WO1991014646A1 - Treuil repondant automatiquement a la charge - Google Patents

Treuil repondant automatiquement a la charge Download PDF

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Publication number
WO1991014646A1
WO1991014646A1 PCT/US1991/001804 US9101804W WO9114646A1 WO 1991014646 A1 WO1991014646 A1 WO 1991014646A1 US 9101804 W US9101804 W US 9101804W WO 9114646 A1 WO9114646 A1 WO 9114646A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
gear
vertical position
pawls
winch
Prior art date
Application number
PCT/US1991/001804
Other languages
English (en)
Inventor
Bruno Resch
Guillermo Ferramola
Original Assignee
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. filed Critical Imi Barient, Inc.
Priority to DE69126426T priority Critical patent/DE69126426T2/de
Priority to EP91907622A priority patent/EP0521109B1/fr
Publication of WO1991014646A1 publication Critical patent/WO1991014646A1/fr

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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
    • B66D1/7484—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
    • B66D1/7421—Capstans having a vertical rotation axis
    • B66D1/7431—Capstans having a vertical rotation axis driven manually only

Definitions

  • This invention relates to winches and has been devised particularly though not solely for use in winches employed on marine craft such as yachts.
  • winches are known and are used extensively in yachting for tensioning sheets, halyards and other running rigging of yachts.
  • the tensioning is effected by winding a handle which turns a winch drum through a plurality of gear trains of differing velocity ratios ' so that by progressively, selectively increasing the velocity ratios, a sheet, for example, can be quickly brought up to the required tension.
  • selection of the appropriate velocity ratio is effected by reversal of the direction of rota- tion of the operating handle.
  • the third velocity ratio is offered by vertical movement of a handle shaft to cause a dog clutch to be engaged or disengaged from a direct drive connection to the winch drum.
  • a three-speed winch in which a lever is operated to engage a first gear train (the gear train which is normally used first and has the lowest velocity ratio).
  • the winch handle is rotated in one direction in first gear, then in the opposite direction to automatically engage second gear (a gear train of intermediate velocity ratio) and then the winch handle is again reversed to engage third gear (the gear train of highest velocity ratio) .
  • a three-speed winch in which a number of gears are provided, one set mounted on a shaft fixed to a base and other sets being mounted on a rotatable carrier which is rotatable on the base and which is spring-loaded to engage under zero or minimum load on the winch drum a first gear train out of three gear trains, the first gear train including a gear on the shaft fixed to the base. If the handle is rotated in one direction, say clockwise, in these conditions, the first gear train is operated instead of a third gear train so long as the carrier is not caused by operation of the handle in the opposite direction to move against the loading spring.
  • This three-speed winch is not load responsive in the sense that the operable gear train is dependent on the torque load on the winch, which is generated by the sheet load.
  • the description gives emphasis to the fea ⁇ ture that the transition between the three-gear trains takes place fully automatically only by changing direc ⁇ tion of rotation of the driving gear, and this winch must always start in first gear even if the initial sheet load is high so that the winch .operator is re ⁇ quired to start cranking the winch in the second gear direction in order to shift the winch out of first gear into third gear via the second gear.
  • International Application PCT/AU88/0053 (Interna ⁇ tional Publication No. WO88/06565) describes a three- speed winch having three gear trains.
  • This particular winch has the disadvantage that it is reasonably complex and, therefore, expensive to manufacture. Still further, the complexity adds to the weight of the winch. A still further disadvantage is that the winch does not lend itself for adapting to the configuration of existing winches.
  • an automatic load-responsive winch which includes a base, a winch drum rotatably mounted on the base, and a rotatable drive shaft for driving the winch drum.
  • the winch also includes at least two gear trains mounted on driven shafts and linked between said drive shaft and said drum for rotating said drum in response to rotation of the drive shaft.
  • One of the two gear trains produces a different drum speed than the other of the gear trains for the same rotational speed of the drive shaft.
  • a variable torque load is applied to one of the shafts by operation of a line or rope wound on the winch drum.
  • the winch includes a mechanism displacable verti ⁇ cally with respect to the one shaft in response to changes in the variable torque load.
  • the mechanism in ⁇ cludes a means for engaging one of the gear trains at a first vertical position of the mechanism and for disen ⁇ gaging the gear train at a second vertical position to isolate the one gear train and provide for rotation of the drum by the other gear train.
  • the mechanism is mounted for rotation with the one shaft and includes a cylindrical opening for receiving the shaft.
  • the opening includes a plurality of longitu ⁇ dinally extending splines and the shaft also has a plurality of longit ⁇ dinally extending splines engaging the splines of the mechanism.
  • the mechanism rotates in response to rotation of the shaft, but is slidable longitudinally with respect to the shaft from the first vertical position to the second vertical position.
  • the mechanism reciprocates up and down and is spring biased to the first vertical position and slidable against said bias to the second vertical position.
  • the shaft splines engage the mechanism splines to produce fric ⁇ tion that increases as the torque load on the winch increases.
  • the mechanism is maintained in the second vertical position when the friction is increased in response to the torque load to an amount sufficient to overcome the spring bias on the mechanism.
  • the mechanism described in the paragraph immediately above includes a . plurality of ramps protruding verti ⁇ cally upwardly therefrom and being spaced in an arc around the mechanism.
  • the ramps periodically engage a plurality of ramps located in a fixed vertical position with respect to the shaft.
  • the ramps of the mechanism ride over the ramps fixed with respect to the shaft to displace the mechanism vertically and reciprocally.
  • the friction reaches a point where the friction overcomes the bias, the mechanism is held in the second vertical position by the friction between the splines.
  • a camming element is located in a fixed vertical position with respect to the one shaft.
  • the camming element includes at least one cam surface shaped in an arcuate relation with respect to the shaft, and most preferably, a helical relation.
  • the displacable mechanism includes a cam follower that- rides on the helical cam surface. The cam follower rides on the camming surface in response to changes in the torque load to move the mechanism from the first vertical position to the second vertical position.
  • the camming element includes a plurality of protrusions that extend longitudinally from the camming element toward the mechanism.
  • the mechanism includes a plural ⁇ ity of like protrusions.
  • the protrusions have mirror image helical faces that ride against each other and move the mechanism vertically in response to increases in the torque load.
  • the mechanism is displacable vertically in response to changes in the torque load.
  • the mechanism is operably connected to a transfer member.
  • the transfer rotates with the one shaft and is slidable vertically on the shaft in response to vertical movement of the mechanism.
  • the transfer member includes a plurality of pawls biased radially outwardly of the transfer member.
  • the one gear train includes an annular gear having internal ratchet teeth that are engaged by the pawls.
  • the annular gear has external gear teeth for driving one of the gear trains.
  • the winch includes an annular flange extending radially inwardly of the internal ratchet teeth, and the flange retains the pawls out of engagement with the ratchet teeth in the second verti- cal position.
  • the flange includes a radial face that retains the pawls out of engagement once the transfer member has moved longitudinally with respect to the gear having the internal ratchet teeth.
  • the annular flange includes a ramp on top surface thereof for moving the pawls radially inwardly as the transfer member moves downwardly with respect to the annular gear.
  • the winch according to the present invention is responsive to variations in torque load placed on the winch. If the load is very high, the winch operates in one gear train. If the load is low, the winch operates in another gear train.
  • Other advantages of a winch in accordance with the present invention will be apparent from the following detailed description. Brief Description Of Drawings
  • FIGURE 1 is a schematic part section side eleva ⁇ tion of a three-speed winch for use on a yacht;
  • FIGURES 2, 3 and 4 are schematic side elevations of the central drive portion of the winch of FIGURE 1, in ' three driving modes wherein FIGURE 2 shows the winch wherein the drum rotates at the highest speed with the lowest power; wherein FIGURE 3 shows the winch wherein the drum rotates at a medium speed with medium power transmitted; and wherein FIGURE 4 shows the winch wherein the drum rotates at the slowest speed and the maximum power is transmitted;
  • FIGURE 5 is a schematic part exploded perspective view of the central drive portion of the winch of FIGURE 1;
  • FIGURE 6 is a perspective view of another winch in accordance with the present invention.
  • FIGURE 7 is a top view of the winch shown in FIGURE 6;
  • FIGURE 8 is a sectional view along the plane 8-8 of FIGURE 7;
  • FIGURE 9 is a view similar to that shown in FIGURE 8, except that the button on the top of the winch has been depressed and retained in a depressed position;
  • FIGURE 10 is a perspective view of the ramp shown in FIGURES 8 and 9;
  • FIGURE 11 is a perspective exploded view of the essential components for shifting between gear trains in respect to variations in torque load;
  • FIGURE 12 is a perspective view of the bottom of one of the parts shown in FIGURE 11;
  • FIGURE 13 is a partial section view along the planes 13-13 of FIGURE 7;
  • FIGURE 14 is " a sectional view along the plane A-A Of FIGURE 13;
  • FIGURE 15 is a sectional view along the planes 15-15 of FIGURE 7;
  • FIGURE 16 is a sectional view along the plane B-B Of FIGURE 15.
  • the winch illustrated is sectioned by two vertical planes which intersect along the axis of drive shaft 12.
  • One plane passes through the axis of driven shaft 44 and the other plane passes through the axis of drive shaft 45.
  • the winch 10 has a central drive assembly 11 with an input drive shaft 12.
  • the shaft 12 has an upper- splined socket 13 which is engaged by a crank handle not shown.
  • Surrounding the shaft 12 is a winch drum 14 which rotates clockwise when viewed from above. Refer ⁇ ring to FIGURE 2, when the shaft 12 is initially driven in a clockwise direction as shown by the arrow, rota ⁇ tion of the shaft 12 produces the highest rotational speed of the drum 14. If the rotation of the shaft 12 is reversed as shown in the arrow in FIGURE 3, the next highest or medium speed ' of the drum 14 is achieved. Again, the rotational direction of the drum 14 is clockwise, despite the counter-clockwise rotation of the shaft 12. If the rotational direction is again reversed as shown by the arrow in FIGURE 4 and the shaft 12 driven in a clockwise direction, the slowest speed of the drum 14 is produced. Again, the rota- tional direction of the drum 14 is clockwise.
  • the drive assembly 11 mounteded on and driven by the shaft 12 is the drive assembly 11, which drive assembly 11 includes an upper gear 17 which forms part of the gear train providing the second highest speed (FIGURE 3).
  • the gear 17 has internal splines 15, which engage the splines 16 of the shaft 12; splines 15 and 16 prevent rotation of gear 17 with respect to shaft 12 but permit 17 to slide longi ⁇ tudinally with respect to shaft 12.
  • the drive assembly further includes an intermediate gear 18 which forms part of the gear train of the lowest speed (FIGURE 4.
  • the gear 18 has internal splines 19 which are engaged with the splines 16.
  • the highest speed gear train includes a gear 20, which forms part of the drive assembly 11.
  • the gear 20 is selectively driven by a ratchet and pawl mechanism 21.
  • the ratchet and pawl mechanism includes a base 22 which has internal splines 23 meshed with splines 16.
  • the base 22 is also provided with external splines 24 which engage the internal splines 25 of a transfer member 26.
  • the transfer member 26 is provided with a pair of pivotally mounted pawls 27 which are resili- ently biased radially outward by means of springs 28.
  • the pawls 27 engage ratchet teeth 29 formed internally on the gear 20.
  • the gear 20 is also provided with an annular flange 3.0 that extends radially inwardly.
  • the base 22 is fixed to the shaft so as not to be movable longitudinally thereof.
  • the transfer member 26, gear 18 and gear 17 are movable longitudinally of the shaft 12.
  • extending between the base 22 and gear 18 are springs 31, while extending between the transfer member 26 and the gear 18 are springs 32.
  • the gear 18 is provided with an annular flange 33 that extends radially outwardly. Rotation of the gear 18 relative to the transfer member 26 is prevented by screws 34a, which are fixed to the transfer member through insertion in threaded holes 34b, but pass through apertures in the flange 33, so that the gear 18 may move longitudinally of the shaft relative to the transfer member 26.
  • Extending between the gears 17 and 18 is a spacer sleeve 35, best shown in FIGURES 2-4.
  • the gear 17 has an annular flange 36 provided with a plurality of spaced- apart ramp surfaces 37.
  • a plate 38 Positioned above the gear 17 is a plate 38 which has a plurality of spaced-apart ramp surfaces 39 positioned to ride over the ramp sur ⁇ faces 37, which cause gear 17 to reciprocate longitu ⁇ dinally with respect to plate 38.
  • the gear 17 has been forced downwardly by a distance equal to the height of one of the ramps 37 and 39.
  • the plate 38 has annularly extending slots 40 which receive one.or more pins 41 to hold the plate 38 stationary.
  • the winch 10 has a main body 42 with with a base plate 43 to be secured to a support ⁇ ing structure.
  • the base plate 43 and the associated gear housing support a pair of parallel driven shafts 44 and 45, as well as rotatably supporting the drive shaft 12 by bearings 46 and 47.
  • the drum 14 is rota ⁇ tably supported on the body 42 by bearings 48 and 49.
  • the bearings 49 engage a spacer 50 which also rotatably supports the shaft 12 via a bearing 51.
  • a thrust bear ⁇ ing 52 extends between the spacer 50 and an abutment surface 53 of the drum 14.
  • the spacer 50 finds support on the base plate 43.
  • a gear mem ⁇ ber 54 Rotatably supported by the shaft 44 is a gear mem ⁇ ber 54, which includes a first gear 55 meshingly en ⁇ gaged with the gear 20.
  • the gear member 54 has an upper gear 56, which is meshingly engaged with a further gear 57 rotatably supported by the shaft 45.
  • the gear 57 engages an internal ring gear 58 which is part of the drum 14.
  • gear 59 which is meshingly engaged with the gear 18.
  • the gear 59 engages the gear member 54 via ratchet teeth 60 and pawls 61.
  • the pawls 61 are pivotally mounted on the gear member 56 and are provided with springs to bias them radially outward into engagement with the ratchet teeth 60.
  • gear 62 Also rotatably supported on the shaft 45 via the gear 57 is a gear 62.
  • the gear 62 engages the gear 57 via pawls 63 which are pivotally mounted on the gear 57.
  • the pawls 63 engage ratchet teeth 64 formed on an internal surface of the gear 62.
  • the gear 62 is mesh ⁇ ingly engaged with the gear 17, with the gears 17 and 62 providing the intermediate speed (FIGURE 3).
  • the lowest rotational speed of the drum 14 is pro ⁇ vided by the gears 18, 59, 56, 57 and 58.
  • the rotational power is transferred via the gear member 54 and pawls 61 and ratchet teeth 50.
  • the transfer member 26 needs to be moved down ⁇ wardly and longitudinally of the shaft 12 to isolate the gear 20. Upward movement of the transfer member 26 is also required to reinstate connection between the transfer member 26 and the gear 30. This movement of the transfer member 26 is effected by the springs 31, 32 and interaction of the ramp surfaces 37 and 39. In the initial position, the pawls 27 are engaged with the teeth 29 to transfer power between the transfer member 26 and the gear 20. When in this position, the springs. 31 bias the gear 18 together with the spacer 35 and gear 17 upward. However these items are caused to reciprocate vertically due to the ramp surfaces 37 riding over ramp surfaces 39. The relative movement between the gear 18 and the transfer member 26 is accommodated by the springs 34.
  • the plate 37 is not fixed to the body 42. Accordingly, the plate 38 is permitted to fall from engagement with the pins 41 and therefore rotate with the gear 17.
  • FIGURES 6 through 16 another em ⁇ bodiment of a winch in accordance in the present invention will now be described.
  • the winch shown in these FIGURES has four speeds.
  • the winch includes a main drive shaft 100 which is driven from below in a conventional manner.
  • the winch also includes three driven shafts 102, 104, and 106.
  • the winch includes a top ' drive button 108 for manually engaging the initial gear of the winch.
  • the drive button 108 and its associated transfer mechanism 109 is held within the winch drum 110 by a top cover plate 112 which covers the internal components of the winch and retains button 108.
  • the ini ⁇ tial gear train is driven by engagement of pawls 114 with ratchet 116 of an annular gear 118 that is con ⁇ nected to drum 110. More specifically, referring to FIGURE 9, pawls 114 are biased outwardly into engage ⁇ ment with ratchet teeth 116 when the button 108 is in the downward position of FIGURE 9. At this point the shaft is rotating in a clockwise direction when viewed from above. The shift from this initial gear to the first gear will be described by comparison between FIGURES 8 and 9.
  • the button 108 when the button 108 is re ⁇ leased and moved vertically upwardly to the position shown in FIGURE 8, the pawls 114 as they move upwardly contact ramp 120 and are urged radially inwardly against the bias on the pawls to a position wherein the pawls are retained out of engagement with ratchet teeth 116. More specifically, the pawls are retained by the radial face 122 out of engagement so that when a drive shaft 100 rotates in the clockwise direction, the pawls 114 are out of engagement with respect to the ratchet teeth 116.
  • pawls 114 are re ⁇ tained radially inwardly against engagement with rat ⁇ chet teeth 116 is better described with respect to FIGURE 11, which is a different pawl mechanism within the winch, but this pawl mechanism functions in a similar manner.
  • FIGURE 8 shows the button in a first vertical position while FIGURE 9 shows the button in a second vertical position wherein the button has been moved downwardly.
  • the button is mounted to a second drive shaft section 126 and is slidable vertically with respect to the main section 101 of drive shaft 100.
  • the second shaft section 126 is biased longitudinally upwardly by the spring 128 and is movable vertically downwardly to compress the spring 128 as shown in FIGURE 9.
  • the main section of shaft 100 includes a radial opening 130 that has a pin 132 movable out of the opening and biased by a spring 134.
  • the internal cylindrical surface of shaft section 126 includes a pin receiving detent 136.
  • pin 132 fits within detinet 136 to retain said button in the lower vertical position and provide for engagement of pawls 114 with ratchet teeth 116.
  • the drive shaft 100 is rotating in a clockwise direction in the initial gear speed. In order to change speeds, the person operating the winch rotates the drive shaft in a counter-clockwise direction and the winch will be in second speed. After the shaft 100 has been rotated through an angle of at least 180 degrees, the pins 138, which extend radially outwardly of drive shaft section 126, ride up on ramps 140.
  • the ramps 140 are best shown in FIGURE 10 which shows a cylindrical support 142 that has ramps 140 protruding upwardly therefrom.
  • the ramps are located 180 degrees apart, and provide a surface which urges pins 138 vertically upwardly as the drive shaft 100 is rotated in a counter-clockwise direction.
  • a spring clutch 141 permits rotation of support 142 in a clockwise direc ⁇ tion and locks support 142 against rotation in a counter-clockwise direction.
  • the force of pins 138 against ramps 140 is sufficient to overcome the spring 134 that retains pin 132 into engagement with detent 136.
  • the button 108 pops vertically upwardly from the position in FIGURE 9 to the position shown in FIGURE 8, which disengages the pawls 114 from the ratchet teeth 116.
  • the winch includes a wide variety of thrust bearings which are generally indi ⁇ cated by circular spheres shown at reference character 144.
  • the winch also includes a wide variety of roller bearings 146 .which are generally indicated by an X through a rectangular box. These are of conventional operation and need not be described further.
  • a person operating the winch gets into the initial winch . speed by pressing down button 108 and rotating the shaft in a clockwise direction.
  • the button moves upwardly and disengages the initial speed and thus engaging pawls 114 with ratchet teeth 116.
  • the person rotating the shaft has two options. He can continue to rotate the shaft in a counter-clockwise direction and drive the winch in the. second speed, which is the only winch speed that is driven by rotation of the drive shaft in a counter-clockwise direction.
  • FIGURE 13 shows the winch in the first speed, which is a speed that is between the initial speed and the second speed.
  • FIGURE 15 shows the winch in the third speed, which is the slowest speed. In both the first speed and the third speed shown in FIGURES 13 and 15, the drive shaft 100 rotates in a clockwise direc ⁇ tion.
  • the winch When the winch has a substantial torque load, the winch is in the position shown in FIGURE 15. If the torque load slackens, the winch is in the position shown in FIGURE 13.
  • a camming element 150 is located in a fixed vertical position with re- spect to driven shaft 102.
  • a cam follower mechanism 152 moves from a first vertical position shown in FIGURE 13 to a second vertical position shown in FIGURE 15.
  • the parts described with respect to FIGURES 13 and 15 are also shown in exploded perspective view in FIGURES 11 and 12.
  • the camming element 150 and the cam follower mechanism 152 is shown in a side sectional view so that the working of the camming surfaces and the camming element can be better understood.
  • the displacable cam follower mechanism 152 is movable from the first verti ⁇ cal position shown in FIGURE 13 to the second vertical position shown in FIGURE 15.
  • the mecha ⁇ nism 152 rotates from a first rotational position to a second rotational position offset from said first rota ⁇ tional position by a distance 154 shown in FIGURE 15.
  • the camming element 150 includes at least one and preferably several camming surfaces 156 shaped in an arc, and preferably shaped in a helical relation with respect to the shaft 102.
  • the camming surface 156 abuts a cam follower 158 on said mechanism 152.
  • the mechanism 152 moves in a helical pattern from the position shown in FIGURE 13 to a position shown in FIGURE 15.
  • the mechanism 1S2 is biased upwardly to the posi ⁇ tion shown in FIGURE 13 by a series of conical springs 160 which are also known as "Belleville” springs.
  • the Belleville springs 160 urge mechanism 152 upwardly.
  • the mechanism 152 is movable downwardly against the bias springs 160.
  • the springs are accessible by cover 162 so that the spring tension can be changed if desired.
  • the mechanism 152 begins to move vertically and rotate from the position shown in FIGURE 13 to the position shown in FIGURE 15 through the transmission of a torque load into vertical displacement of member 152. As will be described subsequently, the difference in position of the mechanism 152 provides for engagement of different gear trains.
  • the camming element includes a plura ⁇ lity of protrusions 164 that extend longitudinally from the camming element 150 toward the mechanism.
  • the protrusions of the camming element 150 are essentially the mirror image of the cam followers 166 of mechanism 152.
  • Each camming surface 164 and 166 includes a face 168 that is bounded by two edges 170 and 172.
  • edges 170 and 172 are part of two concentric helices that extend in a helical shape with respect to shaft 102.
  • the face 168 lies in a line 174 that passes between both edges 170 and 172 and the axis of the shaft wherein the line is perpendicular to the shaft axis. More specifically, referring to FIGURE 11, line 174 is perpendicular to shaft axis 176 and intersects both edge 170 and edge 172.
  • the face 168 would always be coinci ⁇ dent with the lines 174, in the preferred embodiment of the invention.
  • each camming protrusion 166 on the mechanism 152 has a mirror image camming protrusion 164 and the camming element 150.
  • the camming protrusions are spaced apart and have located therebetween a series of rectangular protru ⁇ sions 165 and 167 spaced equally about the shaft axis 176 in the same circular path. These protrusions 165 and 167 form stop surfaces that define the first and second positions of the mechanism 152. More particu ⁇ larly, referring to a comparison between FIGURES 13 and 15, the surface 178 of protrusion 165 contacts the surface 180 of the protrusion 167 when the mechanism moves from the position shown in FIGURE 13 to the position shown in FIGURE 15.
  • the camming element 150 as shown in FIGURES 11 through 15 has the mirror image of the pro ⁇ trusions of mechanism 152 including the various stop surfaces and the camming protrusions.
  • the mechanism 152 also includes outwardly extending gear teeth 182 that engage with ' similar teeth on shaft 106 as shown in FIGURE 15.
  • the mechanism 152 preferably includes a transfer member 184 that is shown in perspective in FIGURE 12 5 and that is shown in two sectional views in FIGURES 14 and 16.
  • the transfer member is preferably integral with mechanism 152 and includes a series of pawls 186 that are biased radially outwardly by springs 188 as shown in FIGURE 14. •
  • the pawls are movable radially i ⁇ inwardly against the bias of spring 188 as shown in FIGURE 16.
  • the pawls 188 are inserted into pawls cavities 190 and the transfer member 184.
  • Spacer elements 192 are shown in FIGURE 11 are inserted after the pawls have been inserted.
  • the pawls 186 drive an annual gear 194 which has internal ratchet teeth 196 and external drive teeth 198. In the position shown in FIGURE 13, the pawls 186 are biased radially outwardly into engagement with rat ⁇ chet teeth 196. Thus, when shaft 102 is turned, the
  • annular flange 200 extends beneath the inter ⁇ nal ratchet teeth.
  • the flange 200 includes a radial face 202 that retains the pawls out of engagement with the ratchet teeth 196.
  • the annular flange includes a ramp ' 204 from the upper surface thereof
  • Drive shaft 100 is rotated clockwise. This rotates the drum 110 by means of pawls 114 and ratchets 116.
  • the winch is driven in the initial gear, it is also driving portions of the first gear and third gear drive trains. Since both of these gears are slower speeds, the winch actually overruns these gears by means of pawls and ratchets.
  • First gear is trying to drive the winch through gear 301 in FIGURE 8 which is fixed to the input shaft 100.
  • Gear 301 drives gear 304, in FIGURE 13.
  • Gear 304 is part of shaft 104 which drives integral gear 305.
  • Gear 305 drives gear 198 in FIGURE 11.
  • Pawls 186 which are part of mechanism 152, engage ratchets 196 and drive mechanism 152.
  • Combining element 150 has pawls 306 which ride in it and try to drive ratchets 307 in drive pinion 308.
  • the ratchets 307 are moving faster than the- pawls 306 due to the drum 110, which is being driven through the initial drive, being attached to the ring gear 310 which drives gear 309 which is part of pinion 308. This explains how first gear is overrun.
  • Third gear is also being driven but it too is being overrun. Third gear is driven from gear 311 on the drive shaft 100, FIGURE 15, driving gear 312.
  • Gear 312 has ratchets 313 cut on its inside diameter which trey to drive pawls 314.
  • Pawls 314 are actually overrunning the ratchets 313. This is caused by first gear driving gear 152 which drives gear 315 on the shaft 106 which causes pawls 314 to overrun ratchets 313. Pawls 314 ride in ratchet hub 316 which is attached to shaft 106. A clockwise rotation of shaft 100 causes pawls 302 to ratchet on ratchet 303. These are the second speed ratchets. This ratcheting disables second gear from driving.
  • First gear is also driven by a clockwise rotation of input shaft 100.
  • Button 108 must be in the up position and the winch must only be lightly loaded to drive in this gear.
  • First gear must only be lightly loaded to drive in this gear.
  • First gear is driven through gear 301 in FIGURE 8 which is fixed to the drive shaft 100.
  • Gear 301 drives gear 304 in FIGURE 13
  • Gear 304 is part of shaft 104 which also has part of it gear 305.
  • This gear drives gear 198 in FIGURE 11.
  • Pawls 186 which are part of mechanism 152, engage ratchets 196 and drive mechanism 152. This torque is transferred through to camming element 150.
  • Camming element has pawls 306 which ride in it and drive ratchets 307 in pinion 308. .
  • This drive pinion 308 which includes gear 309.
  • Gear 309 drives ring gear 310 which drive the drum 110.
  • Third gear is also being driven but it too is being overrun.
  • Third gear is driven from gear 311 on the . drive shaft 100, FIGURE 15, driving gear 312.
  • Gear 312 has ratchets cut on its inside diameter which try to drive pawls 314.
  • Pawls 314 are actually overrunning the ratchets 313. This is caused by first gear driving mechanism 152 which drives gear 315 on the shaft 106 which causes pawls 314 to overrun ratchets 313.
  • Pawls 314 ride in ratchet 316 which is attached to shaft 106.
  • a clockwise rotation of shaft 100 causes pawls 302 to ratchet on ratchet 303. This ratcheting disables second gear from driving.
  • Second gear is driven by a counter-clockwise rota ⁇ tion of shaft 100.
  • Gear 317 which is fixed to shaft 100 has pawls 302 which engage ratchets 303. This drives gear 318 which has gear teeth 300. This drives gear 182 which is part of mechanism 152.
  • This torque is transferred through to camming element 150.
  • Camming element 150 has pawls 306 which ride in it and drive ratchets 307 in pinion 308.
  • This drives pinion 308 which includes gear 309.
  • Gear 309 drives ring gear 310 which drives the drum 110.
  • the counter-clockwise rota ⁇ tion of shaft 100 also tries to drive first gear and third gear backwards. This action just ratchets pawls.
  • gear 301 drives gear 304.
  • Gear 304 is attached to shaft 10 ' 4 which has gear 305.
  • Gear 305 is 5 part of annular gear 194 which has ratchets 196. These ratchets ride over pawls 186, driving third gear in a counter-clockwise rotation drives gear 311 which drives gear 312.
  • Gear 312 has ratchets 313 which ratchet on the pawls 314 thereby not driving in third gear.
  • Third gear is driven by a clockwise rotation of the drive shaft 100 when the winch is highly loaded and the top drive button is in the up position. Third gear drives through gear 311 which is attached to the drive
  • Camming element 150 has pawls 306 which ride in it and drive ratchets 307 in pinion 308. This drives pinion 308 which includes gear 309. Gear 309 drives ring gear 310 which drives the drum 110. First gear is trying to
  • a winch in accordance with the present invention has a torque load sensing capability that enables the winch to shift to the appropriate gear speed in response to variations in torque load. This is done in a particularly simple manner without parts that wear to a significant degree.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Un système de treuil répondant automatiquement à la charge comprend une base (43), un tambour de treuil (14, 110) monté rotatif sur la base, et un arbre moteur rotatif (12, 100) servant à entraîner le tambour du treuil. Au moins deux trains d'engrenages sont montés sur des arbres menés (44, 45, 102, 104, 106) et sont reliés entre l'arbre moteur et le tambour pour faire tourner le tambour en réponse à la rotation de l'arbre moteur. Le premier des deux trains d'engrenages génère une vitesse de tambour différente de celle du deuxième train d'engrenages. Lorsqu'une charge à moment de torsion variable s'exerce sur un des arbres via le tambour, un mécanisme (26) se déplace verticalement par rapport à un des arbres, en réponse aux variations du moment de torsion de la charge. Le mécanisme comprend un système (29, 30) qui permet de mettre en prise un des deux trains d'engrenages dans une première position verticale du mécanisme et qui sert à désengrener le premier train d'engrenages dans une deuxième position verticale pour isoler ledit train d'engrenages et permettre la rotation du tambour par le deuxième train d'engrenages.
PCT/US1991/001804 1990-03-21 1991-03-21 Treuil repondant automatiquement a la charge WO1991014646A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE69126426T DE69126426T2 (de) 1990-03-21 1991-03-21 Automatisches lastabhängiges windwerk
EP91907622A EP0521109B1 (fr) 1990-03-21 1991-03-21 Treuil repondant automatiquement a la charge

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AUPJ9224 1990-03-21
AUPJ922490 1990-03-21

Publications (1)

Publication Number Publication Date
WO1991014646A1 true WO1991014646A1 (fr) 1991-10-03

Family

ID=3774564

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1991/001804 WO1991014646A1 (fr) 1990-03-21 1991-03-21 Treuil repondant automatiquement a la charge

Country Status (3)

Country Link
EP (1) EP0521109B1 (fr)
DE (1) DE69126426T2 (fr)
WO (1) WO1991014646A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6776397B2 (en) * 2002-05-17 2004-08-17 Giovanni Antonio Vado Convertible winch
FR3015451A1 (fr) * 2013-12-23 2015-06-26 Pontos Cabestan automatique a prise systematique
CN105271038A (zh) * 2015-11-18 2016-01-27 镇江华虹机械有限公司 一种全封闭式自动控制绞盘

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3728914A (en) * 1970-12-29 1973-04-24 Barient Co Three speed deck winch
US3809368A (en) * 1972-03-07 1974-05-07 Knowsley Eng Ltd Marine winch
US3927580A (en) * 1971-07-02 1975-12-23 Lewmar Marine Ltd Disengaging clutch systems for a three-speed winch
US3962935A (en) * 1973-11-12 1976-06-15 Barwin Pty. Limited Variable speed winch
US3973755A (en) * 1973-12-19 1976-08-10 Lewmar Marine Limited Hand operated winch
US3981208A (en) * 1974-05-29 1976-09-21 Enkes N.V. Sheet winch
US4111397A (en) * 1975-12-19 1978-09-05 Costruzioni Barbarossa Three-speed winch particularly for nautical use
US4208036A (en) * 1977-07-27 1980-06-17 Lewmar Marine Limited Winch
US4582299A (en) * 1982-09-30 1986-04-15 Royle Ian Arthur Winches with pull cord drive
US4667934A (en) * 1986-01-16 1987-05-26 Barient, Inc. Multi-speed winch
US4699360A (en) * 1984-04-16 1987-10-13 Enkes Marine B.V. Automatic three-speed winch
US4974814A (en) * 1987-05-08 1990-12-04 Maxwell Marine Limited Multispeed winch

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3728914A (en) * 1970-12-29 1973-04-24 Barient Co Three speed deck winch
US3927580A (en) * 1971-07-02 1975-12-23 Lewmar Marine Ltd Disengaging clutch systems for a three-speed winch
US3809368A (en) * 1972-03-07 1974-05-07 Knowsley Eng Ltd Marine winch
US3962935A (en) * 1973-11-12 1976-06-15 Barwin Pty. Limited Variable speed winch
US3973755A (en) * 1973-12-19 1976-08-10 Lewmar Marine Limited Hand operated winch
US3981208A (en) * 1974-05-29 1976-09-21 Enkes N.V. Sheet winch
US4111397A (en) * 1975-12-19 1978-09-05 Costruzioni Barbarossa Three-speed winch particularly for nautical use
US4208036A (en) * 1977-07-27 1980-06-17 Lewmar Marine Limited Winch
US4582299A (en) * 1982-09-30 1986-04-15 Royle Ian Arthur Winches with pull cord drive
US4699360A (en) * 1984-04-16 1987-10-13 Enkes Marine B.V. Automatic three-speed winch
US4667934A (en) * 1986-01-16 1987-05-26 Barient, Inc. Multi-speed winch
US4974814A (en) * 1987-05-08 1990-12-04 Maxwell Marine Limited Multispeed winch

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0521109A4 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6776397B2 (en) * 2002-05-17 2004-08-17 Giovanni Antonio Vado Convertible winch
FR3015451A1 (fr) * 2013-12-23 2015-06-26 Pontos Cabestan automatique a prise systematique
WO2015097198A1 (fr) * 2013-12-23 2015-07-02 Pontos Cabestan automatique à prise systématique
CN105271038A (zh) * 2015-11-18 2016-01-27 镇江华虹机械有限公司 一种全封闭式自动控制绞盘

Also Published As

Publication number Publication date
DE69126426T2 (de) 1998-02-12
EP0521109A1 (fr) 1993-01-07
EP0521109A4 (en) 1994-08-10
DE69126426D1 (de) 1997-07-10
EP0521109B1 (fr) 1997-06-04

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