EP0678473A2 - Dispositif de levage - Google Patents

Dispositif de levage Download PDF

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Publication number
EP0678473A2
EP0678473A2 EP95105587A EP95105587A EP0678473A2 EP 0678473 A2 EP0678473 A2 EP 0678473A2 EP 95105587 A EP95105587 A EP 95105587A EP 95105587 A EP95105587 A EP 95105587A EP 0678473 A2 EP0678473 A2 EP 0678473A2
Authority
EP
European Patent Office
Prior art keywords
shaft
magnetic field
housing
axis
hoist
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.)
Withdrawn
Application number
EP95105587A
Other languages
German (de)
English (en)
Other versions
EP0678473A3 (fr
Inventor
Walter Härtweg
Ulrich Peukert
Manfred Finzel
Raimund Stein
Reiner Bühlmayer
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.)
R Stahl Foerdertechnik GmbH
Original Assignee
R Stahl Foerdertechnik 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 R Stahl Foerdertechnik GmbH filed Critical R Stahl Foerdertechnik GmbH
Publication of EP0678473A2 publication Critical patent/EP0678473A2/fr
Publication of EP0678473A3 publication Critical patent/EP0678473A3/en
Withdrawn legal-status Critical Current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
    • B66D1/54—Safety gear
    • B66D1/58—Safety gear responsive to excess of load
    • 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
    • B66D1/56—Adaptations of limit switches

Definitions

  • slip clutch between the drive motor and the load handling device in the transmission, with the aid of which the torque transmitted from the motor to the load handling device is limited to harmless values.
  • slip clutches have the advantage that they work loss-free below the limit load and cut the maximum torque to be transmitted on a relatively steep flank when the limit load is reached.
  • Another way of dangerous operating conditions To prevent overload due to the use of force measuring devices that intervene in the motor control and interrupt the motor current if the hook load exceeds the permissible maximum limit load.
  • a load measuring device which for this purpose evaluates the axial force which occurs on the axes of helical gear wheels.
  • the known arrangement comprises a cable drum rotatably mounted in a frame, which is rotatably coupled to an output shaft of a gear transmission, which is driven by an electric motor. All gear wheels of the transmission including a countershaft are helically toothed. With the exception of the countershaft, all other shafts are axially immovable.
  • the axially displaceable countershaft is biased into an end position by means of a plate spring assembly. Due to the axial force occurring when transmitting a torque in the sense of lifting the load, the countershaft is displaced against the action of the springs. The shift that occurs is detected with the aid of a measuring device in order to obtain a signal for switching off the engine.
  • the magnetic field strength at the location of the permanent magnet is comparatively large compared to interference magnetic fields that arise solely because of the connected electric motor.
  • the large useful field ensures a comparatively large sensitivity, even if there is only a slight relative movement between the magnets and the magnet-sensitive device.
  • this makes it possible to make do with a small displaceability of the shaft in question, so that commercially available, axially displaceable cylindrical roller bearings can be used for its storage. There is no risk that the cylindrical rollers will partially free themselves from the corresponding running surface when the relevant axis or shaft is displaced.
  • the rotationally symmetrical magnetization of the magnet also contributes to increasing the sensitivity or simplifying assembly, because no special installation position has to be taken into account. It is sufficient to fix the magnet with a corresponding surface on the pin.
  • the rotationally symmetrical magnetization enables the use of a pin that rotates with the shaft itself, which means that additional mechanical transmission elements for transmitting the axis, a displacement of the axis or shaft on the pin can be saved.
  • the transmission becomes particularly simple if the gear in question is in one piece with the axis or shaft in question.
  • an axis or shaft can also be used, which also carries another gear.
  • a single idler gear that does not represent a gear ratio can also be used for force measurement.
  • the toroidal rotationally symmetrical magnetic field in the space is expediently coaxial with the axis of rotation of the shaft or axis in question.
  • the magnetic field-sensitive device can be designed in two parts, the two parts being arranged diametrically with respect to the axis of rotation of the shaft or axis in question.
  • the pin is expediently only guided in a longitudinally displaceable manner and is otherwise rotationally fixed. This can be achieved if the pin is formed on a plunger or plunger which is guided in the housing so as to be longitudinally displaceable but non-rotatable.
  • the magnetic field-sensitive device is expediently located in an intermediate housing which is screwed into the housing of the lifting mechanism in the region of the relevant pin.
  • the intermediate housing can be adjusted as desired via a worm which engages in the worm gear toothing and is fixedly mounted on the housing.
  • the intermediate housing can be used to support the plunger, which provides a comparatively small component that can be easily machined with high accuracy so that the plunger can be guided largely without play.
  • a transmission of the axial preload forces via the cylindrical roller or needle bearing is avoided if the preloading device has a shoulder bearing, the inner bearing ring of which is guided in a longitudinally displaceable manner on the axle or shaft and is clamped between a contact surface in the axle or shaft and spring members, while the outer bearing ring on one in the housing stationary stop is supported such that the bearing supporting the axle or shaft is free from axial forces caused by the pretensioning device.
  • the evaluation of the electrical signals is particularly simple if, based on the power flow, the axis or shaft, the axial displacement of which is evaluated, is arranged as close as possible to the drive motor, because in this case the frequency caused by a radial runout is comparatively high and lighter can be filtered out.
  • Fig. 1 shows a cable 1 as an example of a hoist; However, the hoist can also be a chain hoist, a cable winch or the like.
  • the cable 1 has an elongated cable housing 3 which is open on its underside 2 and in which a drum 5 provided with cable grooves 4 is rotatably mounted. A steel cable 6 is wound on the cable drum 5.
  • a gear housing 8 is flanged to an end face 7 of the cable housing 3, which carries a three-phase motor 11 serving as a drive motor on its end face 9 remote from the end face 7.
  • a switch box 13 On a face 12 opposite the face 7 there is a switch box 13 in which terminals and control contactors for the drive motor 11 are accommodated.
  • the gearbox located in the gearbox 8 is a helical-toothed spur gearbox and, as the section according to FIG. 2 shows, it contains at least two countershafts 14 and 15, the countershaft 15 being the countershaft which carries a gear 16 which does not directly engage one illustrated pinion combs.
  • a pinion 17 which is integral with the countershaft 15 and is thus connected in a rotationally fixed manner to the gear 16 meshes with a gear 18 which is arranged in a rotationally fixed manner on the countershaft 14.
  • the countershaft 14 is provided with a one-piece pinion 19, via which a gearwheel, which is rotatably fixed with the cable drum 5 and not shown, is driven.
  • Helical toothed gears are known to generate an axial force which is dependent on the helix angle of the toothing and is proportional to the force which acts on the pitch circle diameter of the gear concerned. Therefore, this axial force can be used to measure the rope force, pulling on the rope 6. Although friction occurs on the tooth flanks of the gearwheels which are in engagement with one another, this does not, however, falsify the measurement result when the parts in engagement with one another rotate. In the rotating state, the measurement result can be assumed to be free of hysteresis within the permissible tolerances, ie it is not falsified beyond the permissible level by the friction that occurs.
  • the axis or shaft of the gear unit used for the measurement is preferably as close as possible to the drive motor 11 from the point of view of the power flow. This is where the greatest speeds occur and the shaft in question can move fastest into a position proportional to the applied force.
  • the countershaft 15 is therefore axially displaceable, as is explained in detail with reference to FIG. 3.
  • the gear housing 8 contains two aligned bearing bores 19 and 21, in which cylindrical roller bearings 22 and 23 are seated, the inner bearing rings 24 and 25 of which are placed on corresponding journals and shaft sections 26 and 27.
  • the cylindrical roller bearings 22 and 23 allow the countershaft 15 to have a slight axial stroke of approximately 1 to 2 mm. They are installed in such a way that their thrust collar located on the inner bearing ring 24 or 25 faces the pinion 17.
  • the countershaft is prestressed to the right with reference to FIG. 3, so that the inner bearing ring 25 rests with its collar on the ring of cylindrical rollers 29, while a correspondingly large gap 31 is present at the relevant point of the cylindrical roller bearing 22 is.
  • the axial movement of the countershaft 15 is with Detected by means of a fixed magnetic field sensitive device 32.
  • the bearing bore 21 is a stepped bore with an enlarged section 33 which merges at a shoulder 34 into a cylindrical section 35 which leads to the outside through a corresponding housing wall 36.
  • the countershaft 15 protrudes into the stepped bore 21 formed in this way with its section 27, a section 37 adjoining the section 27 to the outside, followed by a section 39 with a smaller diameter provided with an external thread 38.
  • the last section on this side of the countershaft 15 finally forms a cylindrical section 41, which, however, still lies within the bore section 35.
  • the inner bearing ring 25 is seated on the shaft section 27 in such a way that its collar can be supported on a shoulder 42 of the countershaft 15.
  • the outer bearing ring of the cylindrical roller bearing 23 bears against a support disk 43 which is located between the outer bearing ring in question and the shoulder 34.
  • the outer bearing ring of the cylindrical roller bearing 23 is secured axially almost free of play by means of a snap ring 44 inserted into a corresponding groove in the bore section 33.
  • annular disk spring 45 On the side of the support disk 43 remote from the cylindrical roller bearing 23, an annular disk spring 45 abuts with its outer edge.
  • the abutment for the thrust ball bearing 46 forms a nut 47 which is screwed onto the shaft section 39 provided with the thread 38.
  • the nut 47 is smooth with a cylindrical Provided outer surface 48 on which a lip seal 49 rests sealingly.
  • the plate spring 45 As a result of the plate spring 45, the countershaft 15 is shifted to the right until, as already mentioned, the shoulder of the inner bearing ring 25 abuts against the relevant end face of the cylindrical rollers 29.
  • the biasing force is set with the aid of the plate spring 45 and the nut 47.
  • the plate spring 45 stops and the relative movement between the plate spring 45 and the nut 48 is absorbed by the pressure ball bearing 46.
  • a bushing 51 is inserted into the bore section 45 until its flange 52, which projects radially outward, lies flat on a corresponding surface on the outside of the wall 36.
  • the bushing 51 is held in the bore section 35 by means of screws 53 which pass through the flange 52 and are screwed into threaded bores 54.
  • the bushing 51 is sealed against the bore section 35 with the aid of seals.
  • a stepped bore 55 having several sections passes through the bushing 51.
  • the lip seal 49 already mentioned is arranged in a section of the stepped bore 55, while another section which is further out is provided with an internal thread 56.
  • An essentially tubular intermediate housing 57 is screwed into this internal thread 56 and, as the enlarged illustration in FIG. 4 shows, is provided with an external thread 58 for this purpose.
  • the section projecting to the right via the thread 58 and thus out of the bush 51 is provided on its cylindrical outer circumference with worm gear teeth 59, in which a worm 61 engages.
  • the worm 61 is fixed on the bush 51 by means of pillow blocks 62 which are screwed onto the flange 52.
  • the intermediate housing 57 contains a partition 60, as a result of which the intermediate housing 57 is divided into an internal cylindrical chamber 63 and an external chamber 64.
  • a piston or plunger 65 which is approximately hat-shaped in cross section, is axially displaceable, which is formed by means of two cylindrical pins 66 inserted into the partition wall 60, which by corresponding grooves, not shown in the figure, in a radially outwardly projecting flange 67 is secured against rotation.
  • a compression spring 68 is also supported on this flange, which acts between the flange 67 and the partition wall 60 in order to move the piston 65 to the left.
  • the stroke of the piston 65 is limited by a snap ring 69 seated in a groove.
  • the piston 65 is freely displaceable between the snap ring 69 and the partition 60.
  • the cylindrical pins 66 which extend parallel to the axial direction and are inserted into bores in the partition 60, prevent the piston 65 from rotating.
  • the piston 65 coaxially carries a pin 71, on the free end of which a magnet 72 is glued.
  • the magnet 72 has the shape of a disk, the outer diameter of which corresponds approximately to the outer diameter of the pin 72. It is magnetized in such a way that one pole face is that face which is adjacent to the free end of the pin 71, while the other pole face is the opposite end face. This creates a toroidal magnetic field that is coaxial with the axis of the pin 71.
  • the pin 71 is in turn largely coaxial with the axis of the countershaft 15, so that existing wobble leads to the least possible tilting movements of the pin 71.
  • the pin 71 moves in a cup-shaped protuberance 73 of the partition 72.
  • the protuberance 73 protrudes into the chamber 64 so that the magnetic field of the magnet 72 can reach the magnetic field-sensitive device 32 arranged next to the protuberance 73.
  • the intermediate housing 57 which is integral with the partition 60 and the cup-shaped protuberance 73, is made of a material that hinders the passage of the magnetic field as little as possible, for example aluminum.
  • the magnetic field-dependent device 32 is an integrated module in which, as can be seen in FIG. 5, a total of four field plates 76 are connected to form a bridge.
  • a connection 77 of the bridge is connected to the positive supply voltage, while another connection 78 is connected to a circuit ground.
  • the terminals 79 and 81 of the bridge branch are connected to inputs 82, 83 of a preamplifier 84, from which two floating lines 85 extend.
  • the bridge from the field plates 76 and the preamplifier 84 are arranged on a printed circuit board 86 which is inserted in corresponding receiving grooves in the chamber 64. Via the lines 85, the preamplifier 84 is connected to a microprocessor device which serves to evaluate the signals coming from the magnetic field sensitive device 32.
  • the countershaft 15 maintains its axial rest position when lifting loads that are significantly smaller than a predetermined limit load. It rotates in this operating position, in which the countershaft 15 is displaced the furthest in the direction of the intermediate housing 57.
  • the preload force of the preloaded plate spring 45 and the axial force acting in the opposite direction are the same.
  • the force between the cylindrical rollers 29 and the radially outwardly projecting collar of the inner bearing ring 25 disappears.
  • the beginning overload situation is to be recognized even before the gap 31 in the opposite bearing 22 is completely closed.
  • the position of the magnetic field-sensitive device 32 must be adjusted relative to the magnet 72. This is done by rotating the worm 61, whereby the intermediate housing 57 is rotated in the thread 56 to either bring it closer to the countershaft 15 or to move it away from the housing. Since the position of the magnet 72, which is firmly supported on the countershaft 15 via the pin 71 and the pin 74 and the ball 75, does not change with this setting, but on the other hand the magnetic field-sensitive device 32 moves with the intermediate housing 57 in the axial direction , the desired setting is made.
  • FIG. 6 shows an alternative embodiment in which the pin 71 is an integral part of the countershaft 15.
  • the piston 65 and the steel ball 75 can be omitted.
  • the countershaft 15 thus protrudes with its integrally molded pin 71 directly into the cup-like protuberance 73. Because it cannot be guaranteed during assembly that the toroidal magnetic field of the magnet 72 is exactly coaxial with the axis of rotation of the countershaft 15, a more or less large radial shock of the magnetic field always occurs when the countershaft 15 rotates, which is at the location of the magnetic field-sensitive device 32 leads to a change in field strength, which could simulate an axial movement of the countershaft 15. In order to eliminate such effects, in the exemplary embodiment according to FIG.
  • two magnetic field-sensitive devices 32 and 32 ′ are located on the circuit board 86, which are opposite one another with respect to the axis of rotation of the disk-shaped magnet 72.
  • the prestressing force of the plate spring 45 takes up the cylindrical rollers 29, which are supported on the one hand on the collar of the inner bearing ring 25 and on the obliquely opposite collar of the outer bearing ring 23. The result is a tilting moment in the cylindrical rollers 29 about their transverse axis. If no shortening of the life of the cylindrical roller bearing 25 is to be accepted, the permissible preload force is determined by the plate spring 45 by the radial forces acting on the cylindrical roller bearing 23 attack.
  • Fig. 7 shows an embodiment in which the cylindrical rollers 29 are free of tilting moment. This is achieved by using a shoulder bearing 91, the outer bearing ring 92 of which rests on the support disk 43.
  • the inner bearing ring 93 is seated without play on a bearing bush 94, which is attached to the shaft section 37. In the idle state, the inner bearing ring 93 abuts a shoulder 95 at the transition point between the shaft section 27 and the shaft section 37.
  • a package of several plate springs 96 lies between the nut 47 and a washer 97 which engages the inner bearing ring 93.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Rolling Contact Bearings (AREA)
EP95105587A 1994-04-20 1995-04-13 Dispositif de levage Withdrawn EP0678473A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4413717 1994-04-20
DE19944413717 DE4413717C2 (de) 1994-04-20 1994-04-20 Hubwerk

Publications (2)

Publication Number Publication Date
EP0678473A2 true EP0678473A2 (fr) 1995-10-25
EP0678473A3 EP0678473A3 (fr) 1995-12-06

Family

ID=6515957

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95105587A Withdrawn EP0678473A2 (fr) 1994-04-20 1995-04-13 Dispositif de levage

Country Status (2)

Country Link
EP (1) EP0678473A2 (fr)
DE (1) DE4413717C2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6564954B1 (en) * 1996-08-22 2003-05-20 R. Stahl Fordertechnik Gmbh Rope hoist with elastic frame
EP1661845A1 (fr) * 2004-11-25 2006-05-31 M.A.T. Malmedie Antriebstechnik GmbH Dispositif de levage et procédé d'utiliser ce dispositif
CN102730569A (zh) * 2012-06-25 2012-10-17 奇瑞汽车股份有限公司 一种搬运小车升降链条松脱检测装置及其检测方法
CN106276660A (zh) * 2016-08-24 2017-01-04 德马科起重机械有限公司 一种电动葫芦防撞限位装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019133150B4 (de) 2019-12-05 2022-02-10 Schaeffler Technologies AG & Co. KG Überlastschutz für Getriebe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0207923A1 (fr) * 1985-06-14 1987-01-07 HUMBLET, Fernand Appareil de détection d'écarts
EP0511486A1 (fr) * 1991-04-22 1992-11-04 Kabushiki Kaisha Kito Palan électrique

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1736280U (de) * 1954-11-19 1956-12-20 Karl Dipl Ing Boetz Lastmess- und steueranordnung, insbesondere fuer hubwinden.
FR2485142B1 (fr) * 1980-06-19 1986-06-13 Huchez & Cie Dispositif de securite de transmission par engrenages

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0207923A1 (fr) * 1985-06-14 1987-01-07 HUMBLET, Fernand Appareil de détection d'écarts
EP0511486A1 (fr) * 1991-04-22 1992-11-04 Kabushiki Kaisha Kito Palan électrique

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6564954B1 (en) * 1996-08-22 2003-05-20 R. Stahl Fordertechnik Gmbh Rope hoist with elastic frame
EP1661845A1 (fr) * 2004-11-25 2006-05-31 M.A.T. Malmedie Antriebstechnik GmbH Dispositif de levage et procédé d'utiliser ce dispositif
WO2006056193A1 (fr) * 2004-11-25 2006-06-01 M.A.T. Malmedie Antriebstechnik Gmbh Configuration de systeme d'un dispositif de levage, destinee notamment a un portique a conteneurs servant a soulever des charges, et procede pour faire fonctionner cette configuration de systeme
CN101102958B (zh) * 2004-11-25 2011-05-11 Mat马勒麦迭传动科技有限公司 起重装置及其操作方法
US7970520B2 (en) 2004-11-25 2011-06-28 M.A.T. Malmedie Antriebstechnik Gmbh System arrangement of a lifting device, in particular for a container crane for the lifting of loads and moving for the operation of the system arrangement
KR101283328B1 (ko) * 2004-11-25 2013-07-15 엠.아.테.말메디 안트리브스테크니크 게엠베하 부하의 리프팅을 위한 컨테이너 크레인용 리프팅 장치의시스템 어레인지먼트 및 시스템 어레인지먼트 동작을 위한구동
CN102730569A (zh) * 2012-06-25 2012-10-17 奇瑞汽车股份有限公司 一种搬运小车升降链条松脱检测装置及其检测方法
CN102730569B (zh) * 2012-06-25 2015-01-28 奇瑞汽车股份有限公司 一种搬运小车升降链条松脱检测装置及其检测方法
CN106276660A (zh) * 2016-08-24 2017-01-04 德马科起重机械有限公司 一种电动葫芦防撞限位装置

Also Published As

Publication number Publication date
DE4413717A1 (de) 1995-10-26
DE4413717C2 (de) 1996-04-04
EP0678473A3 (fr) 1995-12-06

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