CA1254876A - Winch with level-wind regulator - Google Patents
Winch with level-wind regulatorInfo
- Publication number
- CA1254876A CA1254876A CA000463805A CA463805A CA1254876A CA 1254876 A CA1254876 A CA 1254876A CA 000463805 A CA000463805 A CA 000463805A CA 463805 A CA463805 A CA 463805A CA 1254876 A CA1254876 A CA 1254876A
- Authority
- CA
- Canada
- Prior art keywords
- sheave
- support frame
- wire rope
- winch
- end portion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/28—Other constructional details
- B66D1/36—Guiding, or otherwise ensuring winding in an orderly manner, of ropes, cables, or chains
- B66D1/38—Guiding, or otherwise ensuring winding in an orderly manner, of ropes, cables, or chains by means of guides movable relative to drum or barrel
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Jib Cranes (AREA)
- Wind Motors (AREA)
Abstract
INVENTION: WINCH WITH LEVEL-WIND REGULATOR
INVENTOR : DEREK FOSTER
ABSTRACT OF THE DISCLOSURE
A winch and level-wind regulator basically of the swinging arm type mounted on a single support frame and suitable for spooling wire rope under loads in excess of 200 tons is described. The winch includes a conventional wire rope drum and drive which serve to haul in and pay out the wire rope.
Movement of the wire rope to and from the rope drum is directed by a sheave assembly which includes an elongate sheave support frame, a first sheave rotatably mounted adjacent a first end of the support frame, and a second sheave rotatably mounted inset from a second end of the support frame, the sheaves being generally coplanar and rotating about parallel sheave axes. The first end of the sheave support is hinged to the support frame for hinged movement about a first hinge axis which is perpendicular to the rotational axis of the drum thereby permitting the second end of the sheave frame to pivot back and forth along an arcuate path close to the wire rope drum. The support frame includes a connecting arm coaxially mounted with the first sheave about a common axle to permit the second end of the sheave support frame to pivot relative the first end. The second end of the sheave support frame is driven back and forth along the arcuate path by a drive mechanism which includes a diamond-threaded rotatable shaft parallel to the drum rotational axis, a drive member which travels longitudinally on the guide shaft when the guide shaft is rotated, a floating connection joining the second end of the sheave frame to the drive member for movement therewith while permitting the second end of the sheave assembly to follow the arcuate path, and a synchronizing mechanism which synchronizes movement of the drive member with drum rotation to provide for proper spooling. Severe forces which might otherwise act on the drive mechanism, particularly the guide shaft, are avoided by a stop which engages the second end of the sheave support. The stop has a planar bronze surface plate which contacts a fluorocarbon surface plate on the second end portion of the sheave support thereby providing a low-friction stop which does not impede operation of the drive mechanism.
The hinge provided between the sheave support frame ends ensures that severe bending moments are not applied to the hinge joint between the sheave assembly and the winch support frame.
INVENTOR : DEREK FOSTER
ABSTRACT OF THE DISCLOSURE
A winch and level-wind regulator basically of the swinging arm type mounted on a single support frame and suitable for spooling wire rope under loads in excess of 200 tons is described. The winch includes a conventional wire rope drum and drive which serve to haul in and pay out the wire rope.
Movement of the wire rope to and from the rope drum is directed by a sheave assembly which includes an elongate sheave support frame, a first sheave rotatably mounted adjacent a first end of the support frame, and a second sheave rotatably mounted inset from a second end of the support frame, the sheaves being generally coplanar and rotating about parallel sheave axes. The first end of the sheave support is hinged to the support frame for hinged movement about a first hinge axis which is perpendicular to the rotational axis of the drum thereby permitting the second end of the sheave frame to pivot back and forth along an arcuate path close to the wire rope drum. The support frame includes a connecting arm coaxially mounted with the first sheave about a common axle to permit the second end of the sheave support frame to pivot relative the first end. The second end of the sheave support frame is driven back and forth along the arcuate path by a drive mechanism which includes a diamond-threaded rotatable shaft parallel to the drum rotational axis, a drive member which travels longitudinally on the guide shaft when the guide shaft is rotated, a floating connection joining the second end of the sheave frame to the drive member for movement therewith while permitting the second end of the sheave assembly to follow the arcuate path, and a synchronizing mechanism which synchronizes movement of the drive member with drum rotation to provide for proper spooling. Severe forces which might otherwise act on the drive mechanism, particularly the guide shaft, are avoided by a stop which engages the second end of the sheave support. The stop has a planar bronze surface plate which contacts a fluorocarbon surface plate on the second end portion of the sheave support thereby providing a low-friction stop which does not impede operation of the drive mechanism.
The hinge provided between the sheave support frame ends ensures that severe bending moments are not applied to the hinge joint between the sheave assembly and the winch support frame.
Description
3 7~:i FIELD OF TEIE INVENTION
__ _ The invention relates generally to the design and construction of winches, and more particularly to the construction of winches with level-wind regulators suitable for spooling wire rope under loads exceeding 200 tons such as migh-t occur for example in winches on ocean-yoing tugs or in the mooring of offshore drill platforms.
BACKGROUND OF TE~E INVENTION
The spooling of wire rope commonly involves a winch equipped with a wire rope drum and a drive which rotates the drum either to haul in or pay out the wire rope. The wire rope drum conventlonally has a cylindrical drum portion on which wraps of wire rope are laid down, most commonly several layers deep, and a pair of lS circular flanges at opposing ends of the cylindrical : : drum portion which conine the wire rope during spooling operations~ For tight side-by-side spooling : of wraps of wire rope on the drum, the maximum angle formed between the wire rope and a perpendicular from the cylindrical drum portion, namely, the "fleet angle", must be kept less than l~degrees throughout the spooling operation. If the fleet angle is allowed to exceed the speci-fied value, there will :~be a tenda.ncy for cross winding, excessive rope ; ;: , ..
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bending and snagglng in the wraps laid clown. Also, during paying out of -the wire rope under heavy loads, the rope may be subjected to sudden shocks as snagged lengths of rope are suddenly released.
All these factors tend to reduce the useful lifetime of the rope which in high -tension applications tends to be very expensive to replace.
In typicàl spooling operations, wire rope is initially directed to a winch by a fairlead sheave fixed to appropriate support structure remote from the winch. The fleet angle can be confined to an ideal range less than about 1~ degrees by simply locating the fairlead sheave a considerable dlstance from the winch drum; however, space constraints commonly makes such applications impractical. In order to provide a versatile winch which can accommodate pre-existing space requirements, it is common to mount a fleet angle compensator, commonly referred to as a "level-wind", directly on a winch support frame proximate to the assoclated wire rope drum. The level-wind serves to reduce the fleet angle effectively seen by the wire rope drum.
~ A variety of practical level-winds mounted directly on an associated winch support frame have 'r . /
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been manufactured Eor hlgh-load appll,cations. Thec;e level-wind~ most oEten lnvolve a rope c~uide mounted on heavy guide bars for movement back and forth in front of a rope drum. The rope guide quite commonly includes a pair of vertical rollers between which the rope is passed to the drum. A common alternative to vertical paired rollers is the provision on the rope guide of a sheave about which the wire rope travels towards the drum. A
variety of drive mechanisms have commonly been used to move the rope guide along the guide bars, including diamond-threaded screw drives, screw drives with more conventional helical threads, and hydraulically-operated pistons. In winches 15; employing screw-drives, movement of the guide member on the screw drive is commonly synchroni~ed with rotation of the drum for proper spooling by mechanically coupling the screw drive to the drum, as~with a chain drive, and the drum drive serves to simultaneously rotate the wire rope drum~and operate the level-wind. Synchronization in winches employing piston-type level-wind driv~s has been more complicated.
There are several problems associated with the level-winds commonly incorpora~ed on winches `''`'' .~
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for high-load appl:LcatLons. In particular, yuicle rollers are not particularly well suited to conveyance of w:ire rope, and often subject the rope to excessive bending during the effective reduction of fleet angle, thereby tending to shorten the useful lifetime of the wire rope unless the guide rollers are dramatically increased in diameter. Rope guides incorporating a sheave for transmission of the wire rope tend to damage the rope less, but normally require sheaves formed as very large and expensive forgings to resist reaction loads due to rope bend about the sheave and the manner of sheave mounting required.
Moreover, level winds of the type described above incorporating a sheave as a rope guide member have generally not been able to accommodate a very large fleet angle. Also, the rope guides and associated .
drive mechanisms must have a particularly robust constructions to withstand forces imposed on the mechanisms by bending of the path of the wire rope under high tension. For example, at an incldent fleet angle of 15 degrees, which is not ; uncommon in many practical applications, forces approaching 26 percent of the line load are applied . :
directly to the rope guide drive mechanism. These I .
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forces are very signlf:ican-t when line loads exceecl 200 tons. AccorcLingly, the various components of the rope guide and guide drive tend to be over-sized and expensive.
In light-load applications, winches have been manufactured which incorporate a level-wind with a "swinging arm". These level-winds include an arm which is hinged to the suppor-t frame of the winch and which normal].y carries a pair of sheaves, a first sheave positioned adjacent the hinge joint and a second sheave positioned adjacent the free, swinging end of the arm. Rope is commonly received initially by the first sheave, as from a remotely-located fairlead sheave, and transferred to the second sheave which then directs the rope towards the rope drum. The free end of the arm sweeps along an arcuate path a].ong which the second sheave can trans~er the rope to axially spaced-apart positlons along the wire rope drum. In applications ~ where th~e winch is to serve only as a storage winch, a traction winch may be interposed between the ncoming~wire rope and the storage winch so that the storage winch sees very little load. In such ;circumstances, the~swinain~ arm is allowed to pivot under the influence of the rope, and no special synchronization mechanism is required -~o ~:
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-ensure proper wrapping of the rope on the associated drum. In other applications, the swinging arm has been supported in a cantilevered arrangement, movement of the swinging arm being synchronized with the rota-tion of the drum by means oE a con-trol mechanism involving a hydraulic-cylinder drive which forms part of the cantilevered arrangemen-t.
Synchronization of arm movement with drum rotation in such a device has been a relatively complicated process.
Prior art level-winds of the swinging arm type have had the advantage that large fleet angles are eliminated, and that they can be positioned in very restricted space because distance from a remote fixed sheave initially directing rope towards the level-wind does not affect operation and the orces to which the swinging arm is otherwise subjected.
Also, they tend not to stress the associated wire rope excessively, because transfer of the wire rope is effected entirely over sheaves. However, a convenient mechanism for controlling arm movement, particularly under significant loads, has not been found. Moreover~ none of the prior art level-winds of the swinging arm type can be readily adapted for use on a winch intended for high-load applications, except at very considerable expense and with very great :, ` ~
- ~A -weight, because o~ the forces brough-t to bear on the mechan:Lsms.
:[t is one objec-t of the present disclosure to provide a winch with an associated level-wind ; :
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generally of the sWincJincJ arm type wlth a relLAh:Le control or drive rnechanism for regulatincJ arm movement.
It is another object of the present disclosure to provide a winch with an associated level-wind generally of the swinging arm type adapted for high-load applications.
BRIEF SUMMARY OF TH:E INVENTION
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The invention provides a winch for spooling wire rope. The winch includes a support frame, a rope drum rotatably mounted on the support frame, and an associated rope drum drive also mounted on the ~ support frame for rotating the wire rope drum.
Sheave assembly means serve to transfer the wire rope to and from the rope drum. The sheave assembly means include a sheave support frame with irst and second end portions, a ~irst sheave mounted on the sheave support frame intermediate of the first and second end portions, and a second sheave moun~ted on the sheave support frarne intermediate of the first sheave and the second sheave support frame end portion. The sheaves are maintained in generally coplanar relationship, and have substantially parallel rotational axes. First hinge means connect , ., :
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, the first sheave suppor-t end por-tion to the winch support frame for hinged movement of the sheave support frame about a first hinge axis which is oriented generally perpendicular -to the drum rotational axis and also the sheave rotational axes. Second hinge means associated with the sheave support frame permit relative hinged movement of the first and second sheave support frame end portions about a second hinge axis which is oriented generally parallel to the first and second sheave rotational axes.
Drive means mounted on the winch support frame serve to drive the second sheave support end portion back and forth along a preselected arcuate path. The path is so selected that the second sheave is positioned along the path to convey the wire rope to and from the wire rope drum. The drive means include a guide shaft oriented generally parallel to the drum rotational axis, a drive member which is driven axially back and forth along the guide shaft, floating connection means whlch serve to connect the second sheave support end portion for axial movement with the drive member along the guide shaft and which permit displacem~nt of the second sheave support end portion from the drive member in a direction transverse to 7i' ~` '`'.
the longitud:inal ax:Ls oE the gllide shaE-t whereby tlle second sheave support end port:Lon can follow its arcuate path while the drive member Eollows its axially-directed path. Synchronization means associated with the drive means synchronize movement of the second sheave support end portion with rotation of the drum to reduce in operation the fleet angle formed between -the second sheave and the wire rope drum.
Various advantages of this type of winch construction will become more apparent from the description below of a preferred embodiment of the invention together wi.th directions regarding useful variationswhiich can be made to the preferred 15 ernbodlment.
DESCRIPTION OF THE DRAWINGS
The invention will be better understood with reference to drawings illustrating a preferred : embodiment, in which:
:~ fig. 1 is a side elevational view of a : 2`0 winch:embodying the invention;
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: fig. 2 is a plan v.iew of the winch;
fig. 3 is a fragmented side elevational view in vertical cross-section detailing the construction :~` ; : :
of a swinging arm type level-wind associated with the : 25 wlnch;
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fig. 4 :is a ragmented end vLew in verticaL
cross-section fur-ther detailing the construction of the level-wind; and, figs. 5-11 diagrammatically illustrate alternative orientations of the winch and associated level-wind mechanism.
DESCRIPTION OF PREFERRED EMBODIMENT
Figs. 1-4 illustrate a winch 10 for spooling wire rope 12 under line loads in excess of 200 tons. The winch 10 includes a winch support~frame of steel I-beam construction. A
lq ~wire rope drum ~ is mounted on an axle 20 to the winch support frame 14 for rotation about a generally horizontal, longitudinal drum rotational axis 22.
The rope drum ~ has a cylindrical drum section 24 on whlch wraps 26 cf the wire rope 12 are laid down, and a pair of opposing circular flanges 28, 30 which serve to contain the wire rope wraps 26. A hydraulic ~motor drum drive 32 mounted on the winch support frame 14 serves to rotate the rope drum ~ about its ~20 rotational~ axi~ 22 to haul in and pay out the wire ; rope 12. The construction of these various components incIuding brake mechanisms, controls etc. is well :
known,` and consequently will not be described in greater detail.
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A sheave assembly 3fi serves to trans:Ee:r the wire rope 12 to and from the rope drum 16. The sheave assembly 34 includes a steel support frame 36 which has a p~ir of opposing end portions 38, 40.
Wire rope is conveyed by the sheave assembly 34 over a pair of sheaves, namely, a first sheave 41 mounted intermediate of the sheave support frame end portions 38, 40, and a second sheave 42 mounted intermediate of the first sheave 40 and the second sheave support frame end portion 36. The sheaves 41, 42 are mounted on axles 44, 46, respectively, for rotation about sheave rotational axes 48, 50, respectively. The axle 44 is supported by roller bearing 52 from a pair of generally triangular-shaped, parallel plate portions 56, 58. The axle46 is supported b~ roller bearing 57 from a : connecting arm 60 including two generally parallel :plate~members 62, 64. The connecting arm 60 ~eeps : the ;sh~ave rotational axes 48, 50 substantially parallel, and keeps the sheaves 41, 42 generally : : coplanar and rigidly separated. A sheave 66 is : :provided on the winch support frame 14 to direct the wire rope 12 towards the sheave assembly 34, but this initial directing function could be provided by a sheave fixed to structure remote from the winch 10u :~ :
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A hillcJe joint 68 connects the sheave support frame end portion 38 to the winch support frame 14 to permi-t hinged movement of the sheave support frame 36 about a hinge axis 70. The hinge axis 70 is generally perpenclicular to the drum rotational axis 22 and -to the sheave rotational axes 48, S0, and thereby permits the second sheave support frame end portion 40 to swing along an arcuate path 72. Extreme positions 74, 76 of this swinging movement of the sheave support frame 36 are illustrated in stippled outline in fig. 2. The sheave 42 is positioned along the arcuate path 72 to deliver rope to and from the wire rope drum 16.
15The hinge joint 68 includes a pair of bearings 78~ 80 which attach the sheave support frame end portion 38 to the winch support frame 14 for rotation about the hinge axis 70. The bearlngs 78, 80 are axially aligned with the hinge axis 70, the bearing 78 being positiGned to one side 82 of the sheave rotational axis 48 proximate ~to the wire rope drum 16, and the bearing 80 being positioned to an opposing side 84 of the sheave : rotational axis 48, relatively distant from the 25wire rope drum 160 The bearing 78 is a thrust bearing braced on the winch support frame 14, as ` vj ; ti ~ 16 -illustrated in fig. 3,ayainst axial movement. rLIhe bearing 78 has a central aperture aligned with the hinge axis 70 and dimensioned to permit passage o the wire rope 12 axially along -the hinge axis 70. The ci.rcumferential rope groove 86 of the sheave 48 is so positioned that the first hinge axis passes substantially tangentially through the wire rope groove 48. The significance of this arrangement will be discussed in greater detail below.
A second hinge joint 88 permits relative hinged movement of the sheave support frame end portions about a second hinge axis, which in this particular embodiment of -the invention, is lS coincident with the sheave rotational axis 48. The hinge joint 88 is formed by coaxially mounting an end portion of the connecting arm 60 with the :~ sheave 41 on the axle 44~ This represents a very : simple way o forming the second hinge joint 88, :although for the purposes of the invention, as will be more apparent from the discussions below, the second hinge joint could be formed between the axle : 44 and the sheave support frame end portion 38. The ~ latter arrangement would, however, require additional : 25 components, such as an axle for pivotting attachmen-t of the connecting arm 60 to the support frame end , ., portion 38.
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~ dri.ve mechanism (not specii.ca~1y indicated) mounted on the w.inch support frame 14 serves to drive the sheave support frame end portion 40 back and forth along the arcuate path 72 in a manner conducive to proper spooling and unspooling of the wire rope 12 from the rope drum 16. The drive mechanism includes a diamond-threaded guide shaft 90 which is mounted on the winch support frame 14 by roller hearings (only one bearing 92 specifically illustrated and indicated in fig. 4) for rotation about a longitudinal guide shaft axis 94. The drive shaft has an endless helical groove 96, extending longitudinally along the guide shaft 94, a diamond~patterned groove such as found on many conventional screw drives. The guide shaft 90 extends through a pair of aligned apertures 98, 100 in the plate members 62, 64, with the guide shaEt : axis 94 ori.ented generally parallel to the drum rotational axis 22. The guide shaft 90 also 6 20 extends through a cylindrical aperture ~ Eormed in~a cast bronze drive member 104 positioned ~xially between the connecting arm plate members 62, 64.
The drive member includes a manganese-bronze fing~r 106 whlch extends into the helical groove 96 of the guide shaft 90, and consequently causes the drive member 10~ to move axially back and forth along '`:
~, the guide shaft 90 with rotation of the guide sha~t 90 about its axis 94.
The sheave suppor-t frame end portion 40 is connected to the drive member 104 by means of a floating connec-tion 108. The floating connection 108 includes a pair of slotted steel plates 110, 112, which are rigidly Eixed to the sheave support frame end portion 40 in substantially parallel, spaced-apart relationship, transversely between the connecting arm plates 62, 64. The plates 110, 112 have elongate slots 114, 116, respectively, which are substantially parallel to one another and oriented along radii extending from the hinge axis 70 about which the sheave support frame 36 swings.
Projectlons fixed to the drive member 104 extend into the slots 114, 116 for movement between opposing slot ends. The projections take the -form of two ~ axially-aligned stud-type track rollers 118, 120 which : are screwed respectively into threaded sockets 122, 124 integrally formed with the drive member 104. This : arrangement causes axial displacement of the sheave :~
`~ ~ support frame end portion 40 with axial movement of the drive member 104 along the guide shaft 90, and : slmultaneously permits displacement of the second : 25 sheave support frame end portion 40 relative ~o the drive member 104 transversely to the guide shaft ,, .
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90. The floating connec-tion thereby permits -the sheave support frame end portion 40 to be dr:iver along its arcuate path 72, as the drive member 104 is driven axially along the guide shaft 90 by rotation of the guide shaft 90.
The guide shaft 90 is mechanically coupled to the drum drive 32 Eor simultaneous rotation w:ith the rope drum 16 in an arrangement which reduces synchronization problems. The guide shaft 90 carries a sprocket 126 which is coupled by a chain 128 to a gear box 130 mounted on the winch support frame 14 and containing an epicyclic gear system. The gear box 130 is coupled by a pinion gear to peripheral portions 132 of the drurn flange 30 which are formed with a circumferential toothed track that mates wi.th the pinion gear. The gear ratio is selected so that the ratio of guide shaft rotation to drum rotation is fixed at a ~alue whlch tends to reduce flee~ angle during spooling.
The fleet angle is further reduced by a small electric motor 134 mounted on the gear box 130 and controlled by an associated fleet angle detector. The motor 134 is~coupled to the epicyclic gear system to advance ~; or retard the rate of rotation of the guide shaft 25~ 90 in response to the detected fleet angle thereby tending to drive the fleet angle to a zero value. The operation of such an epicycl~c gear system in the ~ 20 context oE a level-wind regulator involving a rope guicle drive of the screw--thread type powered from a drum clrive is known in the art, and conse~uen-tly will not be described in greater detail. Various alternative synchronization systems will also be apparent to one skilled in the art, and the system described is intended only to be exemplary.
A special stop mechanism is provided to reduce loading of the guide shaft 90 and the associated drive mechanism by the wire rope. The stop mechanism includes a plate-shaped steel stop member 136 which is fixed to the winch support frame 14. The stop member 136 is oriented generally parallel to the drum rotational axis 22, and acts against the sheave support frame end portion 40 which engages the stop member 136 throughout the arcuate path 72. This lateral mo~ement of the sheave support end portion 40 relative the stop member 136 is of course resisted by friction. Means are provided to reduce this frictional engagement thereby 20 ~ reducing the frictional forces which must ultimately be borne by the guide shaft 90 and associated drive : , ~
~mechanism. In particular, a ~ inch thick bronze rub plate is attached by countersunk screws to the stop meMber 136, covering the full extent of the stop member 136 normally expected to engage the sheave support frame end portion 40~ A second ~ inch plate formed of a ~, ~'`''~'" :
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__ _ The invention relates generally to the design and construction of winches, and more particularly to the construction of winches with level-wind regulators suitable for spooling wire rope under loads exceeding 200 tons such as migh-t occur for example in winches on ocean-yoing tugs or in the mooring of offshore drill platforms.
BACKGROUND OF TE~E INVENTION
The spooling of wire rope commonly involves a winch equipped with a wire rope drum and a drive which rotates the drum either to haul in or pay out the wire rope. The wire rope drum conventlonally has a cylindrical drum portion on which wraps of wire rope are laid down, most commonly several layers deep, and a pair of lS circular flanges at opposing ends of the cylindrical : : drum portion which conine the wire rope during spooling operations~ For tight side-by-side spooling : of wraps of wire rope on the drum, the maximum angle formed between the wire rope and a perpendicular from the cylindrical drum portion, namely, the "fleet angle", must be kept less than l~degrees throughout the spooling operation. If the fleet angle is allowed to exceed the speci-fied value, there will :~be a tenda.ncy for cross winding, excessive rope ; ;: , ..
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bending and snagglng in the wraps laid clown. Also, during paying out of -the wire rope under heavy loads, the rope may be subjected to sudden shocks as snagged lengths of rope are suddenly released.
All these factors tend to reduce the useful lifetime of the rope which in high -tension applications tends to be very expensive to replace.
In typicàl spooling operations, wire rope is initially directed to a winch by a fairlead sheave fixed to appropriate support structure remote from the winch. The fleet angle can be confined to an ideal range less than about 1~ degrees by simply locating the fairlead sheave a considerable dlstance from the winch drum; however, space constraints commonly makes such applications impractical. In order to provide a versatile winch which can accommodate pre-existing space requirements, it is common to mount a fleet angle compensator, commonly referred to as a "level-wind", directly on a winch support frame proximate to the assoclated wire rope drum. The level-wind serves to reduce the fleet angle effectively seen by the wire rope drum.
~ A variety of practical level-winds mounted directly on an associated winch support frame have 'r . /
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been manufactured Eor hlgh-load appll,cations. Thec;e level-wind~ most oEten lnvolve a rope c~uide mounted on heavy guide bars for movement back and forth in front of a rope drum. The rope guide quite commonly includes a pair of vertical rollers between which the rope is passed to the drum. A common alternative to vertical paired rollers is the provision on the rope guide of a sheave about which the wire rope travels towards the drum. A
variety of drive mechanisms have commonly been used to move the rope guide along the guide bars, including diamond-threaded screw drives, screw drives with more conventional helical threads, and hydraulically-operated pistons. In winches 15; employing screw-drives, movement of the guide member on the screw drive is commonly synchroni~ed with rotation of the drum for proper spooling by mechanically coupling the screw drive to the drum, as~with a chain drive, and the drum drive serves to simultaneously rotate the wire rope drum~and operate the level-wind. Synchronization in winches employing piston-type level-wind driv~s has been more complicated.
There are several problems associated with the level-winds commonly incorpora~ed on winches `''`'' .~
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for high-load appl:LcatLons. In particular, yuicle rollers are not particularly well suited to conveyance of w:ire rope, and often subject the rope to excessive bending during the effective reduction of fleet angle, thereby tending to shorten the useful lifetime of the wire rope unless the guide rollers are dramatically increased in diameter. Rope guides incorporating a sheave for transmission of the wire rope tend to damage the rope less, but normally require sheaves formed as very large and expensive forgings to resist reaction loads due to rope bend about the sheave and the manner of sheave mounting required.
Moreover, level winds of the type described above incorporating a sheave as a rope guide member have generally not been able to accommodate a very large fleet angle. Also, the rope guides and associated .
drive mechanisms must have a particularly robust constructions to withstand forces imposed on the mechanisms by bending of the path of the wire rope under high tension. For example, at an incldent fleet angle of 15 degrees, which is not ; uncommon in many practical applications, forces approaching 26 percent of the line load are applied . :
directly to the rope guide drive mechanism. These I .
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forces are very signlf:ican-t when line loads exceecl 200 tons. AccorcLingly, the various components of the rope guide and guide drive tend to be over-sized and expensive.
In light-load applications, winches have been manufactured which incorporate a level-wind with a "swinging arm". These level-winds include an arm which is hinged to the suppor-t frame of the winch and which normal].y carries a pair of sheaves, a first sheave positioned adjacent the hinge joint and a second sheave positioned adjacent the free, swinging end of the arm. Rope is commonly received initially by the first sheave, as from a remotely-located fairlead sheave, and transferred to the second sheave which then directs the rope towards the rope drum. The free end of the arm sweeps along an arcuate path a].ong which the second sheave can trans~er the rope to axially spaced-apart positlons along the wire rope drum. In applications ~ where th~e winch is to serve only as a storage winch, a traction winch may be interposed between the ncoming~wire rope and the storage winch so that the storage winch sees very little load. In such ;circumstances, the~swinain~ arm is allowed to pivot under the influence of the rope, and no special synchronization mechanism is required -~o ~:
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-ensure proper wrapping of the rope on the associated drum. In other applications, the swinging arm has been supported in a cantilevered arrangement, movement of the swinging arm being synchronized with the rota-tion of the drum by means oE a con-trol mechanism involving a hydraulic-cylinder drive which forms part of the cantilevered arrangemen-t.
Synchronization of arm movement with drum rotation in such a device has been a relatively complicated process.
Prior art level-winds of the swinging arm type have had the advantage that large fleet angles are eliminated, and that they can be positioned in very restricted space because distance from a remote fixed sheave initially directing rope towards the level-wind does not affect operation and the orces to which the swinging arm is otherwise subjected.
Also, they tend not to stress the associated wire rope excessively, because transfer of the wire rope is effected entirely over sheaves. However, a convenient mechanism for controlling arm movement, particularly under significant loads, has not been found. Moreover~ none of the prior art level-winds of the swinging arm type can be readily adapted for use on a winch intended for high-load applications, except at very considerable expense and with very great :, ` ~
- ~A -weight, because o~ the forces brough-t to bear on the mechan:Lsms.
:[t is one objec-t of the present disclosure to provide a winch with an associated level-wind ; :
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generally of the sWincJincJ arm type wlth a relLAh:Le control or drive rnechanism for regulatincJ arm movement.
It is another object of the present disclosure to provide a winch with an associated level-wind generally of the swinging arm type adapted for high-load applications.
BRIEF SUMMARY OF TH:E INVENTION
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The invention provides a winch for spooling wire rope. The winch includes a support frame, a rope drum rotatably mounted on the support frame, and an associated rope drum drive also mounted on the ~ support frame for rotating the wire rope drum.
Sheave assembly means serve to transfer the wire rope to and from the rope drum. The sheave assembly means include a sheave support frame with irst and second end portions, a ~irst sheave mounted on the sheave support frame intermediate of the first and second end portions, and a second sheave moun~ted on the sheave support frarne intermediate of the first sheave and the second sheave support frame end portion. The sheaves are maintained in generally coplanar relationship, and have substantially parallel rotational axes. First hinge means connect , ., :
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, the first sheave suppor-t end por-tion to the winch support frame for hinged movement of the sheave support frame about a first hinge axis which is oriented generally perpendicular -to the drum rotational axis and also the sheave rotational axes. Second hinge means associated with the sheave support frame permit relative hinged movement of the first and second sheave support frame end portions about a second hinge axis which is oriented generally parallel to the first and second sheave rotational axes.
Drive means mounted on the winch support frame serve to drive the second sheave support end portion back and forth along a preselected arcuate path. The path is so selected that the second sheave is positioned along the path to convey the wire rope to and from the wire rope drum. The drive means include a guide shaft oriented generally parallel to the drum rotational axis, a drive member which is driven axially back and forth along the guide shaft, floating connection means whlch serve to connect the second sheave support end portion for axial movement with the drive member along the guide shaft and which permit displacem~nt of the second sheave support end portion from the drive member in a direction transverse to 7i' ~` '`'.
the longitud:inal ax:Ls oE the gllide shaE-t whereby tlle second sheave support end port:Lon can follow its arcuate path while the drive member Eollows its axially-directed path. Synchronization means associated with the drive means synchronize movement of the second sheave support end portion with rotation of the drum to reduce in operation the fleet angle formed between -the second sheave and the wire rope drum.
Various advantages of this type of winch construction will become more apparent from the description below of a preferred embodiment of the invention together wi.th directions regarding useful variationswhiich can be made to the preferred 15 ernbodlment.
DESCRIPTION OF THE DRAWINGS
The invention will be better understood with reference to drawings illustrating a preferred : embodiment, in which:
:~ fig. 1 is a side elevational view of a : 2`0 winch:embodying the invention;
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: fig. 2 is a plan v.iew of the winch;
fig. 3 is a fragmented side elevational view in vertical cross-section detailing the construction :~` ; : :
of a swinging arm type level-wind associated with the : 25 wlnch;
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fig. 4 :is a ragmented end vLew in verticaL
cross-section fur-ther detailing the construction of the level-wind; and, figs. 5-11 diagrammatically illustrate alternative orientations of the winch and associated level-wind mechanism.
DESCRIPTION OF PREFERRED EMBODIMENT
Figs. 1-4 illustrate a winch 10 for spooling wire rope 12 under line loads in excess of 200 tons. The winch 10 includes a winch support~frame of steel I-beam construction. A
lq ~wire rope drum ~ is mounted on an axle 20 to the winch support frame 14 for rotation about a generally horizontal, longitudinal drum rotational axis 22.
The rope drum ~ has a cylindrical drum section 24 on whlch wraps 26 cf the wire rope 12 are laid down, and a pair of opposing circular flanges 28, 30 which serve to contain the wire rope wraps 26. A hydraulic ~motor drum drive 32 mounted on the winch support frame 14 serves to rotate the rope drum ~ about its ~20 rotational~ axi~ 22 to haul in and pay out the wire ; rope 12. The construction of these various components incIuding brake mechanisms, controls etc. is well :
known,` and consequently will not be described in greater detail.
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A sheave assembly 3fi serves to trans:Ee:r the wire rope 12 to and from the rope drum 16. The sheave assembly 34 includes a steel support frame 36 which has a p~ir of opposing end portions 38, 40.
Wire rope is conveyed by the sheave assembly 34 over a pair of sheaves, namely, a first sheave 41 mounted intermediate of the sheave support frame end portions 38, 40, and a second sheave 42 mounted intermediate of the first sheave 40 and the second sheave support frame end portion 36. The sheaves 41, 42 are mounted on axles 44, 46, respectively, for rotation about sheave rotational axes 48, 50, respectively. The axle 44 is supported by roller bearing 52 from a pair of generally triangular-shaped, parallel plate portions 56, 58. The axle46 is supported b~ roller bearing 57 from a : connecting arm 60 including two generally parallel :plate~members 62, 64. The connecting arm 60 ~eeps : the ;sh~ave rotational axes 48, 50 substantially parallel, and keeps the sheaves 41, 42 generally : : coplanar and rigidly separated. A sheave 66 is : :provided on the winch support frame 14 to direct the wire rope 12 towards the sheave assembly 34, but this initial directing function could be provided by a sheave fixed to structure remote from the winch 10u :~ :
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A hillcJe joint 68 connects the sheave support frame end portion 38 to the winch support frame 14 to permi-t hinged movement of the sheave support frame 36 about a hinge axis 70. The hinge axis 70 is generally perpenclicular to the drum rotational axis 22 and -to the sheave rotational axes 48, S0, and thereby permits the second sheave support frame end portion 40 to swing along an arcuate path 72. Extreme positions 74, 76 of this swinging movement of the sheave support frame 36 are illustrated in stippled outline in fig. 2. The sheave 42 is positioned along the arcuate path 72 to deliver rope to and from the wire rope drum 16.
15The hinge joint 68 includes a pair of bearings 78~ 80 which attach the sheave support frame end portion 38 to the winch support frame 14 for rotation about the hinge axis 70. The bearlngs 78, 80 are axially aligned with the hinge axis 70, the bearing 78 being positiGned to one side 82 of the sheave rotational axis 48 proximate ~to the wire rope drum 16, and the bearing 80 being positioned to an opposing side 84 of the sheave : rotational axis 48, relatively distant from the 25wire rope drum 160 The bearing 78 is a thrust bearing braced on the winch support frame 14, as ` vj ; ti ~ 16 -illustrated in fig. 3,ayainst axial movement. rLIhe bearing 78 has a central aperture aligned with the hinge axis 70 and dimensioned to permit passage o the wire rope 12 axially along -the hinge axis 70. The ci.rcumferential rope groove 86 of the sheave 48 is so positioned that the first hinge axis passes substantially tangentially through the wire rope groove 48. The significance of this arrangement will be discussed in greater detail below.
A second hinge joint 88 permits relative hinged movement of the sheave support frame end portions about a second hinge axis, which in this particular embodiment of -the invention, is lS coincident with the sheave rotational axis 48. The hinge joint 88 is formed by coaxially mounting an end portion of the connecting arm 60 with the :~ sheave 41 on the axle 44~ This represents a very : simple way o forming the second hinge joint 88, :although for the purposes of the invention, as will be more apparent from the discussions below, the second hinge joint could be formed between the axle : 44 and the sheave support frame end portion 38. The ~ latter arrangement would, however, require additional : 25 components, such as an axle for pivotting attachmen-t of the connecting arm 60 to the support frame end , ., portion 38.
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~ dri.ve mechanism (not specii.ca~1y indicated) mounted on the w.inch support frame 14 serves to drive the sheave support frame end portion 40 back and forth along the arcuate path 72 in a manner conducive to proper spooling and unspooling of the wire rope 12 from the rope drum 16. The drive mechanism includes a diamond-threaded guide shaft 90 which is mounted on the winch support frame 14 by roller hearings (only one bearing 92 specifically illustrated and indicated in fig. 4) for rotation about a longitudinal guide shaft axis 94. The drive shaft has an endless helical groove 96, extending longitudinally along the guide shaft 94, a diamond~patterned groove such as found on many conventional screw drives. The guide shaft 90 extends through a pair of aligned apertures 98, 100 in the plate members 62, 64, with the guide shaEt : axis 94 ori.ented generally parallel to the drum rotational axis 22. The guide shaft 90 also 6 20 extends through a cylindrical aperture ~ Eormed in~a cast bronze drive member 104 positioned ~xially between the connecting arm plate members 62, 64.
The drive member includes a manganese-bronze fing~r 106 whlch extends into the helical groove 96 of the guide shaft 90, and consequently causes the drive member 10~ to move axially back and forth along '`:
~, the guide shaft 90 with rotation of the guide sha~t 90 about its axis 94.
The sheave suppor-t frame end portion 40 is connected to the drive member 104 by means of a floating connec-tion 108. The floating connection 108 includes a pair of slotted steel plates 110, 112, which are rigidly Eixed to the sheave support frame end portion 40 in substantially parallel, spaced-apart relationship, transversely between the connecting arm plates 62, 64. The plates 110, 112 have elongate slots 114, 116, respectively, which are substantially parallel to one another and oriented along radii extending from the hinge axis 70 about which the sheave support frame 36 swings.
Projectlons fixed to the drive member 104 extend into the slots 114, 116 for movement between opposing slot ends. The projections take the -form of two ~ axially-aligned stud-type track rollers 118, 120 which : are screwed respectively into threaded sockets 122, 124 integrally formed with the drive member 104. This : arrangement causes axial displacement of the sheave :~
`~ ~ support frame end portion 40 with axial movement of the drive member 104 along the guide shaft 90, and : slmultaneously permits displacement of the second : 25 sheave support frame end portion 40 relative ~o the drive member 104 transversely to the guide shaft ,, .
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90. The floating connec-tion thereby permits -the sheave support frame end portion 40 to be dr:iver along its arcuate path 72, as the drive member 104 is driven axially along the guide shaft 90 by rotation of the guide shaft 90.
The guide shaft 90 is mechanically coupled to the drum drive 32 Eor simultaneous rotation w:ith the rope drum 16 in an arrangement which reduces synchronization problems. The guide shaft 90 carries a sprocket 126 which is coupled by a chain 128 to a gear box 130 mounted on the winch support frame 14 and containing an epicyclic gear system. The gear box 130 is coupled by a pinion gear to peripheral portions 132 of the drurn flange 30 which are formed with a circumferential toothed track that mates wi.th the pinion gear. The gear ratio is selected so that the ratio of guide shaft rotation to drum rotation is fixed at a ~alue whlch tends to reduce flee~ angle during spooling.
The fleet angle is further reduced by a small electric motor 134 mounted on the gear box 130 and controlled by an associated fleet angle detector. The motor 134 is~coupled to the epicyclic gear system to advance ~; or retard the rate of rotation of the guide shaft 25~ 90 in response to the detected fleet angle thereby tending to drive the fleet angle to a zero value. The operation of such an epicycl~c gear system in the ~ 20 context oE a level-wind regulator involving a rope guicle drive of the screw--thread type powered from a drum clrive is known in the art, and conse~uen-tly will not be described in greater detail. Various alternative synchronization systems will also be apparent to one skilled in the art, and the system described is intended only to be exemplary.
A special stop mechanism is provided to reduce loading of the guide shaft 90 and the associated drive mechanism by the wire rope. The stop mechanism includes a plate-shaped steel stop member 136 which is fixed to the winch support frame 14. The stop member 136 is oriented generally parallel to the drum rotational axis 22, and acts against the sheave support frame end portion 40 which engages the stop member 136 throughout the arcuate path 72. This lateral mo~ement of the sheave support end portion 40 relative the stop member 136 is of course resisted by friction. Means are provided to reduce this frictional engagement thereby 20 ~ reducing the frictional forces which must ultimately be borne by the guide shaft 90 and associated drive : , ~
~mechanism. In particular, a ~ inch thick bronze rub plate is attached by countersunk screws to the stop meMber 136, covering the full extent of the stop member 136 normally expected to engage the sheave support frame end portion 40~ A second ~ inch plate formed of a ~, ~'`''~'" :
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Eluorocarbon and havincJ dimensions Oe about :L2 :in~he;
by 36 inches, is attached by countersunk sc:rews to a steel backing plate 142 which :is rigidly fixed to the sheave support frame end portion 40. The exposed planar surface of the plate 140 overlays the exposed planar surface of the bronze plate 138 throughou-t the swinging movement of the sheave support frame 36.
The contacted surfaces of the plates 138, 140 have a coefficient of frictiorl in the order of about .05-.1, and accordingly, in the arrangement described, if the line load on the wire rope 12 is about 200 tons, a frictional axially-directed force of only about 10-20 tons must be borne directly by the guide shaft 90 and the associated drive mechanism. Since only 10-20 percent of line load must be accommodated, it will be apparent that the arrangement described produces a significant reduction in th~ size and expense associated with the components of the guide shat 90 and associated drive mechanism, as compared wi-th prior art level-w.ind~
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: ~ 20 ;intended for high-load applications.
; There are a number of advantages obtained with the~winch and level-wind design described above.
First, because of the inherent swinging arm design, fleet : angles are eliminated even on very wide drums, wire rope : 25 is not unduly stressed, and long rope leads from remote sheaves are not required, as has been the case with .
``~ prior art high-load spooling devices, thereby permitting :: ' - 21A ~
the winch to more readily accommodate -the space constraints o:E a host vessel or structure. The provision of the hinge joint 88 between the sheave support frame end portions ~ .
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38, 40 ensures tha-t a .l.arge bending moment whi.ch wouLd otherwise o~cur w.ith passage o the wire rope ove:r the sheaves 41, 42 is not applied -to the hinge joint 68 at the winch support frame 14. The forces are instead reacted into the winch support frame 14 by the stop member 136. Addi-tionally, because of -the tangential passage of the hinge axes 70 through the wire rope groove 86 of the sheave 41, axial forces applied by the wire rope to the hinge joint 68 can be accommodated almost entirely by the thrust bearing 78, which can be conveniently sized to withstand axial forces exceeding the breakaye limit of the wire rope. Moreover, the engagement of the stop member 136 with the sheave support frame end portion 40 reduces to a very managable level the extremely high loads which would otherwise : have to be borne by the guide shaft 90 and associated . drive mechanism, given the swinging arm design.
This of course permits use of less c05tly CompGnents.
A number of variations may be made in the winch design described above. In particular, the stop mechanism provided, namely~ a pair of rub plates w1th a low coefficient of friction, could be replaced by a set of rollers mounted on the support frame end portion 40 for rolling movement along the stop member 1360 This arrangement would be particularly `.";
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~ 23 -suitable Eor lighter loads. The use of such rollers in high-load applica-tions may be considerably more costl~
than the use oE the rub plates described, as both the stop member 136 and the rollers would have to be provided with extremely hard surfaces to ensure a proper reduction of rolling friction, and this would involve cos-tly metal alloys and manufacturing techniques.
Alkernative rub surfaces can be provided on the stop member 136 and the sheave support end portion 40.
For example, the stop member can be provided with a s-teel plate electroplated with nickel or chromium. The plate attached to the sheave support end portion can be made of bronze with graphite or other dry lubricants empregnated in i~ surface, or of phenolic resin empregnated with graphite or nolybedinium disulphide, or of an appropriate nylon. Many alternatives are possible, the primary concern being a low coefficient o~ friction, and in most applications, concern for hardness and corros_on resistant quallties.
Also, in light-load applications, it is possible to eliminate the stop member 136, and to allow the guide shaft 90 and associated drive mechanisms to bear the line loads. Many of the advantages described above are still obtained, such as elimination of large fleet angles, gentle treatment of the wire rope, dispensing with long rope leads and convenient control of swinying arm movement. However, it should be noted that such an ' .~ .
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- 2~ -arrangement would ten~ to be oversizecl and prohibitivel~
expensive for high-load applications.
The sheave 66 mounted on the support frame 14 permits very convenien-t installation of the winch 10 on a pre-existing host vessel or structure. In the winch 10, the sheave 66 is moun-ted in a vertical plane to receive rope from below. Howevar, the sheave 66 can be mounted in any orientation, for example, horizontal or angled relative to horizontal, to accommodate any pre-existing rope guiding system found on the host structure that dictates the dixection from which rope is to be received. The winch can consequently be constructed to accommodate the existing space constraints of the host vessel or structure. A swivelling sheave might be substituted for the sheave 66, to obtain additional versatility in use, but such a sheave assembly would~have an expensive construction to accommodate the high loads.
FigsO 5 11 diagrammatically illustrate a1ternative relative configurations of the rope drum 16~and the sheave assembly 34. The arrangements are all substantially identical to that inherent in the views of figs. 1-4, except -the hinge axis joining the sheave support frame 34 to the winch frame 14 has been relocated in most instances. These variants might . , :
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~ 25 -be considered where space requirements in given applications require rope init:ially to be received from directions dictated by equipment or structures adjacent the winch.
I-t will be appreciated that a particular embodiment of the invention has been described, and that modifications may be made therein without departing from the spirit of the invention or the scope of the appended claims.
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Eluorocarbon and havincJ dimensions Oe about :L2 :in~he;
by 36 inches, is attached by countersunk sc:rews to a steel backing plate 142 which :is rigidly fixed to the sheave support frame end portion 40. The exposed planar surface of the plate 140 overlays the exposed planar surface of the bronze plate 138 throughou-t the swinging movement of the sheave support frame 36.
The contacted surfaces of the plates 138, 140 have a coefficient of frictiorl in the order of about .05-.1, and accordingly, in the arrangement described, if the line load on the wire rope 12 is about 200 tons, a frictional axially-directed force of only about 10-20 tons must be borne directly by the guide shaft 90 and the associated drive mechanism. Since only 10-20 percent of line load must be accommodated, it will be apparent that the arrangement described produces a significant reduction in th~ size and expense associated with the components of the guide shat 90 and associated drive mechanism, as compared wi-th prior art level-w.ind~
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: ~ 20 ;intended for high-load applications.
; There are a number of advantages obtained with the~winch and level-wind design described above.
First, because of the inherent swinging arm design, fleet : angles are eliminated even on very wide drums, wire rope : 25 is not unduly stressed, and long rope leads from remote sheaves are not required, as has been the case with .
``~ prior art high-load spooling devices, thereby permitting :: ' - 21A ~
the winch to more readily accommodate -the space constraints o:E a host vessel or structure. The provision of the hinge joint 88 between the sheave support frame end portions ~ .
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38, 40 ensures tha-t a .l.arge bending moment whi.ch wouLd otherwise o~cur w.ith passage o the wire rope ove:r the sheaves 41, 42 is not applied -to the hinge joint 68 at the winch support frame 14. The forces are instead reacted into the winch support frame 14 by the stop member 136. Addi-tionally, because of -the tangential passage of the hinge axes 70 through the wire rope groove 86 of the sheave 41, axial forces applied by the wire rope to the hinge joint 68 can be accommodated almost entirely by the thrust bearing 78, which can be conveniently sized to withstand axial forces exceeding the breakaye limit of the wire rope. Moreover, the engagement of the stop member 136 with the sheave support frame end portion 40 reduces to a very managable level the extremely high loads which would otherwise : have to be borne by the guide shaft 90 and associated . drive mechanism, given the swinging arm design.
This of course permits use of less c05tly CompGnents.
A number of variations may be made in the winch design described above. In particular, the stop mechanism provided, namely~ a pair of rub plates w1th a low coefficient of friction, could be replaced by a set of rollers mounted on the support frame end portion 40 for rolling movement along the stop member 1360 This arrangement would be particularly `.";
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~ 23 -suitable Eor lighter loads. The use of such rollers in high-load applica-tions may be considerably more costl~
than the use oE the rub plates described, as both the stop member 136 and the rollers would have to be provided with extremely hard surfaces to ensure a proper reduction of rolling friction, and this would involve cos-tly metal alloys and manufacturing techniques.
Alkernative rub surfaces can be provided on the stop member 136 and the sheave support end portion 40.
For example, the stop member can be provided with a s-teel plate electroplated with nickel or chromium. The plate attached to the sheave support end portion can be made of bronze with graphite or other dry lubricants empregnated in i~ surface, or of phenolic resin empregnated with graphite or nolybedinium disulphide, or of an appropriate nylon. Many alternatives are possible, the primary concern being a low coefficient o~ friction, and in most applications, concern for hardness and corros_on resistant quallties.
Also, in light-load applications, it is possible to eliminate the stop member 136, and to allow the guide shaft 90 and associated drive mechanisms to bear the line loads. Many of the advantages described above are still obtained, such as elimination of large fleet angles, gentle treatment of the wire rope, dispensing with long rope leads and convenient control of swinying arm movement. However, it should be noted that such an ' .~ .
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7~
- 2~ -arrangement would ten~ to be oversizecl and prohibitivel~
expensive for high-load applications.
The sheave 66 mounted on the support frame 14 permits very convenien-t installation of the winch 10 on a pre-existing host vessel or structure. In the winch 10, the sheave 66 is moun-ted in a vertical plane to receive rope from below. Howevar, the sheave 66 can be mounted in any orientation, for example, horizontal or angled relative to horizontal, to accommodate any pre-existing rope guiding system found on the host structure that dictates the dixection from which rope is to be received. The winch can consequently be constructed to accommodate the existing space constraints of the host vessel or structure. A swivelling sheave might be substituted for the sheave 66, to obtain additional versatility in use, but such a sheave assembly would~have an expensive construction to accommodate the high loads.
FigsO 5 11 diagrammatically illustrate a1ternative relative configurations of the rope drum 16~and the sheave assembly 34. The arrangements are all substantially identical to that inherent in the views of figs. 1-4, except -the hinge axis joining the sheave support frame 34 to the winch frame 14 has been relocated in most instances. These variants might . , :
.
~ .
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~ 25 -be considered where space requirements in given applications require rope init:ially to be received from directions dictated by equipment or structures adjacent the winch.
I-t will be appreciated that a particular embodiment of the invention has been described, and that modifications may be made therein without departing from the spirit of the invention or the scope of the appended claims.
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Claims (8)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A winch for spooling wire rope, comprising:
a winch support frame;
a wire rope drum mounted on the winch support frame for rotation about a longitudinal drum rotational axis;
a rope drum drive mounted on the winch support frame for rotating the wire rope drum about the drum rotational axis;
sheave assembly means for transfering the wire rope to and from the wire rope drum, the sheave assembly means including (a) a sheave support frame having first and second sheave support frame end portions, (b) a first sheave mounted on the sheave support frame intermediate of the first and second support frame end portions for rotation about a first sheave rotational axis, (c) a second sheave mounted on the sheave support frame intermediate of the first sheave and the second sheave support frame end portion for rotation about a second sheave rotational axis substantially parallel to the first sheave rotational axis, the sheave support frame including means for maintaining the second sheave generally co-planar with and rigidly separated from the first sheave, (d) first hinge means for connecting the first sheave support frame end portion to the winch support frame for hinged movement of the sheave support frame about a first hinge axis generally perpendicular to the drum rotational axis and to the first and second sheave rotational axes, and (e) second hinge means for connecting the second sheave support frame end portion to the first sheave support end portion for relative hinged movement of the first and second sheave support frame end portions about a second hinge axis generally parallel to the first and second sheave rotational axes;
drive means mounted on the winch support frame for driving the second sheave support frame end portion back and forth along a preselected arcuate path along which the second sheave is positioned to convey the wire rope to and from the wire rope drum, the drive means including (a) a guide shaft having a longitudinal guide shaft axis generally parallel to the drum rotational axis, (b) a drive member attached to the guide shaft and driven by the drive means axially back and forth along the guide shaft, (c) floating connection means for connecting the second sheave support end portion to the drive member for axial movement with the drive member along the guide shaft and for permitting displacement of the second sheave support end portion from the drive member transverse to the longitudinal axis of the guide shaft, and, (d) synchronization means for synchronizing the rate of movement of the second sheave support end portion along the arcuate path with the rate of rotation of the drum to thereby reduce in operation the fleet angle formed between the second sheave and the wire rope drum;
stop means acting between the winch support frame and the second sheave support end portion for preventing hinged movement of the second sheave support end portion towards the wire rope drum as the second sheave support end portion is driven by the driving means along the preselected arcuate path.
a winch support frame;
a wire rope drum mounted on the winch support frame for rotation about a longitudinal drum rotational axis;
a rope drum drive mounted on the winch support frame for rotating the wire rope drum about the drum rotational axis;
sheave assembly means for transfering the wire rope to and from the wire rope drum, the sheave assembly means including (a) a sheave support frame having first and second sheave support frame end portions, (b) a first sheave mounted on the sheave support frame intermediate of the first and second support frame end portions for rotation about a first sheave rotational axis, (c) a second sheave mounted on the sheave support frame intermediate of the first sheave and the second sheave support frame end portion for rotation about a second sheave rotational axis substantially parallel to the first sheave rotational axis, the sheave support frame including means for maintaining the second sheave generally co-planar with and rigidly separated from the first sheave, (d) first hinge means for connecting the first sheave support frame end portion to the winch support frame for hinged movement of the sheave support frame about a first hinge axis generally perpendicular to the drum rotational axis and to the first and second sheave rotational axes, and (e) second hinge means for connecting the second sheave support frame end portion to the first sheave support end portion for relative hinged movement of the first and second sheave support frame end portions about a second hinge axis generally parallel to the first and second sheave rotational axes;
drive means mounted on the winch support frame for driving the second sheave support frame end portion back and forth along a preselected arcuate path along which the second sheave is positioned to convey the wire rope to and from the wire rope drum, the drive means including (a) a guide shaft having a longitudinal guide shaft axis generally parallel to the drum rotational axis, (b) a drive member attached to the guide shaft and driven by the drive means axially back and forth along the guide shaft, (c) floating connection means for connecting the second sheave support end portion to the drive member for axial movement with the drive member along the guide shaft and for permitting displacement of the second sheave support end portion from the drive member transverse to the longitudinal axis of the guide shaft, and, (d) synchronization means for synchronizing the rate of movement of the second sheave support end portion along the arcuate path with the rate of rotation of the drum to thereby reduce in operation the fleet angle formed between the second sheave and the wire rope drum;
stop means acting between the winch support frame and the second sheave support end portion for preventing hinged movement of the second sheave support end portion towards the wire rope drum as the second sheave support end portion is driven by the driving means along the preselected arcuate path.
2. A winch as claimed in claim 2 in which the stop means comprise a stop member fixed to the sheave support generally parallel to the drum rotational axis and engaging the second sheave end portion, and resistance reduction means acting between the stop member and the second sheave support end portion for reducing frictional resistance to lateral movement of the second sheave support end portion relative to the stop member due to engagement of the stop member with the second sheave support end portion.
3. A winch as claimed in claim 2 in which:
the guide shaft is mounted on the winch support frame for rotation about the guide shaft axis;
the guide shaft has an endless helical groove extending longitudinally along the guide shaft;
the drive member has a projection so fitted in the endless helical groove that rotation of the guide shaft about the guide shaft axis causes the drive member to move axially back and forth along the guide shaft; and, the drive means include rotation means for rotating the guide shaft about the guide shaft axis.
the guide shaft is mounted on the winch support frame for rotation about the guide shaft axis;
the guide shaft has an endless helical groove extending longitudinally along the guide shaft;
the drive member has a projection so fitted in the endless helical groove that rotation of the guide shaft about the guide shaft axis causes the drive member to move axially back and forth along the guide shaft; and, the drive means include rotation means for rotating the guide shaft about the guide shaft axis.
4. A winch as claimed in claim 3 in which:
the rotation means include mechanical coupling means for coupling the guide shaft to the rope drum drive for rotation of the guide shaft by the rope drum drive, the mechanical coupling means including means for fixing the ratio of the rate of rotation of the guide shaft to the rate of rotation of the wire rope drum at a value selected to reduce in operation the fleet angle formed between the second sheave and the wire rope drum.
the rotation means include mechanical coupling means for coupling the guide shaft to the rope drum drive for rotation of the guide shaft by the rope drum drive, the mechanical coupling means including means for fixing the ratio of the rate of rotation of the guide shaft to the rate of rotation of the wire rope drum at a value selected to reduce in operation the fleet angle formed between the second sheave and the wire rope drum.
5. A winch as claimed in claim 2 in which the floating connection means comprise:
a first connection member rigidly fixed to one of the drive member and the second sheave support frame end portion, the first connection member having an elongate slot oriented generally transverse to the guide shaft axis and having a pair of opposing slot ends;
a second connection member fixed to the other of the drive member and the second sheave support frame end portion, the second connection member having a projection fitted in the elongate slot for movement between the opposing slot ends.
a first connection member rigidly fixed to one of the drive member and the second sheave support frame end portion, the first connection member having an elongate slot oriented generally transverse to the guide shaft axis and having a pair of opposing slot ends;
a second connection member fixed to the other of the drive member and the second sheave support frame end portion, the second connection member having a projection fitted in the elongate slot for movement between the opposing slot ends.
6. A winch as claimed in claim 2 in which:
the stop means have a first planar surface substantially parallel to the drum rotational axis;
the second sheave support frame end portion has a second planar surface overlaying the first planar surface;
the first planar surface has sufficient extent that the second planar surface remains in overlaying contact with the first planar surface as the second sheave support frame end portion moves along the preselected arcuate path; and, the first and second planar surfaces are formed of materials which have a mutual coefficient of friction less than about .2.
the stop means have a first planar surface substantially parallel to the drum rotational axis;
the second sheave support frame end portion has a second planar surface overlaying the first planar surface;
the first planar surface has sufficient extent that the second planar surface remains in overlaying contact with the first planar surface as the second sheave support frame end portion moves along the preselected arcuate path; and, the first and second planar surfaces are formed of materials which have a mutual coefficient of friction less than about .2.
7. A winch as claimed in claim 2 in which the first hinge means comprise:
first and second bearings attaching the first sheave support frame end portion to the winch support frame, the first and second bearings being axially aligned with the first hinge axis, the first bearing being positioned along the first hinge axis to one side of the first sheave rotational axis relatively proximate to the wire rope and the second bearing being positioned along the first hinge axis to an opposing side of the first sheave rotational axis;
the first bearing being a thrust bearing braced on the winch support frame against axial movement and having a central aperture dimensioned to permit passage of the wire rope axially through the first bearing;
the first sheave having a circumferential rope groove and being so positioned that the first hinge axis passes substantially tangentially through the wire rope groove, whereby, the wire rope may be conveyed along the first hinge axis through the first bearing and around the rope groove.
first and second bearings attaching the first sheave support frame end portion to the winch support frame, the first and second bearings being axially aligned with the first hinge axis, the first bearing being positioned along the first hinge axis to one side of the first sheave rotational axis relatively proximate to the wire rope and the second bearing being positioned along the first hinge axis to an opposing side of the first sheave rotational axis;
the first bearing being a thrust bearing braced on the winch support frame against axial movement and having a central aperture dimensioned to permit passage of the wire rope axially through the first bearing;
the first sheave having a circumferential rope groove and being so positioned that the first hinge axis passes substantially tangentially through the wire rope groove, whereby, the wire rope may be conveyed along the first hinge axis through the first bearing and around the rope groove.
8. A winch for spooling wire rope, comprising:
a winch support frame;
a wire rope drum mounted on the winch support frame for rotation about a longitudinal drum rotational axis;
a rope drum drive mounted on the winch support frame for rotating the wire rope drum about the drum rotational axis;
sheave assembly means for transfering the wire rope to and from the wire rope drum, the sheave assembly means including (a) a sheave support frame having first and second sheave support frame end portions, (b) a first sheave mounted on the sheave support frame intermediate of the first and second support frame end portions for rotation about a first sheave rotational axis, (c) a second sheave mounted on the sheave support frame intermediate of the first sheave and the second sheave support frame end portion for rotation about a second sheave rotational axis substantially parallel to the first sheave rotational axis, the sheave support frame including means for maintaining the second sheave generally co-planar with and rigidly separated from the first sheave, (d) first hinge means for connecting the first sheave support frame end portion to the winch support frame for hinged movement of the sheave support frame about a first hinge axis generally perpendicular to the drum rotational axis and to the first and second sheave rotational axes, and (e) second hinge means for connecting the second sheave support frame end portion to the first sheave support end portion for relative hinged movement of the first and second sheave support frame end portions about a second hinge axis generally parallel to the first and second sheave rotational axes;
drive means mounted on the winch support frame for driving the second sheave support frame end portion back and forth along a preselected arcuate path along which the second sheave is positioned to convey the wire rope to and from the wire rope drum, the drive means including (a) a guide shaft having a longitudinal guide shaft axis generally parallel to the drum rotational axis, (b) a drive member attached to the guide shaft and driven by the drive means axially back and forth along the guide shaft, (c) floating connection means for connecting the second sheave support end portion to the drive member for axial movement with the drive member along the guide shaft and for permitting displacement of the second sheave support end portion from the drive member transverse to the longitudinal axis of the guide shaft, and, (d) synchronization means for synchronizing the rate of movement of the second sheave support end portion along the arcuate path with the rate of rotation of the drum to thereby reduce in operation the fleet angle formed between the second sheave and the wire rope drum.
a winch support frame;
a wire rope drum mounted on the winch support frame for rotation about a longitudinal drum rotational axis;
a rope drum drive mounted on the winch support frame for rotating the wire rope drum about the drum rotational axis;
sheave assembly means for transfering the wire rope to and from the wire rope drum, the sheave assembly means including (a) a sheave support frame having first and second sheave support frame end portions, (b) a first sheave mounted on the sheave support frame intermediate of the first and second support frame end portions for rotation about a first sheave rotational axis, (c) a second sheave mounted on the sheave support frame intermediate of the first sheave and the second sheave support frame end portion for rotation about a second sheave rotational axis substantially parallel to the first sheave rotational axis, the sheave support frame including means for maintaining the second sheave generally co-planar with and rigidly separated from the first sheave, (d) first hinge means for connecting the first sheave support frame end portion to the winch support frame for hinged movement of the sheave support frame about a first hinge axis generally perpendicular to the drum rotational axis and to the first and second sheave rotational axes, and (e) second hinge means for connecting the second sheave support frame end portion to the first sheave support end portion for relative hinged movement of the first and second sheave support frame end portions about a second hinge axis generally parallel to the first and second sheave rotational axes;
drive means mounted on the winch support frame for driving the second sheave support frame end portion back and forth along a preselected arcuate path along which the second sheave is positioned to convey the wire rope to and from the wire rope drum, the drive means including (a) a guide shaft having a longitudinal guide shaft axis generally parallel to the drum rotational axis, (b) a drive member attached to the guide shaft and driven by the drive means axially back and forth along the guide shaft, (c) floating connection means for connecting the second sheave support end portion to the drive member for axial movement with the drive member along the guide shaft and for permitting displacement of the second sheave support end portion from the drive member transverse to the longitudinal axis of the guide shaft, and, (d) synchronization means for synchronizing the rate of movement of the second sheave support end portion along the arcuate path with the rate of rotation of the drum to thereby reduce in operation the fleet angle formed between the second sheave and the wire rope drum.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000463805A CA1254876A (en) | 1984-09-21 | 1984-09-21 | Winch with level-wind regulator |
| GB08523420A GB2165201B (en) | 1984-09-21 | 1985-09-23 | Winch with level-wind regulator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000463805A CA1254876A (en) | 1984-09-21 | 1984-09-21 | Winch with level-wind regulator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1254876A true CA1254876A (en) | 1989-05-30 |
Family
ID=4128759
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000463805A Expired CA1254876A (en) | 1984-09-21 | 1984-09-21 | Winch with level-wind regulator |
Country Status (2)
| Country | Link |
|---|---|
| CA (1) | CA1254876A (en) |
| GB (1) | GB2165201B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012013527B4 (en) * | 2012-07-04 | 2017-05-04 | Jenoptik Advanced Systems Gmbh | Cable drum for a capstan winch |
| CN111156376A (en) * | 2020-01-15 | 2020-05-15 | 广州广兴牧业设备集团有限公司 | Wear-resisting system for traction steel wire rope of feeding machine |
-
1984
- 1984-09-21 CA CA000463805A patent/CA1254876A/en not_active Expired
-
1985
- 1985-09-23 GB GB08523420A patent/GB2165201B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| GB8523420D0 (en) | 1985-10-30 |
| GB2165201A (en) | 1986-04-09 |
| GB2165201B (en) | 1987-06-17 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |