EP3771681B1 - Elevator with elastically supported support column - Google Patents

Description

The invention relates to a ship with an ammunition elevator or with an ammunition elevator system. For example, elevators for ammo are off EP 3 214 399 famous. Furthermore, counterweight-free elevators are designed to increase space efficiency EP 2 862 831 A2 famous.

For ammunition, depending on the gun, the corresponding ammunition is stored differently in the ship. Various storage facilities are also used for provisions. Other goods such as equipment, crew or passenger personal belongings, clothing, spare parts, tools, consumables such as oils, fuel, waste, etc. may also be transported by elevators and are accordingly stored on board a ship. Examples of this storage are transport containers such as crates, pallets, sacks, barrels, boxes, racks, shelves, etc. The elevators inside the ship are suitable for transporting these and other transport containers. Here, filled transport containers are transported, e.g. to the guns and to the kitchen, and emptied containers are transported back, e.g. from the guns and from the galley.

Ships are subject to various forces. In addition to the usual wave movements, different impulses are generated in armed ships and when ammunition is fired, depending on the type of ammunition, and are transmitted to the ship via the guns and their mounts. In addition, attacks directed at the ship could result in increased swell in the event of a detonation in front, alongside, behind, or below the ship, and additional forces if the ship is hit. Forces of this type acting on the ship are referred to below in particular as forces acting in the manner of impulses.

In such conditions, it is advantageous to protect particularly sensitive equipment within the ship from forces such as those outlined above. The functionality of elevators inside the ship will be improved when For example, the drive unit of an elevator is protected from such forces. From the pamphlet EP 3 214 399 known, therefore, the drive unit can be attached elastically to the mast of the elevator. A disadvantage of the elevator shown therein is that the elevator itself, the load carrier and the conveyed goods contained are not protected against impulsive forces.

It is therefore the object of the invention to overcome the disadvantages of the prior art, in particular to provide a ship with an ammunition elevator in which the elevator and the conveyed goods are protected from forces acting on the ship, in particular from forces acting on the ship in a pulsed manner.

The object is solved by the subject matter of independent claim 1. Accordingly, a ship according to the invention comprises an ammunition elevator. The ammunition elevator comprises a load carrier for receiving goods to be conveyed, such as ammunition or provisions, and a support column on which the load carrier is attached so that it can move longitudinally, the load carrier being driven by a drive unit via a traction device guided along the support column, the support column being elastic in relation to the Hull or the ship structure is supported. Due to the elastic support of the support column on which the load carrier is attached, the forces that occur are damped and their effect on the lift, the load carrier and thus also on the conveyed goods is reduced.

An elastic support of the support column relative to the ship's hull is preferably to be understood as the attachment of the support column to the ship's hull via elastic connection elements. As a result, forces occurring in a pulsed manner, which are transmitted from the ship's hull to the support column, are to be at least partially intercepted and dampened by the elastic connecting element. Preferably at least 50%, 70%, 90% or 100% of the weight of the support column is borne by elastic connection elements. Under the elastic support is to be understood in particular an elastic support that ensures a minimum of relative movement of the support column relative to the hull. In order to prevent damage to sensitive components of the elevator or the conveyed goods, it has proven to be advantageous to design the elastic support in such a way that the support column can be displaced by up to 10 mm, 20 mm, 30 mm, 40 mm as a result of particularly large, impulsive forces , 50 mm or 60 mm can be moved relative to the hull. In particular, it has been found that the elastic support preferably takes place in such a way that the relative movement between the support column and the hull of the ship can take place in at least two, preferably in three, directions, in particular cardinal points. For this purpose, it has proven to be particularly advantageous to use wire cable spring elements as elastic connecting elements, which in particular allow elastic deformation in several directions.

Wire rope spring elements preferably have two connecting sections for fastening, in particular screwing, the wire rope spring elements to the ship's hull and to the support column. The two connecting sections are particularly preferably connected to one another by at least two, preferably at least three, four, five or six, curved, in particular arc-shaped, wire ropes. The elastic connecting elements, in particular the wire cables of the wire cable spring elements, are preferably made of stainless steel cables. Compared to conventional steel cables or elastomer dampers, these have a greater deformation capacity for shock absorption and improved vibration damping. In view of the increased risk of corrosion on ships, the use of stainless steel cables for the elastic connection elements has proven to be advantageous.

The elastic connecting elements are preferably designed as shock absorbers and vibration absorbers. An example of such shock and vibration dampers are wire cable spring elements. In particular, these have low natural frequencies. In addition, wire cable spring elements have a resonance overhaul of 150% to 450%, in particular 250% to 350%, which means that vibration of the support column after a pulse-like impact quickly subsides.

The elastic connecting elements used preferably have a spring deflection of at least 2 mm, 4 mm or 6 mm and/or at most 8 mm, 10 mm or 12 mm under a load of 430 kilograms. In particular, the dynamic rigidity of the elastic connecting elements is preferably at least 500 N/mm, 700 N/mm or 900 N/mm and/or at most 1300 N/mm, 1800 N/mm or 2300 N/mm. The natural frequency of the elastic connecting elements is preferably at least 5 Hz, 6 Hz or 7 Hz and/or at most 10 Hz, 11 Hz or 12 Hz. The maximum spring force of at least one of the elastic connecting elements is preferably at least 10 kN, 14 kN or 16 kN and /or maximum 25 kN, 30 kN or 35 kN. The maximum spring deflection of the elastic connecting elements is preferably at least 10 mm, 30 mm or 40 mm and/or at most 45 mm, 50 mm or 60 mm. Advantageous embodiments for the elastic spring elements can be found in particular in the CAVOFLEX product data sheet from Willbrandt Gummitechnik. The use of wire rope spring elements of type H160-267-100-125-8 has proven particularly advantageous.

Alternatively or additionally, it has proven to be advantageous to elastically support the support column on several ceilings and/or walls, in particular via elastic connecting elements, on the ship's hull. In this case, support can also be fitted downwards in a pit that is deeper than the support column. This is particularly useful when the load carrier protrudes at least partially into the pit in the lowest position on the support column. In particular, the support column can be elastically supported on the bottom of the elevator shaft.

Due to the elastic support of the support column on the ship's hull, impulse-like forces can be partially compensated for by the relative movement of the support column relative to the ship's hull. In this case, elastic connecting elements absorb the forces that occur due to elastic deformation and dampen them via the damping constant of the same. The elastic support of the support column has proven to be particularly advantageous because it protects all components of the elevator that are attached to the support column from impulse-like forces. As a result, in particular, the drive unit, the towing device and the transported goods can be moved in a pulsed manner at the same time occurring forces are protected.

Surprisingly, it has been found that the elastic support of the support column on the hull dampens the impulse-like forces so well that the drive unit can be rigidly connected to the support column and can be adequately protected against impulse-like forces simply by the elastic attachment of the support column to the hull . In one embodiment of the invention, the drive unit is therefore rigidly connected to the support column. A rigid connection is to be understood in particular as such a connection, in particular screwing, welding, gluing or some other connection, of the drive unit to the support column which essentially prevents relative movement between the support column and the drive unit. Substantially is only to be understood that small relative movements as a result of assembly play or low elasticity, the support column, the drive or connecting elements, which are also inherent in the most rigid material, should also be included in this embodiment of a rigid connection.

The particular advantage of the rigid connection between the drive unit and the support column is that the output shaft of the drive unit can simultaneously form the drive shaft of the traction device, since there are essentially no relative movements between the drive unit and the traction device. However, it was also recognized that depending on the embodiment of the support column, the goods to be conveyed, the traction device used and the drive unit used, damping of different strengths may be required for the corresponding components. Therefore, as an alternative or in addition to the above statements, it is proposed to support the drive unit elastically with respect to the ship's hull. The elastic support preferably takes place via elastic connecting elements, such as wire rope spring elements.

In a particularly preferred embodiment, both the support column and the drive unit are elastically supported with respect to the hull. In particular, the drive unit and the support column are independently, in particular separately, elastically supported with respect to the ship's hull. It has proven particularly advantageous to attach both the drive unit and the support column in an elastic manner an elevator shaft wall, in particular on the same elevator shaft wall. It has proven to be particularly advantageous to mount the support column and the drive unit on different sides of the wall of the elevator shaft. This can in particular prevent the support column and the drive unit from colliding with one another as a result of different movement amplitudes and/or phase shifts. It has turned out to be particularly preferable to provide a recess in the common wall of the elevator shaft, via which the pulling device can be coupled to the drive unit through the wall of the elevator shaft. For this purpose, a deflection roller of the traction device preferably protrudes through the recess onto the other side of the elevator shaft walls, on which the drive unit is elastically supported. Preferably at least one traction device, particularly preferably at least two traction devices, is guided via this deflection roller from the side of the elevator shaft wall on which the support column is attached to the side of the elevator shaft wall on which the drive unit is attached, deflected over the deflection rollers and back to the side of the Elevator shaft wall out, to which the support column is attached. The deflection roller is particularly preferably designed as a drive shaft of the pulling device, which is driven via the drive unit.

The term hull is to be interpreted broadly in connection with the present invention. In particular, the hull of the ship is not to be understood exclusively as meaning the hull or the ship's shell, which gives the ship its buoyancy. Rather, the hull is to be understood as meaning the ship's structure, which in particular includes ship's walls, such as floors, ceilings and/or elevator shaft walls. The support column is particularly preferably supported elastically on an elevator shaft wall. It is clear that the support column in particular is not to be understood as part of the hull.

According to a development of the present invention, the support column is elastically supported on the ship's hull via elastic connecting elements; the elastic connecting elements preferably being spring elements, in particular wire rope spring elements. Alternatively or additionally, the elastic support allows a relative movement of the support column in at least two, preferably in at least three, directions.

According to a development of the present invention, the drive unit is supported elastically on the hull. Alternatively or additionally, the propulsion unit can be elastically supported against a part of the ship other than the support column. Alternatively, the drive unit can be rigidly attached to the support column.

According to an advantageous embodiment of the present invention, the drive unit and the traction device are coupled to one another in a force-transmitting manner via a force transmission device, a tensioning device for adjusting the tension of the force transmission device preferably being provided

A motor with an output shaft is preferably used as the drive unit. Torque is preferably transmitted to the pulling device via the output shaft. For this purpose, the output shaft of the drive unit can act as a drive shaft on the pulling device side. This one-piece embodiment of the output shaft of the drive unit and the drive shaft of the pulling device has potential for cost savings in particular. However, it has proven to be advantageous to design the output shaft of the drive unit and the drive shaft of the pulling device in two parts. In this way, in particular, a decoupling of the drive unit and the towing device can be ensured. In particular, this enables a relative movement between the drive unit and the traction device without transmitting the forces that occur directly to the traction means of the traction device.

The drive unit and the traction device are preferably coupled to one another in a force-transmitting manner via a force transmission device. The power transmission device preferably includes a traction device, such as a revolving chain or a revolving belt, in particular a flat belt or toothed belt, which transmits the torque from the output shaft of the drive unit to the drive shaft of the traction device. A chain drive is preferably used. The power transmission device particularly preferably comprises a transmission means (transmission point), in particular in the form of a gear, on the output shaft of the drive unit and/or a transmission means, in particular in the form of a gear, on the drive shaft of the traction device. Preferably, the traction means of the power transmission device is in Engagement with the drive-side and the drawbar-side transmission means. The drive torque of the drive unit is preferably transmitted to the drive shaft of the traction device via the power transmission device. The traction means of the power transmission device preferably runs around the transmission means of the output shaft of the drive unit and the drive shaft of the traction device.

The power transmission device can transmit the power between the drive unit and the traction device in a force-fitting manner, in particular via flat belts and shafts with a smooth surface, or in a form-fitting manner, in particular via toothed belts with toothed shafts or via chain drives.

In order to compensate for relative movement between the drive unit and the traction devices, the inner circumference of the power transmission device is preferably larger than the circumference spanned by the two transmission means, ie the inner circumference that a traction means running directly around the two transmission means would have. The inner circumference of the force transmission device is preferably at least 10%, 20%, 30% or 50% larger than the inner circumference spanned by the two transmission means. Alternatively or additionally, the inner circumference of the traction mechanism of the power transmission device is selected to be larger than the circumference spanned by the two transmission mechanisms so that a relative movement of at least 10 mm, 30 mm or 40 mm and/or at most 45 mm, 50 mm or 60 mm between the drive unit and Support column can be compensated. In order to simultaneously ensure constant power transmission in this embodiment, a tensioning device is preferably provided which has at least one deflection roller, via which the circumference spanned by the transmission means and the at least one deflection roller can be kept constant even when there is a relative movement between the drive unit and the support column. The deflection roller of the tensioning device is preferably pretensioned so that when it is at rest (no waves or other impulses that could produce a relative movement between the drive unit and the support column) it tensions the force transmission device, while in load states (relative movement between the drive unit and the support column) the force transmission device is affected by the relative movement The force exerted pushes the deflection roller back against the pretension. Preferably the Clamping device designed in such a way that it provides a substantially constant voltage of the power transmission device both at rest and in the different load conditions and / or provides a constant extent that is spanned by the transmission means and the deflection roller.

According to one embodiment of the present invention, the support column delimits, in particular encloses, transversely to the longitudinal direction, an assembly space that extends along the column, wherein the support column preferably extends as a particularly rectangular frame around the assembly space, and/or wherein the pulling device is at least partially within the assembly space is arranged.

In connection with the present invention, a support column is to be understood in particular as a support column running around an assembly space. The support column preferably forms a structure that is closed transversely to the longitudinal direction. In this way, in particular, the moment of resistance of the support column can be increased, so that the material thickness can be reduced and thus material and weight can be saved. For simplified assembly and repair work, it has proven to be advantageous to provide the closed structure of the support column with recesses for engaging in the support column. In particular, the support column is designed as a casing structure, within which sensitive elements, such as electronic components and/or movably mounted parts, such as deflection rollers, can be arranged and, in particular, protected against damage. In particular, the support column delimits an angular, preferably parallelogram-like, particularly preferably rectangular, assembly space transversely to the longitudinal axis. The support column preferably extends as a rectangular frame parallel to the longitudinal axis of the support column. More preferably, a long side (connection part) of the rectangular frame is at least 50%, 100%, 150%, 200% or 250% larger than a short side (support part) of the rectangular frame. Preferably, two long sides arranged opposite one another, in particular arranged parallel to one another, and two short sides arranged opposite one another, in particular arranged parallel to one another, delimit the assembly space of the support column. The long sides and the short sides are particularly preferably aligned orthogonally to one another. It has turned out to be particularly advantageous To design pulling device and / or the load carrier such that the point of application of the weight of a recorded by the load carrier conveyed between the extension of the two short sides, preferably extends centrally between the extension of both short sides.

The pulling device is particularly preferably guided at least partially within the support column. In particular, the pulling device is guided in the center of the assembly space surrounded by the support column. Preferably, at least two, particularly preferably at least four, deflection rollers are rotatably mounted in the support column. Extending the pulling device at least in sections within the assembly space means in particular that the deflection rollers preferably extend at least 50% within the assembly space surrounded by the support column and/or that at least 30% of the longitudinal extent of at least one traction means extends within the assembly space the support column extends.

The electrical components are preferably routed in the side areas of the assembly space surrounded by the support column. The electrical components are particularly preferably guided in the manner of a sandwich to the left and right of the pulling device within the support column.

According to an advantageous embodiment of the present invention, the support column is constructed in several parts from column walls that are connected to one another, preferably screwed or welded, such as support parts and connecting parts, with four column walls in particular that are connected to one another, preferably screwed or welded, in particular sheet metal, and are preferably rectangular in particular Limit column section, preferably several column sections are connected longitudinally to the support column. Alternatively or additionally, at least two column sections are connected to one another transversely to the longitudinal direction to form the support column.

Alternatively or additionally, the column walls delimiting a column section in each case are arranged offset to one another in the longitudinal direction. By offsetting the column walls, the column sections can be interlocked, which means that the strength of the support column can be increased. Preferably two opposite column walls of a column section are offset in the longitudinal direction to the remaining column walls of the column section. Column walls which are connected to one another are preferably arranged offset in relation to one another in the longitudinal direction. Column walls in the form of support parts or short sides can preferably be arranged offset to column walls in the form of connecting parts or long sides. In particular, the column walls are offset from one another over at least 10%, 20%, 30% or 40% of their extent in the longitudinal direction.

Preferably, the support column can be constructed in a modular fashion from a plurality of column sections. Due to the possibility of being able to connect several column sections to one another in the longitudinal direction, supporting columns of different lengths can be produced in particular with a modular system. Due to the possibility of being able to connect the column sections to one another transversely to the longitudinal direction, support columns of different widths can be produced in particular with a modular system. As a result, with a modular system, in particular, support columns can be formed with different widths of the assembly space encircled by the support column. Furthermore, the strength of the column can thereby be adapted to the load profile of the elevator. The column sections themselves are particularly preferably designed in a modular manner from column walls connected to one another.

The support column is preferably made up of several parts, in particular made up of column walls that are screwed together, such as support parts and connecting plates. As a result, the support column can be transported more easily and installed within narrow elevator shafts. Furthermore, the multi-part design of the support column offers in particular the possibility of a modular design for elevators of different sizes and/or with different load profiles. The multi-part design can also make it easier to replace defective parts or parts that have worn out due to corrosion. The support column is particularly preferably designed as a sheet metal construction. In particular, the support column comprises at least two metal sheets (connecting metal sheets) which are aligned parallel to one another and extend in the longitudinal direction. At least two metal sheets are particularly preferably designed as flat metal sheets and are supported by at least two further, in particular folded, preferably L-shaped or U-shaped supporting parts connected with each other. The support parts preferably have a greater wall thickness and/or greater material strength than the connecting plates. To attach support parts and connecting parts to the support column, these are preferably screwed. In comparison to welding, welding stresses in particular can be avoided in this way, so that in particular the strength of the support column can be increased. In this way, in particular, the wall thickness of the supporting and connecting parts to be used can be reduced and material weight can thus be saved.

Electrical components, such as lines and sensors, of the elevator are preferably mounted within the support column. As a result, the electronics can be protected in particular from damage. The electronics are particularly preferably preassembled in preassembled column sections. As a result, the electrical components can already be protected against damage during transport and assembly. In addition, the hollow interior of the column sections can thus be optimally utilized.

According to a preferred embodiment of the present invention, the support column has at least one deflection device, which directs a traction mechanism of the traction device from the support column to a drive shaft, in particular of the traction device, and from the drive shaft back to the support column, and/or wherein the drive shaft is inside or is located outside an elevator shaft in which the elevator is mounted. In particular, the deflection device comprises a deflection roller for deflecting at least one traction means away from the support column and/or a feed roller for feeding at least one traction means to the support column. The difference between a deflection roller and a feed roller or a deflection roller should consist in particular in the fact that a deflection roller deflects a traction means by around 180°, in particular by 180° ± 30°, with a feed roller or a deflection roller deflecting the traction means by around 90° , in particular by 90 ° ° ± 30 deflects. The at least one traction mechanism is preferably deflected by 180° from the deflection roller to the feed roller via the drive shaft of the traction device. By designing a deflection device, at least one traction device, preferably two traction devices, of the traction device can be deflected out of an elevator shaft. The at least one traction mechanism can then preferably be moved outside of the elevator shaft via a drive shaft and are guided back into the elevator shaft via a deflection roller, preferably in the form of the drive shaft. In particular, a drive unit for the elevator can be attached outside the elevator shaft in a simplified manner.

The longitudinally movable attachment of the load carrier is to be understood in particular as meaning that the load carrier can be moved parallel to the longitudinal axis of the support column. The load carrier particularly preferably has a safety frame, via which the load carrier is guided along the longitudinal axis of the support column. The safety frame preferably surrounds the support column in sections and/or is in engagement with guide rails, which extend in particular on opposite sides of the support column along the longitudinal axis of the support column. The longitudinal axis of the support column is referred to below as the longitudinal direction. The longitudinal direction is to be understood as meaning both directions parallel to the longitudinal axis of the support column.

The ammunition elevator is preferably to be understood as an elevator that is accessible from at least one, preferably from at least two or three, sides. Accessibility from one side means in particular that the load carrier of the ammunition elevator can be loaded with goods to be conveyed from this side. For this purpose, the load carrier preferably has a carrier base (base plate) which is free of boundary walls on at least one, preferably on at least two sides, which extend parallel to the support column. The load carrier particularly preferably has fastening struts which extend parallel to the support column and via which the conveyed goods can be fastened to the load carrier. Particularly preferably, the load carrier has a framework that covers the carrier floor and consists of fastening struts, in particular longitudinal struts and transverse struts, to which the conveyed goods can preferably be fastened. The carrier floor can optionally be equipped with rollers or balls to support the loading. The load carrier can have walls that can preferably be produced from folded sheet metal profiles or a steel structure. Optionally, the load carrier can have an upper boundary wall that acts as a ceiling. At one or more access sides, the respective delimiting wall can be interrupted for access. Optionally, further devices can be attached to the walls of the sides that can serve as loading sides, such as a table, preferably a roller table, which can be folded in or out. The interruptions to be used as access openings Walls on the access sides can be closed, preferably by one or more doors or by means of a roller blind. Furthermore, securing by means of a barrier that can be folded in or out is conceivable, which is preferably designed as a sheet metal profile. Additional elements can be attached to the barrier, such as monitoring devices that serve to ensure safety. These monitoring devices can be designed to detect, for example, cargo, people and/or other events, such as fire, water, movement, temperatures, etc. Various sensors can be used for this, such as optical, acoustic or contact sensors, etc. Alternatively or In addition, the load carrier can have a border running around the carrier floor to secure the conveyed goods against slipping. A border is to be understood in particular as a frame extending over a maximum of 100 mm, 80 mm, 60 mm, 50 mm, 40 mm, 30 mm, 20 mm or 10 mm from the carrier base in the longitudinal direction. Borders that extend higher could in particular limit the accessibility of the load carrier too much. It has been found that the aforementioned height of the border is particularly preferred because, on the one hand, it provides effective slip protection for goods to be transported, in particular for goods to be transported stored in crates, while accessibility is hardly impaired and can at least be guaranteed via ramps or lift trucks.

The load carrier is preferably limited exclusively on the side facing the support column by a boundary wall parallel to the support column. It is clear that fastening struts, which delimit or run around a side from which the load carrier can be loaded and unloaded, do not represent a delimiting wall within the meaning of the present invention. The accessibility of at least one, preferably at least two or three, sides is realized in particular by the fact that the load carrier is guided in an elevator shaft, in which on at least one floor, preferably on each floor, at least one, preferably at least two or three, entrances to the Elevator shaft are provided, which are dimensioned such that the conveyed loaded onto the load carrier and can be unloaded from them.

The invention also relates to a ship with an ammunition hoist system. The ammunition elevator system includes an elevator according to one or more of the embodiments described above and below and an elevator shaft. The support column can be elastically supported relative to the hull of the ship by elastic support of the support column on the elevator shaft. Alternatively or additionally, the support column can be arranged at least in sections in the elevator shaft. The at least partial arrangement of the support column in the elevator shaft is to be understood in particular that the support column can protrude from the elevator shaft in sections in the longitudinal direction. The elevator shaft can be delimited transversely to the longitudinal direction by elevator shaft walls. In particular, the elevator shaft can be completely delimited by elevator shaft walls transversely to the longitudinal direction. Access to the elevator shaft can be implemented via loading points, in particular passageways, introduced into the elevator shaft wall. The elevator shaft can be square, in particular rectangular, and delimited by four shaft walls. The elevator shaft may be formed in the hull of a ship. The support column can be fastened, in particular elastically supported, to a shaft wall extending in the longitudinal direction and/or to a shaft bottom. In particular, the support column can be firmly attached to a shaft wall in such a way that no pivoting movement of the support column is permitted relative to the shaft wall. It is clear that relative movements of the support column relative to the shaft wall as a result of elastic support of the support column on the shaft wall are not to be understood as pivoting movements.

The elevator shaft can be open at one end in the longitudinal direction, so that the load carrier can drive out of the elevator shaft. For this purpose, the support column can protrude in sections from the elevator shaft through an opening in the elevator shaft.

The ship according to the invention can be designed with an ammunition elevator according to one or more of the embodiments described above and below or with the ammunition elevator system described above. In particular in an embodiment with the ammunition elevator system described above, the elevator shaft can be formed in the ship's hull. In particular, the elevator shaft can be open to the ship's deck, so that the load carrier from the Ship's hull can be moved out to the ship's deck. For this purpose, the support column can extend in sections inside and in sections outside the elevator shaft.

The ship can be a military ship or a warship. In particular, the ship can be a ship with guns, such as cannons, and/or gun turrets. In particular, the ship may have a weight of at least one ton, two tons, five tons, ten tons, twenty tons, thirty tons, fifty tons, one hundred tons, two hundred tons, five hundred tons or one thousand tons.

In order to manufacture an elevator suitable for ships, the selection of corrosion-resistant materials is particularly important. Furthermore, ships are exposed to impulse-like forces (shock) due to waves and/or detonations next to, above, below or on the ship. Therefore, when designing elevators for ships that are still working, especially after the effects of shock and/or must not reach a critical operating state, such as ammunition elevators, damping (shock-resistant storage) of sensitive components of the elevator, such as the drive, the towing device and/or of the conveyed goods. In the case of the ammunition elevator, the damping of the conveyed goods can be of essential importance, for example in order to be able to guarantee the ammunition supply even after a hit.

According to a development of the present invention, the elevator includes a drive shaft attached to the support column and driven by the drive unit, in particular a toothed disc or toothed shaft, of the traction device, with the power transmission preferably taking place from the drive unit to the drive shaft via a power transmission device.

According to a further development of the invention, the elevator comprises a slipping clutch for coupling and decoupling the traction device to the drive unit in terms of power transmission, with the slipping clutch preferably having a slipping hub and a slipping shaft, with the slipping hub or the slipping shaft preferably forming the drive shaft of the traction device, with the respective remaining slip shaft or slip hub is driven by the drive unit, preferably is driven by the drive unit via a power transmission device.

In a preferred embodiment, the drive shaft of the traction device is designed as a slipping hub of the slipping clutch, which is arranged on a slipping shaft of the slipping clutch. In the embodiment in which the drive unit and the support column are rigidly connected to one another, the slipping shaft of the slipping clutch is preferably formed by the output shaft of the drive unit. In the preferred embodiment, in which the drive unit and the support column are elastically supported relative to the ship's hull independently of one another, the slipping shaft of the slipping clutch is preferably designed as a separate shaft which is driven by the drive unit via the power transmission device. In particular, the slip hub can prevent the transmission of excessively high forces between the drive unit and the pulling device. For this purpose, the slipping clutch is preferably designed in such a way that slipping is permitted when at least 150%, 200%, 250% or 300% of the maximum operating load occurs. Such loads are hereinafter referred to as excessive loads. Excessively high loads can, for example, be introduced from the support column and/or the hull into elevator components, such as the drive unit and/or the traction device. The slipping clutch can prevent the power flow between the drive unit and the towing device when excessively high loads occur. For example, an excessively high load, which acts on the slipping clutch as a result of an impulse coming from the load carrier, can lead to the slipping clutch slipping, so that the excessively high load cannot be passed on to the drive unit, so that it is protected from damage. Furthermore, an excessively high load acting on the slipping clutch as a result of an impulse from the drive unit can also cause the slipping clutch to slip, so that the excessively high load is not passed on to the towing device, so that it can be protected from damage. As a result, in particular traction means with a lower maximum permissible tensile load can be used. In particular, the use of a slipping clutch facilitates the use of a belt-like pulling device.

It has been found that if the slipping clutch slips or a towing device tears, in the worst case scenario this can lead to the load carrier falling uncontrolled along the support column. To damage the To minimize the load carrier and the conveyed goods in the event of such an uncontrolled fall of the load carrier, it has proven to be advantageous to use lift buffers which are arranged in the area of the lower end of the support column, in particular on the floor, in order to dampen the uncontrolled fall of the load carrier. Two lift buffers are preferably provided for this purpose.

Alternatively or additionally, a ship according to the invention with an ammunition hoist preferably comprises a catching device. The catching device is preferably activated when a maximum travel speed is exceeded in order to slow down the travel speed of the load carrier. For this purpose, the safety gear preferably has a measuring device, which detects the travel speed of the load carrier and activates the safety gear, in particular initiates a braking process, when a maximum travel speed is exceeded. The measuring device preferably comprises a controller cable, in particular a steel cable, which has one end on the
is attached to the load carrier and the other end is attached to a freely suspended tension weight which tensions the governor cable. The governor cable is preferably deflected between the load carrier and the tension weight by a deflection pulley, in particular by 180°. The governor cable is preferably guided along a speed controller, which detects the speed of the governor cable and triggers the braking process when the maximum travel speed is exceeded. For the braking process, the safety gear preferably has a safety brake that brakes the load carrier. For this purpose, the safety brake is placed in a braking position. In the braking position, the safety brake is preferably extended in such a way that it exerts a clamping effect between the load carrier and the support column. The safety brake is preferably set in the braking position with the aid of a brake lever.

In an embodiment of the elevator, the driving unit is elastically supported against a part of the ship other than the supporting column, and the driving force is transmitted to the supporting column via a power transmission device. Because the propulsion unit is supported on another part of the ship, decoupling occurs. This is advantageous because it allows other bearing elements to be used.

In a further exemplary embodiment, the elevator further comprises a tensioning device for adjusting the tension of the power transmission device. In particular, the tensioning device can compensate for a relative movement between elevator components, such as the drive unit, the support column, the load carrier and/or the traction device. Relative movements between elevator components can take place relative to one another, in particular as a result of elastic support of two components, in particular via elastic connecting elements. Two components can be supported elastically relative to one another, in particular by direct elastic support of one component on the other component or by separate elastic support of two components, for example via separate elastic connecting elements.

In a further exemplary embodiment, the support column is attached to the ship's wall, in particular the ship's hull, by means of elastic connecting elements. Advantageously, these elastic connecting elements are springs. Even more advantageously, these elastic connecting elements can absorb forces in two or three axes. The absorption capacity of the connecting elements in two or three axes has a further positive effect on the damping of occurring forces on the ship.

In a further exemplary embodiment, the support column consists of at least two support parts with at least one connecting part, in particular connecting plate, lying between them. This configuration has a positive effect on the stability of the support column.

In a further embodiment, the support parts each consist of several parts. This makes it easier to transport the support parts and bring them inside the ship to be assembled there. Furthermore, individual parts that have been damaged can be replaced more easily.

In a further exemplary embodiment, at least two parts are connected to one another, in particular screwed, in such a way that the column is widened in comparison with the other exemplary embodiments, particularly in the horizontal direction. This advantageously also increases the stability and use of space, which leads to advantages in particular in the case of higher loads.

In a further exemplary embodiment, the support column has at least one deflection device in order to deflect the forces applied via the pulling device. The deflection device preferably has at least one, in particular smooth, deflection or feed roller. A smooth discharge or feed roller is to be understood in particular as a discharge or feed roller with a smooth outer surface, i.e. a tooth-free outer surface. The deflection of the propulsion forces applied via the towing device enables more flexible positioning of the propulsion unit and support column inside the ship.

According to an advantageous embodiment, the pulling device is designed like a belt. The pulling device preferably comprises at least one pulling means which is guided along the support column. The pulling device particularly preferably comprises at least two pulling means, which in particular are parallel to one another along the Supporting column are guided. The traction means can in particular be self-contained, ie form a closed perimeter. Preferably, however, traction means with two ends are used, which are in particular attached to the load carrier with both ends. In particular, one end of the at least one traction mechanism is firmly connected, in particular in a positive or non-positive manner, to the load carrier. In a particularly preferred embodiment, one end of the at least two traction means is connected to a rocker, which is rotatably connected to the load carrier. If there is only one traction device, the rocker can be omitted. As a result, length compensation can take place between the at least two traction means, in particular if the load carrier is loaded unevenly or if the goods to be transported slip on the load carrier. In addition, the stretching of the traction means is compensated for in this way, and the monitoring of a crack and/or slackening of the belt is facilitated.

By attaching the at least two traction devices to the seesaw, the tension in the at least two traction devices can be kept essentially the same. In this way, in particular, a different stretching of the traction means can be prevented. In this way, it can be prevented in particular that the traction means have different lengths. Furthermore, by keeping the tension in the at least two traction means the same, it can be prevented that one traction means is subjected to a greater load than the other traction means. In this way, in particular, uneven wear of the at least two traction means can be prevented.

Furthermore, the rocker can be used to detect tearing and/or slacking of the at least two traction means. In particular, the waves on ships and the detonation of projectiles can lead to shock-like loads on the traction means, so that the detection of tearing and/or slackening of the traction means is of increased importance. For this purpose, the rocker can be fastened to the load carrier so that it can rotate in such a way that a tearing or slackening of at least one of the at least two traction means leads to a movement of the rocker. In particular, the rocker can be rotatably attached to the load carrier in such a way that tearing or slackening of at least one of the at least two traction means leads to a rotary movement of the rocker about the pivot bearing.

The elevator can have a detection device which is designed to detect a rotary movement of the seesaw. The sensing device can be a sensor or a switch. In a preferred embodiment, the detection device is designed as a switch. In a particularly preferred embodiment, the switch is designed as a position switch. The position switch can have a sensor, in particular in the form of a roller, which is in engagement with the rocker. The sensor can be movably, in particular linearly movably, mounted in the position switch. The position switch can be designed in such a way that a movement of the sensor triggers the position switch. In particular, the position switch can be designed in such a way that it is only triggered after a predetermined movement of the sensor.

A rotary movement of the rocker can be detected by using the rocker and detection device described above. The switch can be coupled to a controller which is designed to issue a warning signal and/or switch off the elevator when the switch is triggered. Switching off the elevator can in particular be understood to mean switching off the drive unit and/or triggering safety mechanisms, such as activating a brake, in particular a safety brake. The predetermined movement of the sensor, which triggers the switch, is preferably adapted to the number and/or strength of the traction means used. Alternatively or additionally, the predetermined movement of the sensor can be adapted to the operating state of the elevator. In particular, the controller can be designed to adapt the predetermined movement of the sensor as a function of predetermined operating states. For example, a first operating state can depict the normal operation of the ammunition elevator system, in which even a small movement of the sensor leads to the elevator being switched off in order not to unnecessarily load the traction means. In contrast, a second mode of operation may represent combat operation of a ship in which greater movement of the probe is tolerated in order to maintain elevator operability in combat.

The position switch can have a translationally movable shaft which, after a predetermined movement has taken place, can actuate a trigger of the position switch at one end. At another end, in particular at the opposite end, the shaft can be provided with a sensor, in particular in the form of be connected to a rotatably mounted roller which is in engagement with the seesaw. In particular, the feeler and the rocker are configured in relation to one another in such a way that a rotary movement of the rocker causes a translatory movement of the feeler and of the shaft holding the feeler. For this purpose, the sensor can be in engagement with an edge of the rocker and/or a trough of the rocker that is inclined relative to an orthogonal to the translational movement axis of the shaft.

The combination of the rocker, detection device and controller described above can also be referred to as switch-off devices. Alternatively or additionally, the controller can be designed in such a way that movements of the rocker detected via the detection device are stored in order to draw conclusions about the load, in particular the wear, of the traction means. As a result, in particular time intervals in which the traction mechanism has to be replaced or serviced can be better estimated.

In embodiments with at least two traction means, the traction means can preferably be arranged at the same distance from one another for the rotatable mounting of the seesaw. In particular, the rocker can be rotatably attached to the load carrier via a pivot bearing formed centrally on the rocker. The at least two traction devices can be attached to the seesaw at a distance from the pivot bearing, in particular at the same distances from the pivot bearing. In particular, the attachment of the at least two traction means to the seesaw can also be done in a rotatable manner, in particular via pivot bearings.

The pulling device can have at least three, in particular at least four, pulling means. Particularly in the case of larger loads, the use of at least three traction devices may be necessary in order to prevent excessive loading of the individual traction devices. In order to prevent different stresses and/or expansions in the at least three traction devices and/or to be able to detect tearing and/or slacking of individual traction devices when using at least three traction devices, the use of at least two rockers can be preferred. The elevator can have at least two rockers. At least two of the at least three traction devices can each be fastened with one end to one of the at least two rockers. The at least one remaining traction mechanism can be attached to the remaining of the at least two rockers. Through the use of at least two rockers, tension and/or expansion compensation can take place in at least three traction means. In particular, an expansion compensation can take place in four traction means by two traction means being fastened to a seesaw. In one embodiment, two traction means are attached to a seesaw.

Furthermore, the device can have at least two detection devices, in particular switches, for detecting a movement, in particular a rotary movement, of the rocker. By using at least two detection devices, tearing and/or slacking of each of at least three, in particular at least four, traction means can be individually detected. For this purpose, a detection device can be designed to detect a movement, in particular a rotary movement, of a seesaw.

The at least two rockers can be attached to the load carrier so that they can rotate independently of one another. At least two traction means can be attached to each of the at least two rockers. Furthermore, a detection device can be designed to detect a movement of a rocker in each case in order to detect tearing and/or slackening of a traction mechanism on the respective rocker. Alternatively, at least one of the at least two rockers is rotatably attached to the other rocker. In this case, one of the at least two rockers can be designed as a main rocker, which is rotatably attached to the load carrier. The second of the at least two seesaws can be rotatably attached to the main seesaw as a sub-seesaw. Such an arrangement can in particular be referred to as a cascading arrangement. In particular, two traction devices can be attached to the lower rocker and one traction device to the main rocker. One traction device can be attached directly to the main rocker, while two traction devices are attached to the sub-rocker. As a result, expansion compensation and/or length compensation of the two traction means attached to the lower rocker can take place with one another via the lower rocker. In addition, expansion compensation and/or length compensation between the two traction means fastened to the lower rocker and the traction means fastened to the main rocker can take place via the main rocker.

Furthermore, a detection device for detecting the movement of the main seesaw and a detection device for detecting the movement of the Be trained lower rocker. As a result, tearing and/or slackening of a traction mechanism on the lower rocker can be detected and tearing of the traction mechanism on the main rocker can be detected.

Furthermore, the elevator can have at least three rockers. One of the at least three rockers can be designed as a main rocker which is rotatably attached to the load carrier. The remaining at least two seesaws can be designed as sub-seesaws, each of which is rotatably attached to the main seesaw. At least two traction devices can be attached to each of the two lower rockers. With such an arrangement, on the one hand, length and/or expansion compensation between traction means fastened to a lower rocker can take place via the lower rockers, and length and/or expansion compensation between pairs of traction means can also take place via the main rocker.

Furthermore, the elevator can have at least three detection devices. A detection device can be designed to detect a movement of the main rocker. The remaining at least two sensing devices may be configured to detect movement of the sub-rockers relative to the main rocker. As a result, tearing and/or slacking of the individual traction means can be detected. In addition, uneven loads on the individual traction devices can be detected by detecting movements of the lower rockers. Uneven loads between pairs of traction devices can be detected by detecting movements of the main rocker.

Uneven loads on the traction means can be caused in particular by uneven stretching of the traction means. These can be caused in particular by impermissibly wide stretching of a cord, in particular an insert, of a traction mechanism.

The other end of the at least one traction means is preferably connected to the load carrier via a tensioning device, in particular a belt tensioning device, as described in detail further below.

A belt-like design of the pulling device is to be understood in particular as meaning that the pulling device has at least one belt-like pulling means, that pulls the load carrier along the support column. The tensile force required to pull the load carrier is provided in particular via the drive unit, which drives the belt via a drive shaft of the pulling device. The drive shaft can in particular also be designed as a toothed shaft. For this purpose, the drive means preferably runs around at least two deflection rollers for deflecting the traction means at two opposite ends of the support column. The at least two deflection rollers preferably limit the travel of the load carrier in the longitudinal direction. The at least one traction means preferably runs around the at least two deflection rollers by at least 90°, in particular by approximately 180°.

A belt-like traction means is to be understood in particular as an elongate, in particular strip-like, traction means. In particular, a belt-like traction means is designed to be elastic at least in one direction. A belt-like traction means is preferably elastic along its thickness or its width, so that forces acting between the traction means and deflection rollers and/or drive rollers of the traction device can be at least partially dampened by elastic deformation. In particular, the traction means, which is made of an at least partially elastic material, preferably through rubber or other vulcanizates of natural or synthetic rubber or through a composite material, runs on deflection rollers and other guiding elements, which are preferably made of steel or similar materials. In this way, in particular, the noise emission and the wear of the pulling device can be reduced. Furthermore, the generation and transmission of oscillation and vibration during operation can be reduced. Elastic in connection with elastic traction means is to be understood in particular as elasticity, which is provided, for example, by elastomers. A small degree of elasticity, such as the elasticity of a metal chain, should not be regarded as elastic but as rigid with regard to traction means. The belt-like traction means preferably comprise at least one layer of elastic material. For example, a belt-like traction device could have a metal band for power transmission in the longitudinal direction of the traction device, while an elastic layer, in particular an elastomer layer, is provided on the running surfaces of the traction device, over which the belt-like traction device is guided via drive shafts and deflection rollers. As an alternative or in addition, a belt-like traction mechanism could be spring-loaded or be hung. Rubber, chloroprene rubber, hydrogenated acrylonitrile butadiene rubber or polyurethane, for example, could be used as the material for the layer of elastic material.

According to an advantageous embodiment, the pulling device comprises at least one, preferably at least two, belt-like pulling means, wherein the belt-like pulling means is preferably elastic in at least one direction, in particular in the thickness direction or in the width direction of the belt-like pulling means, and/or wherein the belt-like pulling means has at least one Elastomer-comprehensive layer, in particular made of elastomer, which extends in the longitudinal direction over the entire traction means. The at least one traction device can include a cord, in particular an insert.

According to an advantageous embodiment, the pulling device has at least two belt-like pulling means, which preferably extend parallel to one another, wherein the at least two belt-like pulling means are preferably each connected at one end to the load carrier via an in particular common rocker, and/or wherein the at least two belt-like Traction means are each connected at one end to the load carrier via a particular separate tensioning device, in particular a belt tensioning device.

According to an advantageous embodiment, the pulling device has at least one, preferably at least two, belt-like pulling means, which is guided longitudinally along two sides of the support column via at least two deflection rollers, with preferably two ends of the at least one belt-like pulling means on one side of the column with the load carrier , In particular via a fastening device are attached.

According to an advantageous embodiment of the present invention, the belt-like traction device comprises at least one belt-like traction means in the form of a belt, in particular at least one flat belt or toothed belt, with the elevator preferably having a belt tensioning device for each belt to adjust the tension of the respective belt, flat belt or toothed belt. Power is preferably transmitted from the drive unit to the belt via a drive shaft. The power coupling between the drive unit and drive shaft can in particular take place in a non-positive manner. A non-positive power transmission preferably takes place via the combination of a flat belt and a drive shaft with a smooth cylindrical surface. Alternatively or additionally, the force can be transmitted in a form-fitting manner. A form-fitting power transmission preferably takes place via the combination of a toothed belt with a splined shaft.

A particular advantage of the use of toothed belts is the reduction or avoidance of slippage, as a result of which increased positioning accuracy can be achieved. Furthermore, larger forces can be transmitted through the form-fitting power transmission of toothed belts. One advantage of toothed belts compared to flat belts is that they are largely independent of environmental influences thanks to the form-fitting power transmission. On the other hand, moisture in the elevator shaft, for example, can reduce the force that can be transmitted via the adhesion of a flat belt, which can lead to the belt slipping. The use of toothed belts is therefore of particular advantage when using the ship according to the invention with an ammunition hoist in a shaft that is open at the top. In this way, in particular, the influence of moisture, which can get into the shaft via the opening, can be reduced on the power transmission.

A belt is to be understood in particular as a belt-like traction means which is elastic both in the longitudinal direction and in the width direction and strength direction. The gauge direction is to be understood in particular as the direction in which the running surface and the outer surface of the belt are spaced apart from one another. In the case of a toothed belt, the thickness direction is in particular the direction in which the teeth of the belt extend. A belt within the meaning of the present invention can consist exclusively of an elastic material, such as an elastomer. The traction mechanism is preferably made from a composite material. Preferably, the composite material comprises an elastic material, such as rubber or other vulcanizates of natural or synthetic rubbers, and reinforcing structures. In particular, thin metal cables, preferably steel cables, which preferably extend in the longitudinal direction of the belt, can be used as reinforcement structures. Alternatively or additionally, fibers can be used as reinforcement structures. In particular, a belt within the meaning of the present invention can consist of a fiber-reinforced plastic. For example, a belt can be embedded in an elastomer or in a thermoplastic Reinforcing fibers such as inorganic fibers such as

Glass fibres, organic fibres, such as carbon or aramid fibres, or metallic fibres, such as steel fibres. In particular, the belt-like traction means can have a steel core made of thin wire cables.

The toothed belt has proven to be the preferred form of belt. A toothed belt is to be understood in particular as a belt with teeth on the running surface, via which the belt is driven. In the advantageous embodiment of the at least one belt-like traction means as a toothed belt, toothed discs or toothed shafts are preferably used as the drive shaft and/or as the deflection shaft of the traction device. Due to the form-fitting power transmission via the teeth, a power transmission from the drive shaft to the belt is possible, especially with low pretension. Furthermore, slip is largely avoided, in particular, by the meshing of the teeth.

It has proven particularly advantageous to combine the use of a belt-like pulling device with the inventive elastic support of the support column relative to the ship's hull. Due to the elastic support of the support column, it has surprisingly been found that the forces acting on the ship in a pulse-like manner can be damped in such a way that the load on the pulling device is reduced. In particular, this makes it possible to use a belt-like pulling device, which has a lower strength in comparison to the chain, instead of a metal chain with high strength as the pulling means of the pulling device.

A spring element, such as a spiral spring, can be provided as a tensioning device, in particular a belt tensioning device, for the belt-like traction means, via which the pretensioning of the traction means can be adjusted. A spiral spring is particularly preferably placed on a threaded rod for this purpose, with a stop being provided at one end of the spiral spring and a nut being provided at the other end of the spring, via which the prestressing of the pulling device, in particular the pulling means, can be adjusted. On the one hand, the pretensioning of the belt-like traction means can be adjusted in a simplified manner via the tensioning device. On the other hand, the clamping device can be used to dampen pulsed forces by elastic deformation of the clamping device, in particular the spring element of the clamping device.

The elevator can have a counterweight which is coupled to the load carrier in such a way that the drive power required to drive the load carrier is reduced.

The counterweight and the load carrier can be coupled to one another via at least one traction device. The at least one traction device can be deflected between the counterweight and the load carrier at least once, in particular via a deflection roller, so that the counterweight counteracts the weight of the load carrier. By using the counterweight, the load capacity of the elevator can be increased with the same drive power of the drive unit. This is particularly advantageous in combination with the gear-free drive described below, since the drive torque of such drives cannot usually be applied at any high level, so that for an increased load without a counterweight, the use of more powerful drives would be required. In contrast, the counterweight can reduce the drive power required to drive the load carrier, so that increased loads can be achieved with the same drive or a less powerful drive can be used while maintaining the load. Due to the smaller size of less powerful drives, the installation space requirement of the drive and in particular of the elevator can be reduced. Furthermore, the energy consumption of the elevator can be reduced due to the reduced drive power required.

According to one embodiment, the at least one traction device that couples the load carrier to the counterweight can be designed as a traction device that is separate from the traction device, in particular as a cable, chain, or belt traction device. In this embodiment, the balancing weight can also be referred to as a counterweight. In particular, through the use of a separate traction device, the use of a balancing weight can be combined with an endless traction device, in particular an endless belt. In the context of the present invention, an endless traction device is to be understood in particular as a traction device that is attached to the load carrier at both ends. Accordingly, by using a separate traction device for the counterweight, the rocker and tensioning device described above and below can be combined with the counterweight.

In particular, the at least one separate traction device that couples the load carrier to the counterweight can also be referred to as a compensating traction device. The at least one compensating traction means can be attached to the load carrier at one end and to the counterweight at the other end. The compensating traction device can be deflected between the load carrier and the compensating weight via at least one deflection roller. The deflection roller can be attached to the support column or to a shaft wall. In one embodiment, the counterweight can be coupled to the load carrier via at least two compensating traction means. The at least two compensating traction means can each be attached at one end to the load carrier and at the other end to a common compensating weight or at least two separate compensating weights. In one embodiment, at least 20%, 40%, 60%, 80%, 90%, 95% or 100% of the weight of the load carrier is balanced with the counterweight. For this, the balancing weight can have a corresponding proportion of the weight of the load carrier. According to an alternative embodiment, the at least one traction device can be a traction device of the traction device. In particular, the traction mechanism can be formed by the at least one traction mechanism described above. In particular, the traction means coupling the load carrier to the counterweight can be integrated into the traction device. In particular, the at least one traction device can be attached at one end to the load carrier, for example via the rocker or tensioning device described above and below, in particular a belt tensioning device, and the other end to the counterweight. The at least one traction device preferably extends from the load carrier to a deflection roller, from where the at least one traction device is deflected to the drive shaft of the traction device. The at least one traction mechanism can extend from the drive shaft to the counterweight. The at least one traction means can be deflected between the drive shaft and the counterweight via at least one, preferably via two, deflection rollers. The at least one traction means is preferably deflected by at least one deflection roller by 150° to 210°, in particular by 180°. In particular, the at least one traction device can be deflected by 150° to 210°, in particular by 180°, via a deflection roller between the load carrier and drive shaft, or can be deflected by at least two deflection rollers by 75° to 105°, in particular by 90°. Alternatively or additionally it can at least one traction device between the drive shaft and the counterweight can be deflected by at least two deflection rollers by 150° to 210°, in particular by 180°.

The weight of the load carrier can be understood in particular as the weight of a load-bearing platform of the load carrier, a frame surrounding the platform and/or other components that move with the load carrier. For the purposes of the present invention, the weight of the load carrier is to be understood as the weight of the load carrier in the unloaded state. In contrast, the weight of the load carrier in the loaded state, for example in a state in which ammunition, provisions or people are loaded on the load carrier, is to be understood as the loading weight. Particularly in the embodiment in which the at least one traction mechanism that couples the load carrier and the counterweight is integrated into the at least one traction device, the counterweight can be at least 20%, 40%, 60%, 80%, 100%, 120%, 140% or Balance 150% of a predetermined load weight. In this way, in particular, the required drive power for driving the load carrier can be further reduced, even in the loaded state, and thus the energy consumption and/or the installation space requirement of the drive unit can be reduced. Alternatively, in this embodiment as well, at least 20%, 40%, 60%, 80%, 90%, 95% or 100% of the weight of the load carrier can be compensated for in the unloaded state.

According to one embodiment, the counterweight is arranged at least in sections within a counterweight receptacle delimited by the support column. The counterweight receptacle can be partially or completely enclosed by the support column transversely, in particular orthogonally, to the longitudinal direction. By arranging the counterweight in sections in the counterweight receptacle delimited by the support column, the installation space requirement of the support column can in particular be reduced.

The counterweight receptacle can be delimited by the support column on at least two sides transversely to the longitudinal direction. The counterweight receptacle can preferably be limited by at least two opposite column walls. In addition, the counterweight recording can be limited by at least a third column wall, which the two opposite column walls connected to each other. In particular, the at least three column walls can form a U-shaped wall section of the support column. The area delimited by the U-shaped wall section can be referred to as a counterweight receptacle. Such an embodiment of the counterweight receptacle can in particular be described as being partially enclosed by the support column. Alternatively or additionally, a fourth column wall can be arranged opposite the third column wall in such a way that the at least fourth column walls of the support column form an in particular rectangular frame surrounding the counterweight receptacle.

In one embodiment, the counterweight receptacle can be formed by an assembly space delimited by the support column. The assembly space can be completely enclosed transversely to the longitudinal direction by the column walls, in particular by four column walls, of the support column. In particular, the support column can extend as a closed frame or at least a partially closed frame around the assembly space. The frame can be rectangular. The counterweight can be located entirely within the assembly space. In the case of a frame that is open in sections, the counterweight can be arranged in sections inside and in sections outside of the assembly space.

According to an alternative embodiment, the counterweight receptacle can be designed separately from the assembly space. In particular, the inside of the column walls can delimit an assembly space. With the outside, the column walls can limit the counterweight absorption from at least three sides in particular. The counterweight receptacle can be limited by a U-shaped wall section of the support column. The U-shaped wall section of the counterweight receptacle can be open on one side. As a result, in particular, the counterweight can be arranged in sections in the counterweight receptacle and in sections outside of the counterweight receptacle. In particular, the counterweight can be arranged at least 20%, 40%, 60%, 80%, 90% or 100% within the counterweight receptacle. The remaining part of the counterweight can be arranged outside of the counterweight receptacle.

By arranging the counterweight at least in sections outside of the counterweight receptacle, the point of application of the force of the counterweight can be shifted towards the point of application of the force of the load carrier. In this way, in particular, an improved load distribution can be achieved in relation to the support column, so that the strength of the support column can be increased with the same material thickness of the column walls or can be maintained with a reduced wall thickness of the column walls. The advantage of arranging the counterweight within the support column is the resulting reduced space requirement for the counterweight. A sectional arrangement of the counterweight in the counterweight receptacle has turned out to be a surprisingly good compromise between these two advantages. However, depending on the requirement for the load and the installation space of the elevator, it has also turned out to be advantageous to arrange the counterweight either completely within the support column or completely outside of the support column.

Alternatively or additionally, the counterweight can be guided on the support column. The counterweight can be guided via guide means, such as guide rails, fastened to the support column. In particular, the guide means can be arranged within the counterweight receptacle. The guide means of the counterweight can be arranged on a common line with the guide means, in particular with guide rails, of the load carrier. Alternatively or additionally, the guide means of the counterweight can be offset in relation to the guide means of the load carrier. The guide means of the counterweight can be arranged between the guide means of the load carrier. In particular, the guide means of the counterweight and the guide means of the load carrier can be attached to separate column walls. In particular, the column walls to which the guide means of the counterweight are attached can extend parallel to the column walls to which the guide means of the load carrier are attached. In particular, the column walls in which the guide means of the counterweight are fastened can be arranged between the column walls to which the guide means of the load carrier are fastened.

In an embodiment with separate compensating traction means, the at least one can be arranged between the load carrier and the compensating weight Deflection roller offset to the at least one arranged between the load carrier and the drive shaft deflection roller. In particular, the at least one deflection roller of the compensating traction device can be offset towards the load carrier in relation to the deflection roller of the at least one traction device.

According to one embodiment, the pulling device is designed as a block and tackle in order to reduce the driving force required to drive the load carrier. In particular, the load carrier can be coupled to at least one traction means of the traction device via a loose deflection roller. In particular, the at least one traction means can be fixed at one end to the support column, to a shaft wall or to another wall of a ship's hull. The at least one traction means can extend from this fixed end to the idler pulley and extend from the idler pulley to a fixed pulley. A fixed deflection pulley can be understood to mean a deflection pulley which is firmly attached to the support column, a shaft wall or another wall of a ship's hull. In contrast, and a loose deflection roller is to be understood as a deflection roller that is movable relative to the fixed deflection roller. By designing the pulling device as a block and tackle, in particular the driving force required to drive the load carrier can be reduced. The embodiment with a block and tackle can in particular be combined with the previously described embodiment with a counterweight integrated into the pulling device. In particular, the counterweight can be attached to a loose deflection pulley, which is coupled to the at least one traction means of the traction device. For this purpose, the other end of the at least one traction means of the traction device can also be fixed firmly to the support column, a shaft wall or another wall of a ship's hull. The at least one traction means can extend from this fixed end to the loose deflection roller and from the loose deflection roller to a further fixed deflection roller.

By using the block and tackle, the driving force required, in particular the driving torque required, for driving the load carrier can be reduced. As a result, the drive unit can be reduced with the same payload or the payload can be increased with the same drive unit. In addition, the load on the drawbar can be reduced, so that at the same traction means, the load can be increased or with the same load, the traction means can be made smaller or can be made of less resilient but cheaper material.

A gear reduction of 2:1 is preferably achieved with the block and tackle. This means in particular that the driving force required to drive the load carrier is reduced in that the at least one traction device has to be driven over twice the distance for the same path of the load carrier. The design of the pulling device as a block and tackle has proven to be particularly advantageous in combination with the gear-free drive described below.

The drive unit can be designed as a synchronous motor. The synchronous motor can be designed to provide an output speed of 10 rpm to 150 rpm, in particular 40 rpm to 90 rpm. The particular advantage of using a synchronous motor is that, compared to an asynchronous motor with speeds of around 1500 rpm, it can provide lower speeds in favor of higher torques. As a result, the speed reduction ratio required to provide a sufficiently high torque for driving the load carrier can be significantly reduced compared to an asynchronous motor. As a result, the use of toothed gears, in particular spur gears and/or planetary gears, which can provide a large reduction ratio, can be dispensed with.

Alternatively or additionally, the drive unit is coupled to the traction device without a gear train, in particular by means of traction means. Instead of using a gear drive, the drive unit can be coupled to the traction device via a traction device, in particular via a traction device of the power transmission device described above and below. In a less preferred embodiment, the output shaft of the drive unit can also be coupled directly to the traction means of the drive unit.

It has been found that the total efficiency of the power transmission can be significantly increased, in particular from approximately 60% to 90%, by coupling the drive unit and traction device without gears.

Alternatively or additionally, a reduction ratio of the output speed of an output shaft of the drive unit to a drive shaft of the traction device is less than 30/1, 20/1, 10/1, 5/1 or 3/1. Preferably, the reduction ratio is about 2/1. It has been found that, in particular, high reduction ratios of the speeds lead to large losses in efficiency, so that the efficiency of the power transmission is preferred through the use of drive units with high output torques and low speeds, such as synchronous motors, compared to drive units with high speeds and low output torques, such as asynchronous motors .

A problem that can occur when using small speed reduction ratios is the associated limitation of the load capacity of the load carrier due to the relatively small torque of the drive used. This can mean that small reduction ratios have to be bought in favor of greater efficiency at the expense of larger drives and thus at the expense of acquisition costs and space requirements.

The inventors of the present invention have found that it is therefore of particular advantage to combine the counterweights described above and below with the use of a synchronous motor, a gear-free coupling and/or a small speed reduction ratio. As a result, on the one hand a high level of efficiency can be achieved and on the other hand the load capacity can be increased even with small drives.

Fig. 1a

eine Tragsäule entsprechend einem Ausführungsbeispiel,

Fig. 1b

einen vergrößerten Ausschnitt der Tragsäule entsprechend einem Ausführungsbeispiel,

Fig. 2a

eine Draufsicht auf eine Trägersäule gemäß einem Ausführungsbeispiel,

Fig. 2b

eine Draufsicht auf eine schematisch dargestellte Trägersäule im Querschnitt,

Fig. 3

einen Aufzug entsprechend einem Ausführungsbeispiel,

Figuren 4a - 4d

einen Aufzug mit verschiedenen Montagepositionen der Antriebseinheit entsprechend einem Ausführungsbeispiel,

Fig. 5

eine schematische Darstellung einer von dem Schiffskörper entkoppelten Tragsäule,

Fig. 6a - 6d

einen beispielhaften Aufbau einer Antriebseinheit entsprechend einem Ausführungsbeispiel,

Fig. 7

eine Anordnung einer Zugeinrichtung entsprechend einem Ausführungsbeispiel,

Fig. 8a - 8e

eine Befestigungsmöglichkeit der riemenartigen Zugeinrichtung an den Lastenträger entsprechend einem Ausführungsbeispiel,

Fig. 9

eine Seitenansicht eines Aufzugs mit separat geführtem Gegengewicht;

Fig. 10

eine Seitenansicht eines Aufzugs mit in die Zugeinrichtung integriertem Gegengewicht;

Fig. 11

eine Seitenansicht eines Aufzugs mit Gegengewicht und Flaschenzug;

Fig. 12

eine Draufsicht auf einen Aufzug mit separat geführtem Gegengewicht;

Fig. 13

eine Draufsicht auf einen Aufzug mit separat geführtem Gegengewicht mit alternativer Position des Gegengewichts;

Fig. 14

einen Ausschnitt einer Tragsäule mit versetzt angeordneten Säulenwandungen;

Fig. 15

eine schematische Darstellung einer Wippe mit Abschaltfunktion;

Fig. 16

eine schematische Darstellung von zwei Wippen mit Abschaltfunktion;

Fig. 17

eine schematische Darstellung drei Wippen mit Abschaltfunktion; und

Fig. 18a- 18c

Ansichten einer Wippe gemäß der schematischen Darstellung aus Figur. 15.

Preferred embodiments of the invention are specified in the subclaims. Further advantages, features and properties of the invention are explained by the following description of preferred embodiments of the accompanying drawings:

Fig. 1a

a support column according to an embodiment,

Fig. 1b

an enlarged section of the support column according to an embodiment,

Figure 2a

a plan view of a support column according to an embodiment,

Figure 2b

a plan view of a support column shown schematically in Cross-section,

3

an elevator according to an embodiment,

Figures 4a - 4d

an elevator with different mounting positions of the drive unit according to an embodiment,

figure 5

a schematic representation of a support column decoupled from the hull,

Figures 6a - 6d

an exemplary structure of a drive unit according to an embodiment,

7

an arrangement of a towing device according to an embodiment,

Figures 8a - 8e

a possibility of fastening the belt-like pulling device to the load carrier according to an exemplary embodiment,

9

a side view of an elevator with a separately guided counterweight;

10

a side view of an elevator with integrated in the traction device counterweight;

11

a side view of an elevator with counterweight and pulley;

12

a plan view of an elevator with a separately guided counterweight;

13

a top view of an elevator with a separately guided counterweight with an alternative position of the counterweight;

14

a section of a support column with staggered column walls;

15

a schematic representation of a rocker with switch-off function;

16

a schematic representation of two rockers with switch-off function;

17

a schematic representation of three rockers with switch-off function; and

18a-18c

Views of a seesaw according to the schematic representation Figure. 15 .

The same or similar reference symbols are used below for the same or similar components.

Fig. 1a shows a support column 100 which is mounted on elastic supports 110 and can be attached elastically to a hull of a ship via these. The support column 100 can be installed in ships of all kinds. The size of the elevator and thus of the support column 100 can be adapted to the size of the ship. Instead of being attached to a ship's hull, the support column 100 can also be attached to components of a ship which are later assembled to form a ship or which are available as replacement components. Any forces acting on the ship are weakened and possibly even completely intercepted by these elastic bearings, so that the support column 100 and the remaining parts of the elevator and any conveyed goods 350 located therein are subjected to fewer forces or none at all. This increases the protection of the sensitive parts of the elevator and the conveyed goods 350. The number and type of attachment of the bearings 110 to the support column 100 can be implemented in various ways, and the option shown is merely an exemplary embodiment, which is shown again in an enlarged detail in Fig. 1b is shown. In a preferred embodiment, elastic buffers 120 are formed in the area of the lower end of the support column.

The support column 100 shown is just an example. The proportions as well as the number of bearing points are adjusted for the respective installation location on board a ship. Depending on the size of the elevator and the associated size of the support column 100, a different number of bearing points is required. The overall size of the ship can also affect the number of storage points required. In addition, the type, quantity and weight of the conveyed goods 350 to be transported can also influence the number of long points.

The support column 100 can be constructed in various ways. Figure 2a shows a plan view of a support column 100 according to an embodiment. Figure 2b shows a plan view of a schematic structure of a support column 100 in cross section.

The support column 100 can consist, for example, of at least two support parts and at least one connecting plate. The shape of the support parts 200 can have different characteristics. The support parts 200 can be designed, for example, with U, T, double T, Z or L profiles or as a round tube or with 3, 4 or more corners as a square tube. Other configurations of the support parts are also conceivable.

The at least two support parts 200 are connected to at least one connecting plate 210 . The connecting plates can have recesses which on the one hand can reduce the overall weight and on the other hand enable or facilitate access to elements fitted inside the resulting cavities, such as lines, operating parts or fastenings.

In connection with the present invention, a support column 100 is to be understood in particular as a support column 100 running around an assembly space 500 . The support column 100 preferably forms a structure that is closed transversely to the longitudinal direction. As a result, in particular the moment of resistance of the support column 100 can be increased, so that the material thickness can be reduced and material and weight can thus be saved. For simplified assembly and repair work, it has proven to be advantageous to provide the closed structure of the support column 100 with recesses 510 for engaging in the support column 100. In particular, the support column 100 is designed as a casing structure, within which sensitive elements, such as electronic components and/or movably mounted parts, such as deflection rollers 1020, can be arranged and, in particular, protected against damage. In particular, support column 100 delimits an angular, preferably parallelogram-like, particularly preferably rectangular assembly space 500 transversely to longitudinal axis L. Support column 100 preferably extends as a rectangular frame parallel to longitudinal axis L of support column 100.

Particularly preferably, a long side 210 (connecting part) of the rectangular frame is at least 50%, 100%, 150%, 200% or 250% larger than a short side 200 (supporting part) of the frame of the support column 100 spanning the assembly space 500. Preferably, two delimit each other long sides 210 arranged, in particular parallel to one another, and two short sides 200 arranged opposite one another, in particular arranged parallel to one another, the assembly space 500 of the support column. The long sides 210 and the short sides 200 are particularly preferably aligned orthogonally to one another. It has proven to be particularly advantageous to configure the pulling device 420 and/or the load carrier 310 in such a way that the point of application of the weight G of an item to be conveyed 350 picked up by the load carrier is between the extension 520 of the two short sides 200, preferably centrally between the Extension 520 of both short sides 200 extends.

The support column 100 is preferably made up of several parts, in particular made up of column walls 200, 210, such as supporting parts 200 and connecting parts 210, which are screwed together. As a result, the support column can be transported more easily and installed within narrow elevator shafts. However, the support column is preferably preassembled outside of the elevator shaft and lifted into the elevator shaft by a crane. In ships in particular, the elevator shaft can be open at the top for this purpose, so that the elevator can also be installed in an otherwise already finished ship. Furthermore, the multi-part design of the support column 100 offers in particular the possibility of a modular design for elevators of different sizes and/or with different load profiles. The multi-part design can also make it easier to replace defective parts or parts that have worn out due to corrosion. The support column 100 is particularly preferably designed as a sheet metal construction. In particular, the support column comprises at least two plates (connecting plates 210) which are aligned parallel to one another and extend in the longitudinal direction. At least two metal sheets are particularly preferably designed as flat metal sheets and are connected to one another by at least two further, in particular folded, preferably L-shaped or U-shaped supporting parts 200 . The support parts 200 preferably have a greater wall thickness and/or greater material strength than the connecting plates 210 . In particular, the long side 210 (connection part) of the support column is formed from flat sheets, while the short side 200 (support part) of the support column 100 is formed from U-shaped sheets. To attach support parts 200 and connecting parts 210 to the support column 100, these are preferably connected to one another via screws 530. In comparison to welding, welding stresses in particular can thereby be avoided, so that in particular the strength of the support column 100 can be increased. In this way, in particular, the wall thickness of the supporting and connecting parts to be used can be reduced and material weight can thus be saved.

figure 14 shows a section of a support column 100, which is constructed in several parts from column walls 200, 210 screwed together in the form of support parts 200 and connecting parts 210. In this case, two supporting parts 200 and connecting parts 210 connected to one another in each case delimit a rectangular one column section. A plurality of column sections are connected longitudinally (in the longitudinal direction L) to form the support column 100 . The column walls 200, 210 delimiting a column section in each case are arranged offset in relation to one another in the longitudinal direction L. As in particular at the top end of figure 14 As can be seen, the support parts 200 protruding in the longitudinal direction L relative to the connecting parts 210 result in a toothing of the column sections, as a result of which the strength of the support column can be increased. In the illustrated embodiment, the support members 210 are each offset from the connecting members 200 by approximately 40% of their longitudinal extent.

The pulling device is particularly preferably guided at least partially within the support column. In particular, the pulling device is guided in the center of the mounting space 500 surrounded by the support column. At least two, particularly preferably at least four, deflection rollers 1020 are preferably rotatably fastened in the support column 100 . In particular, the deflection rollers 1020 preferably extend at least 50% within the support column 100, in particular within the assembly space 500 surrounded by the support column.

The electrical components are preferably guided in the side areas 540 of the assembly space 500 surrounded by the support column 100 . In particular, the support column 100 preferably forms cable ducts in the side areas 540 for routing cables.

In particular Figure 2a support points 130 can be seen, via which the support column 100 can be elastically supported on the ship's hull. Preferably, elastic connecting elements 110 are used for the elastic support of the support column on the ship's hull, as shown schematically in FIG Figure 2a implied. Wire cable spring elements 110 are particularly preferably used. Wire rope spring elements 110 preferably have two connecting sections 140 for fastening, in particular screwing, the wire rope spring elements to the ship's hull and to the support column 100. The connection sections 140 of the elastic spring elements 100 are connected in particular rigidly to the support points 130, for example with screws 530. The two connecting sections 140 are particularly preferably connected to one another by at least two, preferably at least three, four, five or six, curved wire ropes 150, in particular in the form of arcuate sections.

The load carrier 310 particularly preferably has a safety frame 330 over which the load carrier is guided along the longitudinal axis L of the support column 100 . The retaining frame 330 preferably encompasses the support column 100 in sections and/or is in engagement with guide rails 340, which extend in particular on opposite sides of the support column 100 along the longitudinal axis L of the support column 100. The safety frame 330 is preferably U-shaped and has one leg in engagement with a guide rail 340.

3 shows an exemplary structure of an elevator 300 with a support column 100 and support points 130 for the elastic support of the support column on the hull. A load carrier 310 is attached to the support column 100 so as to be longitudinally movable. The load carrier 310 can be designed as an open or closed cabin. The load carrier 310 can also consist of just a base plate, or of a base plate with a surrounding border directly on the base plate. In particular, one or more fully or partially circumferential safety devices spaced apart from the base plate can also be provided. These can be designed as simple rods, tubes, cables, plates or the like.

The load carrier 310 can be moved lengthwise along the support column 100 . Various loading points 320 are shown at which the load carrier 310 can be loaded and unloaded. The loading stations 320 can be constructed in such a way that transport containers equipped with rollers can be pushed out or rolled out. Docking stations 320 with sills can be used to prevent accidental slipping or rolling out. Loading stations 320 can also be used where a sill can be used in an extendable and retractable manner, so that there is protection against accidental rolling out or slipping out, but does not present an additional hindrance to loading and unloading when it is lowered. Other ways of securing are also conceivable. Loading stations 320 may have a door that is closable and lockable. Loading stations 320 may also include a barrier that is used for security.

The transport containers can also be fixed on the load carrier 310 by, for example, latching, tying or magnetically, so that the load can be secured during transport and before and during loading and unloading is given.

the figures 4a , 4b , 4c and 4d 12 show an elevator 300 with different mounting positions of the drive unit 410 according to an exemplary embodiment. Here shows the Figure 4a the supporting column 100 which is elastically supported relative to a part of the ship's hull, the supporting column 100 being supported via elastic bearings 110 . The load carrier is attached to the support column 100 so that it can move longitudinally.

The power unit 410 may be an electric motor, or an engine powered by fuel such as gasoline, diesel, or LPG. A hybrid engine that combines both types is also conceivable.

The drive unit 410 is in Figure 4a elastically supported against a part of the ship other than the support column 100, and power transmission is effected from the drive unit 410 at the upper end to the traction device 420 guided along the support column 100.

As another part for supporting the power unit 410, any part of the ship's hull to which the support column 100 is not attached may serve. The propulsion unit 410 can be installed in all types of vessels. The size of the elevator and thus of the drive unit 410 can be adapted to the size of the ship. Instead of being attached to a ship's hull, the propulsion unit 410 can also be mounted in components of a ship which are later assembled into a ship or which are available as spare components.

The drive unit 410 is in Figure 4b elastically supported against a part of the ship other than the support column 100, and the power generated by the drive unit 410 is transmitted via the output shaft 2020 and the power transmission device 2030 to the drive shaft 1035 of the traction device 420 guided between the upper end and the lower end of the support column 100 . The pulling device 420 includes two deflection rollers 1020 for guiding the pulling means 430 along the pulling device 420. The pulling device 420 also includes in Figure 4b a deflection device 1010, each with a deflection roller 1030 for deflecting the traction means away from the support column 100 and one Feed roller 1030 for feeding the traction means to the support column 1030. The difference between a deflection roller 1020 and a feed roller 1030 or a deflection roller 1030 should consist in particular in the fact that a deflection roller 1020 rotates a traction means by about 180°, in particular by 180° ± 30°, deflects, while a feed roller or a deflection roller deflects the traction means by approximately 90°, in particular by 90° ± 30°. The at least one traction means 420 is deflected by 180° from the deflection roller 1030 to the feed roller 1030 via the drive shaft 1035 of the traction device 420. The drive shaft 1035, like all other shafts, can be designed as toothed shafts.

The drive unit 410 is in Figure 4c elastically supported against a part of the ship other than the support column 100, and power transmission is effected from the drive unit 410 at the lower end to the traction device 420 guided along the support column 100.

In the configurations of Figure 4a , 4b and 4c For example, the propulsion unit 410 is attached to a part of the ship other than the support column 100, and the propulsive power is transmitted to the support column 100 via a power transmission device. A local separation can have a positive effect on the safety of the individual components.

The pulling device 420 can comprise chains, ropes, for example made of steel, shafts or belts. A power transmission device can also be designed as chains, cables, for example made of steel, shaft or belt-like.

In this case, the elevator can advantageously also have a tensioning device for adjusting the tension of the power transmission device. In this way, an offset can be compensated for that can arise because the support column 100 is elastically mounted differently than the drive unit 410.

In Figure 4d the drive unit 410 is attached to the support column 100 . Since the support column 100 is elastically supported, the drive unit 410 that may be rigidly attached to it is also protected from the forces that occur. The power transmission can of the drive unit 410 analogous to the figures 4a , 4b or 4c shown ways at the top, bottom or one Place in between on the guided along the support column 100 traction device 420 are effected. In this embodiment, the drive unit 410 is attached directly to the support column 100 . In this case, the drive unit 410 can drive the pulling device 420 directly, but a further power transmission device can also be used in order to vary the location at which the drive unit is fastened.

figure 5 shows a support column 100 according to the invention with bearing points 110. As can be seen in the figure, the support column 100 is exclusively elastically connected to the hull. As a result, the forces acting on the ship for the support column 100 can be dampened, and the elevator, the load carrier and the load are less stressed. Overall, this has a positive effect on the durability of the elevator and the integrity of the item 350 to be conveyed.

In all of the configurations, the elastic connecting elements on the bearings 110 can advantageously be springs. Springs can be used here that can absorb forces in two or three axes.

The support column 100 can advantageously consist of at least two support parts 200 . These support parts 200 can be connected to at least one connecting plate 210 lying between them. The connecting plates 210 can in this case be arranged centrally between the support parts 200 but also symmetrically or asymmetrically offset laterally from the center. Depending on how the metal sheets 210 are attached, a recess or a hollow interior space is created, which can be used for the assembly of further elements of the elevator or other devices. In order to allow or facilitate access to these hollow interiors, the connecting plates 210 can have recesses.

Furthermore, the supporting parts 200 can each consist of several parts. Multi-piece support members 200 are easier to transport. The hollow interiors in the support parts 200 can also be used for the assembly of further elements of the elevator or other devices.

The drive unit 410 is preferably a motor with an output shaft 2020 used. A torque is preferably transmitted to the pulling device 420 via the output shaft 2020 . For this purpose, the output shaft 2020 of the drive unit 410 can act as a drive shaft on the pulling device side. This one-piece embodiment of the output shaft 2020 of the drive unit 410 and the drive shaft for the pulling device 420 has potential for cost savings in particular. However, it has proven to be advantageous to design the output shaft 2020 of the drive unit 410 and the drive shaft 1035 of the pulling device 420 in two parts. In this way, in particular, a decoupling of the drive unit 410 and the pulling device 420 can be ensured. In particular, this enables a relative movement between the drive unit 410 and the pulling device 420 without transmitting the forces that occur directly to the pulling means of the pulling device 420 .

The drive unit 410 and the traction device 420 are preferably coupled to one another in a force-transmitting manner via a force transmission device 2030 . the Figures 6a to 6d show a preferred embodiment of the present invention, in which the power transmission device 2030 is designed as a chain drive (chain not shown). The power transmission device preferably includes a traction device 2040, such as a revolving chain, which transmits the torque from the output shaft 2020 of the drive unit 410 to the drive shaft 1035 of the traction device 420. A chain drive is preferably used. Power transmission device 2030 particularly preferably comprises a transmission means 2021 (transmission point), in particular in the form of a gear wheel, on output shaft 2020 of drive unit 410 and/or a transmission means 1036, in particular in the form of a gear wheel, on drive shaft 1035 of traction device 420 Traction means 2040 of the power transmission device 2030 respectively engaged with the drive-side and the traction device-side transmission means 1036, 2021. The power transmission device 2030 preferably transmits the drive torque of the drive unit 410 to the drive shaft 1035 of the traction device 420. The traction means 2040 of the power transmission device 2030 preferably runs around the transmission means 2021 of the output shaft 2020 of the drive unit 410 and the drive shaft 1035 of the traction device 420.

To allow relative movement between the drive unit 410 and the towbars 420, the inner circumference of the force transmission device 2030 is preferably larger than the circumference spanned by the two transmission means 1036, 2021, ie the inner circumference that a traction means running directly around the two transmission means 1036, 2021 would have. The inner circumference of the traction means 2040 of the force transmission device 2030 is preferably at least 10%, 20%, 30% or 50% larger than the inner circumference spanned by the two transmission means 1036, 2021. Alternatively or additionally, the inner circumference of the traction element 2040 of the force transmission device 2030 is selected to be larger than the circumference spanned by the two transmission elements such that a relative movement of at least 10 mm, 30 mm or 40 mm and/or at most 45 mm, 50 mm or 60 mm between Drive unit 410 and support column 100 can be compensated. In order to simultaneously ensure constant power transmission in this embodiment, a tensioning device 2050 is preferably provided, which has at least one tensioning roller 2051, over which the circumference spanned by the transmission means 1036, 2021 and the at least one deflection roller can be rotated even when there is a relative movement between drive unit 410 and the support column 100 can be kept constant.

the Figures 6a to 6d show a particularly preferred embodiment, in which both the support column 100 and the drive unit 410 are supported elastically with respect to the hull. In particular, the drive unit 410 and the support column 100 are independently, in particular separately, elastically supported with respect to the ship's hull. It has proven particularly advantageous to elastically support both the drive unit 410 and the support column 100 on an elevator shaft wall 160, in particular on the same elevator shaft wall 160. It has proven to be particularly advantageous to attach the support column 100 and the drive unit 410 to different sides of the wall 160 of the elevator shaft. This can in particular prevent the support column 100 and the drive unit 410 from colliding with one another as a result of different movement amplitudes and/or phase shifts. As in particular in Figures 6a and 6b As can be seen, the support column 100 and the drive unit 410 are each elastically supported on the elevator shaft wall 160 via elastic connecting elements 110 . In order to be able to see the elastic connecting elements better, the section of the elevator shaft wall 160 to which the elastic connecting elements 110 of the support column 100 are attached is in FIGS Figures 6a and 6b hidden. Wire cable spring elements 110 are indicated schematically as elastic connecting elements 110 . It has proven particularly preferable to provide a recess 170 in the common wall 160 of the elevator shaft, via which the traction device (not shown) can be coupled to the drive unit 410 through the wall 160 of the elevator shaft. For this purpose, a deflection roller 1035 of the pulling device 420 preferably protrudes through the recess 170 onto the other side of the elevator shaft walls 160, on which the drive unit 410 is elastically supported. At least one traction element, particularly preferably at least two traction elements, is guided via this deflection roller 1035 from the side of the elevator shaft wall 160 on which the support column 100 is attached to the side of the elevator shaft wall 160 on which the drive unit 410 is attached, deflected over the deflection roller 1035 and guided back to the side of the elevator shaft wall 160 on which the support column 100 is attached. The deflection roller 1035, as in FIGS Figures 6a to 6d shown as a drive shaft 1035 of the pulling device 420 which is driven via the drive unit 410.

the Figures 6a to 6d show an exemplary structure of a drive unit 410. The drive unit 410, as in connection with Figures 4a to 4c shown, be elastically supported at different positions on the hull or, as in Figure 4d shown to be rigidly attached to the support column 100.

Power is generated electrically or otherwise in the drive unit 410 in the manner described above, and the output shaft 2020 is driven with this power. The shaft has a transmission point 2021, at which the power transmission device 2030 takes the power and passes it on to the further transmission point 1036 on the deflection roller 1035, which serves as a drive shaft. Also visible is the tensioner 2050 for adjusting the tension of the transmission 2030 as described above. Depending on where the drive unit 410 is mounted, a different one of the pulleys 1020, 1035 can be used as the drive shaft.

Although, as described above, the power transmission device 2030 can be designed as chains, cables, for example made of steel, shaft or belt-like, limit themselves Figures 6a to 6d then to show a possibility of the transmission points 2021 and 1036 with gears that are suitable for a chain.

In Figure 6d there are also deflection and delivery rollers 1030 to see.

The support column preferably has at least one deflection device, in particular in the form of two deflection rollers 1020, in order to deflect the forces applied via the pulling device.

7 shows an arrangement 1000 of a pulling device 420, in particular a belt-like pulling device. The pulling device 420 is guided in the arrangement 1000 via deflection rollers 1020, 1035 and discharge or feed rollers 1030. The upper and lower deflection rollers 1020 are always present. The deflection or feed rollers 1030 are an optional possibility if the drive of the pulling device 420 is to be placed in front of the arrangement 1000 . In addition, each of the deflection rollers 1020, 1035 can be used to transmit power to the belt-like pulling device 420.

At the ends of the pulling device 420 there is a fastening option 1040 on the side facing the upper end of the load carrier, on which the load carrier can be fastened to the belt-like pulling device 420 . In this case, the load carrier is fastened to the fastening option 1040 in such a way that the force can be transmitted to the load carrier via the belt-like pulling device 420 . At the end of the pulling device 420 facing the lower end of the load carrier there is a fastening possibility 1050. The load carrier can be connected elastically to the fastening possibility 1050. This can be effected using tension springs or also using another device that has greater elasticity than the tension device 420 itself.

As in figure 7 indicated, the attachment option 1040 is preferably designed as a rocker 1040 . Both traction means 430 are preferably connected to a rocker 1040 which can be connected to the load carrier (not shown) so that it can rotate via a pivot bearing 1045 . The other end of the two traction means 430 is preferably connected to the load carrier via a fastening option 1050 in the form of a belt tensioning device 1050 . In the figure 7 indicated belt tensioning device 1050 and rocker 1045 are related with the Figures 8a to 8e described in detail.

the Figures 8a to 8e show the possibility of fastening 1050 the pulling device 420 to the load carrier 310. As described above, the two-part configuration of the pulling device 420 is only one of the possibilities. Additional guide pulleys 1080 are shown to guide the belt-type traction device 420 .

In particular, the Figures 8a to 8e the advantageous embodiment of the fastening options 1040, 1050 of the traction means 430 on a fastening device 1060 connected to the load carrier 310. Two fastening options 1040 are formed on the fastening device 1060, each for one end 1047 of the two traction means 430 in the form of a rocker 1050. The rocker 1050 is rotatably attached to the fastening device 1060 via a rotary bearing 1045 with a rotary axis 1046 . The ends 1047 of the traction means 430 connected to the rocker are in particular in Figure 8a and 8c to see.

figure 15 shows a schematic representation of a seesaw 1040 to which two traction means 430 are attached. The rocker 1040 is rotatably attached to the load carrier, not shown, via a pivot bearing 1045 . Furthermore, a detection device 4000 in the form of a position switch 4000 is shown schematically. The detection device has a translationally mounted shaft 4010 at the end of which a sensor 4020 in the form of a roller 1020 is attached. The roller 4020 engages with an edge 4030 of the rocker 1040 that is inclined relative to an orthogonal to the translational movement axis of the shaft 4010 . As a result of uneven loading of the traction means 430, slacking and/or tearing of one of the traction means 430, the rocker 1040 can rotate about the pivot bearing 1045, which can lead to a movement of the shaft 4010, which in turn can trigger the position switch. As a result, in particular an uneven load, tearing and/or slacking of one of the traction means 430 can be detected.

The at least one rocker 1040, as in the Figures 15 to 17 shown, be triangular. Triangular does not necessarily mean that the rocker has to have pointed corners. As in particular in the Figures 15 to 17 As can be seen, the corners of the rocker can be rounded. In particular, the Rocker 1040 can be rotatably mounted in the area of one corner via the pivot bearing 1045, while the traction means 430 are fastened in the area of the other corners. As in particular from the Figures 18a to 18c As can be seen, the rocker 1040 can also have shapes that deviate from a triangular shape.

figure 16 shows an embodiment with three traction means 430, in particular belts. The use of at least three traction means 430 may be necessary, particularly in the case of high loads on the load carrier. In figure 16 the three traction means 430 are coupled to the load carrier via two rockers 1040, 4040. A first rocker 1040 is designed as the main rocker. The main rocker is rotatably connected to the load carrier via the pivot bearing 1045. The second seesaw 4040 is formed as a sub-seesaw 4040 rotatably attached to the main seesaw 1040 . The sub-rocker 4040 is rotatably attached to the main rocker 1040 via a pivot bearing 4045 . One of the three traction devices 430 is attached to the main seesaw 1040 . The other two traction devices 430 are attached to the lower rocker 4040. So that a rotary movement of the rockers 1040, 4040 is caused when the traction means tear, become slack and/or are loaded unevenly, the traction means are spaced apart from the respective pivot bearing 1045, 4045 by a lever arm. In order to also be able to detect uneven loading between the two traction devices 430 attached to the lower rocker 4040 and the traction device 430 attached to the main rocker 1040, the pivot bearing 4045 of the lower rocker is also spaced apart from the pivot bearing of the main rocker 1045 via a lever arm. In one embodiment with three traction means, it has proven advantageous to design the lever arm between pivot bearing 4045 of lower rocker 4040 and pivot bearing 1045 of main rocker 1040 to be larger than the lever arm between traction means 430 attached to main rocker 1040 and pivot bearing 1045 of main rocker 1040 It has proven to be particularly advantageous to set a lever arm between the pivot bearing 4045 of the lower rocker 1040 and the pivot bearing 1045 of the main rocker 1040 that is twice as large as the lever arm between the traction mechanism 430 attached to the main rocker 1040 and the pivot bearing 1045 of the main rocker 1040.

In the embodiment according to figure 16 two detection devices 4000 are used. One of the detecting devices 4000 is engaged with the main seesaw 1040. The other of the detecting device 4000 is engaged with the sub-seesaw 4040. As a result, on the one hand, an uneven load between the traction means 430 fastened to the lower rocker 4040 can be detected. On the other hand, an uneven load can be detected between the pair of traction means 430 fixed to the sub-rocker 4040 and the traction means 430 fixed to the main rocker.

figure 17 shows an alternative embodiment with four traction means 430 and three rockers 1040, 4040. One of the rockers 1040 is designed as a main rocker 1040, which is rotatably attached to the load carrier via a pivot bearing 1045. The remaining two seesaws 4040 are designed as sub-seesaws, each of which is rotatably attached to the main seesaw via a pivot bearing 4045 . Two traction means 430 are fastened to each of the two lower rockers 4040 . In an embodiment with two lower rockers 1040, it has proven to be advantageous to form the same lever arm between the pivot bearings 1045 of the lower rockers 4040 and the pivot bearing 1045 of the main rocker 1040.

in the in figure 17 In the embodiment shown, a detection device 4000 for detecting a movement of the main rocker 1040 and two further detection devices 4000 for detecting movements of the sub-rockers 4040 relative to the main rocker 1040 are provided.

Figure 18a shows a perspective view of a rocker 1040 with a position switch 4000, which is engaged with the rocker 1040 through a recess 4050 in a frame 4060 surrounding the rocker 1040. Figure 18b shows the rocker 1040 according to FIG Figure 18a , with a portion of frame 4060 shown in phantom. Figure 18c shows a front view of the rocker 1040 according to FIG Figure 18a and Figure 18b . The two associated with the rocker 1040 traction means 430 are in the Figures 18a to 18c shown cut off. The traction means 430 are attached to the rocker 1040 via clamping devices 4070 . The clamping devices each comprise two clamping jaws 4080, 4090, between which the traction means 430 are clamped. The clamping jaws 4080, 4090 are connected to one another via screws 4095. In the embodiments shown here, the traction means 430 are designed as toothed belts with a corresponding traction means profile 435 . To improve the attachment between the traction means 430 and the clamping device 4030, one of the clamping jaws 4080 has a profile 435 adapted to the traction means profiling on. The clamping devices 4070 are rotatably attached to the rocker 1040 via pivot bearings 4100 . The rocker 1040 is in turn fastened to the load carrier via a rotary bearing 1045 so that it can rotate.

The rocker 1040 comprises two rocker jaws 1049, between which a clamping jaw 4090 of the clamping devices is fastened. How from the Figures 18a 19c to 19c, the rocker 1040 and/or the rocker jaws 1049 can be triangular in shape with flattened tips.

The position switch 4000 has a translationally movable shaft 4010 . A sensor 4020 in the form of a roller 4020 is attached to the shaft 4010 . The roller is rotatably attached to the shaft 4010. A trough is formed in the rocker 1040, in particular in at least one of the clamping jaws 4080, 4090 of the rocker, in which the sensor 4020 is mounted. As a result, the sensor 4020 is displaced in a translatory manner as a result of a rotary movement of the rocker 1040, as a result of which the position switch 4000 can be actuated.

Furthermore, the fastening device 1060 has two fastening options 1050 for the respective other end 1048 of the two traction means 430 in the form of tensioning devices 1050, in particular belt tensioning devices. A spring element 1051 in the form of a spiral spring 1051 is provided here as the preferred tensioning device 1050 for the traction means 430, via which the pretensioning of the traction means 430 can be adjusted. For this purpose, the spiral spring 1051 is placed on a threaded rod, with a stop 1052 being provided at one end of the spiral spring 1051 and a nut 1053 being provided at the other end of the spiral spring, via which the pretension of the traction means 430 can be adjusted.

In the Figures 8a and 8c is by the wavy lines the section through the in the Figures 8a to 8d shown traction means shown. The traction means 430 preferably extend from these cutting lines, as in FIGS figures 7 , 4a until 4d and 5 shown along the support column 100.

As in particular in Figure 8c shown is the end 1048 of the traction means 430 connected to the belt tensioning device 1050, preferably S-shaped via two rollers 1080, 1090, in particular via a toothed disc 1080 and a smooth one Roller 1090, directed to the respective belt tensioning device 1050.

figure 9 shows a side view of an elevator 300 with a separately guided counterweight 3000. The counterweight 3000 is coupled to the load carrier 310 via a traction device 3010 that is separate from the traction device 430 of the traction device 420. In this embodiment, the counterweight 3000 can also be referred to as a balance weight 3000 . The separate traction device 3010 can be referred to as a compensating traction device 3010 . The compensating traction means 3010 is attached to the load carrier 310 at one end and to the counterweight 3000 at the other end. The compensating traction means 3010 extends from the load carrier 310 to a separate deflection roller 3020, where it is deflected by 180° to the counterweight 3000. The separate pulley 3020 is firmly attached to the support column 100 in the Figures 9 to 11 is indicated by the dashed frame 100 in each case. The counterweight 3000 reduces the force that has to be applied by the drive unit (not shown) to move the load carrier 310 . The drive unit is coupled to the traction device via a power transmission device. A drive shaft 1035 of the traction device, which is driven by the power transmission device from the drive unit, is shown in FIGS Figures 9 to 11 represented schematically by a drive shaft 1035 .

the figures 10 and 11 show embodiments of an elevator 300 with a counterweight 3000, in which the counterweight 3000 is integrated into the traction device 420. In figure 10 one end of the traction device 430 is attached to the load carrier 310 . The other end of the traction device 430 is attached to the counterweight 3000 . The traction device 430 is deflected from the load carrier 310 via two deflection rollers 1020 to the drive shaft 1035 of the traction device. Each of the deflection rollers 1020 deflects the traction means by 90°. A deflection roller 1030 and a feed roller 1030 are also provided directly in front of and behind the drive shaft 1035 of the traction device, in order to deflect the traction means 430 from a vertical alignment to a horizontal alignment to the drive shaft 1035 and from the drive shaft 1035 again from a horizontal alignment to a vertical one Alignment to redirect counterweight 3000. In particular, this can ensure that the drive shaft 1035 has an engagement angle of 180° with the traction mechanism 430 . Alternatively or additionally, the traction means can be deflected to a drive shaft 1035 by this deflection roller 1030 and feed roller 1030, which is arranged at a distance from the support column 100 and/or outside of an elevator shaft. From the drive shaft 1035, the traction mechanism is first deflected by 180° in the direction opposite to the gravitational direction and then by a further 180° back in the gravitational direction to the counterweight 3000 via two further deflection rollers 1020. The deflection roller, which first deflects the traction means 430 starting from the counterweight 3000, is arranged on an upper section of the support column 100, in particular in the upper 50%, 30%, 20% or 10% of the support column. This can in particular ensure that the counterweight can be moved in the longitudinal direction L over at least 50%, 70%, 80% or 90% of the extension of the support column 100 . The deflection roller, which deflects the traction means 430 second, starting from the counterweight 3000, is arranged in a lower section of the support column, in particular in the lower 50%, 30%, 20% or 10% of the extension of the support column in the longitudinal direction. In this way, in particular, a uniform load distribution of the counterweight 3000 along the longitudinal extent of the support column 100 can be ensured. In particular, the two deflection rollers 1020 arranged between the drive shaft 1035 and the load carrier 310 are spaced apart from one another by at least 50%, 60%, 70% or 80% of the longitudinal extension of the support column 100 .

figure 11 shows an embodiment of an elevator with a counterweight 3000 and a load carrier 310, which are coupled to the traction means 430 via a block and tackle. In this case, the load carrier 310 and the counterweight 3000 are each coupled to the traction mechanism 430 via a loose deflection roller 3030 . Alternatively, only the load carrier 310 or only the counterweight 3000 can also be coupled to the traction mechanism 430 via a loose deflection roller 3030 . In the embodiment shown, the traction means 430 is firmly attached to the support column 100 at both ends. Furthermore, the traction means extends from the fixed end to the loose deflection roller 3030 and from the loose deflection roller 3030 to a fixed deflection roller 1020. As a result, the force required to lift the load carrier 310 and/or the counterweight 3000 can be reduced to half the weight of the load carrier and/or the counterweight 3000 can be reduced. In addition, the counterweight 3000 at least partially balances the weight of the load carrier 3010, so that the required driving force of the drive unit can be further reduced.

the Figures 12 and 13 show a view from above of an elevator with a separately guided counterweight 3000, which is arranged at least in sections within a counterweight receptacle 3040 delimited by the support column. The counterweight 3000 is coupled to the load carrier via two separate traction devices (not shown), which are deflected between the counterweight 3000 and the load carrier 310 via two separate deflection rollers 3020 . Two deflection rollers 1020 for deflecting two traction means (not shown) of the traction device are arranged between the separate deflection rollers 3020 . The axes of rotation 1025 of the deflection rollers 1020 of the traction means of the traction device are offset from the axes of rotation 3025 of the separate deflection roller 3020 for the traction means of the counterweight 3000 . In particular, the axes of rotation 3025 of the separate deflection roller 3020 are offset relative to the axes of rotation 1025 of the deflection rollers 1020 of the pulling device toward the load carrier 3010 .

Even if the arrangement of the counterweight 3000 is only shown in connection with embodiments in which the counterweight 3000 is coupled to the load carrier 310 via separate traction means, it is clear that the arrangement and guidance of the counterweight 3000 described below can also be implemented in embodiments in which the counterweight 3000 is coupled to the at least one traction means of the traction device.

in the in figure 12 In the illustrated embodiment, the counterweight 3000 is arranged in sections in the counterweight receptacle 3040. The counterweight receptacle 3040 is delimited in sections by the support column 100 . The counterweight receptacle 3040 is delimited by a U-shaped wall section of the support column 100 . The U-shaped wall section has two opposite column walls 3050, which form the legs 3050 of the U-shaped wall section. The two opposing legs 3050 are joined together by a third column wall 3060 which forms the base 3060 of the U-shaped wall section. As figure 12 can be removed, the counterweight 3000 can be arranged in such a way that it extends in sections beyond the legs 3050 of the U-shaped wall section. So this is in figure 12 The counterweight 3000 shown is only partially arranged in the counterweight receptacle 3040.

The counterweight 3000 can be attached via guide rails 3080 attached to the support column 100 . The guide rails 3080 can be arranged in the counterweight receptacle 3040 . In particular, the guide rails 3070 can be fastened to the legs 3050 of the U-shaped wall section that delimits the counterweight receptacle 3040 . In particular, the guide rails 3080 for the counterweight 3000 can be offset relative to the guide rails 340 for the load carrier, in particular offset transversely to the longitudinal axis L. In particular, the axes of rotation 3025 of the separate deflection roller 3020 can be offset in relation to the guide rails 3080 of the counterweight 2000 .

As in figure 12 shown, the counterweight receptacle 3040 can be formed in addition to the mounting space 500 . The counterweight receptacle 3040 is delimited by the outside of the column walls 3050, 3060 of the support column 100, while the assembly space 500 is delimited by the inside of the column walls 210, 3060, 3070. As a result, at least one section of traction mechanism 430 of traction device 420 can be shielded from the path of counterweight 3000, which in particular can prevent the counterweight from colliding with this section of traction mechanism 430 and thus reduce the risk of the traction mechanism tearing.

The mounting space 500 may include a center portion 505 and side portions 540 . In figure 12 For example, the mounting space is U-shaped, with the center portion 505 of the mounting space forming the base and the side portions 540 of the mounting space forming the legs. In contrast, as in figure 13 shown, the mounting space 500 can also be rectangular. Alternatively or additionally, the central area 505 and the outer areas 540 can be separated from one another by opposing partitions 3070 . In this case, the partition walls can form boundary walls of the middle region 505 of the assembly space 500 .

By dividing the assembly space into a central region 505 and side regions, traction means 430, 3020 and/or the counterweight 3000 can be guided in the central region 505 of the assembly space 500, for example, while in the outer areas 540 of the assembly space 500, for example, cables can be routed.

The partition walls 3070 can be connected to one another by further column walls 3060, 210, in particular in such a way that the central area 505 is completely surrounded by a frame. Column walls 3060, 210 of this type can also be referred to as a connecting part or connecting plate. In one embodiment with a counterweight receptacle 3040 that is separate from the assembly space 500, such as in figure 12 shown, a column wall 3060 form a connecting part or connecting plate of the assembly space 500 and a base of the U-shaped wall section of the counterweight receptacle 3040 at the same time.

The outer areas 540 of the assembly space 500 can be delimited by opposite column walls 3070, 200. The outer areas 540 can be delimited on the inside by a column wall 3070 in the form of a partition 3070 and on the outside by column walls 200 in the form of support parts 200. In particular, the partition walls 3070 and the support parts 200 can be designed as U-shaped column walls. The opposite column walls 3070, 200 of the outer areas 540 of the assembly space 500 can be connected to one another by further column walls 3060, 200. These additional column walls 3060, 200 can also be referred to as connecting parts or connecting plates. In particular, these additional column walls 3060, 200 can be formed by the same column walls 3060, 200 that connect the partition walls 3070 of the central area 505, the assembly space 500 to one another. For this purpose, these connecting parts or connecting plates 3060, 210 can extend from a support part 200 over both partitions 1070 to the second support part 200. In an embodiment with a U-shaped mounting space 500, one of the connecting parts or connecting plates 210 can extend in a straight line. The other connecting part or connecting plate 3060 can be angled at the transition from the central area 505 of the mounting space to the side areas 540 of the mounting space 500 . In an embodiment with a rectangular cross section, both connecting parts or connecting plates 3060, 210 can extend in a straight line.

In figure 13 an embodiment is shown in which the counterweight receptacle 3040 is formed by the assembly space 500, in particular by the central region 505 of the assembly space. The counterweight receptacle 3040 can be delimited by two opposite column walls 3070, 200, which are connected via two further column walls 210 to form a frame. The first two opposite pillar walls can be formed as partition walls 3070 which separate the central area of the assembly space 505 from side areas 540 of the assembly space 500 . In particular, guide rails 3070 of the counterweight 3000 can be attached to the partition walls 3070 . Guide rails 3070 of the counterweight 3000 can be attached to the support column 100 in line with the guide rails 340 of the load carrier 310 .

The features disclosed in the above description, the figures and the claims can be important both individually and in any combination for the implementation of the invention in various configurations.

Reference List

100

support column

110

elastic connecting elements, bearings, wire spring element

120

Lift buffers, oil buffers

130

base

140

connecting sections

150

wire ropes

160

elevator shaft wall

170

Recess in elevator shaft wall

200

Support parts/short side//column wall

210

Connecting part/connecting plate//long side/column wall

300

Elevator

310

load carrier

320

loading points

330

capture frame

340

guide rails

350

conveyed goods

410

drive unit

420

draw gear

430

traction means

435

traction mechanism profiling

500

assembly room

505

Central area of the assembly room

510

recess

520

Extension of the two short sides

530

screws

540

Side areas of the assembly room

1000

arrangement

1010

deflection device

1020

pulleys

1025

Axis of rotation of the deflection pulley

1030

Deflection roller/feed roller

1035

Deflection roller/drive shaft of the towing device

1036

Transmission point/means of transmission/gear

1040

Mounting option/rocker/main rocker

1045

pivot bearing

1046

axis of rotation

1047

ends of the traction mechanism connected to the seesaw

1048

end of the traction means connected to the belt tensioning device

1049

rocker jaws

1050

Attachment option/belt tensioner

1051

spring element

1052

attack

1053

mother

1060

fastening device

1080

toothed washer

1090

smooth roll

2020

Motor/drive unit output shaft

2021

Transmission point/means of transmission/gear wheel

2030

power transmission device

2040

Traction means of the power transmission device

2050

clamping device

2051

tensioning roller of the tensioning device

3000

counterweight

3010

separate traction device/compensation traction device

3020

separate pulley

3025

Axis of rotation of the separate deflection roller

3030

loose pulley

3040

counterweight pickup

3050

Column wall/leg of the U-shaped wall section

3060

Column wall/base of U-shaped wall section

3070

Column wall/partitions/connecting part/connecting plate

3080

Counterweight guide rails

4000

Detection device/position switch

4010

translationally mounted shaft of the position switch

4020

Position switch feeler/roller

4030

inclined edge of the seesaw

4040

lower rocker

4045

Pivot bearing of the lower rocker

4050

Recess in the frame of the seesaw

4060

frame of the seesaw

4070

clamping device

4080

jaws

4090

profiled jaw

4095

screws

4100

Pivot bearing of the clamping devices

L

longitudinal direction

G

point of application of the weight

Claims (15)

1. A ship with an ammunition elevator, comprising:

   a load carrier (310) for receiving material to be conveyed (350), such as ammunition or provisions; and

   a support column (100) to which the load carrier (310) is longitudinally movably attached;

   wherein the load carrier (310) is driven by a drive unit (410) via a traction device (420) guided along the support column (100);

   characterized in that

   the support column (100) is elastically supported relative to the ship's hull.
2. The ship according to claim 1,

   wherein the support column (100) is elastically supported on the ship's wall, in particular the ship's hull, via elastic connection elements (110); wherein preferably the elastic connection elements (110) are spring elements, in particular wire rope spring elements (110); and/or

   wherein the elastic support allows a relative movement of the support column (100) in at least two, preferably in at least three, directions.
3. The ship according to claim 1 or 2,

   wherein the drive unit (410) is elastically supported on the ship's hull; and/or wherein the drive unit (410) is elastically supported with respect to a part of the ship other than the support column (100); or

   wherein the drive unit (410) is rigidly attached to the support column (100).
4. The ship according to one of the preceding claims,
   wherein the drive unit (410) and the traction device (420) are coupled to each other in a force-transmitting manner via a force-transmitting device (2030), preferably wherein a tensioning device (2050) is provided for adjusting the tension of the force-transmitting device (2030).
5. The ship according to one of the preceding claims, wherein the support column (100) delimits, in particular encloses, an assembly space (500), which extends along the support column (ioo),transversely to the support column (100), wherein the support column preferably extends as a, in particular rectangular, frame around the assembly space (500), and/or wherein the traction device (420) is arranged at least in sections within the assembly space (500).
6. The ship according to one of the preceding claims, wherein the support column (100) is formed in multiple parts from interconnected, preferably screwed or welded, column walls (200, 210), such as support parts (200) and connection parts (210), wherein preferably in each case in particular four interconnected, in particular sheet metal-like, column walls (200, 210) delimit an in particular rectangular column section, wherein preferably at least two column sections are connected in that they adjoin each other in longitudinal direction to form the support column (100), and/or wherein at least two column sections are connected in that they adjoin each other transversely to the longitudinal direction to form the support column (100), and/or wherein the column walls (200, 210), which define a column section, are arranged offset to each other in longitudinal direction.
7. The ship according to one of the preceding claims, wherein the support column (100) comprises at least one deflection device (1010) which guides a traction means (430) of the traction device (420) from the support column (100) to a drive shaft (1035), in particular of the traction device (420), and from the drive shaft (1035) back to the support column (420), and/or wherein the drive shaft (1035) is arranged inside or outside an elevator shaft in which the elevator (300) is mounted.
8. The ship according to one of the preceding claims, comprising a counterweight (3000) coupled to the load carrier (310) such that a drive power required to drive the load carrier (310) is reduced.
9. The ship according to claim 8, wherein the counterweight (3000) is arranged at least in sections within a counterweight receptacle (3040), which is delimited by the support column (100), and/or wherein the counterweight (3000) is guided on the support column (100), in particular is guided via guide means fastened to the support column (100).
10. The ship according to one of the preceding claims, wherein the traction device (420) comprises at least two in particular belt-like traction means (430) which preferably extend parallel to one another, wherein the at least two traction means (430) are preferably each connected by one end (1047) to the load carrier (310) via an in particular common rocker (1040), and/or wherein the at least two traction means (430) are each connected by one end (1048) to the load carrier (310) via an in particular separate tensioning device (1050), in particular belt tensioning device (1050).
11. The ship according to one of the preceding claims, wherein the traction device (420) comprises at least three traction means (430), in particular wherein the elevator comprises at least two rockers (1040, 4040), in particular wherein at least two of the at least three traction means (430) are each attached with one end (1047) to one of the at least two rockers (1040) and the at least one remaining traction means (430) is attached to the remaining rocker (4040) of the at least two rockers (1040, 4040), in particular wherein the elevator (300) comprises at least two detection devices (4000), in particular switches, for detecting a movement, in particular a rotational movement, of the rockers (1040, 4040), and/or wherein at least one rocker (4040) of the at least two rockers (1040, 4040) is rotationally movably attached to the other rocker (1040).
12. The ship according to one of the preceding claims, wherein the drive unit (410) is designed as a synchronous motor, in particular with an output speed of 10 rpm to 150 rpm, in particular of 40 rpm to 90 rpm, and/or wherein the drive unit (410) is coupled to the traction device (420) without a toothed gear, in particular by use of traction means (2040),, and/or wherein a reduction ratio of the rotational speed of an output shaft (2020) of the drive unit (410) to a drive shaft (1035) of the traction device (420) is less than 30/1, 20/1, 10/1, 5/1 or 3/1.
13. The ship according to one of the preceding claims, with an ammunition elevator system, comprising:
    An elevator shaft, in particular wherein the elastic support of the support column relative to the ship's hull is provided by an elastic support of the support column on the elevator shaft.
14. The ship according to claim 13, wherein the support column (100) is arranged at least in sections in the elevator shaft, in particular, wherein the elevator shaft is open in the longitudinal direction at one end so that the load carrier (310) can drive out of the elevator shaft.
15. The ship according to one of the claims 1 to 14, wherein the elevator shaft is formed in the ship's hull and is preferably open to the ship's deck so that the load carrier (310) can drive out of the ship's hull.

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