US3782319A

US3782319A - Apparatus for launching, towing and recovering a submersible body from a vessel

Info

Publication number: US3782319A
Application number: US00327003A
Authority: US
Inventors: N Hale
Original assignee: Fathom Oceanology Ltd
Current assignee: Fathom Oceanology Ltd
Priority date: 1972-02-29
Filing date: 1973-01-26
Publication date: 1974-01-01
Anticipated expiration: 1991-01-01
Also published as: JPS4898588A; DE2309546A1; GB1427350A; SU559635A3; IL41555A; IL46584A; FR2174147A1; IL41555A0; FR2174147B1; AU5248973A; CA978427A; GB1427349A

Abstract

Apparatus for launching, towing and recovering a submersible and towable body from a vessel includes a saddle, a winch and cable spooling and tension apparatus. The saddle includes a roller box which is rotatable about the axis of the tow sheave to maintain constant pressure against the cable during towing. A skewable Aframe for lowering the saddle near the water surface includes a transom arm which is pivotally mounted to the transom and to the tow sheave. The winch may be a multi-drum assembly, where the drums are co-axially mounted; and the drums are rotatably mounted in peripheral bearings at each end, which are mounted in the ends of the winch enclosure. The winch enclosure has a cover plate with a transverse slot to permit reeling and unreeling of cable from a drum. A latch mechanism provides for positive locking of a drum for rotation or non-rotation, depending on whether it or another drum is the one on which cable is being reeled or unreeled. The drums of a multi-drum assembly also have a transverse slot formed in them; and the lips of each slot are profiled to turn inwardly with a smaller apparent radius of curvature than the nominal radius of the drum.

Description

lUnite b 'ttes atent [1 1 Male [111 3,7fi2fiw [451 Jan, 1, 1974 APPARATUS FOR LAUNCHENG, TOWING Al lll) REQQVERENG A SlUBii/HERSHBLE BODY FROM A VESSEL [75] inventor: Neville 11. Hole, Mississauga,

Ontario, Canada [73] Assignee: Fathom Oceanology Limited, Port Credit, Ontario, Canada {22] Filed: Jan. 26, 1973 [2]] Appl. No; 327,003

{30] Foreign Application Priority Data Frimary Examiner-George E. A. Halvosa Assistant Examiner-5her1nan l). Basinger Attorney-Douglas S. Johnson 5 7] ABSTRAT Apparatus for launching, towing and recovering a submersible and towable body from a vessel includes a saddle, a winch and cable spooling and tension apparatus. The saddle includes a roller box which is rotatable about the axis of the tow sheave to maintain constant pressure against the cable during towing. A skewable A-frame for lowering the saddle near the water surface includes a transom arm which is pivotally mounted to the. transom and to the tow sheave. The winch may be a multi-drum assembly, where the drums are co-axially mounted; and the drums are rotatably mounted in peripheral bearings at each end, which are mounted in the ends of the winch enclosure. The winch enclosure has a cover plate with a transverse slot to permit reeling and unreeling of cable from a drum. A latch mechanism provides for positive locking of a drum for rotation or non-rotation, depending on whether it or another drum is the one on which cable is being reeled or unreeled. The drums of a multi-drum assembly also have a transverse slot formed in them; and the lips of each slot are profiled to turn inwardly with a smaller apparent radius of curvature than the nominal radius of the drum.

12 Claims, 21 Drawing Figures PATENTEUJANY m 3,782,319

' sum 01 or 10 FIG. 1

2 12 I02 I w PATENTEDJAN 119M 3.782.319

SHEET 08 0F 10.

' PATENTEUJAN H 3,782,319

' sum as nr 10 PATENTEDJAN' H 4 v sum .10 or 10 AIR lCUOLElD MIQIROWAVIE COOKTNG OVEN AND DOOR BACKGROUND OF THE TNVENTION This invention relates to a cooking apparatus using electricity, gas, hot blast and the like as the heat source thereof, and more particularly to an improved cooking apparatus in which the cooling unit is provided to maintain the whole of the apparatus at a comparatively low temperature of safety.

The cooking apparatus, in general, use electricity, gas, hot blast and so forth as the energy source thereof. These energies are supplied to the interior of the oven compartment, wherein the foodstuff and the like absorb these energies and thereby the foodstuff is cooked. Since the oven walls and door walls generally consist of metal having good heat conductivity, these walls are heated at a considerably high temperature due to the heat from the energy source or the foodstuff when cooking is is progress. Therefore, in order to secure safety in entry and withdrawal of the foodstuff from the oven compartment, the handle-attached door as well as the oven walls must be kept at a relatively low temperature.

In conventional cooking apparatus, although the cooling unit for the oven walls is provided by establishing a passage for circulation of an air stream between the oven walls and the cabinet enclosing the oven walls, the cooling of the door is scarcely considered for various reasons. Examples of the cooling unit are disclosed in US. Pat. Nos. 3,081,392 and 3,339,054. The effective cooling of the door is essential for domestic use. In case of installing the cooling unit in or on the door which very often is moved to an open or a closed position, the door construction becomes complicated and much more expensive than previous designs and further is inconvenient for the opening and closing of the door. in the prior art the cooling of the door is attained by naturally cooling or filling the interior of the door with a heat isolator and accordingly the cooling power for the door is poor and the door will be dangerously heated to a considerably high temperature due to long, continuous use. In case of microwave oven wherein the foodstuff within the oven compartment is cooked by dielectric heating alone, metallic oven walls and door walls are heated a little due to the heat from the foodstuff and the like, but are not heated to such a degree that the operator might feel the heat around the door, and thus there is no particular necessity of the door cooling unit. On the contrary, in case of another microwave oven wherein a register type heater or a source of hot blast is provided to produce browning or to speed up the cooking, the radiant heat from the heater, hot air and fumes cause the oven walls and the door walls to be overheated. Of course, where such overheating becomes excessive, it causes damage to the operator in entering and withdrawing of the foodstuff into the oven compartment.

During the cooking process oil or the other exhalation from the foodstuff get scorched and stuck to the inner walls of the oven compartment and the door. In the case where the inner walls are overheated it is difiicult to remove a stain on the inner walls therefrom. However, in the case where the wall surface is properly cooled at a low temperature a stain on the inner walls could be easily removed by merely wiping off with a piece of cloth after the cooling process.

OBJECTS AND SUMMARY OF THE lNVENTION Accordingly, the primary object of this invention is to provide an improved cooking apparatus wherein a forced-air cooling unit is adopted to cool effectively the interior of the door.

Another object of this invention is to provide an improved cooling apparatus which is provided with a cooling unit for making an air stream passing over the interior of the door circulating along the outer surface of the oven compartment thereby cooling the interior of the door and the exterior of the oven compartment.

Still another objct of this invention is to provide an improved cooling apparatus having a simple blower unit for simultaneously exhausting an air stream for cooling the door and an air stream for the interior of the oven compartment.

A further object of this invention is to provide an improved cooking apparatus having an effective cooling unit suitable for microwave oven wherein a resistor type heater or a source of hot blast is installed.

In summary, this invention refers primarily to im proved cooling apparatus which comprises an enclosure having an access opening therein to receive an article or other foodstuff to be heated, at door fitted to said enclosure to freely open and close said access opening and means for cooling the interior of said door. A blower means for effectively cooling the door is designed to aspirate air from the surrounding ambience and to exhaust air passing over the interior of the door to the surrounding ambience. The door is provided with an outer wall having a plurality of apertures to permit the stream of air to be introduced into the interior of the door and with inner wall having another aperture to permit the stream of 'air to escape from the interior of the door. In a preferred example, a microwave cooking apparatus comprises a metallic oven having an access opening therein to receive foodstufi to be cooked, a metallic door fitted to said oven to freely open and close said access opening, means for supplying high frequency electromagnetic waves to the interior of said oven, browning means for surface browning of foodstuff and cooling means for sending air to the interior of said door and the exterior of said oven thereby preventing the temperature rise of said door and said oven due to the heat from said browning means.

Further details. will be apparent from the following explanation of examples of embodiments of this invention with reference to the accompanying drawings.

BRIEF DESCRIPTTON OF THE DRAWINGS FIG. 1 is a sectional view in vertical section showing an oven structure of this invention.

FIG. 2 is a sectional view in vertical section showing another embodiment of this invention.

FIG. 3 is a sectional view in horizontal section showing still another embodiment.

DESCRlPTlON OF THE PREFERRED EMBODIMENTS Referring now to the drawings, in EEG. it, it will be seen that reference character l indicates generally a cooking apparatus of the type disclosed in the aforementioned summary. The cooking apparatus li contains a metallic enclosure or oven compartment indicated by the numeral 2. The oven compartment 2 may comprise a rectangular chamber having a top wall, a bottom wall,

rigidity is thereby achieved in a minimum of athwartships space and with a lower weight. Also, of course, the frame enclosure provides protection of the stowed cable against ice build-up; and because the cable is stowed under tension, considerably less hazard due to cable breakage is afforded for personnel working near the winch.

Where a considerable length of cable is to be stowed by the winch for example, in excess of 1,000 feet the winch construction may comprise two or more drums which are coaxially mounted. The drums are arranged with a transverse slot in the surface of each drum except the innermost one, so that cable may be reeled and unreeled from the multiple drum assembly; with the cable being unreeled serially from the outermost to the inner most drum and reeled serially from the innermost to the outer most drum. However, to maintain alignment of the transverse slots in each of the drums which is outwards of the drum on which cable is being reeled or unreeled, it is necessary to latch those outward drums for nonrotation. Also, because only the innermost drum is driven, it is necessary to latch the innermost drum and any other drums having cable reeled upon them with the drum upon which cable is being reeled at any one time for rotation so as to be driven by the winch drive means. Still further, it is desirable to provide latch means for automatically latching or unlatching adjacent ones of the drums as cable is reeled onto or off those drums without having to stop the outboard or inboard (i.e. unreeling or reeling) movement of the cable relative to the winch. Automatic latching means are therefore provided by this invention which meet the above requirements with respect to non-stop reeling in a multidrum winch.

Because the cable is wound under tension, and because in most circumstances the cable may be faired, it is necessary to provide a multidrum winch assembly wherein the clearance between drums is sufficient to permit stowage of cable on a drum having a transverse slot without interference of the cable on that drum with the cable which is stowed on the drum immediately inwards thereof. Also, it is desirable to reduce the radial loads in the material of the drum to zero load at the edges of the transverse slots. This invention therefore provides a drum construction wherein the lips formed on the transverse edges of each transverse slot are curved inwardly towards the interior of the drum with an apparent radius of curvature being less than the nominal radius of that respective drum. By so doing, a slotted drum construction for a multidrum assembly can be provided having a strength comparable to a conventional, unslotted drum; and therefore the multidrum winch construction is capable of reeling and unreeling and stowing cable which is in tension.

It is desirable when working with a faired cable to provide a slotted drum surface to accommodate that cable. This invention contemplates the provision of a slotted or grooved drum section by the application to the surface of the material from which the drum is formed of an outer layer of relatively flexible material which has a cross-section so as to form the desired grooves at the outer surface of the drum.

This invention also contemplates the provision of a roller box assembly which forms part of the launch and recovery saddle for the submersible and towable body and which can be accommodated to saddles of the noninverting type. In the usual case, the present invention contemplates an inverting saddle for the most effective and economical structure for launch and recovery of the submersible and towable body at the air/water interface. However, other structures also exist whereby a saddle is rigidly fixed with respect to the horizontal at least as defined by the deck of the vessel and where the saddle is moved to the air/water interface by means of a pantographic assembly. However, it would be desirable to tow the body from a tow sheave which is intimately associated with the recovery saddle, and also to provide means for maintaining a constant pressure against the nose of a faired cable as it passes from the tow sheave to the towed body as it is underwater. This is especially true when the cable is faired so that the body tends to be towed in a position which is very nearly beneath the vessel; and so that the cable pierces the air/water interface (the water surface) in a nearly vertical orientation. Still further, however, is the requirement that a roller box be provided which not only has a nose roller but which has side rollers, one on either side of the cable, and that the roller box be based so as to maintain a position relative to the cable as it passes through the roller box so that the axes of the side rollers are substantially perpendicular to the axis of the cable. This is especially important when towoff occurs as the vessel turns or rolls, so as to preclude a tendency of the cable to corkscrew. It is also important, during towoff, that the roller box be adapted to absorb sideways loading as the side rollers make contact with the cable.

DESCRIPTION OF THE PRIOR ART The above discussion has related particularly to certain of the desiderata which surround the present invention and various aspects thereof. These desiderata and the objects of the invention annunciated hereafter may be more clearly appreciated when considered in view of the prior art, of which the most relevent prior art is believed to include U.S. Pat. No. 2,780,196 issued Feb. 5, 1957 to Jareckie for Hoist Boom Towing Connection; Hale et al U.S. Pat. No. 3,604,387, issued Sept. I4, 1971, for Means for Launching, Towing and Recovering an Oceanographic Towed Body in a Seaway; and Hale U.S. Pat. No. 3,576,295, issued Apr. 27, 1971 for Means for Stowing Crush-sensative Cable Configurations. The latter two patents are assigned to a common assignee with the present invention.

The Jarackie patent teaches an earlier launch and recovery apparatus which includes a pantographic movement to swing the towed body aboardships from the air/water interface. Such apparatus is subject to very high transverse loads, and is such that it is not possible to maintain constant cable length while the body is secured against the saddle.

The Hale patent relating to the means for storinng crush-sensative cable configurations teaches a winch construction which may be single or multidrum. However, the supporting means for the drum construction is heavy and considerably wider than the width of drum upon which cable may be wound. Also, the latching means between drums are such that reeling or unreeling operation must be stopped by stopping rotation of the driven drum.

The Hale et al patent teaches an earlier apparatus for launching, towing and recovering a towed body; but that patent teaches the fundamental principle of an inverting saddle. However, the apparatus taught in the earlier I-Iale et al patent has no provision for moving the saddle downwards to the air-water interface except by inverting it around the axis of rotation of the tow sheave, and therefore the apparatus is not useful in vessels having high decks. The I-lale et al patent also teaches the provision of free lateral movement for a spooling sheave so as to overcome fleet angle problems; and a spring biased saddle which tended always to float upwards so as to maintain pressure of a nose roller against the cable during towing operation, particularly so as to preclude the possibility of the cable escaping from the saddle. The present invention, therefore, provides improvements to the earlier l-lale et al I invention in those matters.

BRIEF SUMMARY OF THE INVENTION An object of this invention is to provide anapparatus for launching, towing and recovering a submersible and towable body from a vessel, including improved means whereby a deck frame upon which a winch, towing sheave and launching and recovery saddle are mounted may be tilted on a transom arm means which forms one leg of a skewable A-frame; so that by tilting the deck frame and moving the tow sheave and saddle close to the air/water interface, the length of cable between the winch and the body does not change until it is desired to move the body through the air water interface. A compact apparatus for launching, towing and recovery of a submersible body is therefore provided for installation on a vessel.

Another object of this invention is to provide a cable spooling assembly for use in association with a winch upon which cable which is in tension may be reeled and unreeled, and stowed.

A further object of this invention is to provide a winch construction comprising one or more drums upon which cable may be reeled and unreeled the second and subsequent drums being mounted coaxially with the first drum in a multidrum assembly and where the drum means is supported by a frame including a wrap-around enclosure plate between the ends in which the drum means is rotatably mounted, and without massive external support or stress-relieving structures.

Yet a further object of this invention is to provide a latching assembly for latching any two adjacent drums in a multidrum winch assembly where the drums are coaxially mounted, which latching assembly is automatically operative without stopping the reeling or unreeling operation of the winch and which latches a given drum for rotation or non-rotation as required, depending on whether that drum or the next adjacent drum is the one from which the cable is being reeled or unreeled.

A still further object of this invention is to provide a drum construction for a multi-drum winch assembly wherein all the drums except the innermost have a transverse slot formed therein, and where the lips at the edges of each transverse slot are formed so to provide stress relief in the material of the drum when the drum is loaded with cable which is in tension. Also, a drum construction is provided whereby the outer surface of each drum has grooves formed thereon to accommodate a cable which is to be wound on that drum, and where the grooved surface is accomplished by securing an outer layer of relatively flexible material having an appropriately formed cross-section to the surface of the drum.

Yet another object of this invention is to provide a roller box for use in association with the recovery and stowage saddle for a submersible and towable body, where the roller box is adapted to maintain a specified attitude with respect to a cable passing therethrough as the body is being towed; and where the roller box may be mounted independently of the saddle, if required.

BRIEF DESCRIPTION OF THE DRAWINGS These and other objects and features of this invention are more clearly discussed hereafter, in association with the accompanying drawings, in which;

FIG. I is a general perspective view of a preferred embodiment of the apparatus according to this invention.

FIG. 2. is a side elevation of apparatus such as that shown in FIG. ll, showing the towed body in the stowage position.

FIG. 3 is similar to FIG. 2, and shows the apparatus in an extended position for launch and recovery of the towed body.

FIG. 4 is similar to FIGS. 2 and 3 and shows the apparatus during a towing operation.

FIG. 5 is a side elevation of an alternate embodiment of apparatus according to this invention, when the apparatus is in its inboard position.

FIG. 6 is a view similar to FIG. 5 showing the apparatus of FIG. 5 in the extended, outboard position for launch and recovery of a towed body.

FIG. 7 is a perspective view showing a preferred embodiment of a cable spooling assembly according to this invention, and including cable tension stabilizer means.

FIG. 8 is a diagrammatic view showing the relationship between the cable spooling assembly of FIG. 7 and a winch drum.

FIG. 9 is a perspective view of an alternate cable spooling assembly and cable tension stabilizer.

FIG. III is a diagrarnatic view showing the relationship between the cable spooling assembly of FIG. F and a winch drum.

FIG. Ill is a pserspective view showing drive means for driving the cable spooling assembly of FIG. 9.

FIG. 12 is a perspective, partially fragmented view of a multi-drum winch assembly and its frame.

FIG. 13 isa partial cross section along the lines I3 13 of FIG. I2.

FIGS. MA to MG are diagrammatic, progressive representations illustrating the operation of the latching mechanism according to this invention. FIG. I5 is a partial view showing a detail of the latching mechamsm.

FIG. 16 is a further partial view showing another detail of the latch mechanism.

FIG. 17 is a diagrammatic cross-sectional view of a double drum winch as contemplated by this invention.

FIG. Id is a partial cross-sectional view showing a typical assembly at a drum surface.

FIG. 19 is a perspective view of a saddle and roller box assembly according to this invention, together with its associated bias assembly.

FIG. 20 is a diagrammatic view showing the saddle of FIG. I9, together with a towed body and the cable, in the stowage position.

FIG. 21 is a perspective view of an alternative saddle assembly, where the roller box is biased independently of the saddle.

DESCRIPTION OF THE PREFERRED EMBODIMENTS There follows hereinafter a description of several em bodiments of apparatus as contemplated by this invention. In particular, the following discussion relates to a preferred embodiment and an alternative embodiment of apparatus contemplated by this invention, which in each case embodies the principles defined herein but which may vary as to detail of the integers and mechanical components. Discussion is made of certain particular aspects of the present invention, including altemative arrangements for a transom arm, alternative arrangements for a cable spooling assembly, an enclosed multi-drum winch, a latching mechanism for multidrum winch, the drum and surface construction and configurations of multi-drum winches, and alternative arrangements for a roller box and saddle assembly. Whenever appropriate, and for the sake of continuity and clarity of meaning, like reference numerals are used in various figures of the drawings to refer to the same integer.

As noted above, it is a major consideration of the present invention to provide an apparatus whereby a towable and submersible body may be launched, towed and recovered from the vessel while the vessel is moving. The apparatus discussed herein is such as to withstand heavy stock loading on the cable or on the apparatus itself, including sideways, or athwartships loading on the winch or the saddle and/or roller box; so as to take into account military requirements as well as the practical, physical requirements of high speed towing in heavy seas. Also, as noted, when a submersiable and towable body is to be towed in the water, it is preferable to physically force the body through the air/water interface for initial submersion while the body floods; because the body may have negative buoyancy when dry, and so as to preclude the possibility of snap loading the tow cable. When the body is being towed, especially with the faired cable, it may be very nearly beneath the vessel. It is desirable to provide an apparatus which maintains cable tension and is able to accommodate movement of the vessel as it rolls or pitches.

FIG. I shows a preferred embodiment of the apparatus as contemplated by this invention; and includes a submersible and towable body W which is intended to be towed with a faired cable I02. The cable M2 is stowed in winch assembly 108, and is reeled and unreeled therefrom. A spooling assembly and cable tension shock absorbers is indicated generally at 1106. A pivoting saddle assembly is indicated at MM; and the saddle assembly i ll t, cable spooling assembly 106 and winch assembly 108 are all mounted on a deck frame indicated generally at 1MB.

Referring to FIGS. 2, 3 and t, along with FIG. I, it will be seen how the towable and submersible body 100 is moved from its stowage position as indicated in FIGS. I and 2 to the recovery and launch position indicated in FIG. 3. The towing position is indicated in FIG. 4. In the apparatus of FIGS. 1 to 4, when the towed body 100 is in its stowage position as in FIGS. 1 and 2, the entire weight of that apparatus is transferred to the vessel at three points per side. Those three points are indicated at 204), 2M and 204. It will be noted that the point indicated at 200 is at the lower end of a transom arm 206, and each transom arm 2% is pivotally attached to the vessel at is respective point 200. Suitable cross bracing 216 may be placed between the transom arms 206. The load transfer point 202 may conveniently comprise a roller assembly which is secured to the mounting deck 219 of the vessel. The roller assembly 2G2 is adapted to engage with track assembly 210 which forms part of the deck frame 110. The load pickup point 204 is also secured to the deck 219 and it is adapted to support the forward end (relative to the vessel) of the deck frame 110.

A pair of hydraulic cylinders 212 may conveniently be attached to the deck frame 110, one on either side thereof, so that the ends of the hydraulic cylinders at 214 are pivotally attached near the load pickup mint 202.

The saddle assembly 104 comprises, interalia, an inverting saddle I12 and a rotatable towing sheave 114. The axis of rotation of the saddle I12 and sheave 114 is indicated generally at 218. I

When it is desired to launch the body 100, the h draulic cylinders 212 are extended as indicated in FIG. 3. It will be noted that the entire deck frame is moved backwardly and downwardly with respect to the vessel, and particularly that a transom arm 206 which is pivotally attached to the transom 208 at point 200 is pivoted backwardly and downwardly. It will also be noted that the entire weight of the apparatus with the body 1100 still in its stowage position as shown in full lines in FIG. 3 is picked up and transferred to the vessel at

points

200 and 202; and therefore that the transom arms 206 and the deck frame 110 form a skewable A- frame having its apex at the axis of rotation 218. It will also be noted that the length of cable from the winch 108 to the outer end of the cable where it is secured to body lltltl is unchanged as the skewable A frame is skewed and the axis of rotation 218 of the saddle is brought close to the waters surface. By releasing a suitable brake assembly on the winch 103, the saddle 112 is permitted to invert from the stowage position to the position indicated in ghost lines in FIG. 3, because a certain amount of cable is permitted to unreel from the winch 108. However, only sufficient cable to permit the inverting of the saddle is first unreeled from winch 108, as the body pierces the air/water interface and is securely held in its saddle 112 below the surface of the water for flooding period. Further cable is then permitted to be unreeled from the winch, and the body begins to sink and tow in a submerged condition. When the body is sufficiently below the surface, the hydraulic cylinders 212 are retracted, and the deck frame 110 and transom arms 2% assume their original position, but with the body being towed as indicated in FIG. 4. Thus, the skewable A frame which is formed by the deck frame and the transom arm pivoted to the transom of the vessle is such as to permit controlled launch of the submersible and towable body. The recovery operation is, of course, essentially the reverse of the launch operation discussed above. The skewable A-frame has one foot being at the pivot point 200 for the transom arm, and the other foot being at the point 202 where load from the apparatus is transferred to the vessel above the pivot and load transfer point 200. The apex of the skewable A-frame is defined at the axis of rotation of the sheave I114.

In the usual circumstance, a pair of transome arms 206 are pivotally mounted to the transom 208. As

noted, the upper ends of the transom arms are adopted to bearingly support the sheave 1114. The points 299 at which the transom arms 296 mount to transom 299 of the vessel are, of course, below the winch 1199.

An alternative transom arm arrangement is indicated in FlGS. 5 and 6. In this embodiment, there is at least one transom arm 999, and usually a pair of transom arms which are pivotally mounted at their lower ends 996 to the transom 929. The upper ends of the transom arms 999 are adapted to bearingly support a sheave 922 which is rotatably mounted with its axis of rotation indicated at 999. Once again, the sheave 922 is physically situated lengthwise along the cable 924 which is reeled and unreeled from winch 926. [in this embodiment, winch 926 is shown as being essentially open and having side frame members 929 supporting it.]

At least one hydraulic ram or cylinder 994 is pivotally mounted to the deck of the vessel at 914, and is also pivotally mounted at its other end 9l6-to a tilt arm 992 which supports the entire assembly including winch 926 and side supports 929 from its upper end at 9112. The tilt arm 992 is pivotally mounted to the deck of the vessel at 9119.

When the apparatus of FIGS. 5 and 6 is to be tilted so as to swing the transom arm 999 backwardly and downwardly with respect to the vessel to bring sheave 922 and the saddle 939 into close proximity with the air/water interface, the hydraulic ram 994 is actuated and the tilt arm 992 is driven upwardly and backwardly from the position shown in FIG. 5 to the position shown in FIG. 6. Of course, the transom arm drives backwardly and downwardly, as shown, and a skewable A- frame is formed between the lower pivotal point 996 of transom arm 999, the axis 999(about which the upper end of transom arm 999 and sheave 922 are rotatable), and the stop 9119 against which the deck frame 932 is driven by the motion of tilt arm 992 and through which point load is transferred from the deck frame 932 including winch 926 etc. to the vessel.

The towing position of the apparatus of FIGS. 5 and 6, is of course, as indicated in FIG. 5 with the transom arm 999 swung upwardly to its original, stowage position.

FTG. '7 shows a cable spooling assembly and a cable tension stabilizer assembly which are generally indicated at 196 in F933. 1 to 4. lit will be noted in FIGS. 11 to 4 that cable 1192 is reeled forward from the top of the winch 1199 past the cable spooling assembly 196 and thence rearwardly to the sheave 11114. The assembly 196 includes a beam or first arm 499 which is rotatably mounted in a pair of bearings 492. Bearings 492 are supported in housings 429 which are attached to the deck frame 119. The beam 499 essentially comprises a box section so that the faired cable 192 can move freely along the beam, substantially along the longitudinal axis thereof indicated at 426. A second arm or pair of arms 494 is rotatably mounted at 496 to the first arm 499. Sheaves 499 and 4119 are bearingly mounted in the arms 494 at 439 respectively. The axis of rotation 434 of the rotatable mounting of arm 494 to arm 499 is substantially perpendicular to the axis of rotation 426 of arm 499 in bearings 492. it will be further noted, especially with reference to FIGS. l to 4, that the direction of the axis of rotation 434 is substantially parallel to the axis of the winch 1199.

With reference to FIGS. '7 and 9 together, where FIG. 9 shows the relationship of sheaves 499 and 4T9 to a winch diagamatically indicated at 429, it will be noted that the upper cable reach 422 which extends to the winch 429 from the upper sheave 419 is substantially parallel to the lower cable reach 424. Also, it is noted that the upper reach 422 is substantially at the same height as the top of the winch. The cable 192 is under tension, as indicated by arrows 4116 and 419 on the lower and

upper reaches

424 and 422 respectively. In this embodiment, the arm 499 is free to rotate in its bearing 492, and because the cable is in tension, the arm will rotate so that the upper cable reach 422 may describe an are as indicated at 436 in FIG. 9, depending upon where the upper cable reach 422 is reeling or unreeling from the winch 199. Thus, the arm 494 pivots from side to side with arm 499 so as to achieve the shortest cable-run distance from the winch to the towoff sheave with the cable tension, and thereby reducing the fleet angle of spooling from the drum 429 of the winch 1199 to the upper sheave 4119 to substantially zero fleet angle. Because the lower cable reach 424 is sub stantially coaxial with the axis of rotation 426 of the arm 499, there is no fleet angle between the lower sheave 499 and the tow-sheave.

Another feature of the apparatus illustrated in Fit 7 is that it includes a cable tension stabilizer which comprises a pair of shock absorbers which, in this case, are hydraulic cylinders 4112 The hydraulic cylinders 4112 are pressurized from an oil/gas accumulator 4114, and are mounted between the arm 494 and 499 Thus, the arm 494 is biased so as to resist pivoting motion about its rotational axis 434 When a transient load increase occurs in the cable 192, thereby increasing the cable tension as shown at 426 and 4H9, a torque is created by the cable 1192 on the arm 494 about axis 434, and acts against the shock absorber 4112 so as to damp out the transient load. Such loads may occur because of the vessels movement in rough water during towing. NOS. 2 and 4 show the upper sheave rotated backwardly at position 419A, in ghost lines; and in normal operating conditions, the position of the sheave 4119 may be somewhat as indicated in F168. 2 and 4. 0f course, arm 494 and sheave 499 are also swung forwardly or to the right as indicated in FIG. 7 and the cylinders 412 are extended or partially extended under the influence of pressure from the accumulator 4114. Other shock absorber means may be provided, acting forwardly with respect to the fore-andaft direction of the vessel against the arm 494.

An alternative cable spooling assembly and shock absorber assembly is shown in NOS. 9, t9, and ii. That assembly is very similar to the cable spooler assembly indicated together with the other apparatus shown in F163. 5 and 6; and it will be noted that a single spooling sheave 964 is a feature of this embodiment. A longitudinal horizontal arm 999 is pivotally mounted between two frame mounted bearing

plates

952 and 954. A pair of arms 956 and 959 are commonly mounted on rotational axis 969 which is near the end of arm 959 and substantially perpendicular thereto. The axis 969 is substantially parallel to the axis of winch 926 of P165. 5 and 6, and also to axis 926 of sheave 946 which is bearingly and rotationally mounted at the upper end of arms 956 and 959. [it should be noted that the apparatus of FIG. 9 is turned endto-end with respect to the way it is to be seen in FlGS. 6 and 6.]

Qnce again, cable T92 is wrapped around the sheave 964 and passes from the winch 926 to the towing sheave 922 of FlGS. 5 and 6. A cable stabilizer comprises a pair of shock absorbers sich as

hydraulic cylinders

966 and 968 which connect the arms 056 and 958 respectively to the arm hall). Hydraulic cylinders 966 and ass are connected at their lower ends to the arm 50 through a cross-shaft 770. The

hydraulic cylinders

966 and 968 are pressurized by a suitable gas/oil accumulator and act to damp out transient cable loads in the cable hi2 substantially in the same manner as described above with respect to the cable tension stabilizer means shown in FIG. 7.

The spooler sheave 9.15 is usually considerably smaller than a winch drum such as that which is indicated diagramatically in PEG. it at 972. It therefore becomes necessary to powerdrive the spooling sheave 96d athwartships of the vessel so that the upper cable reach 984 from the sheave to the winch drum 972 falls substantially into longitudinal alignment with the point on the winch drum from which the cable is reeling. One manner by which the spooling sheave 9M4 may be driven athwartships is shown in FIG. 17, including a gear reducing box 974 which has a drive input 976 coming rom the winch drum as the drum is rotating for reeling or unreeling of cable therefrom. A rotary output of the gear reducer box 947 takes the form of a crank arm upon which a cam follower 9380 is fitted. The cam follower 98b is engaged with a cam 982 which is so profiled as to cause the spooler sheave 964 and the arms 956, ass, and 95th together with the shock absorber cable tension stabilizer assembly to pivot about an axis 936 which is substantially longitudinal of the arm The rate of drive and the camming arrangement is such as to drive the spooling sheave 964 in increments of one pitch of the cable which is reeled on the winch drum J72 per turn of that drum.

FIGS. 12 and 13 shown more detail as to the construction of the winch assembly 108. The winch construction includes a substantially cylindrical enclosure designated generally at 506}, which in turn comprises a pair of ends noted generally at 5&2, which ends are joined by an enclosure plate 55% A transverse slot which is defined at its transverse edges at SW and 512 is formed in the enclosure plate 508, and is formed from one end 502 of the frame 50-0 to the outer end 502. The faired tow cable W2 may be reeled or unreeled through the transverse slot onto one or a plurality of drums which may be (to-axially mounted within the frame Still, as discussed hereafter.

A drum assembly is mounted within the frame 500 on axis 5%. The innermost drum in a multi-drum assembly is driven at a sprocket 522 which is rigidly secured to the drum by a drive transfer means such as chain 528 which in turn is driven by a drive sprocket 524i suitably coupled to a drive means such as an hydraulic or electric motor 526. An idler gear 532 is mounted on one of the ends $62.

Whether there is a single drum or a multi-drum assembly within the frame Sill), the drum assembly is bearingly supported between the ends 502. In the embodiment illsutrated in the FIGS. 12 and 13, two drums 518 and 5119 are co-axially mounted about the axis 506, with drum 529 being the inner drum which is rigidly secured to and driven from sprocket 522. The bearing support means for each of the

drums

518 and 519 includes, in each case, a pair of opposed circular races with bearings between them. The outer drum SE8 is bearingly supported between the end 502 by a pair of races 515 and 5116 which form a suitable bearing aperture 504 between them. Suitable roller or ball bearings are carried therein. In like manner, the inner drum 519 is bearingly supported to the end plate 502 to the end 513 of the outer drum 518. A circular race 520 is secured to the end plate 513 of the outer drum 518, and an opposed race 521 is secured to the end plate 511 of the inner drum 5w. Latch means are also provided, as discussed hereafter, to latch the drums for rotation or non-rotation with respect to the frame 560, depending upon which of the drums may be having cable reeled or unreeled therefrom.

it will be noted that the winch construction illus trated in FlGS. l2 and 13 provides a winch having multi-drum capacity, as recalled, and which has quite a substantial lateral rididity within a lateral space requirement which is very little wider than the width of the drums accommodated in the winch structure. The enclosure plate 508, of course, provides substantial protection for the faired cable 1102 which is stowed within the winch structure. Also, as noted, the faiied cable 102 is normally stowed in tension, so that the frame 506 including ends $02 and enclosure plate 508 provides a substantial protection for 2d personnel working in the area of the winch in the event of a cable break. A guard, such as guard 529 shown in FIG. l is suitably provided over the drive transfer chain 528 and the sprockets 524 and 52.2 to protect them from from icing and other weather conditions, dirt, etc., as well as to protect personnel working near the winch 108.

It will be seen, particularly upon reference to FIGS. 12 and 17 as well upon reference to the Hale US. Pat. No. 3,576,295 mentioned above that when a multi-drum assembly is provided, it is necessary also to provide suitable latching means to latch any adjacent pair of drums together for rotation or for non-rotation relative to the static 5WD as the case may be, depending on whether cable is being reeled or unreeled in a particular drum or one adjacent to it. Thus, cable is stored on each of the drums in a multi-drum assembly, but is unreeled first from the out-erniost drum and thence serially inwardly to the innermost drum; as a corollary thereto, cable is reeled on the innermost drum first and thence outwardly serially to the outermost drum. In the most simple mul'ti-drum assembly, being a two-drum assembly such as that illustrated in FIGS. l2 and 17, cable is reeled off the outer drum and then off the inner drum, and reeled onto the inner drum and then onto the outer drum.

Referring to FIGS. l2, 13, 15, 16 and MA to MG, an automatic latch means is described showing the manner in which drum 5E8 may be latched to drum SE9 to be driven therewith or latched in nonrotating position so as to allow only drum Slt) to be driven.

Referring specifically to the FIGS. it will be seen that the latch means comprises a plurality of levers, as fol lows. A first lever 69% is directly coupled to a shaft 6R0 which is rotatably mounted in an end of the inner drum 519. A second lever, 608 is also directly coupled to the shaft 610. A third lever 602 is rotatably mounted to the end of the outer drum 5118. A stop 6% is secured in non-rotating relationship to both of the

outer drums

518 and 519, and may be suitably secured to the outer portion of the end 502 of the frame sea of winch construction as shown in Fiture 312. Fourth and

fifth levers

604 and 605 respectively are directly coupled to a shaft 667 which is rotatably mounted in the end of the outer drum 518.

The operation of the latch means is as follows. Referring to PKG. MA, it will be noted that the outer drum 5118 is secured in non-rotating position by the interaction of both of

levers

602 and 604 with the stop 606. When the first lever 60b is in the position substantially as shown in FllG. MA that is, it does not extend radially outwardly at the end of drum 519 beyond the outermost extension of the drum drum W is adapted to be rotated in either clockwise or counterclockwise direction, as indicated by arrow 62f. The first lever 660 has operative and non-operative positions, the non operative position being such as indicated in FlG. MA when the inner drum is not completely filled with cable being wound thereupon. The shaft'6llll upon which levers 60(1) and 608 are directly coupled, is rotatably mounted and situated in the end of drum 5119 in a position so that when at last half turn of cable is being wound onto the inner drum 519, the second lever 668 is depressed by the cable, and the first lever 666 is rotated by being directly coupled to the shaft 6116 which itself is rotated by lever 66% being depressed, so that lever 666 assumes its operative position. FIG. l5 clearly shows the manner in which the lever 696 is depressed by the last half-tum of the cable 102 as it is wound onto the drum 5T9. [When the cable is being wound onto drum 5B9, the drum is being driven in the clockwise direction as shown by arrow 622 in lFlG. MB. It is also shown in FIG. MB that the operative position of lever 66b is such that it extends radially beyond the outer radial limit of the drum 519. Reference to FIG. MC shows that the lever 60th is engagable when in its operative position against lever 602, which is then rotated out of engagement with stop 666, so that drum 516 is released so as to rotate in a clockwise direction as indicated by arrow 623. it is seen, therefore, that lever 602 cooperates with stop 666 to preclude rotation of the outer drum 5th in the reeling direction of that drum. It is also seen that when levers 666i and 662 are engaged, and rotation of the lever 662 is stopped by a stop 61133, the drive which is imparted to the drum 519 is also transferred to drum 5 18, which rotates together with drum 519 and at the same rotative speed therewith.

As the first half turn of cable is wound onto the drum 51%, it engages the lever 665 which is directly coupled to shaft 667 to which lever 664i is also directly coupled. The lever 64M is therefore rotated to its non-operative position, out of co-operation with the stop 666. in that condition i.e. when cable is wound onto drurn SW and at least a half turn of cable is wound onto drum 518 each drum is free to rotate in either direction as indicated by arrow 62 1 in FIG. ll lll).

When cable is unreeled from drum 5T6, as the last half turn is removed from the drum, lever 665 is returned to the position shown in FIG. 16 so that lever 60d engages with stop 606. During unreeling from drum 518, both drums 5118 and 519 are driven in the counter-clockwise direction. It is thus seen that the operative position of lever 64% is such as to co-operate with stops 606 to preclude rotation of the outer drum 51th in the unreeling direction of rotation thereof.

As the first half-turn is unreeled from inner drum 5119, lever 66% returns to its original position and may be biased by such as spring 611T shown in FIG. so that lever 660 disengages from lever 662, and

lever 662 re-engages with stop 666 and co-operates therewith so as to preclude rotation of drum 518 in the reeling direction of rotation thereof. The condition of all the levers which comprise the latch means as shown in FlG. G is, therefore, substantially identical to the condition of those levers as they are shown in FIG. A.

FIG. 17 is a diagrammatic representation of a typical two-drum assembly, comprising inner drum S19 and outer drum 5118. A transverse slot 766 is formed in the outer drum 516 between the lips 762 and 764. The width of the slot itltl is such as to permit cable to be reeled or unreeled from drum 519 when drum 518 is non-rotative. The distance between drums 5M and S18 is such that when a faired cable 1162 under tension is stowed on the drums, there is no interference of the cable on drum 5116 with the cable on the drum 519 through the slot 766.

The material of the drum 5% is profiled in the region of lips 702 and 76 3 so that the apparent radius of curvature of the material is less than the nominal radius of the drum, and each lip curves noticeably inwardly towards the interior of the drum. it is preferable that the lip be so formed that the edges 762 and of the transfer slot 76%) underlie the cable which lies across the slot and is curved away from contact therewith. in this manner, radial loads which are induced by the cable tension of cable B62 in the drum 5H8 are reduced to zero at the edges of the radial slot.

it will be noticed, of course, that when the cable 162 is being reeled or unreeled from drum 5119, it will be in the position as indicated at 7M; and when the reeling transfers to drum 5 t8, the cable lifts onto the drum 5% past the lip 762. The cable then assumes the position indicated at 7112 for reeling or unreeling from outer drum 5116.

The reduced curvature in the region of the lips 72 and 764 is such that there is an increase in section moldulus of the material of the drum 513, and therefore a reduction of stress in the drum. it is therefore possible to provide the slotted drum 5118 having a strength of capability to withstand reeling, unreeling and stowage of cable under tension thereon, and which strength capability is substantially equal to that of the conventional unslottecl drum of the same nominal diameter.

When a faired cable is wound onto a drum, it is desirable to include a helical groove on the outer surface of that drum. in the past, such helical grooves have been machined into the surface of the drum with the commensurate high machining and material costs. The present invention contemplates the formation of a grooved outer surface for a drum by securing to the surface of a plain drum an outer layer of a relatively flexible material which has a suitable cross-section. Thus, an extrusion such as that indicated at T5612 in FIG. lb may be secured to the face of a drum indicated at 866, with an interface 36d which may suitably be an adhesive. Relatively flexible materials which are suitable for application to the surface of the drum so as to form a grooved surface thereon, include aluminum extru sions and rigid or semi-rigid vinyl or other suitable plastics.

it has been noted that, in the usual circumstance such as illustrated in FllGS. l to 6, the saddle is an inverting saddle against which the towed body is securely held when in its stowage position, and which inverts to permit passage of the towed body through the air/water interface. in that case, a saddle such as saddle EM shown in FIG. 19, may be used, The saddle assembly 104 includes suitable bumpers or rollers 324 is provided, and the bumpers 324 are such that the towed body may be securely held and nested against them. The saddle 164 is rotatably about the axis of rotation 216, which is also the axis of rotation of the tow sheave 316. It has been noted that it is desireable to provide means whereby a substantially constant pressure of contact can be maintained against the nose of the cable 102 when the body is being towed; and also that the body may tow very nearly beneath the vessel, even at high speeds when the cable is properly faired. The angle that the faired cable 102 makes with the nominal surface of the water is the piercing angle, and is shown in FIG. 4, at 300. it has also been noted that other, non-inverting saddles may be used, such as the saddle indicated generally at 326 in FIG. 21. That saddle may be mounted to

pantograph arms

328 and 330, and the latter arms may be rotatably mounted and bearingly support a shaft 332 upon which tow sheave 316 is rotatably mounted. (The Jareckie US. Pat. No. 2,780,196, referred to above, shows the use of a pantographic assembly.)

The piercing angle 300 of the faired cable 102 changes as the speed of the vessel changes. Also, as the vessel turns or rolls, the faired cable 102 may assume a two-off from the towing sheave 316; i.e. the cable does not tow straight from the tow sheave. It is important, of course, to keep the cable from escaping from the tow sheave, and provision is made by the invention contemplated herein for transferring side loads from the cable during tow-off. Such provision may include a roller box such as the roller box 328 shown in FIG. 21 or the roller box 330 shown in FIG. 19. lln FlG. 21, roller box 328 includes a frame 332, a nose roller 334 and a pair of side rollers 336; and the roller box 328 is rotatably and bearingly mounted to the shaft 332 by arms 338. It will be noted, therefore, that the roller box 328 is free to rotate on the shaft 332 about the same axis of rotation 340 as that of tow sheave 316, independently of saddle 326.

Because of the change of piercing angle, and the requirement to accommodate side loads during tow-off, it is important that the roller box be such as to maintain a substantially constant pressure of contact between the nose roller and the cable; and it has been found that it is best when the direction of the axis of the nose roller and the direction of the axis of the cable as it passes through the roller box and contacts the nose roller be substantially perpendicular. Also, during tow-off when there may be contact by the cable to either of the side rollers, it has been found to be best when the direction of the axes of the side rollers are substantially perpendicular to the direction of the axis of the cable so as to preclude any tendency of the cables to corkscrew" during interference of the cable with either side roller. Thus, it is desireable to provide the roller box so that the direction of the axes of the side roller, the direction of the axis of the nose roller and the direction of the axis of the cable as it passes through the roller box during normal towing operation, are all mutually perpendicular. These principles hold true both with respect to the roller box 328 which is free to rotate about axis 340 independently above saddle 326, as shown in FIG. 21; and roller box 330 which is mounted for rotation together with the saddle 104, about axis 218, as shown in FIG. 19.

Bias means are therefore provided to effect rotation of the roller box about its axis of rotation; particularly so as to maintain substantially constant pressure of contact between the nose roller and the forward edge of the cable. With reference to the roller box 330, the nose roller is indicated at 302 and the side rollers at 314; while in roller box 328, the nose roller is indicated at 334 and the side rollers at 336. The bias means is the same for each roller box, and includes a spring means such as an hydraulic cylinder 334 which is attached to the deck frame ll MD in a convenient place. The hydraulic cylinder is conveniently pressurized by gas/oil accumulator 306. A cable 303 is attached to the hydraulic cylinder 305 and is wrapped around and terminates at cam 312 at the cable end remote from the cylinder 304. The cam 312 is securely fixed to the

saddle box

328 or 330, so that as the cam rotates under the influence of the spring means such as hydraulic cylinder 304, the respective roller box also rotates therewith. The spring means biases the roller box upwards so as to maintain a substantially constant pressure between the

nose roller

302 or 334 and the cable 102 as it passes through the roller box.

The shape of the cam is profiled to provide a variable torque to the roller box due to the bias effect of the spring means, so as to take into account the shifting centre of gravity of the roller box (or roller box and saddle combined) as it rotates. Thus, the cam is profiled to provide a biasing torque to the roller box which varies substantially directly as the amount which the centre of gravity changes position, and is therefore a function of that change.

The design of the cam 312 may also take into account the fact that as the cylinder 304 retracts, the gas pressure in the gas/oil accumulator 306 reduces. The torque arrn generated by the cam 312 (being the distance between cable 308 and axis 216 or 340), must increase because of the combined effect of the shifting of the centre of gravity of the roller box and the reduced biasing effort supplied by the cylinder 30d.

There is shown on the roller box 330 of FIG. 19 a curved plate 318 which curves away from the frame and from the nose roller 302 therein at the end of the frame remote from the nose roller. The purpose of the plate 318 is a cable depressor, and is shown diagramatically in FIG. 20. There, it will be seen that when the submersible and towable body is secured into the saddle 104 by the tension in cable 102, and the saddle is inverted as shown, the cable reach from the saddle is lifted off the tow sheave 316 and the cable pull is horizontal. It has been mentioned above that when the towed body is launched, the deck frame is tilted on the skewable A-frame before the saddle is inverted as shown, the cable reach from the saddle is lifted off the two sheave 316 and the cable pull is horizontal. It has been mentioned above that when the towed body is launched, the deck frame is tilted on the slcewable A- frame before the saddle is inverted to insert the towed body through the air/water interface, the length of cable which is unreeled from the winch remains constant. Thus, plate 318 depresses the cable so as to maintain tension therein; and therefore the fairings which are applied to the cable stop short of the tow point 320 on the towed body, at a point 322.

There has been described an improved apparatus for launching, towing and recovering a submersible and towable body from a vessel, including; apparatus having a transom arm which together with a deck frame on which a winch, saddle and tow sheave are mounted forms a skewable A-frame, and an alternative embodiment thereof; alternative embodiments of a cable spooler assembly and cable tension stabilizer; an enclosed winch construction for single or milti-drum assemblies to be rotatably mounted therein; an improved, automatic latching mechanism for latching adjacent co-axial drums in a multi-drum assembly for reeling and unreeling cable from any drum thereof; an improved drum construction having stress relief and an inexpensive grooved surface; and alternative embodiments of a roller box and saddle assembly for maintaining constant nose pressure against the cable during towing, and for accommodating side loading during tow-off.

It is not intended that the preceeding discussion be limiting with respect to the invention described herein, but illustrative of principles and concepts involved.

I claim:

1. In apparatus for launching, towing and recovering a submersible and towable body from a vessel, where said apparatus includes: winch means for storing cable, at the outer end of which cable said body is secured; rotatably sheave means over which said cable runs, said sheave means having an axis of rotation situated lengthwise along said cable between said body and said winch means; saddle means against which said body is secured when in its stowed position; and deck frame means upon which said sheave, saddle and winch are mounted; the improvement comprising:

transom arm means pivotally attached to said vessel to form in combination with said deck frame means, a skewable A-frame, one foot of said A- frame being at the pivot point for said transom arm means, the other foot of said A-frame being at a point on said vessel where loading from said apparatus transfers to the vessel, and the apex of said skewable A-frame being at the axis of rotation of said sheave means;

and actuator means secured to said vessel and to said deck frame means to move said deck frame means with respect to said vessel so as to skew the apex of said skewable A-frame.

2. The apparatus of claim l where said transom arm means comprises at least one arm adapted to bearingly support said sheave; said arm being pivotally mounted to said vessel at an end of said arm remote from said sheave and at a point below the level at which said winch operates.

3. The apparatus of claim 1 where said transom arm means comprises a pair of arms, each pivotally mounted to said vessel at a point below the level at which said winch operates; the upper end of each of said pair of arms being adopted to bearingly support said sheave for rotation about said axis of rotation.

4. The apparatus of claim 3 when mounted at the aft endof a vessel, said actuator means being adapted to drive the upper ends of said transom arm means, the rear end of said deck frame means, and said sheave, backwardly and downwardly from said aft end of said vessel.

5. The apparatus of claim 4 where said actuator means comprises hydraulic ram means having foreand-aft ends relative to the fore-and-aft direction of said vessel, where the foreward end of said hydraulic ram means is pivotally attached to said vessel and the aft end of said hydraulic ram means is arranged so as to skew the apex of said skewable A-frame backwardly and downwardly with respect to said vessel.

6. ln apparatus for launching, towing and recovering a submersible and towable body from a vessel, where said apparatus includes: winch means for storing cable, at the outer end of which cable runs, said sheave means having an axis of rotation situated lengthwide along said cable between said body and said winch means; saddle means against which said body is secured when in its stowed position; and deck frame means upon which said sheave, saddle and winch are mounted; the improvement comprising:

roller box means mounted for rotation about the axis of rotation of said sheave; said roller box means comprising a frame, a pair of side rollers in said frame and situated so that one of said pair of side rollers lies on each side of said cable when said body is being towed and said cable extends downwardly from said sheave to said body, and a nose roller at one end of said frame adapted to contact the forward edge of said cable when said body is being towed;

and bias means to effect rotation of said roller box about said axis of rotation so as to maintain substantially constant pressure of contact between said nose roller and the forward edge of said cable; said bias means including cam means adapted for rota tion about the axis of rotation of said sheave together with said roller box means, and a cable wrapped around said cam and secured at its end remote from said cam to spring means.

7. The apparatus of claim 6 where said pair of side rollers and said nose roller are mounted so that the direction of the axis of the nose roller is substantially perpendicualr to the direction of the axis of each of said side rollers; and so that during normal towing operation when said cable extends downwardly from said nose roller and substantially in a perpendicular direction when viewed from above with respect to said nose roller, said bias means is adapted to maintain the position of said roller box with respect to said cable so that the direction of the axis of said side rollers, the direction of the axis of said nose roller, and the direction of the axis of said cable as it passes through said roller box in contact with said nose roller, are all mutually perpendicular.

8. The apparatus of claim 6 where said spring means includes an hydraulic cylinder pressurized by an hydraulic accumulator.

9. The apparatus of claim where said cam means is such that as said remote end of said cable is drawn by said cylinder away from roller box and said roller box rotates about the axis of rotation of said sheave, the torque provided by said cable as it is wrapped around said cam to said roller box varies substantially directly as the amount which the centre of gravity of said roller box changes position, so as to keep substantially constant pressure between said cable and said nose roller.

10. The apparatus of claim 9 where said saddle and said roller box are mounted for rotation with each other about said axis of rotation of said sheave, and said saddle is secured to said roller box.

11. The apparatus of claim 6 where said saddle and said roller box are mounted for rotation with each other about said axis of rotation of said sheave, and said saddle is secured to said roller box.

12. The apparatus of claim 11, further comprising a curved plate at the end of said frame remote from said nose roller, said plate curving away from said frame and said roller box.

Claims

1. In apparatus for launching, towing and recovering a submersible and towable body from a vessel, where said apparatus includes: winch means for storing cable, at the outer end of which cable said body is secured; rotatable sheave means over which said cable runs, said sheave means having an axis of rotation situated lengthwise along said cable between said body and said winch means; saddle means against which said body is secured when in its stowed position; and deck frame means upon which said sheave, saddle and winch are mounted; the improvement comprising: transom arm means pivotally attached to said vessel to form in combination with said deck frame means, a skewable A-frame, one foot of said A-frame being at the pivot point for said transom arm means, the other foot of said A-frame being at a point on said vessel where loading from said apparatus transfers to the vessel, and the apex of said skewable A-frame being at the axis of rotation of said sheave means; and actuator means secured to said vessel and to said deck frame means to move said deck frame means with respect to said vessel so as to skew the apex of said skewable A-frame.

2. The apparatus of claim 1 where said transom arm means comprises at least one arm adapted to bearingly support said sheave; said arm being pivotally mounted to said vessel at an end of said arm remote from said sheave and at a point below the level at which said winch operates.

4. The apparatus of claim 3 when mounted at the aft end of a vessel, said actuator means being adapted to drive the upper ends of said transom arm means, the rear End of said deck frame means, and said sheave, backwardly and downwardly from said aft end of said vessel.

5. The apparatus of claim 4 where said actuator means comprises hydraulic ram means having fore-and-aft ends relative to the fore-and-aft direction of said vessel, where the forward end of said hydraulic ram means is pivotally attached to said vessel and the aft end of said hydraulic ram means is arranged so as to skew the apex of said skewable A-frame backwardly and downwardly with respect to said vessel.

6. In apparatus for launching, towing and recovering a submersible and towable body from a vessel, where said apparatus includes: winch means for storing cable, at the outer end of which cable said body is secured; rotatable sheave means over which said cable runs, said sheave means having an axis of rotation situated lengthwise along said cable between said body and said winch means; saddle means against which said body is secured when in its stowed position; and deck frame means upon which said sheave, saddle and winch are mounted; the improvement comprising: roller box means mounted for rotation about the axis of rotation of said sheave; said roller box means comprising a frame, a pair of side rollers in said frame and situated so that one of said pair of side rollers lies on each side of said cable when said body is being towed and said cable extends downwardly from said sheave to said body, and a nose roller at one end of said frame adapted to contact the forward edge of said cable when said body is being towed; and bias means to effect rotation of said roller box about said axis of rotation so as to maintain substantially constant pressure of contact between said nose roller and the forward edge of said cable; said bias means including cam means adapted for rotation about the axis of rotation of said sheave together with said roller box means, and a cable wrapped around said cam and secured at its end remote from said cam to spring means.

7. The apparatus of claim 6 where said pair of side rollers and said nose roller are mounted so that the direction of the axis of the nose roller is substantially perpendicualr to the direction of the axis of each of said side rollers; and so that during normal towing operation when said cable extends downwardly from said nose roller and substantially in a perpendicular direction when viewed from above with respect to said nose roller, said bias means is adapted to maintain the position of said roller box with respect to said cable so that the direction of the axes of said side rollers, the direction of the axis of said nose roller, and the direction of the axis of said cable as it passes through said roller box in contact with said nose roller, are all mutually perpendicular.

9. The apparatus of claim 8 where said cam means is such that as said remote end of said cable is drawn by said cylinder away from roller box and said roller box rotates about the axis of rotation of said sheave, the torque provided by said cable as it is wrapped around said cam to said roller box varies substantially directly as the amount which the centre of gravity of said roller box changes position, so as to keep substantially constant pressure between said cable and said nose roller.