Patent Application
20190135589
The invention concerns a regenerative compensating device for maintaining specifiable target positions of a load that may be manipulated by means of a cable hoist, wherein said load is attached to a cable of said hoist, wherein said load unintentionally changes its specifiable target position into a deviating actual position due to interference factors, comprised of at least one sensor device for the direct or indirect acquisition of the respective actual position of the load; a rotatory drive for providing an effective cable length from the cable hoist; and at least one control device which, after acquisition of the respective actual position of the load, changes the effective cable length until the load is again in its specified target position.
A prior art solution to this end is depicted in part schematically in
To transport the load, the respective cable hoist is provided with a cable winch of the commonly used kind, which is provided with a reversible electric or hydraulic motor that serves as rotating drive for winding and unwinding of the cable. If the described usual load lifting operation with its specifiable target positions of the load is now superimposed by the interference factors described earlier, for example because a cargo ship fitted with a cable hoist is subjected to a more or less strong wave action, the load attached to the cable hoist through the cable would, without the known compensating device, follow the wave action in real time by assuming actual positions that deviate from the target positions, and may be damaged for example when lowered onto solid ground, such as a wharfage or the sea bed. Thus the free lowering path of the load attached to the cable becomes shorter or longer, the effective length of which is defined by the free length of cable unwound from the cable drum as soon as the cargo ship follows the respective wave action with the cable hoist.
To solve this problem, the known solution, as shown schematically in
Thus the shortening or extension of the effective cable length depends exclusively on the travel distance when extending or retracting the piston rod unit so that for large deviations of the actual position from the target position a relatively long duty stroke of the power cylinder is required. To achieve this, large hydraulic power cylinders including hydraulic pumps are therefore often used in practical application, which require a correspondingly large installation space in the vicinity of the actual cable hoist. Due to the large amounts of hydraulic fluid required for the operation of the power cylinder by the hydraulic pump, which has to be circulated in the corresponding hydraulic circuit, the overall efficiency of the compensating device has to be rated as relatively low. Moreover, the cable is subjected to increased friction wear at least in the section in which the guide pulley of the power cylinder moves for the compensating process and the cable is redirected. Since a lot of time is required for each compensating retraction and extension move of the power cylinder, controlled by its hydraulic system, and thus large quantities of fluid have to be moved, the known solution is not suitable to implement immediate compensation processes on the effective cable length, which impairs the operational and functional safety as well as the positioning accuracy. Due to its dimensions and weight as well as its functionality the known compensating device is basically only suitable for use on large equipment. Already existing plant or machine parts cannot be retrofitted with such a compensating device at a reasonable effort.
Based upon said prior art it is the object of the invention to provide an improved compensating device which avoids the above-described disadvantages.
Said object is met by a compensating device with the characteristics of claim 1.
Due to the fact that, according to the characterising part of claim 1, the respective rotatory drive is controlled at least partially by at least one bi-directional hydraulic motor, which is connected in a fluid-conducting manner to an actuating device which, whilst forming a drive means for the respective hydraulic motor, is provided with at least two from each other separated pressure chambers that are at different pressure levels during operation and which may be operated by the control device, a modern hydraulic motor drive concept is described for the directly driven cable winch of the cable hoist where only small quantities of drive fluid need to be circulated, which provides better efficiency and dynamic response compared to the drive concepts with hydraulic power cylinders as they are known from the prior art. Since the respective hydraulic motor does not have a separate cable guide, like the said guide pulley used on the power cylinder, but rather operates the rotatory drive of the cable winch of the cable hoist directly, for example by means of a hydraulic clutch, or even forms its entire drive module, a low-wearing cable guide is achieved via the cable winch only, where said winch is required in any case. By using a correspondingly large winch diameter it is possible to reduce cable friction and thus minimise wear, particularly on the cable.
Since the hydraulic motor is directly controlled via the respective pressure chambers of the actuating device due to its direct coupling with the cable winch, the compensating actions required on the cable can be achieved without delay, which increases the operational and functional reliability as well the positioning accuracy of the compensating device according to the invention. Due to the modular-like design of the compensating device with its components such as sensor and control devices including the hydraulic motor with its actuating device, it can easily be retrofitted to existing plants or equipment in a cost-effective manner and can be mounted directly at the cable hoist in the vicinity of the cable drum in a space-saving manner. This has no equivalent in the prior art.
In a particularly advantageous manner the drive means of the actuating device can be operated by at least one actuator. The at least two from each other separated pressure chambers of the actuating device have each a fluid connection to the respective hydraulic motor in such a way that either the one or the other pressure chamber serves to drive the respective hydraulic motor in the one or the other rotational direction respectively, and that the pressure chamber, which is currently not used to drive the respective hydraulic motor, will take up the displaced fluid for a subsequent discharge process when said drive is operated. The functional separation of the actuating device into a drive means to drive the hydraulic motor and an actuator to drive the drive means provides for the employment of different technical solutions for the design and sizing of the actuator. Besides a preferred implementation of the actuator in form of a hydraulically operated power cylinder, it may also be implemented through an electric motor or a hydraulic motor that operates a spindle drive.
In a particularly advantageous design the control device is provided with at least one valve arrangement, which is used to control the actuator in contra-rotating directions using an operating pressure from a supply source. Compared to other drives, in particular electrical drives, the actuator designed as a fluid-driven, hydraulic power cylinder makes a rapid change of direction possible when controlling the drive means of the actuating device.
In particularly advantageous exemplary embodiments the sensor device is provided with at least one gyroscope and/or inertia-based sensor and/or a satellite-based navigation device. Such sensors and devices can be obtained relatively cheaply but are still sufficiently accurate to determine the respective load position with certainty. Sensors of this kind are often already on site, for example on board of a cargo ship to monitor its orientation and position, making it possible to use said sensors to also acquire the position of the load suspended on the cable relative to the respective transportation means.
In a preferred embodiment of the compensating device according to the invention provision is made that the drive means and the actuator each are provided with at least one piston that is guided inside a common housing of the actuating device, and that the adjacently located pistons are operatively connected to each other via a coupling device. Instead of providing a spatially separated arrangement of the drive means of the actuating device for controlling the hydraulic motor through the actuator for operating and controlling said drive means, which may also be in operative connection to each other via a hydraulic coupling device, for example, they may preferably be combined in a common actuator housing in a space-saving manner. In this instance the coupling is preferably achieved mechanically via a common piston rod. This way the drive means as well as the actuator of the actuating device are provided as hydraulically operated power cylinders. This design provides a cost-effective and functionally reliable realisation of the compensating device.
In a further preferred embodiment of the compensating device according to the invention provision is made that the individual pistons of the piston rod unit, preferably with the same outer diameter, subdivide the housing of the actuating device into at least four pressure chambers with at least partially varying pressure levels and volumes and are assigned directly to the drive means and the actuator. Since the respective pistons delimit said pressure chambers and are simultaneously displaceable by means of the piston rod unit into one or the other opposite direction, a change in pressure level transfers directly onto the piston movement, that is, onto the piston and piston rod and reverse, so that immediate control actions are possible for the hydraulic motor of the cable winch of the cable hoist.
In a particularly preferred embodiment of the compensating device according to the invention provision is made that an additional pressure chamber of the actuating device is preloaded by means of an energy store, such as a hydraulic accumulator, with the objective to move the drive means with the actuator in a specifiable movement direction and to establish a force equilibrium at the drive means. When certain interference factors influence the overall facility, the released fluid volume is stored via the additional pressure chamber with its connected hydraulic accumulator to be reused in a subsequent process step. Particularly when starting up the cable winch under high load, or when interference factors influence the overall facility, the additional pressure chamber with its connected hydraulic accumulator ensures a jerk-free operation and causes a corresponding damping effect in the overall movement of the hydraulic motor in its operation of the attached cable winch by damping the piston rod unit of the actuating device in its respective displacement movement.
As described above, it is possible to store a certain volume of fluid, which may also be of advantage for other pending solutions with devices of this kind. One advantage of a drive with a rotatory cable winch is the possibility of combining one or more variable displacement motors into a single drive unit in order to achieve the required cubic capacity in operation. This also opens up the possibility to approximate the required load pressure difference to the pressure inside the accumulator, which leads to an increase in the overall efficiency whilst minimising the required actuator power.
A fixed, optimal accumulator pressure may insofar be preselected, and at heavy loads the entire cubic capacity of the respective rotatory drive is adjusted upwards; at light loads, on the other hand, it is adjusted downwards, but always so that the load pressure is able to approximate the accumulator pressure equalisation. This has the advantage that it is not necessary to correct the accumulator pressure during the lifting process with pending load changes, for example due to the mass of the reeled-off cable length or due to buoyancy when the attached load passes through the water surface. The installed accumulator energy can always be fully utilised. A smaller rotatory displacement is required for lighter loads, and more compensated revolutions can be achieved at the cable winches with the same accumulator volume. In that way lighter loads can be corrected over longer traversing paths.
In a further preferred embodiment of the compensating device according to the invention provision is made that the one pressure chamber of the actuating device is operated in a high-pressure mode, and in contrast at least one other pressure chamber of the drive means is operated in a low-pressure mode. Although when the compensating device is in operation, the operating pressure in low-pressure mode can rise significantly, and that of the high pressure mode is reduced accordingly, such a subdivision makes particularly the lifting of the load by means of the cable hoist easier since an increased drive torque is provided in this manner. Moreover, it is preferably provided that the pressure chamber, which is mainly operated in low-pressure mode, is preferably connected permanently to a low-pressure accumulator. In this manner it is possible to correct the operating fluid volume and the pressure for the pressure chambers of the actuating device so that the hydraulic components for the cable winch drive is supplied with a sufficient amount of fluid even during the dynamic reversing operation.
In a further particularly preferred embodiment of the compensating device according to the invention the actuating device is provided with a position sensing device, which makes it possible to acquire the position of the actuator and/or the drive means, and that the controller controls the respective actuator under consideration of said position by means of a processor unit. Since the position of the piston rod unit of the actuating device can be detected by means of the sensing device, the controller with associated processor unit is able to acquire the current actual position of the piston rod unit and use it for a control process to correct the actual load position towards the respective target load position.
In a further preferred embodiment of the compensating device according to the invention the respective hydraulic motor can be accelerated and decelerated in both contra-rotating directions through a hydraulic driving and braking unit, which is superimposed upon the application of pressure by the respective pressure chamber of the drive means. In this manner the major part of the load lifting and lowering process with the cable winch can be achieved through the driving and braking unit, and the additional hydraulic motor has exclusively the function of undertaking the compensating processes for maintaining the target load position. The hydraulic motor may thus be sized correspondingly small and requires only small amounts of fluid volume for the compensating and reversing operation of the cable winch. It follows from this that the actuating device with its drive means and pressure chambers with different pressure levels also needs to supply only small amounts of operating fluid volume to effectively operate the compensating hydraulic motor.
The cable hoist may be installed fixed, in particular be part of a dockyard crane system, or it is part of an installation location that is subjected to interference factors, in particular a floating transport means that is subject to wave action, in particular in form of a ship or a conveyor platform. Moreover, the compensating device may be used in vehicles that are fitted with at least comparable cable hoists such as mobile cranes, cable-operated forklifts or other lifting devices.
Further advantages of the invention become apparent from the following description and the drawing. Shown are, schematically and not to scale, in:
A section of a prior art compensating device 100 is depicted in
In this example the cable hoist 202 is part of an installation location 220 that is subject to interference factors, in particular a floating transport means in form of a ship that is subject to wave action. The cable hoist 202 is provided as part of the structure of the ship 220 and serves for the lifting and lowering of the load 206 from/to the sea floor 222. The cable hoist 202 is provided with a cable winch 204 onto which the cable 216 can be wound on and off again. Starting from the cable winch 204, the cable 216 extends via a pulley 224 to the load 206. As is common practice, multiple pulleys and booms as well as hooks or other coupling devices may be provided as part of the cable hoist 202, which have not been included in this schematic diagram for reasons of simplification.
The cable winch 204 may be operated with a hydraulic motor 226, 228, 230 in one and in the opposite rotational direction. As an example,
The raising and lowering of the load 206 is possible with the cable hoist 202 described so far. The problem is, however, that the position and orientation of the cargo ship 220 can change due to wave action or wind loads. Said changed orientation or position would be transferred via the cable hoist 202 to the load 206, so that the load also constantly changes its position and in particular its height above the sea floor 222. Thus the precise dropping of a load 206 to the sea floor 222 is made very difficult, if not impossible.
To remedy this, the compensating device 200 according to the invention is provided. The compensating device 200 comprises a sensor device 240, 242 for the direct or indirect acquisition of the respective actual position of load 206, the rotatory drive in form of the cable winch 204, driven by the respective hydraulic motor 226, 228, 230, for paying out an effective cable length of the cable hoist 202, and a control device 244 which, after acquisition of the respective actual position of the load changes the effective cable length until the load 206 has regained its specified target position again. According to the invention the rotatory drive may be controlled by a contra-rotating hydraulic motor 226, 228, 230, which has a fluid connection to an actuating device 246. Whilst forming a drive means 248 for the respective hydraulic motor 226, 228, 230, the actuating device 246 comprises at least two from each other separated pressure chambers 250, 252 with different pressure levels when in operation, and which may be controlled by the control device 244.
The actuating device 246 is connected parallel to hydraulic pump 236 via corresponding fluid lines 254, 256 to the hydraulic motor 226, 228, 230, depending on which one will come into operation. The respective hydraulic motor 226, 228, 230 may be accelerated or decelerated respectively in both contra-rotating directions, superimposed by the pressure applied from the respective pressure chamber 250, 252 of drive means 248 and by a hydraulic driving and braking unit in form of a hydraulic pump 236 of the cable hoist 202.
The actuating device 246 is implemented as a triple-piston with a drive means 248 and an actuator 258. The actuating device 246 is subdivided overall into three sections 260, 262, 264 of which in the drawing the upper section 260 is called the high-pressure section, the centre section 262 is called the low-pressure section and the lower section 264 is the actuator section. Each section 260-264 is provided with a piston 266, 268, 270 within a common, pressure-resistant housing 272, wherein the pistons 266, 268, 270 are connected and separated from each other by a common piston rod 274. The sections 260-264 are separated from each other leak-proof through the separating walls 276, 278, and the piston rod 274 passes through them. The drive means 248 and the actuator 258 each are thus provided with a piston 266, 268, 270 that is guided in the common housing 272 of the actuating device 246, wherein the adjacent pistons 266, 268, 270 are in operative connection with each other via a coupling device in form of the piston rod 274. The coupling device 274 in form of the piston rod forms, together with the respective pistons 266, 268, 270 that are guided inside housing 272 of the actuating device 246, the piston rod unit 280 as a whole. The pistons 266, 268, 270 of the piston rod unit 280 subdivide, preferably with the same outside diameter, the housing 272 of the actuating device 246 into a total of six pressure chambers 250, 252, 282, 284, 286, 288.
Two from each other separated pressure chambers 250, 252 of the actuating device 246 each have a fluid connection to the associable hydraulic motors 226, 228, 230 in such a way that either the one or the other pressure chamber 250, 252 serves to drive the respective hydraulic motor 226, 228, 230 in the one or the other contra-rotating direction, and that the pressure chamber 250, 252 that is not engaged in driving the respective hydraulic motor 226, 228, 230 takes up the fluid, which was displaced by said driving process, for a subsequent discharge process. The additional pressure chamber 282 of the drive means 248 of the actuating device 246 is preloaded by an energy store 290 in form of a container and thus aims to move the piston rod unit 280 with the actuator 258 into a specifiable movement direction. To this end the pressure chamber 282 and the energy store 290 are filled with an operating gas in form of nitrogen (N2) with specified preloading. The additional pressure chamber 282 of the actuating device 246 can thus be operated in a kind of high-pressure mode, whilst in contrast another additional pressure chamber 284 of the drive means 248 is operated in a kind of low-pressure mode and is open to the environment U. A low-pressure store 292 is connected permanently to pressure chamber 252. Said low-pressure store 292 has the purpose to maintain a sufficiently high pressure level in pressure chamber 252 and in the fluid line 254 and to prevent possible cavitation.
The drive means 248 of the actuating device 246 may be operated by the actuator 258. A control device 244 with a valve device 294 is provided for controlling the actuator 258, with which a supply pressure of a supply unit 296 can be applied to the actuator 258 in opposite movement directions. The supply unit 296 comprises a hydraulic pump 298, which draws hydraulic fluid from a tank 300. A hydro-pneumatic pressure store 302 is inserted between the hydraulic pump 298 and the valve device 294 as equalisation buffer. The valve device 294 takes the form of a 4/3-way proportional valve. In the left switch position of the valve device 294, as shown in the drawing, the hydraulic pump 298 feeds fluid into a rod-side pressure chamber 286 of the actuator 258, whilst fluid is able to flow away from the opposite, piston-side pressure chamber 288 in the direction of the tank 300. In this switch position the piston rod unit 280 is lowered inside the housing. In the right switch position both pressure chambers 286, 288 of the actuator 258 are supplied with hydraulic fluid. Due to the pressure-active area at the rod-side 304 of piston 270 of the actuator 258 this leads to a lifting of the piston rod unit 280. In the central neutral position both pressure chambers 286, 288 of the actuator 258 have a fluid connection to each other via a restrictors 305 as well as with the tank 300 via a restrictor 305. The actuator 258 is inactive in this switch position. The valve piston 306 of the valve device is centred in its middle neutral position via springs 308 provided at the end. In order to set the required switch positions of the valve piston 306 with the control device 244, an electromagnetic operating device 310 is provided.
A safety device 312 is additionally installed in the fluid lines 314, 316 between the valve device 294 and the actuator 258. Said safety device is provided with further sensors and/or valves for controlling the actuator 258.
The control device 244 is coupled with two sensor devices 240, 242. The one sensor device 240 comprises a gyroscope or inertia-based sensor, in particular an acceleration sensor as well as, where necessary, an additional satellite-based position acquisition device. This sensing facility makes it possible to determine the position and orientation of the cable hoist 202 and thus indirectly the actual position of the load 206. The actuating device 246 comprises a further sensing device 242 in form of a position sensing device 242 with which the position of the piston rod unit 280 within the actuator 258 and that of the drive means 248 can be determined. By means of a processor unit 318 the control device 244 controls the actuator 258 under consideration of said position and orientation data.
The compensating device 200 according to the invention acts in parallel to the hydraulic pump 236 of the cable hoist 202 of the respective hydraulic motor 226, 228, 230 of the cable winch 204. The hydraulic fluid of a hydraulic circuit 320 of the cable hoist 202 may be fed into a corresponding pressure chamber 250, 252 of the drive means 248 of the actuating device 246 of the compensating device 200, and its pressure-based energy may be stored temporarily in the corresponding energy store 290, 292. In the opposite operating direction the energy may be released from the energy stores 290, 292 from the actuating device 246 in order to decelerate and accelerate the hydraulic motor 226, 228, 230 of the cable hoist 202. Moreover, the drive means 248 of the actuating device 246 may be operated by the actuator 258 so as to selectively control the deceleration or acceleration of the hydraulic motor 226, 228, 230 of the cable hoist 202 to compensate for the interference factors. The actuator 258 is controlled by the control device 244 in conjunction with the position and orientation information of the cable hoist 202 and the piston rod unit 280 inside the actuating device 246, which has been acquired with the sensor devices 240, 242.
The solution according to the invention thus proposes a modern hydraulic motor drive concept for the directly drivable cable winch 204 of the cable hoist 202 with small quantities of operating or drive fluid, which exhibits a greater degree of efficiency than the drive concepts using hydraulic power cylinders 108 as per the prior art. Since the respective hydraulic motor does not have its own cable guide, for example the above-described guide pulley 114 on power cylinder 108, but rather acts directly on the rotatory drive 226, 228, 230 of the cable winch 204 of the cable hoist 202, for example by means of a hydraulic clutch, or forms its drive module entirely, it is possible to achieve a low-wearing cable guidance solely through the already necessary cable winch 204. By using a correspondingly large winch diameter the cable friction may be further reduced so as to minimise wear in particular on cable 216.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2016 005 477.8 | May 2016 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2017/000350 | 3/20/2017 | WO | 00 |
