WINCH

Abstract: A winch (10) is disclosed which includes a base member (12) adapted for mounting to a support surface, a stationary shaft (14) upstanding from the base member (12) and a drum (16) co-axial with the shaft and including an inner surface portion spaced from the shaft and an outer surface (17) for holding working lines. A first one-way clutch (20) is operative within the space between an upper portion of the drum (16) and an upper portion of the shaft (14) the one-way clutch (20) having an inner race (21) defining a working surface (24), an outer race working surface (26) being defined by an upper inner portion of the drum. A plurality of rollers (28) are positioned between the race surfaces (24, 26) to effect torque transmission in a first direction from the inner race (21) to the drum (16) while the rollers provide antifriction bearing support in the opposite direction. A second one-way clutch (22) is defined between the lower inner portion of the drum (16) and the stationary shaft (14) the outer portion of the shaft defining an inner race clutch working surface (30) and the inner opposed portion of the drum defining an outer race clutch working surface (32). A plurality of rollers (34) are disposed therebetween and arranged to provide clutching engagement between the surface (30, 32) in a direction opposite the working direction of the first clutch means (20) to thereby provide back-check action for rotational positions of the winch (10) as a working line is wound thereabout. The unidirectional clutches (20, 22) are of the hyperboloidal surface-roller type, which engage in one direction and free-wheel in anti-friction rotation in the opposite direction.

Description: WINCH Technical Field The present invention relates to winches for winding and unwinding working lines about an outer surface. Background Art Hand operated winches of the type used for handling working lines on marine craft are generally known in various types. Some of these winches are provided with relatively similar structure and mechanisms and others are somewhat complex. In either case, the objective is to tie a working line about a convenient surface where the line will be kept out of reach and in a convenient compact location for the next use. In general, it is desirable to wind the line about the storage surface as quickly as possible and with the option of changing the ratio of the turns provided manually on the handle relative to the turns of the actual drum on which the lines are wound. For example, in some applications, it is often required to wind a line more quickly in one circumstance than in another, and in some instances, unwinding a line quickly is just as important as the actual winding procedure. In this respect, winches presently available have incorporated numerous complex devices and features which seek to accomplish these ends, with the result that such winches are relatively costly to manufacture and often do not provide a sturdy fault-free structure capable of use for extended periods without breakage or jamming of one part or another. U.S. Patent No. 3,642,253 relates to a sealed silent winch which includes a combination of silent one- way sprag clutches as opposed to the conventional pawl escapements used for braking the winch. In this regard, the sprag clutches include a plurality of relatively irregularly shaped "sprags" which are positioned within a cage so as to be retained for jamming engagement between two working surfaces spaced apart sufficient that rotation of one race relative to the other creates engaging contact which results in torque transmission through the races. U.S. Patent No. 3,618,896 relates to ratchet winches which utilize combinations of gearing and ratchet wheels to effect line winding and back check of the drum. U.S. Patent No. 3,712,431 discloses a torque device for winches also utilizing a combination of sprag - clutches utilizing sprag elements carried by retainers, springs and relatively complicated combinations thereof to effect winding and back stop action. U.S. Patent No. 4,234,166 discloses a winch which utilizes clutch mechanisms capable of engagement and disengagement for winding lines and webbing. U.S. Patent No. 3,817,494 relates to a drum drive which utilizes a fiber drive unit which includes fibrous surfaces movable into and out of drive engagement positions for effecting driving rotation of a drum while providing the capability for disengagement for rotation in the unwinding direction. Lastly, U.S. Patent No. 3,557,925 discloses a one-way clutch mechanism which transmits torque from one hyperboloidal surface to another by way of a plurality of conical rollers jamming between the surfaces. In this clutch, however, the end rollers become engaged with a portion of one of the races, and can produce discontinuities in the clutch action while damaging the race engaged by the rollers as the races rotate. This patent does not contemplate any type of winch utilizing such clutches. In general, it will be appreciated that while such mechanisms represent certain advances in the art, they nevertheless include relatively complex mechanisms and structures to effect winding, unwinding and back- checking of a drum for line winding. Further, adding such structures as gears and related mechanisms to produce certain gear ratios further complicates these winches. Moreover, in particular, it will be appreciated that while sprag clutches are to a certain extent effective winding and free-wheeling devices, they suffer from several disadvantages, most notable of which include sprag- breakage and the requirement for conventional roller or ball bearings to be utilized therewith for providing antifriction bearing support. The breakage problem stems from the fact that the sprag elements consistently engage along their same contact portions and often are discontinuously lodged into torque transmitting engagement. I have invented a winch which is relatively less complex than those of the prior art and provides clutch transmission of torque for line winding utilizing a combination of one-way clutches which provide back-stop action without the need for separate antifriction bearings or complex mechanisms. Summary of the Invention A winch which comprises base member adapted for mounting to a support surface, a stationary shaft upstanding from the base member, a drum co-axial with the shaft and including an inner surface portion spaced from the shaft and an outer surface for holding working lines, first one-way clutch means operative within the space between an upper portion of the drum and an upper portion of the shaft, the one-way clutch means having an inner race defining a working surface, an outer race working surface defined by an upper inner portion of the drum, and roller means positioned between the race surfaces to effect torque transmission in a first direction from the inner race to the drum while the roller means provide _ anti-friction bearing support in the opposite direction, b and second one-way clutch means defined between the lower inner portion of the drum and the stationary shaft, the outer portion of the shaft defining an inner race clutch working surface and the inner opposed portion of the drum defining an outer race clutch working surface, roller 0 means disposed therebetween and arranged to provide clutching engagement between the surfaces in a direction opposite the working direction of the first clutch means to thereby provide back-check action for rotational positions of the winch as a working line is wound 5 thereabout. In a preferred embodiment, a deck winch is disclosed which comprises base member adapted for mounting to a support surface, a stationary shaft upstanding from the base member, a drum co-axial with the shaft and 0 including an inner surface portion spaced from the shaft and an outer surface for holding working lines, first one-way clutch positioned in the space between an upper portion of the drum and an upper portion of the shaft, the one-way clutch having an inner race having means for 5 rotation thereof, the inner race further having an inner race working surface spaced from an outer race working surface defined by a corresponding opposed inner portion of the drum, roller means disposed between the working surfaces of the races, the working surfaces of the races 30 being so configured and the roller means being configured " and oriented to effect clutch engagement between the inner and the outer race when the inner race is rotated in a first direction and relative freewheeling rotation when the inner race is rotated in the opposite direction, the 35 roller means providing antifriction bearing support between the races, such that rotation of the inner race in the first direction causes corresponding rotation of the drum for winding a working line about the outer surface thereof, and second one-way clutch defined between the lower inner portion of the drum and the stationary shaft, the outer portion of the shaft defining a clutch inner race working surface and the inner opposed portion of the drum spaced therefrom defining an outer race clutch working surface, roller means disposed therebetween, the configurations of the working surfaces and relative configuration and orientation of the roller means being such as to effect clutch engagement of the surfaces and the roller means in the direction opposite the direction of clutch engagement of the first mentioned one-way clutch while providing freewheeling antifriction roller support in the opposite direction thereby to effect braking forces between the drum and the stationary shaft to provide back-check action for the drum as the drum is rotated in the first line winding direction. In the deck winch according to the present invention the working surfaces of the inner and outer races of the second one-way clutch are hyperboloidal surfaces through every point on which two straight line generators may be drawn so as to lie wholly in the surfaces. The roller means comprises a plurality of generally elongated rollers disposed between the inner and outer races of the second one-way clutch. Further, means is provided to selectively increase the space between the inner and outer races of the second one-way clutch to thereby effectively eliminate the clutch engagement forces developed therebetween in the working direction of the inner and outer races so as to cause the outer race to freewheel in both directions with respect to the outer race. In the deck winch according to the present invention working surfaces of the inner and outer races of the first one-way clutch are hyperboloidal surfaces through every point on which two straight line generators may be drawn so as to lie wholly in the surfaces. The roller means of the first clutch means comprises a plurality of generally elongated rollers disposed between the inner and outer races of the first one-way clutch means. Further, roller support means is positioned beneath the rollers of the second one-way clutch means and supporting the rollers against the downward force components caused by the jamming action between the clutch race surfaces and the rollers. The deck winch according to the present invention further comprises roller support means positioned above the rollers of the first one-way clutch and supporting the rollers against the downward force components caused by the jamming action between the clutch race surfaces and the rollers. The deck winch according to claim 9 wherein the roller support means positioned below the rollers of the second one-way clutch comprises a ring member positioned for slidable engagement between the rum and the inner shaft ring member. The roller support means positioned beneath the rollers of the first one-way clutch preferably comprises a ring member positioned between the drum and the inner race of the first one-way clutch, but may also be any other means interpositioned between the rollers and the inner race to slidably support the rollers thereon. The ring member positioned below the rollers of the one-way clutch is preferably fabricated of a self-lubricating resiliently compressible material such as NYLATRON brand material. NYLATRON is a highly lubricated material formed of nylon and molybdenum disulphide marketed by Polymer Corporation, Reading, Pennsylvania. Also, other materials contemplated are bearing bronze, polyethylene, polypropylene, even a form of NYLATRON which includes nylon and teflon (for lubricating) . In some instances, nylon has been found to have sufficient resilience, compressibility and lubricity. The support means may be slidable or it may be fixed to a race, provided it provides a sufficiently slidable surface interposed between the rollers and the race. In addition, the support means may be in the form of a NYLATRON (or other) ring member; however, the means interposed between the rollers and the race may also be in the form of NYLATRON roller tips for example, or similar arrangements as disclosed in my continuation-in-part application (being concurrently filed herewith) of my pending application serial No. 016,458, filed February 18, 1987, both of which are incorporated herein by reference. The rollers of the first one-way clutch comprise a plurality of generally elongated rollers of circular cross-sectional configuration and each preferably having arcuately shaped end portions. The NYLATRON ring positioned below the rollers of the second one-way clutch includes in one embodiment a plurality of spaced arcuate cavities configured and dimensioned for nestled reception of the respective end portions of each the rollers of the second one-way clutch to maintain a predetermined spacing of the rollers during operational engagement of the rollers with the clutch working surfaces. The NYLATRON ring positioned below the rollers of the first one-way clutch preferably includes a plurality of spaced arcuate cavities for nestled reception of the respective end portions of each the rollers of the first one-way clutch thereby maintaining a predetermined spacing of the rollers during operational engagement of the rollers with the clutch working surfaces. Further, the inner race of the first one-way clutch comprises means for rotating the inner race to effect working engagement between the rollers of the one-way clutch and the clutch working surfaces. In addition, the means for rotation of the inner race of the first one-way clutch comprises a drive aperture dimensioned and configured for reception of a drive tool for rotation of the inner race. Preferably, the aperture in the inner race is a multi-sided drive aperture having a square or hexagon shaped aperture. In the preferred embodiment of the present invention the inner and outer race surfaces of the second one-way clutch are generally conical hyperboloidal surfaces having their larger diameters at the lower ends thereof and the means for selectively increasing the space between the working surfaces of the second one-way clutch means comprises means for lifting the drum vertically a predetermined dimension to effectively increase the space between the inner and outer races of the second one-way clutch. Further, the means for lifting the drum of the second one-way clutch comprises a cam member positioned between the drum and a lower support surface and rotatable to a vertical position of greater height dimension than the vertical height dimension corresponding to the first mentioned position, the cam member being positioned so as to engage and lift the drum upwardly with respect to the inner race of the second one-way clutch. Also, a locking nut is threadedly engaged with the upper portion of the drum and positioned between the upper portion of the drum and the upper portion of the inner race of the first one¬ way clutch, the locking nut being configured and dimensioned to retain the components of the winch in assembled relation. Brief Description of the Drawings Preferred embodiments of the invention will be described with reference to the drawings wherein: FIG. 1 is a perspective view with parts separated for illustration purposes, of the winch according to my invention; FIG. 2 is a top view of the winch of my invention with a handle shown in phantom lines; FIG. 3 is a cross-sectional view taken along lines 3-3 of FIG. 2 illustrating the assembled components of the winch of FIG. 2 as well as the features for disassembling same; FIG. 4 is a cross-sectional view of an alternate embodiment of the winch which includes a feature which provides selective conversion of the lower one-way clutch to a two-way freewheeling clutch; FIG. 4a is a cross-sectional view taken along lines 4a-4a of FIG. 4 illustrating the feature which selectively converts the lower one-way clutch to a two-way freewheeling clutch, but in the one-way clutch position; FIG 5 is a cross-sectional view of the winch of FIG. 4 with the lower clutch in the two-way freewheeling condition; and FIG. 5a is a cross-sectional view taken along lines 5a-5a illustrating the clutch of FIG. 4 in a two-way freewheeling condition. Detailed Description of the Preferred Embodiments Referring to the drawings, the winch of the present invention is illustrated in perspective view, with parts separated for convenience of illustration. The winch 10 is described as follows. Winch 10 includes stationary base plate 12 having central shaft 14 upstanding from the upper surface as shown. A drum 16 has an outer configuration capable of receiving working lines wound thereabout and is positioned on the base 12 for rotation by a handle 18 shown in phantom lines in the FIGS. The ratchet-free ' combination, drum rotation and back check operation of my winch will now be described. Referring once again to FIG. 1, there is shown two-one-way roller-hyperboloidal surface type clutches 20 upper, and 22 lower, of the type described and claimed in my co-pending application Serial No. 016,458, filed February 18, 1987, entitled "Improvements In Clutches", and my continuation-in-part application filed concurrently herewith, entitled "Improvements In Clutches", both of which are incorporated herein by reference and made a part of this application. These improved clutches are constructed to provide surfaσe-to-roller-to-surface engagement in one direction and freewheeling motion between inner and outer races in the other direction. Thus, a combination of such clutches having a common axis of rotation as shown in FIG.-l is provided. In particular, as described and claimed in my aforementioned pending application, these clutches are provided with inner race and outer race generally conical hyperboloidal surfaces through every point of which respective straight line generators may be drawn. The rollers - which may be cylindrical or conical shaped - are configured and dimensioned such that they assume an angle relative to the straight line generators of the surfaces to effect jamming or grabbing action to provide one-way clutch rotational engagement forces transmitted via the rollers from the inner race to the outer race. Uniquely, these rollers also provide antifriction bearing support between the inner and outer races so as to effect smooth and silent operation. Since the rollers are continuously rotating during operation of the winch, their effective contact surfaces are constantly changing so that excessive wear on any one portion of the rollers does not prevent a breakage problem due to stress concentration, fatigue or the like. In this environment, the upper clutch 20 is arranged to provide surface-to-roller-to-surface engagement in the direction desired to wind a line about the working surface 17 of drum- 16 and antifriction bearing support and freewheeling motion in the opposite direction; roller or ball-type antifriction bearings are not needed. The lower clutch 22 on the other hand is arranged to provide surface-to-roller-to-surface engagement - or in this case, braking - in the direction opposite the direction of line winding in order to maintain any winding input which may have been made to the line. Referring once again to the drawings, it will be seen that clutch 20 is comprised of inner race 21 having as part of the upper portion thereof a drive portion 19 adapted for reception of a suitable drive tool such as a special handle 18 or drive wrench (not shown) . The inner race 21 of clutch 20 has formed thereon a conical hyperboloidal surface 24 - referred to as the clutch inner race working surface - while corresponding opposed outer conical hyperboloidal surface 26 is defined by the upper inner portion of drum 16. The surfaces of upper clutch 20 are oriented with their greater diameters at the lower portion and their smaller diameters at the upper portion. A plurality of thrust transmitting rollers 28 are positioned between the working surfaces. In the case of upper clutch 20 the confronting surfaces 24 and 26 make thrust transmitting contact with the rollers 28 to rotate the drum in the direction in which it is desired to tie a line onto drum 16, while the rollers of the lower clutch 22 are arranged to provide "reverse thrust transmitting contact" - in this case, "braking contact" - in the opposite direction so as to provide back-check action to maintain the position of the drum as the line is tied thereabout. As illustrated, the conical hyperboloidal surfaces of the lower clutch 22 are positioned in the reverse position of those of the upper clutch 20. The fact that the lower clutch 22 freewheels in the direction opposite the direction of line reeling permits the drum to be rotated freely in that direction but the braking action of lower clutch 22 maintains that position so as to prevent the line from unwinding. The rollers 28, which are preferably constructed of a satisfactory bearing steel material, actually provide antifriction bearing support, thus conveniently dispensing with the need for roller or ball bearings to provide smooth, silent rotation of the drum; all without the need for special antifriction bearings, complex ratchets or the like. In addition, the rollers are preferably cylindrical and of circular cross- sectional configuration, but may well be conically shaped, if desired. Their end portions are preferably arcuate as shown. Lower clutch .22 operates on the same structure and principle as upper clutch 20, with inner conical hyperboloidal surface 30, outer conical hyperboloidal surface 34 and "braking" rollers 34 positioned therebetween. In this case, however, it will be seen tha the rollers are angularly oriented opposite the rollers o upper clutch 20 as viewed in the same plane; thus, their rotational direction of jamming - or surface-to-roller- to-surface contact, is opposite that of upper clutch 20. Turning now to the actual structure of the winc as viewed in FIG. 1 in conjunction with FIG. 3, stationar base plate 12 has an annular stepped portion 16 on which is positioned an annular ring 36 - preferably of a self- lubricating material such as NYLATRON - which acts as a slide bearing between stepped portion 16 and rollers 34 and which supports the rollers as they rotate about their own axes and about the axis of the winch. This ring being self-lubricating actually is free to slidably rotate with respect to the outer drum and the stepped portion 16 defined by the base 12 and shaft 14 thereby preventing the inherent downward force component acting on the rollers 34 when loaded from causing the rollers to engage and mar the surface of stepped portion 13. The NYLATRON ring preferably includes a plurality of cup-shaped arcuate indentations - or cut-out portions - as shown in cross- section in FIG. 3, to receive each of the rollers 34 in nestled relation while maintaining appropriate roller-to- roller spacing. Alternatively, where the rollers may have other end configurations - such as flat as opposed to arcuate - the NYLATRON ring may be appropriately configured to support the rollers 34. A NYLATRON ring 40 is positioned atop the rollers 28 of upper clutch 20 to support the rollers against the inherent upward force components created by inter-engagement between the rollers and the confronting surfaces 24. and 26. Similarly, a NYLATRON ring 42 is positioned between upper clutch 20 and lower clutch 22 and acts as a bearing between the central shaft 14 and the drum 16, while supporting the upper rollers 28 and the lower rollers 34; however, since the rollers are oriented at opposite angles and tend to respectively move in directions opposite each other and away from NYLATRON ring 42, no nestling or cradling cup- shaped indentations are required in this ring. Turning further to the drawings, a flange 44 is positioned at the lower portion of the winch about the base 12 and is threadedly secured by threads 46 engaged with corresponding threads provided on the inner part of the drum as shown. A locking collar 48 is positioned atop flange 44 with self-lubricating NYLATRON discs 50 and 52 respectively positioned between locking collar 48 and flange 44 and between locking collar 48 and drum 16 as shown. Flange 44 is fastened to drum 16 by a suitable fastener, preferably set screw 72 shown in FIG. 3 which is inserted and fastened through aperture 54 in locking collar 48. Similarly, locking collar 48 is secured to base plate 12 by press fitted dowel 56. The entire assembly is secured together by lock nut 58 which is threadedly engaged to the upper part of drum 16 between the drum and the upper drive portion of inner race 21 of upper clutch 20 so as to provide pre-selected downward - compressive pre-load forces on the components including upper inner race 21, NYLATRON ring 40, upper rollers 28, NYLATRON ring 42, lower rollers 34, NYLATRON ring 36 and base plate 16. The method of assembly of the lower components of the winch will now be described. Referring to FIGS. 1 and 3 base plate 12 is provided with a radial aperture 60 which opens into aperture 62 large enough to receive dowel 56 during disassembly. Vertical aperture 64 extends upwardly into base plate in a direction perpendicular to aperture 60 and parallel to the axis of the winch. Flang 44 is similarly provided with aperture 66 which aperture in combination with aperture 64 in base plate 12 provides a unique visual alignment feature with which the components are maintained in alignment during assembly as will be described further. Locking collar 43 is provided with a radial aperture 68 for reception of press-fitted locking dowel 56 which extends into aperture 60 of base plate 12 to retain locking collar 48 in the correct position with respect to base plate 12 as shown. Flange 44 also contains threaded aperture 72 intended to be positioned in registry with corresponding threaded aperture 74 provided in the lower part of drum 16 for reception of set screw 76 as shown clearly in FIG. 3. Beginning with base plate 12 as shown in FIG. l, flange 44 is positioned around shaft 14 while aperture 66 is temporarily held in alignment with corresponding aperture 64 in the base plate either by a dowel or a tool such as a screw driver. This step is followed by positioning NYLATRON ring 50 on flange 48 and then positioning locking collar 48 over the NYLATRON ring 50. Dowel 56 is press-fitted into registered openings 68 in locking collar 48 and 60 in base plate 12 to retain those two members in relative position. Thereafter, NYLATRON ring 52 is placed in position atop locking collar 48 and drum 16 is dropped into position and threads 78 are threadedly engaged by matching threads 46 on the flange 44, all while flange 44 is being retained in relative rotational position with base plate 12 by the dowel or other temporary tool inserted into aperture 64 and aligned aperture 66 as shown. It will become readily clear that upon rotating drum 16 such that threads 78 of the drum advance with the corresponding threads of the flange 44, the flange will be lifted up into position as shown to retain the flange 48 in a fixed position. When the drum is finally threadedly engaged into the flange 44, the drum is rotated to the nearest position consistent with sufficient tightening to maintain apertures 72 and 74 visually in alignment. Thereafter, a tool such as a screw driver is inserted into aperture 54 so as to threadedly advance set screw 76 in position to retain the flange 44 in a fixed and locked position with respect to the drum 16. At this point, the dowel or tool which is temporarily securing flange 44 in position over base plate 12 to maintain apertures 64 and 66 in registry is no longer needed and is thus removed. Clearly, it can be seen that the weight of the drum is now being supported equally between rollers 34 and locking collar 48. After completing the aforementioned procedure, NYLATRON ring 42 is dropped into position about shaft 14, followed by positioning of inner hyperboloidal race 21 with rollers 28 temporarily held in position by a suitable heavy lubricating grease and topped by NYLATRON ring 40. After insertion of the inner race 21 in position, the locking ring 58 is threadedly inserted through engagement of threads 80. Disassembly of the winch is provided by following the aforementioned procedure in reverse order. It should be noted that removal of dowel 70 is effected by driving the dowel inwardly until it falls out of its apertures 68 and 60 ultimately to drop out of aperture 62 for retrieval. It can be seen that the winch as described in FIGS. 1 and 3 is contemplated to be driven by a suitable tool such as a standard winch handle 18 having a drive end portion 19 inserted into a correspondingly shaped opening provided in the center of the inner race 21 of upper clutch 20. Such drive may be square shaped or hexagonal or any suitable drive shape as may be desired. Optionally, the winch will function in a first pre¬ selected direction corresponding to the drive direction of upper clutch 20 which transmits rotary motion from handle 18 through drive 19 to inner race 21 of upper clutch 20 and thereby to drum 16 via inner hyperboloidal conical surface 24, outer hyperboloidal conical surface 26 and drive rollers 28 therebetween. As the line is being wound about the outer working surface 17 of drum 16, the rotational position thereby achieved by the drum is maintained by the back-check action of lower clutch 22 which is arranged to have its working - or braking - direction opposite the working direction of upper clutch 20. Thus, as the handle is rotated in full turns or incremental turns as desired, the first direction will be the winding direction and the handle may be freewheeled opposite the working direction while the position of the line wound about the working surface 17 of drum 16 is thus retained. According to this embodiment, unwinding of the line must be accomplished manually because this embodiment of the winch does not provide for reverse freewheeling as will be provided in the embodiment illustrated in FIGS. 4 and 5 and described hereinbelow. Referring now to FIGS.' 4 and 5, there is illustrated an embodiment of the present winch which incorporates a unique feature which facilitates convenient conversion of the winch from a first driving mode as described hereinabove to a mode in which the operational drum may be made to freewheel in two directions, a feature which will facilitate unwinding of a line from the drum in a manner similar to that which is used to wind the line about the drum. In addition, the winch illustrated in FIGS. 4 and 5 includes an alternate drive arrangement from the standard drive arrangement shown in the embodiment of FIG. 3. The drive arrangement shown in FIGS. 4 and 5 includes a fixed square or other rectangular pin provided at the top of central shaft 14 to receive a specific type of handle, the functional aspects which may include dual inner or outer sleeves, the inner sleeve being retained in fixed position by the square drive end of the shaft and the outer sleeve being arranged to rotate about the inner sleeve and having an outer configuration corresponding to a drive opening provided within the inner race of the upper clutch. Referring now to FIGS. 4 and 5, in combination with FIGS. 4a and 5a, respectively, the feature which facilitates the conversion of the winch to a two-way freewheeling winch includes the provision of means to lift the drum 16 and the flange 44 therewith a minor amount - say approximately .5 mil - so as to disengage the engaging surfaces between the rollers 34 and the hyperboloidal surfaces 30 and 32 as illustrated in FIG. 5. Once this disengagement is made, the braking action of the lower clutch is essentially disabled and unwinding of the line positioned about the working surface of the drum 16 can be readily accomplished. It should be noted that this capability is peculiarly facilitated by the working principles of the conical hyperboloidal clutch forming part of the present invention. The actual feature which provides for lifting of the drum 16 will now be described with reference to FIGS. 4 and 5. A handle 82 which includes a crank portion 84 extends through an aperture 86 provided in locking collar 48 and this handle is secured to cam member 88 for transmitting rotational torque to the cam via key 90 provided in a suitable key way in the cam 88 as shown clearly in FIGS. 4, 4a, 5 and 5a. In the first position which is shown in FIG. 4a, the cam 88 is oriented such that the vertical distance "X" between NYLATRON ring 52 and the top surface of base plate 12 is at its minimum. Upon rotation of the crank 84 an amount suitable to rotat cam 88 from the position shown in FIG. 4a to the position shown in FIG. 5a the drum 16 is lifted upwardly by the forces provided by the cam 88 and the NYLATRON ring 52 thus inactivating the braking action between the hyperboloidal surfaces 30 and 32 and the rollers 34 of th roller clutch 22 thereby permitting the drum 16 to freewheel in what is normally the braking direction. Thus, any line wound about the drum may thereby be selectively quickly unwound. Similarly, the crank handle 84 may be used to rotate cam 88 back to the position show in FIG. 4a thus returning the lower clutch 22 to the -_ braking - or line winding - direction. The relative orientation of the crank may be manufactured such that it is in the vertical position during winding or unwinding. This aspect is merely a matter of design choice which may be changed from winch to winch. Referring now to the upper drive end of the winch shown in FIGS. 4 and 5, this winch may include the same square shaped opening shown in embodiment of FIG. 3. However, alternately as shown in the arrangement of FIGS. 4 and 5, the central shaft 14 is arranged to include an extension having a square cross-section and intended for use with a suitable handle which includes a drive mechanism having an outer rotatable sleeve 94 which has an outer drive configuration corresponding to the drive opening of the inner race of upper clutch 20 at the top of the winch. A sleeve 96 is fixed by the square end 92 of shaft 14. A particular type handle which operates in this manner is the subject of a separate application filed by me concurrently herewith, entitled "Apparatus for Developing Variable Rotational Drive Torque", the disclosure of which is hereby incorporated herein and made a part of this application. Such unique handle apparatus provides a multiplicity of torque values and mechanical advantages which advantageously provides a multiplicity of "gear ratios" for the present winch, without the need for actual gears, ratchets or the like. However, it should be clear that it is contemplated within the scope of the present invention to include a multiplicity of drive arrangements at the top end of the winch and such drive arrangements may assume a plurality of shapes and configurations. In all other structural respects the components and the method of assembly and disassembly of the winch shown in FIGS. 4 and 5 are the same as the winch shown in FIG. 3 with the exception that the assembly of the handle 82 and the cam 88 must be accomplished within the assembly procedure preceding the positioning of locking ring 48 atop flange 44. In particular, cam 88 is placed in position within a suitable aperture provided in locking collar 48 prior to positioning the locking collar over the base of the winch. Thereafter, handle 82 is inserted into the generally circular opening 81 of cam 88 and may be arranged to provide a slight press-fit or no press-fit, a matter of selection. Key 90 is thereafter inserted into the suitable keyway by slots provided in both handle 82 and cam 88 which are maintained in registry for reception of the key. The key is preferably press-fit into the key way and may be tapped lightly using a small tool and hammer. Thereafter, the assembly procedure of the components with respect to locking collar 48 will follow the procedure previously described.

Claims: CLAIMS What is claimed is; 1. A winch which comprises: a. base member adapted for mounting to a support surface; b. a stationary shaft upstanding from said base member; c. a drum co-axial with said shaft and including an inner surface portion spaced from said shaft and an outer surface for holding working lines; d. first one-way clutch means operative within the space between an upper portion of said drum and an upper portion of said shaft, said one-way clutch means having an inner race defining a working surface, an outer race working surface defined by an upper inner portion of said drum, and roller means positioned between the race surfaces to effect torque transmission in a first direction from said inner race to said drum while said roller means provide antifriction bearing support in the opposite direction; and second one-way clutch means defined between the lower inner portion of said drum and said stationary shaft, the outer portion of said shaft defining an inner race clutch working surface and the inner opposed portion of said drum defining an outer race clutch working surface, roller means disposed therebetween and arranged to provide clutching engagement between 10 said surfaces in a direction opposite the working direction of said first clutch means to thereby provide back-check action for rotational positions of said winch as a working 15 line is wound thereabout. 2. A deck winch which comprises: a. base member adapted for mounting to a 20 support surface; b. a stationary shaft upstanding from said base member; 25 c. a drum co-axial with said shaft and including an inner surface portion spaced from said shaft and an outer surface for holding working lines; 30 d. first one-way clutch positioned in the space between an upper portion of said drum and an upper portion of said shaft, said one-way clutch having an inner race having means for 35 rotation thereof, said inner race having an inner race working surface spaced from an outer race working surface defined by a corresponding opposed inner portion of said drum, roller means disposed between said working surfaces of said races, the working surfaces of said races being so configured and said roller means being configured t and oriented to 10 effect clutch engagement between said inner and said outer race when said inner race is rotated in a first direction and relative freewheeling rotation when said inner race is 15 rotated in the opposite direction, said roller means providing antifriction bearing support between said races, such that rotation of said inner race in said first 20 direction causes corresponding rotation of said drum for winding a working line about the outer surface thereof; and 25 e. second one-way clutch defined between the lower inner portion of said drum and said stationary shaft, the outer portion of said shaft defining a clutch inner race working surface and 30 the inner opposed portion of said drum spaced therefrom defining an outer race clutch working surface, roller means disposed therebetween, the configurations of said working 35 surfaces and relative configuration and orientation of said roller means being such as to effect clutch engagement of said surfaces and said roller means in the direction opposite the direction of clutch engagement of said first mentioned one-way clutch while providing freewheeling antifriction roller support in the opposite direction thereby to effect braking forces between said drum and said stationary shaft to provide back-check action for said drum as said drum is rotated in said first line winding direction. 3. The deck winch according to claim 2 wherein said working surfaces of said inner and outer races of said second one-way clutch are hyperboloidal surfaces through every point on which two straight line generators may be drawn so as to lie wholly in the surfaces. 4. The deck winch according to claim 3 wherein said roller means comprises a plurality of generally elongated rollers disposed between said inner and outer races of said second one-way clutch. 5. The deck winch according to claim 3 wherein said first one-way clutch comprises means at the interface between at least one end portion of each of said roller means and at least one of said inner and outer races to permit slidable movement therebetween at least in a first direction while supporting the roller means axially thereof. 6. The deck winch according to claim 4 wherein said second one-way clutch comprises means at the interface between at least one end portion of each of said roller means and at least one of said inner and outer races to permit slidable movement therebetween at least in a first direction while supporting the roller means axially thereof. 7. The deck winch according to claim 6 further comprising means to selectively increase the space between said inner and outer races of said second one-way clutch to thereby effectively eliminate the clutch engagement forces developed therebetween in the working direction of the inner and outer races so as to cause said outer race to freewheel in both directions with respect to said inner race. 8. The deck winch according to claim 7 wherein working surfaces of said inner and outer races of said first one-way clutch are hyperboloidal surfaces through every point on which two straight line generators may be drawn so as to lie wholly in the surfaces. 9. The deck winch according to claim 8 wherein said roller means of said first clutch means comprises a plurality of generally elongated rollers disposed between said inner and outer races of said first one-way clutch means. 10. The deck winch according to claim 9 wherein said means at the interface between at least one end portion of each of said rollers of said second one-way clutch comprises roller support means positioned beneath said rollers of said second one-way clutch means and supporting said rollers against the force components caused by the action between said rollers and said clutch race surfaces. 11. The deck winch according to claim 10 _b wherein said means at the interface between at least one end portion of each of said rollers of said first one-way clutch comprises roller support means positioned above said rollers of said first one-way clutch and supporting said rollers against the force components caused by the action between said.rollers and said clutch race surfaces. 0 12. The deck winch according to claim 10 wherein said roller support means positioned beneath said rollers of said second one-way clutch means is fabricated of a compressible resilient material. 5 13. The deck winch according to claim 11 wherein said roller support means positioned above said rollers of said first one-way clutch is fabricated of a compressible resilient material. 0 14. The deck winch according to claim 12 wherein said roller support means positioned beneath said rollers of said second one-way clutch is fabricated of a compressible resilient material. 5 15. The deck winch according to claim 14 wherein said roller support means positioned beneath said rollers of said second one-way clutch comprises a ring member constructed and positioned to permit slidable 30 movement between said rollers and said inner shaft ring member. 16. The deck winch according to claim 15 wherein said roller support means positioned beneath said 35 rollers of said first one-way clutch comprises a ring member constructed and positioned between said drum and said inner race of said first one-way clutch. 17. The deck winch according to claim 16 wherein said ring member positioned beneath said rollers of said second one-way clutch comprises a ring member constructed and positioned between said drum and said first one-way clutch. 18. The deck winch according to claim 17 wherein said roller support means positioned above said rollers of said first one-way clutch comprises a ring member constructed and positioned between said drum and said stationary shaft. 19. The deck winch according to claim 18 wherein said roller support means positioned beneath the rollers of said first one-way clutch comprises a ring member constructed and positioned between said drum and said stationary shaft. 20. The deck winch according to claim 19 wherein said roller support means positioned beneath said rollers of said first one-way clutch comprises a ring member constructed and positioned between said drum and said inner race of said first one-way clutch. 21. The deck winch according to claim 20 wherein said ring member positioned beneath said rollers of said first one-way clutch is fabricated of a self- lubricating material. 22. The deck winch according to claim 21 wherein said ring members positioned above said rollers of said first one-way clutch is fabricated of a self- lubricating material. 23. The deck winch according to claim 22 wherein said ring member positioned beneath said rollers of said second one-way clutch is fabricated of NYLATRON brand material. 24. The deck winch according to claim 23 wherein said ring member positioned above said rollers of said one-way clutch is fabricated of NYLATRON brand material. 25. The deck winch according to claim 24 further comprising a NYLATRON ring positioned between the plurality of rollers of said first and second one-way clutches to maintain the space therebetween. 26. The deck winch according" to claim 25 wherein said rollers of said second one-way clutch comprises a plurality of generally elongated rollers of circular cross-sectional configuration and each having arcuately shaped end portions. 27. The deck winch according to claim 26 wherein said rollers of said first one-way clutch comprises a plurality of generally elongated rollers of circular cross-sectional configuration and each having arcuately shaped end portions. 28. The deck winch according to claim 27 wherein said NYLATRON ring positioned beneath said rollers of said second one-way clutch includes a plurality of spaced arcuate indentations configured and dimensioned for nestled reception of the respective end portions of each said rollers of said second one-way clutch to maintain a predetermined spacing of said rollers during operational engagement of said rollers with said clutch working surfaces. 29. The deck winch according to claim 27 wherein said NYLATRON ring positioned below said rollers of said first one-way clutch includes a plurality of spaced arcuate indentations for nestled reception of the respective end portions of each said rollers of said first one-way clutch thereby maintaining a predetermined spacing of said rollers during operational engagement of said rollers with said clutch working surfaces. 30. The deck winch according to claim 29 wherein said inner race of said first one-way clutch comprises means for rotating said inner race to effect working engagement between said rollers of said one-way clutch and said clutch working surfaces. 31. The deck winch according to claim 30 wherein said means for rotation of said inner race of said first one-way clutch comprises a drive aperture dimensioned and configured for reception of a drive tool for rotation of said inner race. 32. The deck winch according to claim 31 wherein said aperture in said inner race is a multi-sided drive aperture having a square or hexagon .shaped aperture. 33. The deck winch according to claim 32 wherein said inner and outer race surfaces of said second one-way clutch are generally conical hyperboloidal surfaces having their larger diameters at the lower ends thereof and said means for selectively increasing the space between the working surfaces of said ε< ad one-way clutch means comprises means for lifting said drum vertically a predetermined dimension to effectively increase the space between the inner and outer races of said second one-way clutch. 34. The deck winch according to claim 33 wherein said means for lifting said drum of said second one-way clutch comprises a cam member positioned between said drum and a lower support surface and rotatable to a vertical position of greater height dimension than the vertical height dimension corresponding to the first mentioned position, said cam member being positioned so as to engage and lift said drum upwardly with respect to said inner race of said second one-way clutch. 35. The deck winch according to claim 34 further comprising a locking nut threadedly engaged with the upper portion of said drum and positioned between said upper portion of said drum and the upper portion of said inner race of said first one-way clutch, said locking nut being configured and dimensioned to retain the components of said winch in assembled relation. 36. The deck winch according to claim 35 further comprising a locking collar positioned between said base member and said drum and secured to said based member by means of a press-fitted dowel extending through portions thereof. 37. A winch which comprises: a. base member adapted for mounting to a support surface; -31- b. a stationary shaft upstanding from said base member; c. a drum co-axial with said shaft and including an inner surface portion spaced from said shaft and an outer surface for holding working lines; d. a first one-way clutch positioned in the space between an upper portion of 10 said drum and an upper portion of said shaft, said one-way clutch having an inner race having means for rotation thereof, said inner race further having an inner race working 15 surface spaced from an outer race working surface defined by a corresponding opposed inner portion of said drum, roller means disposed between said working surfaces of said 20 races, a plurality of elongated rollers disposed between said working surfaces of said races, the working surfaces of said races being configured as conical hyperboloidal 25 surfaces and said roller means being configured, dimensioned and oriented to effect clutch engagement between said inner and outer races when said inner race is rotated in a first 30 direction and relative freewheeling rotation when said inner race is rotated in the opposite direction, said roller means providing antifriction bearing support between 35 -32- said races, such that rotation of said inner race in said first direction causes corresponding rotation of said drum for winding a working line about the outer surface thereof; and e. a second one-way clutch defined between the lower inner portion of said drum and said stationary shaft, 10 the outer portion of said shaft defining a clutch inner race working surface being a generally conical hyperboloidal surface and the inner opposed portion of said drum spaced 15 therefrom defining an outer race clutch working surface being a generally conical hyperboloidal surface, a plurality of elongated rollers disposed therebetween, the 20 configurations of said working surfaces and relative configuration, dimensions and orientation of said rollers being such as to effect clutch engagement of said surfaces 25 and said roller means in the direction opposite the direction of clutch engagement of said first mentioned one-way clutch while providing freewheeling antifriction 30 roller support in the opposite direction thereby to effect braking forces between said drum and said stationary shaft to provide back- check action for said drum as said 35 -33- drum is rotated in said first line winding direction. 38. A winch which comprises: a. base means for mounting to a support surface; b. an upstanding shaft fixedly mounted on said base; 10 c. a first one-way clutch mounted to said shaft and arranged to provide braking engagement in a first direction and freewheeling rotation 15 in a second direction; d. a drum including an outer surface for * holding working lines and having means in an inner portion thereof 20 communicating with said first one-way clutch; e. means for providing said braking of said one-way clutch to said drum; 25 f. a second one-way clutch positioned within the upper portion so said drum is arranged to provide braking contact in a direction opposite the 30 direction of braking said one-way clutch such that rotation of said drum in said first direction is permitted by the freewheeling direction of said first clutch in 35 -34- rotation opposite the said first direction is permitted by the freewheeling direction of said second clutch; means for converting said first one- . way clutch so as to freewheel in both directions thereby permitting said drum to be rotated in a freewheeling manner in either of both directions. 10 15 20 25 30 35

Inventors: CASTENS RUDOLF RICHARD, CASTENS, RUDOLF, RICHARD
Applicants: ROMOSTAR CORP NV, ROMOSTAR CORPORATION N.V.
Application year: 1988
Main classification: B66D1
IPC codes: B66D1