WO2009043324A1 - Palan électrique à chaîne à grande vitesse de levage - Google Patents

Palan électrique à chaîne à grande vitesse de levage Download PDF

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Publication number
WO2009043324A1
WO2009043324A1 PCT/DE2008/001441 DE2008001441W WO2009043324A1 WO 2009043324 A1 WO2009043324 A1 WO 2009043324A1 DE 2008001441 W DE2008001441 W DE 2008001441W WO 2009043324 A1 WO2009043324 A1 WO 2009043324A1
Authority
WO
WIPO (PCT)
Prior art keywords
load
shaft
chain hoist
electric chain
gear
Prior art date
Application number
PCT/DE2008/001441
Other languages
German (de)
English (en)
Inventor
Matthias Hühn
Dietrich Hoffmann
Original Assignee
Hoffmann Fördertechnik GmbH Wurzen
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
Priority claimed from DE102007047360A external-priority patent/DE102007047360B4/de
Application filed by Hoffmann Fördertechnik GmbH Wurzen filed Critical Hoffmann Fördertechnik GmbH Wurzen
Publication of WO2009043324A1 publication Critical patent/WO2009043324A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D3/00—Portable or mobile lifting or hauling appliances
    • B66D3/18—Power-operated hoists
    • B66D3/20—Power-operated hoists with driving motor, e.g. electric motor, and drum or barrel contained in a common housing
    • B66D3/22—Power-operated hoists with driving motor, e.g. electric motor, and drum or barrel contained in a common housing with variable-speed gearings between driving motor and drum or barrel

Definitions

  • the invention relates to an electric chain hoist with high lifting speed in which with an electric pole-changing drive motor for the fine stroke and the main stroke, a transmission and an output shaft mounted in a housing with a sprocket a load chain with the load is driven.
  • the electric chain hoists are designed for a comparatively large, maximum lifting force. This maximum force is assigned a low lifting speed in the main stroke. This maximum lifting speed corresponding to the maximum force can not be further increased.
  • the electric chain hoists feature pole-changing motors or speed-controlled motors for the fine lift to reduce the lifting speed. With the pole-changing motor, which has an additional winding for a second engine speed, the fine stroke is accomplished.
  • cables or pulleys with a cable drum are also known.
  • the difference between a cable and the electric chain hoist is the simple and compact design of the electric chain hoist.
  • This compact design is due to the fact that the load chain is directly driven by the load with a small diameter chain sprocket.
  • a rope drum has a much larger drum diameter, because a wire rope can not bend arbitrarily. As a result, the load can not attack directly on the cable drum.
  • the load is lifted by a pulley. Cables have a fine lifting gearbox to reduce the lifting speed. If the lifting speed is to be increased in a winch, two hoist winches and a single rope are used according to DE 1920660 Bl.
  • the number of cable strands of the pulley can also be increased by the shearing.
  • the lifting speed is reduced accordingly at high loads.
  • cables are less well suited according to DE 202006002491 Ul, because a loosely wound in the idle stroke rope can not be loaded with a load. Cables have the serious disadvantage that a load-free wound rope is pulled and clamped when attaching a load in the pulley.
  • the invention aims at a structurally simple electric chain hoist with a large lifting height and a higher lifting speed compared with the known electric chain hoists.
  • the object is achieved in an electric chain hoist in that the electric chain hoist has at least four lifting speeds and a manual transmission with a gearshift with at least two or more gears for a higher chain speed compared to the main stroke.
  • Gear shifts have been known for a long time. Although, for example, from DE 697 36 199 T2 and DE 866 840 C2 drum winches with different speeds and from DE 7317950 Ul heavy winches with mechanical gear change have long been known, it is not yet known that the proposal of a gearshift in an electric chain hoist would ever have been proposed or realized with a lifting chain.
  • the proposed electric chain hoist allows in a structurally simple way the lifting and lowering of different loads with widely divergent lifting speeds.
  • the extraordinary advantage of the electric chain hoist with a gearshift is that with a conventional electric chain hoist a much higher lifting speed when lifting light loads and lowering the load-free load chain from a very large lifting height can be achieved.
  • the lifting speed can not only be reduced in terms of control technology, but significantly increased. This is of particular advantage when relatively small loads are lifted relatively quickly to a lifting height of, for example, 150 m. When lifting heavy loads, the time for lowering the load chain is reduced.
  • Manual transmission simple design such as manual
  • idle shifting is problematic when power flow is interrupted, because the powertrain is at least loaded with the weight of the load chain.
  • the use of a manual transmission due to the weight of a long chain is associated with disadvantages.
  • the lock is connected to the gearbox so that a load fuse can be automatically made during the switching operation.
  • the electric chain hoist allows in this way a safe lifting of different loads at different lifting speeds and an automatic locking of the load line during the switching process to prevent fall of the load.
  • Figure 1 is an electric chain hoist with a manual transmission
  • Figure 2 is an electric chain hoist with a Vorschaltgetriebe
  • Figure 3 is an electric chain hoist with a secondary
  • Figure 4 is an electric chain hoist with a manual transmission
  • Figure 5 shows the electric chain hoist of Figure 4 with an automatic locking of the load line in a schematic representation.
  • a schematically illustrated in Figure 1 electric chain hoist consists of a housing 101 and a laterally arranged on or in the housing 101 drive motor 102.
  • the drive motor 102 is connected by means of its motor shaft 114 with a transmission input shaft 103 to a gearbox 104 with a gearshift with at least two or several gears for different chain speeds leads.
  • the output stage of the gearbox 104 is connected to a main output shaft 105, on which the sprocket 106 is arranged with the load chain 107 with the load hook 108.
  • the attachment of the chain hoist is done via a housing suspension, not shown, which is arranged on the upper side of the housing 101.
  • the load chain 107 exiting at the bottom of the housing 101 is driven in a known manner with the sprocket 106.
  • the gearbox 104 may be a gearbox with multiple gear sets that allow different gear ratios.
  • the change gear can be equipped with a manual manual transmission, for example, if only two different lifting speeds are required.
  • the manual transmission 104 may comprise an automatic change gear, in which the change of the lifting speeds is effected by actuators or a hydraulic system.
  • the manual transmission 104 may be equipped with a corresponding clutch device to enable better shifting. Normally, special coupling devices are not required, because the switching can be made in the main not under load, but before or after completion of the lifting process. Actuating the gearshift to change gears during full traction is usually not required.
  • a manual transmission 104 can also be used with an automatic transmission with a planetary gear or a continuously variable transmission.
  • the electric chain hoist may have an existing reduction gear 109 and a primary gear 110 or a secondary gear 112 according to FIG.
  • a primary gear 110 the conventional reduction gear 109 is extended by a Vorschaltcut.
  • an additional counter stage is attached between the transmission input shaft 103 and the motor shaft 114.
  • the conventional transmission can be equipped analogous to the counter stage with a secondary 112.
  • a secondary 112 for example, between the main output shaft 105 and a sprocket 113 inserted two-stage planetary gear is suitable. This results in the Feinhub four different lifting speeds.
  • the standardized load capacity is, for example, 1000 kg with a lifting speed in the main stroke of 6 meters per minute and a fine stroke of 1.5 meters per minute.
  • a gearshift and a second lifting speed then a smaller load, for example of the order of 250 kg, can be lifted relatively quickly to 150 m in less than 10 minutes.
  • the lowering speed of the empty load hook 108 or the load-free load chain 107 can be increased by a multiple compared to the lifting speed at maximum load at a corresponding gear ratio with a third gear.
  • the gearbox (104) on the engine side an input gear stage, which consists of an axially réelleckenden motor pinion shaft 1 and the gear 2 of the first gear stage.
  • the gear 2 is axially positively connected and rotatably connected to a switching shaft 3.
  • a gear block of a second switchable gear stage is arranged, which consists of the pinion gear 4 and the pinion 5.
  • the pinion gear 4 is like the gear 2 rotatably and positively connected in the axial direction with the switching shaft 3.
  • the pinion 5 is incorporated in the switching shaft 3.
  • the switching shaft 3 with the pinion gear 4 and the pinion 5 form a switchable gear stage, which is mounted axially displaceable.
  • the output gear stage of the gearbox 104 has a smaller gear 6 and a larger gear 7, which are mounted together on the gear shaft 10.
  • the gear shaft 10 further includes a stub shaft 8, which protrudes from the gear cover 9 and described below.
  • the output shaft 11 with the sprocket 12 and the load chain 13 with the load 14 is arranged.
  • the power transmission takes place via a gear set with a gear reduction, which consists of an output gear 15 on the gear shaft 10 and a larger rotatably mounted output gear 16 on the output shaft 11.
  • the drive force is provided by a drive motor 18 arranged laterally on the housing 17.
  • the drive motor 18 is connected to the motor pinion shaft 1 via the motor shaft 21 by means of a slip clutch 19.
  • the shift shaft 3 is pushed with the large pinion gear 4 in the smaller gear 6.
  • the pinion 5 is brought into engagement with the larger gear 7.
  • the motor pinion shaft 1 with the gear 2 is constantly engaged, which slides axially during the switching movement in the tooth flanks.
  • the pinion gear 4 and the gear 6 come out of engagement until the pinion 5 of the shift shaft 3 with the transmission gear 7 is engaged. In this way, a gear with two gears is possible.
  • the operation of the gearshift takes place in the embodiment with a shift rod 22 and an acting on the shift shaft 3 shift claw 23.
  • the switching can be performed by hand.
  • the switching movement of the switching shaft 3 is effected by means of a sliding movement of the shift rod 22.
  • the shift claw 23 is fixed, which engages in an annular groove 25 of the shift shaft 3 and thus enables the transmission of the switching movement to the shift shaft 3.
  • the shift rod 22 seen in the axial direction is provided on both sides with edge grooves 26 which allow a limitation of the switching movement.
  • a control cam 27 is arranged for the actuation of a plunger push button 28.
  • the limitation of the switching movement is carried out by the plunger button 28 by means of the edge grooves 26.
  • the plunger button 28 by the control cam 27th operated and interrupted the power supply of the electric chain hoist by means of the electric ram switch 28.
  • the hoist brake 29 which comes into force in an electroless electric chain hoist.
  • the plunger button 28 is closed in the region of the outer peripheral grooves 26 and the power supply of the electric chain hoist restored.
  • the holding brake for holding the load 14 during shifting of the gears with respect to the output shaft 11 is not effective and the power flow is interrupted. Since the switching movement must be carried out without danger even at low load 14 or at a high weight of the load chain 13 and the lifting means, a locking of the output gear stage is provided for automatic load protection.
  • the locking of the output gear stage for automatic load protection can be carried out in various ways electrically, pneumatically or manually. According to the embodiment shown here, the locking of the output gear stage, for example, also be controlled electrically by means of the plunger button 28 and the control cam 27. Likewise, the electrical or pneumatic control of the lock can be combined for example with an electric or pneumatic actuator for the gearshift.
  • the invention should not be limited to the aforementioned embodiments. Rather, various embodiments of the invention are possible within the scope of the claims.
  • the shift claw 23 connected to the shift rod 22 has on the opposite side of the shift shaft 3, a latching element with a toothing 31 which positively engages with a fixed to the transmission shaft 10 of the second output gear stage ratchet wheel 32 at the beginning of the shift operation and during the switching operation with the ratchet wheel 32 is engaged.
  • the output shaft 11 with the sprocket 12 via the transmission shaft 10 with the output gear 15 and the rotatably mounted output gear 16 on the output shaft 11, automatically locked.
  • the ratchet wheel 32 is rotatably mounted on the protruding from the gear cover 9 stub shaft 8 of the transmission shaft 10 of the output gear stage.
  • the ratchet wheel 32 is designed in its outer contour so that it easily rotates angularly into the teeth 31 of the shift claw 23 with a small circumferential clearance.
  • a handwheel 33 is provided in the extension of the stub shaft 8. The hand wheel 33 can be moved during the switching operation in the circumferential direction.
  • the gear pairs to be switched are adjusted during shifting. Since the shift claw 23 is immovable in the circumferential direction, a locking of the set of teeth with the output gear 15 on the transmission shaft 10 and the larger rotationally fixed output gear 16 on the output shaft 11 results in a load crash during the switching process is completely excluded.

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

Abstract

L'invention concerne un palan électrique à chaîne comprenant un moteur d'entraînement électrique, une transmission et un arbre de sortie monté dans un carter et doté d'un pignon à chaîne et d'une chaîne de levage pourvue de la charge. L'invention vise un tel palan électrique à chaîne ayant une construction simple et une vitesse de levage accrue. Le palan électrique à chaîne selon l'invention présente une transmission à variation de vitesse (104) avec un changement de vitesse à au moins deux vitesses ou davantage, pour une vitesse de chaîne supérieure par rapport au levage principal. Pour de grandes hauteurs de levage, une charge plus légère peut être soulevée avec une plus grande vitesse de levage et un régime supérieur au régime nominal, avec un couple réduit d'autant. De même, à la suite du levage d'une charge lourde à une grande hauteur de levage, il est avantageux de ramener la chaîne de levage dans la position initiale à grande vitesse. De plus, l'étage de sortie de la transmission est pourvu d'un blocage qui permet d'empêcher un abaissement de la charge (14) pendant l'opération de changement de vitesse.
PCT/DE2008/001441 2007-10-02 2008-08-28 Palan électrique à chaîne à grande vitesse de levage WO2009043324A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007047360A DE102007047360B4 (de) 2007-10-02 2007-10-02 Elektrokettenzug
DE102007047360.7 2007-10-02
DE102007052990.4 2007-11-05
DE200710052990 DE102007052990A1 (de) 2007-10-02 2007-11-05 Elektrokettenzug mit einem Schaltgetriebe

Publications (1)

Publication Number Publication Date
WO2009043324A1 true WO2009043324A1 (fr) 2009-04-09

Family

ID=40149593

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2008/001441 WO2009043324A1 (fr) 2007-10-02 2008-08-28 Palan électrique à chaîne à grande vitesse de levage

Country Status (1)

Country Link
WO (1) WO2009043324A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7317950U (de) * 1973-05-12 1978-03-02 Gewerkschaft Eisenhuette Westfalia, 4670 Luenen Schaltgetriebe fuer schiffs-schwergutwinden
DE4434373A1 (de) * 1994-09-15 1996-03-28 Mannesmann Ag Elektrozug mit drehzahlgeregelter Geschwindigkeit
DE69736199T2 (de) * 1997-01-30 2007-05-03 Milemarker, Inc., Pompano Beach Winde mit mehreren gängen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7317950U (de) * 1973-05-12 1978-03-02 Gewerkschaft Eisenhuette Westfalia, 4670 Luenen Schaltgetriebe fuer schiffs-schwergutwinden
DE4434373A1 (de) * 1994-09-15 1996-03-28 Mannesmann Ag Elektrozug mit drehzahlgeregelter Geschwindigkeit
DE69736199T2 (de) * 1997-01-30 2007-05-03 Milemarker, Inc., Pompano Beach Winde mit mehreren gängen

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