EP0538662B1 - Treuil à chute libre - Google Patents

Treuil à chute libre Download PDF

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Publication number
EP0538662B1
EP0538662B1 EP19920116897 EP92116897A EP0538662B1 EP 0538662 B1 EP0538662 B1 EP 0538662B1 EP 19920116897 EP19920116897 EP 19920116897 EP 92116897 A EP92116897 A EP 92116897A EP 0538662 B1 EP0538662 B1 EP 0538662B1
Authority
EP
European Patent Office
Prior art keywords
planetary stage
winch
brake
set forth
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
EP19920116897
Other languages
German (de)
English (en)
Other versions
EP0538662A3 (fr
EP0538662A2 (fr
Inventor
Winfried Felder
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 EP0538662A2 publication Critical patent/EP0538662A2/fr
Publication of EP0538662A3 publication Critical patent/EP0538662A3/xx
Application granted granted Critical
Publication of EP0538662B1 publication Critical patent/EP0538662B1/fr
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
    • 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 present invention relates to a free fall winch according to the preamble of claim 1.
  • a winch in particular a cable winch, whereby suitable traction means should generally be included under the term “rope”, often has the problem of a certain distance or with a load hanging on the winch hook or with the empty hook alone Rope length in "free fall", ie when the winch drum is idling, put back.
  • a hanging load is lowered in a controlled manner at high rope speeds.
  • a small cable pull should be adjustable independently of the drive, so that the cable can be reeled off cleanly with the setting of a defined residual cable.
  • a free-fall winch in a drilling machine, in which the drill pipe is quickly lowered in controlled free-fall and, during drilling, the rope is pulled off the rope drum with little but defined force depending on the drilling feed.
  • a free fall winch in a duty cycle crawler crane, in which a scraper bucket is thrown out by swiveling the superstructure with the boom quickly by unwinding the winch cable from the free-running drum when the drive is stopped.
  • a particular technical problem is the braking of the free-falling load or the free-running winch rope.
  • DE-OS 2 304 370 discloses a cable winch with a two-stage planetary gear, in which a motor drives the sun gear of the first planetary stage, the planetary web of which is connected to the sun gear of the second planetary stage. The planet stage of the second stage then drives the winch drum. To brake and hold the drum, a drum brake acting against the winch housing is provided.
  • a so-called free-fall winch whose cable drum is driven by a hydraulic motor via a planetary gear, the motor acting on the sun gear of a first planetary stage, the planetary web is connected to the sun gear of a second planetary stage, is disclosed by DE-PS 3 223 632.
  • the planet web of the second planetary stage is connected to the winch frame, while a drum brake acting on the cable drum is attached to the common ring gear of the two planetary stages.
  • the inner and outer jaws of this drum brake enclose a ring segment of the winch drum.
  • the drum brake primarily fulfills the coupling function in that a frictional connection between the driven common ring gear and the cable drum is established by pressing the inner jaws, the so-called inner band, onto the cable drum.
  • the drum brake can also be used as a free-fall brake. In this case, the outer jaws of the drum brake, the outer band, attached to the winch housing are pressed onto the winch drum.
  • drum brakes with organic dry linings are subject to high thermal loads, are subject to heavy wear and cannot be controlled sensitively as a result of fluctuations in the coefficient of friction.
  • the multi-disc brakes on the gearbox output which also serve as clutches, are of a large size for the torque that occurs and are therefore unnecessarily high in terms of acquisition costs.
  • DE-GM 75 16 081 relates to a drum winch with a single or multi-stage planetary gear housed in the drum.
  • a multi-disc brake is proposed as the brake, which is arranged entirely or partially within the axial extent of the drum.
  • a winch with a planetary gear between the drive shaft of the motor and the drum is known according to the preamble of claim 1.
  • the sun gear of a first gear stage sits on the drive shaft and drives the planet gear of this first gear stage via a first ring gear, the sun gear of a second stage, the ring gear of which is supported on the winch housing and the planet web is connected to the winch drum.
  • the planet gears of the first gear stage are simultaneously in meshing engagement with a second ring gear of this first gear stage, which is also supported on the winch housing.
  • the planetary web of the first gear stage can be braked with respect to this second ring gear by means of a multi-disc brake.
  • the torques to be absorbed by the brake can be reduced in proportion to the reduction ratio of the upstream stage to the output stage and the brake can be designed with a smaller diameter that is less expensive. Since the large multi-disc brakes commonly used make up a large proportion of the acquisition costs for the entire winch, considerable savings can be made in relation to the total price for the winch.
  • the invention fundamentally opens up the possibility of driving this still free web by means of a second drive and using the gear as a superimposition gear, whereby the range of use of the winch according to the invention can be expanded.
  • a motor for example a hydraulic or hydraulic motor, expediently drives the sun gear of the upstream planetary stage. According to its function, this stage is therefore referred to below as the drive planet stage.
  • the reduction in the torques to be absorbed by the brake is achieved according to the invention by an intermediate planetary stage arranged between the output planetary stage and the upstream planetary stage, which in turn is driven by the drive stage and drives to the output stage.
  • the drive and intermediate planetary stages form a coupling gear, in which the respective free links, which in turn are not used for driving or driving downstream or upstream gear stages, are coupled in a torsionally rigid manner.
  • the respective ring gears of the drive and intermediate planetary stages are preferably coupled in a torsionally rigid manner.
  • the planetary web of the intermediate planetary stage is rotationally rigidly connected to the ring gear of the drive planetary stage or the planetary web of the drive planetary stage is torsionally rigidly connected to the ring gear of the intermediate planetary stage.
  • the torsionally rigid connection can be produced by mutual welding, screwing and / or suitable accommodation in a common housing.
  • the torsionally rigidly connected members of these planetary stages are advantageously freely rotatably mounted both with respect to the housing and with respect to the drum of the cable winch.
  • a particular advantage of the present invention is also due to the fact that the non-aborting web of the drive planetary stage - also referred to as a free link -, namely the planetary web or the ring gear, are attached to a shaft which can be braked on the one hand to stop the free-running winch drum, which on the other hand can serve as a drive shaft for a second drive motor.
  • the rotary movements of two drive motors are brought together on the drive planetary stage, superimposed and transmitted via their output land to the first planetary stage, which serves as the output stage for the winch drum.
  • a type of modular system is thus created in which the free-fall brake and the second drive motor can be exchanged in a module-like manner or both can be used simultaneously in order to be able to perform the function of either a free-fall winch or a high-speed winch or in combination of a kind of "all-round winch".
  • the shaft for the driven sun gear of the input planetary stage is rotatably mounted within the hollow shaft of the torsionally rigidly connected ring gears.
  • Both shafts abbreviated as brake or output shaft, can be braked by two separate multi-disc brakes.
  • the free-fall brake according to the invention takes on the additional function of locking the two torsionally rigidly connected ring gears of the input and intermediate planetary stages relative to the housing in order to enable the winch drum to be activated.
  • the brake is designed as a multi-disc brake and brakes a shaft, to which the non-aborting web of the upstream planetary stage is attached, against the frame of the cable winch. If on the one hand lower torques are to be braked, on the other hand the specific thermal load in the brake arrangement selected according to the invention increases as a result of the higher speeds to be braked.
  • the lamella surfaces are therefore advantageously flooded with oil for cooling purposes.
  • FIGS. 1 and 2 show two simple alternative embodiments of cable winches 1 with known two-stage planetary gears.
  • the two-stage planetary gear 10 is arranged in a housing pot 8, which in turn is located in the drum 2, to which it is connected in a torsionally rigid manner.
  • the drum 2 is rotatably mounted in the frame 3 of the winch 1.
  • An arrow marked “L” indicates the direction of force of a load hanging on the winch drum 2.
  • a first drive motor 15 drives a sun gear 43 of a planetary stage 42 via a drive shaft 16, which is therefore referred to below as the drive planetary stage 42.
  • the rotary movement of the sun gear 43 is transmitted to the sun gear 23 of a first planetary stage via a common planet web 44 of the planet gears 45, 46 and 47 (not shown).
  • the sun gear 23 is connected to the planetary web 44 via a hollow shaft 21.
  • the rotational movement of the sun gear 23 is transmitted via the planet gears 25, 26 and the planet gear 27, not shown, to the ring gear 28 of the first planetary stage, which is connected to the housing pot 8 and thus the drum 2 in a torsionally rigid manner.
  • the first planetary stage 22, which will be referred to in the following in terms of function as the output planetary stage 22, thus has planetary gears 25, 26 and 27, which absorb the reaction forces of the drum 2 as a result of their support against the frame 3.
  • the ring gear 48 of the drive planetary stage 42 is fastened to a shaft 12 which is rotatably mounted relative to the housing pot 8 of the planetary gear 10 and the frame 3 of the cable winch 1 and on which a brake 11, which is fixedly connected to the winch frame 3, acts as a free-fall brake. Due to this arrangement of the free-fall brake 11, comparatively high speeds must be used are braked, which on the other hand, however, is accompanied by a proportional reduction in the torque to be absorbed.
  • the thermal load can be controlled by using an oil-filled multi-disc brake 11.
  • the brake 11 is arranged outside the winch frame 2 in the exemplary embodiment and is therefore easily accessible in the event of necessary maintenance and repair work.
  • a dashed line shows a second drive motor 17, which drives the ring gear 48 of the drive planetary stage 42 via the shaft 12 which now serves as the drive shaft.
  • the drive planetary stage 42 now transmits the superimposed rotary movements of both drive motors 15 and 17 to the sun gear 23 of the output planetary stage 22 by means of its planetary web 44.
  • Fig. 2 shows an alternative embodiment with a known planetary gear, which differs from that shown in Fig. 1 only in that instead of the planetary web 44, the ring gear 48 of the drive planetary stage 42 serves as an output web for the output planetary stage 22.
  • the planetary web 44 of the drive planetary stage 42 is the non-abrading web (free link), which can be braked with respect to the winch frame 3 by the free-fall brake 11.
  • a three-stage planetary gear 10 is used, in which an intermediate planetary stage 32 is driven by the driven planetary web 44 of the drive planetary stage 42 and whose planetary web 34 in turn serves as an output to the output planetary stage 22.
  • the abrupt planetary webs 44 and 34 are each connected via hollow shafts 21 and 19 to the sun gears 33 and 23 of the subsequent planetary stages.
  • the drive shaft 16 of the drive motor 15 extends through both hollow shafts 19 and 21 to the sun gear 43 of the drive planetary stage 42.
  • the free, non-abrasive ring gears 32 and 42 of the intermediate and drive planetary stages 32 and 42 are torsionally rigidly connected to one another and arranged in a common connecting bell 9.
  • the connecting bell 9, which can be designed as a tin pot or made from a suitable light metal alloy, is at 19 and 29 with respect to the housing pot 8 of the planetary gear 10 and the winch frame 3 is freely rotatable.
  • the shaft 12 serves only as a brake shaft on which the free-fall brake 11, which is designed as a multi-disc brake, engages, which in turn is fastened to the winch frame 3.
  • the intermediate and drive planetary stages 32 and 42 together form, via their torsionally rigidly interconnected ring gears 38 and 48, a coupling gear 40 with a rotating housing designed as a connecting bell 9. Only its reaction torque is fed to the correspondingly small brake 11.
  • the second drive motor 17 drives a sun gear 63 of an additional input planetary stage 62 via a drive shaft 18.
  • the planetary web 64 of this input planetary stage 62 is torsionally rigidly connected to the ring gear 48 of the drive planetary stage 42.
  • the rotary movements of the first and second drive motors 15 and 17 are now brought together and superimposed on the drive planetary stage 42 and are driven via their planetary web 44 onto the sun gear 33 of the intermediate planetary stage 32 connected downstream.
  • the connecting bell 9 in which the ring gears 38 and 68 of the intermediate and input planetary stages 32 and 62 are arranged so as to be torsionally rigid, is again attached to the shaft 12 on which the free-fall brake 11 engages.
  • the intermediate and input planetary stages 32 and 62 form a superimposed coupling gear 41 due to their torsionally rigid connection together with the drive planetary stage 42.
  • the shaft 12 is designed as a hollow shaft through which the drive shaft 18 of the second drive motor 17 extends.
  • a multi-disc brake 7 or 11 is provided for both the shaft 12 and the drive shaft 18. In operation as a free-fall winch, the winch drum 2 is released by actuating the brake 11. The two holding brakes 6 and 7 remain closed.
  • the planetary gear 10 acts as a superposition gear for the two drive motors 15 and 17.
  • the cable winch 1 is in this case used as a high-speed Winch operated. At closed brakes 6 and 11, but released brake 7, a fine lift operation of the cable winch 1 can be realized by driving the second drive motor 17 alone, with a corresponding translation of the input planetary stage.
  • This embodiment clearly shows the high versatility of the cable winch due to the modular combination of the functional elements free fall brake 11 and second drive motor 17.

Claims (19)

  1. Treuil à chute libre
    a) avec un moteur d'entraînement (15),
    b) avec un étage planétaire entraîné (22),
    b1) dont la roue solaire (23) est entraînée,
    b2) dont le porte-planétaire (24) ou la roue creuse (28) s'appuient sur le bâti (3) du treuil (1),
    b3) dont l'organe restant libre est relié à rotation solidaire à un tambour (2) du treuil (1),
    c) avec un étage d'entraînement à planétaires (42),
    c1) dont la roue solaire (43) est entraînée,
    c2) dont le porte-planétaire (44) ou la roue creuse (48) entraînent la roue solaire (23) de l'étage entraîné à planétaires (22), et
    d) avec un frein (11) pour le freinage ou la libération du tambour (2) du treuil,
    e) l'organe restant libre (44 ou 48) de l'étage d'entraînement à planétaires (42) pouvant être freiné par le frein (11),
    caractérisé en ce que
    f) entre l'étage d'entraînement à planétaires (42) et l'étage entraîné à planétaires (22) est intercalé un étage intermédiaire à planétaires (32) qui forme un mécanisme d'accouplement (40) avec l'étage d'entraînement à planétaires (42), et
    g) les deux organes libres (44 ou 48, 34 ou 38) respectifs de l'étage d'entraînement à planétaires et de l'étage intermédiaire à planétaires (42, 32) qui ne sont pas utilisés pour l'entraînement d'un étage de transmission situé en aval ou pour la réception de l'entraînement d'un étage de transmission situé en amont sont accouplés à rotation solidaire.
  2. Treuil à chute libre selon la revendication 1, caractérisé en ce que la roue creuse (48) de l'étage d'entraînement à planétaires (42) peut être freinée par le frein (11) par l'intermédiaire d'un arbre (12).
  3. Treuil à chute libre selon la revendication 1, caractérisé en ce que le porte-planétaire (44) de l'étage d'entraînement à planétaires (42) peut être freiné par le frein (11) par l'intermédiaire d'un arbre (12).
  4. Treuil à chute libre selon l'une des revendications 1 à 3, caractérisé en ce que la roue creuse (38) de l'étage intermédiaire à planétaires (32) et la roue creuse (48) de l'étage d'entraînement à planétaires (42) sont reliés à rotation solidaire à une cloche de liaison (9) qui peut être freinée par le frein (11).
  5. Treuil à chute libre selon l'une des revendications 1 à 3, caractérisé en ce que la roue creuse (38) de l'étage intermédiaire à planétaires (32) et la traverse (44) de l'étage d'entraînement à planétaires (42) sont reliés à rotation solidaire à une cloche de liaison (9) qui peut être freinée par le frein (11).
  6. Treuil à chute libre selon l'une des revendications 1 à 3, caractérisé en ce que la traverse de planétaire (34) de l'étage intermédiaire à planétaires (32) et la roue creuse (48) de l'étage d'entraînement à planétaires (42) sont reliées à rotation solidaire à une cloche de liaison (9) qui peut être freinée par le frein (11).
  7. Treuil à chute libre selon l'une des revendications 2 ou 3, caractérisé en ce que pour réduire le couple de protection de l'arbre de frein (12), un étage supplémentaire à planétaires (62) est intercalé entre ce dernier et la transmission d'accouplement (40).
  8. Treuil à chute libre selon la revendication 7, caractérisé en ce que la roue creuse (38) de l'étage intermédiaire à planétaires (32) et la roue creuse (68) de l'étage supplémentaire à planétaires (62) sont reliées à rotation solidaire à une cloche de liaison (9) qui peut être freinée par le frein (11).
  9. Treuil à chute libre selon l'une des revendications 4 à 8, caractérisé en ce que la cloche de liaison (9) est montée à rotation libre par rapport au boîtier (3) du treuil à câble (1) et par rapport au tambour d'enroulement (2).
  10. Treuil à chute libre selon l'une des revendications 1 à 9, caractérisé en ce que la traverse de planétaire (34) de l'étage intermédiaire à planétaires (32) entraîne la roue solaire (23) de l'étage entraîné à planétaires (22).
  11. Treuil à chute libre selon l'une des revendications 1 à 10, caractérisé en ce que la roue solaire (23, 33) de l'étage entraîné à planétaires (22) ou de l'étage intermédiaire à planétaires (32) est configurée comme arbre creux (19, 21) traversé par l'arbre d'entraînement (16) du moteur d'entraînement (15).
  12. Treuil à chute libre selon l'une des revendications 1 à 11, caractérisé en ce que l'étage d'entraînement à planétaires (42) forme avec l'étage supplémentaire à planétaires (62) un étage de superposition (42), la roue creuse (48) ou la traverse (44) de l'étage d'entraînement à planétaires (42) pouvant être entraînées par un deuxième moteur d'entraînement (17) par l'intermédiaire de l'étage supplémentaire à planétaires (62).
  13. Treuil à chute libre selon la revendication 12, caractérisé en ce que pour augmenter le couple du deuxième moteur d'entraînement (17), il est prévu un étage supplémentaire à planétaires (62), dont la roue solaire (63) peut être entraînée par le deuxième moteur d'entraînement (17).
  14. Treuil à chute libre selon la revendication 13, caractérisé en ce que le deuxième moteur d'entraînement (17) et le frein (11) sont placés sur deux arbres (12, 18) distincts.
  15. Treuil à chute libre selon la revendication 14, caractérisé en ce que les deux arbres (12, 18) peuvent être freinés par des freins (7, 11) qui peuvent être actionnés indépendamment l'un de l'autre.
  16. Treuil à chute libre selon la revendication 15, caractérisé en ce que le deuxième frein (7) est configuré comme frein d'arrêt.
  17. Treuil à chute libre selon l'une des revendications 1 à 16, caractérisé en ce que le premier et/ou le deuxième moteur d'entraînement (15, 17) sont réalisés sous la forme de moteurs hydrauliques.
  18. Treuil à chute libre selon l'une des revendications 4 à 6 ou 8 ou 9, caractérisé en ce que la cloche de liaison (9) est réalisée en un alliage de métaux légers ou sous la forme d'une cloche en tôle.
  19. Treuil à chute libre selon l'une des revendications 12 à 18, caractérisé en ce que, lorsque le frein (11) est ouvert, le deuxième moteur d'entraînement (17) est prévu en vue d'accélérer plus rapidement la rotation du tambour de câble (2) et des parties de la transmission qui lui sont reliées.
EP19920116897 1991-10-21 1992-10-02 Treuil à chute libre Expired - Lifetime EP0538662B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19914134722 DE4134722C3 (de) 1991-10-21 1991-10-21 Freifallwinde
DE4134722 1991-10-21

Publications (3)

Publication Number Publication Date
EP0538662A2 EP0538662A2 (fr) 1993-04-28
EP0538662A3 EP0538662A3 (fr) 1994-08-03
EP0538662B1 true EP0538662B1 (fr) 1997-05-28

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920116897 Expired - Lifetime EP0538662B1 (fr) 1991-10-21 1992-10-02 Treuil à chute libre

Country Status (3)

Country Link
EP (1) EP0538662B1 (fr)
DE (1) DE4134722C3 (fr)
NO (1) NO304780B1 (fr)

Cited By (3)

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CN102328886A (zh) * 2011-07-20 2012-01-25 徐州科源液压有限公司 卷扬减速机
DE202017105348U1 (de) 2017-09-05 2018-12-07 Liebherr-Components Biberach Gmbh Freifallwinde
DE102017120490A1 (de) 2017-09-06 2019-03-07 Liebherr-Components Biberach Gmbh Freifallwinde

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DE29609536U1 (de) * 1996-05-30 1997-10-30 Siebenhaar Antriebstechnik Gmb Zweistufiges Getriebe zum Einbau in eine Freifallwinde
DE10120249C1 (de) * 2001-04-25 2002-10-02 Lohmann & Stolterfoht Gmbh Freifallwinde
DE102010062560B4 (de) * 2010-08-12 2012-09-13 Zollern Gmbh & Co. Kg Winde mit Fliehkraftregeleinheit
DE102014117981B4 (de) 2014-12-05 2020-12-03 Zollern Gmbh & Co. Kg Winde mit einer Notabsenkeinrichtung
EP3028983B1 (fr) 2014-12-05 2018-02-07 Zollern GmbH & Co. KG Treuil, en particulier treuil à chute libre doté d'un frein de service et d'arrêt
DE102015003980A1 (de) * 2015-03-26 2016-09-29 Liebherr-Werk Nenzing Gmbh Verfahren zur Steuerung einer Baumaschine sowie Schürfkübelbagger
US20180111806A1 (en) * 2016-10-24 2018-04-26 Ingersoll-Rand Company Dual capacity winch using two motors and a single gearbox and drum
DE102017116956A1 (de) 2017-07-26 2019-01-31 Zollern Gmbh & Co. Kg Winde, insbesondere Freifallwinde mit einer Bremse
DE102017223472A1 (de) * 2017-12-20 2019-06-27 Zf Friedrichshafen Ag Winden-Schaltgetriebe

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102328886A (zh) * 2011-07-20 2012-01-25 徐州科源液压有限公司 卷扬减速机
CN102328886B (zh) * 2011-07-20 2013-08-21 徐州科源液压有限公司 卷扬减速机
DE202017105348U1 (de) 2017-09-05 2018-12-07 Liebherr-Components Biberach Gmbh Freifallwinde
WO2019048303A1 (fr) 2017-09-05 2019-03-14 Liebherr-Components Biberach Gmbh Treuil à chute libre
DE102017120490A1 (de) 2017-09-06 2019-03-07 Liebherr-Components Biberach Gmbh Freifallwinde
WO2019048282A1 (fr) 2017-09-06 2019-03-14 Liebherr-Components Biberach Gmbh Treuil à chute libre
CN111511671A (zh) * 2017-09-06 2020-08-07 比伯拉赫利勃海尔零部件有限公司 自由下落绞车
CN111511671B (zh) * 2017-09-06 2021-11-16 比伯拉赫利勃海尔零部件有限公司 自由下落绞车

Also Published As

Publication number Publication date
DE4134722C3 (de) 1998-02-26
DE4134722A1 (de) 1993-04-22
DE4134722C2 (de) 1993-12-09
EP0538662A3 (fr) 1994-08-03
EP0538662A2 (fr) 1993-04-28
NO924053L (no) 1993-04-22
NO924053D0 (no) 1992-10-20
NO304780B1 (no) 1999-02-15

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