EP2304149B1 - Device for the automatic displacement of a leaf of a window or of a door with a spring-load device - Google Patents

Description

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

In order to ventilate a room advantageously over an open window or an open door, without having to accept excessive heat loss in the cold season, for example, after an adequate ventilation period, it is necessary to close the window or the door. For this closing process to proceed independently, has already been proposed ( DE 195 41 198 A1 ), when opening the window or door wing to tension a spring store, with its energy an actuator can be acted upon to close the wing, when the locked in the tensioning spring storage is unlocked after the expiration of a simultaneously wound with the tensioning of the spring accumulator movement. 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.

It is also known for the independent closing of sliding doors ( DE 195 13 742 A1 ) to load the sliding door by means of a cable with a weight 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 device is for example from the DE 44 45 366 A1 known 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 means of 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 locking 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 object of the invention is achieved by a generic component with the features of the characterizing part of claim 1.

In such a device, the advantageous automatic closing function is extended by a locking function which automatically takes effect when closing, and which, like the closing function, also has no external energy source, such as 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.

In addition, while the locking member is biased by a spring element in the reverse direction, that is in engagement with the Verrieglungsfläche and adjustable by means of an actuator in a not in engagement with the locking surface release position. Thereby, the locking 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.

Further, since the actuator is formed by a pulling element, the operation can be moved with simple means and cost of the possibly difficult to reach locking device in an easily accessible handling area.

According to the invention, the adjustment path for the locking member or the actuating member in the direction of the release position or unlocking position is further limited by a stop element or a defined fixed point on the locking system or on the wing and by the actuator in the form of the tension element is a handle for tilting the Wing formed around the horizontal pivot axis against the tensile force of the spring accumulator of the locking device. This ensures that the required to tilt the wing traction on the actuator is reliably and without damaging the locking system is introduced into the window sash, after unlocking the locking system takes place in a first phase with relatively low tensile force and only in a second phase, the tilting of the wing ,

In particular, the tension element can be guided by guide means or deflecting means on the closing device for closing the wing to a handling area. If in this case an operation by pulling on the tension element, 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 on the tension element this can be used in a row simultaneously 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 tension element, namely in the region of the closure device, the biasing of the spring accumulator can be done by opening the wing with relatively little effort.

In addition, the tension element can also be used for triggering or activating further additional functions, that is to say for switching functions, further adjustment 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 air freshener of commercial design, for instance by fixing the air freshener between the free end of the tension element grasped by the user and a fixed stop point of the tension element and the tension occurring in the pulling element Tension a spray button pressed. The attachment of the fragrance dispenser can take place on the wing, but advantageously also on the tension element alone. So z. B. the tension element in the form of a Perlonschnur over deflection points on the air freshener or this receiving bracket be loops, with a deflection point is connected to the Duftspendergehäuse or the holder and another deflection 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 locking recess 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 the wing a violent opening of such a device are a high resistance opposes. 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 acted upon by the Exzenterklemmelement 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 locking surface is effective, whereby the locking element is clamped between Exzenterklemmelement and support member and a movement of the wing in Direction of the open position is prevented. 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 locking teeth on the locking element and the locking teeth on the locking element for certain applications in quiet zones such as bedrooms or sick rooms could cause disturbing noises, it may be advantageous if a sliding element can be used on the locking teeth of the locking element, the locking surface in shape considered the 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. 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 causes such a locking system without particular attention to structural conditions of the locking fitting, can also be retrofitted and thus retrofitting a security-related locking system is easily possible.

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, for example, incorporation of components, e.g. allow with a so-called Eurofalz with a seam height of about 12 mm.

The actuator for unlocking the locking member according to the invention as a tension element, designed as a drawstring, whereby the actuator can be easily redirected by simple means, such as pulleys or guide sleeves from the locking system to an ergonomically favorable for the user operating area. 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. The tension element can be approximately from the locking system on the upper frame part of the sash, within the frame part be approached horizontally to the subsequent vertical frame part and be led out in this area by a grommet to the wing front side, which in a passage with rounded edges only a slight frictional 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 tension member 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 a non-integrated locking system, since the opening process is thereby facilitated.

A favorable for practical design of the device with the lowest possible actuation forces is given when the horizontal pivot axis in the region of the lower horizontal frame part of the wing and the implementation of the tension element or the point of force application of the drawn by the user pulling element is arranged on the upper horizontal frame part of the wing.

The component may further be embodied such that the actuating drive comprises an actuating cylinder with an actuating cylinder which is adjustable between a first end position corresponding to the initial position and a second end position corresponding to the pretensioning position, and which is movably connected to the spring accumulator and operatively connected to the spring accumulator the cylinder inner surface bounded at least a variable, a fluid receiving working space and in the working space a first flow path for the fluid flows, in which a check valve is arranged, which in the actuation of the actuating piston caused by the blade actuation from the first end position to the second end position in the open position is, and a second flow path for the fluid opens, in which a delay element in the form of a timed shut-off valve or a throttle valve is arranged, which in the caused by the relaxation of the spring accumulator V Creation of the actuating piston from the second end position in the first end position flow-inhibiting is effective 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 operation of the wing for biasing the spring accumulator, the phase of autonomous adjustment of the wing begins by relaxation of the spring accumulator, wherein the volume change of the working space and thus also the adjustment of the delay by the delay element in the form of timed shut-off valve or in the form of flow restricting effective throttle valve Control piston is prevented for a defined period of time or is very low. As a result, the desired time delay of the adjustment of the wing can be achieved.

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 adjustment greatly lowered first adjustment phase in which can be done by temporarily remaining in the open position of the window or the door air exchange between the room interior and the outside environment, is by the second adjustment phase with rapid adjustment a reliable adjustment, 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 of the spring accumulator can also be referred to as a storage spring, which may have a linear spring characteristic, but also deviating degressive or progressive spring characteristics are 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 gas compressed in the gas spring, wherein the compression during adjustment of the wing from the initial position takes place in the biasing position, in particular using a force acting between frame and wing traction means whose movement is converted into an adjustment of a piston in the gas spring becomes. 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.

It can be used in particular gas spring-damper combinations that are well known in the art and in addition to a gas spring assembly also 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 can be achieved for the operation of heavy wings by choosing a high filling pressure, 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 covers the free end of the traction device when looping the pulley by 180 ° twice the way, according to the reversal of the principle of operation of a pulley. Due to the possible small design of the closing device with a gas spring arise in particular in connection with the use of a traction device for power transmission to the wing various applications, such as for the automatic closing of windows or doors of various kinds, such as tilt 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. By using air can be dispensed 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 allows the transfer of high forces with small paths and therefore small structural 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 temperature changes of the hydraulic oil causes the adjustment speeds and the actuating forces remain largely unaffected by the operating temperature in the temperature changes occurring in the use of the actuator.

Small structural dimensions make it possible in particular to integrate the actuating drive of the closing device inside a wing or a fixed window or door frame, whereby the closing device does not influence the overall visual impression 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 to be able to influence the speed of the spring-loaded automatic adjustment of the actuating piston, 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 the relaxation rate, 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 options for mounting the locking device on a frame or a wing, it is advantageous if the motion connection between the actuating piston and the wing comprises a traction piston fixed traction means, with the actuating piston against the action of the spring accumulator on the first end position in the second end position is adjustable. In particular, in a little rigid traction means, a deflection of the force directions is possible and are therefore directional deviations between the adjustment of the actuating piston in the actuating cylinder and the adjustment of the wing with respect. Of the fixed Frame 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 residual volume of the working space which remains as small as possible at the end of this displacement when the second end position is reached by the actuating piston forms a good prerequisite for a rapid build-up of the required underpressure.

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 spring force of the locking 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 axially displaceable or axially deformable mounted in a seal seat on the actuating cylinder and the adjustment of the actuating piston from the first end position to the second end position the traction means itself and by the operation of the traction means caused pressure differences on the opposite sides of the seals to spend 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 accumulator is adjustable in its bias, for example by mutually offset in the axial direction Einhängepunkte for a tension spring.

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 fluidly 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 unblocking of the check 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 end position 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 design of the actuating cylinder can be helpful for demolding during production in an injection molding process, since an axially tapered inner core is easier to demold.

To achieve an anti-rotation for the actuating piston in the actuating cylinder to the cylinder longitudinal axis, it is also possible to run the cylinder cross-section not circular but non-circular, in particular oval, since this means no extra effort for the production of injection molding components and still uses simple sealing rings as a piston seal 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 cylinder bottom in the cocked 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 throttle effect of the air inlet valve vacuum. But so are the conditions for a delayed over a longer period of time closing movement of the wing by the spring-loaded actuator, so at a sufficient opening width the wing over a reasonable period of time a good room ventilation can be guaranteed. However, with the high negative pressure of the piston from its stop-limited starting position effective delay the closing movement involves the risk that at the end of the closing movement of the then largely relaxed spring storage no longer provide the required locking of the wing in the closed position closing force can, especially in the sense of a strong delay of the closing movement, the power of the storage spring should remain limited. In order to meet these partly conflicting requirements, a vent valve is provided for the resulting between the cylinder bottom and the piston vacuum chamber of the cylinder, which is actuated in response to the stroke of the piston. As with the ventilation of the vacuum chamber of the prevailing negative pressure is rapidly reduced, the spring force of the spring accumulator comes fully to fruition, which leads to a corresponding acceleration of the closing movement of the wing with the effect that the inertia forces of the accelerated wing lead to its secure locking, namely even when using relatively soft memory springs, which are well suited for longer suspension travel.

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, however, arise when the storage spring is designed as a tension spring and on the side facing away from the vacuum chamber, vented side of the cylinder engages the piston, because in this case the memory spring can be accommodated protected in the cylinder with a small 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 during the tensioning of the accumulator spring via the air outlet valve. 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 construction conditions, however, arise 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 the release of the memory spring for a dosed due to the throttling air access to the vacuum chamber and thereby the adjusting movement the piston according to its spring loading correspondingly brakes. With an 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 venting valve for the vacuum chamber provided for releasing the piston after a braked adjusting movement can preferably be designed as a passage opening in the cylinder jacket, which is not mandatory, however. 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 of 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 embodiments illustrated in the drawings.

Fig. 1

ein Schließsystem für einen Fensterflügel mit einer Schließvorrichtung zum Schließen eines Fensterflügels;

Fig. 2

eine nicht erfindungsgemäße Ausführungsform der Schließvorrichtung mit einem Arbeitsraum der als Überdruckraum wirkt;

Fig. 3

eine weitere Ausführungsform der Schließvorrichtung mit einer Vorsteuerung;

Fig. 4

eine weitere Ausführungsform der Schließvorrichtung mit geschlossenen Fluidkreisläufen, insbesondere für die Verwendung von Hydrauliköl als Fluid;

Fig. 5

eine Ausführungsform der Schließvorrichtung mit einem Federspeicher in Form eines Gasfederelements und Verwendung von Hydraulikflüssigkeit als Fluid zur Erzielung der Verzögerungswirkung;

Fig. 6

eine weitere Ausführungsform der Schließvorrichtung mit einem Federspeicher in Form einer Gasfeder und Verwendung von Hydrauliköl als Fluid zur Erzielung der Verzögerungswirkung;

Fig. 7

eine ausschnittsweise Ansicht eines Zylindermantels eines Stellzylinders für ein gasförmiges Fluid;

Fig. 8

eine ausschnittsweise Ansicht eines weiteren Ausführungsbeispiels eines Stellzylinders für eines gasförmiges Fluid;

Fig. 9

einen Teilschnitt durch ein weiteres Ausführungsbeispiel einer Schließvorrichtung mit einer speziellen Form des Rückschlagventiles;

Fig. 10

ein Bauelement mit einer Schließvorrichtung zum Schließen eines Flügels und einem Verriegelungssystem für den Flügel;

Fig. 11

ein Beispiel für ein Verriegelungssystem gemäß Fig. 10 in Schnittdarstellung;

Fig. 12

eine weitere Ausführung eines Verriegelungssystems gemäß Fig. 10 in einer Explosionsdarstellung;

Fig. 13

eine weitere Ausführungsform der Schließvorrichtung in Schnittdarstellung;

Fig. 14

eine Schließvorrichtung in Explosionsdarstellung.

Fig. 15

eine Ansicht einer weiteren Ausführungsform eines Bauelements in Form eines Fensters mit Drehkippflügel mit einer Schließvorrichtung für den gekippten Flügel und einem verdeckt angeordneten Verriegelungssystem;

Fig. 16

eine Draufsicht auf das Bauelement gemäß Fig. 5 in Richtung des Pfeiles XVI in Fig. 15 mit geschlossenem Flügel;

Fig. 17

eine Draufsicht auf ein verdeckt angeordnetes Verriegelungssystem für das Bauelement;

Fig. 18

eine mögliche Anordnung zur Betätigung des Verriegelungssystems;

Each shows in a simplified schematic representation:

Fig. 1

a sash closure system having a closure device for closing a sash;

Fig. 2

a non-inventive embodiment of the closure device with a working space which acts as a pressure chamber;

Fig. 3

a further embodiment of the locking device with a pilot control;

Fig. 4

a further embodiment of the closure device with closed fluid circuits, in particular for the use of hydraulic oil as fluid;

Fig. 5

an embodiment of the closure device with a spring accumulator in the form of a gas spring element and use of hydraulic fluid as a fluid to achieve the retarding effect;

Fig. 6

a further embodiment of the closure device with a spring memory in the form of a gas spring and use of hydraulic oil as a fluid to achieve the retarding effect;

Fig. 7

a partial view of a cylinder jacket of a cylinder for a gaseous fluid;

Fig. 8

a fragmentary view of another embodiment of an actuating cylinder for a gaseous fluid;

Fig. 9

a partial section through another embodiment of a closure device with a special form of the check valve;

Fig. 10

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

Fig. 11

an example of a locking system according to Fig. 10 in sectional view;

Fig. 12

a further embodiment of a locking system according to Fig. 10 in an exploded view;

Fig. 13

a further embodiment of the closure device in sectional view;

Fig. 14

a locking device in exploded view.

Fig. 15

a view of another embodiment of a device in the form of a window with tilt-wing with a tilting device for the tilted wing and a concealed locking system;

Fig. 16

a plan view of the device according to Fig. 5 in the direction of the arrow XVI in Fig. 15 with closed wing;

Fig. 17

a plan view of a concealed locking system for the device;

Fig. 18

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 component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and are to be transferred to the new situation mutatis mutandis when a change in position. Furthermore, individual features or combinations of features from the different exemplary embodiments shown and described can also represent independent, inventive or inventive solutions.

All information on ranges of values in representational description should be understood to include any and all sub-ranges thereof, eg the indication 1 to 10 is to be understood as encompassing all partial regions, starting from the lower limit 1 and the upper limit 10, ie all partial regions starting with a lower limit of 1 or greater and ending 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 device with a locking device 101 for the time-delayed self-adjusting a wing 102 of the device, in the form of a window or door, relative to a fixed frame 103. The wing 102 is between a dashed line shown starting position 104, which corresponds to the closed position and one also 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 is moved back to the starting position 104 from the initial position 104 to the bias position 105 of the wing 102 of the locking device 101 in a time-delayed independent adjustment 107 by a manual operation shown by a dotted arrow 106 manual wing operation.

The closing device 101 comprises an adjusting cylinder 108 in which an adjusting piston 109 is adjustably mounted, which with the wing 102, as in Fig. 1 represented by a pulling means in the form of a string 110 with the wing 102 is movement connected and further operatively connected to a spring memory 111. 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 111 are arranged so that an adjustment of the actuating piston 109 from the first end position 112 in the second end position 113 increases the voltage in the spring 111, this is biased by the movement and in return by an adjustment of the actuating piston 109 the second end position 113 is relaxed 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 is a direct relationship between the first end position 112 of the actuating piston 109 and the initial 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.

Because in Fig. 1 the spring accumulator 111 is designed approximately as a tension spring 115, the spring force acts in the drawing to the right; the pressure exerted by the working chamber 117 on the actuating piston surface 119 pressure force must therefore act to the left 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 according to 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 contained in the working space 117 in the form of air 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 actuating piston 109 in the in Fig. 1 Starting from this position would be spent by the tensioned spring 111 of the actuator piston 109 again directly into the right first end position 112 and thereby also the wing 102 are moved to the closed position 104 home. 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 actuating piston 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 in 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 pressure acting on the right side of the piston ambient pressure a resulting Compressive force 121 to the left causes, with increasing piston stroke rises until it is in equilibrium of forces with the right-acting spring force 111 exerted by the spring accumulator 111 and decreasing with increasing piston travel. 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 comprises either a timed shut-off valve 128 or a throttle valve 129 for this purpose. Timed shut-off valve 128 releases second flow path 126 after a predefined period of time and is connected to an arbitrary timer element.

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

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 in the embodiment according to Fig. 1 formed by a simple pressure equalization port 131 in the cylinder jacket of the actuating cylinder 108, wherein the position along the cylinder longitudinal axis is the time of switching from the lower closing speed determined by the delay element 127 to the only caused 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 Ausgleichsfließwegs 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 locking device 101 according to Fig. 1 the check valve 125 corresponds to an air outlet valve, the throttle valve 129 an air inlet valve and the pressure equalization port 131 a vent valve.

Fig. 2 shows a further, non-inventive embodiment of a locking device 101 with an actuator 123, comprising an actuating cylinder 108 with an adjustable between a first end position 112 and a second end position 113 actuating piston 109. The adjustment of the actuating piston 109 from the first end position 112 in 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 in accordance with the embodiment Fig. 2 formed by a compression spring 132, the spring force 120 acts in this case to the right and the working space 117 is arranged to the right of the actuating piston 109. In order for the delayed adjustment of the actuating piston 109 from the second end position 113 into the first end position 112 on the actuating piston 109, a resulting pressure force 121 can act, which acts against the spring force 120, 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 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 adjustment 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 embodiment of a closing device 101 is shown schematically, in which between the actuating piston 109 and the second end position 113 - Fig. 3 indicated left dashed - located work space 117 again acts as a vacuum chamber and the fluid is again formed by air. The adjustment of the actuating piston 109 corresponding to the blade actuation 106 from the right, first end position 112 into the left, second end position 113 is again effected by a traction means in the form of a cord 110, and air contained in the working space 117 through the first piston during this piston movement Flow path 124 discharged. The first flow path 124 has in its course again a check valve 125 which allows this air discharge largely unhindered.

However, the displaced air is not discharged directly to the ambient air in this embodiment, but in a pilot control 136, comprising a pilot cylinder 137 and a displaceably mounted therein pilot piston 138, passed. In this pilot cylinder 137, a pilot chamber 139 is delimited by the spring-mounted pilot piston 138, in which an overpressure cushion is formed by the air flowing over from the working space 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 caused by the negative pressure in the working space 117 after a short relaxation movement to the right - an entry of air is through the immediate 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 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 according to Fig. 3 further shows a slightly conical design of the adjusting cylinder 108, in the region of the first end position 112, ie in Figure 3 has a larger inner cylinder diameter on the right than in the region of the second end position 113 in FIG 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 illustrated Embodiment formed by two O-rings of an elastomer. The use of such a piston seal is of course also possible in other embodiments.

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.

In Fig. 4 a further and independent embodiment of the closure device 101 is shown, wherein the same reference numerals or component designations are used as in the preceding Fig. Again for the same parts. To avoid unnecessary repetition, reference is made to the detailed description in the preceding figures. At this point, therefore, it is only mentioned that in this embodiment, the flow paths 124, 126 and the Ausgleichsfließweg 130 are guided in closed circuits, which is why this embodiment is particularly suitable for a fluid in the form of an incompressible liquid, preferably hydraulic oil.

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

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

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 compensation element 144, for example of a closed-cell, foamed elastomer is arranged, which by volume reduction, the displacement of hydraulic fluid by a connected to the actuating piston 109 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 again with the same parts the same reference numerals or component names are used as in the previous figure. 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 lead into the piston rod side working chamber 148 through which a corresponding amount of hydraulic oil can be displaced.

In the dashed left illustrated second end position 113 of the actuating piston 109 of the Ausgleichsfließweg 130, which is formed by a cylinder in the longitudinal direction through hole in the actuator piston 109 is largely sealed by a separating piston 146 arranged coaxially to the through hole stopper 149, which shortly before reaching this position Hydraulic oil drain from the working space 117 can only be done via the check valve 125, which does not affect the wing operation, however, noticeably.

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 that hydraulic oil is displaced from the right second working chamber 148 into the left first working chamber 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 into the transverse bore. As a result of the volume flow restricted by the throttle valve 129, the actuating piston moves only very slowly in the first movement phase and is thereby 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 is withdrawn again from the through bore in the actuating piston 109, the hydraulic oil can again via the Ausgleichsfließweg 130 in the form of the through hole from the right second working chamber 148th flow into the left first working space 117, whereby in the second phase of the independent adjustment 107, this takes place again at the desired higher speed.

By the illustrated guidance of the traction means or the cord 110 of a relative to the actuating cylinder 108 fixed pivot point 153 via a connected to the piston rod 147 pulley 154, the adjustment of the actuating piston 109 is translated into a twice as large adjustment of the wing 102, making this type of short Lengths of the actuator 123 allows.

Notwithstanding the execution according to Fig. 5 are also simpler variants of commercially available gas spring elements for the locking device 101 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.

In Fig. 6 a similar embodiment of the closure device 101 is shown with a gas spring element in which the serving as a spring 111 gas 145 is enclosed in an actual actuating cylinder 108 outside enclosing outer cylinder 155 and again separated by a sliding separating piston 146 from the hydraulic oil, which is in the second working space 148, which is formed by the outer cylinder 155, the separating piston 146 and the actuating cylinder 108 frontally final cylinder head 156 is located. 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.

Fig. 7 shows a fragmentary view of the actuating cylinder 108 having a plurality of closely spaced along a circumferential line pressure equalization openings 131. These pressure equalization openings 131 form the Ausgleichsfließweg 130 and can be covered by a sliding cover 157 with a preferably wedge-shaped recess 158 as needed in various numbers or 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 Ausgleichsfließwegs 130 takes place again by covering or exposing the pressure equalization openings 131 by means of the cover 157th

In the embodiments according to FIGS. 7 and 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 an oblong hole, which can be more or less covered by the covering element, is formed.

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 to the faster, determined by Ausgleichsfließweg 130 adjustment speed, such as by individual cover exactly the pressure compensation opening, the Switching the speed effect 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. In this case, the check valve 125 comprises a traction means 159 with circular cross-section and smooth surface acting on the actuating piston 109 and a sealing arrangement 160 mounted on the actuating cylinder 108. The sealing arrangement comprises in a simple embodiment at least one O-ring 161 whose inner diameter is slightly smaller , 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 frontal implementation of the traction device 159 from the working space 117 of the adjusting cylinder 108, a sealing seat 162 is formed in the form of an approximately cylindrical bore in which the seal assembly 160, here in the form of the O-ring 161, axially movable or deformable by a short distance and having 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 position of the case, since here of the outer recesses 163 on the left end face 164 still radial channels 165 lead to the feedthrough bore 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 can therefore not be effective, and a fluid passage from the working space 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 is in Fig. 9 nor the in the left position of the seal assembly 160 possible flow path for the fluid represented by an arrow 167.

Fig. 10 10 shows a locking system 168 for the time-delayed self-closing and locking of 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 locking system 169 acting unidirectionally blocking between the fixed frame 103 and the adjustable wing 102. In the exemplary embodiment shown, 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 actuator 172 in the form of a pull cord 173 to the locking device 101, which is attached to the upper right corner of the sash, is guided by this and deflected in the region of the window frame down. The pull cord 173 depends thereby not just in the middle of the window but laterally downwards and causes in a pulling operation that on the one hand the locking device 171 is actuated and on the other hand the required to open the window sash 102 tensile force in the region of the locking device 101 is introduced into the window sash where also the force for biasing the spring accumulator between locking device 101 and window frame 103 is transmitted.

A section through one embodiment of the locking system 169 is shown in FIG Fig. 11 shown. 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 projecting above it, by the locking element 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, since the extraction of the locking element 170th is prevented from the insertion opening 175 by the locking member 176.

The locking member is here formed by an Exzenterklemmelement 177 in the form of a Exzenterklemmrolle 178, which cooperates with the locking member 170 such that it is clamped between the Exzenterklemmrolle 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. By frictional forces between the locking surface 174 on the locking member 170 and the Exzenterklemmrolle 178 this is pivoted to the left on pulling the locking member 170 to the left about the eccentric pivot axis 180, whereby the between Exzenterklemmrolle 178 and support member 179 extending nip in the insertion opening 175 is narrower and the Locking occurs due to the self-locking strong rising clamping forces.

Upon movement of the locking element 170 in the insertion opening to the right, the clamping is canceled by reversing the effect described above.

The Exzenterklemmelement 177 is biased by a biasing spring 182 so that act in the nip upon movement of the locking member 170 to the left required for the occurrence of self-locking contact forces between the locking surface 174 and Exzenterklemmelement 177. 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 downward, which is fixed to the right of the roller axis 181, ie approximately with respect to the pivot axis 180 relative to the roller axis 181 on the eccentric clamping roller 178. The nip is thereby increased and released the lock.

Fig. 12 shows an exploded view of another embodiment of the locking system 169 with a locking member 170 and a unidirectional locking locking device 171. The locking member 170 has for this purpose a locking surface 174, which is provided with a locking toothing 183. The cooperating with the locking element 170 in the locking device 171 locking member 176 has a cooperating locking teeth 184 on. As in the example below Fig. 11 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.

In Fig. 13 is a further embodiment of a closing device for the time-delayed self-closing a wing of a window or a door in a schematic axial section shown.

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 memory spring 4 is formed 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 setting of the bias of the tension spring 5 more attachment points. 8 having. 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 embodiment in the form of a needle valve, the screw-adjustable 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 throttling action 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 negative pressure is moved to the closed position. This unrestrained piston movement causes an acceleration of the shooting movement of the wing after, wherein the associated inertia forces ensure a safe closing and locking of the wing in the closed position.

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

In the FIGS. 15 and 16 For example, a structural element 201 in the form of a window 202 is shown, which comprises a fixed frame or window 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 Drehkippflügel 205 can be opened from a closed, resting on the frame 203 starting position either about the vertical axis of rotation 208 in the region of a side edge of the wing 204 or about the horizontal pivot axis 209th can preferably be pivoted or tilted in the interior of the room in the region of a lower edge of the wing 204. 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 the form of fittings shears.

In the common fitting arrangements 206, the setting of the fitting functions is carried out by pivoting the actuating handle 210, starting from a generally downward pointing in solid lines shown basic position 211 in a dashed lines shown 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 upwardly oriented shown in dotted lines tilting position 213 about the Drehkippflügel 205 about the horizontal pivot axis 209 can tilt. 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 actuating 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 closed position. Here are in Fig. 16 with arrows 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 indicated.

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 is at this point a monofilament polyamide cord with a diameter of about 1.20 mm and a carrying capacity of about 750 N called which 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 fixed to the upper horizontal frame part of the frame 203 and a locking device 241 attached to the upper horizontal frame 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 or slowed closing of the tilted wing 204 is automatically effective. The spent in a closed position by the closure device 217 wing 204 with the operating handle 210 in tilt position 213 can not be easily pressed from the outside of the device 201, whereby an unauthorized intrusion by the device 201 from the outside is made difficult by the opening process a higher Noise generated 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 the locking device 217 and locking system 239 are to be designated as independent of each other; a dependency can only be seen in that the closing of the tilting turntable 205 caused 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 further independent of the fitting assembly 206, which in most cases has a locking function coupled to the operating 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 unintentional opening of the wing 204 by unattended infants with the consequent danger of falling, since a toddler is often capable of doing so However, to disable a locking fitting 237 by bringing the operating handle 210 in the open position 212, the probability of simultaneous unlocking of the locking system 239 is significantly lower. In the FIGS. 15 and 16 is the actuating handle 210 at the same time as a locking fitting 237, wherein its components such as tie rods, push rods or rods extending 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 when 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 which occurring about the horizontal pivot axis 209 tilting 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 over the actuating handle 210, which is usually about halfway up 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 causes independent of the locking device 217 and not operatively connected to this locking function after the closing of the wing 204. 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 according to Fig. 10 is that the locking system 239 with the wing closed 204 between the fold of the wing 204 and the fold of the frame 203 is arranged. 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 includes for manual deactivation 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 an operating area which is easily accessible, leads or hangs down for the user.

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.

Fig. 17 shows an advantageous embodiment of the locking system 239, which is arranged between a fold 244 of the sash and a fold 245 of the frame 203 hidden in the component 201. The locking system 239 comprises, as already described with reference to FIGS. 15 and 16 described in the fold 245 of the frame 203 fastened locking element 240 and attached in the fold 244 of the sash locking device 241, the approaching the wing 204 or Drehkippflügels 205 in the closed position unidirectional independent locking of the wing 204 in the closed state relative to the frame 203 causes. The basic shape 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 achieved becomes. 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. Fig. 17 shows the locking system 239 in the locked position so with the locking members 248 into engagement with the locking surfaces 249. The locking members 248 are designed in the form of locking bolts 250 which have in their rear so remote from the locking element 240 end portion a collar 251, with which they as well with the locking member 240 facing shaft portion are mounted adjustably in a base housing 252 of the locking device 241. In this case, in extension of the locking bolt 250 spring elements 253, here in the form of cylindrical compression springs 254, which are each supported with one end on the collar 251 of a locking pin 250 and the other end on the base housing 252 of the locking device 241. The basic bias of the spring elements 253 causes the locking members 248 and the locking pin 250 in the locked position, ie in engagement with the locking recesses 247 and the locking surfaces 249, are pressed. 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 the 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. The eccentric pins 257 are thereby on the collar 251 against the spring elements 253 in the form of the compression springs 254 at. 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 in Fig. 17 designated 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 or hung with a fitting part. The attachment of the locking element 240 in fold 245 of the frame 203 also takes place with screws 259, wherein the locking member 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 approximately perpendicular to an adjustment of the locking element 240 allow for the window area, whereby tolerances in the folding distance between the window rebate 244 and 245 Rahmenfalz 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 mounted state, in particular jagged projections may be provided on the mounting surface, which penetrate slightly into the material of the frame 203 and the non-positive connection between the locking element 240 and frame 203 by the screws 259 by an additional form-fitting effect support. 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 element 240 in the fold 245 of the frame 203, the following mounting method is provided. First, the locking element 240 is in the locked position brought to the locking device 241; Subsequently, the locking system 239 is positioned in the rebate 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, at the front edge of the locking element 240, a marking plate 261 may be arranged, which, as in Fig. 15 indicated, protrudes upward relative to the locking element 240 and projects slightly above the upper edge 262 in the closed state of the wing 204. This position can be easily held on the frame 203 and accordingly easily mounting holes for the positionally correct screwing of the locking element 240 in the fold 245 of the frame 203 can be introduced. Alternatively, it would also be possible to provide a marking mandrel 263 on the rear side of the locking element 240, which leaves a small, non-irritating mark in the fold 245 of the frame 203 when the wing 204 is assembled with the locking system 239 approaching the frame 203 and thus likewise 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 Vernegelungselements 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 process, these are as in FIGS. 17 and 18 shown connected in a special way with the actuator 235 in the form of the tension element 236. The tension member 236 is as in Fig. 18 represented by both 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. Now, if a pulling movement is performed with the free end of the tension member 236, the tensioned tension member 236 can only follow this movement by shortening its length between a force application point 265 at the free end and the fix point 264, this shortening causing rotational movement of the unlocking members 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 existing in the unlocking 256 bays as far as possible, whereby a resulting rotational movement of the unlocking 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 according to Fig. 18 via the tension member 236 and a plurality of locking systems 239 parallel or successively serially coupled and unlocked via a train on the tension member 236, which provides even greater security against violent opening of the wing 204 with still simple and 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.

Fig. 14 further shows a front end of the closing device 1, 101, 217 disposed deflecting element 222, here in the form of a guide roller 223, with the traction means 10, 110, 159, 219 starting from the axial direction of the adjusting cylinder 108 in any direction, in particular approximately at right angles, in Direction can be deflected to the fixed frame or the wing. In particular, the deflecting element 222, for example, the bearing block 223 bearing the bearing roller with respect to the axial direction of the actuating cylinder 108 may be rotatable, whereby the locking device 1, 101, 217 can be adapted to different mounting situations with little effort.

Fig. 15 shows further for ease of gripping the tension member 236, which can be used for the unlocking of the locking system 239 and the tilting of the Drehkippflügels 5, attached to the free end of a pull knob 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 embodiments show possible embodiments of the closing device 101, 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 embodiments are mutually possible and this possibility of variation due to the teaching of technical action by objective invention in the skill of those working in this technical field. ,

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 the Fig. 1; 2 ; 3; 4 ; 5; 6 ; 7; 8th ; 9 ; 10 ; 11 ; 12 ; 13 ; 14 ; 15, 16 . 17 and 18 shown embodiments form the subject 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. <B> Reference Numbers </ b> 1 actuator 2 actuating cylinder 3 piston 4 storage spring 41 5 mainspring 42 43 6 cover 44 7 anchor bolts 45 8th anchorage point 9 cylinder base 46 10 traction means 47 48 11 air release 49 12 Air inlet valve 50 13 needle 14 Pressurized space 51 15 Through opening 52 53 16 vent valve 54 17 pusher 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 123rd actuator 82 124th First flow path 83 125th check valve 84 126th Second flow path 85 127th delay element 128th Timed shut-off valve 86 129th throttle valve 87 130th Ausgleichsfließweg 88 89 131st Pressure equalization port 90 132nd compression spring 133rd Cylinder front side 91 134th vent 92 135th bypass line 93 94 136th feedforward 95 137th pilot cylinder 96 138th pilot piston 97 139th pilot chamber 98 140th pilot choke 99 100 141st Pilot check valve 142nd piston seal 101 contraption 143rd compensation space 102 wing 144th compensation element 103 frame 145th gas spring 104 starting position 105 biasing position 146th separating piston 147th piston rod 106 thumb actuation 148th working space 107 Self-adjustment 149th stopping plug 108 actuating cylinder 150th Piston Ring 109 actuating piston 110 Cord / traction means 151st valve needle 152nd cross hole 111th spring 153rd articulation 112th First end position 154th idler pulley 113th Second end position 155th outer cylinder 114th Mechanical spring 115th mainspring 156th cylinder head 157th cover 116th Cylinder inner wall 158th recess 117th working space 159th traction means 118th Cylinder front side 160th sealing arrangement 119th Adjusting piston area 120th spring force 161st O-ring 162nd seal seat 121st thrust 163rd recess 122nd fluid 164th face 165th radial channel 206th fitting assembly 166th execution 207th hinge 167th arrow 208th Vertical axis of rotation 168th locking system 209th Horizontal axis of rotation 169th locking system 210th operating handle 170th locking element 211th initial position 171st locking device 212th open position 172nd actuator 213th tilt 173rd drawstring 214th Opening and closing movement 174th locking surface 215th tilt 175th insertion 216th closing movement 176th locking member 217th closing device 177th Exzenterklemmelement 218th spring 178th Exzenterklemmrolle 219th traction means 179th support organ 220th rope 180th swivel axis 221st frame element 181st roller axis 222nd deflecting 182nd biasing spring 223rd idler pulley 183rd locking teeth 224th 184th locking teeth 225th 185th Slide 226th 186th leading edge 227th 187th 228th 188th 229th 189th 230th 190th 231st 191st 232nd 192nd 233rd 193rd 234th 194th 235th actuator 195th 236th tension element 196th 237th Fastener 197th The 238th distance 198th 239th locking system 199th 240th locking element 200th 241st locking device Two hundred and first module 242nd execution 202nd window 243rd Wing front 203rd frame 244th fold 204th wing 245th fold 205th tilt-turn 246th face 247th locking recess 248th locking member 249th locking surface 250th locking bolt 251st Federation 252nd Headers 253rd spring element 254th compression spring 255th bevel 256th unlocking 257th eccentric 258th adjustment 259th screw 260th Long hole 261st Marker plates 262nd top edge 263rd mark Dorn 264th fixed point 265th Force application point 266th Through channel 267, respectively. bottom 268th operation bore 269th pull knob 270th shell

Claims (13)

1. A component (201), in particular a window or door with a pivoted leaf and top-hung window or pivoted window, comprising a frame (103, 203) and a leaf (102, 204) which may be pivoted about a substantially horizontal pivot axis (209) relative to the frame (103, 203), a closing device (1, 101, 217) with a spring-load device (4, 111, 218) for the delayed or retarded automatic 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), wherein the locking system (169, 239), on closing of the leaf (102, 204) has an automatically self-locking design and comprises a locking element (170, 240), fixed to the frame (103, 203), having a locking surface (174, 249), and a locking device (171, 241), fixed to the leaf (102, 204), with a locking member (176, 248) cooperating with the locking surface (174, 249), the locking member (176, 248) is pre-stressed by means of a spring element (182, 253) in the locking direction, i.e. in engagement with the locking surface (174, 249), and is displaceable by means of an actuating member (172, 235) into a release position situated out of engagement with the locking surface (174, 249), and the actuating member (172, 235) is formed by a tension element (173, 236) and furthermore the displacement path for the locking member (176, 248) is delimited by a stop element or the displacement path for the actuating member (172, 235) in the direction of the release position is delimited by a fixed point (264) on the locking system (169, 239) or on the leaf (102, 204), characterized in that through the actuating member (172, 235) in the form of the tension element (173, 236), a handle is formed for tilting the leaf (102, 204) about the horizontal pivot axis (209) contrary to the tractive force of the spring-load device (4, 111, 218) of the closing device (101, 217).
2. The component (201) according to Claim 1, characterized in that the locking system (239), with closed leaf (204), is arranged between the rebate (244) of the leaf (204) and the rebate (245) of the frame (203), whereby the locking element (240) and the locking device (241) are not visible in frontal view of the component (201).
3. The component (201) according to Claim 1 or 2, characterized in that the tension element (236) is guided by the locking system (239) through a feed-through (242) in the leaf (204) to the front side (243) of the leaf.
4. The component (201) according to one of Claims 1 to 3, characterized in that the closing device (101) for the delayed or retarded automatic closing of the leaf (102) of a window or of a door from an opened pre-stressed position (105) into a closed initial position (104) has an actuator (1, 123), engaging on the leaf (102), able to be acted upon by a spring-load device (4, 111), and means for the delayed or retarded relaxing of the spring-load device (4, 111), which is able to be tensioned on a leaf actuation (106) from the initial position (104) into the pre-stressed position (105) in the opposite direction to the automatic displacement (107), wherein the actuator (1, 123) comprises an actuating cylinder (2, 108) with a setting piston (3, 109), displaceable therein between a first end position (112) corresponding to the initial position (104) and a second end position (113) corresponding to the pre-stressed position (105), connected with the leaf (102) with regard to movement and operatively connected with the spring-load device (4, 111), which setting piston together with the cylinder inner surface (116) defines at least one changeable working chamber (117) receiving a fluid, and into the working chamber (117) a first flow path (124) for the fluid opens, in which a non-return valve (11,125) is arranged, which on the displacement of the setting piston (3, 109), brought about by the leaf actuation (106), from the first end position (112) into the second end position (113), is in open position, and a second flow path (126) for the fluid opens, in which a delay element (127) in the form of a time-controlled shut-off valve (128) or in the form of a throttle valve (12, 129) is arranged, which is active in a shutting-off or flow-inhibiting manner for the automatic displacement (107) of the setting piston (3, 109) from the second end position (113) into the first end position (112) in the second flow path (126) caused by the relaxing of the spring-load device (4, 111), and that on the displacement of the setting piston (3, 109) from the second end position (113) into the first end position (112) at least one equalizing flow path (130), opening into the working chamber (117), becomes active, wherein the working chamber (117) in the second end position (113) of the setting piston (109) has a smaller, preferably very small, volume, than in the first end position (112) of the setting piston (109) and thereby acts as a vacuum chamber, and that the connection with regard to movement between setting piston (109) and leaf comprises a tension means (110, 159) fastened to the setting piston (109), by which the setting piston (109) is able to be displaced, contrary to the action of the spring-load device (111), from the first end position (112) into the second end position (113), and the tension means (110, 159) penetrates the working chamber (117) axially and, sealed by a seal arrangement (160), is guided out from the setting cylinder (108).
5. The component (201) according to one of Claims 1 to 4, characterized in that the spring-load device (111) is formed by a mechanical spring (4, 114), in particular a tension spring (115).
6. The component (201) according to one of Claims 1 to 4, characterized in that the spring-load device (111) is formed by a gas spring (145) or a gas spring element with changeable gas volume.
7. The component (201) according to one of Claims 4 to 6, characterized in that the fluid is formed by a gas, in particular air.
8. The component (201) according to one of Claims 4 to 7, characterized in that the throttle valve (129) has an adjustable through-flow cross-section.
9. The component (201) according to one of Claims 4 to 8, characterized in that the equalizing flow path (130) has an adjustable through-flow cross-section.
10. The component (201) according to one of Claims 4 to 9, characterized in that the tension means (110, 159) is guided at an end of the setting cylinder (108) over a deflection element (222), by which it is able to be deflected, starting from the axial direction, into a direction deviating therefrom, in particular at right angles thereto.
11. The component (201) according to one of Claims 4 to 10, characterized in that the non-return valve (125) is formed by the tension means (110, 159) with circular cross-section and smooth surface and with a seal arrangement (160) co-operating therewith, mounted on the setting cylinder (108) on the front face, wherein the seal arrangement (160) comprises at least one elastic sealing ring, in particular an O-ring (161), an X-ring or equivalent, and the seal arrangement (160) is mounted in a seal seat (162) on the setting cylinder (108) so as to be axially displaceable or axially deformable, and on the displacement of the setting piston (109) from the first end position (112) into the second end position (113) the tension means (159), and pressure differences brought about by the actuation of the tension means (159), bring the seal arrangement (160) into an axial position or bring about an axial deformation, in which recesses (163) in the seal seat (162) are active, which form the low-resistance first flow path (124).
12. The component (201) according to one of Claims 4 to 11, characterized in that the spring-load device (111) is adjustable in its pre-stressing.
13. The component (201) according to one of Claims 4 to 12, characterized in that the equalizing flow path (130) comprises at least one pressure equalization opening (131), arranged on the cylinder jacket of the setting cylinder (108), which in particular is changeable in its passage cross-section by a covering element (157).

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