Weight Compensation For Vertically Movable Façade Components

Abstract

The present invention is concerned with vertically sliding facade components. In order to improve operability and user comfort for vertically displaceable facade components, a weight compensation device (10) for vertically displaceable facade components comprises a spring element (12) for at least partial compensation of its own weight of a vertically displaceable facade component and a compensator (14). The spring element provides a spring force as a driving force (F.sub.AN) for lifting the vertically displaceable facade component. The spring element is movable between a compressed state (P.sub.K) and an expanded state (P.sub.E). The spring force has a decreasing value when moving from the compressed state to the expanded state. The compensator at least partially compensates for the decrease in the input force and provides an output force (F.sub.AB) that decreases less than the input force.

Claims

1. A weight compensation device (10) for vertically displaceable facade components, comprising: a spring element (12) for an at least partial compensation of its own weight of a vertically displaceable facade component; a compensator (14); wherein the spring element provides a spring force as a driving force (F.sub.AN) for lifting the vertically displaceable facade component, and wherein the spring element is movable between a compressed state (P.sub.K) and an expanded state (P.sub.E); wherein the spring force has a decreasing value when moving from the compressed state to the expanded state; and wherein the compensator at least partially compensates for the decrease in the driving force and provides an output force (F.sub.AB) that decreases less than the driving force.

2. Weight compensation device according to claim 1, wherein the compensator has a force input (16) and a force output (18); wherein a gear mechanism (20) is provided between the force input and the force output, the gear ratio of which changes and becomes smaller or larger when moving from the compressed state to the expanded state.

3. Weight compensation device according to claim 2, wherein the transmission comprises a cable reel (30) on which a cable is windable that is connectable to the vertically displaceable facade component; wherein the cable reel is rotatably driven by the spring element; and wherein the cable reel has a decreasing winding circumference for a winding cable.

4. Weight compensation device according to claim 3, wherein the spring element displaces the cable reel during the winding process in pulling direction of the cable winding on the reel, so that the vertically displaceable facade component is movable by a stroke composed of two movements, wherein in one movement the cable is windable on the cable reel and wherein in another movement the cable reel is displaceable, and wherein both movements are simultaneously executable.

5. Weight compensation device according to claim 3 or 4, wherein the transmission comprises a shaft (34) which is rotatably drivable by the spring element on a drive side and which comprises the cable reel on a driven side.

6. Weight compensation device according to claim 5, wherein the shaft has a gear wheel (36) on the drive side that meshes with a fixed toothed rack profile (38), and wherein the spring element moves the shaft with the gear wheel attached linearly transverse to the shaft axis and thereby rotationally drives the shaft; wherein the cable is attached to the cable reel and is windable and un-windable by rotation of the cable reel; and wherein the cable is windable onto the cable reel by moving the spring member from the compressed state to the expanded state.

7. Weight compensation device according to claim 6, wherein the gear wheel is replaceable and different sized gear wheels are provided with which the lifting force and lifting height of the compensation device can be varied.

8. Weight compensation device according to one of claims 3 to 7, wherein the cable reel comprises a cone-shaped winding body (44) in which a spirally extending winding groove (46) is provided for receiving the cable.

9. Weight compensation device according to one of the preceding claims, wherein the spring element is a linear spring element; and/or wherein the spring element is formed as a pneumatic spring (24); wherein the pneumatic spring is formed as a gas compression spring or a gas tension spring.

10. Weight compensation device according to claim 9, wherein the pneumatic spring (24) includes a valve (58) inserted transversely of the spring direction and accessible when installed; and wherein the pneumatic spring is fillable and drainable via the valve so that the spring force is variable when installed.

11. Weight compensation device according to claim 9 or 10, wherein the pneumatic spring, when installed, is adjustable for a sash weight in a range between 10 and 400 kg.

12. Weight compensation device according to one of claims 9 to 11, wherein the pneumatic spring comprises a cylinder (24) and a piston (26), the cylinder being supportable at one end (28) at a support point in a facade; wherein the piston is connected at its end to the shaft; wherein with an extension of the piston, the shaft rotatably supported at the end of the piston is drivable via gear wheel and toothed rack profile; and wherein with the cable reel attached to the shaft with the decreasing winding circumference, a torque for winding up the cable can be reduced due to the decreasing lever distance of the shaft axis to the cable and thus a weakening of the force of the pneumatic spring can be at least partially cancelled.

13. Weight compensation device according to one of claims 3 to 12, wherein a vertical retaining profile (60) is provided, to the upper end of which an upper end of the spring element is attached, and wherein, at the lower end of the spring element, the cable reel is rotatably retained; wherein the retaining profile comprises, in a lower segment (62), a vertical guide (64) for the other end of the spring element, and a vertically extending toothed profile wherein the cable reel is connected to a toothed wheel which meshes in the toothed profile and rotates the winding reel.

14. Weight compensation device according to one of the preceding claims, wherein the vertically slidable facade component is a vertical sliding window having at least one movable sash.

15. Weight compensation device according to one of the preceding claims, wherein the spring element forms a first force element and the driving force forms a first force; and wherein the compensator comprises a second force element providing a second force which compensates for the decreasing spring force of the first actuator when moving from the compressed state to the expanded state, such that a resulting force as the output force is provided which decreases less than the first force for compensating the weight of the vertically displaceable facade component; wherein, preferably, the second force element provides as the second force: i) an increasing compensation force acting in the direction of the first force; or ii) a decreasing compensation force acting against the first force; and wherein the compensation force compensates for the decreasing spring force of the first force element when moving the first force element from the compressed state to the expanded state.

16. A weight compensation device (10) for vertically displaceable facade components, comprising: a spring element (12) for at least partially compensating its own weight of a vertically displaceable facade component; a compensator (14); wherein the spring element provides a spring force as a driving force (F.sub.AN) for lifting the vertically displaceable facade component, and wherein the spring element is movable between a compressed state (P.sub.K) and an expanded state (P.sub.E); wherein the spring force has a decreasing value when moving from the compressed state to the expanded state; wherein the compensator at least partially compensates for the decrease in the driving force and provides an output force (F.sub.AB) that decreases less than the driving force; wherein the compensator comprises a gear mechanism (20) between a force input (16) and a force output (18), the gear ratio of which changes as the compensator moves from the compressed state to the expanded state; wherein the transmission comprises a cable reel (30) mounted on a shaft (34), on which a cable connectable to the vertically displaceable facade component can be wound; wherein the cable reel has a decreasing winding circumference for a winding cable; wherein the shaft comprises a gear wheel (36) meshing with a fixed toothed rack profile (38); wherein the shaft is movable by the spring member in the direction of the toothed rack profile to thereby rotate the cable reel for winding and un-winding the cable.

17. An adjustable weight compensation kit (80) for vertically displaceable facade components, the weight compensation kit comprising: at least one weight compensation device according to one of claims 1 to 16; wherein the spring element is adjustable in its spring effect in installed state; and/or wherein the compensator comprises a transmission device for force transmission, wherein a gear transmission ratio of the transmission device is adjustable.

18. Adjustable weight compensation kit according to claim 17, wherein the spring element is a pneumatic spring which has a valve inserted transversely to the spring direction, which valve is accessible in the installed state and can be filled and emptied via the valve, so that the spring force can be changed in the installed state; and/or wherein the transmission comprises a shaft (34) that is rotatably drivable on a drive side by the spring element via a gear wheel (36) meshing in a fixed toothed rack profile (38) in order to rotate a cable reel mounted on the shaft, on which a cable is held that is windable and un-windable by the rotation of the cable reel; wherein the gear wheel is exchangeable and at least two differently sized gear wheels (82) are provided with which the gear transmission ratio for the rotational drive of the cable reel is variable.

19. A facade module (100) comprising: a vertically displaceable facade component (102); and at least one weight compensation device (10) according to one of claims 1 to 16 or a weight compensation kit according to one of claim 17 or 18; wherein the at least one weight compensation device or weight compensation kit is connected to the vertically displaceable facade component and compensates the weight at least in part; and wherein the at least one vertically displaceable facade component is formed as a vertically slideable window element.

20. A method (200) for moving a vertically displaceable facade component, comprising the steps of: applying (202) a holding force to a vertically movable facade component to at least partially compensate for the own weight of the vertically movable facade component through a spring element; wherein the spring element provides a spring force as a driving force to lift the vertically movable facade component, and wherein the spring element is moved between a compressed state and an expanded state; wherein the spring force has a decreasing value when moving from the compressed state to the expanded state; and providing (204) a compensator that at least partially compensates for a decreasing input force and provides an output force that decreases less than the input force.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0115] In the following, examples of embodiments of the invention are described in more detail with reference to the accompanying drawings.

[0116] FIG. 1 shows an example of a weight compensation device in a schematic functional diagram.

[0117] FIG. 2A shows the example from FIG. 1 with a spring element in a compressed state.

[0118] FIG. 2B shows the example from FIG. 1 or FIG. 2A with the spring element in an expanded state.

[0119] FIG. 3 shows an example of a method for moving a vertically movable facade component.

[0120] FIG. 4A shows another example of a compensation device in a schematic diagram with the spring element in the compressed state.

[0121] FIG. 4B shows the example from FIG. 4A with the spring element in the expanded state.

[0122] FIG. 5A shows an example of the compensation device with a vertical retaining profile in a first side view.

[0123] FIG. 5B shows the example of FIG. 5A in a second side view.

[0124] FIG. 6 shows an upper end of the compensation device of FIGS. 5A and 5B with a pneumatic spring held in place.

[0125] FIG. 7 shows an upper end of the pneumatic spring from FIG. 6 with a valve inserted at the side.

[0126] FIG. 8A, FIG. 8B and FIG. 8C show a lower end of the compensation device with the vertical retaining profile of FIG. 6 and a vertically extending tooth profile in different views.

DETAILED DESCRIPTION OF EMBODIMENTS

[0127] FIG. 1 shows an example of a weight compensation device 10 for vertically displaceable facade components in a schematic functional diagram. The weight compensation device 10 has a spring element 12 for at least partially compensating a weight of a vertically displaceable facade component. The weight compensation device 10 also comprises a compensator 14. The spring element 12 provides a spring force as a driving force F.sub.AN for lifting the vertically displaceable facade component. The spring element 12 is movable between a compressed state P.sub.K and an expanded state P.sub.E. The spring force has a decreasing value when moving from the compressed state P.sub.K to the expanded state P.sub.E. The compensator 14 at least partially compensates for the decrease in the input force and provides an output force F.sub.AB that decreases less than the input force F.sub.AN.

[0128] In an option, the compensator 14 is provided with a force input 16 and a force output 18. A gear mechanism 20 is provided between the force input 16 and the force output 18, the gear transmission ratio of which becomes smaller when moving from the compressed state to the expanded state, and vice versa.

[0129] In FIG. 2A, the compensation device 10 of FIG. 1 is shown with the spring element 12 in the compressed state P.sub.K. In FIG. 2B, the weight compensation device 10 from FIG. 1 is shown with the spring element 12 in the expanded state P.sub.E. Purely symbolically, it is indicated that the driving force F.sub.AN is greater in the compressed state P.sub.K than in the expanded state P.sub.E. The compensator 14 is indicated with a frame of different size to indicate that the compensator 14 has a different compensating effect on the driving force F.sub.AN in the compressed state P.sub.K and the expanded state P.sub.E in such a way that the output force F.sub.AB differs to a lesser extent, and in particular decreases to a lesser extent, than the driving force F.sub.AN. Preferably, the output force F.sub.AB is constant.

[0130] FIG. 3 shows an example of a method 200 for moving a vertically displaceable facade component. The method 200 comprises the following steps: [0131] In a first step 202, also referred to as step a), a holding force is applied to a vertically displaceable facade component for at least partially compensating the weight of the vertically displaceable facade component by a spring element. The spring element provides a spring force as a driving force for lifting the vertically displaceable facade component; the spring element is moved between a compressed state and an expanded state. The spring force has a decreasing value when moving from the compressed state to the expanded state. [0132] In a second step 204, also referred to as step b), a compensator is provided to at least partially compensate for a decreasing driving force and provide an output force that decreases less than the driving force.

[0133] For example, the first step 202 and the second step 204 occur simultaneously.

[0134] FIG. 4A and FIG. 4B show another example of the compensation device 10 in a schematic view. The spring element 12 is, for example, a linear spring element. In the option shown in FIG. 4A and FIG. 4B, the spring element 12 is a pneumatic spring 22. The pneumatic spring has a cylinder 24 and a piston 26; the cylinder 24 can be supported at one end 28 at a holding point in a facade.

[0135] In FIG. 4A, the spring element 12 is shown in the compressed state P.sub.K and in FIG. 4B, the spring element 12 is shown in the expanded state P.sub.E.

[0136] It should be noted that in FIG. 4A and FIG. 4B, the assembled state is shown as an option in connection with the indicated vertically movable facade component.

[0137] In an option, the transmission 20 is provided with a cable reel 30 on which a cable 32 can be wound, which can be connected to the vertically displaceable facade component. The cable reel 30 is rotationally driven by the spring element 12. The cable reel 30 has a decreasing winding circumference U.sub.W for a winding cable.

[0138] In another option, the transmission 20 is provided with a shaft 34 having a shaft axis A.sub.W , which is rotatably drivable by the spring element 12 on a drive side and which has the cable reel 30 on a driven side.

[0139] In an option, the shaft 34 is provided with a gear wheel 36 on the drive side, which meshes in a fixed toothed rack profile 38. The spring element 12 moves the shaft 34 with the gear wheel 36 attached to it linearly transverse to the shaft axis A.sub.W and thereby drives the shaft 34 in rotation. (In FIG. 3A and FIG. 3B, this is shown somewhat distorted in perspective to better illustrate the functional relationship). For example, the cable 32 is attached to the cable reel 30 and can be wound and un-wound by rotating the cable reel 30. The cable 32 can be wound onto the cable reel 30 by moving the spring element 12 from the compressed state P.sub.K to the expanded state P.sub.E.

[0140] As an option, it is provided that the gear wheel 36 is replaceable and differently sized gears are provided (not shown) with which the lifting force and lifting height of the compensation device can be changed.

[0141] In an option, the piston 26 is connected at its end to the shaft 32. As the piston 26 is extended, the shaft 32, which is rotatably mounted on the end of the piston 26, can be driven via the gear wheel and toothed rack profile. With the cable reel 30 attached to the shaft 32, as the winding circumference decreases, a torque for winding the cable can be reduced due to the decreasing lever distance of the shaft axis from the cable, thereby at least partially negating a weakening of the force of the pneumatic spring.

[0142] The cylinder 24 is supportable at its free end at the holding point of the facade, that is, at the end opposite the opening of the cylinder 24. The open end of the cylinder 24 is the area where the piston 26 is provided. The piston 26 is connected to the shaft 34 at its free end, that is, at the end opposite a bottom of the cylinder 24.

[0143] In the example shown in FIG. 4, the cylinder 24 of the pneumatic spring 22 has its end 28 fixable, i.e. mountable, at an upper region. The other end faces downward and the piston 26 moves downward out of the cylinder 24 as it moves from the compressed state P.sub.K to the expanded state P.sub.E. Attached to the free end of the piston 26 is the shaft 34, which meshes with the gear wheel 36 in the toothed rack profile 38. Moving the piston 26 downward also moves the shaft 34 downward. As the gear wheel 36 on the shaft 34 engages the rack and pinion profile 38, the shaft 34 rotates in a first direction. As a result, the cable reel 30 mounted on the shaft 34 is rotated about the shaft axis A.sub.W and simultaneously displaced downward. The cable reel 30 has a first region with a first diameter D1 and a second region with a second diameter D2. The first diameter D1 is larger than the second diameter D2. This also results in a changing winding circumference.

[0144] The winding circumference in turn means a changing lever. The cable reel 30 with the conical body therefore provides a variable lever.

[0145] The cable 32 is attached to the cable reel 30, which is connected to the vertically displaceable facade component 40, e.g. a vertical sliding window. The cable 32 runs from the cable reel 30 upwards and there over a deflection pulley 42, which is fixable, i.e. mountable, at an upper area. The vertically movable facade component 40, e.g. the vertical sliding window, is then held suspended from the free end of the cable. An arrow F.sub.G indicates the weight force of the vertically sliding facade component 40 resulting from its own weight.

[0146] The pneumatic spring 22 thus acts on the vertically sliding facade component 40, e.g., the vertical sliding window, with an upwardly acting force, i.e. a lifting force or lifting force.

[0147] In FIG. 4A and FIG. 4B it is shown that the lifting movement acting on the window sash is composed of a first movement portion and a second movement portion. On the one hand, the cable reel 30 is displaced downward, which means a first movement component. On the other hand, the cable 32 is wound up by the rotating cable reel 30, which means a second movement component.

[0148] In FIG. 4A, a valve 58 is provided as an option, which is inserted at the pneumatic spring 24 transverse to the spring direction. The valve 58 is accessible in the installed state. The pneumatic spring can be filled and emptied via the valve 58, so that the spring force can be changed in the installed state. For example, the pneumatic spring 24 can be adjusted for a sash weight in a range between 10 and 400 kg when installed.

[0149] The valve 58 is also provided as an option in the other embodiments shown or described.

[0150] The vertically movable facade component 40, for example the vertical sliding window, is movable from a first, lower position P1 to a second, upper position P2 and vice versa. The lower position P1 may be a closed position in case of a vertical sliding window, for example, and the upper position P2 may be an open position.

[0151] In the first/lower position P1 of the vertically displaceable facade component, the pneumatic spring 22 is compressed and acts with a first force on the vertically displaceable facade component 40 via the shaft 34, the cable reel 30 and the cable 32. The pneumatic spring acts with a rotating driving force on the cable reel 30.

[0152] In the first/lower position of the vertically displaceable facade component, the cable 32 is held on the cable reel 30 in the first area with the first diameter D1.

[0153] When the vertically sliding facade component 40 is lifted and moved to the second/upper position P2, the cable 32 is increasingly wound on the cable reel 30.

[0154] In the second/upper position P2 of the vertically displaceable facade component 40, the cable 32 is held on the cable reel 34 in the second area with the second diameter D2.

[0155] In the first/lower position P1 of the vertically displaceable facade component 40, the power transmission from the shaft 34 to the vertically displaceable facade component 40 takes place via the larger diameter of the cable reel 30, i.e. with a larger lever (than in the second/upper position P2).

[0156] In the second/upper position P2 of the vertically displaceable facade component 40, the power transmission from the shaft 34 to the vertically displaceable facade component 40 takes place via the smaller diameter of the cable reel, i.e. with a smaller lever (than in the first/lower position P1).

[0157] When the pneumatic spring piston is inserted in the first/lower position P1, a high torque (in relation to the second/upper position P2) acts on the shaft 34. The cable reel 30 is then un-wound, so that there is then a long lever (in relation to the second/upper position P2).

[0158] When the pneumatic spring piston is extended in the second/upper position P2, a low torque (in relation to the first/lower position P1) acts on the shaft 34. The cable reel 30 is then wound up, so that there is then a short lever (in relation to the first/lower position P1).

[0159] The transmission of the pneumatic spring force through the gear wheel 36 and the toothed rack profile 38 to the shaft 34 and thus the cable reel 30 is constant. In other words, the lever for transmitting force from the pneumatic spring 22 to the cable reel 30 is constant. However, the force from the pneumatic spring, i.e. the driving force, is not constant, i.e. variable. The spring force decreases from the compressed state (first/lower position P1) to the expanded state (second/upper position P2). Thus, the force on the shaft 34 is also not constant.

[0160] The transmission of the rotational force from the shaft 34 or from the cable reel 30 (via the deflection pulley 42) to the vertically displaceable facade component 40 is variable via the path of the pneumatic spring. In other words, the lever for transmitting force from the pneumatic spring 22 to the cable reel 30 is not constant, i.e. variable. The force acting on the cable reel 30 is also variable. The variability of the lever is set up for the variability of the force acting on the cable reel in such a way that the two variabilities balance each other out: The holding force acting on the cable, i.e. the output force, is constant, i.e. not variable.

[0161] The force of the pneumatic spring 22 and the transmission through the gear mechanism, i.e. the compensator, are matched in such a way that the weight force of the vertically displaceable element is compensated by the output force acting on the cable 32. The user can thus very easily move the vertically displaceable element manually, i.e. raise or lower it.

[0162] If the output force is too great, the vertically displaceable element 40 is lifted and, at least without being locked, unintentionally moved upwards.

[0163] If the down force is too small, the user will have to apply a larger opening force and the vertically sliding element 40 will unintentionally move down again after being released, at least without being locked.

[0164] When the window (or other vertically movable element 40) is raised, an additional upward force (i.e. counteracting the weight force) is applied to the window so that the spring force of the pneumatic spring 22 can push the shaft 34 of the cable reel 30 downward. The cable reel 30 is rotated by the rotation of the shaft, thereby winding up the cable.

[0165] Irrespective of the cable reel rotation, the load, i.e. for example the vertical sliding window, is lifted by the stroke of the piston.

[0166] Simultaneously with the extension of the piston of the pneumatic spring 22 and the resulting weakening of the force of the pneumatic spring 22, the shaft 34, which is rotatably mounted at the end of the piston 26, is driven via the gear wheel 36 and the toothed rack 38. In the process, the torque of the shaft 34, i.e. the cable reel 30, decreases. Thus, the lever on the cable reel 30 changes due to the changing distance of the shaft axis from the cable; as the cable on the cable reel increases, the lever becomes shorter. In this case, the weakening of the force of the pneumatic spring is cancelled out by the shortening of the lever.

[0167] As the stroke of the piston increases, the force of the pneumatic spring 22 decreases (compression or characteristic curve). This is accompanied by a reduction in the torque of the shaft. The torque is therefore variable.

[0168] In an option, the cable reel 30 is provided with a cone-shaped winding body 44 in which a spirally extending winding groove 46 is provided for receiving the cable 42.

[0169] A first double arrow 50 indicates the vertical movement of the shaft 34 and thus also of the cable reel 30. A second double arrow 52 indicates the vertical movement of the vertically movable facade component 40. A first rotational arrow 54 indicates the resultant rotational movement of the gear wheel 36, and a second rotational arrow 56 indicates the resultant rotational movement of the shaft 34 and thus the cable reel 30.

[0170] It should be noted that lateral guides of the vertically sliding facade component 40 are not shown.

[0171] In an option, the vertically sliding facade component 40 is a vertical sliding window (not shown in more detail) having at least one movable sash.

[0172] In another option (not shown), the spring element 12 is provided to form a first force element and the driving force forms a first force. The compensator 14 has a second force element that provides a second force that compensates for the decreasing spring force of the first actuator as it moves from the compressed state to the expanded state, such that a resultant force is provided as the output force to compensate for the weight of the vertically displaceable facade component that decreases less than the first force.

[0173] In a first option, it is provided that the second force element provides as the second force an increasing compensation force acting in the direction of the first force. The compensation force compensates for the decreasing spring force of the first force element when moving the first force element from the compressed state to the expanded state.

[0174] In a second option, it is provided that the second force element provides as the second force a decreasing compensation force that acts in opposition to the first force. The compensation force compensates for the decreasing spring force of the first force element when moving the first force element from the compressed state to the expanded state.

[0175] The resulting force can also be referred to as the supporting force or balancing force.

[0176] The force can also be called lifting force to lift the window. In the installed state, the (lifting) force is acting in the opposite direction to the weight force of the sliding facade component. In case of a window sash, the weight force is mainly caused by the weight of the pane(s) and by the sash frame construction.

[0177] In an example, a weight compensation device for vertically displaceable facade components is provided, which has a force element that provides a force for lifting a vertically displaceable facade component for at least partially compensating its own weight. A second force element is also provided. The force element is a spring element movable between a compressed state and an expanded state. The spring element provides a spring force that has a decreasing value when moving from the compressed state to the expanded state. The second force element provides a second force that compensates for the decreasing spring force of the first force element when moving from the compressed state to the expanded state such that a resultant force that decreases less than the first force is provided to compensate for the weight of the vertically movable facade component.

[0178] In another option, a facade module 100 is provided that includes a vertically slidable facade component 102 and at least one example of the weight compensation device 10 according to any of the preceding examples. The at least one weight compensation device is connected to the vertically displaceable facade component and at least partially compensates its own weight.

[0179] In an option, the at least one vertically movable facade component is designed as a vertically movable window element.

[0180] Additionally, as an option, two of the weight compensation devices are provided for the vertically sliding facade component.

[0181] The facade module can also be called the window module.

[0182] In an example, a guide is provided for moving the vertically sliding facade component. The weight compensation devices are arranged, for example, in each case at the side of the sliding window element. The term window is also used here in the sense of a window sash.

[0183] In another example, a weight compensation device is provided for e.g. the vertically sliding sash of a vertical sliding window. A pneumatic spring is fixedly mounted on a supporting unit at one end, e.g. with the cylinder. The other end, e.g. the piston, is mounted for linear movement, for example in a rail guide. The piston can thus be extended and retracted without obstruction. An axially rotatable shaft is mounted at the end of the piston, normal to the piston. At one end of this shaft, a gear wheel is fixed to the shaft, and at the other end, a cable reel is fixed to the shaft. The gear wheel is guided on a toothed rack. A cable hangs on the cable reel and the window sash to be moved hangs on this cable, for example via a deflection pulley.

[0184] When the piston of the pneumatic spring is pushed out, the gear wheel on the rack moves and the shaft is rotated as a result. Because the gear wheel is fixed to the cable reel, the cable reel also rotates. Depending on the direction of rotation of the cable reel, the cable is wound or un-wound on this cable reel.

[0185] When the piston of the pneumatic spring is pushed out, the cable reel rotates so that the cable is wound up. The load at the other end of the cable is thus lifted.

[0186] When the piston is pushed into the cylinder, cable is un-wound from the cable reel and the load hanging from the end of the cable sinks.

[0187] To compensate for the progression of the pneumatic spring, the cable reel is conical, e.g. helical. The cable is fixed at the end of the cable reel with the larger diameter and is wound up in the direction of the smaller cable reel diameter. The constellation pneumatic spring—cable reel thus results in the following situations: [0188] The pneumatic spring is retracted—the cable is on the larger cable reel diameter, long lever. [0189] The pneumatic spring is extended—the cable is on the smaller cable reel diameter, short lever.

[0190] If a constant weight is suspended from the other end of the cable, this means that the different position of the cable on the cable reel causes a shorter or longer lever to act on the pivot point of the cable reel. However, a constant weight but levers of different lengths also mean a different torque depending on the position of the cable on the cable reel.

[0191] However, this difference in the torque of the cable reel is compensated for by the progressive force curve of the pneumatic spring: [0192] Pneumatic spring pushed in=>high torque—cable on large diameter=>long lever [0193] Pneumatic spring extended=>low torque—cable on small diameter=>short lever

[0194] If the ratio of the taper of the cable reel is adjusted to the progression of the pneumatic spring, the uneven force progression of the pneumatic spring can be compensated via unequal length levers on the cable reel and the load at the end of the cable can be kept in balance.

[0195] Another effect that occurs when the cable reel is moved by pushing out the piston of the pneumatic spring is that this raises the load independently of the spooling of the cable. This effect allows the size of the cable reel and the turns on it to be reduced.

[0196] Different loads can be compensated for simply by filling the pneumatic spring in different ways. The term “different filling” refers to different pressure due to different filling by different amounts of filling gas or other suitable fluids. The term “different filling” also refers to different gases or other suitable fluids.

[0197] Another way to compensate for the different counterweights is to change the cable reel diameter or the diameter of the gear. A combination of different measures is also possible. In addition to changing the cable reel diameter, the ratio of the large diameter to the small diameter can also be adjusted.

[0198] The shaft can be set in motion in combination with the pneumatic spring in different ways: Gear—rack, sprocket—chain, cable reel—cable, or belt pulley—belt. There are several options for the suspension of the counterweight: cable, chain and/or belt.

[0199] In another example, a weight compensation is provided that includes the following assemblies: spring element, gear mechanism with a conical reel, a shaft and at least one gear, a rack, a pulley and a counterweight or the wings.

[0200] FIG. 5A shows an example of the compensation device 10 with a vertical retaining profile 60 in a first side view. The upper end of the vertical retaining profile 60 is an upper end of the spring element 12 attached. The lower end of the spring element 12 rotatably supports the cable reel 30. FIG. 5A and FIG. 5B show the spring element 12 in an extended, i.e. expanded, state.

[0201] The retaining profile 60 has a vertical guide 64 in a lower segment 62 for the other end of the spring element 12 and a vertically extending toothed profile 66. The cable reel 30 is connected to a gear wheel (hidden in the figures) which meshes with the tooth profile 66 and rotates the cable reel 30.

[0202] In an example, the gear wheel is formed with a pinion profile with a rounded tooth profile and the rack segment has a rounded tooth profile. This ensures the lowest possible noise level when moving a sash, i.e. a low-noise mechanism.

[0203] In an example, the vertical retaining profile 60 has an upper region that extends along the spring element, for example a pneumatic spring. The upper region is used to connect to the lower region and to transfer force to the facade or wall structure. The upper region has, for example, a U-shaped profile in cross-section so as to be able to absorb and transmit more force. The vertical retaining profile 60 also has a lower region extending along the area that the spring element can expand or extend in an expanded state. The lower region has an area with the rack and pinion profile, but also serves to transfer force to the facade or wall structure. For example, the lower area has a U-shaped profile in cross-section so as to be more stable. The upper and lower sections are offset by 90° (about a longitudinal axis), for example The upper and lower regions of the retaining profile 60 are formed, for example, from a metal sheet by laser cutting and folding.

[0204] FIG. 5B shows a second side view of the example in FIG. 5A.

[0205] As an option, an adaptable counterweight kit 80 for vertically movable facade components is shown in FIG. 5B. The weight compensation kit 80 has at least one compensation device according to one of the preceding examples. The spring element 12 is adjustable in its spring effect when installed. Supplementally or alternatively, the compensator comprises a transmission device for transmitting power, wherein a gear transmission ratio of the transmission device is adjustable. For example, exchangeable gear wheels 82 are provided.

[0206] In an option, the spring element is designed as an exchangeable pneumatic cylinder, for example to be able to take loads in a higher range, or to be able to use smaller but more powerful pneumatic cylinders, for example in a very narrow installation space. The interchangeability allows the use of pneumatic springs with different strokes.

[0207] FIG. 6 shows an upper end of the compensation device of FIGS. 5A and 5B with a held pneumatic spring. The pneumatic spring is held in a holder, for example with a pin 68, which is inserted through a transverse through hole 70.

[0208] FIG. 7 shows an upper end of the pneumatic spring of FIG. 6 with the inserted valve 58 facing sideways, i.e. toward the room.

[0209] FIG. 8A, FIG. 8B and FIG. 8C show a lower end of the compensation device with the vertical retaining profile 60 of FIG. 6 and the vertically extending tooth profile 66 in different views.

[0210] The embodiments described above may be combined in various ways. In particular, aspects of the devices can also be used for the embodiments of the method and vice versa.

[0211] In addition, it should be noted that “comprising” does not exclude other elements or steps, and “one” or “a” does not exclude a plurality. It should further be noted that features or steps that have been described with reference to any of the above embodiments may also be used in combination with other features or steps of other embodiments described above. Reference signs in the claims are not to be regarded as a limitation.