DE2508581A1 - Support boom for underwater research vessel - with cable drums and swinging action to bring vessel on board - Google Patents

Abstract

The rear of the oceanographic survey vessel is fitted with parallel booms which are swung outwards over the stern about a horizontal axis. The end of the boom has cable guide wheels which guide the cable connection to the underwater research vessel while it is being towed. The boom is mounted on elastic supports to accommodate variations in the tow tension and towing direction. When the vessel is hauled in it is clamped to the end of the boom on pivoted clamps so that it can be swung onto the deck. The deck winding wheel has a larger diameter than the underwater wheel.

Description

Device for lowering, towing and retrieving an oceanographic Tug at sea Device for lowering, towing and retrieving an oceanographic tug at sea The invention relates to a device for lowering, towing and retrieving an oceanographic tug, the comprises a crane boom which can be rotatably mounted on a towing vehicle; Drive means for the selective pivoting of the crane boom around a practically horizontal one Axis; an angetrielbe ne winch assembly with a drum for winding and unwinding a cable; a tow cable that is attached to the drum at one end and is wrapped around this and has means with the help of which it is on its outer End can be connected to a body to be towed; a grooved wheel device on the crane boom, which is in engagement with the cable while the Cable on and unwinding from the winch drum; one rotatable on the crane boom attached carriage, which is provided with a contoured surface that the Part of the body to be towed during the lowering and retrieval of the same thus engaged, corresponds to; a shock absorber system and a Sannungskonstanthalttingsvorrichtung for the tow cable; Means to ensure the desired tightening angle of the Cable during the winding and unwinding of the cable onto or from the winch drum for unwinding and winding up the tow cable; and a compensation mechanism for selective mounting of the slide in a usual horizontal position independently from the rotation of the crane boom. (Hit "Tightening angle" refers to the angle between the cable guide immediately before reaching the winch drum and a theoretical line drawn at right angles to the winch drum axis when viewed from above is).

Numerous attempts have been made to provide a device to create, with the help of which the towed body is easily lowered and heaved up and handled during the towing operation can be that further Minimal damage to the towing cable and the body to be towed during towing holds, and in which the shock absorber system and the voltage stabilization device Changes in tension in the line of pull, which are two separate ones, in the water floating masses, e.g. B. a submerged, pulled by a moving ship Echosounder, or underwater locator, connects to each other at minimum values keep. It was found that the tow cable tends to become slack and then go back into a taut state. The transitional burden of the cable at the moment of cable tightening is several orders of magnitude higher than with the nominal tensile load. Cable breakage and damage can result. When towing submerged massive bodies, e.g. B. one on a towing vehicle attached echo sounder or sonar device, the problem of shock absorption becomes much more difficult. In rough seas, the intensity of such transitional loads can of the cable can be very strong, especially because of one occurring in the pull line Snapping action from the flaccid to the taut state that affects the two, relatively bodies moving at different speeds to one another is.

The technical problem shown is therefore solved according to the invention by creating a towing device equipped with a crane boom, which the The possibility of high transitional loads within a train line is significantly reduced and practically eliminates all spring parts of the assembly to allow drainage and retrieval operations to facilitate what is achieved by a cable guide on the crane boom is rotatably mounted and configured in such a way that a controlled surface it is ensured to which such a cable after one or the other Page can swing out while practically staying in line with the intended Grooved wheel devices, and also by means for the elastic application of a Turning force on the crane boom via the articulation connection on the towing vehicle the same that is appropriate and responsive to any changes made to the crane boom exerted load and / or the moment of motion of the same.

According to an advantageous embodiment of the invention, the Cable guiding device on a frame part which is rotatable about an axis of rotation, which has practically the same extent as the axis of rotation of the grooved wheel device and runs practically parallel to it, a group from within the frame part freely rotatable side guide rollers, against which the cable during the Drag operation can press, a front freely rotatable roller and a rear freely rotatable roller, which are mounted on the frame part in a plane that transversely to the level of the lateral guide rollers, and a spring preload device for unilateral pressing of the cable guide device in such a direction that the can press the front roller against the cable regardless of the angle of the towing cable. the Cable management device thus creates a controlled surface around which the cable can turn to one side or the other while staying in one line with the grooved wheel. The guide rollers according to this embodiment are kept in a practically constant position with respect to the cable and follow its behavior when swinging back and forth when the speed of the ship is increased or decreased.

According to a further Isierkmal of the invention, the resilient Torque applying means includes: a linear drive actuator with a compressible fluid that is filled at the end of the piston rod, the head end being rotatably attached to the front end of the winch frame; one free rotatable pulley device mounted on the rear end of the winch frame is; a pivot arm attached to the crane boom at its pivot mount; and a cable attached at one end to the piston rod through the pulley runs and is attached to the swivel arm at the other end.

It has already been recognized by those skilled in the art that the tightening angle during winch operation of the cable should be reduced to ensure a satisfactory deposition of neighboring To achieve cable turns on the winch drum. For precise winding of the cable the cable should be led to the drum at a right angle, i.e. H. the Tightening angle should be as close to zero as is practical.

To achieve a tightening angle as close to zero as possible there are numerous methods in arrangements, which are used as leveling veins (level winders) are known. These have a running-guide device, which moved laterally relative to the cable, d. H. in a direction parallel to the cylinder drum axis of rotation, by one gear (distance between the windings) for each revolution of the winch drum, the cable must run through this guide device before reaching the winch.

Typical barrel guide bodies of this type for reducing the angle of articulation lie in arrangements as they are for. B. in Canadian patents 692 070 and 707 634.

In the case of cables for towing sonar equipment, the problem becomes winding using the specified cable management devices is even more difficult due to the cladding they use for hydrodynamic anti-drag purposes wear. Attempts have also been made to turn off such cable routing devices, namely by moving the winch drum while the cable is being wound up, such as this z. B. in the Canadian patent 655 052 is described. In this known device, the movement of the winch drum is dependent on the Cable tension exerted and consequently the angle of tightening varies in such Arrangements proportional to the changes in the load. Such an arrangement is satisfactory when the cable is subjected to practically constant loads is.

According to the technical problems identified are a automatic assurance that the tightening angle of the cable is as close as possible the practically achievable optimum value lies during the winding up of the cable the or the unwinding of the same from the winch drum, as well as the creation of a Winding device for a winch in the towing device that meets the requirement makes it unnecessary for cable routing devices and thus signs of wear and tear turns off on the cable casing, solved by the fact that the horizontal center line the drive means is arranged offset by 2 to 3 ° from the horizontal center line of the crane boom.

This special feature of the invention is therefore by a careful orientation of the winch drum relative to the cantilever groove wheel during the entire work movement, by limiting the width of the winch drum and by offsetting the boom assembly by 2 to 3 °, preferably by 2030, eliminates the need the use of any separate winding device is superfluous.

This inventive feature ensures that between the both extremes from the full stretch of the crane boom, where the entire cable is either unrolled or unrolled until the crane boom is fully brought on board, with the entire cable wrapped around the drum, the tightening angle below the critical 3 0 value. This means that a separate cable reel is unnecessary is and that the cable winds on the mind drum without further complications.

In the field of towing sonic technology, the is let into the water the echo sounder body lifted from the deck of the ship, swung over the stern, until it is largely submerged in the water and then released by the delivery mechanism, so that he swims afterwards under the surface of the water. The haul-in operation includes winding up the towed sonar until it is in the crane carriage captured is, and then its lifting on board by starting up the crane.

The professional world has the problem of interconnecting the sonar device with the crane boom and the crane carriage arrangement. According to the state however, in the art, means have been developed for trapping the sonar in the Slide once the interface was reached. Spring loaded and hydraulically released hooks, hydraulically operated bolts and similar means were usually the result of such developments. Although theoretch is functional, such agents caused considerable environmental difficulties under which they have to work.

Such facilities must be functional at times when they are completely immersed in sea water, as well as at temperatures that vary depending on the location of the ship range from 60 to -29 0C.

Furthermore, the known mechanical means are usually such highly dependent on an exact alignment of the fitting parts on the slide and towed echo sounder body and any misalignment increases the risk of a faulty work.

According to the technical problem shown, the dragged To keep the sonar device in firm contact with a crane carriage without getting over the Interface to make use of distributed mechanical interlocks, and at the same time To create a carrier for the towed sonar device and / or the crane boom is indifferent whether the crane boom is in its maximum inboard position or in its maximum Outboard position is solved in that the Siiittmmwith frame parts which are freely rotatably attached to the crane boom and wherein the carriage also has a plurality of brackets, each of which in a resilient end cap ends, which has an arcuate surface that is directed downward and to be engaged is with part of the surface of one too sluggish Body, and a towed body support is also provided on the crane boom attached and designed in such a way that it is the body to be towed inevitably supports when the boom is in its maximum inboard position is located, and / or a bracket that is attached to the deck of the ship for support of the crane boom when the boom is in its maximum inboard position is located, and / or a bracket that is attached to the stern of the Sdiffes and for Support for the crane boom is used when the boom is in its maximum outboard position is located.

According to an advantageous embodiment, the device exists according to the invention from a winch assembly that is on the deck of a ship and on Stern of the ship is mounted. A pair of crane boom or ditch arms that are structurally connected to one another to form a unified whole are rotatably attached to the winch assembly behind the stern of the ship for pivoting between a stowage position where they go up and over the stern of the ship protrude in a position where they extend up and over the stern of the ship, and a towed body discharge or retrieval position where they move down from the stern of the The ship away. A slide is rotatably mounted between the crane boom arms and a groove wheel is rotatably supported on the same axis as the carriage. A hydraulically operated drive device is between the crane boom arms mounted on the boom pivot points to move the crane boom. A compensation mechanism is intended to hold the slide in a horizontal position when the Crane boom is moved and a motorized winch drum device is provided for unwinding and rolling up the cable.

According to an advantageous embodiment of this according to the invention Embodiment, the compensation mechanism has pulley devices that are attached to the drive device in such a way that they come together with the drive device rotate, furthermore a pulley arrangement, which is attached to the crane boom coaxially with the carriage, as well as a cable, which revolves the pulley device and the pulley assembly.

In all of these embodiments of the invention, it turns out to be particularly advantageous if the towing cable with cladding or sheathing elements is provided, each sheathing element is a solid component, its Opposite ends form surfaces which abut adjacent ones Shroud members which are in a head-to-head orientation, wherein the cable and the sheathing elements have an electrical conductor attached to the towing vehicle is attached and extends through the cable. According to such an embodiment an electric conductor winch is provided for guiding part of the electric conductor between the towing vehicle and the driven winch drum during the and unwinding the cable. The electric ladder winch consists of a first storage drum, which is connected to the powered winch drum and is connected to it to achieve a consistent rotary movement with this, a second storage drum, which is spaced from the first drum and a winch mechanism, which is in engagement with the electrical conductor at points that represent an over-bridging with respect to the first and second storage drums, respectively, and which is movable about the outer surface of the same for transferring the electrical conductor part which is in engagement therewith from one drum to the other between the first and second storage drums and according to the rotary motion of the driven line drum.

It is a useful feature of the invention that the crane boom is lowered to its extreme position during lowering and Recovering the sonar to fully submerge the corner sounder body during its Drain phase so that the echo sounder body with; [water can fill, while it remains in the area of the slide. On the other hand, the echo sounder body should sit well adjusted in the sledge when hauling in, listening to himself under the Is located on the water surface and is therefore exposed to forces that move it into a and seek to bring back orientation.

during towing, the crane boom is as close as possible to the horizontal one Location held. When raising and lowering the ship's stern v / uld in the absence of Compensation means of the dragged echo sounder body pulled up or sinking left by a similar amount that varies through the serpentine line of the cable and the angle between the echo sounder body and the ship, which depends on the towing speed is determined. Since another advantageous feature of the invention is the sonar device to cover a straight and at the same height jeg leave, external forces of the type shown are undesirable, which is why a passive one Cable slack compensation system is used. This system includes lever arms and linear actuator actuators. The arrangement serves as a spring, whereby the "actuator actuators" Are gas / spring cylinders (one on each side) that work in such a way that when additional forces are exerted on the tow cable, e.g. B.

when the ship's stern goes up, the damping effect of the drive actuators allows the crane boom to go down.

Conversely, there is a decrease when the ship goes down the cable load is registered by the drive actuators and the crane boom is upscale. This is to create a device that ensures that between certain limits of the drag point, d. H. the crane jib grooved wheel, travels a distance, which is as straight as possible in the vertical plane, regardless of movement of the tow vehicle in the same plane.

The invention is illustrated in more detail by the accompanying drawing, in which: FIG. 1 shows a side view of the device according to the invention according to FIG an advantageous embodiment, the sonar to be towed in its is shown in full outboard position, FIG. 2 is a view of the one shown in FIG Embodiment seen from the rear, Fig. 3 is a perspective view of a cable winch mechanism, how it can be used in the device according to the invention, FIG. 4 is a partial cross-sectional view a winch arrangement as it can be used in the device according to the invention, FIG. 5 is a cross-sectional view of an electric ladder winch assembly as shown in FIG device according to the invention can be used, FIG. 6 is a cross-sectional view of a Details of the electric conductor winch shown in Fig. 5, Fig. 7 is a view of the Winch housing, which is partly broken open for the sake of clarity Fig. 8 is a partial cross-sectional view of a partial view of Fig.

which is the relative spatial position of the center line horizontal axes the crane boom drive device and the crane boom itself, FIG. 9 shows a schematic representation of the hydraulic system for that shown in FIG inventive device and Fig. 10 is a schematic sectional view of crane boom positions, as they are with the aid of the device according to the invention possible are.

According to the embodiment shown in Figures 1 and 2 of The invention is a sonar device to be towed at different depths from an inboard stowage position transferable to an outboard drain position. The towed body can move out of its deflated position released and lowered to the required operating depth on its tow cable will. This depth is controlled by adjusting the length of the tow cable that is unrolled by a cable winch, as well as by the speed of the towing vehicle. After the towing operations have been completed, the towed body can be retrieved by reversing the drain procedure. In addition to funds for drainage, towing, depth change and retrieval operations are performed by the device according to the invention according to a preferred one Embodiment a shock absorption system that allows excessive changes in through Cable tension caused by waves is prevented.

According to the embodiment shown in Figures 1 and 2 is a towing winch assembly 10, a hoist crane assembly 50, a sled / cable guide / pulley assembly 100 and a shock absorber system 150. There is also a hydraulic drive unit and a motor controller is provided.

The tow winch arrangement 10 is made according to an advantageous embodiment from a winch drum 11, which is mounted on a base frame 12, which is attached is on the aft deck 13 of a ship 14. The winch drum 11 is driven of a hydraulic motor of the elne band brake, generally designated 15 16 of the type that is inserted with spring force and released hydraulically. The winch drum 11 drives an electric ladder winch 17 on the starboard side the winch drum 11 is mounted and ensures continuous electrical conduction from the conductors (not shown) of the towing cable 18 to the (not shown) Ship internal sonar circuits 14.

The function of the winch assembly 10 is to provide the desired length of towing cable 18 unwind and retrieve and the crane boom 51 and the drive device 58 to assist in lowering into the water and retrieving the towed body 103.

According to a preferred embodiment shown in FIG the winch drum 11 is made of aluminum plates, which consist of an outer Sheath 19 are made and on the inner surface and at the ends reinforcement plates 20 have. The reinforcement plates 20 are all of the open construction type for the sake of ease and to allow access to the electrical Conductor cables inside the winch drum 11. The outer surface of the winch drum 11 is notched with grooves 21 to accommodate the required length of sheathed towing cable 18 in a single layer. At intervals along the Outer surface of the winch drum 11 are bored holes (not shown) around a Allow water drainage to be closed.

The anchorage 22 of the towing cable 18 is inel; half of an on-port side kerblocks 23 clamped to the inside of the / end plate 24 of the winch drum 11 is screwed. Another clamp 25 is on the inside of the winch drum 11 attached to one of the reinforcement plates 20 for holding a (not shown) electrical connector, which is located at the end of the electrical conductor cable 36. A stub shaft 27 is attached to the two end plates 24 and 28 of the winch drum 11 screwed. Each shaft 27 rotates within the bearing bushes 29, which are preferably fiber-reinforced phenolic bearings that are mounted in bearing blocks 30, which are attached to the winch frame 12.

Grease nipples (not shown) are easily accessible on the bearing blocks 30 to lubricate the bearings.

The winch frame 12 is made in accordance with a preferred embodiment made of a welded aluminum structure that supports the entire lifting system. On the winch frame 12 suitable surfaces are provided for fastening the winch mounting arrangement 30, the winch motor 15 and the band brake assembly 16, the crane boom - rehrtntifjbw $ ndeleiterinde 17 and the gas cylinders (not shown) as well as linear drive means 110 and pulleys 120 for the shock absorber system 150.

According to an advantageous embodiment, the winch drum 11 through a starboard tower 27 with the help of a low-speed hydraulic rotors 15 of high torque driven by the radial piston type. The motor 15 forms one integral unit with a band brake 16 of the type inserted with spring force and hydraulically released brakes, which is completed by a mounting bracket.

As can be seen from FIGS. 3 and 5 to 7, there is an electric conductor winch 17 provided around means for maintaining a continuous electrical line between the electrical conductors of the tow cable 18 and the internal sonar circuits of the ship without the use of slip rings. She is on the port side the winch drum 11 and included according to an advantageous embodiment in a waterproof housing 31, which is preferably made of aluminum, and two Has showcase 32. The winch consists of a primary drum 33, a stationary spool 34 and a negator spring arrangement 35 (see FIG. 3).

The winch mechanism 17 consists of an arm 521 between its Ends attached to a shaft 522 for rotation in the hub 541 and part which protrudes beyond the side walls of the coil 34 for reasons which will be described below become understandable. The arm 521 terminates at one end in a fork-like part 523, which has a groove wheel 39, that rotatably attached to it is e.g. B. with the help of a pin 525. At the opposite end of the arm 521 a plurality of counterweights 41 are removably attached, e.g. B. with the help of a Stud 527 screwed into the end of arm 521. The arm 521 rotates therefore about the axis of shaft 522, which in turn aligns with the axis of the shaft 27

The grooved wheel 39 is freely rotatable about the pin 525, the axis of which is perpendicular to the axis of the arm 521.

The winch mechanism 17 is connected to a negator spring arrangement 35, consisting of a drum 671 which is attached to part of the shaft 522, which consists of the Housing side wall j (teragsraggt,) is attached to a rolled up ribbon spring 672 and an anchor for the spring. The drum 671 is attached to the shaft and the band spring 672 is wound on its outside, one end of which is wound on the drum 671 is anchored and the other end is wound around a supply spool is, which is rotatably mounted on a stub shaft 673, which on the housing side wall is attached. The ribbon spring 672 is of a selected length and is on a supply spool 673 is wound and the stored rewind spring resists unwinding. The outer The end of the coiled spring is tied up and facing in the opposite direction the drum (work coil) 671 is wound. The spring that works in such a way that if it tries to wind itself clockwise around the supply reel, it exercises a comparative effect constant, counter-clockwise rotating force on the work coil (drum) 671 off. This results in a preload that moves the drum 671 in a counterclockwise direction seeks to turn. Since the drum 671 is attached to the shaft 522, the Winch arm 521 is biased in a corresponding manner by spring force for rotation in one direction counterclockwise. The ribbon spring 672 stands out in particular advantageously through practically constant torque properties.

The electrical conductor cable 36 is connected to the towing cable 18 by a (not shown) plug-coupling arrangement connected to the inside of the winch drum 11 is clamped. The cable 36 is passed through the drum shaft 38 and the port stub shaft 27 passed onto the primary drum 33 of the winch 17. It then goes through the role setup 39 and on the stationary spool 34. From this spool 34, the cable 36 is through a Sealing sleeve 40 in the bottom of the winch housing 31 and to the internal circuits of the ship 14 led. The rotation of the winch drum 11 in any direction causes the cable 36 to run back and forth between the primary drum 33 and the stationary reel 34 via the roller device 39. The roller device 39, the balanced by a weight 41 attached to one end is with the negator spring assembly 35 connected. This spring arrangement 35 receives the roller device 39 spring-preloaded clockwise (when looking to starboard) and stops with it a nominal voltage is maintained in the electrical conductor cable 36 at all times.

A maximum cable unwind end limit switch 42 is also provided mounted inside the winch housing 31. It is operated by a thumb cam 43, which is driven via a worm drive reduction gear 44 and chain drive 45 by means of a gear 46 which is attached to the port stub shaft 27 the winch drum 11. The winch housing 31 is heated by two heating strips 47, which are still completed by a fixed thermostatic control to ensure that the electrical conductor cable 36 remains flexible at all times.

The operation of the winch mechanism can be described as follows. The winch drum 11 is rotated in a suitable manner for winding and unwinding of the cable 18. Is the towing cable 18 mounted on the winch drum 11, i. H. wound up, the main part of that protruding beyond the winch drum 11 is Multi-conductor cable 36 stored on the stationary coil 34. Will the winch drum 11 When turned clockwise to unwind the cable, the primary drum rotates 33 coincides with the drum 11 and causes the conductor cable 36 turns is wound around the turn on the primary drum 33. Since the supply of the Cable is located on the non-rotatable stationary reel 34, which causes it resulting pull on the cable causes a twisting motion that acts on the winch rod mechanism 17 works. This rotational force in turn causes the rod or arm 521 to be in the same Direction of how the winch drum 11 rotates against the bias of the spring 672. At the Rotating the winch bar 521 pulls the cable from the stationary drum 34 and this makes the cable effective from the stianar drum / onto the rotary supply drum 33 convicted. The bias of the spring 672 prevents the slack from rolling Cable and the cable drawn off from the stationary reel 34 therefore runs over the grooved wheel 39 and winds itself on the drum 33, since the winch bar 521 with a smaller Speed rotates as the drum 33. The speed of rotation of the winch bar 521 should be just enough to maintain tension throughout the cable and this speed adjusts itself, since it changes from the to the multi-core Conductor cable being pulled around in a circle.

The specified mechanism of action applies to the case that the Winch unwinds cable. If the winch winds up cables, then the electric conductor cable winch fulfills the same function, except that the spring preload is that of the slack cable pulled off the drum 33 picks up and transfers it to the drum 34.

Two stop bearings 48 (see FIG. 4) are on the inden frame in such Assembled manner that each stop bearing 48 has a small clearance with the side edges which has port and starboard winch drum end plates 24,28. These stop bearings 48 have the purpose of lateral shock loads from the winch drum 11 from the winch frame 12 to be recorded and distributed in it. There is a grease nipple on each stop bearing for lubrication purposes Installed.

As can be seen in particular from Figures 1 and 2, are on the winch frame 12 two loading bay locks 59, 60, mounted to fix and hold the crane boom 50 in the inboard stowage position. Each lock 59, 60 is according to one advantageous embodiment of an aluminum welded piece with an elastomer Rubber buffer Dolster 62 is provided. There is also a lower towbar lock 63 mounted on the winch frame 12 to the front part 121 of the towed body 103 from below when in the inboard stowage position (not shown) is located. According to an advantageous embodiment, it consists of an aluminum weldment, which is provided with an elastomeric rubber buffer pad 65.

According to an advantageous embodiment, the crane boom arrangement 50 a crane boom 51, which is constructed from the two boom arms 52, 53, which consist of aluminum supports and plates that are firmly screwed to a cross brace 54 to form an "H" configuration. Two bearing blocks 67, which are preferably made of steel, are connected to the inboard ends 55 of the cantilever arms 52, 53, screwed and then wedged onto the stub shaft 68 of the rotary drive winch motor 158. The rotary drive winch motor 158 is on the base frame 12 of the towing winch assembly assembled.

The purpose of the crane boom 51 and rotary drive winch motor 158 arrangement is that towing body 103 from the inboard stowage position (not shown) to transfer into the (shown) outboard take-off position and vice versa with the help the winch assembly 10.

The crane boom 51 is from the inboard stowage position (not shown) moved to the outboard starting position (as shown in Fig. 1) and vice versa with The aid of the rotary drive winch motor 158, which is preferably a hydraulic one Rotation drive acts. The drive motor 158 is on the underside of the one Part 66 of the winch frame 12 is attached, which overhangs over the stern of the ship 14. The horizontal centerline of the drive motor 158 is around 2 to 3 degrees, preferably by 2 1/2 °, deviating from the dwars ship center line (cf. Figure 8). This causes the cantilever groove wheel 123 to move slightly sideways moved during the lowering and retrieving cycles and thus the correct winding of the towing cable 18 on the winch drum 11 is supported.

Across between the cantilever arms 522 53 is an H-shaped carrier locking member 61 attached. When the crane boom is in its outboard deflate or home position is located, the locking part 61 comes to rest on rubber buffers 64, which are at the rear of the ship are attached.

The carriage / cable guide / bull wheel assembly 100 is driven by a horizontal shaft 101 supported on the outboard end portions 56 of the Lifting crane boom s 51. The carriage 102 forms a stable seat for the towed body 103, e.g. B.

the sonar device, during lowering and retrieving, and is in a held almost horizontal position with the help of a compensating mechanism 104. He also offers the towed body 103 protection by preferably made of polyurethane formed buffers 105 attached to its underside. The cable management arrangement 106 comprises a series of side guide rollers 107 against which the tow cable 18 is pressed during the towing operation to view the various towing cable angles To compensate, the guide arrangement 106 is provided with spring preload by using two ribbon leaf springs 108 in such a direction that the Rollers 107 are always at right angles to the towing cable 18.

The guide wheel shaft 122 is preferably made of a chrome-plated one Steel pipe attached to the outboard ends 56 of the cantilever arms 52,53. the Guide wheel shaft 122 carries the groove wheel 123, the carriage assembly 102 and the Cable routing arrangement 106.

The grooved wheel 123 is according to an advantageous embodiment around an aluminum structure that rotates freely on the guide wheel shaft 122 in the Bearings 24 which are preferably fiber-reinforced phenolic bearings. It is made from a welding piece 125 with which two edge mounts 126 are screwed which form the groove 127 of the groove wheel 123. In this groove 127 are one Variety, e.g. B.

eight arc-shaped segments made of plastic material, e.g. B.

Polyurethane material, introduced, which serve to make the nose pieces 69 of the sheathing 70 of the towing cable 18 to protect.

A grease fitting (not shown) is light for lubricating the bearings accessible.

The slide arrangement 102 is advantageous in accordance with an advantageous one Embodiment to a welded structure made of aluminum plates 128, the The purpose is to have a stable seat for the towed body 103 during lowering and hauling in. The assembly 102 is carried on the guide wheel shaft 122 in the bearings 24, which are preferably fiber-reinforced phenolic bearings acts. A grease fitting (not shown) is on each bearing for lubricating the same easily accessible.

A variety, e.g. B. eight hemispherical buffers 105, which are preferably consist of polyurethane, are screwed to the underside of the carriage assembly 102. They are attached in such a way that they conform to the upper curve of the towed body 103 and the towed body protect during lowering and retrieving operations.

The special configuration of the cable guide arrangement 106 makes this requirement after long side rolls that protrude far enough to allow adaptation to the different trailing cable angles to enable completely superfluous. According to an advantageous embodiment, the cable guide arrangement 106 consists of two welded aluminum arms 129, each at one end of the guide wheel shaft 122 is carried in bearings 130 which are preferably fiber reinforced Phenol storage acts. A grease fitting (not shown) is on each bearing for Lubrication easily accessible. The assembly is cross-connected at the other end of each arm 129 with three spacer sleeves 131.

Freely rotatable rollers 132, 133 are mounted on two of these sleeves 131, which are preferably fiber-reinforced phenolic rollers, where one roller 132 in front of the SiLeppkabel 18 and the other roller 133 behind it is located.

Similar rollers 134 are mounted on the side of each arm 129, so that the towing cable 18 through the middle of the roller set 107 runs. The cable management arrangement 106 is with the carriage assembly 102 by two ribbon springs 108 with constant Torque connected. These springs give the cable guide a spring preload in such a direction that the front roller 132 is always against the nose pieces 69 of the sheathing 70 of the towing cable 18 pushes independently of the towing cable angle.

The slide arrangement 102 brd in all crane boom positions in held in a horizontal position with the aid of a compensating device 104. This The device consists of two component sets 135 each consisting of two pulleys, with one kit on the port side and the other on the starboard side is arranged. A pulley 136 of each set of components 135 is attached to the housing of the Crane boom drive 110 attached and the other pulley 137 of each component set is attached to the sled assembly 102. Each set of 135 sheaves is connected by a cable 138 which is preferably a stainless steel cable Steel, which is fixed to each pulley by mounting pins 139.

The shock absorber system 150 consists of two identical component set components, one set on the port side of the inden frame and the other set on the starboard side of the same is arranged. Each component set consists of one linear drive part 110, which is attached to its head end 112 by hinge pins 111 is rotatably articulated on the outermost pre-piston tangender side 113 of the winch frame 12. Only the vende 118 å each drive part 110 is with a compressible fluid filled, e.g. B. a gas, such as nitrogen gas, which is a reservoir of two gas bottles 207 are removed, which are attached to the front end of the winch frame 12 are. The gas pressure in the drive part can be easily changed by operating two valves 203, 204 on the hydraulic prime mover 151.

The piston rod 115 of the drive part 110 is with a piece of the Cable 116 connected via a freely rotatable pulley 120 which is attached to the winch frame 12 is mounted, runs. The cable 116 is then connected to a rotating arm 117, which is attached to the crane boom pivot point 57.

If a towed sonar device is brought on board in the usual way, so it is lowered onto the deck of the ship in a storage rack which is in suitable spatial position is brought and attached to the deck. On smaller ships or on a crowded deck it is usually not always possible to find the appropriate one To create space for a storage rack.

As can be seen from FIG. 10, the invention is used to solve this problem a towed body support 71 created on the crane boom 51 in such a way is attached that the towed body 103 automatically comes to sit in this Towing body position 71 when the crane boom is in its outermost inboard position (such as indicated by solid lines).

This towed body support 71 can carry the towed body completely or only partially, in the latter case an additional one mounted on deck Bracket 63 is present.

The towing system is operated hydraulically and is manual and electrically controlled by a hydraulic prime mover. A special feature according to an advantageous embodiment of the invention is that during the lowering and retrieving operations of the towed bodies 103 are held in the slide 102 is caused by tension in the trailing cable 18. This tension is kept practically constant with the help of a pressure-compensated hydrostatic drive system with closed Line, which is described in more detail below.

A movement of the crane boom 51 around its central pivot point 57 during the towing operation causes compression depending on the size of the cable load or expansion of the gas and springs (not shown) within the drive member 110. This compression or expansion is only sufficient, a moment of force on the crane boom to counteract the moment of force caused by the cable load. During the towing operation, the crane boom is held at an angle of 0 ° and the gas pressure in the drive parts is adjusted in such a way that at a constant cable pull the crane boom remains comparatively quiet. Elevated If the cable pulls, the crane boom and the gas and the springs fall down within the drive part are compressed. However, the crane boom only falls by such an amount that this is due to the drive parts on the crane boom exerted moment of force increases sufficiently to the caused by the increased cable tension To counteract the moment of force. If the cable tension decreases, the crane boom is raised and the gas and springs expand. In this case, too, the crane boom rises only by such an amount that the boom due to the drive parts on the crane exerted moment of force decreases sufficiently to the caused by the reduced cable tension To counteract the moment of force.

A hydraulic power machine 151 is provided to operate the system. It includes a variable displacement axial piston pump system, the is shown schematically as unit 154 (cf.

Figure 9) and both manual and pressure compensation control means having. A closed loop 155 containing a twin-shaft electric motor 156 and pump 157 provides a hydrostatic drive system that includes the Winch motor 158 drives at different speeds and in both directions.

unit Also included in the hydraulic prime mover is a fixed displacement in-line gear pump 160.

An outlet of the pump delivers oil which is filtered through 10 micron filter 162 wird'zum crane boom circuit and the other outlet 163 supplies oil that passes through 10 micron filter 164 is filtered, for disengaging the winch brake and for the Flooding controls of the variable displacement pump 157.

The specified components are together with various valves on a container 165 with a capacity of approximately 210 liters (55 gallons) assembled. The container 165 is according to an advantageous embodiment around a welded aluminum structure using the usual known mechanisms is provided, e.g. B. cleaning caps, a filler vent cap, an oil level gauge and a drain valve (none of which are shown). It is also provided with 250 micron size 166, 167 oil filters to protect pumps 160 and 157, respectively Impurities.

The winch assembly 10 is according to an advantageous embodiment driven by a low-speed hydraulic radial piston motor 15 with high Rotary force of the rotary housing type. The band brake 16, which is engaged by spring force and is hydraulically disengaged by a linear drive part 168 acts on the outer surface of the motor housing. The motor 15, the band brake 16 and the Drive parts 168 are mounted on a common base plate 169.

The crane boom is preferably moved by a hydraulic one Rotary drive winch motor 158, of the double wing type, which has maximum angular excursion of 155 °.

As can be seen from Figure 9, the hydraulic system comprises a variable one Positive displacement axial piston pump system 154 with manual and pressure compensation control means. During manual control, it supplies oil to drive the winch motor 158 variable speed and in both directions. During lowering and retrieving it maintains a constant pressure on the winding side of the winch motor regardless of the oil flow 158 upright. The refill pump 224 provides a pilot pressure for operating the Direction control valve 159 in winch circuit 155.

The system also includes an oil filter 167 (e.g. 250 micron size) and a filter 217 (e.g., 10 microns in size) to protect the refill pump 224 from contamination from reservoir 165, and to filter the oil from the refill pump 224.

The system also includes a fixed displacement in-line gear pump 160 on. An outlet 161 supplies oil to the crane boom circuit. The other outlet 163 supplies oil for the release of the winch band brake 16 and for the very general with 183 designated inclined seat control valves (swash controls) of the pump 157. This Part of the system also includes an oil strainer 166 (e.g. 250 microns in size) and a filter 162 (e.g. 10 microns in size) to protect the pump 160 from contamination from the reservoir 165 and for filtering the oil from the outlet 161 of the pump 160.

The system that runs from the pump 160 to the crane jib winch-up and roll-off system is equipped with a manually operated directional control valve 173 for directing oil to and from the crane boom rotary winch motor 158, as well as having a Solenoid operated directional control valve 171 for directing oil to and from the Winch band brake 16. Also provided in this system is a pilot pressure controlled overflow valve 182, about the pressure in the brake circuit and to the angle seat control valves 183 of pump 157 to about 49 kg / cm2 (700 psi) to limit.

In the mind circuit 155 is a solenoid-controlled, by pilot pressure operated direction control valve 159 arranged.

In the de-energized state, it hydraulically blocks the inden motor 158 and directs the oil from pump 157 such that motor 158 is bypassed entirely. When switched on, it fills the closed supply circuit 155 of the Pump 157 and winch motor 158.

A remote control device 174 is in the system between pump 160 and the pump system 154 arranged. This controls the oil discharge volume of the pump 157.

The crane boom is operated by a double-wing rotary drive winch motor 158, which moves the crane boom from the inboard stowed position to the outboard deflated position (see. Fig. 1) moves and vice versa. An over-center valve 180 is in the crane boom control circuit intended. This valve prevents the crane boom 51 from running away. In the crane boom control circuit there is also a pilot pressure-controlled overflow valve 218 to control the pressure of the crane boom circuit to around 63 kg / cm2 (soo psi). A ball valve 205 is provided in the crane boom circuit to allow oil flow from one side of the Crane boom rotary winch motor 158 to the other side during shock absorption to enable. A double overflow valve 219 is arranged in the crane boom circuit, around the pressure in the brake disengagement and in the angle seat valve-controlled rotary winch motor 158 to 105 kg / cm2 (1500 psi) and protect the drive motor housing. A filter 164 (e.g.

10 micron size) is also arranged in the crane boom circuit, to filter oil from outlet 163 of pump 160.

A pressure switch 220 is arranged in the winch control circuit 155, which is completed by an indicator lamp that lights up when the pressure rises. If the indicator lamp goes out, this means a warning that the boost pressure for the winch circuit is low, e.g. B. below about 2.8 kg / cm2 (40 psi).

The throttle valve 198, which is arranged in the pressure circuit of the pump 160 is, restricts the flow of oil to the / stepped seat valve 183 and thereby maintains a constant Remote control pressure 174 upright.

The variable displacement pump system includes a solenoid operated Directional control valve 172. It is deenergized during lowering and retrieving and connects a scan line from the winding side of the winch line closed circuit 155 to the pressure compensator 184 of the pump 157. The compensator 184 then sets the The discharge from pump 157 is automatically constant at practically all times Pressure a. During the winch control, the valve 172 is in operation and interrupted the scan line from compensator 184, which drives pump 157 at varying pressures able to work as desired by the operator.

The closed Winiqnleiterkreis 155 includes a low high-speed radial piston engine 158 with high torque and a band brake actuator or drive portion 168. The motor 158 drives the winch drum. One by guiding print actuated overflow valve 221 is provided to through high transitional loads of the cable caused high pressure surges in the winding side of the winch circuit 155 impede. A transmission unit, the cross-line overflow valves, is also provided and regulating valves. The cross-line relief valves limit the pressure on each side of the closed winch system 155.

An overflow valve actuated by pilot pressure is also provided 178 to limit the winch charging circuit pressure to 12 kg / cm2 (170 psi). A regulating valve 222 ensures that the housing of the winch motor 158 is always full of oil.

damping The shock control system includes linear drive parts or Be-spring actuator 110 of the / reset type (those at the piston rod ends filled with gas are). They compensate by advancing or retracting the piston rods the varying moments of force exerted on the crane boom that are caused due to increased or decreased cable pull during shock absorption.

The shock absorption system includes nitrogen gas cylinders 207, the gas supply for the shock absorption operation. The gas supply is regulated by the Nitrogen gas regulator 208, which, as mentioned, the gas supply to the shock absorber system controls. Shut-off valves 203, 204 and 223 are provided for supplying gas from the gas bottles 207 to the linear drive members or actuators 110 to vent gas from the linear ones Actuators 110 and to protect the pressure gauge 202. The pressure gauge 202 shows the gas pressure in the piston rod ends of the linear drive actuators 110 at.

The device according to the invention can be in the neutral state, in the drainage and retrieve condition, winch control condition and / or shock absorber condition. In the following, the actuation and mode of operation of the hydraulic system in these different states are described.

Neutral state solenoid operated valves, namely the directional control valve til 159 and the solenoid operated valves 171 in the crane boom drive system and 172 in the variable displacement pump system 154, are deenergized and turned off and the manually operated valve 173 and remote control 174 are in FIG the spring-centered neutral position.

Once the remote control 174 is in the spring centered position the variable displacement pump 157 has zero displacement. Will such a Pump 157 flooded by moving the handle 175 of the controller 174 in any one direction, oil flows through the closed winch pipe system 155 the passages 176, 177 of the valve 159, completely bypassing the winch motor 158. The pump 157 sub-circulates the oil in the closed conductor circuit 155 Bypassing winch motor 158 using directional control valve 159.

The outlet 161 of the fixed displacement pump 160 allows that Oil flows through passages 178, 179 of valve 173 to the spill valve section 181 of over center valve 181.

The spill valve 180 opens by pilot pressure from the pump outlet 161 at about 7 kg / cm2 (100 psi) and then the oil flows through valve 181 to the Container 165.

The other outlet 163 of the fixed displacement pump 160 displaces Oil at about 49 kg / cm2 (700 psi) back through the spill valve 182 to the reservoir 165. It also supplies oil to the remote control device 174 and the / Schrygsitzventi 185 the variable displacement pump 157.

Deflate and Recover Conditions The solenoid operated valve 172 is deenergized and solenoid operated valves 159 and 171 are energized. The closed one Winch circuit system 155 is filled by switching on the directional control valve 159. The winch system pressure line 155 on the take-up side is through the de-energized Valve 172 connected to pressure compensator 184 of the variable displacement pump 157

If the handle 175 of the remote control device 174 is completely over the WINCH Moved in the IN direction, the pressure compensator 184 regulates the pressure of the oil the variable displacement pump 157 to an almost constant value of about 67 kg / cm2 (950 psi) regardless of the oil volume requirement and the direction of the Oil flow.

This pressure creates an almost constant tension in the towing cable 18, which has the towed body 103 in firm contact with the carriage 102 during the Lowering and hauling in.

The lever 186 of the valve 173 is used to lower the crane into the water OFF direction and then oil flows from outlet 161 of the fixed displacement pump 160 through valve 173 and passage 179 to passage 187 to the LOWER passages of the crane boom rotary winch motor 158. As soon as the crane boom 51 lowers, oil flows from the LIFT passages 193, 194 of the rotary winch motor 158 through the Passages 192 and 178 of valve 173 and through open valve 181 back to Container 165 through return line 195. As soon as the crane boom 51 has reached the 90 ° angle goes through, the gravity of the combined weights gradually overcomes the Pull the cable 18 when the boom 51 swings out further. The boom 51 is inclined to an acceleration due to the increasing moment of force caused by the change the location of gravity and the pressure in the rotary winch motor 158 drops to about 7 kg / cm2 (100 psi), this value being the setting of the over-center valve 181 corresponds. At this pressure, the valve 181, which is actuated by pilot pressure, blocks from the drive motor supply line 190 and the feed line 191, the Oil outflow from the rotary winch motor 158 or throttles it. It is therefore formed a back pressure from downstream of the winch motor 158 so that the crane boom 51 is prevented from falling in this way, and its speed becomes controlled by the volume of oil pumped into the rotary winch motor 158.

Lever 186 of valve 173 is turned in the CRANE IN direction for retrieval moves and thereupon oil flows out of the outlet 161 of the fixed displacement pump 160 through passages 179 and 192 of valve 173 to the LIFTING passages 193, 1g4 of the rotary winch motor 158. As soon as the crane boom rises, flows oil from the LOWER passages 188, 189 of the rotary winch motor 158 through the passages 187 and 178 of valve 173 and through open valve 181 back to the container 165 through the return line 195. As soon as the crane boom 51 is at the 90 ° angle Approaching position, the pull of the cable 18 overcomes the force of gravity of the united Weights. When the crane boom 51 is further in the inboard stowage position moved, the force of gravity acts with the pull of the cable 18; the over-center valve 181 prevents a free fall of the crane boom 51 by forming a Back pressure downstream of the rotary winch motor 158.

From the other outlet 163 of the fixed displacement pump 160 through through passages 196, 197 of valve 171, the oil pressure acts on the winch brake drive actuator 168 and thereby holds the band brake 16 in the released position. Oil also flows to the remote control device 174 and through the throttle valve 198 to the inclined / veruerungeñ 183 of the variable displacement pump 157. Is the oil requirement for these components when satisfied, the excess oil flows through at about 49 k kg / cm2 2 (700 psi) the spill valve 182 back to the container 165 through the return line 199. Will When the system is returned to neutral, valve 171 is turned off and oil flows from winch brake drive actuator 168 through passages 197, 201 of the valve 171 back to the container 165 through the return line 199, whereby the band brake 16 is actuated.

Windenst your state when starting up the solenoid-operated Valve 159, the closed winch circuit system 155 is closed. The solenoid operated Valve 171 is supplied with energy and releases the winch belt brake 16.

The pressure compensator 184 on the variable displacement pump 157 is turned off by turning on the solenoid-actuated Valve 172. If the handle 175 of the remote control device 174 is moved in any direction, a pressure signal is sent from the control unit 174 to the / steguerungs-Leitiruckventil 185, which the angle seat valve control 183 of the variable Displacement pump 157 controls. Oil then flows in the closed lithium circulation system 155, its direction and volume depending on the direction and extent in which the handle 175 of the control device 174 was moved.

Shock absorber state After the towed body 103 is lowered up to the required towing depth, the crane boom 51 is set to a 0 ° boom angle set and the valve 173 brought into the neutral position.

The gas pressure in drive actuator 110 is then measured on the pressure gauge 202 read. This pressure is set either by supplying gas through the shut-off valve 203 into the drive actuator 110 or by draining existing Gas through the drain stop valve 204 from the drive actuator 110 to one Value that is sufficient to give the crane boom 51 a moment of force that through the existing loads on the towing cable 18 caused the moment of force approximately counteracts.

The ball valve 205 is fully open and thereby sets the shock absorber system 150 in motion. When the crane boom falls and well below the 0 ° boom angle stands, gas is supplied into the drive actuator 110 through the valve 203 to to raise the crane boom 51 to the 0 ° boom angle. When the crane boom is raised and is clearly above the 0 O boom angle, gas is released from drive actuator 110 through valve 204 to move crane boom 51 to zero ° lower boom angle. When the crane boom 51 excessive vibration is exposed, the ball valve 205 may be partially closed will by means of the handle 206, which restricts the flow of oil and dampens the system 150 will.

At this point the power plant powered by engine 156 becomes stopped. The gas pressure in drive actuator 110 is then adjusted so that the vibrations of the crane boom 151 kept approximately at the 0 O boom angle will. Factors that require adjustment of the gas pressure adjustment are / basieck loss from the system after several hours of operation, what an addition of gas from the gas storage areas 207 via the gas regulator 208 makes it necessary, and a change in the ship's speed and / or the sea condition and / or the Towing depth that lead to a change in the towing cable loads. The towing depth can be changed without switching off the shock absorber system 150.

The winch pump control circuit can also be in the neutral state, are in the lowering and retrieving state and in the winch control state. Hereinafter these states are described in more detail.

Neutral state valve 172 is switched off and the remote control device 174 is spring centered.

Oil from the pump 160 flows through the throttle valve 198 and is stopped on the manual (remote) control device 174, which is in the neutral center position. Lines are connected to one another to the tank return line in the manual (remote) control device, which have no shifting effect on the spool of the pilot valve 185 and the en Allow free movement in any direction.

Oil is also directed from pump 160 through the throttle valve 198 to the piston rod end port of the angle seat valve controller 183 and to the port 210 of the pilot valve 185. The pressure compensator valve 184 is through the directional control valve 172 connected to the high pressure side 155 of the hydrostatic winch drive. In however, in this condition the line pressures are well below the pressure setting of valve 184 so that it does not come into action; the piston end passage of the Angle seat valve control 183 is therefore with the pilot valve 185 through the passages of the pressure compensator 184 is connected.

The feedback link and spring hold the solenoid of the pilot valve closed as long as the pump 157 is in an almost zero flooding position, the oil being collected in the piston end of the servo actuator so that any change the flooding is prevented. If pump 157 is flooded in any direction, so the feedback shifts the spool of the pilot valve 185 by the required amount Direction to allow oil into the piston end passage of the angle seat valve control 183 through Inject or withdraw oil from the piston end passage through the pilot valve 185 the pilot valve 185 until the angle seat valve control practically resumes the flooding resets to the zero position. It deserves to be emphasized that that oil fed into the piston end passage of the angle seat valve controller 483 is the same The same pressure as the oil supplied at the piston rod end passage. Because the piston end area is larger than the piston rod end area, the angle seat valve control is activated 183 extended, which changes the flooding of the pump 157.

The feedback connection is adjustable within narrow limits (Zero flooding setting), which is a particularly advantageous setting of a very allows low flooding of the pump 157 in the neutral state while achieving a constant lubrication and cooling for the pump.

Deflate and Recover State Valve 172 is inoperative and lever 175 of the manual (remote) controller 174 is fully or partially on WINDS posed.

Completely shifting the control lever 175 results in one maximum pilot pressure. This pressure pushes the spool of the pilot valve 185 over against the feedback binding spring and thus oil is in the piston end passage of the angle seat valve control 183 fed in from the pump 160 through the throttle valve 198, the Leitvetil 185 and through pressure compensator valve 184.

The piston of the angle seat valve controller 183 moves to the left flooding the pump 157 for full volume in the winding direction of the winch.

In this state, the valve 159 is also in operation and completed the closed hydrostatic circuit line drive by the winch pump 154 and the winch motor 158. The set full volume of the winch pump is to this designed to drive the winch motor at full speed in the WINCH IN direction.

Is the rotation of the winch motor restricted, prevented or forced in the opposite direction (as when lowering) due to cable tension, so increases the pressure in the "high pressure" side 155 of the closed piping system immediately until it reaches the set pressure value of the pressure compensator 184. In this Moment overcomes the line pressure on the pressure compensator 184 by the Reference line and through passages 211 and 214 of shut-off valve 172 acts, its spring setting and switches the connection between pilot valve 185 and angle seat valve control 183. The angle seat valve seat valve control stops its movement and keeps the flooding constant. If the line pressure is still increasing further on via the existing pressure setting of the compensator 184, the latter moves Conductive pressure pushes the coil of the compensator 184 even further against its spring force and sets a connection between the piston end passages of the angle seat valve control 183 and reservoir return line 216 so that oil flows out of the piston end passage the angle seat valve controller 183 into the container return line 216. The constant Auxiliary pressure of the angle seat valve control 183 acting on the rod end passage now moves the piston to the right, reducing the flooding of the pump 157, until the line pressure corresponds to the set value. At this stage it switches the spring of the pressure compensator provides the flow connection from the angle seat valve control 183 and thus stops the movement of the angle seat valve control and brings the Flooding to a constant value.

When the cable tension increases the speed for the winch motor permissible (e.g. when hauling in), is the current flooding of the pump for this new condition no longer adequate and line pressure drops. The spring of the Pressure compensator 184 now moves the spool against the reduced pilot pressure and thus again opens the connection between the pilot valve 185 and the angle seat valve control 183 so that oil is fed into the piston end passage of the angle seat valve control 183 which now moves to the left, increasing the flooding until it is equalized is reached with the line pressure at the set pressure value of the compensator 184 is held.

These control mechanisms therefore keep an almost constant pressure upright in the winch circuit by regulating the outflow of the pump 157 depending on Need and even to an extent where the flow is reversed when cable tension on the winch and the manually operated (remote) control lever 175 is held in the WINCH ON position.

Winding state of control valve 172 is energized and interrupted thereby the scanning line from the winch circuit to the pressure compensator valve 184.

The manual (Pern) control lever 175 is in one direction for riJINDE ON and moved into the other for WINCH OFF. The amount of flow in each direction and thus the winch speed depends on the size of the pressure signals in the outflow lines of the controller 174 to the pilot valve 185. These pressure signals (and iXinden speeds) vary proportionally to the angular path that the manual Control lever 175 moves back.

When the control lever 175 is moved to WINCH ON, it becomes regulated Pilot pressure applied to the left end of the spool of pilot valve 185 and shifts them to the right against the suspension of the feedback spring force.

Oil from the pump 160 flows through the pilot valve 185 and through the Pressure compensator 184 in the piston end passage of the angle seat valve control 183. The piston of the Schrägsitzventilsteue tion 183 moves to the left with an increase the flooding and the volume output of the pump 157 in the desired direction, until the increasing spring tension of the feedback suspension equals that exerted on the spool Master pressure overcomes and thus the coil moves to the left into its neutral position. The piston of the angle seat valve control 183 stops its movement and the pump stops 157 maintains a constant discharge volume, i.e. H. a constant winch speed, upright.

If the control lever 175 is moved to WINDS OFF, it is now a regulated pilot pressure applied to the right end of the pilot coil 185 with displacement same to the left against the spring force of the feedback suspension. Oil is now flowing from the piston end passage of the angle seat valve controller 183 through the compensator valve 184 and through the pilot valve 185 to the reservoir return line 216. The piston of the oblique valve control valve 183 moves to the right, increasing the flooding of the pump in the desired Direction until the increasing spring force of the feedback suspension hits the lead coil 185 moves back to the closed center position. The angle seat valve control 183 the flooding of the pump 157 and the indene speed are now constant, as long as the position of the manual control lever 175 remains unchanged.

A certain expression in the lines between the manual control device 174 and the pilot valve 185 exist for each position of the manual control lever 175. This pressure determines the position of the angle seat valve control 183 and thus the amount and direction of the oil flow in the hydrostatic winch drive and thus also the speed and direction of rotation of the winch.

Claims (10)

Patent claims Device for lowering, towing and retrieving an oceanographic Tug at sea, characterized by a combination of a) a crane boom, which can be rotatably attached to a towing vehicle, b) drive means for selective pivoting of the crane boom around a practically horizontal axis, c) one driven winch arrangement with a drum for winding and unwinding a cable, d) a cable wrapped around the drum and designed in such a way, that it can be connected at the other end to a body to be towed, e) a bull wheel device on the crane boom which engages the cable during the winding and unwinding of the cable onto and from the winch drum, f) a slide that is rotatably attached to the crane boom and is contoured with a Surface is provided which corresponds to the part of the body to be towed that is engaged with it during lowering and retrieving of the towed body, g) a cable guide device which is rotatably attached to the crane boom and a controlled surface provides around which the cable to one side or the other can swing out while practically in line with the grooved wheel device remains while the body is being dragged, h) means for elastic application of a Turning force on the crane boom to the articulation of the same on the towing vehicle, that is reasonable and responsive to changes to any one exerted on the crane boom Load and / or torque of the same, and i) a compensation mechanism for selective holding of the slide in a usual horizontal position independently from the rotation of the crane boom. 2. Apparatus according to claim 1, characterized in that the carriage (f) has frame parts which are freely rotatably attached to the crane boom (a) and that it also has several pins, each ending in a resilient cap with an arcuate surface that faces downward and engages too bring is with part of the surface of the body to be towed. 3. Apparatus according to claim 1, characterized in that the cable guide device (g) comprises: frame parts which are rotatable about an axis of rotation which is practically of is the same expansion as the axis of rotation of the Riffelradeinrichtung (e) and practical runs parallel to this; a group of side guide rollers that are free are rotatably mounted within the frame part and against which the cable (d) can press during towing operation; a front, freely rotatable roller and a rear, freely rotatable roller, which is mounted on the frame part in one plane which runs transversely to the plane of the lateral guide rollers; and spring biasing means for biasing the cable guide means in such a direction that the front roller Can press against the tow cable regardless of the tow cable angle. 4. Apparatus according to claim 1, characterized in that the means (h) for the elastic application of a torsional force have: (say linear actuator with a compressible fluid attached to the piston rod end the same is filled, the head end being rotatably attached to the front end of the inner frame; (n) a freely rotatable pulley arrangement on the rear The end of the winch frame is mounted; (o) a swivel arm that attaches to the crane boom is at the pivot attachment of the same; and (p) a cable that has at one end the piston rod is connected, the pulley (s) and at the other end is attached to the swivel arm (o). 5. Apparatus according to claim 1, characterized in that the compensation mechanism (i) comprises: (j) roller assemblies attached to the drive means (b) in such a manner are attached to rotate with them; (k) roller assemblies that are mounted coaxially with the carriage on the crane boom; and (1) a cable that takes the roller assemblies (j) and the grooved wheel device (e) with it. 6. Apparatus according to claim 1, characterized in that cable (d) is provided with sheathing members each of which is a solid member consists, the opposite ends of which form surfaces that abut adjacently arranged, in head-to-head alignment, sheathing elements, wherein the cable (d) and the sheathing elements have an electrical conductor, which is attached to the tow vehicle and extends through the cable, and wherein there is also an electric conductor winch for guiding part of the electric conductor between the towing vehicle and the driven winch drum during the and unwinding the cable; that the electric conductor winch has a first storage drum having connected to the driven winch drum is, to rotate in conjunction with this; and that a second, at a distance from the first rnror lamel arranged storage trimmer and a winding mechanism, which grips the electrical conductor at points that are in a bridging relationship with respect to the first and second storage media and are moveable by the Periphery of the winch mechanism for transferring the electrical conductor part captured by it from one drum to the other of these storage drums and in dependence from the rotary movement of the driven winch drum. 7. The device according to claim 1 with the device features (a), (b), (c) and (e), characterized in that the horizontal center line of the drive means (b) is offset by 2 to 3 from the horizontal center line of the crane boom (a). 8. The device according to claim 1 with the Vorrichtunt, characteristics (a) to (g) characterized by (q) a towed body support on the crane boom (a) is attached and designed in such a way that it is to be towed Body inevitably supports when the crane boom is in its maximum inboard position is located. G. Device according to claim o, characterized by (r) one on the ship deck Fixed bracket to support the crane boom (a) when it is is in its maximum inboard position. 10. Device according to claims 8 or 9, characterized by (s) a holding device attached to the stern of the ship to support the crane boom (a) when in its maximum outboard position.