EP0720962B1 - Winde mit einer als Freifallbremse verwendbaren Kupplung - Google Patents

Winde mit einer als Freifallbremse verwendbaren Kupplung Download PDF

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Publication number
EP0720962B1
EP0720962B1 EP95120468A EP95120468A EP0720962B1 EP 0720962 B1 EP0720962 B1 EP 0720962B1 EP 95120468 A EP95120468 A EP 95120468A EP 95120468 A EP95120468 A EP 95120468A EP 0720962 B1 EP0720962 B1 EP 0720962B1
Authority
EP
European Patent Office
Prior art keywords
winch
set forth
slip member
shift
planetary stage
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
EP95120468A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0720962A1 (de
Inventor
Winfried Ing. Felder
Manfred Grieble
Roland Hartmann
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.)
Fuerstlich Hohenzollernsche Werke Laucherthal & Co GmbH
Original Assignee
Fuerstlich Hohenzollernsche Werke Laucherthal & Co GmbH
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 Fuerstlich Hohenzollernsche Werke Laucherthal & Co GmbH filed Critical Fuerstlich Hohenzollernsche Werke Laucherthal & Co GmbH
Publication of EP0720962A1 publication Critical patent/EP0720962A1/de
Application granted granted Critical
Publication of EP0720962B1 publication Critical patent/EP0720962B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/04—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes actuated by centrifugal force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/14—Power transmissions between power sources and drums or barrels
    • B66D1/22—Planetary or differential gearings, i.e. with planet gears having movable axes of rotation

Definitions

  • the invention relates to a motor-operated winch with an at least two-stage Planetary gear according to the preamble of claim 1.
  • Winches that can also be used as free-fall winches will have at least two in a row switched planetary gear stages used, one of which is similar as an output planetary stage a coaxial spur gear works.
  • this known transmission for example the ring gear of an input planetary stage with a sensitive multi-disc brake sufficient thermal load-bearing capacity can be braked when slipping, so that a load is lowered at high speed in free fall and unwinding one Rope can be controlled by a winch drum through the slip of the brake.
  • winches have recently been used to advantage in drilling rigs and cable excavators used to allow the free fall of a load as an additional working mode.
  • the winches are operated exclusively with motors, which are preferably high-pressure hydraulic motors work.
  • the so-called free-fall brake is one of the reaction elements that are necessary so that the winch gear operated with only one degree of freedom is what creates a defined stroke ratio. For example, is a gripper pulled up, then the free-fall brake is opened, preferably the hydraulic motor stops and the drive shaft is braked by an input brake. For the Lifting operation, this winch is always dependent on the fact that electrical for the drive motor or hydraulic energy is available.
  • the invention has set itself the task of creating a winch that one defined, safe free fall operation allowed, building as small as possible and one uniform power flow from a drive via an at least two-stage planetary gear on a winch drum.
  • a winch according to the preamble of claim 1 has a sensitive according to the invention adjustable slip link on, both as a clutch and as a free-fall brake between the planet carrier or the ring gear of the drive planetary stage and the Winch drum is switched.
  • a sensitive according to the invention adjustable slip link on both as a clutch and as a free-fall brake between the planet carrier or the ring gear of the drive planetary stage and the Winch drum is switched.
  • the clutch according to the invention for the lifting operation Winch a planetary coupling gear, in which the slip member is the coupling between two produces planetary stages that drift on the winch drum.
  • this clutch according to the invention is a sensitively adjustable slip member, preferably a finely adjustable multi-disc brake can be a free-falling load power-consuming braking in slip mode.
  • the slip is itself accordingly designed with sufficient thermal resilience.
  • the load can be constantly lowered in a controlled manner by means of sensitive, adjustable slip.
  • the sensitive adjustability of the slip member enables its use in the double function as clutch and free-fall brake.
  • the arrangement of the slip member between the planet carrier or the ring gear Drive planetary stage and the winch drum also opens up the possibility of using a Hand crank to the fast rotating and therefore absorbing low torques To get sun gears of the input and output planetary stage.
  • a hand crank would open up new uses for the invention Winds open, namely where a failure that can never be completely ruled out of a drive motor cannot be tolerated, as is the case with emergency services, for example at sea or in the mountains.
  • the slip member is preferably used to produce a frictional connection, in particular for the Lifting operation, can be loaded with a preload.
  • the prestressing force acts between a primary part and a secondary part of the slip member, preferably a spring force, via a force transmission piece, on the primary part is arranged on brake elements, in particular plates, which are displaceable on the primary part are arranged.
  • the force transmission piece is preferably pivotable on the primary part, in particular in the manner of a rocker arm.
  • the slip member is preferably not only due to the prestressing force, but instead its or in addition to this when centrifugal forces turn the winch drum Friction can be brought.
  • the centrifugal force by the same power transmission piece as that Transfer the preload to the slip member.
  • the biasing force or the centrifugal force can preferably Biasing force can be taken from the slip member by a switching means while the Centrifugal force when the winch drum rotates, supporting the pretensioning force or alone, works. Due to the centrifugal force, it is possible that the Load and stop the motor drive shaft in an absolutely reliable manner, a braking torque is generated by the free-fall brake, which with increasing downward speed increases, creating a clear limit speed of the sinking load can be met.
  • the prestressing force acts on the force transmission piece via an actuating means.
  • the actuating means can be fixed in a position in which none Preload force acts on the power transmission piece. In this position, only the Centrifugal force.
  • the actuating means is on a releasable release bearing attached.
  • the switching means according to the invention is in Slidable in the direction of an axis of rotation of the winch drum and has a stop, with which it pushes against the release bearing during its displacement and thereby the Actuating means disengages from the power transmission means.
  • a hand crank for lifting a load by hand activated.
  • the hand crank in particular its crankshaft, has at least one Activation means, via which it can be connected to the drive planetary stage.
  • gears which are preferably by Moving the hand crank or the crankshaft in the direction of the axis of rotation Winch drum optionally with the sun gear or the planet carrier of the drive planetary stage, which in turn drives the sun gear of the output planetary stage can be brought.
  • an engagement means arranged for the sun gear and another engagement means for the planet carrier. This makes manual operation with two stroke ratios with different Force possible.
  • the switching means and the hand crank are connected to one another in such a way that the hand crank is carried by this when the switching means is moved.
  • the Switching means thus fulfills a double function, on the one hand, by the actuating means or the actuating means in the case of several evenly on the circumference of the ring gear Drive planetary stage distributed power transmission pieces out of engagement brings this power transmission piece or these power transmission pieces and to another connects the hand crank with one of the sun gears of the two planetary stages.
  • a particularly space-saving design is that the switching means by Switching hollow shaft is formed, in which the crankshaft is rotatably supported and preferably is axially fixed.
  • the switching hollow shaft is in turn turned by means of a lever, for example, brought into their various displacement positions via a spindle.
  • the lever is preferably guided in a shifting gate in which it is connected to it attached ball catch can be locked in the desired displacement positions.
  • These displacement positions are preferably the "load stroke” positions with hand force slowly “,” load stroke with hand force fast “, in which a load with the Hand crank is raised, and “load stroke with engine power”, in which the slip member is brought into frictional engagement and held by the prestressing force and finally the position "lower load defined”, in which not the pretensioning force, but only one with increasing speed of the winch drum, increasing centrifugal force acts on the slip member.
  • the simple adjustability of the operating mode of the winch also has an advantageous effect on the Use of the winch according to the invention in rescue operations, for example on ships, out.
  • a one-way clutch which prevents rotation of the drive shaft against the direction of rotation of the drive motor.
  • the reaction torque for stopping the drive shaft becomes due to the one-way clutch transfer.
  • the one-way clutch provides together or alternatively to that on the Drive shaft of the motor arranged closed holding brake that the sun gear Drive planetary stage stops when a relative speed in free fall when the load is lowered should arise on the slip member.
  • the one-way clutch provides equally sure that if the load stroke is lost by hand, the load remains suspended and cannot sink by itself.
  • FIG. 1 shows a winch 1 with a winch drum 2, which is driven by a motor 15 two-stage planetary gear is driven or drivable.
  • the motor 15 drives a sun gear 43 of a drive planetary stage via a drive shaft 16 42 on.
  • This sun gear 43 is in engagement with planet gears, which in turn with mesh a ring gear 48 of the drive planetary stage 42.
  • a planet carrier 44 of the Planetary gears of the drive planetary stage 42 are torsionally rigid with a sun gear 43 Output planetary stage 22 connected. It thus takes place via the planet carrier 44 Output from the drive planetary stage 42 to the output planetary stage 22.
  • the planet carrier 44 concentrically surrounds the drive shaft 16.
  • the sun gear 23 meshes with Planetary gears of the output planetary stage 22, the planet carrier 24 for receiving the Reaction moment is supported on a frame 3 of the winch 1.
  • the planet gears of the Output planet stage 22 mesh with the ring gear 28, the torsionally rigid with the winch drum 2 is connected.
  • the winch drum 2 is opposite the ring gear 48 of the drive planetary stage 42 pivoted.
  • the ring gear 48 carries a primary part 48a of a slip member 11, in Embodiment of a multi-plate clutch 11.
  • the primary part 48a plates are the Multi-plate clutch 11 is torsionally rigid and in the direction of an axis of rotation of the winch drum 3 straightly connected.
  • the winch drum 2 is a counterpart to the primary part 48a, a secondary part 48b of the multi-plate clutch is connected in a torsionally rigid manner.
  • the slats of the Primary parts 48a are on displaceable inner rings of two on both sides of the multi-plate clutch 11 arranged pivot bearing fixed between the ring gear 48 and the winch frame 3, whose respective outer rings are attached to the winch drum 2.
  • the primary part 48a and the ring gear 48 are additionally stable on the planet carrier 24 the output planetary stage 22 rotatably.
  • the winch frame 3 fixed axes of the planet carrier 24 a piece on the planet gears of the output planetary stage 22 extended.
  • the multi-plate clutch 11 is closed by countering the plates of the primary part 48a that of the secondary part 48b are pressed, the drive planetary stage 42 with the Output planetary stage 22 coupled via the winch drum 2.
  • a two-stage arises Planetary coupling gear with a very uniform power flow from the drive shaft 16 through the two planetary stages 42 and 22 onto the winch drum 2.
  • the ring gear 28 could also be supported on the winch frame 3 and accordingly the planet carrier 24 can be connected in a torsionally rigid manner to the winch drum 2.
  • the output could go from the input planetary stage 42 to the output planetary stage 22 the ring gear 48 instead of the planet carrier 44.
  • the planet carrier 44 of the drive planetary stage 42 as Support for the primary part 48a of the multi-plate clutch 11 serve.
  • the multi-plate clutch 11 is sensitive with sufficient thermal resilience adjustable slip member, which consumes friction a controlled free fall a load attached to a rope of the winch drum 2 allowed. Controlled means here that the load drops under its own weight, but the drop due a finely adjustable friction consumption is controlled in the slip member 11.
  • the Drive shaft 16 is stopped in free fall operation of winch 1. For this, the Drive shaft 16 braked by a holding brake 6.
  • the holding brake 6 is a multi-disc brake executed. A primary part of the holding brake 6 is on the winch frame 3 and Secondary part attached to the drive shaft 16 accordingly.
  • the holding brake 6 is under a biasing force so that it brakes the drive shaft 16 when its energy supply ceases or sets.
  • a one-way clutch 17 is arranged.
  • the one-way clutch 17 ensures that together with or as an alternative to that by a prestressing force, in particular by Spring pressure, holding brake 6 closed, the sun gear 43 stands still when in free fall operation when the load drops, a relative speed as in this operating mode Free-fall brake acting multi-plate clutch 11 should arise.
  • the one-way clutch 17 prevents rotation of the sun gear 43 of the output planetary stage 42 against the Direction of rotation in lifting operation.
  • the Pressure piece 50 is by a biasing force, in the embodiment by a force arranged on the circumference of the primary part 48a spring 12, so that it with a Nose 50a presses against the fins of the primary part 48a. This creates a frictional connection between the primary part 48a and the secondary part 48b and thus between the ring gear 48 and the winch drum 2 made.
  • the nose 50a presses against the inner ring the pivot bearing between the winch drum 2 and the ring gear 48.
  • On the circumference of the The primary part 48a is a plurality of such pressure elements 50 which can be loaded with spring force evenly distributed.
  • the springs 12 each act via an actuating means 18b, which is in the manner of a Coupling sleeve is formed on the part of a pressure piece 50, which from the nose 50a seen from the pivot bearing 49 of the pressure piece 50 is extended.
  • the pressure pieces 50 thus act as rocker arms.
  • a centrifugal device is attached to each of the pressure pieces 50.
  • the essential Elements of each of these centrifugal devices are a centrifugal weight 13, a guide 51 and a control spring 52.
  • the guides 51 are in the embodiment by straight waves educated.
  • Each of the flyweights 13 is along its guide 51 against the pressure of the respective control spring 52 arranged to be straight.
  • the waves 51 are in turn on the Pressure pieces 50 firmly attached. They point at an angle of at least 40 °, preferably about 60 °, away from the axis of rotation of the winch drum 2.
  • the Center lines of the shafts 51 thus run on one when the primary part 48a is rotated Cone jacket with an opening angle of at least 80 ° and preferably of about 120 ° around.
  • the slip member 11 can act as a free fall brake, i.e. to the free fall operation of the To allow winch 1, the biasing force generated by the springs 12 of the Pressure piece 50 and thus be taken from the multi-plate clutch 11.
  • a switching hollow shaft 59 on the winch frame 3 in the direction of The axis of rotation of the winch drum 2 is arranged to be straight. Moving the Switching hollow shaft 59 takes place by rotating the same via a between the switching hollow shaft 59 and the winch frame 3 trained spindle drive 63. The rotation of the Switching hollow shaft 59 can be done manually via a lever 60, which is preferably by means of a Hand cable 65 is operated.
  • a rotary bearing 18a is on the switching hollow shaft 59 arranged displaceably in the longitudinal direction of the switching hollow shaft 59.
  • the actuating means 18b is fastened, which together with the Primary part 48a of slip member 11 rotates.
  • the switching hollow shaft 59 at its inner end the rotary bearing 18a acting as a release bearing is arranged for the actuating means 18b, has a stop 59a for the release bearing 18a with which it moves can press against this release bearing 18a.
  • the release bearing 18a is moved through the stop 59a, such as a Seeger ring, taken, which the Move the actuating means 18b away from the pressure pieces 50 and the multi-plate clutch 11 is opened.
  • crankshaft 54 of the hand crank 53 is an extension of the Drive shaft 16 arranged on the side of the winch 1 opposite the motor 15.
  • the crankshaft 54 is concentrically rotatably supported in the switching hollow shaft 59 and axially fixed to the switching hollow shaft 59. When turning the switching hollow shaft 59 and its associated longitudinal displacement, the crankshaft 54 is therefore equally in Moved longitudinally in the direction of the axis of rotation of the winch drum 2.
  • crankshaft 54 has two engagement means in the form of an external ring gear 55 and one Internal gear 56 on.
  • the counterparts to these two activation means 55 and 56 are by an internal gear 58, which on the through the planet gears of the drive planetary stage 42 extending axles of the planet carrier 44 is attached torsionally rigid, and a External gear 57 formed, the torsionally rigid via a shaft extending the drive shaft 16 is attached to the sun gear 43 of the drive planetary stage.
  • the internal gear 58 and the external gear 57 for driving the two sun gears 43 and 23 are arranged to coincide with one another, while the corresponding activation means 55 and 56 of the hand crank 53 in the longitudinal direction of the crankshaft 54 offset from one another are arranged.
  • these two activation means 55 and 56 could be outside and inside toothed gear are formed and the two counterparts 57 and 58 to be arranged offset from one another. It is only important that only one of the driving means 55, 56 driving on its corresponding counterpart 58 or 57 can work. Thus, it is due to a corresponding shift of the switching hollow shaft 59 possible, at the same time the hand crank 53 in optional engagement with one of the two Bring sun gears 23 and 43 of the two planetary stages 22 and 42. Furthermore can also actuate the actuating means 18b by shifting the switching hollow shaft 59 Engagement on the pressure pieces 50 are brought so that a free fall operation is possible.
  • the longitudinal displacement of the switching hollow shaft 59 is brought about by a spindle drive 63, in which the switching hollow shaft 59 is spindle-like in a sleeve fixed to the winch frame 64 rotates and is longitudinally displaced by the rotary movement.
  • a shifting gate 61 is arranged, in which one on the lever 60 Switching hollow shaft 59 attached ball catch 62 is guided. The ball of this ball catch 62 is pressed firmly into the link guide 61 by spring force.
  • the Ball catch 62 can be locked in four sliding positions in the backdrop 61. This shifting or Locking positions correspond to the operating modes of the winch 1.
  • the winch 1 is in the operating mode "load stroke with motor power”.
  • the holding brake 6 is positively opened and the motor 15 drives via the drive shaft 16 the sun gear 43 of the drive planetary stage 42.
  • the actuating means 18b are by their respective springs 12, which are supported on the primary part 48a of the slip member 11, against the respective seen from the lugs 50a beyond the pivot bearing 49 extended parts of the pressure pieces 50 pressed.
  • the pressure pieces 50 are thereby their noses 50a pressed against the slats of the primary part 48a of the slip member 11, the thereby brought into a firm frictional engagement with the secondary part 48b and held therein is so that a torsionally rigid connection between the ring gear 48 of the drive planetary stage 42 and the winch frame 2 is guaranteed.
  • the switching hollow shaft 54 the slip member 11 acts as a multi-plate clutch and couples the two planetary stages 22 and 42 via their respective ring gears 28 and 48.
  • the motor 15 and the holding brake 6 are de-energized switched so that the holding brake 6 closes under spring pressure and the motor 15 and the Drive shaft 16 sets.
  • the one-way clutch 17 is opened so that the drive shaft 16 is decoupled from the sun gear 43 of the drive planetary stage 42.
  • the switching hollow shaft 59 can be in the position "load stroke with manual force fast" or "load stroke with manual force slow” be moved.
  • the "load stroke with manual force slow” position disengages the external gear 55 and the internal gear 56 engages the torsionally rigid with the sun gear 43 of the drive planetary stage 42 connected gear 57 brought.
  • This is an access to the fast rotating and low torque absorbing sun gears 23 and 43 like him is particularly desirable for manual operation.
  • the operator also has two Different stroke ratios are available, namely for the heavy goods train and for the Rapid traverse with very different effort.
  • the one-way clutch 17 also provides sure that if a lifting force on the crank handle 53 is lost, the load remains in suspension and cannot sink by itself by setting the sun gear 43.
  • the winch drum 2 can thus under the weight of a load against the direction of rotation in Turn lifting operation.
  • the one-way clutch 17 prevents the sun gear 43 from rotating, so that in free fall when the load drops, a relative speed at the slip member 11 can arise.
  • the rotation of the winch drum 3 is controlled via the output planetary stage 22 transferred to the drive planetary stage 42 and thus to the ring gear 48.
  • the Thrust pieces 50 and thus the centrifugal force devices 13, 51, 52 are on the primary part 48a and thus fastened to the ring gear 48 in a torsionally rigid manner, thus rotating with it.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Braking Arrangements (AREA)
  • Maintenance And Inspection Apparatuses For Elevators (AREA)
  • Mechanical Operated Clutches (AREA)
EP95120468A 1994-12-23 1995-12-22 Winde mit einer als Freifallbremse verwendbaren Kupplung Expired - Lifetime EP0720962B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4446443 1994-12-23
DE4446443A DE4446443C2 (de) 1994-12-23 1994-12-23 Winde mit einer als Freifallbremse verwendbaren Kupplung

Publications (2)

Publication Number Publication Date
EP0720962A1 EP0720962A1 (de) 1996-07-10
EP0720962B1 true EP0720962B1 (de) 2001-04-04

Family

ID=6537009

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95120468A Expired - Lifetime EP0720962B1 (de) 1994-12-23 1995-12-22 Winde mit einer als Freifallbremse verwendbaren Kupplung

Country Status (5)

Country Link
EP (1) EP0720962B1 (no)
AT (1) ATE200267T1 (no)
DE (1) DE4446443C2 (no)
DK (1) DK0720962T3 (no)
NO (1) NO311294B1 (no)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220220756A1 (en) * 2019-04-26 2022-07-14 Fabrications Tjd Inc. Impactor apparatus operated from rotorcraft

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AUPQ403099A0 (en) * 1999-11-15 1999-12-09 Muir Engineering Pty. Limited Free fall windlasses
DE102010062560B4 (de) 2010-08-12 2012-09-13 Zollern Gmbh & Co. Kg Winde mit Fliehkraftregeleinheit
RU2552785C1 (ru) * 2014-01-27 2015-06-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Южно-Уральский государственный университет" (национальный исследовательский университет) (ФГБОУ ВПО "ЮУрГУ" (НИУ)) Мобильная лебедка
DE202017105348U1 (de) * 2017-09-05 2018-12-07 Liebherr-Components Biberach Gmbh Freifallwinde
CN109368525B (zh) * 2018-10-30 2020-08-07 姜启胜 安装有自动换挡的行星齿轮变速器的卷扬机
US11078058B2 (en) 2019-03-28 2021-08-03 Goodrich Corporation Overload clutch assembly for hoist

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1028925A (fr) * 1949-11-04 1953-05-28 Westinghouse Electric Corp Commande à démultiplication pour appareils de levage
US4328954A (en) * 1979-05-07 1982-05-11 Pettibone Corporation Winch with compact, high efficiency and high ratio gearing suitable for free fall
DE3223632A1 (de) * 1982-06-22 1983-12-22 Mannesmann AG, 4000 Düsseldorf Freifallwinde
DE4134722C3 (de) * 1991-10-21 1998-02-26 Fuerstlich Hohenzollernsche We Freifallwinde

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20220220756A1 (en) * 2019-04-26 2022-07-14 Fabrications Tjd Inc. Impactor apparatus operated from rotorcraft

Also Published As

Publication number Publication date
NO311294B1 (no) 2001-11-12
EP0720962A1 (de) 1996-07-10
ATE200267T1 (de) 2001-04-15
DK0720962T3 (da) 2001-05-07
DE4446443A1 (de) 1996-06-27
DE4446443C2 (de) 1996-10-02
NO955212D0 (no) 1995-12-21
NO955212L (no) 1996-06-24

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