US3690409A - Level winding winch mechanism and heavy-duty drive therefor - Google Patents

Level winding winch mechanism and heavy-duty drive therefor Download PDF

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Publication number
US3690409A
US3690409A US769326A US3690409DA US3690409A US 3690409 A US3690409 A US 3690409A US 769326 A US769326 A US 769326A US 3690409D A US3690409D A US 3690409DA US 3690409 A US3690409 A US 3690409A
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US
United States
Prior art keywords
winch
drum
winch drum
pivot
staging
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.)
Expired - Lifetime
Application number
US769326A
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English (en)
Inventor
Albert Brauss
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.)
SPIDER STAGING Inc
Original Assignee
SPIDER STAGING Inc
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Filing date
Publication date
Application filed by SPIDER STAGING Inc filed Critical SPIDER STAGING Inc
Application granted granted Critical
Publication of US3690409A publication Critical patent/US3690409A/en
Anticipated expiration legal-status Critical
Assigned to U.S. BANK OF WASHINGTON, NATIONAL ASSOCIATION reassignment U.S. BANK OF WASHINGTON, NATIONAL ASSOCIATION SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SPIDER STAGING CORPORATIN, A CORP. OF WA.
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04G—SCAFFOLDING; FORMS; SHUTTERING; BUILDING IMPLEMENTS OR AIDS, OR THEIR USE; HANDLING BUILDING MATERIALS ON THE SITE; REPAIRING, BREAKING-UP OR OTHER WORK ON EXISTING BUILDINGS
    • E04G3/00—Scaffolds essentially supported by building constructions, e.g. adjustable in height
    • E04G3/28—Mobile scaffolds; Scaffolds with mobile platforms
    • E04G3/30—Mobile scaffolds; Scaffolds with mobile platforms suspended by flexible supporting elements, e.g. cables
    • E04G3/32—Hoisting devices; Safety devices
    • 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
    • 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
    • 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
    • B66D2700/0183—Details, e.g. winch drums, cooling, bearings, mounting, base structures, cable guiding or attachment of the cable to the drum

Definitions

  • a pivot control using a primary spring and a secondary spring energized only after the wire rope reaches a predetermined point on the winch drum is provided to counteract the increase in leverage when an extra long winch drum is used.
  • a low temperature-high capacity drive arrangement for a winch on a suspended staging A pair of worms are driven through spur gears from a common pinion spur gear on a motor shaft. The worms engage two worm gears fixed on a common shaft. A beveled pinion gear is also fixed to an end of the worm gear. The beveled pinion gear meshes with a beveled ring gear which is secured to the winch drum. The distribution of the loading between the worms reduces the operating temperature of the drive arrangement for compliance with the rigid safety requirements for suspended staging. Oil from the worms is splashed against a vertical fin extending down from the top of the worm gear casing. The fin guides the oil into a trough through the walls between the spur and worm gear casing for lubricating the driven spur gears.
  • the angle of approach of the wire rope with respect to the surface of the drum is commonly called the fleet angle".
  • the'fleet angle is optimumally 90 to the drum surface as, for example, in the condition when the wire rope is directly beneath the fairlead of the staging frame.
  • This invention is directed to overcoming the aforementioned problems encountered with increased capacity and length of the winch drum.
  • the fleet angle is kept close to 90, by shifting the ends of the drum axially while the cable is being wound or unwound.
  • shifting is obtained by pivoting the winch about a pivot point located below the axis of rotation of the winch drum.
  • the end of the drum which the wire rope is approaching is pivoted or shifted toward said imaginary perpendicular line to decrease the angle between the wire rope and the imaginary perpendicular line and thus to increase the fleet angle of the wire rope and the surface of the drum.
  • the problem is additionally compensated for by placing the pivot point at a more remote distance from the drum axis of rotation.
  • a pivot control mechanism is provided to apply a variable resistance in opposition to the pivotal action of the winch to counteract the increase in lever arm as the wire rope approaches the end of an extra long drum.
  • a primary resistance is continually increased until the wire rope reaches a predetermined point along the length of the drum, for example, three-fourths of the distance across the length of the drum, and then a constantly increasing secondary resistance is added to the primary resistance to counteract the increased leverage.
  • the pivot control prevents flopping of the drum about the pivot as the wire rope is wound or unwound from the drum.
  • FIG. 1 is a perspective view from a lower aspect of a single-suspension power driven staging, incorporating a high capacity winch unit characterizing the present invention
  • FIG. 2 is a side view of a portion of the equipment illustrated in FIG. 1 with parts broken away for clarity;
  • FIG. 3 is a fragmentary section of a tilt control assembly incorporated in the equipment illustrated in FIG. 2;
  • FIG. 4 is a fragmentary plan view of the equipment illustrated in FIG. 1;
  • FIG. 5 is a cross'sectional view of a portion of the drive unit used in the equipment shown in FIG. 1, taken along the line 5-5 of FIG. 4 and with parts broken away for clarity;
  • FIG. 6 is an end elevation of the equipment shown in FIG. 5 and partly in cross-section as taken along the line 6-6 of FIG. 5;
  • FIG. 7 is an elevation view of the drive unit partly in section as taken along the line 7-7 of FIG. 6 and with parts broken away for clarity.
  • the staging comprises a frame 10 having an upper portion 12 and a lower portion 14.
  • the upper portion includes an operators cage C having a deck D and mounting a fixed mast or tripod T having at the top thereof a wire rope guide or fairlead F.
  • Wire rope R is led through the fairlead from a mounting on top of the building from which the staging is suspended.
  • a winch unit W is mounted below the deck D in the lower portion of the frame and includes a power driven winch drum WD around which the wire rope is wound.
  • the staging details are in many respects quite similar to those of the staging disclosed in the aforesaid Fisher U.S. Pat. No. 2,998,094 with the upper portion 12 of the frame 10 serving to support the operator and the tripod T providing a support for the fairlead F.
  • the fairlead in the instant application includes three case-hardened pins, not shown, that guide the wire rope as it passes through the tripod.
  • a tension holder 17 is fixed to the tripod just below the fairlead and includes two sets of vertically spaced rollers I8, 20.
  • the wire rope R passes between the sets of rollers and one set is movable toward the other by a handle 21 to hold the wire rope and keep it from forming loose coils on the drum when the staging platform is rested on the ground.
  • the rollers serve as additional low friction guides to position and reduce wear on the wire rope R.
  • the lower portion 14 of the staging frame I is provided with a rectangular bottom frame 22 which includes pairs of spaced lower and upper cross braces 24 and 25, respectively.
  • Each of the four cross braces is provided with a support plate 26 which mount two vertical braces 27 joining the lower and upper cross braces.
  • An I-beam 28 is secured between each support plate 26 and vertical brace 27.
  • the I-beam is provided with two sets of vertically downwardly extending pin-mounting brackets 30 which are apertured to receive a pivot pin 32.
  • two pivot pins are provided at spaced distances along the I-beam 28.
  • pivot block 34 Mounted for free pivotal movement on each pivot pin is a pivot block 34 that is formed integrally on each of two sets of webs or arms 36.
  • the webs are spaced from one another to provide a central opening 38 which surrounds the I-beam 28 and are secured at their upper ends to a winch mounting plate 40.
  • a support block 41 mounts a right hand, as viewed in FIG. 2, bearing block 42 and is fixed, as by welding, to the winch mounting plate.
  • a left hand bearing block 44 is fixed to the other end of the winch mounting plate.
  • the bearing blocks rotatably mount an axle 46 on which the winch drum WD is rigidly secured.
  • An electric motor M and suitable driving gear, to be later described, are also secured to the winch mounting plate 40 for rotating the winch drum.
  • the motor M is a suitable reversible electric motor or, in the alternative, may be an air motor or an internal combustion engine as disclosed in the aforesaid Fisher US. Pat. No. 2,998,094.
  • the motor and drive gearing are suitable to rotate the winch drum at the desired speed to provide a vertical staging climbing rate of approximately 18 feet per minute. l-Iigher or lower speeds may, of course, also be obtained depending on the safety requirements and the type of service to which the staging is being employed.
  • a tilt control assembly 50 is provided to dampen the intensity of this rocking action. As is best shown in FIGS. 2 and 3 the tilt control assembly 50 includes a cylinder 51 that is pivotally secured to the bottom frame 22. A control rod 52 is slidably received in a stepped-diameter abutment tube 53. A small collar or stop tube 53a of a soft metal, such as aluminum, is positioned on the control rod 52 at one end of the abutment tube 52 and serves as a positive stop to limit the pivotal movement of the winch unit W in one direction.
  • the tilting of the winch unit W in the other direction is limited to a lesser degree by washer 59 resting on a tube 58 that is fixed to the cylinder 51. This is to compensate for the effect of the lay of the wire rope which is discussed later.
  • the abutment tube 53 has an enlarged portion 53b that acts as a spring abutment for a secondary spring 54.
  • a primary spring 55 circumscribes the control rod and abutment tube and engages a pair of spaced upper and lower washers 56a and 56b, respectively, secured to the control rod by adjustable nuts 57.
  • the washers each engage a clip ring 58 secured in grooves in the ends of the cylinder 51.
  • the free end of the control rod 52 is pinned for pivotal movement to the support block 41 on the right-hand end of the winch mounting plate 40.
  • pivotal movement of the winch unit w to the left about the pivot pins 32 will pull the control rod 52 against the lower washer 56b to compress the primary spring 55 against the upper washer 56a.
  • the secondary spring 54 engages the upper washer 56a and is compressed against the enlarged portion 53b of the abutment tube 53.
  • the secondary spring 54 engages the upper washer 56a only after the primary spring has undergone considerable compression and thus acts to immediately increase the resistance against further pivotal movement of the winch unit.
  • This feature is important since the extra long length of the drum WD causes the wire rope R to move further out from the pivot point (pivot pins 32) of the winch unit and this substantially increases the lever arm and torque acting to pivot the winch unit. As the lever arm increases the secondary spring becomes engaged to counteract the increased torque and thus keeps the pivotal movement under control in all position.
  • the stop tube or collar 53a engages the upper washer 56a when the unit has pivoted the maximum limit desired and prevents further pivoting in that direction.
  • the stop tube may be easily replaced with a stop tube of a larger or smaller length to vary the pivotal limits.
  • Pivot movement of the winch unit W to the right, as viewed in FIG. 2, is also controlled. Pivotal movement in this direction will first compress the primary spring 55 between the upper and lower washers 56a and 56b and then will compress the secondary spring 54 as the pivotal movement continues. Finally the washer 59 will engage the tube 58 to prohibit further movement.
  • FIG. 2 The pivotal movement of the winch drum WD with respect to the fairlead F is best shown in FIG. 2.
  • FIG. 2 The pivotal movement of the winch drum WD with respect to the fairlead F is best shown in FIG. 2.
  • an imaginary, vertical perpendicular line x has been drawn downward from the fairlead F to a horizontal plane y that passes through the center line or axis of rotation of the winch drum WD when the winch drum is in the horizontal position.
  • the imaginary perpendicular line x and the plane y are at right angles with the wire rope as shown in FIG. 2
  • the movement of the winch unit W to the right is smaller than to the left which is accomplished by letting washer 59 contact tube 58.
  • the right-hand end of the winch drum is spaced a further distance from fairlead and the imaginary perpendicular line x than the other.
  • the wire rope, indicated by phantom line R has reached the right-hand end of the winch drum WD and in so doing has caused the winch unit W to pivot about the'pivot pins 32.
  • the right-hand end of the winch drum has shifted to the left toward the imaginary perpendicular line x.
  • the angle between the imaginary perpendicular line x and the wire rope R in the phantom position is less than if the drum had been fixed. This, of course, causes the angle between the wire rope and the plane y, i.e., the fleet angle", to more closely approach the 90 right angle that is considered most desirable for winding the wire rope onto the winch drum.
  • the pivot point of the drum WD in the preferred embodiment is approximately 18% inches below the axis of rotation of the drum.
  • the length of the drum is 21 inches and the distance of its axis below the deck D and fairlead F are respectively about 8% and 70 inches.
  • a drive unit includes three interconnected housings, namely, a spur gear housing 76, a worm gear housing 78 and a ring gear housing 80.
  • a common vertical wall 82 interconnects the spur gear housing and the worm gear housing.
  • a top wall 84 (FIG. 6), covers the worm gear housing and is provided with an oil transfer blade or fin 86, for a purpose to be later described, that terminates above a hollow tube 87 mounted in the common vertical wall 82 and passing into the spur gear housing.
  • the tube 87 is cutaway to form a trough to catch the oil flowing from the fin 86.
  • the motor M is bolted to the spur gear housing 76 and includes an output shaft 90 having a spur pinion gear 91 keyed thereto.
  • the pinion gear 91 drives a pair of spaced spur gears 92 which are keyed to a pair of rotatably mounted worm shafts 94.
  • Each worm shaft includes a worm 96 which meshes with a worm gear 97 fixed on a common shaft 98.
  • the common shaft is rotatably mounted in suitable hearings in the end walls of the worm gear housing 78.
  • One end of the common shaft 98 extends into the ring gear housing 80 and has keyed to its free end a suitable bevel pinion 102.
  • the bevel'pinion meshes with a bevel ring gear 104 that is keyed to the axle 46 of the winch drum WD.
  • the loading of the worm gears is distributed between the two worms 96.
  • the dual worm gears reduce the tangential pressure and sliding friction between the worm gears and the worms to produce a substantial reduction in temperature rise and an increase in load capacity.
  • Oil dippers 110 made of any suitable material, such as synthetic, oil resistant rubber, include a plurality of peripherally spaced cups 112 which dip into an oil reservoir 114, common to the spur and worm gear housings 76 and 78, and fling the oil onto the worms 96.
  • the oil dippers are a supplementary lubricating feature and assist in oil distribution.
  • the reservoir 114 is at the same level in each housing due to free flow through a port 116 in the common wall 82.
  • the worm gears 97 and spur pinion gear 91 are lubricated by dipping into the reservoir and one worm and one spur gear are lubricated by direct transfer of the oil from the respective worm gear or spur pinion gear.
  • the spur pinion gear is rotating clockwise, as viewed in FIG. 5, the left-hand spur gear will receive most of the oil carried from the reservoir 114 by the pinion.
  • the righthand spur gear is lubricated by oil passing through the tube 87 that flows onto the pinion 91 and thus directly onto the right-hand spur gear.
  • An additional reservoir 120 is provided in the ring gear housing to lubricate the ring gear 104 and the beveled pinion gear 102. As is thus readily apparent all parts of the driving gearing are effectively lubricated at all times. To still further increase cooling the worm gear housing 78 is provided with a plurality of fins 122 that dissipate heat generated into the surrounding ambient air.
  • a winch mechanism for a suspended, power driven staging comprising:
  • a staging frame having upper and lower portions
  • an elongate winch drum mounted on said frame and having spaced ends and a central rotation axis between aid ends;
  • the winch mechanism defined by claim 1 further including a control assembly for resisting movement of I said drum end toward said imaginary vertical line.
  • the winch mechanism defined by claim 1 further including a control assembly for resisting tilting movement of said drum.
  • control assembly includes primary resistance means for applying a constantly increasing force and secondary resistance means. operable when said drum rotation axis exceeds a predetermined angle.

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Jib Cranes (AREA)
  • Movable Scaffolding (AREA)
US769326A 1968-10-21 1968-10-21 Level winding winch mechanism and heavy-duty drive therefor Expired - Lifetime US3690409A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US76932668A 1968-10-21 1968-10-21

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JP (1) JPS5231097B1 (ja)
GB (1) GB1249405A (ja)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3938781A (en) * 1972-10-12 1976-02-17 Olympic Instruments Inc. Level wind for winch
US3968954A (en) * 1974-05-17 1976-07-13 General Dynamics Corporation Oceanographic apparatus
US4002321A (en) * 1975-07-07 1977-01-11 Cecil A. Pelts Tiltable drums for winding hoist lines
US4226404A (en) * 1977-03-07 1980-10-07 Michael P. Breston Universal long stroke pump system
US5246182A (en) * 1991-06-10 1993-09-21 Waymon Lester Electrical fence wire winding attachment for tractors
US6230844B1 (en) * 1998-07-13 2001-05-15 Inventio Ag Rope traction elevator
US6523806B2 (en) * 2001-02-28 2003-02-25 Yair Bartal Winch mount
US20040251081A1 (en) * 2003-06-10 2004-12-16 Muench Robert Raymond Scaffolding hoist
US20050056819A1 (en) * 2003-09-17 2005-03-17 Rudolf Pockl Winch for a construction machine
US20050104439A1 (en) * 2003-11-14 2005-05-19 Shelah Phillips Wheel weight with body having recess and clip secured therein
WO2008043055A2 (en) * 2006-10-05 2008-04-10 Life-Pack Technologies, Inc. Self powered self-hoisting elevator apparatus
US20090134373A1 (en) * 2007-11-28 2009-05-28 Maximilian Arzberger Winch
WO2013095158A1 (en) 2011-12-23 2013-06-27 Stimline As Drum unit for a well intervention string
US8567764B1 (en) * 2012-05-07 2013-10-29 Joseph Dennis Miller Well pump puller
US8567765B1 (en) * 2012-05-07 2013-10-29 Joseph Dennis Miller Well pump extractor
WO2013180572A1 (en) 2012-05-30 2013-12-05 C6 Technologies As Drum unit with an arch compensator for a well intervention string
US20150008381A1 (en) * 2012-01-27 2015-01-08 Liebherr Components Biberach Gmbh Rope winch
US9228395B2 (en) 2011-12-23 2016-01-05 C6 Technologies As Flexible routing device for well intervention
US9482064B2 (en) 2012-05-30 2016-11-01 C6 Technologies As Drum unit with an arch compensator for a well intervention string
US20160340160A1 (en) * 2015-05-18 2016-11-24 Flexcrane, Inc. Frustoconical drum winch for lifting loads with hook reduced approximation lifting height
US20160368745A1 (en) * 2010-09-29 2016-12-22 Harry Xydias Level wind assembly for a winch drum including a tensioning arm
CN109311640A (zh) * 2016-06-16 2019-02-05 科尼全球公司 绳索提升机的提升装置
US10308488B2 (en) * 2016-09-30 2019-06-04 Hall Labs Llc Load-facing winch
US20200010308A1 (en) * 2018-07-09 2020-01-09 Transking Corporation Pty Limited Winch Assembly
US10919741B2 (en) * 2019-05-09 2021-02-16 Hall Labs Llc Moving drum winch
CN114856228A (zh) * 2022-06-13 2022-08-05 中国十九冶集团有限公司 用于房建高空施工的安全悬挂结构

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2545630A1 (de) * 1975-01-17 1976-07-22 Alberto Sassi Winde, insbesondere fuer aufzuege
GB2296001B (en) * 1994-12-17 1998-12-16 Asep Bv Winch apparatus
JP4516800B2 (ja) * 2004-08-20 2010-08-04 三井造船鉄構工事株式会社 吊足場の構築方法
CN110541556B (zh) * 2019-09-11 2022-04-01 云南建投建筑机械有限公司 附着式升降脚手架及爬升方法
CN112177310B (zh) * 2020-09-17 2022-03-25 中国建筑土木建设有限公司 一种带有可调节的缓冲装置的外墙吊篮及其使用方法
CN112482739B (zh) * 2020-12-08 2022-02-08 山东星斗智能设备有限公司 基于稳定升降卡接固定的建筑施工用吊篮

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2998094A (en) * 1958-09-18 1961-08-29 Spider Staging Inc Level winding winch mechanism
US3297312A (en) * 1965-03-29 1967-01-10 James E Hines Combination shock absorber and spring

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2998094A (en) * 1958-09-18 1961-08-29 Spider Staging Inc Level winding winch mechanism
US3297312A (en) * 1965-03-29 1967-01-10 James E Hines Combination shock absorber and spring

Cited By (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3938781A (en) * 1972-10-12 1976-02-17 Olympic Instruments Inc. Level wind for winch
US3968954A (en) * 1974-05-17 1976-07-13 General Dynamics Corporation Oceanographic apparatus
US4002321A (en) * 1975-07-07 1977-01-11 Cecil A. Pelts Tiltable drums for winding hoist lines
US4226404A (en) * 1977-03-07 1980-10-07 Michael P. Breston Universal long stroke pump system
US5246182A (en) * 1991-06-10 1993-09-21 Waymon Lester Electrical fence wire winding attachment for tractors
US6230844B1 (en) * 1998-07-13 2001-05-15 Inventio Ag Rope traction elevator
US6523806B2 (en) * 2001-02-28 2003-02-25 Yair Bartal Winch mount
US20040251081A1 (en) * 2003-06-10 2004-12-16 Muench Robert Raymond Scaffolding hoist
US20050056819A1 (en) * 2003-09-17 2005-03-17 Rudolf Pockl Winch for a construction machine
US7080826B2 (en) * 2003-09-17 2006-07-25 Bauer Maschinen Gmbh Winch for a construction machine
US20050104439A1 (en) * 2003-11-14 2005-05-19 Shelah Phillips Wheel weight with body having recess and clip secured therein
WO2008043055A2 (en) * 2006-10-05 2008-04-10 Life-Pack Technologies, Inc. Self powered self-hoisting elevator apparatus
WO2008043055A3 (en) * 2006-10-05 2008-10-16 Life Pack Technologies Inc Self powered self-hoisting elevator apparatus
US20090134373A1 (en) * 2007-11-28 2009-05-28 Maximilian Arzberger Winch
US7753345B2 (en) 2007-11-28 2010-07-13 Bauer Maschinen Gmbh Winch
US20160368745A1 (en) * 2010-09-29 2016-12-22 Harry Xydias Level wind assembly for a winch drum including a tensioning arm
WO2013095158A1 (en) 2011-12-23 2013-06-27 Stimline As Drum unit for a well intervention string
US9169102B2 (en) 2011-12-23 2015-10-27 C6 Technologies As Drum unit for a well intervention string
US9228395B2 (en) 2011-12-23 2016-01-05 C6 Technologies As Flexible routing device for well intervention
US9783399B2 (en) * 2012-01-27 2017-10-10 Liebherr Components Biberach Gmbh Rope winch
US20150008381A1 (en) * 2012-01-27 2015-01-08 Liebherr Components Biberach Gmbh Rope winch
US8567764B1 (en) * 2012-05-07 2013-10-29 Joseph Dennis Miller Well pump puller
US8567765B1 (en) * 2012-05-07 2013-10-29 Joseph Dennis Miller Well pump extractor
US9482064B2 (en) 2012-05-30 2016-11-01 C6 Technologies As Drum unit with an arch compensator for a well intervention string
WO2013180572A1 (en) 2012-05-30 2013-12-05 C6 Technologies As Drum unit with an arch compensator for a well intervention string
US20160340160A1 (en) * 2015-05-18 2016-11-24 Flexcrane, Inc. Frustoconical drum winch for lifting loads with hook reduced approximation lifting height
US9963327B2 (en) * 2015-05-18 2018-05-08 Flexcrane, Inc. Frustoconical drum winch for lifting loads with hook reduced approximation lifting height
CN109311640A (zh) * 2016-06-16 2019-02-05 科尼全球公司 绳索提升机的提升装置
US20190135595A1 (en) * 2016-06-16 2019-05-09 Konecranes Global Corporation Hoisting arrangement of rope hoist
US10926982B2 (en) * 2016-06-16 2021-02-23 Konecranes Global Corporation Hoisting arrangement of rope hoist
US10308488B2 (en) * 2016-09-30 2019-06-04 Hall Labs Llc Load-facing winch
US20200010308A1 (en) * 2018-07-09 2020-01-09 Transking Corporation Pty Limited Winch Assembly
US11097928B2 (en) * 2018-07-09 2021-08-24 Transking Corporation Pty Limited Winch assembly
US10919741B2 (en) * 2019-05-09 2021-02-16 Hall Labs Llc Moving drum winch
CN114856228A (zh) * 2022-06-13 2022-08-05 中国十九冶集团有限公司 用于房建高空施工的安全悬挂结构

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Publication number Publication date
GB1249405A (en) 1971-10-13
JPS5231097B1 (ja) 1977-08-12

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