EP0448021B1 - Einrichtung zum Heben einer Last mittels zwei parallelen, synchron drehenden Trommeln - Google Patents

Einrichtung zum Heben einer Last mittels zwei parallelen, synchron drehenden Trommeln Download PDF

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Publication number
EP0448021B1
EP0448021B1 EP91104174A EP91104174A EP0448021B1 EP 0448021 B1 EP0448021 B1 EP 0448021B1 EP 91104174 A EP91104174 A EP 91104174A EP 91104174 A EP91104174 A EP 91104174A EP 0448021 B1 EP0448021 B1 EP 0448021B1
Authority
EP
European Patent Office
Prior art keywords
load
drum
plate
hoisting device
disk
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
EP91104174A
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English (en)
French (fr)
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EP0448021A1 (de
Inventor
Gérard Freneix
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ACB
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ACB
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Publication date
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Publication of EP0448021A1 publication Critical patent/EP0448021A1/de
Application granted granted Critical
Publication of EP0448021B1 publication Critical patent/EP0448021B1/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
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • 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
    • B66D1/54—Safety gear
    • 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
    • B66D1/26—Rope, cable, or chain winding mechanisms; Capstans having several drums or barrels

Definitions

  • the present invention relates to a load lifting system comprising a geared motor group with two parallel output pinions in which each output pinion respectively drives a lifting device, each lifting device comprising a toothed ring meshing with the corresponding output pinion and driving a winch drum whose rotation in the direction corresponding to the descent of the load ensures the coupling of a clutch.
  • GB-A-2 179 618 describes such a system.
  • the load 30 is suspended from the lifting device by a single double-pass cable 31, 32 ensuring a reduction.
  • the two drums 15 and 16 are mounted on a single shaft, therefore very long.
  • the clutch system is such that it requires brakes 29 and emergency brakes 28 because the load tends to cause the motor 23 to rotate in the direction of descent and it must therefore be able to brake it.
  • the object of the invention is to propose a lifting system ensuring anti-fall security by redundancy of the lifting members situated between the load and the lifting gearmotor. In addition, it offers a clutch system requiring no brakes.
  • each lifting device is individually connected to the load by a cable attached to the corresponding drum and wound therein, in that said gear ring of each lifting device drives its drum by said clutch which is a friction clutch comprising an intermediate clutch disc comprising retaining pawls preventing its rotation in the direction corresponding to the descent of the load, the drum of each device of lifting being integral with a central shaft, and in that the central shaft of one of the lifting devices is synchronized in rotation with the central shaft of the other lifting device by means of a plate coupling and coupling disc provided with orthogonal pins, or orthogonal grooves, the two shafts central being supported by a fixed frame.
  • said clutch which is a friction clutch comprising an intermediate clutch disc comprising retaining pawls preventing its rotation in the direction corresponding to the descent of the load
  • the drum of each device of lifting being integral with a central shaft
  • the central shaft of one of the lifting devices is synchronized in rotation with the central shaft of the other lifting device by means of a plate coupling and coupling disc provided with ortho
  • said intermediate clutch disc of each lifting device is sandwiched between a hub ensuring the connection between said drum and said central shaft and comprising a bearing surface against said disc and a nut plate mounted on a threaded seat of said central shaft, said nut plate being driven in rotation by a centralizer integral with said toothed ring, said connection in rotation of the centralizer and said nut plate being effected by means allowing a slight axial displacement of said nut plate with respect to said centralizer, the rotation of said ring gear in the direction corresponding to the rise of said load causing the axial displacement of said plate-nut in the direction ensuring its application against said intermediate clutch disc.
  • the cable of each lifting device is attached to the load and then passes over a front idler pulley to be wound on the drum, the two deflection pulleys being mounted at the two ends of a lifter articulated horizontally in the middle to a fixed part secured to said frame, vertical to said load, the movement of said lifter being limited between two stops each provided with a detector.
  • said load is mounted to slide along a vertical column.
  • FIG. 1 showing the principle of the system for lifting a load according to the invention, there is seen a geared motor 1 comprising at each of its ends an output pinion: pinion 2 to the right and pinion 3 to left. These pinions are arranged in parallel and are strictly integral in rotation.
  • the pinion 2 drives a first lifting device which is connected to a load 4 by a first cable 5.
  • This first lifting device on the right in the figure, comprises a toothed crown 6 which drives, by means of a friction clutch 7, a first winch drum 8 on which the first cable 5 is wound and unwound. and to which it is attached.
  • the left pinion 3 also drives a second lifting device which is connected to the load 4 by a second cable 9.
  • This second lifting device located on the left in the figure, is identical to the first and comprises a ring gear 6A, a friction clutch 7A and a winch drum 8A.
  • the friction clutch 7 (or 7A) comprises an intermediate clutch disc which includes retaining pawls preventing its rotation in the direction which corresponds to the descent of the charge 4.
  • This lifting system is thus redundant and ensures the maintenance of the load 4 whatever the failure of any one or more members of one of the two lifting devices, including the output pinion of the gear motor and the cable, on condition that this failure, or these failures, only occur on one of the two lifting devices, right or left.
  • the clutch for each side, is ensured automatically by the rotation of the output pinion in the direction ensuring the rise of the load 4.
  • the rotation of the drum 8 in the direction corresponding to the Descent of the load 4 also has the automatic effect of ensuring the clutch of the friction clutch 7, the intermediate disc of which is retained by its pawls in the direction of rotation corresponding precisely to this descent of the load.
  • the descent of the load is carried out by an alternative succession of disengaging and clutching the friction clutch by controlling the gear motor in the opposite direction of the ascent: the disengagement being caused by this rotation and the clutch by the rotation of the drum under the weight of the load.
  • each drum is integral with a central shaft: 10 for the right-hand device and 11 for the left-hand device which are synchronized in rotation by a coupling with plates 12 and 13 and coupling disc 14 provided with pins, or of grooves, orthogonal.
  • a coupling is known per se and bears the name of "joint of oldham ".
  • This synchronization device is particularly advantageous because it avoids a single long shaft, it allows the uncoupling of the two shafts for focusing and in particular to make up for the play resulting from a permanent and not identical, inevitable elongation of the two cables.
  • the "oldham joint" comprises a plurality of tenons, and orthogonal grooves so as to allow making a 1/8 or 1/4 turn, for example, to one of the two shafts.
  • this coupling allows a non-alignment of the two shafts, allowing a certain distance d between axes.
  • the general lifting system of the invention is thus redundant, synchronized and entirely mechanical, leading to no particular requirement on the electrical part.
  • pulleys 15 and 16 are mounted at the ends of a lifting beam 17 which is articulated in its middle 18 to a fixed part, integral with the frame of the assembly (described below).
  • the horizontal articulation 18 is vertical to the load 4 which, in this case, is slidably mounted along a vertical column 19.
  • the load 4 can in reality be a support for an organ, for a tool or any charge.
  • the movement of the spreader 17 is limited between two stops 20 and 21 each provided with a detector 22 and 23. This system makes it possible to detect a differential elongation of the two cables 5 and 9 and therefore to carry out the adjustment said above.
  • Figure 2 shows the practical embodiment of the framed part A of Figure 1 comprising the gear motor 1 and the two lifting devices with synchronization.
  • the output pinion 2 meshes with the ring gear 6 which is integral with a centering device 24 which comprises several drive fingers 25 which penetrate into recesses 26 of a nut plate 27 mounted on a threaded seat 28 of the central shaft 10.
  • the recess 26 is deep enough to allow a slight axial movement of the nut plate 27 relative to the centralizer 24 , by screwing and unscrewing the nut plate 27 on the threaded surface 28.
  • the central shaft 10 and the centralizer 24 are rotatably supported by a fixed frame 29 in several parts, by means of ball bearings 30, 31, 32, 33.
  • the bearing 33 is mounted in a bearing 34 fixed to the frame 29.
  • the central shaft 10 is integral with a hub 35 to which the drum 8 is fixed by means of a plate 36.
  • the drum 8 rotates around portions of the fixed frame 29 by rubbing on seals 37, 38 sealing the interior of the mechanism.
  • the hub 35 has a flat surface 39, in the form of a circular crown which sandwiches, with the nut plate 27, an intermediate clutch disc 40 provided with crowns 41, 42 made of a material ensuring good friction.
  • This intermediate clutch disc has pawls 43 with spring 44. These pawls pivot about an axis 45.
  • a fixed toothed ring 46 is linked to the frame 29 by screws 47.
  • the intermediate clutch disc can thus only rotate in the direction of arrow F (FIG. 4) which corresponds to the rotation of the geared motor group 1 in the direction ensuring the rise of the load 4.
  • the central shaft carries the plate 12 which is in abutment on the right against a collar 48 in two parts.
  • the plate 12 carries grooves 49, at least two grooves located at 90 ° from one another, and in practice several pairs of grooves at 90 °, each pair of grooves being offset from the following by a certain angle for example 15 ° or 30 ° so as to allow the length of the cables 5 and 9 to be adjusted.
  • the operation is as follows: To raise the load, the gearmotor is rotated in the direction that causes the nut-plate 27 to be screwed to the right. When, taking into account the weight of the load 4, the tightening of the disc 40 between the plate- nut 27 and the hub 35 is sufficient, the rotation of the nut plate 27 then also rotates the hub 35 and therefore the drum 8 and the central shaft 10 linked to this hub. The rotation of the drum in the opposite direction being, in this engaged position, absolutely impossible because of the ratchet disc 40.
  • the clutch To lower the load, the clutch must be released. To do this, the gear motor 1 is rotated in the opposite direction, which causes the nut plate 27 to move to the left, thus freeing the hub 35 and therefore the drum 8 which rotates under the weight of the load in the direction of the descent (by turning relative to the intermediate disc 40 retained by its pawls 43). However, this rotation of the hub 35 also causes the rotation of the central shaft 10, which immediately causes the nut plate 27 to tighten against the disc 40 and the hub 35, stopping the descent of the load, unless the gear motor keeps spinning. The descent is therefore carried out by an alternative succession of clutch and disengage, the descent speed being in practice perfectly controlled by the speed of rotation of the gear motor 1 and smoothly by a slight sliding of the hub 35 against the intermediate clutch disc 40.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Jib Cranes (AREA)
  • Carriers, Traveling Bodies, And Overhead Traveling Cranes (AREA)
  • Braking Arrangements (AREA)

Claims (4)

  1. System zum Anheben einer Last (4) mit einer Motor-Getriebe-Einheit (1), die zwei parallele, je eine Hebevorrichtung antreibende Ausgangsritzel (2, 3) besitzt, wobei jede Hebevorrichtung einen mit dem entsprechenden Ausgangsritzel (2, 3) kämmenden Zahnkranz (6, 6A) besitzt und eine Seiltrommel (8, 8A) antreibt, deren Drehung in einer der Absenkbewegung der Last entsprechenden Richtung die Ankopplung einer Kupplung bewirkt, dadurch gekennzeichnet, daß jede Hebevorrichtung individuell mit der Last über ein an der entsprechenden Trommel befestigtes und auf diese aufzuwickelndes Seil (4, 5) verbunden ist, daß der Zahnkranz (6, 6A) jeder Hebevorrichtung ihre Trommel (8, 8A) über die Kupplung antreibt, die eine Reibungskupplung ist und eine Zwischenkupplungsscheibe (40) mit Sperrklinken (43) besitzt, die die Drehung der Scheibe in der dem Absenken der Last (4) entsprechenden Richtung verhindern, wobei die Trommel jeder Hebevorrichtung mit einer zentralen Welle (10, 11) fest verbunden ist, und daß die zentrale Welle einer der Hebevorrichtungen mit der zentralen Welle der anderen Hebevorrichtung über eine Drehkupplung mit Platten (12, 13) und Kupplungsscheibe (14) synchronisiert ist und die Kupplungsscheibe (14) senkrechte Zapfen (50) oder senkrechte Rillen besitzt und die beiden zentralen Wellen von einer festen Struktur (29) getragen werden.
  2. Hebevorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Zwischenkupplungsscheibe (40) jeder Hebevorrichtung zwischen einer Nabe (35), die die Verbindung zwischen der Trommel (8) und der zentralen Welle (10) herstellt und eine Andruckfläche (39) gegen die Scheibe (40) besitzt, und einer schraubbaren Platte (27) bewirkt, die auf einem Gewindebereich (28) der zentralen Welle (10) aufgesetzt ist, wobei diese Platte (27) durch ein mit dem Zahnkranz (6) fest verbundenes Zentrierorgan (24) in Drehung versetzt wird und wobei die Drehverbindung zwischen dem Zentrierorgan (24) und der Platte (27) über ein Mittel (25, 26) erfolgt, das eine geringfügige axiale Verschiebung der schraubbaren Platte bezüglich des Zentrierorgans erlaubt, wobei die Drehung des Zahnkranzes (6) in der dem Anheben der Last (4) entsprechenden Richtung zu einer axialen Verschiebung der Platte (27) in der Richtung führt, die diese Platte gegen die Zwischenkupplungsscheibe (40) anlegt.
  3. Hebesystem nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, daß das Seil (5, 9) jeder Hebevorrichtung an der Last (4) befestigt ist, dann über eine Umlenkrolle (15, 16) verläuft, ehe es auf der Trommel (8, 8A) aufgewickelt wird, wobei die beiden Umlenkrollen (15, 16) an den beiden Enden eines Balkens (17) montiert sind, der in seiner Mitte (18) an einen festen Bereich der Struktur (29) senkrecht zur Last (4) angelenkt ist, wobei die Bewegung des Balkens (17) durch zwei je einen Detektor (22, 23) aufweisende Anschläge (20, 21) begrenzt ist.
  4. Hebesystem nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Last entlang einer senkrechten Säule gleitend montiert ist.
EP91104174A 1990-03-21 1991-03-18 Einrichtung zum Heben einer Last mittels zwei parallelen, synchron drehenden Trommeln Expired - Lifetime EP0448021B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9003625 1990-03-21
FR9003625A FR2659951B1 (fr) 1990-03-21 1990-03-21 Systeme de levage d'une charge a deux tambours fonctionnant en parallele, synchronises en rotation.

Publications (2)

Publication Number Publication Date
EP0448021A1 EP0448021A1 (de) 1991-09-25
EP0448021B1 true EP0448021B1 (de) 1994-09-14

Family

ID=9394964

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91104174A Expired - Lifetime EP0448021B1 (de) 1990-03-21 1991-03-18 Einrichtung zum Heben einer Last mittels zwei parallelen, synchron drehenden Trommeln

Country Status (15)

Country Link
US (1) US5324007A (de)
EP (1) EP0448021B1 (de)
JP (1) JPH04223997A (de)
KR (1) KR910016614A (de)
BG (1) BG60028A3 (de)
CA (1) CA2038711C (de)
CS (1) CS76691A2 (de)
DE (1) DE69103937T2 (de)
ES (1) ES2062586T3 (de)
FI (1) FI93202C (de)
FR (1) FR2659951B1 (de)
HU (1) HU208286B (de)
RO (1) RO107397B1 (de)
YU (1) YU47960B (de)
ZA (1) ZA912071B (de)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2324278A (en) * 1997-02-20 1998-10-21 J & A Promotions Ltd Vehicle with vertically movable deck
JP2000344449A (ja) 1999-06-02 2000-12-12 Teijin Seiki Co Ltd エレベータ用駆動装置
US6598859B1 (en) 2001-05-31 2003-07-29 Magnetek, Inc. Multiple hoist synchronization apparatus and method
CA2389957C (en) 2002-06-10 2009-08-04 Brent's Grading Ltd. Blade installation tool
FR2892785B1 (fr) * 2005-11-03 2008-01-18 Unicum Transmission De Puissan Dispositif de securite de transmission mecanique par engrenage irreversible a l'arret
FI118729B (fi) * 2006-04-04 2008-02-29 Kone Corp Järjestely hissikorin pysäyttämiseksi hätäjarrutustilanteessa ja hissi
EP1955976A1 (de) * 2007-02-08 2008-08-13 BAUER Maschinen GmbH Windenvorrichtung
US9624076B2 (en) * 2014-04-04 2017-04-18 David R. Hall Synchronized motorized lifting devices for lifting shared loads
CN104085809B (zh) * 2014-06-30 2016-05-04 东北大学 一种自适应负载卷扬机构
KR102642682B1 (ko) * 2023-11-02 2024-03-04 주식회사 에스디호이스트 로프 꼬임 교정용 리와인딩 장치 및 그 장치를 이용한 드럼 로프 와인딩 방법

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Publication number Priority date Publication date Assignee Title
US1609421A (en) * 1925-08-13 1926-12-07 Almon E Norris Clutch and brake mechanism
GB655450A (en) * 1949-06-08 1951-07-18 Austin Hopkinson Improvements in or relating to hoisting or haulage gear
DE1026505B (de) * 1957-03-30 1958-03-20 Maschf Augsburg Nuernberg Ag Hubwerk fuer Hebezeuge
US2984455A (en) * 1957-08-06 1961-05-16 California Research Corp Multiple-cable tensioning device
DE1202454B (de) * 1961-11-11 1965-10-07 Voest Ag Windwerk
GB978133A (en) * 1961-12-06 1964-12-16 Ass Elect Ind Couplings for non-aligned shafts
FR1495528A (fr) * 1966-07-26 1967-09-22 Mecaniques Ind Soc Atel Perfectionnements apportés aux treuils
DE1276311B (de) * 1966-08-09 1968-08-29 Maschf Augsburg Nuernberg Ag Vorrichtung zur Erzielung einer Auf- und Abwaertsbewegung einer durchziehenden Last
SU483825A3 (ru) * 1970-03-07 1975-09-05 Хеш Машиненфабрик Дейчланд Аг (Фирма) Подъемный механизм
GB1505244A (en) * 1975-10-10 1978-03-30 Gen Electric Winches for use with high masts
FR2380979A1 (fr) * 1977-02-21 1978-09-15 Bretagne Atel Chantiers Treuil de levage comportant un dispositif de securite
SE413833B (sv) * 1977-12-08 1980-06-30 Landstingens Inkopscentral Handdriven vinsch med backsperr serskilt som kraftdon inom sjukvarden
AT356322B (de) * 1977-12-27 1980-04-25 Waagner Biro Ag Kranhubwerk fuer einen laufkran, insbesondere fuer einen giess- oder reaktorkran
US4214664A (en) * 1978-08-24 1980-07-29 The Alliance Machine Company Crane safety reeving
US4489919A (en) * 1983-03-21 1984-12-25 Meyer Ostrobrod Safety winch with disengageable drive
US4653653A (en) * 1985-08-27 1987-03-31 The Alliance Machine Company Hoisting systems
US4851980A (en) * 1988-06-29 1989-07-25 Meade Industrial Services, Inc. Double drum level winding rope lift mechanism for luminaires on high lighting masts

Also Published As

Publication number Publication date
HUT60695A (en) 1992-10-28
US5324007A (en) 1994-06-28
KR910016614A (ko) 1991-11-05
DE69103937T2 (de) 1995-02-09
FI911314A0 (fi) 1991-03-18
HU910932D0 (en) 1991-10-28
CA2038711A1 (fr) 1991-09-22
FI93202C (fi) 1995-03-10
ES2062586T3 (es) 1994-12-16
JPH04223997A (ja) 1992-08-13
FI93202B (fi) 1994-11-30
FR2659951A1 (fr) 1991-09-27
FR2659951B1 (fr) 1992-05-29
EP0448021A1 (de) 1991-09-25
RO107397B1 (ro) 1993-11-30
CS76691A2 (en) 1991-09-15
ZA912071B (en) 1991-12-24
FI911314A (fi) 1991-09-22
BG60028A3 (en) 1993-07-15
YU47960B (sh) 1996-07-24
CA2038711C (fr) 1993-12-21
YU47291A (sh) 1994-09-09
HU208286B (en) 1993-09-28
DE69103937D1 (de) 1994-10-20

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