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WO1989009744A1 - Winch mecanique pour voilier - Google Patents

Winch mecanique pour voilier Download PDF

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Publication number
WO1989009744A1
WO1989009744A1 PCT/US1989/001425 US8901425W WO8909744A1 WO 1989009744 A1 WO1989009744 A1 WO 1989009744A1 US 8901425 W US8901425 W US 8901425W WO 8909744 A1 WO8909744 A1 WO 8909744A1
Authority
WO
WIPO (PCT)
Prior art keywords
drum
line
motor
take
high torque
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.)
Ceased
Application number
PCT/US1989/001425
Other languages
English (en)
Inventor
William Charles Ottemann
Richard Arthur Gabellini
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.)
IMI-BARIENT Inc
IMI Barient Inc
Original Assignee
IMI-BARIENT Inc
IMI Barient Inc
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 IMI-BARIENT Inc, IMI Barient Inc filed Critical IMI-BARIENT Inc
Publication of WO1989009744A1 publication Critical patent/WO1989009744A1/fr
Priority to DK243390A priority Critical patent/DK243390D0/da
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • 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
    • B66D1/76—Capstans having auxiliary drums or barrels for storing the ropes or cables

Definitions

  • This invention relates to sailboat winches. More particularly, a winch for the high speed low tension take-up and final low speed high tension handling of running rigging on Genoa jibs of large Marconi rigged sailboats is disclosed.
  • the Genoa jib is a large triangular sail. This sail often exceeds the size of the so-called "main sail". This being the case, the tensioning of this sail at its extreme point or "clew" from the boat pre ⁇ sents a problem not accommodated by modern powered winches.
  • Most powered take-ups of running line which include line storage are provided by a conventional winding drum with a level wind. A good example of such a drum and level wind is the conventional fishing reel.
  • the drum rotates for line take-up. Usually this rota- tion is under constant tension at a drum brake. Where the tension is exceeded, the brake no longer permits the line to be taken in.
  • the level wind makes sure that line stored on the drum is level.
  • the level wind under an endless thread on a rotating shaft makes excursion back and forth across the drum.
  • Line is threaded through the level wind.
  • the combination of the excur ⁇ sion of the line and the winding of the drum produces on the wound drum a "level wind" of line stored on the drum.
  • the sheet attached to such a Genoa jib on a Marconi rigged sloop is long. It must have suffi- cient length to pass from the winch on one side of the vessel, around the mast and back to the clew of the sail when the sail is close hauled at the opposite side of the vessel. In short, a length of line must be used on such a winch to extend from one winch around the mast all the way back to the remaining winch. Further, and when the vessel is running "before the wind" fur ⁇ ther extension of the sheet may be required. In the case of 120 foot Marconi rigged sloop with a 150 foot mast mentioned above, at least 150 feet of 1 inch line must be used.
  • the tension on the line is far from uniform when it is brought in during a tack.
  • the sail is initially cut loose by letting out the line or sheet attached to the Genoa jib on one side of the vessel.
  • the line or sheet attached to the Genoa jib on the opposite side of the vessel must be rapidly gathered in under low tension to the winch on the oppo ⁇ site side of the vessel.
  • the base or low lying wraps of the winch drum are soft. They are wrapped loosely over one another.
  • the tensions of the initial winds will be far less than 1,000 lbs.
  • Genoa jib provides the correct shape to the wind.
  • Genoa ' s jib are essentially air foils and that they are sculpted by tension with respect to the onrushing wind, the purpose of this ten ⁇ sion can be understood. Further, such sculpting of the sail requires increased tension with increased winds. Tensions in the order of 20,000 lbs. on a 1 inch line may ultimately be required.
  • winch mechanisms used for taking in line under great tension. These mechanisms usually include for the high torque winches a pair of simultaneously rotating drums. These simultaneously rotating drums receive the portion of the line under great tension and discharge the line to a conventional take-up drum, usually equipped with a level wind.
  • the simultaneously rotating drums of the high torque winch are spaced side-by-side and turn on parallel axes. Each of the drums is circumscribed with a series of grooves, typically V-grooves.
  • Threading of the line to such high torque drums can be easily understood.
  • Line is threaded in a spiral.
  • the spiral is wound about one half of one drum and then the remaining half of the other drum.
  • the line is wound around one half of one drum at one of the V-grooves.
  • the line is then passed to the adjacent drum and wound around the other half of the other drum at a similar V-groove.
  • the line is then returned to the former drum and wound about an identi ⁇ cal drum half at an adjacent and typically lower groove.
  • This spiral winding process continues about successive halves of each drum until sufficient turns have been taken around both drums at successive V-grooves to produce the required tension.
  • Modern racing yachts are typically equipped with synthetic racing sails. These sails, while adding speed to the boat, are particularly sensitive to being damaged by luffing. Consequently, it is absolutely required that slack be immediately taken up to prevent immediate sail damage or short term sail failure.
  • a power sailboat winch mechanism for the high speed gathering of running rigging line under initial low tension with final slow speed gathering of the same line under final high tension combined with line storage is disclosed.
  • the winch mechanism includes two drums handling the line in series, these drums constituting a winding drum and a high torque drum.
  • the winding drum is provided threaded to the bitter end of the line with a level wind for even distribution of the line along the drum.
  • This winding drum provides initial rapid line take-up, tailing force to a high torque winch drum and line storage for the requisite amount of line used in the particular running rigging handled by the winch.
  • a conventional high torque winch drum is provided bet ⁇ ween the winding drum and line load.
  • This high torque winch is provided with surfaces to induce line climbing of the drum by conventional crowd climbing over the drum surface.
  • This high torque winch spins free on a ratchet during high speed line gathering at the take-up drum, provides low speed high torque output for required final running rigging tensioning and has a proportional clutch release for letting line go under controlled tension for working of the running rigging.
  • a three speed hydraulic circuit with three hydraulic motors capable of running in parallel for high torque powered operation of the winch is disclosed.
  • a first motor powers the winding drum, runs alone for initial rapid line take-up and sequences the next in series hydraulic motor when drum torque and hence hydraulic inlet pres- sure to the motor exceeds a preset limit.
  • the second hydraulic motor drives the high torque drum at a medium torque speed in parallel with the winding drum driven by its hydraulic motor in a tailing mode.
  • This second motor in turn sequences a third motor driving the high torque drum in parallel. Final tensioning is provided by all three motors driving in parallel.
  • the hydraulic circuit releases a proportionally controlled clutch on each drum for controlled release of the running rigging.
  • An object to this invention is to set forth a combination of winch drums which together can work under power and acceptably store running rigging on the Genoa jib of a large sailboat.
  • a take-up drum is provided threaded to the bitter end of the Genoa jib sheet.
  • This take-up drum provides line storage, initial take-up tension for the prevention of undue sail luffing and tail tensioning of a high torque winch drum.
  • a high torque winch drum is provided in series on the line between the take-up drum and Genoa jib line load.
  • the high torque winch drum has conventional crowd climbing cams on the barrel surface of the winch so that high 7 tension take-up occurs at one side of the drum with tailing tension line release at the other side of the drum.
  • a level wind intermediate the two drums assures even line storage on the take-up drum.
  • the high torque drum does not interfere with the rapid gathering of the line to prevent undue sail luffing.
  • the winding drum and level wind provide three discrete functions. First, sufficient line can be stored on the winding drum to enable full working of sail.
  • the winding drum acts in a tailing capacity to the high torque drum.
  • An additional object of this invention is to disclose the placement of a high torque drum in series with the winding drum so that the variable speed and variable tension take-up problems of a conventional Genoa jib sheet can be accommodated.
  • a high torque winch is placed on the line in series with the load between the loaded end of the line and the winding drum.
  • This high torque winch is provided with pair climbing cams at either side of the drum to enable centering of the line during both line take-up and line release.
  • the winch is driven by at least one and pre ⁇ ferably two hydraulic motors under high torque.
  • the high torque winch is capable of free turning on a ratchet.
  • a clutch here illustrated attach as to the outer ring of a planetary gear drive.
  • An advantage of this aspect of the invention is that the high torque winch only becomes active when high line tension is required. At other times, the winch runs free with the line enabling the required rapid gathering of the line
  • a further advantage of the high torque winch is that it can be driven by two separate motors. One of these motors can drive the high torque drum at inter ⁇ mediate tension with the final motor geared to drive the high torque drum at full tension.
  • a further object to this invention is to set forth a hydraulic circuit for utilization with the dis ⁇ closed winch mechanism.
  • the winding drum is driven by a hydraulic motor.
  • the inlet pressure to the hydraulic motor is a direct function of the tension encountered at the winding drum.
  • a conventional hydraulic sequencing circuit runs a second motor attached to the high torque drum in parallel with the winding drum.
  • This second motor driving the high torque drum in turns sequences a third motor at 1500 psi hydraulic pressure.
  • the third motor is sequenced, all three motors run in parallel to effect low speed high tension line take-up.
  • An advantage of the disclosed hydraulic circuit is that its required shifting to high torque and low speed take-up is solely a function of line tension.
  • This line tension serially sensed by the input to the first and second hydraulic motors, enables winch torque responsive to the ever changing dynamics of weather, sail, sea and angle of attack of the vessel to the wind.
  • An additional object to this invention is to set forth a winch mechanism that enables rapid release of gathered line.
  • the take-up drum is provided with a conven ⁇ tional clutch release which upon release only exerts a small torque.
  • the high torque drum is provided with a dual planetary gear drive wherein one of the outer rings of the planetary gear has a normally engaged clutch. Proportional hydraulics act against the normal clutch or brake engagement to effect clutch or brake release. Consequently, a proportional release of the line can occur that emulates a manual tailed release of line from a conventional modern winch.
  • An advantage of this aspect of the invention is that controlled line release is possible.
  • the tension on the sheet can be eased responsive to either slackening wind or change of angle of attack to the wind.
  • rapid and complete line re ⁇ lease can occur for working the sail as in a tack.
  • the characteristics of a manually tailed modern winch has been automated for line handling on large vessels.
  • Fig. 1 is a side elevation of the disclosed winch illustrating the winding drum at the bitter end of the line with the high torque drum placed in series on the line between the line load and the working end of the line;
  • Fig. 2 is a plan view of the winch mechanism of Fig. 1 illustrating the high torque drum with line 10 spirally wound and crowded across the drum with the output of the high torque drum feeding a level wind for line storage to the winding drum;
  • Eig. 3 is a side elevation section taken along the high torque drum, this section illustrating the dual planetary gear drive with ratchet, by a hydraulic motor drive and clutch for winch free wheeling, high torque rotation and line release; and,
  • Fig. 4 is a schematic of a hydraulic circuit for the operation of the winch.
  • Fig. 5 is a perspective of the winch.
  • a base B mounts two drums; a winding drum T and a high torque drum H.
  • Winding drum T accommodates the bitter end of a line at 14 and thereafter has the line helically disposed in successive layers about the axis 15 of the drum T.
  • the line L passes between conventional level wind W to the high torque drum H at 17.
  • High torque drum H includes two surfaces 18 and 19 to induce climbing of the line L with respect to the drum. That is to say, utilizing the tension on the drum, during line take-up the successive winds of the line L move from surface 19 towards surface 18 under urging of surface 19 during take-up. Conversely, and assuming that the line is being let go, the lines of line L move from surface 18 towards surface 19 when letting go of the line occurs.
  • Three hydraulic motors are provided. These motors are low torque hydraulic motor Ml on take-up drum T, medium torque hydraulic motor M2 and high torque hydraulic motor M3 on high torque drum H.
  • Motor M2 drives high torque drum H through conventional
  • High torque motor M3 communicates in a dual planetary gear drive relationship with respect to the shaft of high torque drum H as is disclosed with respect to Fig. 3. 11
  • a ratchet 90 is placed adjacent the drive from motor M3. This ratchet assumes the load when motor M3 is not provided with hydraulic motive force and hence prevents the winch from backing under the full load of line L.
  • take-up winch T When such series connected powering occurs, the function of take-up winch T will change. It will no longer be the primary motive force bringing the line L. Instead, it will supply what is known as a tailing force through level wind W to high torque winch H.
  • a tailing force is easy to understand. Specifically, the tension exerted on line L between level wind W and point 17 on high torque drum H acts as a line "tailing" force. This line "tailing” force exerts a belt pulley type friction to the line over the successive turns provided on the high torque drum H. This force will be multiplied many times until full tension of the line is realized at point 25.
  • high tension line L will first come in contact with the climbing cam surface 19. This contact will cause the successive winds of line around high torque winch H to move in the direction of arrow 27 to and towards climbing cam surface 18. Upon move ⁇ ment of the line to point 17, conventional discharge to the level wind W will occur.
  • motor M3 through a gear train drives high torque drum H at approximately a 30 to 1 gear ratio. This being the case, great tension may be exerted at line L at point 25. During this phase, 13 the tailing function of take-up drum T will still main ⁇ tain substantially the same tension on the line L.
  • release of line L Upon tack of a vessel, release of line L must be accomplished. This is accomplished by releasing of conventional clutches on take-up drum T and release of the clutch designed within high torque drum H. Upon release of the paired clutches, a controlled release of the line L can occur.
  • the disclosed winch emulates the three line take-up functions of a modern high speed geared winch. Initial rapid line take-up is provided. Thereafter, and under a medium and controlled tension, slack is taken out of a sail. Finally, the sail is tightened to its ultimate "to weather" disposition. Having set forth the overall functionality of the winch, attention can now be directed to the section setting forth the drive of the high torque drum H. The drive of motors Ml and M2 will be ignored; these motors are directly keyed to take-up drum T and high torque drum H.
  • Input sun gear 40 rotates three planetary gears against a stationary outside ring 44.
  • a representative planet gear 46 is illustrated intermediate the rotating sun gear and the stationary ring gear 44.
  • a clutch C is provided. Clutch C when relaxed allows stationary ring gear 44 to slip. Consequently release of the high torque drum H can occur.
  • gear 46 effects relative rotation with a 6 to 1 reduction.
  • This 6 to 1 reduction compels planetary pinion carrier 48 to rotate a second sun gear 50.
  • Second sun gear 50 in turns rotates a second planetary gear 56.
  • Second planetary gear 56 is stationary.
  • the second planetary gear 56 bears against a ring gear 58 on the inside of high torque drum H. This causes the high torque drum H to rotate under a gear ratio of approximately 30 to 1. Consequently, line L is brought in under high torque.
  • a ratchet located at planetary gear carrier 48 enables high torque drum H to free wheel. Accordingly, a conventional ratchet is placed which allows the drum to be gathered in at a speed exceeding that of the motors M2, M3.
  • a hydraulic piston 70 bears against a spring biased plate 75.
  • Spring bias plate 75 in turn biases interleaved clutch plates 80 into the normally engaged position.
  • piston 70 When disengagement is desired, piston 70 is provided with hydraulic force from within chamber 82. This hydraulic force advances the piston 70 against the spring bias plate 75. The frictional engagement be ⁇ tween the clutch plates is released. Consequently, high torque drum H is free to release line under tension.
  • take-up drum T and its level wind W constitute a standard item of manufac- ture.
  • such a take-up drum T can be pur ⁇ chased from Seaway Products of Falmouth, England under the designation Captive Sheet Winch.
  • Take-up drum T is provided with a hydraulic brake. This take-up drum assures that the tension on line L remains uniform.
  • Con ⁇ ventional hydraulic power is provided at hydraulic line 100.
  • Line 100 outputs continually to a three way valve v during winch operation.
  • Three way valve V at first portion 101 provides for take-up of line.
  • the hydraulic circuitry 15 is idle. Tension at the winch will be maintained.
  • the valve provides for proportional release.
  • a control K acting on the valve supplies the respective positions of three way valve V and hence operation of 5 the winch.
  • valve portion 101 registers to the hydraulic line. Thereafter, release will be discussed with respect to 0 valve portion 103.
  • Control K func ⁇ tions to cause the valve to switch between any of its three positions. Assuming that take-up is called for, the control
  • Hydraulic line 100 is registered with valve portion in three way valve 101 V.
  • hydraulic force will pass through line 110 to hydraulic motor Ml.
  • Motor Ml will drive drum T with the resultant of output of low pressure hydraulic fluid to a pump connected to discharge 120.
  • sequence valve 140 When pressure exceeds 1500 lbs., sequence valve 140 will be overcome. This will cause motor M3 to enter the series circuit. Entry into the motor drive will occur through line 143 with exhaust at line 134 to hydraulic discharge. At this latter point, it will be seen that all three motors, Ml, M2 and M3, will effectively be running in parallel.
  • control K is moved in the direction of 108.
  • Hydraulic flow is provided to a proportional controller 170.
  • Proportional controller 170 is conventional. Specifically, it causes the pressure in chamber 82 (see Fig. 3) to be propor ⁇ tionally increased dependent upon the position of handle K along path 108. This proportional controller allows hydraulic pressure to be increased to enable the clutch to slip.
  • spring bias adjust ⁇ ment between the clutch on high torque winch H and the brake on winding drum T occurs.
  • the spring force on high torque winch H is adjusted for release after the brake on winding drum T. This enables the winding drum to release the line L under a conventional release of the belt pulley friction on the high torque drum. Such release is the same as the conventional "tailing" release usually manually accomplished on a manned winch on a sailing yacht.
  • the winch is illustrated in perspective.
  • the series wind respective to the two drums T and H can easily be seen through the level wind w.
  • the reader will, therefore, understand that the novel two winch construction has been illustrated.
  • This construction is especially designed towards the needs of a modern large sailboat. Specifically provi ⁇ sioned for rapid line take-up under low tension and slow line take-up under high tension for the problem of hauling in sail is specifically disclosed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Earth Drilling (AREA)
  • Mechanical Means For Catching Fish (AREA)
  • Jib Cranes (AREA)

Abstract

L'invention concerne un winch mécanique de voilier pour rassembler une ligne de manoeuvre courante sous une faible tension initiale et un rassemblement final à faible vitesse de la ligne, combiné avec le stockage de cette dernière. Le mécanisme du winch comprend un tambour d'enroulement (T) et un tambour classique de couple élevé (H). Le tambour d'enroulement comprend un mécanisme de niveau d'enroulement (W), et assure un enroulement initial rapide de la ligne, une force de fuite au tambour du winch à couple élevé et un stockage de la ligne. Le tambour du winch à couple élevé (H), situé entre le tambour d'enroulement et la charge de la ligne, est en roue libre pendant le rassemblement à haute vitesse de la ligne, et assure une sortie de couple élevé pour le raidissement final. Un circuit hydraulique avec trois moteurs hydrauliques (M1, M2, M3) est décrit. Un premier moteur (M1) actionne le tambour d'enroulement pour l'enroulement rapide de la ligne et met en séquence un second moteur hydraulique (M2) lorsque le couple du tambour dépasse une limite préétablie. Ce second moteur metà son tour en séquence un troisième moteur (M3) pour un raidissement final à couple élevé, ce raidissement final à couple élevé étant effectué par les trois moteurs fonctionnant en parallèle.
PCT/US1989/001425 1988-04-13 1989-04-06 Winch mecanique pour voilier Ceased WO1989009744A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DK243390A DK243390D0 (da) 1988-04-13 1990-10-08 Spil til sejlbaade

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US18100588A 1988-04-13 1988-04-13
US181,005 1988-04-13

Publications (1)

Publication Number Publication Date
WO1989009744A1 true WO1989009744A1 (fr) 1989-10-19

Family

ID=22662481

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1989/001425 Ceased WO1989009744A1 (fr) 1988-04-13 1989-04-06 Winch mecanique pour voilier

Country Status (4)

Country Link
EP (1) EP0414707A4 (fr)
AU (1) AU615397B2 (fr)
DK (1) DK243390D0 (fr)
WO (1) WO1989009744A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2705656A1 (fr) * 1993-05-05 1994-12-02 Duesterloh Gmbh Branchement hydraulique pour la commande de moteurs hydrauliques associés à un treuil à friction en amont duquel un tambour d'accumulation est installé.
WO1995018061A1 (fr) * 1993-12-30 1995-07-06 Thomson-Csf Treuil a moteur hydraulique notamment pour helicoptere muni d'un sonar
CN103373674A (zh) * 2012-04-18 2013-10-30 浙江诺和机电有限公司 一种多滚筒恒速恒拉力液压绞盘
EP3070045A1 (fr) * 2015-03-16 2016-09-21 Airbus Helicopters Système de treuil et aéronef à voilure tournante présentant un tel système
FR3055326A1 (fr) * 2016-08-30 2018-03-02 Bernard Canal Dispositif emmagasineur de cordage pour navire a voiles
GB2591155A (en) * 2019-12-24 2021-07-21 De Liftfabriek Bv Winch assembly for a support structure

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7998464B2 (en) 2005-09-29 2011-08-16 L'oreal S.A. Process for the photoprotective treatment of artificially dyed keratin fibers by application of a liquid water/steam mixture

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US3606257A (en) * 1968-12-31 1971-09-20 Wilson John H Traction drum winch which exerts a predetermined constant tension on a cable
US3698690A (en) * 1970-12-31 1972-10-17 Koontz Machine & Welding Inc Hydraulically operated winch
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US4234167A (en) * 1978-08-18 1980-11-18 Otis Engineering Corporation Automatic inhaul winch system
US4434972A (en) * 1980-10-08 1984-03-06 Potain Poclain Materiel (P.P.M.) Hoisting winch

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FR2487802B1 (fr) * 1980-08-01 1985-08-09 Retel Jr Dispositif de commande d'un treuil
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US1792092A (en) * 1921-10-08 1931-02-10 Sullivan Machinery Co Hoisting mechanism
US3606257A (en) * 1968-12-31 1971-09-20 Wilson John H Traction drum winch which exerts a predetermined constant tension on a cable
US3698690A (en) * 1970-12-31 1972-10-17 Koontz Machine & Welding Inc Hydraulically operated winch
US4136855A (en) * 1976-12-03 1979-01-30 The Manitowoc Company Inc. Hoist drum drive control
US4223871A (en) * 1978-04-04 1980-09-23 Vickers Shipbuilding Group Limited Winch mechanism
US4234167A (en) * 1978-08-18 1980-11-18 Otis Engineering Corporation Automatic inhaul winch system
US4434972A (en) * 1980-10-08 1984-03-06 Potain Poclain Materiel (P.P.M.) Hoisting winch

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See also references of EP0414707A4 *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2705656A1 (fr) * 1993-05-05 1994-12-02 Duesterloh Gmbh Branchement hydraulique pour la commande de moteurs hydrauliques associés à un treuil à friction en amont duquel un tambour d'accumulation est installé.
WO1995018061A1 (fr) * 1993-12-30 1995-07-06 Thomson-Csf Treuil a moteur hydraulique notamment pour helicoptere muni d'un sonar
FR2714663A1 (fr) * 1993-12-30 1995-07-07 Thomson Csf Treuil à moteur hydraulique, notamment pour hélicoptère muni d'un sonar.
CN103373674A (zh) * 2012-04-18 2013-10-30 浙江诺和机电有限公司 一种多滚筒恒速恒拉力液压绞盘
CN103373674B (zh) * 2012-04-18 2015-08-05 浙江诺和机电有限公司 一种多滚筒恒速恒拉力液压绞盘
EP3070045A1 (fr) * 2015-03-16 2016-09-21 Airbus Helicopters Système de treuil et aéronef à voilure tournante présentant un tel système
FR3055326A1 (fr) * 2016-08-30 2018-03-02 Bernard Canal Dispositif emmagasineur de cordage pour navire a voiles
GB2591155A (en) * 2019-12-24 2021-07-21 De Liftfabriek Bv Winch assembly for a support structure
GB2591155B (en) * 2019-12-24 2022-01-12 De Liftfabriek Bv Winch assembly for a support structure

Also Published As

Publication number Publication date
EP0414707A1 (fr) 1991-03-06
AU615397B2 (en) 1991-09-26
EP0414707A4 (en) 1991-09-25
AU3368889A (en) 1989-11-03
DK243390A (da) 1990-10-08
DK243390D0 (da) 1990-10-08

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