EP3423392B1 - Dispositif d'entraînement pour le tambour à cable d'un treuil à cable - Google Patents

Dispositif d'entraînement pour le tambour à cable d'un treuil à cable Download PDF

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Publication number
EP3423392B1
EP3423392B1 EP17708972.9A EP17708972A EP3423392B1 EP 3423392 B1 EP3423392 B1 EP 3423392B1 EP 17708972 A EP17708972 A EP 17708972A EP 3423392 B1 EP3423392 B1 EP 3423392B1
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EP
European Patent Office
Prior art keywords
drive
gear
drive connection
connection
output shaft
Prior art date
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Active
Application number
EP17708972.9A
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German (de)
English (en)
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EP3423392A1 (fr
Inventor
Stefan Beyersdorff
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.)
Rotzler Holding GmbH and Co KG
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Rotzler Holding GmbH and Co KG
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.)
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Application filed by Rotzler Holding GmbH and Co KG filed Critical Rotzler Holding GmbH and Co KG
Publication of EP3423392A1 publication Critical patent/EP3423392A1/fr
Application granted granted Critical
Publication of EP3423392B1 publication Critical patent/EP3423392B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/12—Driving gear incorporating electric motors
    • 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
    • B66D1/20—Chain, belt, or friction drives, e.g. incorporating sheaves of fixed or variable ratio
    • 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
    • B66D1/225—Planetary or differential gearings, i.e. with planet gears having movable axes of rotation variable ratio or reversing gearing

Definitions

  • the invention relates to a drive device for the cable drum of a winch.
  • Drive devices for the cable drum of a cable winch are generally known. They include a drive motor with a drive shaft, a gear and an output shaft driving the cable drum.
  • the transmission has a drive connection between the drive shaft of the drive motor and the output shaft to the cable drum.
  • the output shaft will be driven in a predetermined speed range via a gear ratio.
  • a low speed with high torque is advisable for pulling a load.
  • the drive connection between the drive shaft of the drive motor and the output shaft of the transmission is therefore designed accordingly.
  • a drive device for a cable drum of a cable winch which has a first and a second drive connection between the drive shaft of the drive motor and the output shaft to the cable drum.
  • the second drive connection is formed separately from the first drive connection as a parallel drive path and both drive connections are driven together by the drive shaft of the drive motor.
  • the first drive connection acts on the input shaft of a superposition gear, the housing of which is driven in rotation by the second drive connection.
  • the output shaft of the superposition gear connected to the cable drum rotates depending on an adjustable speed difference of the permanently engaged drive connections.
  • the DE 736 650 C. discloses a drive device for a winch, in which an adjustable belt drive with several belts is provided, which ensure permanent power transmission from the drive motor to the winch.
  • the invention is based on the object of specifying a drive device for the cable drum of a cable winch which, at the same drive speeds of the drive motor with only one drive unit, enables the cable drum to be operated in a slow pulling gear or in an overdrive gear, with a switchover without opening the drive connection between the cable drum and Drive motor or interrupting or stopping the train movement should be possible.
  • a first drive connection drives the output shaft over a first speed range in a first gear and a second drive connection between the drive motor and the output shaft drives the output shaft over a second speed range in a second gear.
  • the second drive connection is designed such that the cable drum can be driven in a second speed range.
  • the second drive connection is formed separately from the first drive connection and forms a parallel drive path which can be switched on and off without interrupting the first drive path. Both drive connections are driven together by the drive shaft of the drive motor. If the second drive connection is effective and the output shaft is driven in the second gear via the second drive connection, the flow of force of the first drive connection from the drive shaft to the output shaft is interrupted. The first drive connection nevertheless remains switched on, so that when the second drive connection is opened, the power flow via the first drive connection to the output shaft is closed again.
  • the construction of the drive device according to the invention ensures that in the event of a faulty second drive connection, for. B. in the event of a break in the second drive connection, the load cannot slip off, since the still existing first drive connection is effective and the load holds when the cable drum slows down. If the speed of the output shaft falls back into the first speed range, the first drive connection becomes effective without the user having to intervene.
  • the design of the drive device according to the invention enables the cable drum to be operated in a slow pull gear or in an overdrive gear at any instantaneous drive speed of the drive motor.
  • the gear change, d. H. the second drive connection is switched on without opening the first drive connection between the cable drum and the drive motor, so that there is no interruption or stopping of the train movement.
  • the first drive connection or the second drive connection is optionally in a torque-transmitting connection to the output shaft of the drive device.
  • the special design of the drive device with two parallel drive connections with different transmission ratios results in a switching ratio between the first drive connection and the second drive connection, which has a first value in a first switchover point when the second drive connection is switched on and a second value in another, second switchover point .
  • the switching ratio between the first drive connection and the second drive connection is advantageous solely by the choice z. B. pulley diameters and / or z. B. adjustable by the choice of meshing gears in a wide range. Since the switching ratio in simply by choosing z. B. the corresponding pulley diameter or the gears used can be configured, the rest of the gear construction can remain unchanged. The main structure and the spatial dimensions of the transmission remain unchanged when the switching ratio changes.
  • the first drive connection expediently has a freewheel, which is effective when the output shaft is driven by the second drive connection at a higher speed.
  • the freewheel allows a faster speed of the output shaft through the second drive connection without the first drive connection being opened mechanically. Only the flow of power is interrupted. If the second drive connection is interrupted, the speed of the output shaft drops until the power flow of the first drive connection engages the output shaft again and the output shaft is driven again via the first drive connection; the freewheel closes the output shaft in the drive direction of the first drive connection.
  • the drive connection is expediently formed from a first drive wheel, an intermediate wheel and a first driven wheel which interacts with the driven shaft.
  • the first drive connection and / or the second drive connection can be designed as a gear transmission.
  • the drive wheel, the intermediate wheel and the driven wheel are thus designed as gear wheels.
  • the intermediate gear of the gear transmission is expediently mounted on the intermediate shaft.
  • a first idler gear is rotatably connected to the idler shaft and a second idler gear is held on the idler shaft via a freewheel.
  • the driven wheel of the first drive connection is fixed in a rotationally fixed manner on the driven shaft.
  • the second drive connection is an at least single-stage belt drive.
  • the belt of the belt drive wraps around a drive pulley that can be activated on the drive shaft and a driven pulley that is non-rotatably connected to the output shaft.
  • the belt drive is advantageously designed as an adjustable belt drive.
  • at least the drive pulley and / or the driven pulley can be designed as a pulley with adjustable diameter.
  • the schematically illustrated drive device 1 for a cable winch comprises a drive motor 2, which can be designed as an electric motor, hydraulic motor or the like. Drive motor.
  • the drive shaft 5 of the drive motor 2 forms the input shaft of a transmission 3, which with an input speed E ( Fig. 3 ) is driven.
  • the output shaft of the transmission 3 is formed by an output shaft 4, which has an output speed A ( Fig. 3 ) turns.
  • the output shaft 4 drives a cable drum 6 of a cable winch in a manner not shown in detail ( Figures 1 and 2nd ).
  • the transmission 3 has as a first gear a first drive connection 10 between the drive shaft 5 of the drive motor 2 and the output shaft 4 to the cable drum 6 with a first transmission ratio F 1 ( Fig. 3 ) on.
  • the first drive connection consists of a first drive wheel 11, a first driven wheel 14 and at least one first intermediate wheel 12 or second intermediate wheel 13 arranged between the drive wheel 11 and the driven wheel 14.
  • the first intermediate wheel 12 is held in a rotationally fixed manner on an intermediate shaft 15; the intermediate shaft 15 rotates in the opposite direction of rotation 8 to the directions of rotation 7 and 9 of the drive shaft 5 and output shaft 4.
  • the second intermediate wheel 13 is held on the intermediate shaft 15 via a freewheel 16. If the intermediate shaft 15 rotates in the direction of rotation 8, the freewheel 16 closes and establishes a torque-transmitting connection to the first driven wheel 14. If the driven gear 14, which is non-rotatably held on the driven shaft 4, drives the idler gear 13 in the direction of rotation 9 faster than the intermediate shaft 15, the freewheel 16 becomes effective and interrupts the flow of force from the input shaft 5 to the driven shaft 4.
  • the first drive connection 10 is designed as a gear transmission.
  • the first drive wheel 11, the first and second intermediate wheels 12 and 13 and the first driven wheel 14 are designed as gear wheels.
  • the first drive wheel 11 is fixed in a rotationally fixed manner on the drive shaft 5 and meshes with the first intermediate wheel 12.
  • the first intermediate wheel 12 is fixed in a rotationally fixed manner on the intermediate shaft 15.
  • the second intermediate gear 13 is connected via the intermediate shaft 15 and the freewheel 16 driven, which meshes with the first driven wheel 14.
  • the first driven wheel 14 is fixed in a rotationally fixed manner on the driven shaft 4.
  • the first driven wheel 11, the first and second intermediate wheels 12 and 13 together with the freewheel 16 and the first driven wheel 14 form the first drive connection 10 with the transmission ratio F 1 .
  • the first drive connection 10 is permanently driven by the rotating drive shaft 5 of the drive motor 2.
  • the flow of force in the direction of the dashed line from the drive shaft 5 to the output shaft 4 is canceled when the output gear 14 of the output shaft 4 rotates the idler gear 13 in the direction of rotation 8 faster than the idler shaft 15 rotates. If the driven wheel 14 of the driven shaft 4 drives the intermediate wheel 13 faster in the direction of rotation 8 than the intermediate shaft 15, the freewheel 16 becomes effective; the second intermediate wheel 13 rotates in the direction of rotation 8 faster than the intermediate shaft 15.
  • a second drive connection 30 with a gear ratio F 2 is provided as the second gear. How Fig. 3 shows, the gear ratio F 2 is steeper or larger than the gear ratio F 1 of the first drive connection 10.
  • the second drive connection 30 with a transmission ratio F 2 is designed as a belt drive 31.
  • a single-stage belt drive is provided; A multi-stage belt drive can also be useful.
  • the belt drive 31 can be designed as an adjustable belt drive.
  • the drive pulley 32 and / or the driven pulley 34 is designed as a pulley 38 with adjustable diameter.
  • the adjustable pulley 38 is composed of two axially adjustable pulley halves. If the pulley halves are adjusted while increasing their distance, the effective diameter of the pulley 38 becomes smaller. Accordingly, the effective diameter of the pulley 38 becomes larger when the pulley halves are moved towards each other. In this way, a variable translation of the belt drive 31 can be achieved.
  • the belt drive 31 consists of a drive pulley 32 which is to be coupled to the drive shaft 5 via a clutch 33.
  • the driving pulley that is to say the drive pulley 32
  • the driven pulley that is to say the driven pulley 34
  • the arrangement of a belt tensioning device can be expedient, in particular if an adjustable belt drive is used.
  • the drive pulley 32 is rotatably carried along by the drive shaft 5 and drives the belt drive 31.
  • the belt 35 acts directly on the driven pulley 34, which is non-rotatably connected to the driven shaft 4.
  • the speed of the drive shaft 5 is thus - via the belt drive 31 - with a gear ratio F 2 ( Fig. 3 ) transferred to the output shaft 4.
  • Both the first drive connection 10 and the second drive connection 30 of the transmission 3 are arranged in a common housing 20, the drive shaft 5 being mounted in the housing 20 with a drive bearing 21.
  • the intermediate shaft 15 is supported at its ends with a first intermediate bearing 22 and a second intermediate bearing 23 in the housing 20 of the transmission 3.
  • the Output shaft 4 is mounted at its first end with an output bearing 24 and in its other end section with an output bearing 25 in the housing 20 of the transmission 3.
  • the drive device 1 In operation of the drive device 1 can - as in Fig. 3 shown - in a first speed range DB1 ( Fig. 3 ) of the output shaft 4 from zero to a maximum speed D 1, the drive takes place exclusively via the first drive connection 10 with the transmission ratio F 1 .
  • the drive shaft 5 rotating in the direction of rotation 7 drives the drive wheel 11, which meshes with the intermediate wheel 12 and rotates the intermediate shaft 15 in the direction of rotation 8.
  • the freewheel 16 closes and transmits the rotational movement of the intermediate shaft 15 to the intermediate wheel 13, which drives the driven wheel 14 and rotates the driven shaft 4. If the drive motor 2 stops, an attached load will attempt to rotate the support shaft 4 counter to the direction of rotation 9.
  • the freewheel 16 closes in this counter-rotation direction, so that there is uninterrupted support of the load up to the drive shaft 5.
  • a brake 28, which engages on the drive shaft 5, is expediently provided, by means of which a load can be securely held even if the drive motor 2 fails.
  • the first drive connection 10 with the transmission ratio F 1 forms the first gear of the drive device 1 for the cable drum 6; the second drive connection 30 with the gear ratio F 2 forms the second gear with increased speed and fast pull.
  • the belt 35 drives the output shaft 4 at a higher speed than the first drive connection 10.
  • the second drive connection 30 with the gear ratio F 2 drives the output shaft 4 in a second speed range DB2; the first speed range DB1 of the first drive connection 10 forms a lower range of the second speed range DB2.
  • both drive connections 10, 30 cover the first speed range DB1 up to the first maximum speed D 1 together. Only the second drive connection 30 covers the entire second speed range DB2 up to a maximum speed D 2 .
  • a slipping clutch 33 can achieve a lower speed than the final speed of the second gear. This is only possible with the torque of the second gear. Since the power that is not transmitted is lost in the clutch 33 as heat, the clutch 33 slipping only makes sense for a short time, that is, if possible only in the changeover phase.
  • a slipping clutch 33 should expediently not be provided as a permanent condition.
  • the drive shaft 10 with the transmission ratio B 1 drives the output shaft 4 at a slow speed for a slow, controlled train.
  • the output shaft 4 is driven by the drive connection 30 with the transmission ratio F 1 at the speed A 1 for a fast train at the input speed E 1 . It is ensured by the freewheel 16 that the output shaft 4 can rotate at a higher speed than the speed possible via the driving drive connection 10 without obstruction by the still closed first drive connection 10.
  • the switching ratio at the switchover point U results from the quotient C / B.
  • the switching ratios C1 / B1, C2 / B2, C3 / B3 at the switching points U1, U2 and U3 can be switched by the clutch at all input speeds.
  • the clutch 33 can also be arranged on the output shaft 9, this structurally enables a compact construction of the gear housing with a smaller gear depth.
  • the attached load will try to rotate the output shaft 4 against the direction of rotation 9. While the freewheel 16 is effective at a high speed in the direction of rotation 9, the freewheel will close against the direction of rotation 9 and a rotationally fixed connection between the driven wheel 14, the second idler gear 13, the freewheel 16 and the intermediate shaft 15 produce, so that the attached load tries to rotate the intermediate shaft 15 against the direction of rotation 8. Since the intermediate shaft 15 is coupled in a rotationally fixed manner to the drive wheel 11 and the drive shaft 5 via the first intermediate wheel 12, z. B. on the brake 28 on the drive shaft 5, the load can be held. Safe operation is also possible in the event of a malfunction.
  • Fig. 2 corresponds to the basic structure Fig. 1 , which is why the same reference numerals are used for the same parts.
  • the second drive connection 30 is formed by a belt drive 31
  • the second drive connection 30 of the overdrive gear is formed by a gear transmission 40.
  • the second drive wheel 41, formed as a gearwheel, of the second drive connection 30 is held on the drive shaft 5 with a bearing 42.
  • the second drive wheel 41 of the second drive connection 30 can be coupled in a rotationally fixed manner to the drive shaft 5 via the clutch 33.
  • the second drive wheel 41 of the second drive connection 30 meshes with an intermediate wheel 45 of the second drive connection 30, which is designed as a toothed wheel and is held on the intermediate shaft 15 in a freely rotatable manner via a bearing 43.
  • the third intermediate gear 45 of the second drive connection 30 meshes with a second output gear 44 of the second drive connection 30, which is designed as a gear and which is coupled in a rotationally fixed manner to the output shaft 4.
  • the first drive connection 10 is constructed in the same way as that in the exemplary embodiment according to FIG Fig. 1 described.
  • the first drive connection 10 is designed for a speed range DB1 of the output shaft 4 up to a maximum speed D 1 . If the first drive wheel 41 of the second drive connection 30 by means of the Coupling 33 rotatably coupled to the drive shaft 5, the output shaft 4 is driven via the drive wheel pair 41/44/45 at an increased speed corresponding to the transmission ratio F 2 of the second drive connection 30.
  • the second drive connection 30 is designed for a speed range DB2 up to a maximum speed D 2 .
  • the first drive connection 10 from the drive shaft 5 via the first drive wheel 11, the first and second intermediate wheels 13 and 14 and the first drive wheel 14 is still closed, the increased speed in the direction of rotation 9 rotating the second intermediate wheel 13 faster than through the intermediate shaft 15 is driven.
  • the second intermediate wheel 13 "overhauls" the intermediate shaft 15; the freewheel 16 opens.
  • the power flow of the first drive connection 10 to the output shaft 4 is interrupted.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Claims (14)

  1. Dispositif d'entraînement pour un tambour à câble (6) d'un treuil à câble, comprenant un moteur d'entraînement (2) avec un arbre d'entraînement (5), une transmission (3) et un arbre de sortie (4) entraînant le tambour à câble (6),
    dans lequel la transmission (3) comporte une première liaison d'entraînement (10) entre l'arbre d'entraînement (5) du moteur d'entraînement (2) et l'arbre de sortie (4) vers le tambour à câble (6),
    et la transmission (3) comporte une deuxième liaison d'entraînement (30) entre le moteur d'entraînement (2) et l'arbre de sortie (4),
    et la deuxième liaison d'entraînement (30) est formée séparément de la première liaison d'entraînement (10), comme un chemin d'entraînement parallèle, et les deux liaisons d'entraînement (10, 30) sont entraînées conjointement par l'arbre d'entraînement (5) du moteur d'entraînement (2),
    caractérisé
    en ce que la première liaison d'entraînement (10) entraîne à une première vitesse l'arbre de sortie (4) sur une première plage de vitesses de rotation (DB1), en ce que la deuxième liaison d'entraînement (30) entraîne à une deuxième vitesse l'arbre de sortie (4) sur une deuxième plage de vitesses de rotation (DB2), et en ce que lors d'un entraînement de l'arbre de sortie (4) par la deuxième liaison d'entraînement (30), la première liaison d'entraînement (10) reste enclenchée, mais le flux de force de la première liaison d'entraînement (10) de l'arbre d'entraînement (5) vers l'arbre de sortie (4) est interrompu, de sorte que c'est sélectivement la première liaison d'entraînement (10) ou la deuxième liaison d'entraînement (30) qui est en liaison de transmission de couple avec l'arbre de sortie (4).
  2. Dispositif d'entraînement selon la revendication 1,
    caractérisé en ce qu'un rapport (C/B) entre la première liaison d'entraînement (10) et la deuxième liaison d'entraînement (30) est réglable.
  3. Dispositif d'entraînement selon la revendication 2,
    caractérisé en ce que le rapport (C/B) peut être changé sans changement de la construction de transmission elle-même.
  4. Dispositif d'entraînement selon l'une des revendications 1 à 3,
    caractérisé en ce que la première liaison d'entraînement (10) comporte une roue libre (16) qui s'ouvre quand la deuxième liaison d'entraînement (30) est enclenchée.
  5. Dispositif d'entraînement selon l'une des revendications 1 à 4,
    caractérisé en ce que la liaison d'entraînement (10) comporte une première roue d'entraînement (11) qui agit par au moins une roue intermédiaire (12, 13) sur une première roue de sortie (14) coopérant avec l'arbre de sortie (4).
  6. Dispositif d'entraînement selon la revendication 5,
    caractérisé en ce que la première liaison d'entraînement (10) et/ou la deuxième liaison d'entraînement (30) est une transmission à engrenages.
  7. Dispositif d'entraînement selon la revendication 5 ou 6,
    caractérisé en ce que la première roue d'entraînement (11), la roue intermédiaire (12, 13) et la première roue de sortie (14) sont formées comme des roues dentées.
  8. Dispositif d'entraînement selon la revendication 5,
    caractérisé en ce que la roue intermédiaire (12, 13, 42) est montée sur un arbre intermédiaire (15).
  9. Dispositif d'entraînement selon la revendication 8,
    caractérisé en ce qu'une première roue intermédiaire (12) est solidaire en rotation de l'arbre intermédiaire (15) et une deuxième roue dentée (13) est retenue sur l'arbre intermédiaire (15) par une roue libre (16).
  10. Dispositif d'entraînement selon la revendication 5,
    caractérisé en ce que la première roue de sortie (14) est retenue solidaire en rotation sur l'arbre de sortie (4).
  11. Dispositif d'entraînement selon l'une des revendications 1 à 10,
    caractérisé en ce que la deuxième liaison d'entraînement (10) est une transmission à courroie à au moins un niveau (31).
  12. Dispositif d'entraînement selon la revendication 11,
    caractérisé en ce que la courroie (35) de la transmission à courroie (31) passe sur une poulie d'entraînement (32) apte à être montée sur l'arbre d'entraînement (5), et sur une poulie de sortie (34) reliée fixe en rotation à l'arbre de sortie (4).
  13. Dispositif d'entraînement selon la revendication 11 ou 12,
    caractérisé en ce que la transmission à courroie (31) est une transmission à courroie réglable.
  14. Dispositif d'entraînement selon la revendication 13,
    caractérisé en ce qu'au moins la poulie d'entraînement (32) et/ou la poulie de sortie (34) est une poulie pour courroie (38) à diamètre réglable.
EP17708972.9A 2016-03-05 2017-03-06 Dispositif d'entraînement pour le tambour à cable d'un treuil à cable Active EP3423392B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016002798.3A DE102016002798A1 (de) 2016-03-05 2016-03-05 Antriebsvorrichtung für die Seiltrommel einer Seilwinde
PCT/EP2017/000298 WO2017153043A1 (fr) 2016-03-05 2017-03-06 Dispositif d'entraînement pour le tambour à cable d'un treuil à cable

Publications (2)

Publication Number Publication Date
EP3423392A1 EP3423392A1 (fr) 2019-01-09
EP3423392B1 true EP3423392B1 (fr) 2020-04-29

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Application Number Title Priority Date Filing Date
EP17708972.9A Active EP3423392B1 (fr) 2016-03-05 2017-03-06 Dispositif d'entraînement pour le tambour à cable d'un treuil à cable

Country Status (6)

Country Link
US (1) US10926980B2 (fr)
EP (1) EP3423392B1 (fr)
CN (1) CN109153552B (fr)
DE (1) DE102016002798A1 (fr)
ES (1) ES2798949T3 (fr)
WO (1) WO2017153043A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210299848A1 (en) * 2018-08-03 2021-09-30 Tecna S.P.A. Balancer for tools
DE102023000949B3 (de) 2023-03-08 2024-07-11 Alexej lsakov Vorrichtung zur Platzierung von Solarplatten an Außenwand von mehrstöckigem Gebäude und Verfahren dafür

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Publication number Priority date Publication date Assignee Title
US1999202A (en) * 1932-12-30 1935-04-30 Sullivan Machinery Co Haulage mechanism
DE736650C (de) * 1936-05-27 1943-06-24 Demag Ag Winde zum Heben und Senken von Lasten mit stufenlos regelbarem, mechanischem Getriebe
US2348382A (en) * 1942-09-17 1944-05-09 Marion Steam Shovel Co Safety device for hoisting mechanism
DE3828205A1 (de) * 1988-05-27 1989-12-07 Johannes Dipl In Herchenroeder Winde und verfahren zur steuerung derselben
KR100749279B1 (ko) * 2006-02-28 2007-08-16 안영신 벨트를 이용한 무단변속기 및 구동방법
DE202008011202U1 (de) 2008-08-22 2009-01-29 Kendrion Linnig Gmbh Reibschaltkupplung mit einem von einem Antriebsmotor über einen Antriebsriemen angetriebenen Antriebsrad und Antriebseinheit
DE102012200035B4 (de) * 2012-01-03 2016-06-09 Alfred Schellenberg Gmbh Antriebsvorrichtung zum Auf- und Abwickeln einer Verdunkelungsvorrichtung, insbesondere eines Rollladens o.dgl.

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Title
None *

Also Published As

Publication number Publication date
ES2798949T3 (es) 2020-12-14
WO2017153043A1 (fr) 2017-09-14
EP3423392A1 (fr) 2019-01-09
CN109153552A (zh) 2019-01-04
US10926980B2 (en) 2021-02-23
US20190161327A1 (en) 2019-05-30
DE102016002798A1 (de) 2017-09-07
CN109153552B (zh) 2022-04-05

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