US3799005A

US3799005A - Drum winch

Info

Publication number: US3799005A
Application number: US00317793A
Authority: US
Inventors: G Koehler
Original assignee: Individual
Current assignee: Individual
Priority date: 1972-06-16
Filing date: 1972-12-22
Publication date: 1974-03-26
Anticipated expiration: 1991-03-26
Also published as: DE2229340B2; DE2229340A1; GB1418013A

Abstract

The present drum winch is especially suitable for use on sailing vessels and comprises in its basic concept two pairs of planetary gear wheels which cooperate with a drive wheel, a disk, and a jack wheel whereby a large step-up ratio may be accomplished in one direction of rotation of the drum shaft. In addition, a slipping or torque release clutch may be arranged operatively between the jack wheel and the disk and a braking action may be applied to the jack wheel by means of pawls and ratchet wheels in one rotational direction whereby a large step-up ratio is obtained in one rotational direction while in the opposite rotational direction a 1:1 transmission or a large reduction or step-down ratio is obtained. In further modification worm gear means may be provided which are connected to or coupled with the jack wheel when the gear is driven through the disk or which are connected to or coupled with the disk when the gear is driven through the jack wheel whereby an additional large step-down ratio is accomplished for a sensitive back and forth rotation of the winch.

Description

United States Patent 1191 Koehler Mar. 26, 1974 DRUM WINCH [76] Inventor: Georg Koehler, Almeidaweg 3, 813) [57] ABSTRACT Stamberg Germany The present drum winch is especially suitable for use [22] Filed: Dec. 22, 1972 on sailing vessels and comprises in its basic concept two pairs of planetary gear wheels which cooperate [21] Appl' 3l7793 with a drive wheel, a disk, and a jack wheel whereby a large step-up ratio may be accomplished in one direc- [30] Foreign Application Priority Data tion of rotation of the drum shaft. In addition, a slip- June 16, 1972 Germany 2229340 P Or tOfque release Clutch y be arranged p tively between the jack wheel and the disk and a brak- 52 US. Cl. 74/812, 254/150 R, 74/626, g action y be pp to the j wheel y means 74/792 of pawls and ratchet wheels in one rotational direction [51] Int. Cl. F16}; 5/52, F16h 57/16, 366d 1/30 whereby a large step-up ratio is obtained in one rota- [58] F eld Of Search 254/150; 74/812, 792, 626 tional direction while in the opposite rotational direction a 1:1 transmission or a large reduction or step- [56] Refer c Cit d down ratio is obtained. In further modification worm UNITED STATES PATENTS gear means may be provided which are connected to or coupled with the jack wheel when the gear is driven 34836;; 3:32; 23'; 4233 through the disk or which are connected to or coupled 3'656:596 4/1972 giil' R X with the disk when the gear is driven through the jack 618,896 11/1971 Bewley 250/150 R Wheel whereby an additional large Step-down ratio is 3,728,914 4/1973 Guangorena et al. 74/812 accomplished for a Sensitive back and forth rotation of Primary Examiner-Arthur T. McKeon Attorney, Agent, or Firm-W. G. Fasse the winch.

28 Claims, 5 Drawing Figures PAIENTEDMARZG m4 SHEET 1 OF 4 PATENTEDMARZS 1974 SHEET u [if 4 Fig.4

DRUM WINCH BACKGROUND OF THE INVENTION The present invention relates to a drum winch. More specifically, the present drum winch is suitable for use on sailing vessels. The winch includes a rope drum rotatably supported relative to a drum shaft. The drum is rotatable by means of a gear drive including a ratchet mechanism in the same direction independently of the direction of rotation of the drum shaft which is selectively rotatable in both directions whereby the drum is rotatable through the ratchet mechanism at different rotational speeds depending on the direction of rotation of the drum shaft. The present winch may further be provided with a releasable brake for the reverse rotation of the drum.

In order to perform sailing maneuvers with the aid of a drum winch, the latter must be capable of being driven with at least two different rotational speedsThis is necessary where the winch is employed to handle the halyard sheet in order to quickly set or hoist the sail. On the other hand, it is necessary to pull tight the sail with a large force against the wind pressure and to regulate the tightness of the sail under wind pressure. Similarly, two speeds are required when the winch is employed to handle the main sheet which may be required to be hauled in quickly as long as the main sheet is not yet under tensional stress. Thereafter, the main sheet must be hauled in against increasing tensional forces up to the maximum tension, whereby the main sheet must also be controlled or regulated.

Further, a winch used on a sail boat regardless whether it is used as a halyard winch or a main sheet winch must provide the possibility of a rapid sheet payout, for example, for taking down the sails or for rapidly turning or tacking. In this connection, it is preferable to provide a possibility of braking the sheet being paid out.

Conventional drum winches for sail boats have drums which are rotatable in the same direction independently of the direction of rotation of the crank handle, however, with different rotational speeds. For this purpose, the driven gear is provided with an internal spur gear rim which meshes with a reversal gear supported on a rotatable disk. The reversing or reversal gear meshes simultaneously with a drive gear attached to the drive shaft. A locking pawl which is effective in but one direction is arranged between the disk and the reversing gear. The locking pawl releases the reversing gear when the driving shaft is rotated in one direction for rotating the driven gear in a step-down fashion. When the drive shaft is rotated in the opposite direction, the locking pawl locks the reversing gear relative to the disk and to the driven gear whereby a 1:1 rotational speed ratio is accomplished between the driving shaft and the driven gear.

With the aid of these conventional drum winches, especially if they are used for regulating the main sheet, particularly in racing, it is only possible to haul-in the sail by a small amount because the 1:] speed ratio is insufficient for a rapid haul-in. Thus, it becomes necessary to haul-in the main sheet by hand while simultaneously rotating the winch quickly enough for taking up the slack portion of the sheet whereby the formation of loops must be avoided because they tend to get tangled. Besides, there is always the danger that the hand or a finger may get caught between the main sheet and the winch. During the rapid haul-in it is hardly possible to temporarily and quickly payout the main sheet again or to apply a braking action by means of the winch because the drum cannot follow quickly enough the rapid movement of the sheet. Besides, at least two persons are required for such a rapid hauling of the main sheet.

The above considerations apply correspondingly where a conventional drum winch is employed as a halyard winch and where a sail for instance a balloon sail is to be set rather rapidly. Here again the l:] rotational speed ratio is not sufficient and the setting of the sail must also be done by hand. If the wind pressure is so large that a further hauling in of the halyard by hand is not possible, it would become necessary to use the winch for a further tightening of the sail provided that the winch can follow up fast enough so that upon letting go of the halyard, the latter will not be slackened altogether. Usually it is not possible to follow up with the drum fast enough and the halyard must be held by hand in the meantime, whereby it may happen that the pull on the halyard becomes so large that the halyard runs through the hand causing substantial burning injuries. Besides, also in this maneuver there is the danger that the hand or the finger may get caught between the halyard and the winch. Last but not least, the change over from the manual handling of the halyard to handling with the aid of the winch entails a substantial loss of time until the setting of the sail under wind pressure is completed. Due to this large danger of injury and due to the cumbersome handling, prior art drum winches are not suitable for operating the halyard nor the main sheet. On the other hand, prior art drum winches which provide a large transmission ratio for the rapid setting of a sail and which simultaeously have the facility of a large step-down ratio for the sensitive setting of the sail have the disadvantage that due to their large space requirements they cannot be suitably installed on a sailboat due to the limited space conditions. Therefore, drum winches for performing of sailing maneuvers have not found widespread application due to the disadvantages outlined above.

OBJECTS OF THE INVENTION In view of the foregoing, it is the aim of the invention to achieve the following objects singly or in combination:

to avoid the drawbacks of the prior art, more specifically to provide a drum winch which is especially suitable for use in connection with the performing of sailing maneuvers;

to provide a drum winch which shall have simple structural features and simultaneously require but little space;

to provide a drum winch which is usable for handling the main sheet as well as the halyard;

to provide a winch which may be easily modified for more than two rotational speed ratios;

to provide a winch which, though especially suitable for use on a sailboat, is equally useful in connection with any kind of hoisting mechanism;

to provide a drum winch having a large step-up ratio in at least one rotational direction of the drum shaft;

to provide a drum winch having a large step-up ratio in one direction of rotation of the drum shaft and a large step-down ratio in the other direction of rotation of the drum shaft, whereby the other direction of rotation of the drum shaft shall also be capable of providing a lzl transmission; and

to provide a drum winch capable of an especially sensitive regulation or control in the forward as well as in the reverse direction of rotation.

SUMMARY OF THE INVENTION According to one embodiment of the invention there is provided a drum winch in which the gear drive means comprise a sun and planetary gear means which include a disk rigidly secured to the drum shaft and at least two pairs of planetary gears rotatably supported in said disk as well as a jack wheel or gearv The pairs of planetary gears mesh with the jack wheel which may be either locked or which is subject to a braking force, whereby in both instances, the drum shaft is rotatable relative to the jack wheel. The jack wheel is coupled to an output drive gear on the drum through one pair of the planetary gears for a step-up transmission and through the other pair of planetary gears for a step-down transmission. The pairs of planetary gears are arranged in such a manner that for each direction of rotation of the drum shaft they counteract each other, whereby depending upon the direction of rotation of the drum shaft, the driving or force transmitting connection between one pair of the pairs of planetary gears and the respective output driving gear is interrupted by means of a locking or ratcheting mechanism. In the just described embodiment the disk is secured to the drum shaft against rotation whereas the jack wheel is either locked, for example, against the gear box or housing or it is subjected to a braking force, the drum shaft-being rotatable relative to the jack wheel. This particular embodiment is advantageous because it permits a clear and simple structural arrangement of the gear means. However, it is also quite possible to secure the jack wheel, instead of the disk, to the drum shaft against rotation and to lock, instead of the jack wheel, the disk or to subject the disk to a braking force.

The construction of the drum winch according to the invention achieves a large step-up transmission in one direction of rotation of the drum shaft while a large step-down transmission may be provided in the other direction of rotation of the drum shaft. This feature has the advantage of a very fast take up of the sheet on the drum in one direction of rotation of the drum shaft and the sheet may be drawn tight with a large force in the other direction of rotation of the drum shaft. Especially, if the disk is'driven and the jack wheel is subjected to a braking force, the required brake may be effective axially on the jack wheel and the brake may be provided with a usual brake lining or the brake may be constructed as a disk brake.

BRIEF FIGURE DESCRIPTION In order that the invention may be clearly understood, it will now be described, by way of example, with reference to the accompanying drawings, wherein:

FIG. 1 is a side view ofa drum winch according to the invention;

FIG. 2 is a longitudinal sectional view through the drum winch according to FIG. 1;

FIG. 3 illustrates in a somewhat schematic manner and by means ofa perspective, exploded view, the gear means of the present drum winch;

FIG. 4 is a gear diagram of modified embodiment according to the invention; and

FIG. 5 is a gear diagram of still another embodiment.

DETAILED DESCRIPTION OF EXAMPLE EMBODIMENTS Referring to FIG. 2, the drum 1 of the present drum winch comprises a left hand face flange 11 which is rotatably supported on the housing 2. The housing is divided along the separation plane 202 whereby two

housing portions

21 and 22 are formed. The gear means for the drum 1 comprise sun and planetary gear means. The face flange 11 of the drum 1 comprises an outer collar 111 which reaches into the housing 2 whereby the flange is supported on the outer circumferential surface of the collar by means of rollers 201 in the housing. A large ring wheel 12 having radially inwardly facing gear teeth is provided on the inner circumference of the outer collar 111. The face flange 11 is further provided with an'inner collar 112 arranged concentrically relative to the large ring wheel 12. The inner collar 112 carries a small sun wheel 13 having teeth facing radially outwardly. A reversing planetary gear 14 meshes with the large ring wheel 12. The reversing gear 14 is rotatably supported in the disk 3 of the sun and planetary gearing means. Further, the reversing planetary gear 14 meshes with the planetary gear 15 which is also rotatably supported in the disk 3.

The dimensions of the reversing planetary gear wheel 14 and of the planetary gear wheel 15 are selected in such a manner that the planetary gear wheel which rotates with its axes about a smaller circumferential circle does not mesh with the external teeth of the small sun wheel 13. However, a further planetary gear wheel 16 meshes with the small sunwheel 13. The planetary gear 16 is also rotatably supported in the disk 3.

A jack wheel 4 is arranged on the side of the disk 3 facing away from the drum. The supporting jack wheel 4 also comprises a large ring wheel 41 with an inwardly facing gearing and a small sun wheel 42 arranged concentrically relative to the large ring wheel and having an external gearing. A planetary gear 43 meshes with the large ring wheel 41 which is supported on the shaft stump 161 of the planetary gear 16 so that the planetary gear 43 is secured against rotation in one direction and rotatable in the opposite direction of rotation. This locking against rotation in one direction is accomplished by means of pawls 431 which cooperate with the ratchet wheel 162 as seen in FIG. 3. The ratchet wheel 162 is secured to the shaft of the planetary gear wheel 16.

Similarly, a planetary gear wheel 44 meshes with the small sun wheel 42. The planetary gear wheel 44 is supported on the shaft 151 of the planetary gear 15 which meshes with the reversing planetary gear 14. The planetary gear 44 is rotatable relative to the shaft 151 in one rotational direction whereas pawls 441 prevent the rotation of the planetary gear 44 in the opposite rotational direction.

The disk 3 of the sun and planetary gear means is secured against rotation to the drum shaft 5. Both ends of the drum shaft 5 are provided with means adapted for cooperation with a crank handle. For example, each end may be provided with a female hexangonal socket 501 into which a crank handle may be selectively insorted either on one side of the drum or on the other side of the drum.

With the aid of the above described sun and planetary gear means, it is possible to drive the drum 1 with two rotational speed ratios in the direction in which the drum shaft 5 and with it the disk 3 are rotated by means of the crank handle. To facilitate the clarity of the illustration, FIG. 3 shows the gear wheels of the sun and planetary gear means by their respective pitch circle. Further, the disk 3 as well as the

pawls

431 and 441 and the

respective ratchet wheels

152 and 162 are shown in FIG. 3 in a somewhat symbolized manner to facilitate the presentation.

Let it be assumed for describing the operation of the sun and planetary gear means that the jack wheel 4 with its large and

small sun wheels

41 and 42 is stationary. If in this instance the disk 3 is rotated in the counter-clockwise direction as indicated by the arrow a in FIG. 3, then the shafts of all the planetary gears also rotate in the counter-clockwise direction about the drum shaft 5. Thus, the planetary gear 43 which meshes with the stationary large ring wheel 41 is revolving in the clockwise direction as indicated by the arrow a1, whereby the pawls 431 of the planetary gear wheel 43 are entrained in the clockwise direction, whereby the ratchet wheel 162 is also entrained in the clockwise direction as indicated by the arrow a2 because the pawls 431 are interlocking with the ratchet wheel 162 in this direction. The ratchet wheel 162 drives the planetary gear 16 through the shaft 161 also in the clockwise direction as indicated by the arrow a3. Since the planetary gear wheel 16 and the small sun wheel 13 mesh together at the face collar 11 of the drum 1, the small sun wheel 13 and with it the drum are entrained in a counter-clockwise rotation as indicated by the arrow a4.

As has been described above with reference to the planetary gear wheel 43, the planetary gear wheel 44 is also entrained with the rotation of the disk 3 in the counter-clockwise direction as indicated by the arrow a. The planetary gear wheel 44 revolves about the stationary small sun wheel 44 of the jack wheel 4 in such a manner that it rotates in the counter-clockwise direction as indicated by the arrow a5. The pawls 441 are also entrained in the same direction. However, when the planetary gear wheel 44 rotates in the counterclockwise direction as mentioned, the pawls ratchet on the corresponding ratchet wheel 152. Therefore, the ratchet wheel 152 and the planetary gear wheel which is rigidly connected to the ratchet wheel 152, are not entrained by the planetary gear wheel 44. This is in good order because the large ring wheel 12 and the small sun wheel 13 in the face flange 11 of the drum 1 rotate at the same angular speed in the counterclockwise direction as indicated by the arrow a6, whereby the reversing planetary gear 14 meshing with the large sun gear 12 also rotates counter-clockwise as indicated by the arrow a7. The reversing planetary gear 14 meshes with the planetary gear 15. Therefore, this planetary gear 15 would lock the gear drive unless the planetary gear 15 is permitted to freely rotate which is accomplished by the cooperation between the corresponding ratchet wheel 152 and the respective pawls 441 whereby the planetary gear 15 may rotate in the clockwise direction as indicated by the arrow a8. Thus, the drum 1 is driven in the counter-clockwise direction as indicated by the arrow 04 when the drum shaft 5 is rotated in the counter-clockwise direction as indicated by the arrow a. The dimensions or the number of teeth of the effectively cooperating gear wheels will determine the driving speed.

On the other hand, when the drum shaft 5 and with it the disk 3 are rotated in the clockwise direction as indicated by the arrow b, the planetary gear wheel 44 revolves about the stationary small sun wheel 42 of the jack wheel 4 also in the clockwise direction as indicated by the arrow bl. In this instance, the ratchet wheel 152 and the pawls 441 are effective whereby the planetary gear wheel 15 is also entrained in the clockwise direction as indicated by the arrow a8. The planetary gear 15 drives now the large sun wheel 12 again in the counterclockwise driection as indicated by the arrow a6 through the reversing planetary gear 14 which rotates also counter-clockwise as indicated by the arrow a7. As a result, the drum 1 now rotates just as in the above described example again in the counterdirection of the rotation of the drum shaft 5, that is in the counter-clockwise direction. However, in the second example, the rotational speed ratio of the drum 1 as compared to the first direction of the drum shaft 5 is now changed by the dimensions of the now effective, driving planetary gear wheels. If the drum shaft 5 rotates in the direction of the arrow b in the clockwise direction the pawls 431 ratchet along the corresponding ratchet wheel 162. Therefore, the meshing of the planetary gear wheel 43 with the stationary large sun wheel 41 does not entrain the respective planetary gear wheel 16 whereby the gear wheel 16 may freely rotate in the direction of the arrow a3 as determined by the large sun wheel 12 and with the same angular speed under the drive of the small sun wheel 13.

In view of the above it will be appreciated that the drum 1 according to the invention may be driven with different rotational speeds depending on the direction of rotation of the drum shaft 5 whereby the drum itself will rotate in the same direction in both instances, for example, counter-clockwise as shown in FIG. 3.

In connection with the above described operation of an embodiment it was assumed that the jack wheel 4 is stationary. In the modified embodiment now to be described, the jack wheel means will not be stationary. Reference is made of FIG. 2 which illustrates an embodiment in which the drum may be rotated with different speeds in the same direction and also with a stepdown transmission. Stated differently, the drum 1 may be rotated with the same angular speed as the drum shaft 5 provided that the jack wheel means 4 as well as the face flange 11 of the drum 1 may be rotated with the same angular speed as the disk 3 which is secured to the drum shaft 5 by tongue and groove means 31. In this embodiment, all planetary gear wheels remain stationary relative to the jack wheel means 4 and relative to the face flange 11 whereby a 1:1 drive ratio of the drum 1 by the drum shaft 5 is accomplished in the following manner.

It is necessary to release the jack wheel means 4 at least for the direction of rotation of the drum in which the sheet is rolled up on the drum if it is desired that the jack wheel means 4 may rotate along with the disk 3 and thus also with the drum 1 for the rolling up of the sheet. This take up rotation of the drum corresponds in its direction to the direction of rotation of the large ring wheel 12 as indicated by the arrow a6 in FIG. 3, that is in the counter-clockwise direction. However, the jack wheel means 4 must be locked in the opposite direction, that is, in the clockwise direction in order to produce the counter-force at the jack wheel 41 which is required for the sets of planetary gears when the drum 1 is driven with one of the above described transmissions that is with a step-up or a step-down transmission. Thus, the jack wheel means 4 must be arrested in the illustration according to FIG. 3 against a clockwise rotation, further, the jack wheel means 4 must be released for a counter-clockwise rotation. This may again be accomplished by means of a ratchet wheel and pawls cooperating with the ratchet wheel. As may be seen from FIG. 2 the jack wheel means 4 are coupled through a clutch 62 to be described in more detail below with a ratchet wheel 61 which may best be seen in the illustration of FIG. 3. The ratchet wheel 61 is released by the pawls 601 in a rotational direction indicated by the arrow 01. The jack wheel means 4 are arrested or locked in the opposite rotational direction as indicated by the arrow 02. According to FIGS. 2 and 3 the pawls are rotatably supported in a worm wheel 6 which is arranged to be driven by a worm gear 7. If the worm gear 7 is provided with a self-locking feature the worm wheel 6 will remain stationary as long as the worm gear 7 is not driven. This driving arrangement through the worm gear 7 will be described in more detail below. Let it be assumed here that the worm wheel 6 is stationary whereby the jack wheel means 4 are released for rotation in a direction indicated by the arrow cl as seen in FIG. 3. This is accomplished through the pawls 601 and the ratchet wheels 61 to which the jack wheel means 4 are coupled by the clutch 62. These elements arrest the jack wheel means against rotation in the opposite direction shown by the arrow c2.

As may be seen from FIG. 2 a slipping or torque release clutch 521 is arranged between the drum shaft and the jack wheel means 4. Another slipping or torque release clutch 511 is effectively interposed between the drum shaft 5 and the drum 1. These clutches are effective as long as the pull of the sheet to be wound up on the drum and thus the torque moment effective on the drum is small. In order to adjust the frictional force of the cooperating slipping

clutches

521 and 511, the drum shaft 5 is provided in two shaft portions 51 and 52 which are connected to each other by tongue and groove means 502 which prevent rotation of one shaft portion relative to the other but which permit an axial shifting. The shaft portions or members 51 and 52 may be adjusted in their axial longitudinal direction relative to each other by means of an adjusting screw 502 having a head resting against the shaft member 51 at the bottom of the respective female socket 501. The threaded shank of the screw 503 is screwed into a threaded bore 505 of the other shaft member 52. Depending upon the extent of adjustment ofthe screw 503 the coupling force of the slipping

clutches

511 and 521 may be adjusted accordingly, whereby the respective cooperating elements or members are pressed together with a larger or smaller frictional force. The adjustment of the screw'503 is secured against release by means of a spring 504 inserted between the shaft members 51 and 52. This spring 504 operates simultaneously as a reset spring since it tends to shift the shaft members 51 and 52 axialy away from each other.

As long as the drum shaft 5 is driven in the take up direction of rotation of the drum 1 and as long as the slipping

clutches

511 and 521 couple the drum 1 and the jack wheel means 4 with the drum shaft 5, the drum 1 is rotated with the angular velocity of the drum shaft 5. However, as soon as the pull or tension of the sheet on the drum 1 becomes so large that the clutches S11 and 521 slip, a relative rotation is established between the drum 1 and the jack wheel means 4 which otherwise would be rotated in the clockwise direction by the pull of the sheet which is prevented by said slipping and due to the fact that the jack wheel means 4 are arrested against rotation in this direction. However, due to the fact that the jack wheel means 4 are arrested for rotation in the clockwise direction and since the disk 3 is still driven counter-clockwise along with the drum shaft 5 due to the tongue and groove means 31 shown in FIG. 2 and as indicated by the arrow 11 in FIG. 3, the planetary gear 44 is supported by the small sun wheel 42 whereby it is enabled to drive the drum as described above through the planetary gear 15, the reversing planetary gear 14 and the large ring wheel 12 as indicated by the arrow a6.

The structural features so far described permit the following operation of a drum winch according to the invention. For example, if the drum winch is employed as a halyard winch, it is possible to rapidly set the respective sail when the drum shaft 1 is rotated in the direction of the arrow a as shown in FIG. 3, whereby the step-up transmission becomes effective and the sail is exposed to the full wind pressure only after it has been substantially set. This has the advantage that damages to the sail due to fluttering are avoided and that the sail is prevented from winding itself about the mast or the shrouds. However, as soon as the sail is substantially set and thus provides a large attack surface for the wind, the tension on the sheet and thus on the drum 1 becomes larger. At this instance the direction of rotation of the drum shaft 5 is to be reversed. Thus, prior to the slipping of the

clutches

511 and 521 when a certain sheet tension has been reached, the drum shaft rotates to drive the disk 3 in the clockwise direction and with a ratio of 111. However, at the instance of slipping of the

clutches

511 and 521 the step-down transmission of the gearing means becomes effective without any interruptions. The step-down drive is accomplished through the small sun wheel 42 and the

planetary gears

44, 15 and 14 as well as through the large sun wheel 12 forming part of the drum flange 11. The sail is now pulled tight with a large force against the force of the wind due to the large step down ratio.

The above described drum winch according to the invention may also be employed in a similar manner for handling the main sheet whereby it is possible to pull the main sheet quickly tight due to the large step-up ratio as long as the main sheet is not subject to a substantial load by the wind through the sail. When the wind pressure increases, the direction of rotation of the crank handle may simply be reversed whereby the 1:1 ratio is automatically established. If the wind pressure increases still more the slipping clutches 511 and S21 become effective and the further tightening of the main sheet is accomplished with a large force due to the now effective step-down ratio The drum winch according to the invention is also suitable for taking the sail down when the winch is used as a halyard winch or for quickly paying out the main sheet for example when coming about and tucking maneuvers are to be performed. In order to accomplish these functions the drum winch as illustrated in FIG. 2 comprises a clutch which cooperates with the jack wheel means 4 whereby a reverse rotation of the jack wheel means 4 and thus the rotation of the drum 1 in the payout direction, that is in the clockwise direction as illustrated in FIG. 3 is possible.

The just mentioned clutch is the clutch 62 which, as mentioned above, and as shown in FIG. 2 is arranged between the jack wheel means 4 and the ratchet wheel 61. The ratchet wheel 61 is supported within the worm wheel 6 for axial displacement by means of a hand wheel 63. The hand wheel 63 is adjustable axially in a housing member 22 by means of a threading 631 for applying a braking action to the jack wheel means 4 through the clutch 62 or for releasing the jack wheel means for rotation in the direction indicated by the arrow 02 in FIG. 3 in which the rotation is otherwise locked by means of the pawls 601. Thus, the ratchet wheel 61 may be shifted into or out of its operative position. The hand wheel 63 is axially supported in the ratchet wheel 61 by means of a ball bearing 632 so that a relative rotation between the ratchet wheel 61 and the hand wheel 63 is possible. Depending on the adjustment of the hand wheel 63 and thus upon the pressure applied to the clutch 62 a larger or smaller braking force may be applied to the jack wheel means 4 with regard to its rotation in the direction which would otherwise be locked due to the pawls 601. If desired, the jack wheel means 4 may be completely released for rotation in the just described direction. Due to these features according to the invention, the present drum winch l is capable to rotate in the backward direction, that is, in the clockwise direction according to FIG. 3 in response to tension applied to the drum 1 due to the wind pressure on the halyard or the main sheet, whereby a braking force may be applied to such reverse rotation. If the clutch is engaged again, the drum 1 may be rotated only in the take-up direction in response to the drive by the drum shaft 5.

Another possibility for releasing the drum rotation in the reverse direction is illustrated in FIG. 5 wherein a sliding clutch 17 is interposed between the drum 1 and the output drive wheel 11. The sliding clutch 17 may be shifted back and forth as indicated by the double arrow 0 for releasing or coupling the drum with the output drive wheel 11. A clutch between the drum 1 and the output drive wheel 11 has the advantage that the drum may rotate in the reverse direction without a corresponding rotation of the crank handle.

As shown in FIG. 2, the worm wheel 6 is provided for operating the drum 1 additionally to the above described possibilities of operation, with a very large stepdown ratio. The worm wheel 6 is driven by a drive worm 7 which is in turn operated by means of a further crank handle not shown or by means of an additional motor 9 shown in FIG. 1, for example an electromotor. This additional very large step down ratio becomes effective when the worm 7 is driven in the direction which in turn rotates the worm wheel 6 in the direction indicated by the arrow 0 that is in the counterclockwise direction. In this direction of rotation the ratchet wheel 61 is entrained by the pawls 601 whereby the jack wheel means 4 are likewise entrained if the clutch 62 shown in FIG. '2 is in its operative position. Accordingly, the jack wheel means 4 rotate in the direction of the arrow c3 as shown in FIG. 3 whereby the planetary gear wheel 44 is driven to rotate in the direction of the arrow b1, whereby the drum 1 is rotated in the counter-clockwise direction according to arrow a6 with the desired large step-down ratio, and whereby the drive train runs from the pawls 44] through the ratchet wheel 154, the planetary gear wheel 15 and the reversing gear wheel 14. During this type of operation or drive the disk 3 and thus the drum shaft 5 remain stationary because the pawls 431 prevent a reverse rotation of the disk 3 in the direction of the arrow 11. A direction of rotation according to arrow 0 would mean that the planetary gear wheel 43 is rotated in the direction of the arrow al, that is, in the clockwise direction. However, this is prevented because the large sun wheel 41 rotates, as mentioned above, in the counterclockwise direction whereby the planetary gear wheel 43 drives also in the counter-clockwise direction of rotation, that is, contrary to the direction of arrow a1.

It is however possible to drive the disk 3 additionally through the drum shaft 5 whereby the drive through the drum shaft is superimposed on the drive through the worm 7 and the worm wheel 6. In this manner it is possible to vary the step-down ratio applied to the drum 1. By the simultaneous driving through the worm 7 and through the drum shaft 5 it is possible to provide a continuously variable step-down ratio or transmission.

By means of the above described position of the pawls 601 as illustrated in FIG. 3, the drive through the worm 7 and the worm wheel 6 becomes effective only in one direction of rotation; namely in the direction of rotation of the worm wheel 6 according to arrow 0 as shown in FIG. 3, that is, in the counter-clockwise direction whereby the ratchet wheel 61 and with it the jack wheel means 4 shown in FIG. 2 are also entrained in the counter-clockwise direction indicated by the arrow c1 in FIG. 3 provided that the clutch is engaged.

If the worm 7 remains stationary it prevents by means of its self locking braking action that the drum 1 would rotate in the reverse direction in response to a load. Incidentally, the self locking braking action of the worm 7 could be supplemented by additional braking means which would be effective on the worm shaft. Further, a braking action may be provided by driving the worm wheel 7 in the clockwise direction contrary to the direction indicated by the arrow c whereby a sensitive backward spooling or run of the drum is accomplished with the aid of the worm 7. By changing the direction of rotation of the worm 7, it is thus possible to adjust the position of the sail attached to the sheet in a sensitive manner and even against a very large wind pressure. In view of the foregoing description it will be appreciated that the drum winch according to the invention may be modified in a plurality of suitable ways.

Among others, the following embodiments are possible.

a. The sun and planetary gear means comprise an output drive wheel 11, a disk 3, jack wheel means 4 and the sets of planetary gear means. With the aid of these elements it is possible to provide a drum winch for a large step-up transmission ratio in one direction and for a large step-down transmission ratio in the other or reverse direction of rotation of the drum shaft 5.

. b. If in addition to the elements mentioned under (a) above a slipping or torque reverse clutch is arranged between the jack wheel means and the disk 3 and a braking action is applied to the jack wheel means through pawls in one direction, it is possible to provide a large step-up transmission ratio for one rotational direction of the drum shaft 5 and to obtain a 1:1 transmission ratio in the opposite rotational direction of the drum shaft whereby in said other direction also a large step-down transmission ratio may be accomplishedfiThus, the just mentioned modification or embodiment of the invention provides three possible rotational speed ratios.

c. If in addition to the elements mentioned above under (a) or (b) a worm wheel is provided which is either connected or which may be coupled to the jack wheel means when the gear train is driven through the disk 3 or which is connected or may be coupled to the disk 3 when the gear train is driven through the jack wheel means, then it is possible to accomplish a very large step-down transmission ratio by means of which the drum winch may be rotated in the forward and reverse direction in a sensitive manner.

In view of the foregoing, it will be appreciated that instead of the disk 3 of the sun and planetary gear train the jack wheel means 4 may be driven with the aid of the drum shaft 5 whereby the components which in accordance with the described example cooperate with the jack wheel means 4 would now cooperate correspondingly with the disk 3.

FIG. 4 illustrates an embodiment of the gear train in which the jack wheel means 4 are driven and the disk 3 remains stationary. The representation has been somewhat symbolized for simplicitys sake. However, the same reference numerals have been employed for the same elements as shown in FIG. 2. According to FIG. 4 the jack wheel means 4 which is rigidly connected to the drum shaft 5 simply comprises a small sun wheel 42 having external gear teeth meshing with the

planetary gear wheels

43 and 44, which are rotatably supported in the disk 3. These

planetary gear wheels

43 and 44 are connected with the planetary gear wheels and 16 through

pawls

441 or 431, whereby a rigid connection is accomplished with regard to one rotational direction and a rotatable connection is accomplished with regard to the other rotational direction. The planetary gear wheel 15 meshes with the large sun wheel 15 having internal gear teeth whereas the planetary gear wheel 16 meshes with the small sun wheel 13 having external gear teeth. The large sun wheel 12 and the small sun wheel 13 are comprised in the drive output wheel 11 which again is formed in the face flange of the drum 1.

According to FIG. 4 the disk 3 is rotatably supported on the drum shaft 5. Further, the disk 3 is coupled with the small sun wheel 42 by means ofa slipping or torque release clutch 521. A band brake 32 is arranged to be effective on the outer circumference of the disk 3. The band brake 32 may be pressed against the disk 3 in the direction of the arrow P or the hand brake 32 may be moved off the disk 3.

By driving the small sun wheel 42 by means of the crank handle 53, the drum is driven, depending upon the direction of rotation of the drum shaft, with a stepup ratio or with a step-down ratio. These ratios are determined by the diameter ratios of the small sun wheel 42 of the jack wheel means and the large ring wheel 12 or small sun gear 13 of the output drive gear wheel. The diameter of the small sun wheel 42 of the jack wheel means is smaller than the diameter of the large ring wheel 12, however, larger than the diameter of the small sun wheel 13 of the output drive wheel.

Another embodiment comprising ajack wheel means driven by the crank handle and a stationary support structure is illustrated in FIG. 5. The basic structural features are the same as those according to FIG. 2 except that the disk 3 in FIG. 5 is itself constructed as the worm wheel 6 which is either arrested by the worm 7 or which is driven by the worm 7. The gear train according to FIG. 5 does not comprise any slipping clutches as described above. Therefore the pawls between the disk 3 and the worm wheel 6 may be obviated. Further, as mentioned above, the modification provides the arrangement of the clutch between the drum 1 and the output drive wheel 11.

The drum winch according to the invention as shown in the embodiment according to FIGS. 1 and 2 is secured to a bearing block 8 at the circumference of the housing half 21 whereby a portion of the flange screws 203 which connect the

housing halfs

21 and 22 to each other at the circumference thereof, serves simultaeously for securing the drum winch to the bearing block 8. It would also be possible to support the drum winch on its drum shaft by extending the drum shaft in one or both directions.

In view of the above, it will be appreciated that for the above described embodiments it will be sufficient if the brake cooperates with the jack wheel means or with the disk. Stated differently, it is not necessary to simultaneously also subject the drum shaft 5 to a braking action. According to the invention, the rotation of the drum shaft in both directions always causes the rotation of the drum in the take-up direction due to the ratchet mechanism incorporated in the gear train. The ratchet mechanism also assures that the drum shaft may not rotate automatically in response to the sheet pull which is effective on the drum.

It should be pointed out that in the embodiment in which the gear train comprises a sun and planetary gear means an especially large step-up transmission ratio on the one hand and a step-down transmission ratio is accomplished on the other hand because the rotation of the disk is superimposed with the rotation of the pairs of planetary gear wheels. In this embodiment the gear drive train is driven by the rotation of the disk and the driving of the pairs of planetary gear wheels about their shafts is accomplished by the supporting function of the stationary jack wheel means. 0n the other hand the just described embodiment makes it possible to construct the gear small and compact for a given step-up or stepdown transmission ratio.

The compact structure of the gear means according to the invention is also facilitated in that the jack wheel means or the power output drive wheel comprises a small sun wheel and a large ring wheel rigidly connected to the small sun wheel and in that one pair of planetary gear wheels is coupled to the large ring whee] whereas the other pair of planetary gear wheels is coupled to the small sun wheel. in this embodiment the size of the respective other gear wheel is reversed, stated differently the size of the power output drive gear or the size of the jack wheel means is advantageously selected in such a manner that it is larger than the smallsun wheel but smaller than the large ring wheel.

The power output drive gear as well as the jack wheel means may be provided with external and/or internal gear teeth. If necessary, one of the pairs of planetary gear wheels could be arranged so as not to directly mesh with the jack wheel means and with the power output drive gear wheel. In this instance a reversing gear wheel would be interposed in the drive gear train between the jack wheel means and the power output drive gear wheel, whereby such reversing gear wheel would be rotatably supported in the above mentioned disk.

In the embodiment where the jack wheel means or the power output drive gear wheel comprises a large ring wheel and a small sun wheel as described above, the large ring wheel may be provided with internal gear teeth and the small sun wheel may be provided with external gear teeth. The planetary gear wheels of the pairs of planetary gears as well as the additional reversing gear wheel if such is used, may be advantageously arranged in the intermediate space between the small sun gear and large ring wheel, whereby said planetary gear wheels mesh with said sun wheels.

An especially small gear wheel drive train which simultaneously provides a large step-down transmission ratio on the one hand and a step-up transmission ratio on the other hand may be accomplished according to the invention in that the jack wheel means as well as the power output drive gear wheel each comprise a large ring wheel having internal gear teeth and a small sun wheel having external gear teeth whereby the ring and sun wheels are rigidly connected to each other and whereby the small sun wheel of the jack wheel means is coupled with the large ring wheel of the power output drive gear wheel through one of the pairs of planetary gear wheels whereas the large ring wheel of the jack wheel means is coupled to the small sun wheel of the power output drive gear wheel through the respective pair of planetary gear wheels. In this instance a reversing gear wheel is rotatably supported in the disk between one of the sun wheels and one of the pairs of planetary gears.

Another advantage of the drum winch according to the invention is seen in that it may be extended by relatively simple means for including additional step-down or step-up transmission ratios. For example, the jack wheel means and the disk may be coupled to each other through a slip or torque release clutch, preferably through the drum shaft. Such slipping clutch prevents a relative rotation between the jack wheel means and the disk when the drum shaft rotates in the direction in which the sheet is spooled onto the drum as long as the slipping clutch does not slip in response to the tension effective on the drum. As soon as slipping occurs the rotational speed of the drum shaft is transmitted to the drum without any translation, that is, with a lzl ratio.

Another advantage of the present drum winch is seen in that it is possible in a simple manner to assure an instantaneous step-down ratio in response to the slipping of the torque release clutch without the need for applying the brake. This feature is accomplished in that the jack wheel means or the disk that is respectively the member which is not rigidly connected to drum shaft, is coupled with a ratchet wheel which is arrested in the direction of rotation which corresponds to the reverse rotation of the drum, said arresting being accomplished by means of pawls. In this embodiment the forward direction of rotation of the drum is released so that the jack wheel means or the disk may be driven in the forward direction of the drum through the slipping clutch without any relative rotation between these two members. As soon as the pull or tension of the sheet exceeds the braking force of the slipping clutch upon continued rotation of the drum shaft, the pawls engage with the ratchet wheel whereby the gear is automatically switched to the step-down transmission ratio. These features are considered to be an independent invention.

Advantageously the ratchet wheel and the jack wheel means or the disk are coupled to each other by means of a releasable clutch. This feature has the advantage that after releasing of the clutch the rotation of the drum in the reverse direction is released which prior to such release was blocked by the ratchet wheel whereby the sheet may be paid out from the drum. Depending on the adjustment of the clutch the clutch may simultaneously act as a brake.

Another advantageous construction is achieved, especially where a ratchet wheel cooperates with the jack wheel means when the ratchet wheel is axially shiftable relative to the pawls for actuating the clutch, whereby the ratchet wheel is actually supported by a pressure bearing which in turn is adjustable by means of a hand wheel supported in a thread in the housing of the gear train means. Thus, the drum shaft and the hand wheel may be operated simultaneously or alternatively whereby a sensitive adjustment of the sail may be accomplished.

In many instances it is advantageous if the clutch for releasing the reverse rotation of the drum is effectively interposed between the drum and the power output drive wheel. Particularly in this embodiment the rotation of the crank handle along with the reversely rotating drum is prevented. Thus, the crank handle may always remain attached to the drive shaft and it is not necessary to remove it for avoiding the danger ofinjury when the drum rotates in the reverse direction.

Another advantage of the invention is seen in that the present drum winch may be modified for an especially large step-down transmission ratio for driving the drum. This has the advantage that the sail may be strongly tightened even against a very large wind pressure. Such additional large step down transmission ratio is accomplished according to the invention in that the ratchet wheel is rotatably supported within a worm gear wheel in which there are installed the pawls and which is driven by the worm 7 as described above. The brake for arresting the pawls in the rotational direction in which they are to lock the ratchet wheel may in this embodiment be applied either to the worm gear wheel 6 or to the shaft of the worm. The worm could be driven either by an additional crank handle or advantageously by means of an electric drive motor. In the latter embodiment it is possible to provide a remote control for several drum winches and the sails controlled by such winches. The brake required for braking the worm gear wheel may then be accomplished by a suitable drive means, the rotation of which is prevented in the standstill.

A separate large step-down transmission ratio by means of the worm and the worm gear wheel in combination with the other drive possibilities of the drum by means of the gear drive train is especially advantageous because the simultaneous or alternate driving of the drum shaft and/or of the worm provides for a sensitive regulation of the sail adjustment. The sail may be pulled tight or slackened depending on the direction of the drive rotation of the worm. In this embodiment additional continuous speed ratio variations for the drum are accomplished when the drum shaft and the worm are driven simultaneously. Here again, it is considered that this arrangement and the effect of the worm wheel constitute a separate invention within the framework of the present application.

in order to arrest the worm wheel when the worm is stationary, it is suggested according to the invention to provide the worm with a self-locking feature relative to the worm wheel gear.

In view of the foregoing. it will be seen that the drum winch according to the invention in its simplest embodiment provides a step-up transmission and a step down transmission which become effective depending upon the direction of rotation of the drive crank handle. If in addition a slipping clutch is installed between the disk and the jack wheel means, a lzl rotational speed ratio is also accomplished. Where, for example, the crank handle drives the disk, and the jack wheel means are arrested only in the direction of rotation corresponding to the reverse direction of rotation of the drum, the sail may be pulled tight quickly, for example, when the winch is used for the main sheet, by rotating the crank handle quickly in said one direction of rotation whereby said step-up ratio becomes effective. As soon as the direction of rotation is reversed, a 1:1 transmission ratio is established whereby the sail may be pulled tight further to an extent which is determined by the slipping strength of the slipping clutch which will slip when the wind pressure exceeds such strength. As soon as the wind pressure exceeds said value, the slipping clutch begins to slip whereby automatically the step-down ratio becomeseffective while the direction of rotation of the crank handle remains the same. As a result, the sail may be pulled tight against a large wind pressure due to said step down ratio.

If in addition a worm gear drive is installed for the ratchet wheel as described above, then the sail may be regulated in a sensitive manner in both directions and against large wind. pressure.

Although the invention has been described with reference to specific example embodiments, it is to be understood, that it is intended to cover all modifications and equivalents within the scope of the appended claims.

What is claimed is:

1. In a drum winch wherein a drum is rotatably mounted relative to a drum shaft which shaft is rotatable selectively in both directions, said drum being rotatable by toothed wheel gear means including a ratchet mechanism whereby the direction of drum rotation is the same independent of the direction of shaft rotation and whereby due to said ratchet mechanism the drum may be rotated with different rotational speeds depending upon the direction of rotation of the drum shaft, and wherein releasable brake means are arranged for cooperation with said drum when the drum rotates reversely, the improvement comprising a disk, first means for controlling the position of said disk relative to said drum shaft, a first pair of planetary gear wheels, means for rotatably supporting said first pair of planetary gear wheels in said disk, a second pair of planetary gear wheels, means for rotatably supporting said second pair of planetary gear wheels in said disk, jack wheel means, second means for controlling the position of said jack wheel means relative to said drum shaft, said first and second pairs of planetary gear wheels being arranged relative to said jack wheel means for intermeshing with the jack wheel means, drive gear means coupled to said drum, one of said pairs of planetary gear wheels being arranged for coupling said jack wheel means to said drive gear means in a step-up sense, the other of said pairs of planetary gear wheels being arranged for coupling said jack wheel means to said drive gear means in a reduction sense, said first and second pairs of planetary gear wheels being arranged to counteract each other for any rotational direction of the drum shaft, said ratchet mechanism being arranged for interrupting the driving connection between one or the other of the pairs of planetary gears and the respective drive gear means in response to the rotational direction of the drum shaft.

2. The drum winch according to claim I, wherein said toothed wheel gear means comprise sun and planetary gear means.

3. The drum winch according to claim 1, wherein said first means for controlling the position of said disk relative to said drum shaft comprise means for securing said disk on said drum shaft to rotate with said drum shaft.

4. The drum winch according to claim 3, wherein said second means for controlling the position of said jack wheel means relative to said drum shaft comprise means for arresting the jack wheel means against rotation, said drum shaft being rotatable relative to said jack wheel means.

5. The drum winch according to claim 3, wherein said second means for controlling the position of said jack wheel means relative to said drum shaft comprise brake means for applying a braking force to said jack wheel means said drum shaft being rotatable relative to said jack wheel means.

6. The drum winch according to claim 1, wherein said second means for controlling the position of said jack wheel means relative to said drum shaft comprise means for securing said jack wheel means to said drum shaft to rotate with said drum shaft.

7. The drum winch according to claim 6, wherein said first means for controlling the position of said disk relative to said drum shaft comprise braking means for applying a braking force to said disk, said drum shaft being rotatable relative to said disk.

8. The drum winch according to claim 6, wherein said first means for controlling the position of said disk relative to said drum shaft comprise arresting means for arresting the disk, said drum shaft being rotatable relative to said disk.

9. The drum winch according to claim 1, wherein said jack wheel means comprise a small sun wheel and a large ring wheel rigidly connected to each other, said drum winch further comprising means for coupling one of said pairs of planetary gear wheels to the large ring wheel and means for coupling the other pair of said planetary gear wheels to the small sun wheel.

10. The drum winch according to claim 9, wherein said large ring wheel comprises radially inwardly facing gear teeth whereas said small sun wheel comprises radially outwardly facing gear teeth.

ll. The drum winch according to claim 1, wherein said drive gear means comprise a small sun wheel and a large ring wheel rigidly connected to each other, said drum winch futher comprising means for coupling one of said pairs of planetary gear wheels to the large ring wheel and means for coupling the other pair of said planetary gear wheels to the small sun wheel.

12. The drum winch according to claim 11, wherein said large ring wheel comprises radially inwardly facing gear teeth whereas said small sun wheel comprises radially outwardly facing gear teeth.

13. The drum winch according to claim 1, wherein the jack wheel means comprise a first large ring wheel with radially inwardly facing gear teeth and a first small sun wheel with radially outwardly facing gear teeth, said drive gear means comprising a second large ring wheel with radially inwardly facing gear teeth and a second small sun wheel with radially outwardly facing gear teeth, said first large ring and small sun wheels being rigidly connected to each other, said second large ring and small sun wheels being rigidly connected to each other, said first small sun wheel being coupled to the second large ring wheel by means of one of said pairs of planetary gear wheels, said first large ring wheel being coupled to the second small sun wheel by means of the other of said pairs of planetary gear wheels, said winch further comprising a reversing gear, and means for rotatably supporting said reversing gear in said disk, said reversing gear being arranged for cooperation with one of said sun wheels and one of said pairs of planetary gear wheels.

14. The drum winch according to claim 1, further comprising a torque release clutch positioned to couple said jack wheel means and said disk to each other.

15. The drum winch according to claim 14, wherein said torque release clutch is positioned to couple said disk and said jack wheel means to each other through said drum shaft.

16. The drum winch according to claim 1, further comprising a ratchet wheel coupled to said jack wheel means, and pawl means arranged for arresting said jack wheel means through said ratchet wheel against rotation in a direction corresponding to the reverse rotational direction of said drum.

17. The drum winch according to claim 16, further comprising a releasable clutch for coupling said jack wheel means and said ratchet wheel to each other.

18. The drum winch according to claim 17, further comprising means for supporting said ratchet wheel for axial shifting relative to said pawl means to permit actuating said releasable clutch, said supporting means comprising gear box means with a threaded axial bore, a bearing for taking up axial pressure, threaded position adjusting means received in said threaded axial bore of said gear box means for adjustably supporting said axial pressure bearing means which bear against said ratchet wheel.

19. The drum winch according to claim 16, further comprising a worm gear means including a worm and a worm gear wheel, means for rotatably supporting said ratchet wheel inside said worm gear wheel, and means for journaling said pawl means also inside said worm gear wheel.

20. The drum winch according to claim 19, wherein said worm is self-locking relative to said worm gear wheel.

21. The drum winch according to claim 1, further comprising a ratchet wheel coupled to said disk, and pawl means positioned for arresting said disk through said ratchet wheel against rotation in a direction corresponding to the reverse rotational direction of said drum.

22. The drum winch according to claim 1, wherein said pairs of planetary gear wheels include respective shafts, and wherein said ratchet mechanism comprises ratchet wheel and pawl means which are arranged between one of said planetary gear wheels and the respective shaft of the pairs of planetary gear wheels.

23. The drum winch according to claim 1, wherein said drive gear means comprise an outer circumferential collar, said collar providing a bearing means for said jack wheel means.

24. The drum winch according to claim 23, further comprising gear box means and roller means for supporting said outer circumferential collar of said drive gear means in said gear box means.

25. The drum winch according to claim 1, further comprising a supporting bearing block, gear box means, and means for securing said gear box means to said bearing block.

26. The drum winch according to claim 1, wherein said drum shaft extends axially through the entire drum and the wheel gear means whereby both ends of said drum shaft are provided with means for cooperating with a crank handle.

27. The drum winch according to claim 1, further comprising torque release clutch means positioned to operatively couple said jack wheel means and said disk to each other, means for axially supporting said torque release clutch means on the drum shaft, housing means, and means for axially adjusting the position of said drum shaft in said housing whereby the braking force of said torque release clutch is adjustable.

28. The drum winch according to claim 1, further comprising a releasable braking clutch for coupling the drum to the drive gear means.

Claims

2. The drum winch according to claim 1, wherein said toothed wheel gear means comprise sun and planetary gear means.

11. The drum winch according to claim 1, wherein said drive gear means comprise a small sun wheel and a large ring wheel rigidly connected to each other, said drum winch futher comprising means for coupling one of said pairs of planetary gear wheels to the large ring wheel and means for coupling the other pair of said planetary gear wheels to the small sun wheel.