EP3771682A1 - Ascenseur doté d'un moyen de traction de courroie - Google Patents

Ascenseur doté d'un moyen de traction de courroie Download PDF

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Publication number
EP3771682A1
EP3771682A1 EP20188973.0A EP20188973A EP3771682A1 EP 3771682 A1 EP3771682 A1 EP 3771682A1 EP 20188973 A EP20188973 A EP 20188973A EP 3771682 A1 EP3771682 A1 EP 3771682A1
Authority
EP
European Patent Office
Prior art keywords
elevator
support column
belt
load carrier
drive unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20188973.0A
Other languages
German (de)
English (en)
Other versions
EP3771682B1 (fr
Inventor
Tom Zischau
Hans Martin Lutz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hans Lutz Maschinenfabrik & Co Kg GmbH
Original Assignee
Hans Lutz Maschinenfabrik & Co Kg GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hans Lutz Maschinenfabrik & Co Kg GmbH filed Critical Hans Lutz Maschinenfabrik & Co Kg GmbH
Publication of EP3771682A1 publication Critical patent/EP3771682A1/fr
Application granted granted Critical
Publication of EP3771682B1 publication Critical patent/EP3771682B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B7/00—Other common features of elevators
    • B66B7/06—Arrangements of ropes or cables
    • B66B7/062—Belts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B11/00—Main component parts of lifts in, or associated with, buildings or other structures
    • B66B11/0065—Roping
    • B66B11/007—Roping for counterweightless elevators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B11/00—Main component parts of lifts in, or associated with, buildings or other structures
    • B66B11/0065—Roping
    • B66B11/008—Roping with hoisting rope or cable operated by frictional engagement with a winding drum or sheave
    • B66B11/0085—Roping with hoisting rope or cable operated by frictional engagement with a winding drum or sheave of rucksack elevators

Definitions

  • the present invention relates to elevators, in particular freight elevators, such as ammunition elevators or provisions elevators, and / or passenger elevators for ships with which conveyed goods such as ammunition or provisions can be moved within a ship in order to supply the conveyed goods, for example, to a gun or a store.
  • the invention also relates to an elevator system with an elevator and an elevator shaft.
  • the invention also relates to a ship with an elevator or with an elevator system. Elevators for ammunition, for example, are off EP 3 214 399 known.
  • chains are usually used in order to transmit the forces generated by the drive unit to the load carrier. But this has some disadvantages. Chains are maintenance-intensive and must be treated with lubricant to reduce wear. These lubricants can cause soiling, both on the elevator in general and on the chain in particular. In addition, chains are generally susceptible to soiling. Chains are also noisy, especially because a chain consists of moving parts. Additional noises have an effect particularly negative for ships, which make it easier to locate them. In addition, the efficiency of chains is relatively low and, as metallic components, they are also at risk of corrosion, especially in marine environments. Chains also have a so-called polygon effect, which can sometimes lead to uneven running. Added to this is the relatively high weight of chains.
  • an elevator according to the invention in particular a freight elevator, such as an ammunition elevator or provisions elevator, and / or passenger elevator, for ships comprises a load carrier for picking up conveyed goods such as ammunition, a support column on which the load carrier is attached in a longitudinally movable manner, and a drive unit for driving of the load carrier via a pulling device running along the support column, the pulling device being 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 are in particular guided parallel to one another along the support column.
  • the traction means can in particular be self-contained, ie form a closed circumference.
  • traction means are used with two ends each, which are fastened in particular with both ends to the load carrier.
  • one end of the at least one traction means is firmly, in particular positively or non-positively, connected to the load carrier.
  • one end of each of the at least two traction means is connected to a rocker that is rotatably connected to the load carrier. If there is only one traction device, the rocker can be omitted.
  • length compensation can take place between the at least two traction means, in particular when the load carrier is unevenly loaded or when the transported goods slip on the load carrier.
  • a Compensation for the elongation of the traction means is achieved, and the monitoring in the event of a crack and / or slack in the belt is facilitated.
  • the tension in the at least two traction means can in particular be kept essentially the same. In this way, in particular, different expansion of the traction means can be prevented. This can in particular prevent the traction means from being of different lengths. Furthermore, by keeping the tension in the at least two traction means equal, it is possible to prevent one traction means from being more heavily loaded than the other traction means. In this way, in particular, uneven wear of the at least two traction means can be prevented.
  • the rocker can be used to detect the tearing and / or slackening of the at least two traction means.
  • the swell in ships and the detonation of projectiles can lead to shock-like loads on the traction means, so that the detection of the tearing and / or slackening of the traction means is of increased importance.
  • the rocker can be attached to the load carrier such that it can rotate in such a way that tearing or slackening of at least one of the at least two traction means leads to a movement of the rocker.
  • the rocker can be rotatably attached to the load carrier in such a way that a tearing or slackening of at least one of the at least two traction means leads to a rotational 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 detection device can be a sensor or a switch.
  • the detection device is designed as a switch.
  • 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 moveable, mounted in the position switch.
  • the position switch can be designed such that a movement of the sensor triggers the position switch.
  • the position switch can be designed such 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 as described above.
  • the switch can be coupled to a controller which is designed to output a warning signal when the switch is triggered and / or to switch off the elevator.
  • Shutting down the elevator can mean, in particular, shutting down the drive unit and / or triggering safety mechanisms, such as activating a brake, in particular a safety brake.
  • the predetermined movement of the sensor that leads to the triggering of the switch is preferably adapted to the number and / or strength of the traction means used.
  • the predetermined movement of the sensor can be adapted to the operating state of the elevator.
  • the controller can be designed to adapt the predetermined movement of the sensor as a function of predetermined operating states.
  • a first operating state can depict the normal operation of the elevator system, in which even a small movement of the sensor leads to the elevator being switched off so as not to unnecessarily load the traction means.
  • a second operating state can map the operation of a ship during a battle, in which a larger movement of the sensor is tolerated in order to maintain the functionality of the elevator in battle.
  • 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.
  • the shaft can be connected to a sensor, in particular in the form of a rotatably mounted roller which is in engagement with the rocker.
  • the sensor and the rocker are designed with respect to one another in such a way that a rotary movement of the rocker causes a translational movement of the sensor and of the shaft holding the sensor.
  • the sensor can be in engagement with an edge of the rocker that is inclined with respect to an orthogonal to the translational movement axis of the shaft and / or a depression in the rocker.
  • the combination of the rocker, detection device and control described above can also be referred to as disconnection devices.
  • the control can be designed in such a way that movements of the rocker that are 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 devices are replaced or have to be serviced can be better estimated.
  • the traction means can preferably be arranged at the same distance from one another to the rotatable mounting of the rocker.
  • the rocker can be rotatably attached to the load carrier via a pivot bearing formed in the center of the rocker.
  • the at least two traction means can be attached to the rocker at a distance from the pivot bearing, in particular at the same distances from the pivot bearing.
  • the fastening of the at least two traction means on the rocker can also take place in a rotatable manner, in particular via pivot bearings.
  • the pulling device can have at least three, in particular at least four, pulling means.
  • the use of at least three traction means may be necessary in particular with larger loads in order to prevent excessive loading of the individual traction means.
  • 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 means can each be fastened with one end to one of the at least two rockers. The at least one remaining traction means can be attached to the remaining one of the at least two rockers.
  • tension and / or expansion compensation can take place in at least three traction means.
  • expansion compensation can take place in four traction devices in that two traction devices are attached to a rocker.
  • two traction devices are attached to a rocker.
  • the device can have at least two detection devices, in particular switches, for detecting a movement, in particular a rotary movement, of the rocker.
  • a Tearing and / or slackening each of at least three, in particular at least four, traction means are individually detected.
  • each detection device can be designed to detect a movement, in particular a rotary movement, of a rocker.
  • the at least two rockers can be attached to the load carrier in a rotatable manner independently of one another.
  • At least two traction means can be attached to each of the at least two rockers.
  • one detection device in each case can be designed to detect a movement of a rocker in each case in order to detect a tearing and / or slackening of a traction device on the respective rocker.
  • at least one of the at least two rockers is rotatably attached to the other rocker.
  • One of the at least two rockers can be designed as a main rocker that is rotatably attached to the load carrier.
  • the second of the at least two rockers can be rotatably attached to the main rocker as a lower rocker.
  • Such an arrangement can in particular be referred to as a cascading arrangement.
  • two traction means can be attached to the lower rocker and one traction means can be attached to the main rocker.
  • One pulling device can be attached directly to the main rocker, while two pulling devices are attached to the lower rocker.
  • 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.
  • the main rocker can be used to compensate for expansion and / or length compensation between the two traction means attached to the lower rocker and the traction means attached to the main rocker.
  • a detection device for detecting the movement of the main rocker and a detection device for detecting the movement of the lower rocker can be designed.
  • the tearing and / or slackening of a traction means on the lower rocker can be detected and the tearing of the traction means on the main rocker can be detected.
  • the elevator can have at least three rockers.
  • One of the at least three rockers can be designed as a main rocker that is rotatably attached to the load carrier.
  • the remaining at least two rockers can be used as Be formed lower rocker, which are each rotatably attached to the main rocker.
  • At least two traction means can be attached to each of the two lower rockers.
  • 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 detection devices can be designed to detect a movement of the lower rocker relative to the main rocker.
  • tearing and / or slackening of the individual traction means can be detected.
  • uneven loads on the individual traction devices can be recorded by detecting movements of the lower rockers. Uneven loads between pairs of traction means can be detected by detecting movements of the main rocker.
  • Uneven loading of the traction means can be caused in particular by uneven stretching of the traction means. These can in particular be caused by an impermissibly large stretching of a cord, in particular an insert, of a traction device.
  • 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 below.
  • a belt-like configuration of the pulling device is to be understood in particular to mean 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.
  • the drive means preferably revolves 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 FIG 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.
  • a belt-like traction means is designed to be elastic at least in one direction.
  • a belt-like traction device is preferably designed to be elastic along its thickness or its width, so that forces acting between the traction device and deflection rollers and / or drive rollers of the traction device can be at least partially damped by elastic deformation.
  • the traction means which is made of an at least partially elastic material, preferably runs through rubber or other vulcanizates of natural or synthetic rubbers or through a composite material, on pulleys and other removal elements, which are preferably made of steel or similar materials.
  • Elastic in connection with elastic traction means is to be understood in particular as the elasticity that is provided, for example, by elastomers.
  • a low degree of elasticity, such as the elasticity of a metal chain, should not be viewed as elastic but rather as rigid with regard to traction means.
  • the belt-like traction means preferably comprise at least one layer of elastic material.
  • a belt-like traction mechanism could have a metal band for power transmission in the longitudinal direction of the traction mechanism, while an elastic layer, in particular an elastomer layer, is provided on the running surfaces of the traction mechanism, over which the belt-like traction mechanism is guided over drive shafts and pulleys.
  • a belt-like traction means for cushioning forces occurring in the form of pulses could, for example, be resiliently mounted or suspended.
  • rubber, chloroprene rubber, hydrogenated acrylonitrile butadiene rubber or polyurethane could be used as the material for the layer made of elastic material.
  • the pulling device comprises at least one, preferably at least two, belt-like pulling means, the belt-like
  • Traction means is preferably designed to be elastic in at least one direction, in particular in the thickness direction or in the width direction of the belt-like traction means, and / or wherein the belt-like traction means comprises at least one layer comprising an elastomer, in particular consisting of elastomer, which extends in the longitudinal direction over the entire traction means extends.
  • the at least one traction means can comprise a cord, in particular an insert.
  • 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 with one end via an in particular common rocker with the load carrier, and / or wherein the at least two belt-like Traction means are each connected with one end via an in particular separate tensioning device, in particular a belt tensioning device, with the load carrier.
  • the pulling device has at least one, preferably at least two, belt-like pulling means, which is guided over at least two pulleys along two sides of the support column, 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.
  • the belt-like pulling device comprises at least one belt-like pulling means in the form of a belt, in particular at least one flat belt or toothed belt, the elevator preferably having a belt tensioning device for each belt to adjust the tension of the respective belt, flat belt or toothed belt.
  • the power is preferably transmitted from the drive unit to the belt via a drive shaft.
  • the force coupling between the drive unit and the drive shaft can in particular take place in a non-positive manner.
  • Force-fit power transmission is preferably achieved by combining a flat belt with a drive shaft with a smooth cylinder surface.
  • the force can be transmitted in a form-fitting manner.
  • a positive force transmission is preferably carried out by combining a toothed belt with a toothed shaft.
  • the use of toothed belts is particularly advantageous in reducing or avoiding slippage, as a result of which increased positioning accuracy can be achieved. Furthermore, the positive force transmission of toothed belts allows greater forces to be transmitted.
  • One advantage of toothed belts over flat belts is in particular that they are largely independent of environmental influences thanks to the positive force transmission.
  • moisture in the elevator shaft for example, can reduce the force that can be transmitted via the frictional connection of a flat belt, which can lead to the belt slipping.
  • the use of toothed belts is therefore of particular advantage when the elevator according to the invention is used in a shaft that is open at the top. This is because in particular the influence of moisture that can get into the shaft through the opening can be reduced on the power transmission.
  • a belt is to be understood as meaning, in particular, a belt-like traction means that is elastic both in the longitudinal direction and in the width direction and thickness direction.
  • the direction of thickness is to be understood in particular as the direction in which the running surface and the outer surface of the belt are spaced 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 in particular consist exclusively of elastic material such as an elastomer.
  • the traction means is preferably made from a composite material.
  • the composite material preferably comprises an elastic material, such as rubber or other vulcanizates of natural or synthetic rubbers, and reinforcing structures.
  • a belt within the meaning of the present invention can consist of a fiber-reinforced plastic.
  • a belt can have reinforcing fibers embedded in an elastomer or in a thermoplastic, such as inorganic fibers such as glass fibers, and / or organic fibers such as carbon or aramid fibers, or metallic fibers such as steel fibers.
  • the belt-like traction means can have a steel core made of thin wire ropes.
  • the toothed belt has proven to be the preferred form of belt. Toothed belt is to be understood in particular as a belt with teeth on the running surfaces via which the belt is driven.
  • toothed disks or toothed shafts are preferably used as the drive shaft and / or as the deflection shaft of the traction device. Due to the positive force transmission via the teeth, a force transmission from the drive shaft to the belt is possible, particularly even with low pretensioning. Furthermore, slip is largely avoided, in particular due to the meshing of the teeth. It has been found to be particularly advantageous to combine the use of the belt-like pulling device according to the invention with a support column that is elastically supported relative to the hull.
  • a tensioning device in particular a belt tensioning device, for the belt-like traction means, in particular a spring element, such as a spiral spring, can be provided, via which the pretensioning of the traction means can be adjusted.
  • a spiral spring is particularly preferably placed on a threaded rod, a stop being provided at one end of the spiral spring and a nut at the other end of the spring, by means of which the pretensioning of the pulling device, in particular the pulling means, can be adjusted.
  • the pretensioning of the belt-like traction means can be set in a simplified manner via the tensioning device.
  • the tensioning device can be used to dampen impulsively occurring forces by elastic deformation of the tensioning device, in particular the spring element of the tensioning device.
  • the drive unit and the pulling device are coupled to one another in a force-transmitting manner via a force transmission device, preferably a tensioning device is provided for adjusting the tension of the power transmission device
  • a motor with an output shaft is preferably used as the drive unit.
  • a torque is preferably transmitted to the pulling device via the output shaft.
  • the output shaft of the drive unit can function 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 in particular has the potential to save costs.
  • the drive unit and the pulling device are preferably coupled to one another in a force-transmitting manner via a force transmission device.
  • the power transmission device preferably comprises a traction device, such as a circulating chain or a circulating 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 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.
  • the traction means of the power transmission device is preferably in engagement with the transmission means on the drive side and the transmission means on the pulling device side.
  • the drive torque of the drive unit is preferably transmitted to the drive shaft of the pulling 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 pulling device.
  • the power transmission device can transfer the power between the drive unit and Pulling device is transmitted non-positively, in particular via flat belts and shafts with a smooth surface, or positively, in particular via toothed belts with toothed shafts or via chain drives.
  • 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 circulating 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 which is spanned by the two transmission means.
  • the inner circumference of the traction means of the power transmission device is selected to be larger than the circumference spanned by the two transmission means 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.
  • a tensioning device which has at least one tensioning roller, by means of which the circumference spanned by the transmission means and the at least one tensioning roller can be kept constant even during a relative movement between the drive unit and the support column.
  • the tensioning roller of the tensioning device is preferably pretensioned so that in the idle state (no waves or other impulses that could generate a relative movement between the drive unit and the support column) it tensions the power transmission device, while in load states (relative movement between the drive unit and the support column) the relative movement on the power transmission device exerted force pushes the tension pulley back against the bias.
  • the tensioning device is preferably designed in such a way that it provides a substantially constant tension of the force transmission device both in the idle state and in the different load states and / or provides a constant circumference that is spanned by the transmission means and the tensioning roller.
  • the elevator comprises a drive shaft, in particular toothed disk or toothed shaft, of the pulling device, which is attached to the support column and driven by the drive unit, the power transmission from the drive unit to the drive shaft preferably taking place via a power transmission device.
  • the elevator comprises a slip clutch for force-transmitting coupling and decoupling of the traction device with the drive unit, the slip clutch preferably having a slip hub and a slip threshold, the slip hub or the slip threshold preferably forming the drive shaft of the traction device, with the respective remaining slip threshold or slip hub is driven by the drive unit, preferably driven by the drive unit via a power transmission device.
  • the drive shaft of the pulling device is designed as a slip hub of the slip clutch, which is arranged on a slip threshold of the slip clutch.
  • the slip threshold of the slip clutch is preferably formed by the output shaft of the drive unit.
  • the slip threshold of the slip clutch is preferably designed as a separate shaft that is driven by the drive unit via the power transmission device. The transmission of excessively high forces between the drive unit and the pulling device can in particular be prevented by the slip hub.
  • the slip 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 occur.
  • loads are hereinafter referred to as excessively high loads.
  • Excessively high loads can be introduced into elevator components, such as the drive unit and / or the pulling device, for example from the support column and / or the hull.
  • the slip clutch can reduce the flow of force between the drive unit and Drawbar be prevented.
  • an excessively high load that acts on the slip clutch as a result of an impulse emanating from the load carrier can lead to the slip clutch slipping, so that the excessively high load cannot be passed on to the drive unit, so that it is protected from damage.
  • an excessively high load acting on the slip clutch as a result of an impulse emanating from the drive unit can lead to the slip clutch slipping, so that the excessively high load is not passed on to the pulling device, so that it can be protected from damage.
  • traction means with a lower maximum permissible tensile load can be used in particular.
  • the use of a slip clutch facilitates the use of a belt-like pulling device.
  • an elevator preferably comprises a safety gear.
  • the safety device is preferably activated when a maximum travel speed is exceeded in order to brake the travel speed of the load carrier.
  • the safety gear preferably has a measuring device which detects the travel speed of the load carrier and activates the safety gear when a maximum travel speed is exceeded, in particular initiates a braking process.
  • the measuring device preferably comprises a control cable, in particular a steel cable, which is fastened at one end to the load carrier and at the other end is fastened to a freely hanging tensioning weight which tensions the control cable.
  • the regulator rope is preferably deflected between the load carrier and the tension weight via a deflection pulley, in particular through 180 °.
  • the regulator rope is preferably guided along a speed regulator that controls the speed of the The control rope is detected and the braking process is triggered when the maximum travel speed is exceeded.
  • the safety gear preferably has a safety brake that brakes the load carrier.
  • the safety brake is put into a 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 placed in the braking position with the aid of a brake lever.
  • the support column delimits, in particular encloses, transversely to the longitudinal direction a mounting space extending along the column, the support column preferably extending as a rectangular frame in particular around the mounting space, and / or the pulling device at least in sections within the mounting space is arranged.
  • a support column is to be understood as meaning, in particular, a support column that encircles an assembly space.
  • the support column preferably forms a structure that is closed transversely to the longitudinal direction.
  • the section modulus of the support column can be increased, so that the material thickness can be reduced and thus material and weight can be saved.
  • the support column is designed as a jacket structure, within which sensitive elements, such as electronic components and / or movably mounted parts, such as pulleys, can be arranged and in particular protected from damage.
  • the support column delimits an angular, preferably parallelogram-like, particularly preferably rectangular, mounting space transversely to the longitudinal axis.
  • the support column preferably extends as a rectangular frame parallel to the longitudinal axis of the support column.
  • a long side (connecting part) of the rectangular frame is particularly preferably at least 50%, 100%, 150%, 200% or 250% larger than a short side (supporting part) of the rectangular frame.
  • two long sides arranged opposite one another, in particular arranged parallel to one another, and two opposite long sides arranged opposite one another delimit in particular, short periods arranged parallel to one another, the assembly space of the support column.
  • the long sides and the short periods are particularly preferably aligned orthogonally to one another.
  • the pulling device is at least partially guided within the support column.
  • the pulling device is guided centrally in the mounting space encircling the support column.
  • at least two, particularly preferably at least four, deflection rollers are rotatably fastened in the support column.
  • the fact that the pulling device extends at least in sections within the assembly space is to be understood in particular as meaning that the deflection rollers preferably extend at least 50% within the assembly space encircled by the support column and / or that at least 30 percent of the longitudinal extension of at least one pulling device extends within the assembly space the support column extends.
  • the electrical components are preferably guided in the side areas of the mounting space encircled by the support column. Particularly preferably, the electrical components are sandwiched to the left and right of the pulling device inside the support column.
  • the support column is constructed in several parts from interconnected, preferably screwed or welded, column walls, such as support parts and connecting parts, wherein preferably in particular four interconnected, preferably screwed or welded, in particular sheet-like column walls, one in particular rectangular Limit the column section, wherein preferably several column sections are connected along the support column.
  • at least two pillar sections are connected to one another transversely to the longitudinal direction to form the support pillar.
  • the column walls delimiting a column section are arranged offset from one another in the longitudinal direction.
  • the column sections can be interlocked, whereby the strength of the support column can be increased.
  • two opposite column walls of a column section are arranged offset in the longitudinal direction with respect to the remaining column walls of the column section.
  • Column walls connected to one another are preferably arranged offset from one another in the longitudinal direction.
  • Pillar walls in the form of support parts or short sides can preferably be arranged offset from pillar walls in the form of connecting parts or long sides.
  • the column walls are offset from one another over at least 10%, 20%, 30% or 40% of their extent in the longitudinal direction.
  • the support column can preferably be designed in a modular manner from several column sections.
  • support 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 module system, in particular support columns with different widths of the mounting space encircled by the support column can be formed. Furthermore, the strength of the column can be adapted to the load profile of the elevator.
  • the pillar sections themselves are particularly preferably designed in a modular manner from interconnected pillar walls.
  • the support column is preferably formed in several parts, in particular from column walls screwed together, such as support parts and connecting plates. As a result, the support column can be transported more easily and mounted within narrow elevator shafts. Furthermore, the multi-part design of the support column in particular offers the possibility of a modular construction for elevators of different sizes and / or with different load profiles. The replacement of defective parts or parts that have been worn out by corrosion can also be facilitated by the multi-part design.
  • the support column is particularly preferably designed as a sheet metal construction. In particular, the support column includes at least two metal sheets (connecting sheets) aligned parallel to one another and extending in the longitudinal direction.
  • At least two metal sheets are particularly preferably designed as flat sheets and are connected to one another by at least two further, in particular, canted, preferably L-shaped or U-shaped, support parts.
  • the support parts preferably have a greater wall thickness and / or a 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 thereby be avoided, so that in particular the strength of the support column can be increased. As a result, in particular the wall thickness of the supporting and connecting parts to be used can be reduced and material weight can be saved.
  • Electrical components, such as cables and sensors, of the elevator are preferably mounted within the support column.
  • the electronics can be protected in particular from damage.
  • the electronics are particularly preferably preassembled in preassembled column sections. This means that the electrical components can be protected from damage during transport and assembly.
  • the especially hollow interior of the column sections can thus be optimally used.
  • the support column has at least one deflection device which directs a traction device of the traction device from the support column to a drive shaft, in particular the traction device, and directs it from the drive shaft back to the support column, and / or with the drive shaft within or is arranged outside an elevator shaft in which the elevator is mounted.
  • the deflection device comprises a deflection roller for deflecting at least one traction means away from the support column and / or a supply roller for supplying at least one traction means to the support column.
  • a deflecting roller deflects a traction means by about 180 °, in particular by 180 ° ⁇ 30 °, with a supply roller or a deflecting roller the traction means by about 90 ° , in particular by 90 ° ⁇ 30, deflects.
  • Via the drive shaft of the drawbar the at least one traction means, preferably deflected by 180 ° from the deflection roller to the feed roller.
  • at least one traction device preferably two traction devices, of the pulling device can be deflected out of an elevator shaft.
  • the at least one traction means can be driven, preferably outside the elevator shaft, via a drive shaft and be guided back into the elevator shaft via a deflection roller, preferably in the form of the drive shaft.
  • 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 catch frame over which the load carrier is guided along the longitudinal axis of the support column.
  • the catch frame preferably encompasses the support column in sections and / or is in engagement with guide rails which in particular extend 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 understood to mean both directions parallel to the longitudinal axis of the support column.
  • a freight 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 is understood to mean in particular that the load carrier of the goods elevator can be loaded with conveyed goods from this side.
  • 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 has fastening struts which extend parallel to the support column and via which the conveyed goods can be fastened to the load carrier.
  • the load carrier has a framework that covers the carrier base and consists of fastening struts, in particular longitudinal struts and transverse struts, to which the conveyed goods can preferably be attached.
  • the carrier floor can optionally be equipped with rollers or balls that support loading.
  • the load carrier can have walls, preferably can be produced from folded sheet metal profiles or a steel structure.
  • the load carrier can have an upper delimitation wall that functions as a ceiling.
  • the respective delimiting wall for access can be interrupted on one or more access sides.
  • further devices can be attached to the walls of the sides, which can serve as loading sides, such as a table, preferably a roller table, which in particular can preferably be folded in or out.
  • the interruptions in the walls on the access sides to be used as access openings can be closable, preferably by means of one or more doors or by means of a roller blind.
  • a retractable or retractable barrier is conceivable, which is preferably designed as a sheet metal profile.
  • Further elements can be attached to the barrier, for example monitoring devices that serve security. These monitoring devices can be designed to detect, for example, cargo, people and / or other occurrences, for example fire, water, movement, temperature, etc.
  • Various sensors can be used for this, such as optical, acoustic or contact sensors, etc ..
  • the load carrier can have a border running around the carrier base to secure the conveyed goods against slipping.
  • a border is to be understood in particular as a frame extending over at most 100 mm, 80 mm, 60 mm, 50 mm, 40 mm, 30 mm, 20 mm or 10 mm from the support base in the longitudinal direction. Borders that extend higher could, in particular, restrict 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 protection against slipping for transported goods, in particular for transported goods stored in boxes, while accessibility is hardly impaired and can at least be guaranteed via ramps or lifting trucks.
  • the elevator can be designed as a passenger elevator.
  • the load carrier can delimit a closed space for people.
  • the closed people area can have an access via which people can get in and out of the people area.
  • the access can preferably be locked via a door, so that the risk of injury while driving, for example from traction means, counterweights or electrical lines, is avoided or can at least be reduced.
  • the load carrier can provide a space for people extending over at least 1.8 meters, 2.0 meters, 2.2 meters or 2.5 meters in the longitudinal direction, so that people can stand upright on the load carrier.
  • the passenger elevator can have a load capacity of at least 80 kilograms, 100 kilograms, 120 kilograms, 150 kilograms, 200 kilograms, 240 kilograms or 320 kilograms in order to be able to transport at least one, two, three or four people.
  • the suitability of the elevator according to the invention as a passenger elevator can in particular be promoted by the use of counterweights, by means of which the load capacity of the elevator can be increased.
  • the load carrier is preferably limited exclusively on the side facing the support column by a boundary wall parallel to the support column. It should be clear that fastening struts which delimit or encircle a side from which the load carrier can be loaded and unloaded do not represent a delimitation wall in the sense of the present invention.
  • the accessibility of at least one, preferably at least two or three, sides is realized in particular that the load carrier is guided in an elevator shaft in which at least one, preferably on each floor, at least one, preferably at least two or three, accesses to the Elevator shaft are provided which are dimensioned such that the conveyed goods can be loaded onto and unloaded from the load carrier.
  • the invention also relates to an elevator system, in particular a goods elevator system, such as an ammunition elevator system or a provisions elevator system, and / or a passenger elevator system.
  • the elevator installation comprises an elevator according to one or more of the embodiments described above and below and an elevator shaft in which the support column is arranged at least in sections.
  • the at least section-wise arrangement of the support column in the elevator shaft is to be understood in particular to mean 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.
  • 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 passages, introduced into the elevator shaft wall.
  • the elevator shaft can be square, in particular rectangular, and delimited by four shaft walls.
  • the elevator shaft can be formed in the hull of a ship.
  • the support column can be fastened to a shaft wall extending in the longitudinal direction and / or to a shaft bottom, in particular be elastically supported.
  • the support column can be firmly attached to a shaft wall in such a way that no pivoting movement of the support column relative to the shaft wall is permitted. It is clear that relative movements of the support column relative to the shaft wall as a result of an elastic support of the support column on the shaft wall should not be understood as a pivoting movement.
  • the elevator shaft can be open at one end in the longitudinal direction so that the load carrier can move out of the elevator shaft.
  • the support column can protrude from the elevator shaft in sections through an opening in the elevator shaft.
  • the present invention further relates to a ship with an elevator according to one or more of the embodiments described above and below or with the elevator system described above.
  • the elevator shaft can be formed in the hull.
  • the elevator shaft can be open towards the ship deck, so that the load carrier can be moved out of the hull to the ship deck.
  • 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.
  • the ship can be a ship with guns, such as cannons, and / or gun turrets.
  • the ship can weigh 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.
  • the drive unit is elastically supported on the hull.
  • the drive unit can also be rigidly attached to the support column, which is preferably supported elastically on the hull.
  • the drive unit can be attached to a part of the ship other than the support column, and the drive force is transported to the support column via a power transmission device. The fact that the drive unit is supported on another part of the ship results in a decoupling. This is advantageous as it allows a different attachment to be used.
  • the elevator furthermore comprises a tensioning device for adjusting the tension of the power transmission device.
  • the tensioning device can in particular compensate for a relative movement between elevator components such as the drive unit, the support column, the load carrier and / or the pulling device.
  • Relative movements between elevator components can occur in particular as a result of elastic support of two components, in particular via elastic connecting elements, relative to one another.
  • An elastic support of two components relative to one another can in particular take place via a direct elastic support of one component on the other component or via a separate elastic support of two components, for example via separate elastic connecting elements.
  • the belt-like pulling device has at least one belt or a toothed belt
  • the elevator further comprises a toothed pulley or toothed shaft attached to the support column, which is driven by the drive unit and which drives the pulling device, and a belt tensioning device for each belt or toothed belt to adjust the tension of the respective belt or toothed belt.
  • the use of belt tensioning devices is advantageous in order to keep the power flow constant.
  • the power is transmitted from the drive unit to the toothed disk or toothed shaft via a further pulling device, in particular a chain.
  • the elevator further comprises a slip clutch for the further pulling device and / or a further tensioning device for adapting the tension of the further pulling device.
  • the support column consists of at least two support parts with at least one connecting plate in between. This configuration has a positive effect on the stability of the support column.
  • the support parts each consist of several parts. This makes the support parts easier to transport and to bring inside the ship to be assembled there. Furthermore, individual parts that have been damaged can be replaced more easily.
  • At least two parts are connected to one another, in particular screwed, in such a way that the column is widened compared to the other exemplary embodiments, in particular in the horizontal direction. This advantageously also increases the stability and use of space, which leads to advantages in particular with higher payloads.
  • the support column has at least one deflection device in order to deflect the forces applied via the pulling device.
  • the deflecting device preferably has at least one in particular smooth discharge 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 jacket, ie a tooth-free outer jacket. The redirection of the drive forces applied by the pulling device enables more flexible positioning of the drive unit and support column inside the ship.
  • the support column is elastically supported with respect to the hull. Due to the elastic support of the support column on which the load carrier is attached, the forces that occur are dampened and their effect on the elevator, the load carrier and thus also on the goods to be conveyed is reduced.
  • An elastic support of the support pillar with respect to the hull is preferably to be understood as the attachment of the support pillar to the hull via elastic connecting elements.
  • impulsive forces that are transmitted from the hull to the support column are 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 supported via elastic connecting elements.
  • the elastic support is to be understood in particular as an elastic support which ensures a minimum amount of relative movement of the support column relative to the hull.
  • the elastic support 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 by up to 10 mm, 20 mm, 30 mm, 40 mm, 50 mm due to particularly large, impulse-like forces mm or 60 mm can be moved relative to the hull.
  • the elastic support preferably takes place in such a way that the relative movement between the support column and the hull can take place in at least two, preferably in three, directions, in particular cardinal points.
  • wire rope spring elements as the elastic connecting elements, which in particular allow elastic deformation in several directions.
  • Wire rope spring elements preferably have two connecting sections to Fasten, in particular screw, the wire rope spring elements to the 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 curved-section-shaped, wire ropes.
  • the elastic connecting elements, in particular the wire ropes of the wire rope spring elements are preferably made from stainless steel ropes. Compared to conventional steel cables or elastomer dampers, these have, in particular, a greater deformability for shock absorption and improved vibration damping. In particular with regard to the increased risk of corrosion in ships, the use of stainless steel cables for the elastic connecting elements has proven advantageous.
  • the elastic connecting elements are preferably designed as shock absorbers and vibration absorbers.
  • An example of such shock and vibration absorbers are wire rope spring elements.
  • these have low natural frequencies.
  • wire rope spring elements have in particular a resonance overhaul of 150% to 450%, in particular from 250% to 350%, as a result of which in particular an oscillation of the support column quickly subsides after a pulse-like impact.
  • the elastic connecting elements used preferably have a deflection travel of at least 2 mm, 4 mm or 6 mm and / or of at most 8 mm, 10 mm or 12 mm under a load of 430 kilograms.
  • 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 elastic connecting element is preferably at least 10 kN, 14 kN or 16 kN and / or at most 25 kN, 30 kN or 35 kN.
  • the maximum spring travel 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 in particular the CAVOFLEX product data sheet from Willbrandt Gummitechnik.
  • the use of wire rope spring elements of the type H160-267-100-125-8 has proven to be particularly advantageous.
  • a downward support can also be attached in a pit located 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.
  • the support column can be supported elastically on the floor of the elevator shaft.
  • the elastic support of the support column on the hull dampens the impulsive forces so well that the drive unit can be rigidly connected to the support column and can be adequately protected against impulsive forces simply by the elastic attachment of the support column to the hull .
  • the drive unit is therefore rigidly connected to the support column.
  • a rigid connection is to be understood in particular as a connection of this type, in particular screwing, welding, gluing or some other connection, between the drive unit and the support column, which essentially results in a relative movement between the support column and the drive unit prevented. Essentially only means that small relative movements as a result of assembly play or low elasticity, the support column, the drive or connecting elements that are inherent in even the most rigid material should also be included in this embodiment of a rigid connection.
  • a 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 pulling device, since essentially no relative movements occur between the drive unit and the pulling device.
  • 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 hull.
  • the elastic support preferably takes place via elastic connecting elements, such as wire rope spring elements.
  • both the support column and the drive unit are elastically supported with respect to the hull.
  • the drive unit and the support column are elastically supported in relation to the hull independently of one another, in particular separately. It has proven to be particularly advantageous to support both the drive unit and the support column elastically on 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 elevator shaft wall. 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 been found to be particularly preferred to provide a recess in the common elevator shaft wall, via which the pulling device can be coupled to the drive unit through the elevator shaft wall.
  • a pulley of the pulling device preferably projects through the recess onto the other side of the elevator shaft walls on which the Drive unit is elastically supported.
  • At least one traction means is preferably guided via this pulley 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 pulleys and back to the side of the elevator shaft wall guided 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 support column is elastically supported on the hull via elastic connecting elements; wherein the elastic connecting elements are preferably spring elements, in particular wire rope spring elements.
  • the elastic support allows a relative movement of the support column in at least two, preferably in at least three, directions.
  • the drive unit is elastically supported on the hull.
  • the drive unit can be supported elastically against a part of the ship other than the support column.
  • the drive unit can be rigidly attached to the support column.
  • hull is to be interpreted broadly in connection with the present invention.
  • the hull is not to be understood exclusively as the hull or the hull, which gives the ship its buoyancy. Rather, the hull is to be understood as the ship structure, which in particular includes ship walls, such as floors, ceilings and / or elevator shaft walls.
  • the elastic support of the support column is particularly preferably carried out on an elevator shaft wall. It is clear that the support column in particular is not to be understood as part of the hull.
  • the elevator can have a counterweight which is coupled to the load carrier in such a way that a 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 means 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.
  • the lifting 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 drive-free drive described below, as the drive torque of such drives can usually not be applied as high as desired, so that more powerful drives would be required for an increased load without a counterweight.
  • 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 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.
  • the at least one pulling means coupling the load carrier to the counterweight can be designed as a pulling means separate from the pulling device, in particular as a wire rope, chain or belt pulling means.
  • the balance weight can also be referred to as a counterweight.
  • the use of a counterweight can be combined with an endless belt.
  • an endless belt is to be understood in particular as a belt which is fastened at both ends to the load carrier. 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.
  • the at least one separate traction means coupling the load carrier to the balance weight can also be referred to as a compensating traction means.
  • the at least one compensating traction device can have one end on the load carrier and be attached at the other end to the balance weight.
  • the compensating traction means can be deflected between the load carrier and the counterweight via at least one deflection roller.
  • the pulley can be attached to the support column or to a shaft wall.
  • 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 counterbalance weight or at least two separate counterbalance weights.
  • the at least one pulling means can be a pulling means of the belt-like pulling device.
  • the traction means can be formed by the at least one belt-like traction means described above.
  • the traction means coupling the load carrier with the counterweight can be integrated into the traction device.
  • the at least one belt-like traction means can be fastened with one end to the load carrier, for example via the rocker or belt tensioning device described above and below, and with the other end to the counterweight.
  • the at least one traction means preferably extends from the load carrier to a deflection roller, from where the at least one traction means is deflected to the drive shaft of the traction device.
  • the at least one traction means 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 150 ° to 210 °, in particular by 180 °, via at least one deflection roller.
  • the at least one traction device can be deflected by 150 ° to 210 °, in particular by 180 °, via a pulley between the load carrier and drive shaft, or by at least two pulleys by 75 ° to 105 °, in particular 90 °, each.
  • the at least one traction means 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 in particular mean the weight of a load-bearing platform of the load carrier, a frame surrounding the platform and / or other components moving with the load carrier.
  • the weight of the load carrier is to be understood as the weight of the load carrier in the unloaded state.
  • 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 load weight.
  • the counterweight can be at least 20%, 40%, 60%, 80%, 100%, 120%, 140% or Balance 150% of a predetermined load weight.
  • the drive power required to drive the load carrier can be further reduced, even in the loaded state, and thus the energy consumption and / or the space requirement of the drive unit can be reduced.
  • the counterweight is arranged at least in sections within a counterweight receptacle bounded by the support column.
  • the counterweight receptacle can be enclosed by the support column in sections or completely transversely, in particular orthogonally, to the longitudinal direction.
  • the section-wise arrangement of the counterweight in the counterweight receptacle delimited by the support column can, in particular, reduce the space requirement of the support column.
  • 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.
  • the counterweight receptacle can be limited by at least one third column wall, which connects the two opposite column walls to one another.
  • the at least three column walls can have a U-shaped wall section Form support column.
  • the area bounded 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 enclosed in sections by the support column.
  • a fourth pillar wall can be arranged opposite the third pillar wall in such a way that the at least fourth pillar walls of the support pillar form an, in particular, rectangular frame surrounding the counterweight receptacle.
  • 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.
  • the support column can extend around the assembly space as a closed or at least partially closed frame.
  • the frame can be rectangular.
  • the counterweight can be arranged completely 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 the assembly space.
  • the counterweight receptacle can be designed separately from the assembly space.
  • the inside of the column walls can delimit an assembly space.
  • the column walls can limit the counterweight receptacle from in particular at least three sides.
  • the counterweight mount 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.
  • the counterweight in particular can be arranged in sections in the counterweight receptacle and in sections outside the counterweight receptacle.
  • at least 20%, 40%, 60%, 80%, 90% or 100% of the counterweight can be arranged within the counterweight receptacle.
  • the respective remaining portion of the counterweight can be arranged outside the counterweight receptacle.
  • the force application point of the counterweight can be shifted to the force application point of the load carrier.
  • an improved load distribution compared to the support column can be achieved in particular, 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 reduced space requirement for the counterweight. Arranging the counterweight in sections in the counterweight receptacle has proven to be a surprisingly good compromise between these two advantages. Depending on the requirements for the load and the installation space of the elevator, however, it has also turned out to be advantageous to arrange the counterweight either completely inside the support column or completely outside the support column.
  • 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.
  • 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.
  • the guide means of the counterweight can be offset with respect 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.
  • the guide means of the counterweight and the guide means of the load carrier can be attached to separate column walls.
  • 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.
  • the column walls, in which the guide means of the counterweight are attached can be arranged between the column walls to which the guide means of the load carrier are attached.
  • the at least one arranged between the load carrier and the counterweight can Deflection roller be arranged offset to the at least one deflection roller arranged between the load carrier and the drive shaft.
  • the at least one deflection roller of the compensating traction device can be offset towards the load carrier with respect to the deflection roller of the at least one traction device.
  • the pulling device is designed as a pulley block in order to reduce a drive force required to drive the load carrier.
  • the load carrier can be coupled to at least one traction means of the traction device via a loose deflection roller.
  • one end of the at least one traction means can be firmly attached 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 loose deflecting roller and extend from the loose deflecting roller to a fixed deflecting roller.
  • a fixed deflection roller can be understood to mean a deflection roller that is firmly attached to the support column, a shaft wall or another wall of a ship's hull.
  • a loose deflection roller is to be understood as a deflection roller which is movable with respect to the fixed deflection roller.
  • the pulling device By designing the pulling device as a pulley block, the drive force required to drive the load carrier can in particular be reduced.
  • the embodiment with a pulley block can in particular be combined with the embodiment described above with a counterweight integrated into the pulling device.
  • the counterweight can be attached to a loose deflection roller which is coupled to the at least one traction means of the traction device.
  • the other end of the at least one traction means of the traction device can also be firmly attached to the support column, a shaft wall or another wall of a ship's hull.
  • the at least one pulling means can extend from this fixed end to the loose deflecting roller and from the loose deflecting roller to a further fixed deflecting roller.
  • the required drive force in particular the required drive torque, for driving the load carrier can be reduced.
  • the drive unit can be reduced in size with the same payload or the payload can be increased with the same drive unit.
  • the load on the pulling device can be reduced, so that the load capacity can be increased with the same pulling means or the pulling means can be made smaller or made from less resilient but cheaper material with the same load.
  • a reduction of 2: 1 is preferably achieved with the pulley system. This is to be understood in particular as the fact that the drive force required to drive the load carrier is reduced in that the at least one traction means must be driven over twice the distance for the same path of the load carrier.
  • the design of the pulling device as a pulley block has proven to be particularly advantageous in combination with the gear drive-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 U / min to 150 U / min, in particular from 40 U / min to 90 U / min.
  • the particular advantage of using a synchronous motor is that it can provide lower speeds in favor of higher torques compared to an asynchronous motor with speeds of around 1500 rpm. As a result, the required reduction ratio of the speed for providing a sufficiently high torque for driving the load carrier can be significantly reduced compared to an asynchronous motor.
  • gear drives in particular spur gear drives and / or planetary drives, which can provide a large reduction ratio, can be dispensed with.
  • the drive unit is coupled to the pulling device without a gear transmission, in particular by means of pulling means.
  • the drive unit can be coupled to the pulling device via a traction device, in particular via a traction device of the power transmission device described above and below.
  • the output shaft of the drive unit can also be coupled directly to the traction means of the drive unit.
  • 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.
  • the reduction ratio is preferably approximately 2/1. It has been found that particularly high reduction ratios of the speeds lead to large losses in efficiency, so that the efficiency of the power transmission through the use of drive units with high output torques and low speeds, such as synchronous motors, is preferred over drive units with high speeds and small output torques, such as asynchronous motors .
  • the inventors of the present invention have found that it is therefore particularly advantageous to combine the counterweights described above and below with the use of a synchronous motor, a gear-free coupling and / or a small reduction ratio of the speed.
  • a high degree of efficiency can be achieved and, on the other hand, the load capacity can be increased even with small drives.
  • FIG. 1 shows an assembly 1000 of the belt type puller 420 of the present invention.
  • the belt-like pulling device 420 can consist of one or more preferably parallel parts. These parts can be designed identically or differently. A conceivable design of different parts could provide one or more main parts, which are supplemented by one or more support parts.
  • the support parts can also be configured identically to one another or differently.
  • Each part can consist of one or more sections that are permanently or detachably connected to one another. This has the advantage that if a section is damaged, the entire part does not have to be replaced. In addition, when the sections are detachably connected, it is advantageous not to remove the entire part from the arrangement, but rather only the damaged section.
  • the belt-like pulling devices 420 are guided in the arrangement 1000 over deflecting rollers 1020, 1035 and diverting or feed rollers 1030.
  • the upper and lower pulleys 1020 are always present.
  • the diverting or feed rollers 1030 are an optional possibility if the drive of the belt-like pulling device 420 is to be placed in front of the arrangement 1000.
  • each of the deflection rollers 1020, 1035 can also be used to transmit power to the belt-like pulling device 420.
  • a fastening option 1040 to which the load carrier can be fastened to the belt-like pulling device 420.
  • the load carrier is fastened to the fastening option 1040 in such a way that the force is applied via the belt-like pulling device 420 to the Load carrier can be transferred.
  • an attachment option 1050 At the end of the belt-like pulling device 420 facing the lower end of the load carrier there is an attachment option 1050.
  • the load carrier can be elastically connected to the attachment option 1050. This can be effected via tension springs or also via a further belt-like device that has a greater elasticity than the belt-like pulling device 420 itself.
  • 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 rotatably connected to the load carrier (not shown) 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.
  • belt tensioning device 1050 and rocker 1045 are in connection with the Figures 7a to 7e described in detail.
  • Fig. 2 shows an arrangement 1000 of the belt-like pulling device 420 together with a drive unit 410 and a load carrier 310.
  • the load carrier 310 can be fastened to the ends of the belt-like pulling device as described above.
  • the load carrier 310 can be designed as an open or closed cabin.
  • the load carrier 310 can also consist only of a base plate, or of a base plate with a surrounding border directly on the base plate.
  • one or more completely or partially circumferential securing devices that are spaced apart from the base plate can also be provided. These can be designed as simple rods, tubes, ropes, plates or the like.
  • the drive unit 410 can be an electric motor or a motor that is powered by fuel, such as gasoline, diesel or LPG.
  • fuel such as gasoline, diesel or LPG.
  • a hybrid engine that combines both types is also conceivable.
  • the drive unit 410 can be seen attached to a fixed part, such as the wall of a ship's hull. This attachment can optionally be effected via elastic mountings 110. This has the advantage that forces acting on the ship are not transmitted to the drive unit 410, or are at least reduced.
  • An output shaft 2020 of the drive unit is driven by the force generated by the drive unit 410. This is transmitted to the deflecting roller 1035 via a force transmission device 2030, as with reference to FIG Figures 6a to 6d is explained in more detail below. Alternatively, the force could also be transmitted to one of the other deflection rollers 1020, 1035, and the illustration is to be understood only as a schematic.
  • the force transmission device 2030 can be designed as chains, ropes, for example made of steel, shafts or belts.
  • a tensioning device 2050 for adapting the tension of the force transmission device 2030 can advantageously also be provided here.
  • an offset can be compensated that can arise because the elevator with the arrangement 1000 is mounted differently than the drive unit 410, and the forces acting on the ship act differently on the arrangement 1000 and the drive unit 410, which could result in an offset which can then be compensated for by the tensioning device 2050.
  • Fig. 3 shows a support column 100 to which the arrangement 1000 is attached to act as an elevator.
  • the support column can advantageously be attached elastically to a hull of a ship via the elastic mountings 110.
  • the support column 100 can be installed in all types of ships.
  • the size of the elevator and thus the support column 100 can be adapted to the size of the ship.
  • the support pillar 100 can also be attached to components of a ship that are later assembled to form a ship or that are available as replacement components. Forces that act on the ship are weakened and possibly even completely intercepted via these elastic mountings, so that the support column 100 and the remaining parts of the elevator as well as any conveyed goods 350 located therein are exposed to little or no forces.
  • the number and type of attachment of the bearings 110 to the support column 100 can be implemented in various ways. The option shown is only an exemplary embodiment.
  • elastic landing buffers 120 are formed in the area of the lower end of the support column.
  • the support column 100 shown is only an example.
  • the proportions as well as the number of bearing points are adapted for the respective mounting location on board a ship.
  • a different number of bearing points is necessary.
  • the overall size of the ship can also affect the number of storage points required.
  • the type, quantity and weight of the conveyed item 350 to be transported can also influence the number of long points.
  • the support column 100 can be constructed in various ways.
  • Figure 4a shows a plan view of a support column 100 according to an embodiment.
  • Figure 4b shows a plan view of a schematic structure of a support column 100 in cross section.
  • the support column 100 can for example consist of at least two support parts and at least one connecting plate.
  • the shape of the support parts can have different characteristics.
  • the support parts 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 cutouts which, on the one hand, can reduce the total weight and, on the other hand, enable or facilitate access to elements attached in the interior of the cavities that are created, such as lines, operating parts or fastenings.
  • the deflection pulleys 1020 shown represent an embodiment for a two-part belt-like pulling device.
  • the at least two support parts are connected to at least one connecting plate.
  • the connecting plates can have cutouts which, on the one hand, can reduce the total weight and, on the other hand, enable or facilitate access to elements attached in the interior of the cavities that are created, such as lines, operating parts or fastenings.
  • a support column 100 is to be understood in particular as a support column 100 surrounding an assembly space 500.
  • the support column 100 preferably forms a structure that is closed transversely to the longitudinal direction.
  • the section modulus of the support column 100 can in particular be increased, so that the material thickness can be reduced and material and weight can be saved.
  • the support column 100 is designed as a jacket 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 from damage.
  • the support column 100 delimits an angular, preferably parallelogram-like, particularly preferably rectangular, mounting space 500 transversely to the longitudinal axis L.
  • the support column 100 preferably extends as a rectangular frame parallel to the longitudinal axis L of the support column 100.
  • a long side 210 (connecting part) of the rectangular frame is particularly preferably 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 mounting space 500.
  • the long sides 210 and the short periods 200 are particularly preferably aligned orthogonally to one another.
  • the support column 100 is preferably formed in several parts, in particular from column walls 200, 210 screwed to one another, such as support parts 200 and connecting parts 210. This allows the support column in particular Easier to transport and assemble 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 the case of ships in particular, the elevator shaft can be open towards 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 replacement of defective parts or parts that have been worn out by corrosion can also be facilitated by the multi-part design.
  • the support column 100 is particularly preferably designed as a sheet metal construction.
  • 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 sheets and are connected to one another by at least two further, in particular canted, preferably L-shaped or U-shaped, support parts 200.
  • the support parts 200 preferably have a greater wall thickness and / or a greater material strength than the connecting plates 210.
  • the long side 210 (connecting part) of the support column is formed from flat metal sheets, while the short side 200 (support part) of the support column 100 is formed from U-shaped metal sheets.
  • support parts 200 and connecting parts 210 to the support column 100 are preferably connected to one another via screws 530.
  • welding stresses in particular can thereby be avoided, so that in particular the strength of the support column 100 can be increased.
  • the wall thickness of the supporting and connecting parts to be used can be reduced and material weight can be saved.
  • Figure 15 shows a section of a support column 100, which is constructed 210 in several parts from column walls 200, 210 screwed together in the form of support parts 200 and connecting parts.
  • two interconnected support parts 200 and connecting parts 210 each delimit a rectangular column section.
  • a plurality of column sections are connected longitudinally (in the longitudinal direction L) to the support column 100.
  • the column walls 200, 210 each delimiting a column section are arranged offset from one another in the longitudinal direction L.
  • projecting support parts 200 realized a toothing of the column sections, whereby the strength of the support column can be increased.
  • the support parts 210 are each offset by approximately 40% of their longitudinal extent with respect to the connection parts 200.
  • the pulling device is at least partially guided within the support column.
  • the pulling device is guided centrally in the mounting space 500 encircling the support column.
  • at least two, particularly preferably at least four, deflection rollers 1020 are rotatably fastened in the support column 100.
  • the deflecting 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 regions 540 of the assembly space 500 encircled by the support column 100.
  • the support column 100 preferably forms cable ducts in the side regions 540 for guiding cables.
  • Support points 130 can be seen, via which the support column 100 can be elastically supported on the hull.
  • elastic connecting elements 110 are used for the elastic support of the support column on the hull, as shown schematically in FIG Figure 4a indicated.
  • Wire rope 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 hull and to the support column 100.
  • the connecting sections 140 of the elastic spring elements 100 are connected to the support points 130 in a particularly rigid manner, 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, in particular curved-section-shaped, wire cables 150.
  • the load carrier 310 particularly preferably has a catch frame 330, over which the load carrier is guided along the longitudinal axis L of the support column 100.
  • the catch frame 330 preferably encompasses the support column 100 in sections and / or is in engagement with guide rails 340, which in particular extend on opposite sides of the support column 100 along the longitudinal axis L of the support column 100.
  • the catch frame 330 is preferably U-shaped and one leg in each case is in engagement with a guide rail 340.
  • Fig. 5 shows an exemplary structure of an elevator 300 with a support column 100 and support points 130 for an elastic support of the support column on the hull 110 or for a rigid attachment of the support column to the hull.
  • a load carrier 310 is attached to the support column 100 such that it can move longitudinally.
  • the load carrier 310 can be embodied in various ways, as above in connection with FIG Fig. 2 explained.
  • 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 points 320 can be constructed in such a way that transport containers equipped with rollers can be pushed out or rolled out. Docking points 320 with thresholds may be used to prevent accidental slipping or rolling out. It is also possible to use loading points 320 in which an extendable and retractable sleeper can be used, so that there is protection against accidental rolling or slipping out, but does not represent any additional hindrance for loading and unloading when it is sunk. Other ways of securing are also conceivable. Loading points 320 may have a door that can be locked and locked. Loading points 320 can 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 even magnetically, so that the load is secured during transport and before and during loading and unloading.
  • a motor with an output shaft 2020 is preferably used as the drive unit 410.
  • a torque is preferably applied to the output shaft 2020 via the Pulling device 420 transferred.
  • the output shaft 2020 of the drive unit 410 can function 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 holds, in particular, potential for cost savings.
  • the drive unit 410 and the pulling 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 comprises 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.
  • the power transmission device 2030 particularly preferably comprises a transmission means 2021 (transmission point), in particular in the form of a gearwheel, on the output shaft 2020 of the drive unit 410 and / or a transmission means 1036, in particular in the form of a gearwheel, on the drive shaft 1035 of the traction device 420 Traction means 2040 of the power transmission device 2030 each in engagement with the drive-side and the traction device-side transmission means 1036, 2021.
  • the drive torque of the drive unit 410 is preferably transmitted to the drive shaft 1035 of the pulling device 420.
  • the traction device 2040 of the power transmission device 2030 preferably runs around the transmission device 2021 of the output shaft 2020 of the drive unit 410 and the drive shaft 1035 of the pulling device 420.
  • the inner circumference of the force transmission device 2030 is preferably greater than the circumference spanned by the two transmission means 1036, 2021, ie the inner circumference that a traction means circulating 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 which is spanned by the two transmission means 1036, 2021.
  • the inner circumference of the traction means 2040 of the force transmission device 2030 is selected to be larger than the circumference spanned by the two transmission means 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.
  • a tensioning device 2050 is preferably provided, which has at least one tensioning roller 2051, via which the circumference spanned by the transmission means 1036, 2021 and the at least one deflection roller even during a relative movement between the drive unit 410 and the support column 100 can be kept constant.
  • FIGS. 6a to 6d show a particularly preferred embodiment in which both the support column 100 and the drive unit 410 are elastically supported with respect to the hull.
  • the drive unit 410 and the support column 100 are supported independently of one another, in particular separately, elastically relative to the hull. It has proven to be particularly advantageous to support both the drive unit 410 and the support column 100 elastically on an elevator shaft wall 160, in particular on the same elevator shaft wall 160. It has proven to be particularly advantageous to mount the support column 100 and the drive unit 410 on different sides of the elevator shaft wall 160.
  • a deflection roller 1035 of the pulling device 420 preferably projects 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 means is guided 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 is particularly preferred, as in FIG Figures 6a to 6d shown as a drive shaft 1035 of the pulling device 420, which is driven by the drive unit 410.
  • the Figures 6a to 6d show an exemplary structure of a drive unit 410.
  • the drive unit 410 can, as in connection with FIGS Figures 8a to 8c shown, are elastically supported at various positions on the hull.
  • the drive unit 410 power is generated electrically or otherwise 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 force transmission device 2030 takes the force and passes it on to the further transmission point 1036 on the deflection roller 1035, which serves as a drive shaft.
  • the tensioning device 2050 for adjusting the tension of the force transmission device 2030, as described above, can also be seen.
  • another of the deflection pulleys 1020, 1035 can be used as the drive shaft.
  • the power transmission device 2030 can be designed as chains, ropes, for example made of steel, shaft or belt-like, these are limited Figures 6a to 6d thereupon to show a possibility of the transmission points 2021 and 1036 with gears that are suitable for a chain.
  • Fig. 6d there are also diverting and supply rollers 1030 of a deflection device.
  • Figures 7a to 7e show the possibility of fastening 1050 the belt-like pulling device 420 to the load carrier 310. As described above, the two-part design of the belt-like pulling device 420 is only one of the possibilities. Further guide rollers 1080 are shown for guiding the belt-like pulling device 420.
  • FIGS 7a to 7e show Figures 7a to 7e 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 for one end 1047 of the two traction means 430 in the form of a rocker 1050.
  • the rocker 1050 is attached to the fastening device 1060 in a rotatable manner via a pivot bearing 1045 with an axis of rotation 1046.
  • the ends 1047 of the traction means 430 connected to the rocker are in particular shown in FIG Figure 7a and 7c to see.
  • FIG 16 shows a schematic representation of a rocker 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.
  • a detection device 4000 in the form of a position switch 4000 is also 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 is in engagement with an edge 4030 of the rocker 1040 which is inclined with respect to an orthogonal to the translational movement axis of the shaft 4010.
  • the at least one rocker 1040 can, as in the Figures 16 to 18 shown, be triangular. Triangular does not necessarily mean that the rocker has to have pointed corners. As in particular in the Figures 16 to 18 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 attached in the area of the other corners. As in particular from the Figures 19a to 19c As can be seen, the rocker 1040 can also have shapes that differ from a triangular shape.
  • Figure 17 shows an embodiment with three belts 430.
  • the use of at least three belts 430 may be necessary, particularly when the load carrier is heavily loaded.
  • the three belts 430 are coupled to the load carrier via two rockers 1040, 4040.
  • a first rocker 1040 is designed as a main rocker.
  • the main rocker is rotatably connected to the load carrier via the pivot bearing 1045.
  • the second rocker 4040 is designed as a lower rocker 4040, which is attached to the main rocker 1040 in a rotatable manner.
  • the lower rocker 4040 is attached to the main rocker 1040 in a rotatable manner via a pivot bearing 4045.
  • One of the three traction devices 430 is attached to the main rocker 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 in the event of tearing, slackening and / or uneven loading of the traction means, the traction means are spaced apart from the respective pivot bearing 1045, 4045 via a lever arm.
  • the pivot bearing 4045 of the lower rocker is also spaced apart from the pivot bearing of the main rocker 1045 by a lever arm.
  • two detection devices 4000 are used.
  • One of the detection devices 4000 is in engagement with the main rocker 1040.
  • the other of the detection device 4000 is in engagement with the lower rocker 4040.
  • an uneven load between the traction means 430 attached to the lower rocker 4040 can be detected.
  • an uneven load can be detected between the pair of pulling means 430, which are attached to the lower rocker 4040, and the pulling means 430, which is attached to the main rocker.
  • Figure 18 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 rockers 4040 are designed as lower rockers, each of which is attached to the main rocker in a rotatable manner via a pivot bearing 4045.
  • Two traction means 430 are attached to each of the two lower rockers 4040.
  • a detection device 4000 for detecting a movement of the main rocker 1040 and two further detection devices 4000 for detecting relative movements of the lower rocker 4040 to the main rocker 1040 are provided.
  • FIG. 10 shows a perspective view of a rocker 1040 with position switch 4000, which is in engagement with rocker 1040 through a recess 4050 in a frame 4060 surrounding rocker 1040.
  • Figure 19b FIG. 10 shows rocker 1040 according to FIG Figure 19a with a portion of the frame 4060 shown through.
  • FIG. 11 shows a front view of the rocker 1040 according to FIG Figure 19a and Figure 19b .
  • the two traction means 430 connected to the rocker 1040 are in the Figures 19a to 19c shown cut off.
  • the traction means 430 are fastened to the rocker 1040 via clamping devices 4070.
  • the clamping devices each include 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.
  • the traction means 430 are designed as toothed belts with a corresponding traction means profiling 435.
  • one of the clamping jaws 4080 has a profiling that is adapted to the traction means profile 435.
  • the clamping devices 4070 are rotatably attached to the rocker 1040 via pivot bearings 4100.
  • the rocker 1040 is in turn attached to the load carrier in a rotatable manner via a pivot bearing 1045.
  • the rocker 1040 comprises two rocker jaws 1049, between which a clamping jaw 4090 of the clamping devices is fastened. As from the Figures 19a to 19c As can be seen, the rocker 1040 and / or the rocker jaws 1049 can be designed triangularly 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 recess is formed in which the sensor 4020 is mounted.
  • the sensor 4020 is displaced translationally as a result of a rotary movement of the rocker 1040, as a result of which the position switch 4000 can be actuated.
  • the fastening device 1060 has two fastening options 1050 for the other end 1048 of the two traction means 430 in the form of belt tensioning devices 1050.
  • the preferred belt tensioning device 1048 for the traction means 430 is a spring element 1051 in the form of a spiral spring 1051, via which the pretensioning of the traction means 430 can be adjusted.
  • the spiral spring 1051 is placed on a threaded rod, with a stop 1052 at one end of the spiral spring 1051 and a stop 1052 at the other end Spiral spring a nut 1053 is provided, via which the pretension of the traction means 430 can be adjusted.
  • FIG. 7a and 7c is through the wavy lines the section through the in the Figures 7a to 7d shown traction means shown.
  • the traction means 430 preferably extend from these cutting lines, as in FIG Figures 1 , 8a to 8c and 9 shown along the support column 100.
  • the end 1048 of the traction means 430 connected to the belt tensioning device 1050 is shown, preferably S-shaped, via two rollers 1080, 1090, in particular via a toothed pulley 1080 and a smooth roller 1090, to the respective belt tensioning device 1050.
  • the Figures 8a , 8b and 8c show an elevator 300 with different mounting positions of the drive unit 410 according to an embodiment.
  • the Figure 8a the option of the support column 100, which is elastically supported with respect to a part of the hull, the support column 100 being supported by elastic bearings 110.
  • the load carrier 310 is attached to the support column 100 so that it can move longitudinally.
  • the force generated by the drive unit 410 is transmitted via the output shaft 2020, the power transmission device 2030 and the pulley 1020, which operates as an output shaft and which is located here at the upper end of the support column 100, to the between the upper end and the lower end to the one along the support column 100 guided pulling device 420 delivered.
  • the drive unit 410 is in Figure 8b elastically supported against another part of the ship than the support column 100, and the force generated by the drive unit 410 is transmitted via the output shaft 2020 and the force transmission device 2030 to the drive shaft 1035 of the pulling device 420 guided between the upper end and the lower end of the support column 100 .
  • the pulling device 420 comprises two deflection rollers 1020 for guiding the pulling device 430 along the pulling device 420.
  • the pulling device 420 also comprises FIG Figure 8b and in Figure 1 a deflection device 1010, each with a deflection roller 1030 for deflecting the traction means away from the support column 100 and a supply roller 1030 for supplying the traction means to the support column 1030
  • a deflecting roller 1020 and a feed roller 1030 or a deflecting roller 1030 should in particular be that a deflecting roller 1020 deflects a traction means by about 180 °, in particular by 180 ° ⁇ 30 °, with a supply roller or a deflecting roller reversing the traction means deflects about 90 °, in particular by 90 ° ° ⁇ 30.
  • the at least one pulling means 420 is deflected by 180 ° from the deflecting roller 1030 to the supplying roller 1030.
  • the drive shaft 1035 can be designed as toothed shafts.
  • the drive unit 410 is in Figure 4c elastic against another part of the ship, here the floor, supported as the support column 100, and the force generated by the drive unit 410 is transmitted via the output shaft 2020, the power transmission device 2030 and the pulley 1020 operating as an output shaft, which is here at the lower end of the Support column 100 is located, to which delivered between the upper end and the lower end of the pulling device 420 guided along the support column 100
  • the load carrier 310 is then moved longitudinally along the support column 100 via the force imparted by the belt-like pulling device 420.
  • the local separation of drive unit 410 and support column 100 can also have a positive effect on the safety of the individual components.
  • Fig. 9 shows a shock-mounted support column 100 with bearing points 110.
  • the support column 100 is only elastically connected to the hull.
  • the forces acting on the ship for the support column 100 can be dampened, and the elevator, the load carrier and the cargo are less stressed. Overall, this has a positive effect on the durability of the elevator and the integrity of the conveyed item 350.
  • the elastic connecting elements on the mountings 110 can advantageously be springs.
  • springs can be used that can absorb forces in two or three axes.
  • the support column 100 can advantageously consist of at least two support parts. These support parts can be connected to at least one connecting plate in between.
  • the connecting plates can be arranged centrally between the support parts but also symmetrically or asymmetrically laterally offset from the center. Depending on how the metal sheets are attached, a recess or a hollow interior is created that can be used for the assembly of other elements of the elevator or other devices. In order to enable or facilitate access to these hollow interior spaces, the connecting plates can have cutouts.
  • the support parts can each consist of several parts. Multi-part support parts are easier to transport.
  • the hollow interior spaces in the support parts can also be used for the assembly of further elements of the elevator or other devices.
  • the support column preferably has at least one deflection device 1010 in order to deflect the forces applied via the pulling device 420.
  • Figure 10 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 pulling means 3010 that is separate from the pulling means 430 of the pulling device 420.
  • the counterweight 3000 can also be referred to as a balance weight 3000.
  • the separate traction means 3010 can be referred to as compensating traction means 3010.
  • the compensating traction device 3010 is fastened at one end to the load carrier 310 and at the other end to the counterweight 3000.
  • the compensating traction device 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, which is in the Figures 10 to 12 is indicated by the respective dashed frame 100.
  • 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 pulling device via a power transmission device.
  • a drive shaft 1035 of the pulling device, which via the power transmission device from the Drive unit is driven is in the Figures 10 to 12 shown schematically by a drive shaft 1035.
  • FIGS 11 and 12 show embodiments of an elevator 300 with a counterweight 3000, in which the counterweight 3000 is integrated into the pulling device 420.
  • one end of the traction means 430 is attached to the load carrier 310.
  • the other end of the traction means 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 pulleys 1020 deflects the traction mechanism by 90 °.
  • a deflection roller 1030 and a feed roller 1030 are additionally provided in order to deflect the pulling means 430 from a vertical orientation into a horizontal orientation towards the drive shaft 1035 and from the drive shaft 1035 again from a horizontal orientation into a vertical one Alignment to redirect towards counterweight 3000.
  • the drive shaft 1035 has a pressure angle of 180 ° with the traction means 430.
  • this deflection roller 1030 and supply roller 1030 can deflect the traction means to a drive shaft 1035, which is arranged at a distance from the support column 100 and / or outside an elevator shaft.
  • the traction means is deflected by the drive shaft 1035 via two further deflection rollers 1020, initially by 180 ° in the direction opposite to the direction of gravity and then by a further 180 ° again in the direction of gravity to the counterweight 3000.
  • 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 over at least 50%, 70%, 80% or 90% of the extent of the support column 100 in the longitudinal direction L.
  • the deflection roller which deflects the traction means 430 starting from the counterweight 3000 second, is arranged in a lower section of the support column, in particular in the lower 50%, 30%, 20% or 10% of the length 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.
  • the two deflection rollers 1020 arranged between the drive shaft 1035 and the load carrier 310 are spaced from one another by at least 50%, 60%, 70% or 80% of the longitudinal extent of the support column 100.
  • Figure 12 shows an embodiment of an elevator with a counterweight 3000 and load carrier 310, which are coupled to the traction means 430 via a pulley system.
  • the load carrier 310 and the counterweight 3000 are each coupled to the traction means 430 via a loose deflection roller 3030.
  • only the load carrier 310 or only the counterweight 3000 can be coupled to the traction means 430 via a loose deflection roller 3030.
  • the traction means 430 is firmly attached to the support column 100 at both ends.
  • the traction means extends from the fixed end to the loose deflecting roller 3030 and from the loose deflecting roller 3030 to a fixed deflecting roller 1020.
  • 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.
  • the counterweight 3000 at least partially compensates for the weight of the load carrier 3010, so that the required drive force of the drive unit can be further reduced.
  • the Figures 13 and 14 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 means (not shown), which are deflected between the counterweight 3000 and the load carrier 310 via two separate deflection rollers 3020. Between the separate deflection roller 3020, two deflection rollers 1020 for deflecting two traction means (not shown) of the traction device are arranged.
  • the axes of rotation 1025 of the deflection rollers 1020 of the traction means of the pulling device are arranged offset to the rotation axes 3025 of the separate deflection roller 3020 for the traction means of the counterweight 3000.
  • the axes of rotation 3025 of the separate deflection roller 3020 are arranged offset with respect to the axes of rotation 1025 of the deflection rollers 1020 of the pulling device towards the load carrier 3010.
  • the counterweight 3000 is arranged in sections in the counterweight receptacle 3040.
  • the counterweight mount 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 opposite legs 3050 are connected to one another by a third column wall 3060, which forms the base 3060 of the U-shaped wall section.
  • the counterweight 3000 can be arranged such that it extends in sections beyond the legs 3050 of the U-shaped wall section. So that's in Figure 13
  • the counterweight 3000 shown is only arranged in sections in the counterweight receptacle 3040.
  • the counterweight 3000 can be fastened via guide rails 3080 fastened to the support column 100.
  • the guide rails 3080 can be arranged in the counterweight mount 3040.
  • the guide rails 3070 can be attached to the legs 3050 of the U-shaped wall section that delimits the counterweight receptacle 3040.
  • the guide rails 3080 for the counterweight 3000 can be offset with respect to the guide rails 340 for the load carrier, in particular offset transversely to the longitudinal axis L.
  • the axes of rotation 3025 of the separate deflection roller 3020 can be offset with respect to the guide rails 3080 of the counterweight 2000.
  • the counterweight receptacle 3040 can be formed in addition to the assembly space 500.
  • the counterweight receptacle 3040 is limited by the outside of the column walls 3050, 3060 of the support column 100, while the assembly space 500 is limited by the inside of the column walls 210, 3060, 3070.
  • at least a section of the traction mechanism 430 of the traction mechanism 420 can be shielded from the course of the counterweight 3000, whereby a collision of the counterweight with this section of the traction mechanism 430 can be avoided and thus the risk of the traction mechanism tearing can be reduced.
  • the mounting space 500 may have a central area 505 and side areas 540.
  • the assembly space is U-shaped, with the central region 505 of the assembly space forming the base and the side regions 540 of the assembly space forming the legs.
  • the assembly space 500 may also be rectangular.
  • the central area 505 and the outer areas 540 can be separated from one another by opposing partition walls 3070.
  • the partition walls can form boundary walls of the central region 505 of the assembly space 500.
  • traction means 430, 3020 and / or the counterweight 3000 can be guided in the central region 505 of the assembly space 500, while cables, for example, can be guided in the outer regions 540 of the assembly space 500.
  • 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 region 505 is completely enclosed by a frame.
  • Such column walls 3060, 210 can also be referred to as a connecting part or connecting plate.
  • a column wall 3060 at the same time 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 form.
  • the outer areas 540 of the assembly space 500 can be delimited by mutually 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 wall 3070 and on the outside by column walls 200 in the form of support parts 200.
  • 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 further column walls 3060, 200 can also be referred to as connecting parts or connecting plates.
  • these further column walls 3060, 200 can be formed by the same column walls 3060, 200 that connect the partition walls 3070 of the central region 505 of the assembly space 500 to one another.
  • these connecting parts or connecting plates 3060, 210 can extend from a support part 200 over both partition walls 1070 to the second support part 200.
  • 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 assembly space to the side areas 540 of the assembly space 500.
  • the two connecting parts or connecting plates 3060, 210 can extend in a straight line.
  • 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 limited by two opposite column walls 3070, 200, which are connected to a frame via two further column walls 210.
  • the first two opposite column walls can be designed as partition walls 3070 which separate the central area of the assembly space 505 from side areas 540 of the assembly space 500.
  • Guide rails 3070 of the counterweight 3000 may be attached to the partition walls 3070.
  • Guide rails 3070 of the counterweight 3000 can be attached to the support column 100 in a line with the guide rails 340 of the load carrier 310.

Landscapes

  • Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Cage And Drive Apparatuses For Elevators (AREA)
  • Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
EP20188973.0A 2019-08-02 2020-07-31 Batteau avec un ascenseur doté d'un moyen de traction de courroie Active EP3771682B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102019120992.7A DE102019120992A1 (de) 2019-08-02 2019-08-02 Aufzug mit riemen-zugmittel

Publications (2)

Publication Number Publication Date
EP3771682A1 true EP3771682A1 (fr) 2021-02-03
EP3771682B1 EP3771682B1 (fr) 2023-08-30

Family

ID=71899626

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Application Number Title Priority Date Filing Date
EP20188973.0A Active EP3771682B1 (fr) 2019-08-02 2020-07-31 Batteau avec un ascenseur doté d'un moyen de traction de courroie

Country Status (3)

Country Link
EP (1) EP3771682B1 (fr)
DE (1) DE102019120992A1 (fr)
FI (1) FI3771682T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115559693A (zh) * 2022-11-09 2023-01-03 山东胜信石油装备有限公司 滑轮式平衡及缠绕提升双作用滚筒立式抽油机

Citations (9)

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US6386324B1 (en) * 1998-02-26 2002-05-14 Otis Elevator Company Elevator traction sheave
WO2003043927A2 (fr) * 2001-11-23 2003-05-30 Inventio Ag Ascenseur comprenant un moyen de transmission de type courroie, notamment une courroie dentee, en tant que moyen de support ou moyen d'entrainement
WO2006053934A1 (fr) * 2004-11-16 2006-05-26 Kone Corporation Ascenseur
EP1700811A1 (fr) * 2005-03-12 2006-09-13 ThyssenKrupp Aufzugswerke GmbH Ascenseur
US20080142313A1 (en) * 2005-03-01 2008-06-19 Mitsubishi Electric Corporation Elevator Apparatus
EP2174903A2 (fr) * 2008-10-12 2010-04-14 H. Henseler AG Entraînement pour une cabine d'ascenseur, maintenable à partir de la cabine
ITRM20100094A1 (it) * 2010-03-05 2011-09-06 Vipal S P A Sistema di movimentazione per elevatore.
EP2862831A2 (fr) * 2013-10-18 2015-04-22 Kone Corporation Machine de levage d'ascenseur et systeme d'ascenseur
EP3214399A1 (fr) 2015-10-29 2017-09-06 Metallverarbeitungsgesellschaft Schubert & Co. (GmbH & Co. KG) Ascenseur de munitions pour navires

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DE9201374U1 (de) * 1992-02-05 1992-04-02 C. Haushahn GmbH & Co, 7000 Stuttgart Seilspannsystem für Aufzüge
DK2423098T3 (da) * 2010-08-24 2013-07-08 Stefan Schulz Serviceskib til offshoreanlæg
DE102012110769A1 (de) * 2012-11-09 2014-05-15 Contitech Antriebssysteme Gmbh Riemen für die Antriebstechnik, insbesondere riemenartiges Zugelement für die Aufzugstechnik, mit brandhemmenden Eigenschaften
DE102013110778A1 (de) * 2013-09-30 2015-04-02 Thyssenkrupp Elevator Ag Aufzuganlage
EP3288887A4 (fr) * 2015-04-27 2019-03-13 KONE Corporation Agencement d'ajustement de tension d'un élément de traction d'un ascenseur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6386324B1 (en) * 1998-02-26 2002-05-14 Otis Elevator Company Elevator traction sheave
WO2003043927A2 (fr) * 2001-11-23 2003-05-30 Inventio Ag Ascenseur comprenant un moyen de transmission de type courroie, notamment une courroie dentee, en tant que moyen de support ou moyen d'entrainement
WO2006053934A1 (fr) * 2004-11-16 2006-05-26 Kone Corporation Ascenseur
US20080142313A1 (en) * 2005-03-01 2008-06-19 Mitsubishi Electric Corporation Elevator Apparatus
EP1700811A1 (fr) * 2005-03-12 2006-09-13 ThyssenKrupp Aufzugswerke GmbH Ascenseur
EP2174903A2 (fr) * 2008-10-12 2010-04-14 H. Henseler AG Entraînement pour une cabine d'ascenseur, maintenable à partir de la cabine
ITRM20100094A1 (it) * 2010-03-05 2011-09-06 Vipal S P A Sistema di movimentazione per elevatore.
EP2862831A2 (fr) * 2013-10-18 2015-04-22 Kone Corporation Machine de levage d'ascenseur et systeme d'ascenseur
EP3214399A1 (fr) 2015-10-29 2017-09-06 Metallverarbeitungsgesellschaft Schubert & Co. (GmbH & Co. KG) Ascenseur de munitions pour navires

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115559693A (zh) * 2022-11-09 2023-01-03 山东胜信石油装备有限公司 滑轮式平衡及缠绕提升双作用滚筒立式抽油机

Also Published As

Publication number Publication date
DE102019120992A1 (de) 2021-02-04
EP3771682B1 (fr) 2023-08-30
FI3771682T3 (fi) 2023-12-01

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