DE2202468A1 - Winch - Google Patents

Description

Jue invention relates »XNE- 5oh3.oppvdLna. ur.-i-d and in particular a control device i'ür such Winds _s as for towing at sea is for example ₉ channels and viasaerstraßen application. Such winches are, however, also suitable for other applications where a dynamic system is required to keep the tension on. Adjust and maintain rope without overloading the rope.

When towing a tf & nntirSahvzevLßß to sea? As aticii in spie-lyweiae drilling rigs, barges, or the like, by means of a tugboat or some other floppy vehicle, problems that are difficult to solve arise. Up to now, load changes on the rope between the pulling and the pulled vehicle, which occurred on the vehicles due to the interactions of the tide, the swell or wind effects, were balanced by the rope itself and the free length of the Therefore ropes have to be extremely long. Between the vehicles there was usually a long, curved ax hanging below the surface of the water

209836/0697

Rope section was created, which can be more or less tensioned Could if the towing and the towed vehicle are different Influences due to the tide, the waves, the river Vindes or the like were exposed, especially when these superimposed on each other ..

Such long lines or ropes make steering the towed vehicle considerably more difficult, especially when entering and navigation in narrow canals or waterways. A heavy barge may require the length of a rope on the order of a quarter of a mile, for example to obtain a rope bow with sufficient safety, with the towing and dao towed vehicle at behave differently to changing external influences without breaking the tow rope. A particularly hot one The problem that arises in this context is the opposite behavior when a vehicle is pulled slows down as soon as it is pulled against a wave crest and a pulling vehicle is subjected to acceleration is as soon as it is picked up by a wave crest pointing in the direction of travel. Provide such long tow ropes also represents an insecurity factor during navigation, especially when visibility is poor and the captain is one other watercraft cannot see the bottom plane, because he either does not see the towed vehicle or perhaps even no vehicle at all. *

Usually the tow rope is on a towing winch and can be run down depending on the prevailing sea conditions and the load to be towed. Depending on the requirements, the winch can be operated to haul in the rope to wipe the distance between the two Vehicles. However, if due to the swell, the tide or the influence of the wind on the vehicles If the rope is overloaded, it can break and cause the towed vehicle to drift, which can be very dangerous

209836/0697

connected is"

The invention therefore relates to a towing winch arrangement, which eliminated the above-mentioned üSaeli parts and uncertainty factors

Inabenondere the invention relates to a Schleppwindenanordnuog, on a sole »hauling of another Fahrseuga or other Roiho Pahraeuge under denser spacing pfahrseug allows ea than was previously the Pall.

The tow winch essentially comprises a winch with one Driven by a coupling with constant slip properties, in order to create a substantially constant tension on the tow rope or cable to be applied As soon as the load on the rope increases above a specified value, the rope runs off the Unwind, however, as soon as the tension decreases again, the rope is rolled onto the winch until the vehicle is pulled again has a predetermined distance from the tractor.

A position sensor and a are available for this purpose connected to the rope and actuated by this to control the slip clutch au, so that the tension is on the rope and the positions of the two vehicles are maintained as long as the different influences on the vehicles maintaining these positions, allow and tension on the rope and positions of the two vehicles opposite each other are restored as soon as the influences on the vehicles or one of these this is permitted.

Slipping clutches operated by fluid pressure for driving winches in order to maintain a constant tension are known, for example, from US Pat. No. 3,373,972. However, in order to design the friction clutch operatively oamsr, en can be expedient to provide an improved Kühloystem as eo-making in the American Patent Office .;] was 19601 ζ of 16 HHR described 1970th

209836/0697

The position indicator is designed so that it changes the fluid pressure for actuating the slip clutch, and is conveniently designed as described in U.S. Patent Application 19564 filed March 16, 1970.

In the drawing, embodiments are shown of the invention _t are explained with reference to the following description, n% forth without thereon a limitation of the invention is to take place "In particular, the invention also apply to other dynamic control systems is suitable in which the tension of a cable and the location of the rope must be controlled or adjusted in order to prevent overloading of the rope and to return a load to its original position depending on changes in the loading conditions. Bs show:

Figure 1 is a perspective view of a tugboat and a sucked barge for visualization the windrow arrangement according to the invention,

FIGS. 2a and 2b together show the control arrangement for the winch, with Bioh FIG. 2b at _{1 below FIG. 2a}

FIG. 3 shows a longitudinal unit through an evaluation switch

or pressure transducer that sur changes the drives the slip clutch as a function of the changes in the load conditions at the bottom face Is used «

FIG. 4 shows a longitudinal section through a position encoder for the rope but change of a pressure signal, which is dependent on the evaluation switch of FIG is initiated by the changes in the position of the tow ropes,

and

209836/0697

Figure 5 partly in aneicht parts in the Iftngaaohnitt the slip clutch to drive the towing winch *

In Figure 1, a tugboat or tugboat V is shown, which has a towing winch V »of which a tow rope or Cable L extends over the stern and is connected to the towed vehicle or the boat B.

Although a rock barge has been shown as an example, the problem of congestion occurs in the tow L also for other pulled loads, such as platform-shaped islands for drilling wells in front of the Coast, damaged ships or the like.

To clarify the representation, the winch W is on the Upper deck of the tugboat shown arranged and a suitable drive or motor M in a lower deck, but can expediently the entire device or individual parts of it are housed in the lower deck, wherein the rope L passed through a guide at the stern of the ship V iat.

In detail, the drive M has a suitable drive connection in the form of a chain 10, which is a Zwisohenwelle can drive via a slip clutch C, as they are in detail shown in Figure 5 and described in more detail below and which is suitable under the control effect of the invention Control device to transmit a torque to the shaft 11 in order to thereby apply the voltage to the Sell L to limit and to determine the mutual position of the towing vehicle V and the boat B. To the Transmission of the torque to the drum 13 of the winch W Iat, for example, a chain 12 is provided, whereby the Hell L

209836/0697

selected can be withdrawn if the / rope tension the Laat dea Kahns B exceeds, but the ax L can run off the drum "if the load of Kahne B has been determined in advance Rope tension exceeds. Bern Seil L uind measuring devices TP assigned that are inserted into the overall system and suitable for the load or tension on the rope L and changes in the To determine the position of the rope L in order to control the rope L accordingly, which is described in more detail below.

According to FIG. 2a, the measuring device TP essentially consists from a hydraulic tension knife 15 and a position transducer 16. The tension knife 15 can be placed on the rope L in this way be that the rope extends between a pair of rollers 17 and 17 and is in engagement with this, which on waves or 20, which are provided in a frame 21, is rotatable. A third roller 22 is with the rope L between the rollers 17 and 18 in connection in order to steer the middle section of the rope L, the pulley 22 being guided on a rope 23 which is rotatably mounted in the frame 21, its movement being fed to a hydraulic sensor unit 24, which generates a hydraulic signal, the magnitude of which is a function of the tension of the rope L. Such facilities 15 are generally known and therefore do not need n'-iher to be described. One such sea is for example the tensiometer device model UD12 from the company Martin-Decker Corp., Santa Ana, California. The LagemeQ value transmitter 16 of the measuring device TF is in detail * in Figure 4 and will be explained in more detail later.

To speed too. control, with which the rope L can change its position, a speed measuring device with a generator 25 but delivery of a speed signal is provided, which is driven by the winch drum 13 and supplies a variable signal to an electropneumatic converter 26, which corresponds to the model T-10, for example supplied by Conoflow Corporation of Blackwood, New Jersey. the

209836/0697

Outputs of the hydraulic unit 15, the LagemeQwertgebera 16 and the converter 26 are in an Äuswerteinrichtung compared, the details of which are shown in Figure 3, to control the clutch C, which is described in more detail below will·

As can be seen from FIG. 5, the clutch G is provided at one end 37 of the intermediate shaft 11. The chain is in engagement with a sprocket 50, which is rotatably supported by means of bearings 52 on the shaft 11 relative to this iat. A disk 54 is attached to the sprocket 50, which in turn by means of fasteners 55 ara sweeter scope a rear plate 56 of the slip clutch C attached let.

The slip clutch C has an outer housing ring 57, An annular flange 58 is soldered to the side opposite the plate by means of fastening elements 59 is. Within the housing ring 57 is a spline connection 60 with the outer periphery of an axial one reciprocating clutch pressure disc 61 is provided. Between the clutch disks 56 and 61, a friction disk 62 with a friction lining 63 is provided on both sides, which, as shown at 64, has a Kellnuten connection with a hub 65 on the free end of the line 37 is provided and fastened by means of a feather key 66. In this way, the rotation of the sprocket 50 is increased the intermediate idler shaft 11 transferred when the slip clutch C is indented so that the rotation of the housing ring 57 and the disks 56 and 61 is transmitted to the friction disk 62.

The engagement of the slip clutch C takes place by means of an annular, expandable actuation hose 67 with an air inlet 68. The actuation hose 67 stands with an annular Body of insulating material 69 engaged between the hose 67 and the clutch pressure disc is arranged. Both clutch plates 56 and 61 have one

209836/0697

Number of concentric cooling channels 56a and 61a spaced apart from one another in the radial direction, which Coolant is supplied in order to discharge the T-Irme occurring by the frictional engagement of the clutch C. This channel 36a and 61a are between the clutch plates and, respectively a YerschleiOscheibe 56b on the disk 56 and one Wear disk 61b provided on disk 61, wherein the friction lining 6? the friction disk 62 engages with the wear disks 56b and 61b.

In this "ice-cooled slip clutches are known and generally provided with a coolant circulation system, which has a stationary coolant connection 71 through which the coolant is fed to a circulating distributor 72 and is discharged therefrom, which is fastened to the coupling flange 58, for example by means of fastening elements 72a, and has a line 73 in order to supply the coolant Channels 56a and 61a, and also lines to feed the Return coolant to the distributor 71 in order to feed it from there to a heat exchanger. In order to cool the clutch even more effectively, uie can be constructed in accordance with the above-mentioned patent application. The circulating distributor 72 has in addition, an air line 74 which leads to the air inlet of the actuation hose 67 from a stationary air inlet 75. As is well known, there is a need for the transferable Torque of such a slip clutch from the air pressure in the actuating machine 67.

In this way, the tension applied to the ax L is determined by the magnitude of the air pressure applied to the actuation hose 67 via the connection 75 as a result of the control is supplied by the evaluation device 27, which will be described in more detail below.

209836/0697

A preferred embodiment of the device 16 for determining the position of the ax of the measuring device TP is enlarged shown in detail in FIG. *> ie consists of an elongated GeMuse 81 with a termination and a cap 82 at one end and an assembly at the other end which has an inlet or feed opening 84 for air, an outlet opening 85 for a controlled air pressure signal, an opening 86 for buffer pressure fluid and has an opening 87 which is in communication with the atmosphere.

An actuating device is provided within the arrangement, generally indicated at 88, a fluid pressure responsive I-piston assembly 89, the is in a Wiricungsverbindungen with the actuator, an opening assembly 90, which is dependent on the the piston device 89 supplied fluid pressure and the force supplied by the actuating device 88 for opening and closing the opening device 90 can be actuated and a combined inlet and outlet valve 91 for controlling the flow of air from the inlet port to the outlet opening 85 and to control the air outleta au «the exit opening to the atra-eye through the opening 87 ·

It is generally the task of the pneumatic control device to determine the position to regulate the output pressure signal to a constant value which is determined by the usable force which is supplied to the piston device 89, whereby the opening arrangement 90 is either opened or closed for a certain period of time, sufficient to provide the Kolboneinrichtung 89, compensate so that the pressure drop remains constant dor opening 90, which has a konotanten Auagangenigruildruck at the mouth of the result of the supplied 27 which subsequently br nUher the Aunwert'stni'lohtung: uuhrie) iua wirrt.

8 1 h /

In detail, the actuating device 88 comprises an Achae 92, which extends in the longitudinal direction through the housing 81 and has an end 93 that extends axially through the cap 82 a suitable bearing 94 and seal 95 extends therethrough. On the axis 92 within the housing 81 is a spring support with a central section smaller diameters provided on which the upper end a helical compression spring 90 is guided. The axis 92 iut provided at 99 with a screw thread and the spring support 96 and the guide portion 97 are with a corresponding one Provided thread, so that by rotating the axis 92, the spring bearing 96 on the axis 92 executes an axially directed movement, since the bearing 96 is prevented from rotating by a pin guided on this which extends into a lateral slot in the frame 81. At the inward end is the spring 93 on a spring support 103, the one Has guide section 104 of smaller diameter. This spring support 103 is attached to the upper ring section 106 of a piston 107 by means of fastening devices 105 Piston device 89 attached. The support 103 and the hanging section 106 are made up of tubular dancers held at a certain axial distance which are provided between them and through which the fastening means 105 extend therethrough. The lower end of the Axis 92 extends through the support 103 and is rotatably mounted in a bearing 109, which is guided in a spider 110, so that openings are distributed around the circumference 111 has in order to receive the tubular diameter pieces 108, whereby the piston device 89 is axially movable.

The arrangement further includes in addition to the spider 110 a spacer ring 112, an annular cylinder 113 for the piston 107 and an annular cylinder 114 »in the a piston 115 is arranged, an annular body 116, which contains the opening arrangement 90 and a bottom part 117.

209836/0697

The spider 110, the spacer ring 112, the cylinders 113 and 114, the annular body 116 and the end part 117 are connected to one another by means of screw bolts or the like and form the cylindrical body 81 * / between the spacer ring 112 and the cylinder 113, the outer peripheral portion is one Diaphragm 119 is clamped and the outer circumferential section of a further diaphragm 120 is clamped between the cylinder 113 and the cylinder 114. Another membrane 121 is clamped with its outer circumferential area between the cylinder 114 and the ring body 116. As can be seen from the drawing, the part 106 of the piston 107 as well as the piston 107 and the piston 115 are connected to one another by a bolt 122, which has an enlarged head 123 at one end, which the inner Urafangbereich of the diaphragm 121 against the adjacent area of the piston 115 is clamped and a nut is screwed onto the other end of the ßolzeno 122 in order to firmly clamp the upper section 106 of the piston 107 with the actual piston 107. The inner peripheral edge of the diaphragm 119 is braced in the same way between the upper part 106 and the piston 107 ₍ and the inner peripheral area of the diaphragm 120 is braced between the piston and the piston 115 also the piston 115. In addition, the piston 107 has an enlarged section 125 which is exposed to the pressure within a chamber 126 which prevails in the cylinder 113 between the diaphragms 119 and 119. The piston 115 is subjected to the pressure in the chamber 127, which in the annular housing section 116 prevails over essentially the entire cross-sectional area of the piston 115. Within the cylinder 1.14, the piston 115 is arranged in a chamber 128 which is vented from the atmosphere through radial openings 129.

209836/0 69 7

Clamped between the ring-shaped body 116 and the bottom part and on the outer peripheral edge is a double membrane arrangement with an upper membrane 130 and a lower membrane 131 which are held at a distance from one another by a spacer ring 132 on the outer circumference, in which one or more of the already mentioned radial exit openings 87 are arranged, which connect the space between the membranes 13ü and 131 with the atmosphere. A chamber 134 is provided in the ring body 116 above the upper membrane 130 and a threaded bore is arranged in the center of the body, in which a nozzle 136 is located, the bore of which communicates with the chamber 134 and the outlet opening of which is arranged opposite a nozzle seat 137 , the aweckm ^: ißigerweiee is provided at the lower end of the bolt 122. The chamber 134 and from there the nozzle 136 is supplied with air through the inlet opening 84 via a channel 138 which extends through the edge of the membrane 130 and 131 and the spacing ring 132 and is in communication with a channel 139 which is connected to the chamber 134 leads. In the channel 139 a flow limiter 140 is provided which has a constricted passage. This flow limiter 140 can be replaced by an opening in the body 116, which opening can be closed by a threaded locking screw HI. On the outside of the membrane 131, a chamber 142 is formed in the closing part 117, which is in communication with the outlet opening 85. The exit opening 85 is also connected via a channel 143 to the chamber 127 in the body 116 below the membrane 121.

The inlet and outlet valve 91 includes a valve seat 144 on a plate 145 below the membrane 131 and has a valve opening I46, which is from the exit camera 142 leads into the space between the membranes 130 and 131. TSine

209836/0697

Helical compression spring 145a is provided below the plate 145, which biases vertically inwards exerts on the diaphragm 131 and the exit valve seat 144. A valve rod 147 is reciprocable in a bore 147a in the .Abschlusseil 117 out, which of the Inlet 84 leads to Aualaß 85 · The pole usually stands under an inward bias applied by a helical compression spring 148, which is in a Screw 149 is mounted in the closure part 170 and acts inwards on a spherical valve head 150, around this opposite an inlet valve seat 151 below To keep bias.

As already mentioned, the pneumatic control device for determining the position works in such a way that it regulates the output signal pressure at the opening 85 to a value which is proportional to the measured movement. Accordingly, on the outer free end 93 of the axle, a drive pulley or pulley 17 of the pulling measure 15 is arranged, which engages with the cable or Sell L to rotate the axle 92 depending on the relative movement between the rope L and the transducer. The movement of the rope L is transmitted to the axis 92 in order to rotate it in one direction or the other, which depends on the direction of movement of the rope L. It can be readily seen that if the axis 92 is rotated in one direction or the other, a greater or lesser compression exerts on the spring 98 in order to apply a greater or lesser force to the piston device 89, which either sets the nozzle 1:57 causes the nozzle 136 to close or to open in order to establish a connection to the chamber 127 and thus to the discharge or signal outlet opening 85 , and the! fluid pressure in chamber 126 which is applied to the

209836/0697

acted upon surface of the piston 107 acts. To these catfish can flow fluid through the opening 86 of the chamber 126 from a remote point to the motion transducer quickly and easily to be calibrated so that the signal output pressure assumes a desired / ert below the input pressure under the condition that the axis 92 is in the neutral or stationary position.

The movement measuring value transmitter then works in the since the spring 98 applies a variable force in a direction which tends to move the piston device 89 towards to move downwards · The force derived from the actuating device counteracts a force that is generated by the application of the pressure on the prestressing or calibration chamber

126 is derived from a distant point, this pressure being applied to the area of the magnification 125 of the piston device 89 for generating a force effective is striving to move the piston device naoh up. Another force which tends to move the piston device 89 upwards is the pressure in the Piston chamber 127, which acts on the piston device 89 via the piston 115, the other side of the Piston 115 is exposed to the atmospheric pressure in chamber 128.

The actually hollow signal output pressure in the piston chamber depends on the decrease in inlet pressure caused by air from inlet 84 flows through the flow limiter 140 into the control pressure chamber, and from the reduction in pressure daduroh that Air from the control pressure chamber 134 through the opening 136 flows into the piston chamber 127, which is illustrated by the arrows. If the facility is able to comply with HQ Figure 4 is, the effective signal output pressure is on the outlet opening 85 is equal to the pressure in the piston chamber

127 and under the specified condition the pressure drop from inlet 84 to outlet 85 remains constant, if not

209836/0697

the force derived from the actuating device 88 or changing the force derived from the pressure set from a distant point.

Assuming that the force is reduced which is derived from the actuating device which tries to To move the piston device 89 downwards, the effective, usable force on the piston device becomes endeavor to move the piston device upwards, so that a greater flow from the control pressure chamber 134 can take place in the piston chamber 127. Such an effect has an immediate decrease in the control pressure in the chamber 134- result. Accordingly move the on the membrane 131 applied pressure and the force of the spring 145a push the exhaust valve seat 144 up and from the end of the valve rod 147 away, ao that the fluid pressure from the outlet chamber 142 and the piston karamer 127 through the outlet opening 87 can escape, as the device again assumes the position according to Figure 4, in which the outlet valve 146 is closed again. At this point in time, the pressure at the outlet opening 85 is stabilized again to a value that caused by the fluid pressures acting on the actuator 88 and the reduced force the spring 98 is determined. A larger amount of air flows past the muzzle lock 137 and the signal output pressure adjusts to a lower tfert.

Assume that the force derived from the actuator tending to affect the piston assembly to move down, is enlarged and the 'font of the Signal output pressure in chamber 127 exceeds then When the orifice closure disc 137 engages the mouth of the bore of the nozzle 136, thereby removing the air path from the control pressure chamber 134 is interrupted in the piston chamber 127 will. Under these conditions, the control pressure is built up in the control chamber 134, the diaphragm 130 and the Presses membrane 131 downwards, whereby the valve 150 is lifted from the seat, so that the inlet pressure aich through

209836/0697

the hole H7a of the inlet 8 / JUiBrittventlie 91 expands » resulting in an increase in the signal output pressure in the output chamber 142 and in the piston chamber 127 in order to thereby "bring the device back into the position which is shown in Figure 4, so that the pressure at outlet 85 again remains constant, but greater.

It can then be seen that there is a change in pressure in chamber 126 from a remote location has the same effect as changing that of the actuator derived force. In other words, it says that if from a remote location from set - ^ ruok is increased, the force also increases that tends to push the piston device 39 upwards asu, but that if the distant one Place set pressure is reduced, the force that tends to push the piston device 89 upwards is reduced to press. The air supply to the chamber 126 through the opening can be seen in FIG. 2a and takes place via a line 86a, which comes from a suitable valve 86b which controls the pressure supplied by a supply line 86c which is supplied by a Suitable pressure source, not shown, comes. The outlet opening 85 is in communication with a line 85a, the leads to the evaluation device 27 described below.

According to FIG. 3, this evaluation device 27 has a console which is intended to be attached to a suitable location. The console 200 carries an end cap 201 with a Peripheral flange 202 for connecting the cap 201 with a Arrangement consisting of a stack of disks 203, 204, 205, 206 and 207 and a housing body 208, all of which are attached to the outer circumference by a suitable number of fastening screws one of which is shown at 209.

209836/06 9 7

The disc 203 has a solid central portion 203 * and a resilient ^{annular membrane 2QJt 1} 'that supports the central portion 203' within the disc 203. Similarly, each of the disks 204t 205, 206 and 207 includes a rigid solid central portion 204 * to 207 'and an annular diaphragm 204 "to 207 *". Between the disks 203 and 207, annular spacer pieces 210, which run on the outer circumference, and central spacers 211 are provided. The outer Abatandöteile 210 are fixed in the overall arrangement by the fastening screw bolts 209. The central spacers 211 are connected to the respective central sections 203 'to 207 * by a pin 212 which carries a head 213 at its lower end and a nut 214 at its upper end to hold the piston sections and the central spacers together.

Pressurized fluid, such as air, is supplied above and below the membrane stack and between the membranes from various sources from the evaluation device 27, whereby an output pressure signal is formed which is a puncture of the various input signals and the constant force of an adjustable helical spring K. , which is arranged inside the cap 201 and rests with one end on a seat 215 above the sole plate portion 203 * and with the other end on a spring support 216 which is carried by an axially reciprocating adjustment pin. The alignment pin 217 is reciprocated by a set screw 218 and herteregbar, which is guided by means of a thread in a nut 219 which is fixed appropriately on the die'in Konuole 200 * Below the disc 207 is a v / urther coil spring K ¹ provided which is mounted with one end on a support 208 'and with its other end underneath the disk part 207' acting against the action of the spring K. In this way, the spring K t; o can be adjusted so that it exerts a desired force on the stack at the solenoids 203 * to 207 *, which is determined by the relationship between the springs K

209836/0697

and K 'is determined.

Air under pressure is transferred to a chamber P1 in the cap 201 from the laying transducer 16 via the line 85a suitable organs supplied, for example an inlet nozzle 220, to a downward force on the impactable piston area of the central section 203 * of the disk 203 to exercise. To increase the size of the 'Force that the pressurized air from the position sensor 16 via the line 85a of the evaluation device 27 feeds, a branch line 85b is led to a chamber P2, which is formed between the membranes 203 "and 204", through a pressure inlet 221, so that this pressure also acts downwards on the pressurizable annular piston area of the central portion 204 * of the disc 204, which is located radially outside of the above this Spacers 211 is located.

Below the annular piston area of the disk section 204 * let a chamber H is provided, which has an inlet 222 has »by the pressurized fluid in the manner described in more detail below is supplied in an order of magnitude that is determined by the evaluation device 27 is determined, wherein the pressure in the chamber R upwards on the pressurizable annular piston area of the Soheibenabschnittes 204 'is effective against the downward force, which is caused by the pressure in the chambers P1 and P2 is derived.

A pressure chamber F is formed between the disks 205 and 206, to which air is supplied through an inlet 223 via a line 26a at a pressure which is determined by the The speed of rotation of the drum 13 is determined, especially under the control effect of the electro-pneumatic converter 26 happens in the previously described Veise. The Soheibenabachabschnitt 206 'forms an annular piston area, the

209836/0697

Bich located radially outside the above located therein spacer 211, said piston area responsive to the pressure in the chamber S, au an effective downward force deliver "below the disc portion 206 'is a further chamber formed ¹ S, the air above a Opening 224 is supplied with a pressure predetermined by the voltage in the Geil L, which will be described in more detail below. This pressure acts upwards on the pressurizable annular piston area of the disk section 206 ■.

Underneath the disk 207 and in the body 208, a chamber X is formed which forms an outlet chamber which is connected to an outlet opening 225 via a duct system 226. The pressure in the chamber acts upwards on the lower disk section 207 ^f and the pressure is fed from the inlet line 27a (Figure 2a) under the control of the evaluation device to the inlet hopper 227 »

Between the body 208 and a closing element with the openings 225 and 227, a double diaphragm arrangement 229 is clamped at its outer peripheral edge, which consists of an upper diaphragm 230 and a lower diaphragm, which by a spacer 232 on the HuSeren Urafangrand at a certain distance held v / ground, in which one or more radial outlet openings 232a are formed, which connect the space between the membranes 230 and the atmosphere. In the body 208, a threaded hole is provided above the upper diaphragm 230, is screwed into the nozzle 236 ₅ whose bore communicates with the space X in compound whose Hündung be acted upon by a valve head, which in a suitable manner from the downwardly facing end of the Zapfen «212 is carried. The chamber 234 is supplied with air and from there, the nozzle 236 from the feed opening 227 via a Ka.iu.il ijB, which extends through the edge of the membrane 230 and 231 and laij /.t^candyslück 232 and with a Kanrü 233 in connection »teht, doc ·

C C 3 7

leads into chamber X. There is a flow restrictor in channel 239 240 provided with a reduced passage. This flow restrictor 240 can through an opening in the body 208 are replaced by a screw plug 241 is lockable. At the bottom of the membrane 231 is in the closure element 228, a chamber 242 is formed which communicates with the outlet opening 225. The outlet opening 225 is still in the previously described Way via the channel 226 with the chamber X in the body below the piston or disk portion 207 * in connection.

An inlet and outlet valve is used to control the Fluid inflow from inlet 227 to chamber 242 and to the outlet of the fluid through the vent 232a provided. This valve comprises a valve seat 244 on a plate 245 below the diaphragm 231 and has a valve port 246 leading from the exit chamber leads into the space between the membranes 230 and 231. A compression coil spring 245 a is provided below the plate 245 and places a normal upward bias on diaphragm 231 and the exhaust valve seat on. A valve rod 247 is guided to and fro in a bore 247a in the closing element 228, the Bore leads from the inlet 227 to the outlet chamber 242. The bar is usually under an inward one applied by the helical compression spring 248 bias in a screw 249 within the closing element 228 is guided and inwardly on a spherical valve head 250 is effective to expose this to a bias in the direction of the Einlaßventiloitzes 251.

209836/0697

As already mentioned, the evaluation device works in the way that you have the eye eye pressure on the opening set to a value that is proportional to the load on the Heil L or its location as well as the speed the drum 13? and the evaluation device can additionally be set so that üio changes the outlet pressure by that either the effective constant force of the spring K or the predetermined suction pressure in the chamber R changes will. The output pressure of chamber X is then through the different pressures in the different chambers P1, P2, R, S and T are determined on the different pistons areas of the disks 2025 to 207 are effective. Ee can then the following equation can be set up:

X = P1 + Ρ2-Κ + Π-Τ + Odsü- K,

where P1 and P2 are the pressure, which is derived from the position of the position sensor 16 and tends to the nozzle 236 to close, R is the pressure derived from a reference pressure source and tends to open the Düae 236, S is the pressure derived from the speed of the drum 13 and tending to üchliaßen the nozzle 236, T is the pressure derived from the train measer 15 and tends to open nozzle 236 and K is the spring rate.

The effective signal output pressure in the output chamber 242 represents a puncture of the decrease in inlet pressure, that by the air flow from inlet 227 through the flow restrictor 240 is caused in the control pressure chamber 234, and the decrease in pressure due to the air flow from the control pressure chamber 234 through the opening 236 into the Pressure chamber X, which is illustrated by the arrows. When the device is in the position straight in Figure 3, is the effective f; L ^ nal outlet pressure at outlet 225 same as that in chamber X and below the Becji / .gung shown the pressure drop from inlet 227 to outlet 225 remains constant, whereby the force is not changed,

209836/0697

from the LagemeGeinrichtung TP, the tachometer 25 or is derived from the reference pressure and accordingly - which will be described in more detail below - that of clutch C. applied actuation pressure remains constant.

Assuming that the force to move the stacked disk sections moves the valve head 237 upwards, so that a larger flow can take place from the internal pressure chamber 234 into the chamber X, this results in a decrease in the control pressure in the chamber 234 result. The pressure applied to the diaphragm and the force of spring 245a consequently move outlet valve seat 244 upward and away from the free end of valve rod 247 to discharge fluid pressure from outlet chamber 242 and chamber X through outlet port 232a between the membranes 230 and 231 until the device assumes the position according to FIG. 3 again, in which the outlet valve opening 246 is closed again. At this time, the pressure is returned to a lower at the outlet 225; ert stabilized, the lot is determined by the change of the forces ^f of the stack of slice sections 203-207 · are effective.

If it is now assumed that the usable force tending to move the stacked disks 203 * to 207 'downward is increased, exceeding the effect of the signal output pressure in the chamber X, then the valve body 237 closes the valve opening 236 whereby the flow of air from control pressure chamber 234 to chamber X is interrupted. Under these UmstHnden the control pressure in the control chamber 234 constructed which presses the diaphragm 230 and the diaphragm downward, whereby the valve 250 is unseated, ao that the Eintrittsdruok passes through the bore 247a of the intake / ^A u8T-8jTveritilü, which results in an increase in the signal output pressure a in the output chamber 242 and the chamber X, which in turn leads the device to the position according to FIG

209836/0697

- 23 less current takes place through the opening 236.

A line 300 leads from the outlet opening 225 of the evaluation device 27 to a control pressure inlet 301 the pressure control device Ci of known type, which is designed is that it controls pneumatic pressure at an output from a suitable source, not shown is supplied through an inlet 303, whereby what will be described below, the slip clutch C in the Is able to apply a controlled constant torque to the drum 13 which is a function of the output signal pressure the evaluation or converter device 27 represents.

The control device G1 can, in particular, be the model 50 Controller from Moore Products Co., Spring House, Pennsylvania, or a Model 2516 controller from the Company Pisaer Gpverner Company, Karohalltown, Iowa, being »where the control device is shown generally in Figure 2b, which is roughly the illustration in Bulletin D-2506A of this company is equivalent to.

The control device CI receives a reference printout at the entrance from a line 305 which is connected via a control valve 306 to a source not shown, where the same reference pressure of the flexion chamber R is the evaluation or Converter unit 27 is supplied. This reference pressure is passed into a bellows 307 of the control device, the down on a plate 308 is effective »The pressure supplied to the inlet 30t by the device 27 causes a Pressure rise in a bellows 309 which is arranged opposite the bellows and which acts downwards on the plate 308. The position of the plate 308 opposite a nozzle 310 to which a controlled flow pressure from the inlet 303 is supplied is determined by the pressure difference in the bellows 307 and 307. v »hen the exit pressure from the evaluation device

209836/0897

grows, the jolt enters your bellows 309 and moves the Plate 308 closer to nozzle 310, reducing the flow through the nozzle, resulting in an increase in pressure in a chamber 311 of a control valve 312 has to follow, which exerts an increased downward force on a membrane assembly that is at a distance from one another having membranes 313 and 314, which carry a valve seat 315. The passage through this stands with the Atmosphere via an opening 316 between the membranes and 314 in connection. The valve seat 315 is in engagement with an inlet and outlet valve under the conditions now described and presses this afterwards below, a head 317 for closing an Aualaßkanals running through the valve seat 315 and a head which can be lifted from a seat 319 so that increased feed pressure can enter a valve outlet duct 320 can, which is effective on the membrane 3H until the valve seat 315 has been moved upwards again to the to allow return movement of the inlet / outlet valve head 318 in the direction of the deusen seat, which is grooved above.

At the same time the pressure in the chamber 320 increases this pressure is fed to outlet 302 and thus to clutch C and also to an adjustable metering valve 321 and depending on the attitude of this one adjustable reset valve 322, which controls the build-up of pressure in a bellows 323. This bellows 323 is after effective down on the plate 308 and strives to lift this from the nozzle 310 to the pressure at the outlet 302 and in the control valve chamber 320 to reduce. This effect the effect of a Balrje 324, which is directed closer to the top and to which pressure is supplied more slowly by the valve 322, is opposite, depending on the setting of the valve 322 is until the plate 308 is moved in the direction of the nozzle 310 in order to restore the pressure at the outlet 302 and in the valve karamer 320 increase.

209836/0 6 97

In the event of a change within the system, there is a pressure drop triggers at inlet 301 to control device C1, occurs reverse effect within the control device, whereby there is always the tendency ^ to a previously existing, return constant pressure to output 302, whereby this pressure is a function of the output pressure of the Chamber X of the evaluation device described above. 27 represents.

The exit pressure from the control device G1 is passed via a line 325 to trigger the action of the clutch C, although a conventional servo device 326 is expediently used. The actual pressure source, which is not shown, for the clutch has an inlet to the servo device 326 of relatively high pressure, and the pressure in the line 325 wij & t on a conventional control valve for the servo device, so that the output 328 of the servo device Alo the signal pressure from the control device .C1 has a higher pressure. In addition, an automatic selector valve 329 can expediently be provided so that the air inlet 75 of clutch C can be connected either to the output 328 of the servo device or, alternatively, to a separate electrical line 330, which is connected to . Has hand operated control valve for actuating the clutch C independently of the control system.

A second control device 02 is used, as already mentioned, in order to change the pressure which is supplied to the chamber T of the converter device 27 as a function of the cable tension in order to adjust the output signal pressure of the atuj value device in accordance with the above equation door the pressure of the chamber X to. impede.

200836/0 ^ 97

From the hydraulic load cell 24 of the access 15 of the measuring device TP, a line 331 leads to the control device 02, whereby a hydraulic pressure signal dependent on the load on or tension in the cable L is transmitted to the control device C2 through the line 331 to control the pneumatic To control pressure supplied to control outlet 332 from inlet 333. This control device '02 can be, for example, a remotely operable proportional controller or converter according to model 4151 from Fieher Governor Company, as shown in Bulletin D-415OC.

In the case of the control device shown in the drawing 02 is a device that responds to hydraulic pressure Bourdon tube 334 "with an increase in pressure in the. '{Eye of a Plate 335 in the direction of an outlet nozzle 36 for the control a valve 337 presses, and a pressure decrease in the tube, the plate 335 τοη the DÜ3e 336 moves away to the Druok in the Ventilkamiaer 333 to change when the measured hydraulic pressure signal is decreased in order to decrease or increase the Justrittsdruok at the outlet 333 and in the chamber T of the control device 27, whereby the actual result is the application of a pressure in the Clutch C, which depends on the voltage in Hell L.

The control valve 337 is designed similarly to the control valve 312 and has a membrane arrangement with a membrane on »which is exposed to the pressure in the Kamiaer 338, the is derived from the inlet 333, and a diaphragm 340 which is exposed to the pressure in the valve chamber 341, the is connected to the output 332. This membrane arrangement carries a valve seat 342, the bore of which with the atmosphere via an opening;> 34 communicates. A combined ElnLuQ-AualaQventll has a head with a seat 342 can be engaged to prevent the escape of the Prevent pressure from the chamber 341 and a head 345

209836/0697

can be brought into engagement with a seat 346, of which Bore with the inlet 333 and the chamber 341 is in communication.

y / hereinafter hen the pressure in the Bourdon-Hoar 334 increases, due to an increase in the iJpannung in the cable L, so dae Ablaaeen the pressure in the chamber 338 is limited _f wae an increase of pressure on the membrane 339 to the episode has , ao that the valve seat 342 with the valve head 344 in. Singriff arrives, whereby the escape of air from the chamber 341 through the automatic opening 343 is prevented and at the same time the valve head 345 is lifted from its seat, so that a pressure increase in the chamber 341 can take place, which tends to return the diaphragm to its initial position " respectively.

Such increased pressure in the chamber 341 is fed to an adjustable valve 347, and from there to a bellows 349, which acts on a plate 335 to remove it from the Move nozzle 336 to lower the pressure in chamber 338. Such movement of the plate 335 acts Bellows 350 with an inlet 351 against which a pressure preset at a remote location is supplied, which can be done by means of a regulating valve 352, the fluid from a suitable source, not shown is supplied, which can be, for example, the same source as that providing the inflection pressure for the fire device 01 and the Auawert- or Y / andleinrichtung 27 supplies.

A decrease in the hydraulic signal pressure from the draw knife 15 to the controller C2 causes the plate 335 to lift off the nozzle 334 and the pressure to decrease in the 3 control valve chamber 338, waa an opening of the bore is valve seat 342 and a decrease in the signal at the output 332 and the evaluation chamber T results in »d.fcu that in the

2 03 3 3 B, ':

- do -

the last-mentioned case, the actuation of the control device takes place opposite to that described above, which should be understandable without further explanation.

Advantageously, a measuring console G according to FIG. 2b is provided for displaying the effective pressures, which are determined by the bearing measured value sensor Kj, the speed sensor 26, the tension meter 15 for the tension in or the load on the rope L, the reference pressure, the preset pressure for the control device C2 and finally the pressure for actuating the slip clutch Q _f, whereby the corresponding measuring devices can be designated as follows:

"POS.", "REFERENCE", "WALKING WALK.", "LOAD", "DEFAULT ?." and "COUPLING"

The "PQS." Measuring device is connected to the output of the Lagonießwertgebers 16 via a line 400, which branches off from the line 85a, which leads to the Auawertkammern P1 and P2. Daa "REFERENCE" -MeßgerHt did connected by a line 401 to the line 305, both au the input 504 of the control means C1 and leads to chamber R of Auowerteinrichtung 27th The "SPEED" measuring device is connected by means of a line 402 to the line 26a which leads to the chamber i> of the ejector device 27 from the electro-pneumatic transducer 26, which is responsive to the drum speed. The "LOAD" measuring device is connected via a line 403 and a line 404 to the output 332 of the control device 02 , which responds to the load or voltage, and to the chamber T of the evaluation device 27. The "VOKGABE ⁿ -MeßgerHt is connected via a line 405 between the specification input 351, the control device C2 responding to the load and the feed control valve 352.

209836/0697

The "COUPLING" measuring device is displayed by means of a line 406 the Lufteintrltteaneehluß 75 of clutch G and the outlet of the selector valve 329 connected *

The mode of action of the invention against the case should be shown below the control of the slip clutch for the drum 15 is clear let recognize »which makes it possible to apply to the rope L a controlled tension in the way that this Tension is maintained substantially constant below a value determined by the predetermined a load of better pressure is given, but the supply of air to the clutch in automatic operation can be controlled by changes in the load or position, which is determined by the measuring device TP, whereby with increased load the rope with by the size of the increased load of predetermined rope speed is released from the drum, the rope tension is restored the given value is reached, and dao Geil is then rolled back onto the drum to readjust the load against the towing vehicle. The speed and is the amount of rope movement in both directions by the speed measuring device 25, 26 and the position measuring device 16 for changing the actuation of the Coupling measurable »to maintain a previously set tension in the rope and a speed of the drum, which are suitable for returning the rope to a given position at a controlled speed

In this way, in the case of all external influences, such as ¹ line, wind and other forces, vehicle B and do are drawn on to dao. " Towing vehicle V, the towed vehicle is held in the NHho of the towing vehicle without the risk of the rope L breaking.

209836/0697

If one also assumes that a speed reference signal of Ot63 kg / cm is fed to the evaluation camera S when the drum is up, a reference pressure of O ₉ 35 kg / cm is fed to the input 304 of the control device CI and the chamber Ii of the evaluation device 27, which Control device C2

supplies a load or tension reference pressure of 0.63 kg / cm to the chamber T at a predetermined rope tension and the position sensor 16 supplies a position of 0.35 kg / cm ² to the chambers p1 and P2 of the evaluation device 27, then has the equation , which represents the output pressure of the evaluation device, has the following form:

X npi + P2 - R + -S - T

X = 0.35 + 0.35-0.35 + 0.63-0.63

X = 0.35

Under these conditions the Auaganga signal is at the input the control device C1 of the evaluation device the same as the reference input pressure signal at input 304 * and thus the signal pressure supplied to the servo unit 326 remains Actuation of the clutch and the rope tension constant, the caused by the torque transmitted through clutch C.

When the pleasure in the rope L decreases because the towed vehicle moves onto the towing vehicle, so that the load signal pressure from the draw knife 15 and from the control device C2 decreases to 0.56 kg / cm, the following relationship applies:

I a Pi + P2 - R + S - T

X = 0.35 + 0.35 - 0.35 + 0.63 - 0.56 X a 0.42

Under these conditions, the output signal at the input 301 of the control device C1 is 0.42 kg / cm, the pull signal, however, 0.35 kg / om ² , which results in a pressure increase in the chamber

209836/0697

of the control valve 2 "ut> ci uair.it one; pressure increase at the outlet 302 of the control device CI by an increase in the pressure as a result, the d * r Bet'lt.,. ^,., ^ tu irich-L-anc- "er coupling with the aim of performing eats, ds <ß rope ^ .a ^ holan. If vice versa the Laot on rope L increases, the balance pressure but Actuation of the clutch abc

Under these conditions, however, changes in position are dee Ropes expressed by the pressure signal transmitted by the from Position sensor-controlled control device C2 is derived, so that when calibrated the rope moves in or out, the actual pressure in the chambers P 1 and P2 of the evaluation device 27 is changed by the position sensor and the effective bridge in the chamber S of the evaluation device is changeable by the drum speed, resulting in a control system that is used to maintain However, it is suitable for a certain position of the towed vehicle under constant voltage conditions allows the rope to be removed from the drum with an increased load beyond a predetermined value let the rope run at a predetermined speed. The system can actually go to a state of equilibrium when it is subjected to loads on the rope that differ from the load to which the System is preset. The system automatically returns the rope to the pre-set position if that Rope is exposed to the preset tension *

- Ansprttohe-

209836/0697

Claims (1)

- 32 - Expectations: Winch, characterized by an adjustable slip clutch (C) for driving a winch drum (13) with a Torque determined by the load on the rope (L) on the winch and control devices (15, C2, 27, CI, 67) for the construction a pre-determined rope layer with a pre-selected rope tension, whereby the control unit organs (16,27, CI, 67) for adjusting the slip clutch, so that the sell (L) from the drum in a predetermined Relation of the rope speed to the increased rope load and to the return of the rope (L) into the predetermined soil layer as soon as the rope tension reaches the previously selected rope tension again. 2. Winch according to claim 1, characterized in that devices (25,26,27,01,67) for controlling the speed of the drum (13) are provided. 5 «winch according to claims 1 and 2, characterized in that da8 the control device has a pulling knife (15) that can be operated by the rope (L) and one by the sell (L) has actuatable position measuring transducer (16), which the slip clutch Depending on load changes and Adjust the position changes of the ropes (L). 4 ο winch according to claim 3 _f daduroh characterized that, in addition, organs (25f26) responsive to the speed are provided for controlling the movement level of the rope (L). 209836/0697 5. winch according to claim 1 to 4 »characterized in that that the rope (L) mounted on the winch drum (13) can be connected to a load (B), that devices (M) for driving the winch drum for taking up and unwinding the rope from the winch drum and a control device it is provided that the drive device for the winch drum (13) has a slip clutch (G) an actuating device (67) which is used to adjust the torque to be transmitted to the drum It is controllable that measuring devices (T, P) are provided which act on the load on the rope (L) and the movement dea rope (L) respond, and that control devices (27 * 01,02) respond to the measuring devices (T? P) to to adjust the notification device (67), which is set to the To limit the tension applied to the rope and to maintain a predetermined rope position when the rope is tensioned remains constant in the general. 6. Winch according to claim 5, characterized in that »that the organs (25, 26) responsive to the speed are controllable duroh the drum (13), the control devices having organs (27, G1) which are triggered by the organs responsive to the speed for setting the actuating device (67) and for controlling the speed of movement of the drum (13) are controllable. 7. Winch according to claim ¹ J and 6, characterized in that the measuring device (T, P) has a with the soil (L) in engagement Zugmeaaer (15) for generating an Auücanßsuignals (T) aufwo solder, dus through the load on Rope (L) is determined that the La £; emeßwertgeber (16) with the 209836/0697 Rope (L) for generating an output signal β (P) in engagement stands because it is determined by the movement of the rope (L), and that the control devices of an evaluation device (27) for receiving these output signals and for generating them a clutch control signal (X) having a constant value determined by the difference between the output signals. 8. Winch according to claim 5 to 7, characterized in that the speed responsive bin directions (25,26) generate an output signal (S) which is determined by the speed of movement of the sell (L), and that the evaluation device of this output signal on the speed responsive devices picks up and a clutch control signal (X) generated by the Difference between the output signal of the tension meter (15) and the output signals of the load and the Speed responsive messaging is determined. 9 «winch according to claims 1 to 8, characterized that the transducers include a draft knife (15 »02), the with the rope (L) to generate an output signal (T) is engaged, which is determined by the load on the rope (L), and a position sensor (16), which is connected to the rope (L) for generating an output signal (P) is engaged, which is determined by the movement of the rope (L) that the control devices to an evaluation unit (27) Receiving these output signals and generating a clutch control signal (X) with a constant value which is determined by the difference between the output signals and that which affects the speed 209836/0697 appealing Einricntuage »(25.2?) by winding it up of the rope (L) on the drum (13) and daa aforlekel dee Ropes (L) from the drum (13) to the ßraeugung one «of the speed-dependent output signal (3) controllable where the evaluation device of this output * signal (S) and adds it to the position control signal to generate a clutch control signal 209836/0697