US3395893A

US3395893A - Hydraulic spooling device

Info

Publication number: US3395893A
Application number: US598096A
Authority: US
Inventors: August W Kumpf
Original assignee: CLYDE IRON WORKS Inc
Current assignee: CLYDE IRON WORKS Inc
Priority date: 1966-11-30
Filing date: 1966-11-30
Publication date: 1968-08-06
Anticipated expiration: 1985-08-06

Description

1968 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE 7 Sheets-Sheet 1 Filed Nov. 30, 1966 INVENTOR.

1906a.- WAZMPA wfloiljm i/wm 1968 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE Filed NOV. 30, 1966 7 Sheets-Sheet 2 I N VEN TOR.

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HYDRAULIC SPOOLING DEVICE Filed Nov. 30, 1966 7 Sheets-Sheet 4 INVENTOR.

Aug. 6, 1968 Filed NOV. 30, 1966 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE 7 Sheets-Sheet 5 INVENTOR.

06057 WKU/WPF TGR/VEKS Aug 1968 A. w. KUMPF 3,395,893

HYDRAULIC SPOOLING DEVICE Filed Nov. 30, 1966 7 Sheets-Sheet 7 L 44 24 J W 234 c Pi 216 "ZZZ SELECTOR PIESEL 2 5 H P aware/c mm P V DIESEL INVEN TOR.

Unit d States Patent 3,395,893 HYDRAULIC SPOOLING DEVICE August'W. Kumpf, Conshohocken,-Pa., assignor to Clyde Iron Works Inc., Duluth, Minn., a corporation of Minnesota Filed Nov. 30, 1966, Ser. No. 598,096 8 Claims. (Cl. 254-190) ABSTRACT OF THE DISCLOSURE A hydraulically driven touring winch for marine use having a specially constructed spooling device and spooling control unit. The spooling device includes a swivelly mounted rope sheave which is reciprocated relative to the windup drum of the winch by opposed pairs of horizontally disposed hydraulic rams. The spooling control unit includes a planetary gear set having a rotary output employed to adjust the control valve for the hydraulic rams. The gear set operates from two rotary inputs, one of which is responsive to rotation of the windup drum, and the other of which is responsive to the extent of linear movement of the rope sheave.

This invention relates to windup devices of the kind having a power-driven rotating drum for winding and unwinding a rope or the like and to spooling units for use with such wind-up devices. In particular, it relates to a winch, such as a marine towing winch, having a spooling unit and to a control unit for the spooling unit.

It is one object of the present invention to provide a hydraulically operated spooling unit for use with a heavy duty winch, the spooling unit having an improved hydraulic drive for reciprocating a rope guide relative to the windup drum of the winch.

It is another object of the invention to provide an improved control mechanism for the drive system of a spooling unit, the control mechanism having an output means which is responsive to the rotation of the windup drum of a winch and to the linear movement of the spooling unit in a manner to maintain proper synchronism of the spooling unit with the windup drum.

It is another object to provide a spooling unit for a heavy duty winch having an improved swivel mounting for the line guiding sheave.

General description The novel features of the present invention are described and illustrated as being embodied in a marine towing winch of the kind which in use is mounted on the after part of the main deck of a tug or the like. The invention is, however, applicable to heavy duty windup devices generally.

The winch unit, in the form illustrated, includes as its major parts a rope windup drum and associated hydraulic drive, a spooling unit having a separate hydraulic drive for guiding the rope on and oil the windup drum, and control systems for the drum'drive and for the spooling unit drive.

The windup drum is journalled in a frame and is driven through gearing and shatting by hydraulic motors which are mounted on the frame. Control of the motors is obtained with a lever-actuated pilot valve which controls a main motor control valve. The lever is manually operated between a neutral position and up and down positions which correspond, respectively, to stop, pay out rope and haul in rope.

The after end of the winch unit is provided with a hydraulically operated spooling unit having a rope sheave mounted in a fair lead swivel block. The swivel block is carried in a spooling unit cross head which is mounted aft Patented Aug. I 6, 1968 of the windup drum. The cross head is mounted for linear movement along a path which is parallel to the axis of the windup drum. When the windup drum rotates, the cross head is moved automatically by a hydraulic drive to spool the rope on or oil the drum, depending on the direction of rotation of the latter. The hydraulic spooling drive includes two pairs of opposed hydraulic pistons slidably carried in cylinders which are fixed to the winch unit frame. Each pair of pistons is disposed so as to engage and support the cross head, the pairs of pistons being mounted on opposite sides of the frame so that each pair drives the cross head in only one direction. The cylinders are supplied with pressure oil from a hydraulic pump through piping and a mechanically operated directional control valve.

The directional control valve for the spooling unit is lever controlled by a mechanical control unit. In operation the control unit holds the lever in a valve-open position to effect a traverse of the spooling unit, then moves the lever to a valve-closed position to stop the spooling unit at its reversal point, and then moves the lever to an opposite valve-open position to effect a traverse of the spooling unit in an opposite direction. The specific operation of the control unit is somewhat more complex in that it is responsive to two inputs, one of which is proportional to rotation of the windup drum and the second of which is proportional to the linear movement of the spooling unit cross head. These rotary inputs are transmitted to a planetary differential gear set which converts them to movement of the valve control lever through a cam rotated by the gear set. The gear set comprises two sun gears and two intermeshing planetary gears each of which meshes with a dilferent one of the sun gears. Rotary motion of the windup drum is transmitted by gearing and shafting to a diamond lead screw. Rotation of the lead screw moves a cross head pawl which, through a rack, pinion and gearing, rotates the first sun gear of the differential planetary gear set. This first input tends to produce a corresponding rotation of the planetary carrier of the gear set on which is fitted the cam for moving the valve lever. The second rotary input is transmitted to the second sun gear of the gear set. This input is obtained from movement of the spooling unit cross head by means of a cable which is connected at its ends to the latter and which is looped over a pair of repeat back drums disposed adjacent the cross head. When the cross head moves, the cable rotates the repeat back drums, and the rotary input to the sun gear is transmitted by a shaft from the axle of one of the repeat back drums.

In operation simultaneous rotation of the sun gears by their respective inputs during a traverse of the spooling unit holds the planetary carrier and the cam in a given valve-open position. The construction and arrangement of the mechanical drive from the windup drum is such that the first input stops just before the spooling unit arrives at its reversal point. The second input continues, because the spooling unit is still moving, and this produces rotation of the planetary carrier and the cam toward a valve-closed posit-ion. Closing of the valve stops the spooling unit at its reversal point, and this stops the second input, However, by this time the mechanical drive from the windup drum has reversed and is again producing the first input although in an opposite direction. As a result, the planetary carrier and cam move toward an opposite valve-open position. As the valve opens the spooling unit begins to move, and this produces the second input. The combination of both inputs holds the carrier and cam in the valve-open position.

The invention will be further understood from the following detailed description taken with the drawings in which:

FIGURE 1 is a top plan view of the above-referred to towing winch;

FIGURE 2 is a side elevational view of the winch shown in FIGURE 1;

FIGURE 3 is an enlarged sectional view of the spooling unit ,cross head taken generally on the line 3-3 of FIGURE 1;

FIGURE 4 is a schematic rear elevational view of the winch of FIGURE 1;

FIGURE 5 is an enlarged sectional view of the spooling control unit taken on the line 55 of FIGURE 1;

FIGURE 6 is an enlarged fragmentary view of the spooling control unit partly in section and partly in elevation looking in the direction of the arrows 66 of FIGURE 1;

FIGURES 7 and 8 are sectional views taken on the lines 7-7 and 8-8, respectively, of FIGURE 6;

FIGURE 9 is an enlarged sectional view of the planetary gear set of FIGURE 6;

FIGURE 9A is a fragmentary sectional view taken on the line 9A-9A of FIGURE 9;

FIGURE 10 is a diagram of the hydraulic systems for the windup drum and for the spooling rams; and

FIGURE 11 is a schematic view illustrating the operation of the parts of the planetary gear set of FIGURES 6 and 9.

Detailed description of mechanical components of windup drum and spooling unit Referring to FIGURES l and 2, there is shown in somewhat simplified form, a towing winch 10 having a hydraulically operated windup drum 12 and a hydraulically operated spooling unit 14 supported by a common main frame. The towing winch 10 is assumed to be mounted near the aft end of a ship with the longitudinal midplane of the ship passing through the axis of the windup drum 12 at a right angle. The frame consists essentially of two spaced apart, vertical frame subassemblies 16 with appropriate horizontal bracing members extending between them. In the interest of simplicity of illustration the details of the framing is not shown, and all fixed parts which serve as supports are identified with the same reference numeral. The windup drum 12 is provided with an integral shaft 18, the ends of which are mounted in bearings 20 carried by the frame subassemblies 16. The spooling unit 14 is carried by the frame subassemblies 16 in a position aft of the windup drum 12 and above the axis thereof. Carried on the port side (the right side as viewed in FIGURE 1) subassembly are two hydraulic motors 22 for driving the windup drum 12 and a manually-operated winch control lever 24 which is mechanically linked to the spool of a pilot valve 26 (FIGURE 10). The pilot valve 26 is hydraulically connected to a main control valve 28 (FIGURE 10) which controls the direction of rotation of the motors 22. Also carried on the port side subassembly '16 is a mechanical spooling control unit 30 for actuating a control valve 32 (FIGURE 10) in the hydraulic drive of the spooling unit 14. The control unit 30 receives one rotary input from the windup drum 12 through a connection which includes an internal input shaft 34 (FIGURE 7) and another rotary input from the spooling unit 14 through a connection which includes an external input shaft 36.

The hydraulic motors 22 for the windup drum are drivingly connected, as by spur gears 38, to a horizontal transverse shaft which is disposed forward of the windup drum 12. The shaft 40 is journalled in the port side frame subassembly 16 and in a pedestal bearing 44 located outwardly of the latter. The outer end of the shaft 40 carries a conventional winch head 46. The inner end of the shaft 40' connects through a manually operated jaw clutch 48 with the inner end of a drum drive shaft so that the winch head 46 may be operated independently of the windup drum 12 when the clutch 48 is disengaged. The drum drive shaft 50 is journalled in the other frame subassembly and carries a pinion which meshes with a large drive gear 54. The latter is coaxial with the wind up drum 12 and is bolted to the starboard end thereof. The outer end of the drum drive shaft 50 carries a large brake drum 56 around which is fitted a steel brake band 58 lined with woven asbestos lining. The brake band 58 is adjustably tightened on the brake drum 56, through levers, links and a large screw, by rotation of a handoperated wheel 62. The brake has sufficient power, when properly tightened, to prevent a large predetermined pull, for example 140,000 pounds, on the first layer of rope to overhaul the windup drum when the clutch 48 is disengaged. The brake will slip when the pull on the rope exceeds the predetermined holding force.

The hydraulic pumps and piping for the motors 22 has been omitted from FIGURES 1 and 2 in the interest of simplicity. This hydraulic system is illustrated schematically in FIGURE 10 and will be described hereinafter.

The hydraulically operated spooling unit 14 includes two pairs of opposed horizontal rams 64 supporting a cross head 66 which carries a fair lead swivelblock 68. The cylinders 70 of the rams 64 are fixed to the outboard sides of the frame subassemblies 16 in a location aft of the windup drum 12 and above the axis thereof. The pistons 72 extend through the frame subassemblies 16 into sockets on the cross head 66. In operation one set of cylinders 70 is pressurized while the other set is connected to exhaust so that the cross head 66 may be moved parallel to the axis of the windup drum 12 in either direction by whichever set of pistons 72 is being extended.

As best seen in FIGURE 3, the fair lead swivel block 68 carries a main sheave 76 and a secondary sheave 78 and is provided with a hollow cylindrical extension 80 through which the rope 82 passes. The cylindrical extension 80 is swivelly mounted in a bore in the center of the spooling unit cross head by means of roller bearings 84 for 360 of rotational movement about a fore and aft axis through the center of the extension 80. In operation, the swivel block 68 will assume the position shown in FIGURES 1 and 2 when the rope 82 is being payed out or wound in along the ships fore and aft center line, in which case the axis of rotation of the

sheaves

76 and 78 is parallel to the axis of rotation of the windup drum 12 and to the direction of movement of the cross head 66. As the lead of the rope 82 changes, the swivel block 68 will rotate about the axis defined by the roller bearings 84. At of lead the rope 82 is parallel to the axis of the windup drum 12, and the swivel block 68 will assume one of the dotted line posi tions illustrated in FIGURE 1 in which position the axes of the sheaves are normal to the windup drum axis.

As seen in FIGURE 4, the lower end of the cross head 66 is fitted with a bracket 86 to which is secured an endless wire rope 88. The wire rope 88 is looped over a pair of spaced apart repeat back rope drums 90 and 92, each of which is journalled on one of the frame subassemblies 16 for free rotation about a fore and aft axis. The wire rope 88 is wrapped around the drum 92 to prevent slippage between the two. Linear movement of the cross head 66 under the action of one of the sets of pistons 72 rotates the

drums

90 and 92, and this rotary movement is transmitted to a shaft 94 which is coupled to the external rotary input shaft 36 of the spool control unit 30 through a universal joint 96.

Detailed description of spool control unit As previously indicated, the spool control unit 30 (FIGURES 5-9), which is mounted on the port side frame subassembly 16, is a mechanical servo-mechanism for synchronizing the movement of the spooling unit cross head 66 with rotation of the windup drum 12. The ultimate output of the control unit 30 is in the form of movement of a lever which moves the spool of the control valve 32 (FIGURE 10) for the spooling rams 64.

The control valve 32 is a four-way valve having a center position in which the rams 64 are hydraulically locked and two end positions in which the spooling unit cross head 66 is driven either to the left or to the right.

The heart of the control unit is a planetary gear set (FIGURES 6, 9 and 9A) which revolves a grooved barrel cam 117, the latter determining the position of the directional control valve 32 (FIGURE 10) by means of a valve control lever 136 (FIGURE 5). The gear set 100 includes two coaxial, spaced-apart sun gears 102 and 104 and two intermeshing

planetary pinions

106 and 108, one of which (106) meshes with the first sun gear 102 and the other of which (108) meshes with the second sun gear 104. The shafts of the pinions are rotatably mounted at 1060 and 108a in spaced-apart plates which, together with a hollow cylindrical member 107, form a planetary carrier 110 or spider. One sun gear 102 is fixed to a shaft 112 extending out of the gear set 100 and journalled in a bearing 114 within the control unit 30. The other sun gear 104 is fixed to an oppositely directed shaft 116 which is journalled in a bearing 118. The shaft 112 is rotated by a mechanical drive connected with the windup drum 12 and provides a first rotary input to the gear set 100; the shaft 116 is rotated by movement of the spooling unit cross head 66 and provides a second rotary input to the gear set 100.

The planetary carrier 110 carries a barrel cam 117 which is made up of a hollow member 119 and two end plates 120 secured together by bolts 121. The end plates 120 are keyed at 122 to oppositely directed stub shafts 123 which project from the ends of the planetary carrier 110. The exterior surface of the barrel cam 117 presents an axially facing cam surface 126 which is engaged by a roller 128 (FIGURE 8) carried out by one end of an arm 130. The other end of the arm 130 is keyed to a rotatable stub shaft 132 (FIGURE 8) which is mounted in a pair of spaced-part bushings 134. The control lever 136 for the spooling unit control valve 32 is keyed to the stub shaft 132.

The overall operation of the gear set 100 is such that rotation of the planetary carrier 110 is responsive to the rotary inputs to the sun gears 102 and 104. Rotation of the carrier 110 rotates the barrel cam 117 and this moves the valve control lever 136 so as to start the movement or stop the movement or to reverse the directions of movement of the spooling rams 64 at the proper times.

The rotary input to the sun gear 104 is directly proportional to the linear movement of the spooling unit cross head 66 and is provided by the extenal shaft 36 which is driven by the shaft 94 from the repeat back rope drum 92. As best seen in FIGURE 6, the external shaft 36 is keyed at 139 to the planetary carrier shaft 116 just outside the control unit 30.

The rotary input to the sun gear 102 is obtained from the windup drum 12 through a mechanical connection which includes a diamond lead screw 140. The mechanical connection begins with the previously mentioned internal input shaft 34 which, as seen in FIGURE 7, is coaxial with the windup drum shaft 18 and connected thereto by a sleeve 141 which is bolted to the drum shaft 18 at 142. The sleeve 141 is keyed to a miter gear 143 which in turn is keyed to the shaft 34, and the assembly of these parts is rotatably mounted in bearings 144. The miter gear 143 meshes with another miter gear 146 which is keyed to a shaft 148 (FIGURE 5). The latter shaft is journalled in bearings 150 and carries a pinion 152 and a hand wheel 154. The hand wheel 154 is accessible for manual rotation by removal of a cover plate 156 which forms part of the casing of the control unit 30. The pinion 152 meshes with a spur gear 158 which is keyed to one end of the diamond lead screw 140, the latter being journalled in bearings 160.

Continuous rotation of the lead screw 140 in either direction is converted to rotary reciprocating movement of the sun gear 102 of the planetary set 100 by means of 6 a swivel pawl cross head 162, a rack 164',- spur gear 166, shaft 168 and

helical gears

170 and 172, the latter being keyed to the sun gear shaft 112 as seen in FIGURE 6. The swivel pawl cross head 162 (FIGURE 5), which includes a swivel nut 174, cooperates with the lead screw 140 and is moved linearly by rotation of the latter. Rotation of the pawl 162 is prevented by two fixed guide rods 176 on which the pawl 162 slides. The relationship of the pawl 162, lead screw 140 and the spooling unit cross head 66 is such that the pawl 162 arrives at its reversal point slightly before the spooling cross head 66 arrives at its reversal point. The rack 164, which extends parallel to the lead screw 140, is fixed to the pawl 162 and is thereby moved longitudinally of itself inside the control unit 30 during rotation of the lead screw 140. The extrernities of the rack 164 are enclosed by covers 178 and 180 which project from the main portion of thecontrol unit 30, as seen in FIGURE 6.

The teeth 182 of the rack 164 mesh with the spur gear 166 which is keyed to the shaft 168. Rotation of the latter within its supporting bearings 184 rotates the helical gear 17 0 which in turn rotates the helical gear 172. The helical gear 172 is keyed to the sun gear shaft 112, as previously described.

FIGURE 10 shows the hydraulic circuits for the windup drum 12 and for the spooling rams 64.

The motors 22 for the windup drum 12 are of a commercially available low speed, high constant torque type having fixed displacement and are fully reversible with identical torque being produced in either direction of rotation. Pressure oil for the motors is supplied by four independent vane-type hydraulic pumps which are located remote from the motors 22. Two compensator pumps 186 are driven by electric motors, for example 25 HP motors producing oil at up to 750 p.s.i. The other two pumps 188 are driven by diesel-powered generators, for example, 75 kw. producing 2100 p.s.i. oil. Pressure oil from the pumps 188 is made available directly to the main motor control valve 28 through

lines

190, 192 and 194. Exhaust oil from the valve 28 passes through a line 196.

Pressure oil from the pumps 186 passes to the motor control valve 28 by way of a selector valve 198 which is adapted to direct oil from either one of the pumps 186 to a line 199 which connects with the

circuit

190, 192, 194. The oil from the other pump 186 is directed to a line 200 for use by the spooling rams 64 and by the ships steering mechanism.

The hydraulic circuit between the main control valve 28 and the motors 22 includes

lines

202 and 204 and a relief valve 206, the latter being arranged with appropriate check valves to pass oil to an exhaust line 208.

As previously indicated, the spool of the main control valve 28 is moved hydraulically by pressure oil received from the pilot valve 26. A compensator vane pump 210 supplies pilot pressure oil to the pilot valve 26 through a line 212 and supplies supercharging oil to the motors 22 through a line 214. The pressure oil from the line 212 is passed to the actuators of the pilot valve 26 through either of

lines

216 or 218 and then to exhaust through a line 220.

Pressure oil from either of the pumps 186 is made available to the ram control valve 32 through the selector valve 198, the line 200 and a line 222. Return oil passes through a return line 224 which connects with the exhaust line 220. The valve 32 passes oil to and from the rams 64 through a circuit which includes lines 226 and 228.

Relief valves

230 and 232, together with appropriate check valves are provided between the lines 226 and 228 for exhausting oil to the exhaust line 208. The spool of the valve 32, when centered, blocks the flow of oil to or from the lines 226 and 228 and hydraulieally locks the rams 64. However, a bypass valve 234 is provided between these lines so that, when the valve 234 7 is open, one set of rams 64 may extend freely while the other set retracts.

Operation As indicated previously, the hydraulic motors 22 which drive the windup drum 12 are controlled manually with the lever 24 which is mechanically linked to the spool of the pilot valve 26. In the neutral position of the lever 24 the spools of both the pilot valve 26 and the main motor control valve 28 are centered. The spool of pilot valve 26 blocks the flow of pilot pressure oil from the line 212 and connects the

lines

216 and 218 to the exhaust line 220. The pilot pump 210 continues to operate but its discharge is reduced by the compensator as the pressure increases until no oil is discharged at 150 psi. The spool of the main control valve 28 passes pressure oil from the line 194 directly to the exhaust line 196. The spool of the main valve 28 also blocks the flow of oil in either direction in the

lines

202 and 204, thus hydraulically locking the motors 22 to prevent overhaul of the drum 12. When moved to a down position the lever 24 moves the spool of the pilot valve 26 to pass pressure oil to the actuator of the main control valve 28. This moves the spool of the latter to a first open position in which pressure oil from the pumps is passed to the motors 22 in a direction to haul in rope. In the up position the lever 24 moves the main valve spool to the second open position which permits the pressure oil to rotate the motors in the direction to pay out rope.

The relief valve 206 opens when the pressure in the motor system reaches a predetermined high pressure for example 21.00 p.s.i. and permits the pressure oil to by-pass to the

lines

202 or 204. This relief valve 206 prevents overloading the motors 22 and pumps and permit rope to pay out from the windup drum when the external pull on the rope develops a pressure in the system which exceeds the relief valve pressure setting.

The motors may be driven by different combinations of the

pumps

186 and 188 to handle different loads and speeds. For a pull of 10,000 lbs. at 70 f.p.m. on the first layer of rope on the windup drum 12, both pumps 188 and one of the pumps 186 are employed. In this case the line is pressurized by oil passing from the pumps 188 through the

lines

190 and 192 and by oil passing from the selector valve 198 through the line 199. For a pull of 25,000 lbs. at 45 f.p.m. on the first layer of rope on the drum 12, one of the pumps 188 and one of the pumps 186 are employed. For a pull of 50,000 lbs. 'at 24 f.p.m. or of 100,- 000 lbs. at 23 f.p.m. one of the pumps 188 alone is employed. Neither of the pumps 186 will discharge oil when the load on the windup drum becomes high, because in this event the pressure in the line 194 exceeds the pressure setting of the compensators tor the pumps 186.

The spooling rams 64 are operated by pressure oil obtained from the line 222 under the control of the spooling control valve 32 which is actuated by the spooling control unit 30. The control valve 32 has a center position in'which oil fiows neither to or from the rams 64 with the result that the latter are hydraulically locked against extension or retraction. In one end position the valve 32 directs pressure oil to one set of rams 64 through one of the lines 226, 228 while exhausting the other set through the line 224. In the other end position the valve 32 reverses the flow of oil so as to reverse the movement of the rams 64. The

relief valves

230 and 232 open at a predetermined high internal pressure, for example 1500 psi, and permit the pressure oil to by-pass to the opposite side of the system. During operation of the ra-ms 64 the

valves

230 and 232 permit the spooling unit 14 to be moved transversely of the ship in either direction by the pull of the rope sheave 76 when this load develops pressure in the spooling rams 64 greater than the relief valve setting. The spooling unit piping is also provided with the bypass valve 234 which, when opened, permits free movement of the spooling unit 14 in either direction by external forces on the rope sheave 76. The connection of the pressure line 222 to the line 200 permits the rams 64 to be operated regardless of whether the line 194 to the motor control valve 28 is being pressurized.

The spooling control valve 32 is operated solely by the spooling control unit 30 through the cam-operated lever 130 (FIGURE 8) and the

linkage

134, 136 interconnecting the valve 32 and the lever 130. The control unit 30 operates as a servo unit in that it rapidly adjusts the position of the control valve 32 in response to inputs which are proportional to movements of certain parts of the winch. The primary overall function of the control unit is, of course, to reverse the direction of movement of the spooling rams 64 in proper synchronization with rotation of the windup drum 12. This is accomplished, in part, with the diamond lead screw 140 and associated pawl 162, the lead screw 140 being rotated by a direct mechanical drive from the windup drum 12. The relationship between the lead screw 140' and the pawl 162 is such that the pawl 162 reverses its direction of movement just before the spooling unit cross head 66 reaches the point at which it should reverse. However, the stopping and reversal of the pawl 162 is not converted directly into movement of the valve control lever 130 to its reverse position. Rather, the stopping of the pawl 162 is employed to initiate a closing signal for transmittal to the valve 32, and the beginning of the subsequent reverse movement of the pawl 162 is employed to initiate a valve-reversing signal. In order to accomplish this sequence the control unit 30 continuously receives a second mechanical input which is directly proportional to the actual movement of the spooling unit 14. The latter input is compared with the pawl movement by the planetary gear set in such a manner that the movement of the spooling unit 14, after the pawl 162 stops, efifects movement of the cam 117 and control lever 130 to the closed position. Thus, the spooling unit 14 in effect produces its own control signal. The planetary gear set 100 also compares the pawl movement with the second input in such a manner that the beginning of subsequent movement of the pawl 162 in its reverse direction effects movement of the cam 117 and valve lever 130 to the appropriate open position.

The effect of the above-outlined sequence of steps is to reverse the direction of the spooling unit 14 with a minimum of stress within the hydraulic system. The spooling unit 14 is of necessity a heavy piece of equipment. The inertia of the equipment plus the external forces acting on the sheave 76 through the rope 82 would on occasion create very high pressures in the hydraulic system if the control valve 32 were moved directly from one open position to a reverse open position. The control unit 30, however, assures that the valve 32 will first move to a closed position before reversing and assures that the necessary synchronism will be maintained between rotation of the drum 12 and reversal of the spooling unit 14.

The actual movement of the parts of the planetary gear set 100 and the resulting movement of the cam 117 before, during and after reversal of the spooling unit 14 is illustrated schematically in FIGURE 11(a) through FIGURE 11(i). The gear set 100 is shown as if viewed from the right in FIGURE 9, and in the interest of simplicity the planetary carrier is shown fragmentarily as an arcuate line. The

cam arrangement

117, 119, 120, 126 is shown as a single projection on the outside of the carrier 110. One half of each

sun gear

102 and 104 has been broken away so that both gears appear in the views.

The arrows designate the direction of rotation of the various parts. Where no arrow appears that part is stationary.

FIGURE 11(a) illustrates the operation of the parts during a routine pass of the spooling unit 14 along the length of the windup drum 12. During this time the windup drum 12 is rotating in one direction or the other depending on whether rope 82 is being payed out or wound in. In either case the continuous rotation of the drum 12 is transmitted to the diamond lead screw 140 through the connection formed by

parts

34, 143, 146, 148, 152 and 158. Assuming that the pawl 162 is in a position intermediate the ends of the lead screw 140, the pawl 162 will be moved linearly along its support rods 176 by the action of the screw 140. Linear movement of the pawl 162 moves the rack 164 with the result that rotary motion is imparted to the sun gear 102 by

parts

166, 168, 170, 172 and 112. At the same time rotary motion in the opposite direction is being imparted to the other sun gear 104 by movement of the spooling unit 14, cable 88, repeat back drums 90 and 92 and shafting 94, 36 and 116. At this stage of the description it is assumed that the control valve 32 is open to one of its two open positions this position being indicated as No. l, and that one set of spooling pistons 72 is pushing the spooling unit 14 along the length of the windup drum 12.

Thus, during traversal of the spooling unit 14 there are two rotary inputs to the planetary gear set 100. As seen in FIGURE ll(a), the sun gear 102 is being driven clockwise, and the sun gear 104 is being driven counterclockwise. Each of the

planetary gears

106 and 108 is also being rotated about its own axis by its respective sun gear. The gear set 100 is so designed that the rotary inputs cancel each other with the result that the planetary carrier 110 and cam 117 are stationary during traversing movement of the spooling unit 14. Accordingly, the cam 117 remains in the No. 1 position until the pawl 162 stops at one end of the lead screw 140, as discussed in the next paragraph.

FIGURE ll(b) illustrates the movement of the parts which occurs when the pawl 162 reaches the end of the lead screw 140 and stops momentarily before reversing. Since the pawl 162 indirectly drives the sun gear 102, the latter stops when the pawl 162 stops. However, the sun gear 104 continues to rotate counterclockwise as before, because the spooling unit 14 is still moving toward one end of its path of travel. That is, the repeat back drums 90 and 92 continue to rotate in the same direction as before with the result that the rotary input to the sun gear 104 does not change. Since the sun gear 102 is stationary and the sun gear 104 is rotating, the carrier 110 will be rotated counterclockwise through the action of the

planetary gears

106 and 108. The result is that the cam 117 moves toward a closed position C. In this position of the cam 117 the spool of the control valve 32 is in a center position in which no oil flows to or from either set of rams 64. Accordingly, in this position of the cam 102 the pistons 72 are stationary and hydraulically locked against movement.

FIGURE ll(c) illustrates the parts immediately after the cam 117 reaches the closed position referred to above. Since the pistons 72 have stopped, the spooling unit 14 and

repeat drums

90 and 92 have stopped. This stops ro tation of the sun gear 104, and since there is now no rotary input to the gear set 100, the cam 117 stops.

Referring to FIGURE ll(d), the pawl 162 now begins to move in the opposite direction because the lead screw 140 and windup drum 12 have continued to rotate without interruption. This reverse movement of the pawl 162 drives the sun gear 102 in a counterclockwise direction. Since the sun gear 104 is stationary and locked, counterclockwise rotation of the sun gear 102 causes the carrier 110 and the cam 117 to move again in a counterclockwise direction. This moves the cam 117 from the closed position toward an opposite open position, No. 2, in which the spool in the control valve 32 directs pressure oil to the opposite set of pistons 72, thus pushing the spooling unit 14 in the opposite direction.

As soon as there is movement of the spooling unit 14, the repeat back drum 92 imposes a rotary input on the sun gear 104, this time in a clockwise direction as shown in FIGURE ll(e). This counteracts the rotary input to the sun gear 102 so that the carrier 110 and cam 117 become stationary at the No. 2 open position.

FIGURE 11( is analogous to FIGURE ll(b) and represents the stopping and locking of the sun gear 102 as the pawl 162 again reaches an end of the lead screw 140. The clockwise input to the sun gear 104 continues, and this causes the carrier 110 and cam 117 to move clockwise toward the closed position.

FIGURE ll(g) is identical to FIGURE 11(0) and represents the stationary position of the carrier 110 and cam 117 after the input to the sun gear 104 stops as a result of closing of the valve 32.

FIGURE ll(h) is analogous to FIGURE ll(d) in showing rotation of the sun gear 102 as the pawl 162 again starts to move in its original direction. Since the valve 32 is still closed, the sun gear 104 is locked. The carrier 110 and cam 117 therefore begin to rotate clockwise toward the No. 1 open position.

In FIGURE ll(i) the cam 117 has arrived at the No. 1 open position with the result that the valve 32 has opened, the spooling unit 14 is being moved and the repeat back drum 92 is driving the sun gear 104 in a counterclockwise direction. Again, the inputs to the gear set cancel each other so that the cam 117 is stationary. Accordingly, FIGURE ll(i) is identical with FIGURE ll(a).

If the operator of the winch stops the wind-up drum 12 by closing the pilot valve 26 with the manually operated lever 24, the diamond lead screw 140 stops and the rotary input to the sun gear 102 stops. Since oil flow to one set of spooling pistons 72 continues, the rotary input to the sun gear 104 continues. However, from FIGURES ll(b) or (f) it will be apparent that the rotation of the sun gear 104 will immediately cause rotation of the carrier and cam 117 to the closed position, so as to close the valve 32 and shut down the spooling drive. Upon the operators starting the winding drum 12 the sun gear 102 will begin to rotate and will move the carrier 110 and cam 117 to the appropriate open position, as illustrated in FIGURE ll(a) or (e).

Adjustment of the spooling control unit 30 so that it operates as described above is made by manually rotating the wheel 154 shown in FIGURE 5, after removing the cover 156 and after disconnecting the universal joint 96 shown in FIGURE 6. The wheel 154 which is fixed to the shaft 148 is first moved slightly to the left as viewed in FIGURE 5 so as to disconnect the

gears

143 and 146. Next, the wheel is rotated to rotate the lead screw and move the pawl 162 to the end of its travel. If the spooling unit cross head 14 is at the port side of the winch, the pawl should be moved to the right as viewed in FIGURE 5. If the cross head 14 is at the starboard side of the winch, the pawl 162 should be moved to the left. The moving of the pawl 162, as described in the previous sentences, centers the spool of the valve 32 by the action of the cam 117 and lever 136. Then the wheel 154 is pushed to the right to reengage the

gears

143 and 146, and the cover 156 is replaced. Further adjustments of the spooling control unit 30 can be made, if required, by disconnecting the universal joint 96 and rotating the input shaft 36 by hand until the spool of the valve 32 has been centered by the cam 102 and lever 13-6. Finally, the universal joint 96 is re-connected while holding the input shaft stationary.

While preferred embodiments of the present invention have been described, further modifications may be made without departing from the scope of the invention. Therefore, it is to be understood that the details set forth or shown in the drawings are to be interpreted in an illustrative, and not in a limiting sense, except as they appear in the appended claims.

What is claimed is:

1. A control device for a line spooling unit of the kind employed in conjunction with a power driven windup drum and having a line guiding means and a drive means for reciprocating the line guiding means along a path between first and second limits corresponding to that length of the drum adapted for carrying the line whereby the line may be spooled on or off the' drum, said control device comprising: a movable output member for controlling the drive means for the line guiding means, said output member having at least one drive position and a stop position; first transmission means adapted to be driven at a speed proportional to the speed of rotation of the windup drum, said first transmission means having means for converting continuous rotation of the windup drum into uniform reciprocating movement of a first member; second transmission means adapted to be driven at a speed proportional to the speed of the line guiding means along its path and in a direction corresponding to the direction of movement of the line guiding means, said second transmission means having means for converting movement of the line guiding means into reciprocating movement of a second member; and third transmission means interconnecting said first and second members with said movable output member for moving said output member from a drive position to its stop position and then to a drive position upon each arrival of the line guiding means at one of its limits,

2. Apparatus as in claim 1 wherein said first transmission means includes a two-way lead screw adapted to be rotated at a speed proportional to the speed of rotation of the windup drum, a pawl mounted on said lead screw and linearly reciprocated by continuous rotation of said lead screw and connecting means for converting reciprocating linear movement of said pawl into reciprocating rotary movement of said first member and wherein the movement of said second member of said second transmission means is rotary and reciprocating.

3. Apparatus as in claim 2 wherein said third transmission means includes a planetary differential gear set having first and second sun gears, a pair of intermeshing planetary gears and a planetary carrier, said first sun gear being drivingly connected to said first member of said first transmission means, said second sun gear being drivingly connected to said second member of said second transmission means and said planetary carrier being drivingly connected to said output member, said planetary gears being rotatably mounted in said carrier, one of said p'anetary gears being in meshing engagement with said first sun gear and the other planetary gear being in meshing engagement with said second sun gear.

4. In a machine having a rotatable windup drum and a spooling device which includes line guiding means and drive means for traversing said line guiding means, an improved control device for said drive means comprising: an output member having at least one drive position and a stop position; means responsive to a predetermined amount of rotation of the windup drum and simultaneously responsive to continued movement of the line guiding means to move said output member from a drive position to said stop position; means responsive to stoppage of the line guiding means to hold said output member in said top position; means responsive to further rtation of the windup drum to move said output member to a drive position; and means responsive to movement of the line guiding means and simultaneously responsive to continued rotation of the windup drum to hold said output member in said last-named drive position.

5. A power winch construction having a power-driven windup drum and a line spooling device disposed adjacent said windup drum, said spooling device comprising: line guiding means disposed adjacent said windup for guiding a line between a remote point and said drum; first and second hydraulic cylinder-and-piston units disposed on opposite sides of said line guiding means, each of said units having an extensible and contractable free end engaging an opposite side of said line guiding means for moving the same between two fixed limits along a straightline path parallel to the axis of said windup drum in a first direction upon simultaneous extension of said first unit and retraction of said second unit and in a second direction upon simultaneous extension of said second and retraction of said second unit, said line guiding means including a cross head engaged by said free ends of said piston and cylinder units and a swivel block, said swivel block including a hollow cylindrical extension extending transversely to the axis of said windup drum and swivelly mounted in a complementary passage through said cross 168d, said line guiding means further including a linereceiving sheave journalled for rotation about its own axis on said swivel block on the opposite side of said hollow extension from said windup drum; and fluid pressure supply means for said piston-andcylinder units including valve means for delivering fluid under pressure to either of said units while exhausting fluid pressure from the other of said units, said fluid pressure supply and control means includes a relief valve operable to exhaust fluid pressure from the piston-and-cylinder units upon occurrence of predetermined high. fluid pressure whereby said line guiding means may be moved against the action of a piston-and-cylinder unit by the pull of the line on said line guiding means when the pull is suflicient to develop pressure in excess of said predetermined high pressure.

6. A machine as in claim 4 wherein said drive means includes a linear hydraulic motor and a valve for controlling the fiow pressure fluid to and from said motor and wherein said output member of said control device is operably associated with said valve.

7. Apparatus as in claim 5 wherein said fluid pressure supply and control means further includes a by-pass valve for exhausting fluid pressure from both said pistonand-cylinder units whereby said line guiding means may be moved freely along said elongated support in either direction by external forces on said guiding means.

8. Apparatus as in claim 5 wherein said valve means has a closed position in which no pressure fluid flows to said cylinder-and-piston units and two opposite open positions, said control unit being continuously and simultaneously responsive to rotation of said windup drum and to movement of said line guiding means to move said valve from one of its open positions to its closed position just before said guiding means reaches one of its limits and to then move said valve to its opposite open position so as to reverse the flow of fluid pressure to said cylinderand-piston units.

References Cited UNITED STATES PATENTS 2,320,554 6/1943 Barrett 242-158 2,391,290 12/1945 Berger 254190 2,404,368 7/1946 Esch 242-458 3,168,261 2/1965 Hainer 242-158 3,174,726 3/1965 Atkinson M 254l FOREIGN PATENTS 1,051,474 2/1959 Germany.

EVON C. BLUNK, Primary Examiner.

H. C. HORNSBY, Assistant Examiner.