EP2592038A1 - Treuil - Google Patents

Treuil Download PDF

Info

Publication number
EP2592038A1
EP2592038A1 EP12191934.4A EP12191934A EP2592038A1 EP 2592038 A1 EP2592038 A1 EP 2592038A1 EP 12191934 A EP12191934 A EP 12191934A EP 2592038 A1 EP2592038 A1 EP 2592038A1
Authority
EP
European Patent Office
Prior art keywords
winch
gear
motor
rope
winding
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12191934.4A
Other languages
German (de)
English (en)
Other versions
EP2592038B1 (fr
Inventor
Robert Graham Fields
Oliver Peter Gregory FALCONER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Lewmar Ltd
Original Assignee
Lewmar Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Lewmar Ltd filed Critical Lewmar Ltd
Priority to SI201230538A priority Critical patent/SI2592038T1/sl
Publication of EP2592038A1 publication Critical patent/EP2592038A1/fr
Application granted granted Critical
Publication of EP2592038B1 publication Critical patent/EP2592038B1/fr
Priority to HRP20160419TT priority patent/HRP20160419T1/hr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B66D1/7421—Capstans having a vertical rotation axis
    • B66D1/7436—Capstans having a vertical rotation axis drivable by both motor and manually
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/14—Power transmissions between power sources and drums or barrels
    • B66D1/24—Power transmissions between power sources and drums or barrels for varying speed or reversing direction of rotation of drums or barrels, i.e. variable ratio or reversing gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B66D1/7484—Details concerning gearing arrangements, e.g. multi-speed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/60—Rope, cable, or chain winding mechanisms; Capstans adapted for special purposes
    • B66D1/74—Capstans
    • B66D1/7494—Self-tailing capstans
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/01—Winches, capstans or pivots
    • B66D2700/0108—Winches, capstans or pivots with devices for paying out or automatically tightening the cable
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/01—Winches, capstans or pivots
    • B66D2700/0125—Motor operated winches

Definitions

  • the present invention relates to winches for watercraft, particularly sailboats.
  • the invention has particular, but not exclusive, applicability to winches that are powered by a motor and capable of being wound by operation of the motor in the forwards direction and in the reverse direction.
  • Winches are well known for use in manoeuvring the sails on a sailboat by controlling the tension on the boat's running and rigging lines. These lines for example may be sail sheets and sail halyards, which are referred to collectively in this disclosure as "ropes". Each rope can be considered to have a loaded end (connected to a sail) and an unloaded end (the “tail” of the rope, which may be collected in a cockpit of the boat).
  • a typical winch includes a rotatable drum mounted with respect to a deck of the boat.
  • the loaded end of the rope is drawn onto the drum by rotation of the drum. Hauling the loaded end of the rope onto the drum in this way is referred to in this disclosure as "forward winding" of the winch.
  • This rotation is typically clockwise rotation, although this is not essential.
  • Rotation of the drum may be achieved by hand-cranking of the winch using a winch handle inserted into a drive socket at the upper end of the winch.
  • the winch may be rotated by operation of an electric or hydraulic motor. Reduction gearing is provided in order to improve mechanical advantage and allow the rope to be drawn onto the drum even under heavy loads.
  • At least two (and sometimes three or four) reduction gear ratios there may be provided at least two (and sometimes three or four) reduction gear ratios.
  • the relevant gear is typically selected simply by the user driving the winch handle in either the clockwise or anticlockwise direction.
  • the diameter of the winch drum typically enlarges slightly from the axial lower end of the drum towards the axial upper end of the drum. This encourages the loaded end of the rope to be located at the axial lower end of the drum.
  • the three or four turns of rope on the drum typically provide a great deal of frictional hold on the rope.
  • the unloaded end of the rope may therefore be simply held in a cleat in order to retain the rope on the winch and retain the load on the loaded end of the rope.
  • the self-tailing arrangement is typically located at the upper end of the winch.
  • the self-tailing arrangement has a pair of opposed rope lock rings with optional gripping features.
  • the rope lock rings are typically spring biased towards each other to allow a range of rope diameters to fit into the channel defined between the rope lock rings and be gripped by the rope lock rings.
  • the rope lock rings rotate with the drum.
  • a feeder arm is provided in order to guide rope from the upper end of the drum into the channel between the rope lock rings. The feeder arm is fixed with respect to the winch, so that the feeder arm does not rotate with the winch drum or the rope lock rings.
  • the rope then passes along the channel between the rope lock rings for nearly a full turn around the winch, the rope exiting the channel at an unloaded end of the rope adjacent the feeder arm, optionally guided out of the channel between the rope lock rings by a suitable guide feature typically known as a stripper.
  • a suitable guide feature typically known as a stripper.
  • Forward winding of the winch therefore draws loaded rope onto the lower end of the drum, thereby reducing the length of rope that is loaded between the winch and the sail.
  • An amount of rope corresponding to the amount drawn onto the winch drum is guided into the self-tailing unit by the feeder arm.
  • a corresponding amount of rope is paid out the self-tailing unit via the stripper and into, e.g. the cockpit of the boat, thereby to increase the length of rope that is unloaded.
  • the rope is gripped (cleated) in the self-tailing arrangement by the rope lock rings.
  • reverse winding relates to controlled rotation of the winch drum in the opposite direction to forward winding, reverse winding thereby increasing the length of loaded rope and decreasing the length of unloaded rope.
  • providing a winch with powered reverse winding capability is relatively complex since typically the additional capability of the winch must not compromise the primary function of the winch to haul in loaded rope as efficiently as possible.
  • GB-A-2276137 discloses a powered winch which has an electric motor capable of driving the winch in the forward direction with different gear ratios. Reverse winding of the winch is made possible by the inclusion of a sun and planetary gear mechanism controlled by the motor. This arrangement is complex and would be difficult to manufacture and assemble.
  • Operation of electrically powered winches is typically carried out by activation of suitable switches in order to supply power to the electric motor.
  • suitable switches for some known powered winches, it is necessary to provide several controls, in order to for the user to select the gear ratio to be used by the winch and in order for the user to activate power to the winch.
  • a control (which may be mechanical or electrical) may be provided in order to select one of a several modes of operation e.g. "forward wind only, different speeds" or "forward/reverse wind”.
  • One or more further controls (typically one or more switches) must then be activated in order to deliver power to the electric motor, allowing the user to select, for example "fast forward wind”, “slow forward wind” or “reverse wind”, but only after operation and/or inspection of at least two controls.
  • Such a non-intuitive control system can be difficult for the user to operate in challenging sailing conditions.
  • WO2011/005172 Another known winch is disclosed in WO2011/005172 .
  • the winch is disclosed as being capable of powered forward winding and powered reverse winding, however it is not explained in WO2011/005172 how gearing may be arranged in the winch in order to allow powered reverse winding.
  • WO2011/005172 discloses a self-tailing arrangement having an upper rope lock ring and a lower rope lock ring, both lock rings being rotatable with the winch drum.
  • the lower rope lock ring is held in a fixed axial position (but is rotatable as previously mentioned) and the upper rope lock ring is skew spring-mounted.
  • the upper rope lock ring is subjected to a dynamic asymmetric motion pattern so that the channel between the rope lock rings is at its widest adjacent the self-tailing arm and at its narrowest diametrically opposite the self-tailing arm.
  • This dynamic asymmetric motion pattern is provided by a forcing means inserted into the channel between the rope lock rings forcing the rope lock rings apart against the force of the springs acting on the upper rope lock ring.
  • the rope lock rings additionally have a bulge of uniform height formed around the self-tailing arrangement.
  • the present invention has been devised in order to address at least one of the above problems.
  • the present invention reduces, ameliorates, avoids or overcomes at least one of the above problems.
  • the present inventors have realised that it would be advantageous to provide a self-tailing arrangement that provides improved performance during reverse winding of the winch, particularly with respect to reliability of operation and ease of insertion of the rope by the user into the self-tailing arrangement.
  • the present invention provides a self-tailing winch for a sailboat comprising:
  • the present invention provides a method of operating a winch according to the first aspect, the method including the step of reverse winding the winch.
  • At least one of the upper and lower rope guide rings is spring mounted to be urged towards the other.
  • the spring mounting of the retainer guide is via the same spring mounting as the upper and/or lower rope guide rings.
  • the width of the rope guide channel is constant around the self-tailing arrangement during normal use of the winch. This allows the self-tailing arrangement to exert a consistent and uniform grip on the rope along the length of the rope held in the rope guide channel.
  • the retainer lip extends for less than about 180° circumferentially around the self-tailing assembly. More preferably, the retainer lip extends for less than about 120° around the self-tailing assembly. The retainer lip preferably extends for more than about 45° around the self-tailing assembly. More preferably, the retainer lip extends for more than about 90° around the self-tailing assembly.
  • the opening for conducting rope is defined at one side by a portion of the retainer lip and at the opposite side by a separate feature.
  • the separate feature may be an extractor located in the rope guide channel.
  • the separate feature may be the feeder arm.
  • the retainer lip has an asymmetric profile when viewed radially.
  • the retainer lip preferably has a reverse winding guide portion. This is located adjacent the opening though which rope is conducted.
  • a tapered portion At the opposite circumferential end of the retainer lip there is preferably provided a tapered portion.
  • the reverse winding guide portion preferably has a sloped profile from the opening to the full axial extent (i.e. height or depth) of the retainer lip.
  • the tapered portion preferably has a sloped profile from the full axial extent of the retainer lip to the minimum axial extent of the retainer lip.
  • the slope of the reverse winding guide portion is preferably steeper than the slope of the tapered portion.
  • the effect of the steeper slope of the reverse winding guide portion is that during reverse winding, the rope is easily guided behind the retainer lip and into the rope guide channel.
  • the steep slope here means that the rope cannot easily accidentally be moved over the retainer lip to come out of the rope guide channel during reverse winding.
  • the reverse winding portion will allow the user to extract the rope from the rope guide channel from the unloaded end of the rope by manually diverting the unloaded rope over the retainer lip and out of the rope guide channel. This can be achieved without the user needing to touch the retainer lip.
  • the effect of the lower slope of the tapered portion is intended to be the opposite of the reverse winding portion, allowing the rope to fit over the retainer lip and press the retainer guide against its spring mounting during forward winding.
  • the user may wind the rope a suitable number of turns around the winch drum and then over the feeder arm and into the rope guide channel.
  • the winch is to be driven manually, the user may fit the rope into the full circumference of the rope guide channel by using the rope to cam open the retainer guide using the tapered portion and insert rope into the rope guide channel behind the retainer lip.
  • the winch When the winch is to be driven by the motor, it may be preferred for the user to fit the rope only into the part of the rope guide channel adjacent the feeder arm and then to forward wind the winch drum in order to allow the rope to the be fitted automatically into the full circumference of the rope guide channel.
  • the tapered portion assists with this by allowing the rope, as it is driven around the self-tailing arrangement, to cam open the retainer guide using the tapered portion, the retainer guide thereby being displaced axially against its spring mounting and insert rope into the rope guide channel behind the retainer lip.
  • the end result is preferably that the rope extends around the rope guide channel, behind the retainer lip and out of the opening adjacent the reverse winding guide portion.
  • the steepness of the retainer lip at a particular location can be considered to be the minimum angle subtended between a tangent to the retainer lip at that location and the plane of the rope guide channel.
  • the steepness of the retainer lip at the reverse winding guide portion is at least 30°, more preferably at least 45°, still more preferably at least 55°.
  • the steepness of the retainer lip at the tapered portion is at most 20°, more preferably at most 15°, still more preferably at most 10°.
  • the retainer guide is preferably held stationary on rotation of the drum by locking engagement with the feeder arm. This provides a convenient arrangement to ensure that the opening from the retainer guide from which unloaded rope is emitted is facing a convenient direction for the user, e.g. towards a cockpit of the sailboat.
  • the locking engagement with the feeder arm allows axial movement of the retainer guide against its spring mounting.
  • a suitable locking engagement may be provided by engagement of a projection (e.g. on the retainer guide) with a corresponding axial slot (e.g. on the feeder arm).
  • the retainer guide (and particularly the retainer lip) is substantially fixed against radial movement.
  • the radial direction is to be taken as a direction perpendicular to the axis of rotation of the winch.
  • the retainer guide is provided as a component that extends around the full circumference of the self-tailing assembly, e.g. in the form of a ring. This allows for convenient association of the retainer guide with the upper or (more preferably) the lower rope lock ring and helps to provide a structure that prevents radial displacement of the retainer guide with respect to the rope guide channel.
  • the self-tailing arrangement preferably includes a forward wind rope extractor.
  • the use of an extractor is known in self-tailing arrangements in order to extract rope from the rope guide channel during forward winding of the winch.
  • the forward wind extractor typically takes the form of a wedge extending from the feeder arm and into the rope guide channel in a direction opposite to the forward wind direction. This acts to prevent rope from jamming behind the feeder arm during forward winding.
  • the self-tailing arrangement preferably also includes a reverse wind rope extractor. In view of the use of the winch for reverse winding, this is preferred in order to prevent rope from becoming jammed behind the feeder arm during reverse winding.
  • the reverse wind extractor typically takes the form of a wedge extending from the feeder arm and into the rope guide channel in a direction opposite to the reverse wind direction. Conveniently, the reverse wind extractor may be formed integrally with the forward wind extractor.
  • the present inventors have devised a mechanical driving arrangement for a winch, the driving arrangement being relatively simple but efficient and providing multi-speed manual operation combined with motorised capability for forward and reverse winding.
  • winches which provides (at least) two forward winding winch speeds under manual operation and forward winding motorised operation.
  • winches are available from Lewmar Limited under the brand name EVOTM.
  • winches typically provide the two forward winding speeds under manual operation using two drive trains, selectable by the direction of cranking of the winch, the two drive trains incorporating respective unidirectional drive means set in opposite senses to each other.
  • a motor is operatively connected to a motor gear shaft via gearing, the motor gear shaft driving forward winding of the drum.
  • winches are not capable of powered reverse winding.
  • the present invention provides a third unidirectional drive means linked to the motor gear shaft, rotation of the third unidirectional drive means by the motor gear shaft in one direction causes forward winding of the winch drum and rotation of the unidirectional drive means by the motor gear shaft in the opposite direction allows reverse winding of the winch drum.
  • a winch for a sailboat comprising:
  • the present invention provides a method of operating a winch according to the third aspect, the method including the step of reverse winding the winch.
  • a third unidirectional drive means provides the advantage that there is no need to provide releasable engagement between the drive trains and the motor gear shaft, e.g. by means of operation of a clutch or similar.
  • reverse winding of the winch drum occurs only when there is a reverse winding torque on the drum.
  • the reverse winding torque can be applied manually (e.g. by a user turning the winch drum in reverse) but more preferably the reverse winding torque is applied by a load on a rope wrapped around the drum. In this way, the reverse winding of the winch drum preferably occurs only when there is a rope under load wrapped around the winch drum.
  • the third unidirectional drive means has a first part and a second part:
  • first and second unidirectional drive means may have a similar configuration to the third unidirectional drive means, i.e. each having first and second parts that engage with each other in one rotation direction and freewheel relative to each other in the opposite rotation direction.
  • first and second unidirectional drive means are set in opposite senses to each other, so that when one is engaged, the other is freewheeling.
  • the unidirectional drive means includes a ratchet track and a corresponding arrangement of pawls.
  • the first and second parts of the third unidirectional drive means are typically engaged to rotate together.
  • the first and second parts of the third unidirectional drive means are engaged to rotate together. This is perhaps counterintuitive, since it would be expected that reverse winding of the winch drum would be achieved by allowing freewheeling of the third unidirectional drive means. However, this is not preferred because this would lead to uncontrolled let-out of loaded rope from the winch drum, which would be unsafe unless additional braking means were provided for braking the reverse winding of the winch drum.
  • having the first and second parts of the third unidirectional drive means engaged to rotate together during reverse winding means that the speed of reverse winding can be controlled by the motor, so that no additional braking means is required.
  • the motor gear shaft is driven by the motor via worm gearing so that the motor gear shaft is rotationally locked when the motor is not operated. This in turn locks the winch drum against reverse winding when the motor is not operated.
  • reverse operation of the motor results in relative rotation of the first and second parts of the third unidirectional drive means in a freewheel configuration.
  • the unidirectional drive means is provided by a ratchet and pawl arrangement or similar, this results in an audible clicking sound to indicate to the operator that the reverse operation of the motor is not being matched by reverse winding of the winch drum.
  • the first gearing ratio is higher than the second gearing ratio.
  • the manual drive spindle is typically driven by means of a crank handle.
  • the crank handle may be removably inserted into a corresponding drive socket, typically formed at the top of the winch.
  • the manual drive spindle is provided with a spindle gear wheel which engages with gear wheels of the first and second drive trains simultaneously.
  • Rotation of the manual drive spindle (and thus the spindle gear wheel) in the reverse direction typically drives rotation of the first unidirectional drive means in the forwards direction and causes the second unidirectional drive means to freewheel.
  • Rotation of the manual drive spindle (and thus the spindle gear wheel) in the forwards direction typically drives rotation of the second unidirectional drive means in the reverse direction and causes the first unidirectional drive means to freewheel.
  • reverse winding torque on the winch drum urges the first and second unidirectional drive means so that the spindle gear wheel locks relative rotation of said gear wheels of the first and second drive trains, and thus prevents reverse winding of the winch drum.
  • the spindle gear wheel is moveable into and out of engagement with at least one of said gear wheels of the first and second drive trains.
  • the spindle gear wheel is moveable into and out of engagement with both of said gear wheels of the first and second drive trains.
  • the spindle gear wheel is moveable axially along the principal axis of the manual drive spindle.
  • the spindle gear wheel is out of engagement when the crank handle is not located in the drive socket of the winch. In this way, location of the crank handle in the winch preferably determines whether or not reverse winding of the winch drum is possible.
  • a plunger for axial travel along the manual drive spindle.
  • the plunger preferably has first spring means for urging the spindle gear wheel towards engagement.
  • the plunger preferably has second spring means for urging the plunger upwards in the manual drive spindle.
  • the effect of these first and second spring means together is preferably that when the crank handle is not located in the drive socket, the second spring means urges the plunger upwards and so the spindle gear wheel out of engagement.
  • the second spring means is preferably compressed and the plunger depressed, the first spring means therefore urging the spindle gear wheel into engagement with the gear wheels of the first and second drive trains.
  • the advantage of providing the first spring means is that the gear wheels of the first and second drive trains may not be in a suitable position to accept the spindle gear wheel. Therefore the first spring means urges the spindle gear wheel into engagement at the next available opportunity on movement of the first and/or second drive trains.
  • the present inventors have realised that the mechanical arrangement to allow the spindle gear wheel to be removed from the first and/or second drive trains represents a development of the invention that may be independent of the linkage used to connect the motor gear shaft to drive forwards and reverse winding of the drum.
  • a winch for a sailboat comprising:
  • the present invention provides a method of operating a winch according to the fifth aspect, the method including the step of moving the spindle gear wheel out of engagement with at least one of said gear wheels of the first and second drive trains and reverse winding the winch under motor-control.
  • winch arrangements for use on sailboats that have advantages for the operator compared with known winch arrangements.
  • reverse winding of the winch drum is advantageously assisted by the tangential load on the winch drum applied by loaded rope wrapped around the winch drum.
  • this reverse winding torque can be used to power reverse winding, the speed of the reverse winding being controlled by the motor.
  • a winch for a sailboat comprising:
  • the present invention provides a method of operating a winch according to the seventh aspect, the method including the step of reverse winding the winch.
  • the reverse-winding torque is applied by loaded rope wrapped around the winch drum.
  • a winch for a sailboat comprising:
  • the present invention provides a method of operating a winch according to the ninth aspect, the method including the step of locating a crank handle in the drive socket of the winch.
  • the winch is still capable of motor-operated forward winding. This is advantageous since it allows the operator to wind in rope quickly and conveniently using a combination of motor power and manual power, without the need for removal of the handle from the winch in order to operate the motor.
  • the motor when the crank handle is located in the drive socket, the motor can be driven in a reverse-winding direction, and non-reverse winding of the winch drum is indicated to the operator by an audible signal.
  • the locking means is a mechanical locking means that prevents the reverse motor drive from being transmitted to the winch drum.
  • an audible signal preferably a mechanically-generated audible signal
  • the audible signal is a clicking sound of a unidirectional drive means in freewheel.
  • the audible signal may be a clicking sound of a ratchet operating in freewheel.
  • the present inventors have further realised that forward and reverse winding of known powered winches is typically carried out using relatively non-intuitive control systems which can be difficult to operate in challenging sailing conditions.
  • a winch arrangement for a sailboat comprising:
  • the present invention provides a method of operating a winch arrangement according to the eleventh aspect, the method including the step of activating the reverse control to reverse wind the winch.
  • the user is presented with an exceptionally straightforward control means, typically one button (or switch) to activate forward winding and one, different, button (or switch) to activate reverse winding.
  • an exceptionally straightforward control means typically one button (or switch) to activate forward winding and one, different, button (or switch) to activate reverse winding.
  • One-handed operation is important for challenging sailing conditions, where the other hand may be needed to support the user.
  • Simple and intuitive operation is important where the user (e.g. not the owner of the sailboat but a crew member) is operating the winch for the first time.
  • any aspect of the invention may be combined with any other aspect of the invention, e.g. in preferred embodiments of winches and winch arrangements.
  • Any aspect of the invention may have any one or, to the extent that they are compatible, any combination of the any of the optional features set out with respect to any aspect of the invention.
  • Fig. 1 shows a self-tailing winch 1 with a rope guide channel 2 and winch drum 3 borne on a stationary column 4 and driven by a central input drive shaft (manual drive spindle) 5 through a two-speed gear train seen in the lower part of the winch and mounted on its base 6.
  • the self-tailing arrangements and the means by which the drum is supported on the column are not described here in detail.
  • the winch is of a type wherein the drum is driven in one direction at successively different speed ratios automatically by reversal of the input drive shaft 5.
  • the Drive is communicated from that shaft via gear teeth 7 (formed by axial grooves formed into the diameter of the shaft 5 at its lower end) and each permanently meshing with a gear of both of the drive trains, which include respectively a first ratchet gear 8,12 (first unidirectional drive means) and a second ratchet gear 9,13 (second unidirectional drive means).
  • the first ratchet gear is mounted on axle 10 and the second ratchet gear on shaft 11.
  • the first ratchet gear has a first part 12 and the second ratchet gear 9 also has a first part 13, gear teeth on the outside of the parts 12,13 being in permanent meshing engagement with each other, the angular arrangement of axles 10,11 being seen more clearly in Fig. 3 .
  • the second part 8 of the first gear and second part 9 of the second gear both mesh with the teeth 7 on the shaft.
  • the parts 9,13 and 8,12 respectively have unidirectional coupling between them which are formed by a ratchet track 14,15 on the parts 12,13, and pawls 16,17 on the parts 8 and 9. These are set to drive in respectively opposite senses of rotation and the arrangement is such that when the input drive shaft 5 is first turned in an anti-clockwise direction (a keyed crank handle (not shown) being fitted in the socket in the head of the shaft for this purpose) drive is transmitted from the teeth 7 on the shaft to gear part 8 which through its pawl 16 and ratchet track 14 drives the gear part 12 which is permanently meshed with an internal gear track 18 on the inside of the base of the drum 3.
  • the shaft also rotates the gear part 9 clockwise but the pawls and ratchets 15,17 being oppositely set no drive is transmitted to the gear part 13 which is therefore free to rotate, being driven by the part 12.
  • the drive is taken up through the pawl 17 and the ratchet track 15 to the gear part 13, which, meshing with the gear part 12 of the other ratchet gear causes drive to be transmitted through that to the gear track 18 in the drum.
  • ratchets and pawls 14,16 are not transmitting drive and are clicking past each other, and gear parts 8,12 are counter-rotating.
  • both the ratchet gears is designed to minimise eccentricity and friction particularly when not transmitting drive through their own pawl and ratchet drives.
  • the first gear is made up of parts 8 and 12 the part 12 which provides the track of teeth has a hub with a central sleeve 20 borne through either a solid or a rolling bearing 21 on the surface of the axle 10.
  • a flange then extends to the skirt 22 forming the outer periphery of this ratchet gear part and on the outer face of which are formed the gear teeth.
  • On its peripheral inner face are formed the ratchets of the ratchet track 14.
  • the other part 8 of this gear has also a sleeve within its gear track and this is mounted directly on the outer periphery of the sleeve 20 and is rotatable about it.
  • a somewhat larger diameter sleeve projects downwardly at 23 into the recess formed between the sleeve 20 and the outer peripheral skirt 22 of the first gear part.
  • Spring loaded pawls 16 are mounted on this downwardly projected part 23 for engagement with the ratchet track 14 upon appropriate drive of the two parts.
  • the gear made up of gear parts 9,13 has gear part 13 being borne directly on its shaft 11 and providing an outer peripheral skirt 25 upon the outer periphery of which the gears are formed and on the inner periphery of which is seen the ratchet track 15.
  • the gear part 9 is journalled on the shaft 11 through a sleeve or rolling contact bearing 26 and offers a downwardly projecting sleeve part 27 within which are pivotally housed the pawls 17.
  • the two parts of the ratchet gear are rendered independent of each other in the sense of one not having to bear any eccentric load exerted on the other.
  • Fig. 2 shows a simple non-self-tailing winch.
  • the central shaft referred to as 5 once more has gear teeth 7 which engages on the one hand with a gear part 8 of a first ratchet gear 8,12 indistinguishable in construction and function, to that described with respect to Fig. 1 .
  • the outer gear with which the teeth 7 mesh and which is mounted on an axle 11 as before shows however how the positioning and journalling of the two gear parts may be in effect inverted.
  • the gear part here referred to as 9' although functionally identical to the gear part 9 of the winch of Fig. 1 has a conformation virtually identical to that of gear part 13 of the first embodiment, while the gear part here referred to as 13' has a conformation in function virtually identical with that of gear part 9 of the winch of Fig. 1 .
  • the functioning of the winch of Fig. 2 is exactly the same in terms of its drive trains as that of Fig. 1 . It is noted that different unidirectional links between the parts of the drive trains can be used to replace the ratchet and pawl mechanisms, e.g. camming roller or rocker catch arrangements can be used.
  • Known winches provide a development of the type of winch illustrated in Figs. 1-3 , in terms of providing motorised operation in addition to manual operation.
  • Such winches provide a motor driving a motor gear shaft (not shown in Figs. 1-3 ) via a worm gear mechanism.
  • CW clockwise
  • ACW gear 8 anticlockwise
  • ACW gear 9 anticlockwise
  • Gear 8 freewheels inside its ratchet track and so the first drive train does not drive the winch drum.
  • gear 9 turning ACW engages its ratchet track, turning gear 13' ACW.
  • gear 12 (the main drive gear) CW which drive the winch drum CW.
  • Gear 12 can turn CW relative to gear 8 due to freewheeling of the ratchet track with respect to gear 8.
  • manual turning of the manual drive spindle 5 ACW has the effect of allowing the second gear train to freewheel but driving rotation of the winch drum CW at a different gearing ratio via the first drive train.
  • the motor gear shaft may be linked into the first or second drive trains.
  • the motor gear shaft is linked into the second drive train for its additional mechanical advantage.
  • gear 13' is driven by the motor gear shaft.
  • ACW rotation of gear 13' by the motor drive shaft turns main drive gear 12 CW and so the winch drum CW.
  • gear 13' being allowed to freewheel inside ratchet track 9.
  • any attempt to turn gear 13' CW by the motor gear shaft is impossible because CW rotation of gear 13' would be coupled to gear 9' by the ratchet, but gear 9 is prevented from CW rotation by engagement with manual drive spindle 5 which cannot be driven ACW by gear 9' because this would in turn drive gear 8 CW which is prevented by the combination of the ratchet track inside gear 8 and main drive gear 12 engaging directly with gear 13'.
  • reverse winding of the winch using the motor (or via manual power) is prevented.
  • Figs. 4-12 illustrate a preferred embodiment of the invention. This can be described generally first with reference to Fig. 17 .
  • Winch 200 has a winch drum 202 rotatable about a principal axis with respect to a support (not shown in Fig. 17 ).
  • Winch drum 202 has a rope-receiving surface of frustoconical shape, the diameter of the rope-receiving surface increasing with axial height up the rope-receiving surface in a known way in order to ensure that the most heavily-loaded turn of rope is located towards the base of the rope-receiving surface.
  • a skirt portion 204 of the winch is formed towards the base of the winch.
  • the winch is mounted on a base support 206 which is fixed with respect to a deck (not shown) of a sailboat (not shown).
  • Base support 206 is connected to a motor gear shaft housing 208 which in turn is connected to motor worm gear housing 210 which houses a worm gear arrangement to be driven by a drive shaft (not shown in Fig. 17 ) of motor 212.
  • Motor 212 and motor worm gear housing 210 are of known configuration (e.g. from the EVOTM winch of Lewmar Limited) and are not described further here.
  • Winch drum 202 is rotatable with respect to support 102 via roller bearings 104. Support 102 is fixed with respect to base 206 which in turn is for fixing with respect to the deck of a sailboat (not shown).
  • Winch drum 202 has a ring gear (drum gear) 108 formed on the inner surface of skirt portion 204.
  • First axle 110 and second axle 112 respectively locate the first and second drive trains of the winch, described in more detail below.
  • the general layout of the first and second drive trains in respect of manual operation of the winch is similar to than seen in Figs. 1-3 .
  • Manual drive spindle 300 which will be described in more detail with respect to Figs. 13-16 , has a drive socket 302 formed at its upper end for driving engagement with a keyed (typically bisquare) protrusion extending from a manual cranking handle (not shown).
  • a keyed typically bisquare
  • Motor gear shaft 114 is coaxial with a rotatable relative to second axle 112. Motor gear shaft 114 is held within motor gear shaft housing 208 and is rotatable relative to motor gear shaft housing 208 via bearing 116. In operation, motor gear shaft 114 is driven by a worm gear (not shown). Due to the gearing reduction provided by the worm gear, it is impossible to turn the motor gear shaft 114 unless the motor is operating. Therefore, with the motor inactive, motor gear shaft 114 is locked against rotation.
  • Main drive gear G2 meshes with ring gear 108.
  • ratchet track R2 At the interior of main drive gear G2 is formed ratchet track R2 within which turns a pawl carrier 118 carrying sprung pawls 120. Pawl carrier 118 and pawls 120 are able to rotate ACW with respect to ratchet track R2.
  • Pawl carrier 118 is formed integrally with gear G4 which, in the configuration shown in Figs. 4-7 , is engaged with spindle gear wheel G5. Spindle gear wheel G5 is held for rotation with spindle 300.
  • gear G4, pawl carrier 118, pawls 120, ratchet track R2 and main drive gear G2 constitute the first drive train. Pawl carrier 118, pawls 120 and ratchet track R2 together constitute the first unidirectional drive means.
  • Motor gear shaft 114 at the end distal from the motor gearbox 210, splays to provide an annular shape having ratchet track R3 formed at the inwards facing part of the annular shape.
  • pawl carrier 122 Located within the annular shape is pawl carrier 122, carrying sprung pawls 124. Pawl carrier 122 and pawls 124 are able to rotate ACW with respect to ratchet track R3. Pawl carrier 122, pawls 124 and ratchet track R3 together constitute the third unidirectional drive means.
  • Pawl carrier 122 is formed integrally with gear G1 which is permanently engaged with main drive gear G2.
  • Gear G1 is also formed integrally with pawl carrier 126 carrying sprung pawls 128.
  • Pawl carrier 126 and sprung pawls 128 are able to rotate ACW with respect to ratchet track R1 which is formed within gear G3.
  • Gear G3 is engaged with spindle gear wheel G5.
  • Pawl carrier 126, pawls 128 and ratchet track R1 constitute the second unidirectional drive means.
  • gear G3, pawl carrier 126, pawls 128, ratchet track R1, gear G1 and main drive gear G2 constitute the second drive train.
  • the reduction gearing ratio provided by the second drive train is greater than that provided by the first drive train.
  • Figs. 5 , 6 and 7 assist in understanding the configuration shown in Fig. 4 by illustration plan sectional views along A-A, B-B and C-C respectively.
  • the configuration of Fig. 4 has spindle gear wheel G5 in engagement with gears G4 and G3.
  • Second unidirectional drive means operation:
  • gear G5 In manual operation, with the winch handle driving rotation of the manual drive spindle 300 ACW, gear G5 is turned ACW, this turns gear G4 CW and by driving through ratchet track R2 turns main drive gear G2 CW, this turns the winch drum CW. Gear G5 also turns gear G3 CW and gear G2 turns gear G1 ACW, these two gears can turn in these opposite directions because ratchet track R1 allows this.
  • the manual drive spindle rotation direction may be changed to CW.
  • Gear G5 is turned CW, this turns gear G3 ACW and by driving through ratchet track R1 turns gear G1 ACW, this turns gear G2 CW and therefore also turns the winch drum CW.
  • Gear G5 also turns gear G4 ACW, gear G2 is already being turned CW.
  • gear G5 remains meshed with gears G4 and G3.
  • the winch drum has an ACW torque applied by the tangential rope load. This attempts to turn gear G2 ACW, which attempts to drive through ratchet track R2 and attempts to turn gear G4 ACW. This then attempts to turn gear G5 CW.
  • Gear G2 also attempts to turn gear G1 CW, this attempts to drive through ratchet track R1 to attempt to turn gear G3 CW, this then attempts to turn gear G5 ACW.
  • gear G5 is being turned CW by gear G4 and ACW by gear G3. The result of this is that the whole gear system locks and so the winch drum does not reverse wind (ACW in this embodiment) under the tangential rope load in the manual driving configuration illustrated in Figs. 4-7 .
  • gear G1 is being turned CW by gear G2, this would drive through ratchet track R3 into motor gear shaft 114.
  • gear G1 is being turned CW by gear G2
  • ratchet track R3 is never engaged in this way.
  • gear G5 engaged with gears G3 and G4
  • motor gear shaft 114 is turned ACW by the motor, this drives through ratchet track R3 and turns gear G1 ACW, this turns gear G2 CW and then this turns the winch drum CW for powered forward winding.
  • Gear G1 is turning ACW which does not drive through ratchet track R1.
  • Gear G2 is turning CW which does not drive through ratchet track R2. Both gear G3 and G4 are not driven and as such neither is gear G5.
  • motor gear shaft 114 is turned ACW by the motor, this drives through ratchet track R3 and turns gear G1 ACW, this turns main drive gear G2 CW and then this turns the winch drum CW.
  • Gear G1 is turning ACW which does not drive through ratchet track R1.
  • Gear G2 is turning CW which does not drive through ratchet track R2.
  • Both gears G3 and G4 are driven via ratchet tracks R1 and R2 but as gear G5 is now removed they play no part in the system.
  • reverse winding of the drum is powered in effect by the rope load.
  • the speed of rotation is controlled by the speed of the motor, but the motor itself does not drive reverse winding - it instead allows reverse winding to occur by providing rotation of the third unidirectional drive means which otherwise would lock the drum against reverse winding.
  • Manual drive spindle 300 has drive socket 302 formed at its upper end and an axial bore 304 formed through the remainder of its length. Plunger 306 slidingly fits in axial bore 304. Head 308 of plunger 306 is formed with a flange against which an upper end of spring 310 bears. The lower end of spring 310 bears against a corresponding recess in axial bore 304, with the result that plunger 306 is urged upwardly along axial bore 304.
  • Spindle collar 312 is formed integrally with spindle gear wheel G5 and fits over a corresponding narrowed portion 314 of spindle 300 for sliding axial movement with respect to spindle 300.
  • Plunger 306 is attached to collar 312 by shear pin 316 extending through radial holes 318 in collar 312, radial slot 320 in narrowed portion 314 and through a corresponding hole (not shown) at the lower end of plunger 306.
  • Spring 322 is held in an axial bore 324 of plunger 306, the spring 322 being held for compression between a blind end of bore 324 and shear pin 316. The urging effect of spring 322 is therefore to slide collar 312 and the integral gear wheel G5 to the lower limit of travel of shear pin 316 in slot 320.
  • Fig. 14 illustrates the configuration in which the winch crank handle (not shown) is inserted into the manual drive socket 302 of the manual drive spindle 300.
  • the insertion of the winch handle into drive socket 302 depresses plunger 306 by bearing against head 308 of plunger 306. This compresses spring 310.
  • Downwards axial movement of plunger 306 causes downward axial movement of collar 312 and integral gear wheel G5 due to the urging of spring 322 against shear pin 316.
  • gear wheels G3 and G4 are angularly disposed in order to receive gear G5, gear G5 will engage with gears G3 and G4.
  • the lower axial extent of G5 is provided with bevelled gear teeth 326 in order to assist with this engagement between G5, G3 and G4.
  • Fig. 16 illustrates the configuration in the case where the winch handle is placed in the manual drive socket 302 but where gears G3 and/or G4 are not yet in an angular position to receive gear G5 for engagement.
  • spring 322 is compressed so that gear G5 is located out of axial engagement with gears G3 and G4.
  • As the winch is operated there will come a point at which gears G3 and G4 are in an angular position to allow engagement with gear G5, at which point urging of spring 322 will axially extend gear G5 into engagement with gears G3 and G4.
  • Fig. 15 shows the configuration of the manual drive spindle with the winch handle removed from drive socket 302. This is the same as the configuration shown for the winch in Fig. 8 .
  • each of springs 310 and 322 urge plunger 306 upwards. The result of this is that gear G5 is retracted from engagement with gears G3 and G4.
  • Fig. 17 shows a perspective view of a motorised winch according to a preferred embodiment of the present invention. The same winch is shown in side view in Fig. 18 , in enlarged perspective view in Fig. 19 , in enlarged side view in Fig. 20 and in enlarged sectional view in Fig. 21 .
  • Self-tailing arrangement 220 is provided in order to take rope from the winding surface of winch drum 202 towards an unloaded end of the rope (not shown). Parts of the self-tailing arrangement rotate with the winch drum 202 and parts of the self-tailing arrangement remain stationary with respect to winch support 102. It should be noted that any parts of the self-tailing arrangement which are stated to remain stationary with respect to the support 102 during operation of the winch may be rotationally adjustable with respect to support 102, for example in order to locate the self-tailing arrangement at a convenient position with respect to the operator.
  • Top cap 240 is arranged to fit at the top of the winch. Top cap 240 remains stationary with respect to winch support 102 during operation of the winch.
  • Feeder arm 242 is provided integrally with top cap 240, in order to guide rope from the winch drum 202 and into the self-tailing arrangement.
  • the self-tailing arrangement further includes upper rope lock ring 244 and lower rope lock ring 246, best seen in Figs. 20 and 21 .
  • Each rope lock ring is provided with knurls, or the like, in order to enhance gripping on rope.
  • Rope lock rings 244, 246 are rotatable with winch drum 202. Together, rope lock rings 244 and 246 define a rope guide channel 248 around the self-tailing arrangement.
  • Lower rope lock ring 246 is spring mounted with respect to the winch drum 202 via springs 250, 252. Corresponding springs may be provided at suitable angular intervals around the lower rope lock ring 246. Spring mounting of the lower rope lock ring 246 in this way allows the width of the rope guide channel 248 to be varied during operation, in order for the rope guide channel to accommodate ropes of different diameters.
  • the description of the self-tailing arrangement corresponds to the self-tailing arrangement known from winches such as the Lewmar EVO TM winch.
  • the winch includes a retainer guide 260 in the form of a ring that extends around the full circumference of the self-tailing arrangement, best seen in Fig. 22 .
  • Retainer guide 260 includes protrusion 262 which fits into a corresponding axial slot 264 formed on the inward face of feeder arm 242. Protrusion 262 and slot 264 cooperate to prevent rotation of retainer guide 260 with respect to feeder arm 242.
  • the axial extendable slot allows retainer guide 260 to move axially to a limited extent with respect to feeder arm 242. The result of this is that, during normal operation of the winch, retainer guide 260 does not rotate with rope lock rings 244 and 246.
  • Fig. 22 shows a perspective view of retainer guide 260.
  • Retainer guide 260 has a retainer lip 266 extending only partly circumferentially around the self-tailing assembly.
  • the shape of retainer lip 266 when viewed from a radial direction has an asymmetric profile.
  • the left hand end of retainer lip 266 has a relatively steep surface and the right hand extent of retainer lip 266 has a relatively shallow tapered surface.
  • the steep surface is a reverse winding guide portion, typically having a steepness of about 60°.
  • the shallow tapered portion 270 has a slope of 15° or less, typically about 7.5°.
  • the retainer lip 266 extends for about 120° around the circumference of the self-tailing assembly.
  • opening 272 is defined between the feeder arm 242 and the reverse winding guide portion 268 which is sized in order to conduct rope out of and into the self-tailing arrangement.
  • reverse winding guide portion 268 on retainer lip 266 guiding the rope through opening 272 and behind retainer lip 266 in the rope guide channel in order to be safely gripped in the rope guide channel between rope lock rings 244 and 246 around the remainder of the circumference of the self-tailing assembly to the feeder arm.
  • the steepness of the slope of reverse winding guide portion 268 prevents the rope from displacing retainer lip 266 (and hence retainer guide 260) downwards during normal operation.
  • the user can extract rope from the rope guide channel by pushing the retainer guide 260 downwards against the urging of springs 250, 252. This can be achieved one-handed if necessary, if the user uses the rope to depress retainer guide 260.
  • tapered portion 270 The relatively shallow slope of tapered portion 270 means that, if rope is only partially inserted into the self-tailing arrangement adjacent feeder arm 242 during forward winding of the winch, the rope travelling around the self-tailing arrangement encounters tapered portion 270. Continued forward winding of the winch causes the rope to cam the retainer guide 260 downwards by virtue of the shallow slope of tapered portion 270, until the rope is fully contained in the rope guide channel behind retainer lip 266, the unloaded end of the rope then being fed through opening 272.
  • reverse wind extractor 276 assists in the extraction of the rope from the rope guide channel and back onto the feeder arm for feeding to the drum 202.
  • Reverse wind extractor 276 has a similar configuration to forward wind extractor 274, in that it is in the form of a wedge.
  • the winch provides at least two (but preferably only two, for simplicity) manual forward driving speeds, of different gearing ratios.
  • the manual forward gearing ratio is selected according to the direction of rotation of the manual drive socket, and thus the direction of rotation of the winch handle.
  • reverse winding is typically only provided when rope wrapped around the winch drum is subjected to a load which provides a reverse winding torque to the winch drum.
  • the winch handle When the winch handle is located in the manual drive socket, the winch is locked against reverse winding. In this way, reverse winding is not possible by manual operation or by motor operation. This provides an important safety feature of the preferred embodiments of the present invention.
  • the winch when the crank handle is located in the drive socket, the winch is still capable of motor-operated forward winding. However it is important to note that in this situation, motor-operated forward winding of the winch does not rotate the crank handle.
  • Suitable controls are provided for controlling the motor.
  • only two selectable on-off controls are provided (these are not illustrated in the drawings).
  • a forwards control button is exclusively for controlling on-off motor-operated forward winding. Thus, there is no other operation possible using this button.
  • a reverse control button is provided exclusively for controlling on-off motor-operated reverse winding of the winch drum. There is no other function provided by this button. The importance of this is that, during challenging sailing conditions, the user does not need to toggle a selector switch in order to ensure that the relevant buttons will provide the required mode of operation of the winch.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Injection Moulding Of Plastics Or The Like (AREA)
EP12191934.4A 2011-11-11 2012-11-09 Treuil Not-in-force EP2592038B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
SI201230538A SI2592038T1 (sl) 2011-11-11 2012-11-09 Vitel
HRP20160419TT HRP20160419T1 (hr) 2011-11-11 2016-04-19 Vitlo

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB1119582.3A GB2496445A (en) 2011-11-11 2011-11-11 Winch with reverse winding function

Publications (2)

Publication Number Publication Date
EP2592038A1 true EP2592038A1 (fr) 2013-05-15
EP2592038B1 EP2592038B1 (fr) 2016-02-03

Family

ID=45444072

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12191934.4A Not-in-force EP2592038B1 (fr) 2011-11-11 2012-11-09 Treuil

Country Status (6)

Country Link
EP (1) EP2592038B1 (fr)
DK (1) DK2592038T3 (fr)
GB (1) GB2496445A (fr)
HR (1) HRP20160419T1 (fr)
HU (1) HUE028937T2 (fr)
SI (1) SI2592038T1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE2150020A1 (en) * 2021-01-13 2022-07-14 Selden Mast Ab A winch arrangement for a sailing boat

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO348029B1 (en) * 2022-05-30 2024-06-24 Proxdrive As Winch handle for Sailboat Winches

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4892291A (en) 1982-10-08 1990-01-09 Lewmar Marine Limited Two-speed winch
GB2276137A (en) 1993-02-23 1994-09-21 Harken Inc Backwind sailboat winch
DE20112015U1 (de) * 2001-07-19 2002-07-04 Dill, Werner, 65232 Taunusstein Schot- und Ankerwinde
US20020092454A1 (en) * 2000-01-18 2002-07-18 Helmut Meyerdierks Winch
WO2011005172A1 (fr) 2009-07-06 2011-01-13 Seldèn Mast Ab Procédé et dispositif relatifs à un winch destiné à une écoute ou une drisse sur un voilier

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4892291A (en) 1982-10-08 1990-01-09 Lewmar Marine Limited Two-speed winch
GB2276137A (en) 1993-02-23 1994-09-21 Harken Inc Backwind sailboat winch
US20020092454A1 (en) * 2000-01-18 2002-07-18 Helmut Meyerdierks Winch
DE20112015U1 (de) * 2001-07-19 2002-07-04 Dill, Werner, 65232 Taunusstein Schot- und Ankerwinde
WO2011005172A1 (fr) 2009-07-06 2011-01-13 Seldèn Mast Ab Procédé et dispositif relatifs à un winch destiné à une écoute ou une drisse sur un voilier

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE2150020A1 (en) * 2021-01-13 2022-07-14 Selden Mast Ab A winch arrangement for a sailing boat
SE545055C2 (en) * 2021-01-13 2023-03-14 Selden Mast Ab A winch arrangement for a sailing boat

Also Published As

Publication number Publication date
EP2592038B1 (fr) 2016-02-03
GB201119582D0 (en) 2011-12-28
DK2592038T3 (en) 2016-04-25
GB2496445A (en) 2013-05-15
HRP20160419T1 (hr) 2016-05-20
HUE028937T2 (en) 2017-01-30
SI2592038T1 (sl) 2016-08-31

Similar Documents

Publication Publication Date Title
US8820720B2 (en) Winch
AU778332B2 (en) Winch
US10131524B2 (en) Gear reduction assembly and winch including gear reduction assembly
US4225118A (en) Direct drive deck winch
EP2592038B1 (fr) Treuil
US9284169B2 (en) Sailboat winch
EP2592039B1 (fr) Treuil
EP2592037B1 (fr) Treuil
JP2000128487A (ja) チェーンブロック
EP3835251B1 (fr) Treuil autoserrant
EP0832842A1 (fr) Treuil
AU645997B2 (en) Winch
SE535253C2 (sv) Sätt och anordning vid linvinsch till segelbåt
JPH0229111Y2 (fr)
JP2002193591A (ja) レバー式巻上機
NO842695L (no) Anordning for rullereving og heising av seil.

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20131113

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

17Q First examination report despatched

Effective date: 20140909

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150706

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 773602

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160215

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602012014342

Country of ref document: DE

REG Reference to a national code

Ref country code: HR

Ref legal event code: TUEP

Ref document number: P20160419

Country of ref document: HR

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20160419

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20160203

REG Reference to a national code

Ref country code: HR

Ref legal event code: T1PR

Ref document number: P20160419

Country of ref document: HR

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 773602

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160504

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160603

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602012014342

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

26N No opposition filed

Effective date: 20161104

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E028937

Country of ref document: HU

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160503

REG Reference to a national code

Ref country code: HR

Ref legal event code: PBON

Ref document number: P20160419

Country of ref document: HR

Effective date: 20161109

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602012014342

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MM4D

Effective date: 20161109

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20161130

Ref country code: NO

Ref legal event code: MMEP

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20161201

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20161109

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: NO

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170531

Ref country code: FI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: HR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

Ref country code: LT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20170731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110

Ref country code: HU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161110

Ref country code: LV

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161201

REG Reference to a national code

Ref country code: SI

Ref legal event code: KO00

Effective date: 20170804

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161130

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170601

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161109

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180601