool

96

139. Pilot room

97 140. Pilot control throttle

98

99 141. Pilot check valve

100 142. Piston seal

101 Device 143. Compensating space

102 wings 144. Compensation element

103 Frame 145. Gas spring

104 starting position

105 Preload position 146. Separating piston

147. Piston rod

106 Wing operation 148. Working space

107 Self-adjusting 149. Plug stopper

108 Stellzy linder 150th piston ring surface

109 actuator piston

110 cord / pulling means 151. valve needle

152. Cross boring

111. spring accumulator 153. articulation point

112. First end position 154. Deflection pulley

113. Second end position 155. Outer cylinder

114. Mechanical spring

115. Tension spring 156. Cylinder head

157. Covering element

116. Cylinder inner wall 158. recess

117. Working space 159. Traction means

118. Cylinder front side 160. Sealing arrangement

119. actuating piston surface

120. Spring 161. O-ring

162. Seal seat

121. Compressive force 163. Recess

122. Fluid 164. Face 165. Radial channel

206. Fitting arrangement

166. Procedure 207. Hinge

167. Arrow 208. Vertical axis of rotation

168. Locking system 209. Horizontal axis of rotation

169. Locking system 210. Operating handle

170. locking element

211. Basic position

171. Locking device 212. Opening position

172. Actuator 213. Tilt position

173. Pull cord 214. Opening and closing movement

174. Locking surface 215. Tilting movement

175. insertion opening

216. closing movement

176. Locking device 217. Locking device

177. Eccentric clamping element 218. Spring accumulator

178. Exzenterklemmrolle 219. Zugmittel

179. Support member 220. Pull rope

180th pivot axis

221. Frame element

181. Roller axle 222. deflecting element

182. Biasing spring 223. Deflection pulley

183. Locking teeth 224.

184. Locking teeth 225.

185. sliding element

226th

186. leading edge 227.

187. 228.

188. 229.

189. 230.

190th

231st

191. 232.

192. 233.

193. 234.

194. 235. B

195th

236. tension element

196. 237. Locking fitting

197. 238. Distance

198. 239. Locking system

199. 240. Locking element

200th

241. Locking device

201. Component 242. Implementation

202. Window 243. Front wing

203. Frame 244. Fold

204. Wings 245. Fold

205. Tilt-and-turn sash 246. Face

247. Barrier recess 248. Locking element

249. Locking surface

25Ö. locking bolt

251. Bundle 0 252. Basic housing

253. Spring element

254. Compression spring

255. Bevel

256. unlocking element

257. Eccentric pin

258. Adjustment direction

259. Bolt Q 260. Slot

261. Marking plate

262. top edge

263. Marker pin5 264. Fixed point

265. Force application point

266. Feedthrough channel

267. Bottom 0 268. Operation hole

269. Pull knob

270th sleeve 5

0

5

0

Claims

P atentan pr oce

1. component (201), in particular window or door with tilt and turn window or hinged window or sliding window, comprising a frame (103, 203) and relative to the frame (103, 203) about a substantially horizontal pivot axis (209) pivotable or relative to the frame (103, 203) sliding wings (102, 204), a locking device (1, 101, 217) for the time-delayed or slowed, self-closing the wing (102, 204) and a locking system (169, 239) for locking the wing (102, 204) in the closed position on the frame (103, 203), characterized in that the locking system (169, 239) is designed to be self-locking when the wing (102, 204) is closed, and one on the frame (103, 203) fastenable locking element (170, 240) having a locking surface (174, 249) and a locking device (171, 241) attached to the wing (102, 204) with a locking surface (174, 249 ) cooperating locking member (176, 248).

2. The component (201) according to claim 1, characterized in that the locking member (176, 248) by means of a spring element (182, 253) in the reverse direction, ie in engagement with the locking surface (174, 249) is biased and by means of an actuator ( 172, 235) in a disengaged from the locking surface (174, 249) located ses position is adjustable.

3. The component (201) according to claim 2, characterized in that the actuating member (172, 235) by a tension element (173, 236) is formed.

4. The component (201) according to claim 3, characterized in that the tension element (173, 236) is guided by guide means or Umlenlαnittel on the closing device (101, 217) to a handling area.

5. The component (201) according to one of claims 1 to 4, characterized in that the frame (103, 203) arranged locking element (240) has at least one Sperrausnehniung (247) and arranged on the wing (102, 204) locking device ( 241) a locking member (248) in the form of at least one, preferably in or from the locking recess (247) displaceable hook element or locking bolt (250).

6. The component (201) according to any one of claims 1 to 3, characterized in that the locking device (171) at least one locking member (176) in the form of an adjustable Exzenterklemmelements (177), in particular a Exzenterklemmrolle (178), and a support member (179 ) for supporting the from the Exzenterklemmelement (177) on the locking surface (174) acted upon locking element (170).

7. The component (201) according to any one of claims 1 to 3, characterized in that the locking element (170) on the locking surface (174) has a latching toothing

(183) and the locking member (176) comprises a locking member (176) in the form of a latching element cooperating with the latching toothing (183) in a form-fitting manner and also having a latching toothing (184).

8. The component (201) according to claim 6, characterized in that on the latching toothing (183) of the locking element (170), a sliding element (185) can be inserted, the locking surface (174) in the form of the locking teeth (183) viewed in the closing direction in a sliding portion without engagement of the locking teeth (184) of the locking element and an adjoining latching portion with engagement of the latching toothing (184) of the latching element divided.

9. The component (201) according to claim 7, characterized in that the sliding element (185) viewed in the direction of movement of the locking element (170), in at least two different positions on the locking toothing (183) can be fixed.

10. The component (201) according to any one of claims 1 to 9, characterized in that between the frame (203) and wings (204) acting, manually or motor-operated locking fitting (237), with which the wing (204) in the closed position relative to the frame (203) is lockable, is formed and the locking system (239) from the locking fitting (237) is functionally and / or structurally independent and not operatively connected to this.

11. The component (201) according to one of claims 1 to 9, characterized in that as a locking system between a frame (203) and wings (204) acting, manually or motor-operated locking fitting (237), with which the wing (204) in the closed position relative to the frame (203) is lockable, is formed, in which in the open position of the wing (204) with an actuating handle (210) of the locking fitting (237) when closing the wing (204) automatically with a locking element (240) on the frame (203) cooperating, spring-mounted locking member (248) is activated and in the closed locked position of the wing (204) the activated locking member (248) by means of the actuating handle (210) out of engagement with the locking gelungselement (240) can be brought.

12. The component (201) according to one of claims 1 to 11, characterized in that the locking system (239) with the wing closed (204) between the fold (244) of the wing (204) and the fold (245) of the frame (203 ), whereby the locking element (240) and the locking device (241) are not visible in a frontal view of the component (201).

13. The component (201) according to claim 12, characterized in that the locking member (248) by means of an actuating member (235) in the form of a tension element (236) in a not engaged with the locking surface (249) located release position is adjustable and the tension element (236) from the locking system (239) through a passage (242) in the wing (204) to the wing front side (243) is guided.

14, component (201) according to claim 13, characterized in that the passage (242) has a vertical distance from the horizontal pivot axis (209) of at least two-thirds of the height of the sash.

15. The component (201) according to claim 13 or 14, characterized in that the horizontal pivot axis (209) in the region of the lower horizontal frame part of the wing (204) and the passage (242) of the tension element (236) on the upper horizontal frame part the wing (204) is arranged.

16. The component (201) according to any one of claims 2 to 10 or 12 to 15, characterized in that the adjustment for the locking member (176, 248) by a stop element or the adjustment for the actuator (172, 235) in the direction of the release position by a fixed point (264) on the locking system (169, 239) or on the wing (102, 204) is limited and by the actuating member (172, 235) in the form of the tension element (173, 236) has a handle for tilting the wing (102, 204) about the horizontal pivot axis (209) against the tensile force of the spring accumulator (4, 111, 218) of the closing device (101, 217) is formed.

17. closing device (101) for the time-delayed or slowed, self-closing, a wing (102) of a window or door from an open biased position (105) in a closed starting position (104) with a wing (102) attacking, by a Spring memory (4, 111) act upon actuator (1, 123) and means for time-delayed or slowed down in a leaf actuation (106) from the starting position (104) in the biasing position (105) in opposite directions to the independent adjustment (107) tensionable spring accumulator (4 , 111), characterized in that the adjusting drive (1, 123) has a setting cylinder (2, 108) with a first end position (112) corresponding to the starting position (104) and a second one corresponding to the pretensioning position (105) Endstellung (113) adjustable, with the wing (102) motion-connected and with the spring memory (4, 111) operatively connected Stellkol Ben (3, 109) which defines together with the cylinder inner surface (116) at least one variable, a fluid receiving working space (117) and in the working space (117) a first flow path (124) opens for the fluid in the Check valve (11, 125) is arranged, which is at the by the blade actuation (106) effected adjustment of the actuating piston (3, 109) from the first end position (112) in the second end position (113) in the open position, and a second flow path ( 126) for the fluid in which a delay element (127) is arranged in the form of a time-controlled shut-off valve (128) or in the form of a throttle valve (12, 129) which is responsible for the pressure released by the expansion of the spring accumulator (4, 111). caused autonomous adjustment (107) of the actuating piston (3, 109) from the second end position (113) in the first end position (112) in the second flow path (126) shut-off or flow-inhibiting effect and that during the adjustment of the actuating piston (3 , 1 09) from the second end position (113) in the first end position (112) at least one in the working space (117) emanating Ausgleichsfließweg (130) is effective.

18, closing device (101) according to claim 17, characterized in that the spring accumulator (111) by a mechanical spring (4, 114), in particular a tension spring (115) is formed.

19. Closing device (101) according to claim 18, characterized in that the spring accumulator (111) is formed by a gas spring (145) or a gas spring element with variable gas volume.

20. Closing device (101) according to any one of claims 17 to 19, characterized in that the fluid is formed by a gas, in particular air.

21, closing device (101) according to any one of claims 17 to 19, characterized in that the fluid by a liquid, in particular a hydraulic oil having a viscosity index with a value of at least 100, preferably at least 120 according to

ISO 2909 and an operating temperature with a lower limit of less than 10 ⁰ C, is formed.

22. Closing device (101) according to any one of claims 17 to 21, characterized in that the working space (117) in the second end position (113) of the actuating piston (109) has a smaller, preferably very low, volume, as in the first end position (112) of the actuating piston (109) and thereby acts as a vacuum chamber.

23. Closing device (101) according to any one of claims 17 to 22, characterized in that the throttle valve (129) has an adjustable flow cross-section.

24. Closing device (101) according to one of claims 17 to 23, characterized in that the compensating flow away (130) has an adjustable flow cross-section.

25, closing device (101) according to any one of claims 17 to 24, characterized in that the first flow path (124) with the check valve (125) and / or the second flow path (126) with the delay element (127) and / or the Ausgleichsfließweg 130 passes through the actuating piston (109).

26. Closing device (101) according to any one of claims 17 to 25, characterized in that the movement connection between the actuating piston (109) and wing on the actuating piston (109) fixed traction means (110, 159), with which the actuating piston (109) entge - The effect of the spring accumulator (111) from the first end position (112) in the second end position (113) is adjustable.

27. Closing device (101) according to claim 26, characterized in that the traction means (110, 159) passes through the working space (117) axially and by a sealing arrangement (160) sealed out of the actuating cylinder (108) is led out.

28, closing device (101) according to claim 26 or 27, characterized in that the traction means (110, 159) at one end of the adjusting cylinder (108) via a deflecting element (222) is guided, with which it starting from the axial direction in one of them deviating, in particular perpendicular direction can be deflected. (Fig. 14)

29, closing device (101) according to claim 28, characterized in that the deflecting element (222) with respect to the axial direction of the adjusting cylinder (108) is rotatably mounted thereon.

30. Closing device (101) according to spoke 27, characterized in that the

Non-return valve (125) by the traction means (110, 159) is formed with circular cross-section and smooth surface and a cooperating with this, on the actuating cylinder (108) frontally mounted seal assembly (160).

31. Closing device (101) according to claim 27 or 30, characterized in that the sealing arrangement (160) comprises at least one elastic sealing ring, in particular an O-ring (161), an X-ring or equivalent.

32. Closing device (101) according to claim 30, characterized in that the sealing arrangement (160) in a seal seat (162) on the actuating cylinder (108) is axially displaceable or axially deformable and in the adjustment of the actuating piston (109) from the first end position (112) in the second end position (113) the traction means (159) and, caused by the actuation of the traction means (159), Drackunterschiede the Dichtungsanord- (160) in an axial position or effect an axial deformation, are effective in the recesses (163) in the seal seat (162) forming the low-resistance first flow path (124).

33. Closing device (101) according to one of claims 17 to 32, characterized in that the spring accumulator (111) is adjustable in its bias.

34. Closing device (101) according to any one of claims 17 to 33, characterized in that the Ausgleichsfließweg (130) at least one on the cylinder jacket of the Stellzy- (108) arranged, in particular by a cover (157) in its passage cross section changeable, pressure compensation opening (130). 131).

35. Closing device (101) according to any one of claims 17 to 34, characterized in that the working space (117) of the adjusting cylinder (108) with a pilot control device (136) is fluidly connected by means of the check valve (125) from the blocking position to the open position is adjustable.

36. Closing device (101) according to any one of claims 17 to 35, characterized in that the actuating cylinder (108) along its longitudinal axis has a variable, in particular conical cylinder cross-section, wherein the cylinder cross-section, starting from the region of the second end position (113) of Setting piston (109) in the direction of the first end position (112) of the actuating piston (109) increases.

37. closing device for time-delayed or slowed independent adjustment, in particular for closing, a wing of a window or door with an attacking wing, acted upon by a spring actuator and a device for delayed or decelerated relaxing the opposite in a wing operation in opposite directions for independent adjustment Spring accumulator, characterized in that the actuating drive (1) comprises a setting cylinder (2) with a piston (3) loaded by a storage spring (4), between which and a cylinder bottom (9) of the cylinders (2) a piston ( 3) in the opposite direction to the accumulator spring (4) acting on negative pressure space (14) that in at least one of the two by the cylinder bottom (9) and the piston (3) resulting end faces of the vacuum chamber (14) on the one hand a Luftauslass- Valve (11) in the form of a check valve and on the other hand, a throttle representing air inlet valve (12) and that the piston (3) a vent valve (16) for the vacuum chamber (14) of the cylinder (2) in response to a predetermined relaxation of the Memory spring (4) controls.

38. Locking device according to claim 37, characterized in that the tension spring (5) formed memory spring (4) on the vacuum chamber (14) facing away, ventilated side of the cylinder (2) on the piston (3) engages.

39. Locking device according to claim 37 or 38, characterized in that the storage spring (4) is adjustable in its bias.

40. Locking device according to one of claims 37 to 39, characterized in that both the air inlet and the air outlet valve (12, 11) in the cylinder bottom (9) are arranged.

41. Locking device according to one of claims 37 to 40, characterized in that the air inlet valve (12) is adjustable with respect to the throttle cross-section.

42. Locking device according to one of claims 37 to 41, characterized marked, that the ventilation valve (16) for the vacuum chamber (14) at least one with the

Piston (3) has cooperating passage opening (15) in the cylinder jacket.

43. Locking device according to claim 42, characterized in that at least two optionally coverable passage openings (15) are provided at a mutual distance in the direction of the cylinder axis.

44. component (201) according to one of claims 1 to 16, characterized in that the closing device (1, 101, 217) according to one of claims 17 to 43 is formed.