EP0284807A2 - Electric hoist - Google Patents

Electric hoist Download PDF

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Publication number
EP0284807A2
EP0284807A2 EP88103243A EP88103243A EP0284807A2 EP 0284807 A2 EP0284807 A2 EP 0284807A2 EP 88103243 A EP88103243 A EP 88103243A EP 88103243 A EP88103243 A EP 88103243A EP 0284807 A2 EP0284807 A2 EP 0284807A2
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EP
European Patent Office
Prior art keywords
friction clutch
electric
train according
armature
drive
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.)
Granted
Application number
EP88103243A
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German (de)
French (fr)
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EP0284807A3 (en
EP0284807B1 (en
Inventor
Manfred Finzel
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R Stahl Foerdertechnik GmbH
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R Stahl Foerdertechnik GmbH
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Application filed by R Stahl Foerdertechnik GmbH filed Critical R Stahl Foerdertechnik GmbH
Priority to AT88103243T priority Critical patent/ATE94148T1/en
Publication of EP0284807A2 publication Critical patent/EP0284807A2/en
Publication of EP0284807A3 publication Critical patent/EP0284807A3/en
Application granted granted Critical
Publication of EP0284807B1 publication Critical patent/EP0284807B1/en
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/12—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect

Definitions

  • the invention relates to an electric train with the features of the preamble of claim 1.
  • Such a generic electric train is known from EU-PS 0077 890.
  • the armature shaft carries, on its side facing the transmission, a pinion which meshes with a spur toothing which is formed on the drive-side friction clutch element of the overload slip clutch.
  • the friction clutch element on the output side is connected in a rotationally fixed manner to an intermediate shaft which likewise rotatably carries a further gearwheel on which the power is tapped for transmission to the chain sprocket.
  • the two friction clutch members are by disc springs; which are supported on the one hand on the intermediate shaft and on the other hand on the driven friction clutch member, pretensioned in the frictional engagement position, to such an extent that, in the event of excessive torque as a result of an overload on the hoist, the friction clutch members rotate against one another.
  • the holding brake serves at stopped electric motor to prevent the armature shaft from rotating when the load on the hoist is striving to rotate the armature shaft in order to lower the load.
  • the holding brake is designed as a cone brake, the fixed part being anchored in the motor housing and the rotatable part sitting on the armature shaft.
  • the armature which is axially immovably mounted, contains a hollow shaft which rotates with the drive-side friction clutch member is coupled.
  • the friction clutch element on the output side is rigidly connected to an output shaft leading to the transmission and passing through the hollow armature shaft, a spring holding the two friction clutch elements together in the frictionally engaged position.
  • the friction clutch element on the output side carries an axially displaceable brake ring which can be braked against the motor housing with the aid of a brake plate. This plate is biased into the braking position by means of a lever and a spring, and the release takes place with the help of an additional magnet that overcomes the spring force.
  • a disadvantage of this arrangement is the additional magnet needed to release the brake when the hoist is to be raised or lowered.
  • DE-PS 691 893 an electric motor with a sliding anchor is shown, which carries the drive-side friction clutch member in a rotationally fixed manner on its armature shaft.
  • the friction clutch element on the output side is formed by a conical bell which sits on an output shaft which is axially displaceable in the motor housing.
  • This output-side friction clutch member is also the rotatable brake member, which is biased in the idle state by a spring in the direction of the armature and thus in the direction of a braking surface connected to the motor housing.
  • the torque transmission capacity of the slip clutch can be small if the friction clutch element on the drive side is connected directly to the armature shaft, since the smallest torques occur there.
  • the slip clutch can also be dimensioned accordingly small. The same applies analogously to the brake, which can be smaller the more it is geared to the motor.
  • the overall space requirements are particularly small and the manufacture is very simple if the friction clutch member on the output side and the rotatable brake member are integrally connected to one another.
  • the coupling of the brake member to the partial drive train on the output side takes place by means of a gearwheel that is connected to the brake member in a rotationally fixed manner and is connected to this partial drive train in a geared manner.
  • Another option is the drive power to pass through the brake member so that the brake member is in the power flow.
  • an electric chain hoist 1 is shown in a longitudinal slot. It contains an electric motor 2, a reduction spur gear 3, and an overload slip clutch 4, via which the mechanical power is transmitted from the electric motor 2 to the gear 3, and a brake 5.
  • the electric motor 2 has an approximately cup-shaped motor housing 6, which is flanged with its open front to an intermediate housing flange 7 by means of screws 8.
  • a stator winding 9 In the interior closed on all sides there is a stator winding 9 and a cone-shaped armature 12 which is seated in a rotationally fixed manner on an armature shaft 11 and is designed as a short-circuit rotor.
  • the motor housing 6 contains, in its end remote from the intermediate flange housing 7, a stepped bore 14, in which, seen from the outside inwards, are inserted: a shaft seal 14 and a deep groove ball bearing 16 in which, with the interposition of a sliding bush 17, the armature shaft 11 is rotatably and axially displaceably mounted is.
  • a compression spring 19 designed as a helical spring is supported at one end, the other end of which rests on the adjacent end face of the armature 12.
  • the armature shaft 11 is in this way by the compression spring 19 in the direction of Intermediate housing flange 7 too biased.
  • the other end of the armature shaft 11 is mounted in a stepped bore 22 which is formed in a wall 23 of the intermediate housing flange adjacent to the motor housing 6.
  • a shaft seal 24 and a needle bearing 25 are inserted, so that the armature shaft 11 is also axially displaceably and sealed in the intermediate housing flange 7.
  • a shell-shaped housing cover 26 is screwed on in a sealed manner, which together with the intermediate housing flange 7 forms a gear housing in which the spur gear 3 is accommodated.
  • a countershaft 27 and an output shaft 28 are mounted between the housing cover 26 and the intermediate housing flange 7 by means of roller bearings 29, 31 and 32, 33 held in a stationary manner parallel to the armature shaft 11.
  • the countershaft 27 carries a large spur gear 34 and a pinion 35 connected to it in a rotationally fixed manner, which meshes with a spur gear 36 which is non-rotatably wedged on the output shaft 28.
  • the output shaft 28 protrudes with a portion 37 through a bore 38 in the intermediate housing flange 7 below the motor housing 6 and carries a non-rotatably seated thereon Chain nut 39 for a chain, not shown.
  • the mechanical power is transmitted from the armature shaft 11 to the chain sprocket 39 via the slip clutch 4.
  • This slip clutch 4 is arranged together with the braking device 5, as shown in FIG. 2, in a cup-shaped recess 41 which is formed in the housing cover 26 in the direction of the intermediate housing flange 7 in the extension of the armature shaft 11.
  • the cylindrical recess 41 is provided in its recessed bottom wall 42 with a stepped bore 43 which is coaxial with the armature shaft 11 and which forms a seat for a shaft seal 44 arranged therein.
  • a shaft section 45 of the armature shaft 11 extends through this stepped bore 43.
  • a hub 48 is rotatably supported by two bushes 46 and 47 on the shaft section 45, which is smaller in diameter than the armature shaft 11 in the region of the needle bearing 25.
  • the hub 48 passes through the stepped bore 43 and is provided there with a cylindrical outer circumferential surface against which the shaft seal 44 lies sealingly.
  • the end of the hub 48 adjacent to the intermediate housing flange 7 is provided with a pinion toothing 49 and meshes with the large gear 34 of the countershaft 28 End of a recess 51, in which a further shaft seal 52 is inserted, which seals the hub 48 against the armature shaft section 45.
  • a circular disk 53 is rigidly fastened on the hub 48 and is equipped with a frustoconical outer peripheral surface 54 serving as a braking surface and a flat ring surface 55 pointing away from the bottom surface 42. Both surfaces are coaxial with the armature shaft 11, the latter serving as an output-side friction clutch member of the overload slip clutch 4.
  • the other drive-side friction clutch member consists of a circular, flat disk 56 which, opposite the friction surface 55, is mounted on a profile shaft section 57 in a rotationally fixed and axially displaceable manner.
  • the profile shaft section 57 is an integral part of the armature shaft 11 and it adjoins the armature shaft section 45 to the outside, and, as shown, protrudes a little to the outside beyond the friction clutch member 56.
  • On this protruding part are a number of disc springs 58, which are supported by means of a spacer 59, a washer 61 and a pressure screw 62 against the friction clutch member 56.
  • the friction clutch member which sits on the profiled shaft section 57 in a rotationally fixed and axially displaceable manner, is prestressed against the disk 53, which in turn is supported via the hub 48 against a shoulder 63 formed between the armature shaft section 45 and the region of the armature shaft 11 located behind it.
  • the conical brake surface 54 Opposite the conical brake surface 54 is the second brake member in the form of the conical brake ring 64, which is held in place by an insert 65 and by screws 66 in the cylindrical recess 41.
  • the holder 65 is finally closed by a detachable cap 67.
  • the smallest clear width of the conical brake ring 64 is slightly larger than the outer diameter of the flat disk 56 and also the conical braking surface 68 widens in the direction of the floor 42 in accordance with the diameter increase of the disk 53.
  • the electric cable 1 described works as follows: in the de-energized or idle state, the armature 12, together with the armature shaft 11, is pushed to the left by the compression spring 19 with reference to the figures, as a result of which the disk 53 with the conical braking surface 54 is held in the frictionally engaged position with the conical braking friction surface 68 . As a result, the countershaft gear 34, which meshes with the pinion 49, is braked and, via the further gear train, the output shaft 37 with the chain sprocket 39 is braked against rotation due to the attached load.
  • the holding force of the braking device 5 results from the material pairing of the brake ring 64 and the disk 53 in combination with the feed force of the compression spring 19.
  • the stator 9 pulls the armature 12 while reducing the air gap 13 against the action of the compression spring 19, as a result of which the armature shaft 11 rigidly connected to the armature 12 is also displaced to the right.
  • the abutting on the friction surface 55 de disk 56 presses the disk 53 to the right, whereby the two braking surfaces 54 and 68 are separated from each other.
  • the braking device 5 is released and no longer acts on the drive train between the armature shaft 11 and the output shaft 37. Since the armature 12 begins to rotate at the same time as a result of the current being switched on the output shaft 37 rotated and the lifting element, not shown, raised or lowered, depending on how the armature 12 runs.
  • the armature continues to rotate the disk 56 connected to it in a rotationally fixed manner, while the driven side of the slip clutch, namely the disk 53, remains stationary.
  • the torque which can be transmitted via the slip clutch 4 can be set in operation by turning the pressure screw 62 to a greater or lesser extent and is independent of the force which the displacement anchor can exert.
  • the armature shaft section 45 rotates within the hub 48 mounted on it, while the two braking surfaces 54 and 68 are held out of engagement by the axial component of the armature cable.
  • the compression spring 19 immediately presses the armature shaft 11 together with the armature 12 to the left until a further displacement movement is blocked by the form-fitting system between the braking surfaces 54 and 68.
  • the disk 53 is pushed forward due to the positive connection of the hub 48 to the ring shoulder 63.
  • the hub 48 also slides accordingly to the left, the pinion toothing 49 on the hub 48 correspondingly through the teeth of the gearwheel 34 slides in the tooth longitudinal direction.
  • the braking device 5 lies in the drive train between the clutch surface 55 and the output shaft 37, the pretension with which the disk 56 is pressed against the friction surface 55 of the disk 53 has no influence on the holding force or the braking torque which is generated by the braking device 5 acts on the output shaft 37 in accordance with the reduction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Non-Insulated Conductors (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)

Abstract

An electric hoist (1) contains a housing in which an electric motor (2) with a sliding armature (12) as well as a reduction gearing (3) driven by the electric motor (2) are arranged. The output shaft (28) of the gearing (3) actuates a driving device (39) for a lifting mechanism. An overload slip clutch (4) is provided in the drive line between the electric motor (2) and the output shaft (28), which overload slip clutch (4) has two friction-clutch members preloaded in frictional connection with one another, of which one is coupled to the motor (2) and the other is coupled to the output shaft (28). In addition, a brake device (5) is provided in order to brake the output shaft (28) via the gearing (3) when the motor (2) is switched off. So that the slipping moment of the overload slip clutch (4) can be set independently of the brake force of the brake device (5), the brake device (5) is connected to that part of the drive line which lies between the slip clutch (4) and the output shaft (28). The brake device (5) is actuated by sliding of the armature (12) when the motor current is switched off or on. <IMAGE>

Description

ElektrozugElectric train

Die Erfindung geht aus von einem Elektrozug mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to an electric train with the features of the preamble of claim 1.

Ein derartiger gattungsgemäßer Elektrozug ist aus der EU-PS 0077 890 bekannt. Bei diesem Elektroketten­zug trägt die Ankerwelle auf ihrer dem Getriebe zuge­wandten Seite ein Ritzel, das mit einer Stirnverzahnung kämmt, die auf dem antriebsseitigen Reibkupplungsglied der Überlastrutschkupplung ausgebildet ist. Das ab­triebsseitige Reibkupplungsglied ist drehfest mit einer Zwischenwelle verbunden, die ebenfalls dreh­fest ein weiteres Zahnrad trägt, an dem die Leistung zur Weiterleitung an die Kettennuß abgegriffen wird. Die beiden Reibkupplungsglieder sind durch Teller­federn; die sich einerseits an der Zwischenwelle und andererseits an dem angetriebenen Reibkupplungs­glied abstützen, in Reibeingriffsstellung vorgespannt, und zwar so stark, daß bei einem übermäßigen Dreh­moment infolge einer Überlast am Hebezeug sich die Reibkupplungsglieder gegeneinander drehen.Such a generic electric train is known from EU-PS 0077 890. In this electric chain hoist, the armature shaft carries, on its side facing the transmission, a pinion which meshes with a spur toothing which is formed on the drive-side friction clutch element of the overload slip clutch. The friction clutch element on the output side is connected in a rotationally fixed manner to an intermediate shaft which likewise rotatably carries a further gearwheel on which the power is tapped for transmission to the chain sprocket. The two friction clutch members are by disc springs; which are supported on the one hand on the intermediate shaft and on the other hand on the driven friction clutch member, pretensioned in the frictional engagement position, to such an extent that, in the event of excessive torque as a result of an overload on the hoist, the friction clutch members rotate against one another.

Auf der dem Ritzel abgewandten Seite der Ankerwelle befindet sich eine Haltebremse, die dazu dient, bei angehaltenem Elektromotor ein Drehen der Ankerwelle zu verhindern, wenn die Last am Hebezeug bestrebt ist, die Ankerwelle im Sinne eines Absenkens der Last zu drehen. Die Haltebremse ist als Konus­bremse ausgebildet, wobei der feststehende Teil im Motorgehäuse verankert ist und der drehbare Teil auf der Ankerwelle sitzt. Beim Einschalten des Motorstroms wird aufgrund der konischen Ausbildung des Luftspaltes im Motor der Verschiebeanker axial verschoben, um das drehbare Bremsglied aus der Reibeingriffsstellung mit dem festen Bremsglied zu lüften. Beim Abschalten des Motorstroms drückt eine auf die Ankerwelle wirkende Feder die Bremsglieder in die Eingriffsstellung.On the side of the armature shaft facing away from the pinion there is a holding brake which serves at stopped electric motor to prevent the armature shaft from rotating when the load on the hoist is striving to rotate the armature shaft in order to lower the load. The holding brake is designed as a cone brake, the fixed part being anchored in the motor housing and the rotatable part sitting on the armature shaft. When the motor current is switched on, due to the conical design of the air gap in the motor, the displacement armature is axially displaced in order to release the rotatable brake member from the frictionally engaged position with the fixed brake member. When the motor current is switched off, a spring acting on the armature shaft presses the brake members into the engagement position.

Bei dieser bekannten Anordnung kann es geschehen, daß im angehaltenen Zustand bspw. eine dynamische Überlast das Reibmoment der Rutschkupplung über­windet und sich die Last allmählich beginnt, abzu­senken, obwohl die Bremse abgebremst ist. Hierdurch können gefährliche Situationen entstehen, da bekannter­maßen zum Aufrechterhalten einer Gleitreibung kleinere Kräfte notwendig sind als zum Überführen einer Haft­reibung in die Gleitreibung. Wenn also die einseitig abgebremste Rutschkupplung durch eine dynamische Überlast angesprochen hat, kann die vorhandene statische Last groß genug sein, um die Rutsch­kupplung im Zustand des Durchrutschens zu halten.With this known arrangement it can happen that, for example, a dynamic overload overcomes the frictional torque of the slip clutch and the load gradually begins to lower, even though the brake is braked, in the stopped state. This can result in dangerous situations, since it is known that smaller forces are required to maintain sliding friction than to convert static friction into sliding friction. So if the one-sided slipping clutch has responded due to a dynamic overload, the existing static load can be large enough to keep the slipping clutch in the state of slipping.

Bei einem aus der DE-PS 28 08 750 bekannten Elektro­zug enthält der Anker, der axial unverschieblich ge­lagert ist, eine Hohlwelle, die drehfest mit dem antriebsseitigen Reibkupplungsglied gekuppelt ist. Das abtriebsseitige Reibkupplungsglied ist mit einer zu dem Getriebe führenden und durch die hohle Anker­welle hindurchgehenden Abtriebswelle starr verbunden, wobei eine Feder die beiden Reibkupplungsglieder miteinander in Reibeingriffsstellung hält. An seinem Außenumfang trägt das abtriebsseitige Reibkupplungs­glied einen axial verschieblichen Bremsring, der mit Hilfe einer Bremsplatte gegen das Motorgehäuse abge­bremst werden kann. Diese Platte ist über einen Hebel und eine Feder in die Bremsstellung vorgespannt, und das Lüften geschieht mit Hilfe eines zusätzlichen Magneten, der die Federkraft überwindet.In an electric train known from DE-PS 28 08 750, the armature, which is axially immovably mounted, contains a hollow shaft which rotates with the drive-side friction clutch member is coupled. The friction clutch element on the output side is rigidly connected to an output shaft leading to the transmission and passing through the hollow armature shaft, a spring holding the two friction clutch elements together in the frictionally engaged position. On its outer circumference, the friction clutch element on the output side carries an axially displaceable brake ring which can be braked against the motor housing with the aid of a brake plate. This plate is biased into the braking position by means of a lever and a spring, and the release takes place with the help of an additional magnet that overcomes the spring force.

Ungünstig bei dieser Anordnung ist der zusätzliche Magnet, der benötigt wird, um die Bremse zu lüften, wenn das Hebezeug gehoben oder gesenkt werden soll.A disadvantage of this arrangement is the additional magnet needed to release the brake when the hoist is to be raised or lowered.

In der DE-PS 691 893 ist ein Elektromotor mit Ver­schiebeanker gezeigt, der auf seiner Ankerwelle drehfest das antriebsseitige Reibkupplungsglied trägt. Das abtriebsseitige Reibkupplungsglied ist von einer kegelförmigen Glocke gebildet, die auf einer in dem Motorgehäuse axial verschieblichen Aus­gangswelle sitzt. Dieses ausgangsseitige Reibkupplungs­glied ist gleichzeitig auch das drehbare Bremsglied, das im Ruhezustand durch eine Feder in Richtung auf den Anker und damit in Richtung auf eine mit dem Motorgehäuse verbundene Bremsfläche vorgespannt ist. Durch Einschalten des Motorstroms wird der Verschiebe­anker in Richtung auf die Ausgangswelle vorgeschoben, wodurch das ausgangsseitige Reibkupplungsglied von der Bremsfläche gelüftet und statt dessen mit dem eingangsseitigen Reibkupplungsglied gekuppelt wird.In DE-PS 691 893 an electric motor with a sliding anchor is shown, which carries the drive-side friction clutch member in a rotationally fixed manner on its armature shaft. The friction clutch element on the output side is formed by a conical bell which sits on an output shaft which is axially displaceable in the motor housing. This output-side friction clutch member is also the rotatable brake member, which is biased in the idle state by a spring in the direction of the armature and thus in the direction of a braking surface connected to the motor housing. By switching on the motor current, the displacement armature is advanced in the direction of the output shaft, as a result of which the friction clutch element on the output side of the braking surface is released and is instead coupled to the input-side friction clutch member.

Bei dieser Anordnung ist entweder die Reibkupplung oder die Bremse in Eingriff bzw. gelüftet. Der Anker schaltet gleichsam die Betriebssituation um, wobei obendrein das Mitnahmemoment in der Rutschkupp­lung vom axialen Ankerzug abhängig ist. Die über die Reibungskupplung übertragbare Kraft ist durch die maximale Axialkraft des Motors begrenzt und nicht einstellbar.With this arrangement, either the friction clutch or the brake is engaged or released. The armature switches the operating situation, as it were, and the driving torque in the slip clutch also depends on the axial armature pull. The force that can be transmitted via the friction clutch is limited by the maximum axial force of the motor and cannot be adjusted.

Ausgehend hiervon ist es Aufgabe der Erfindung, einen Elektrozug mit Verschiebeanker zu schaffen, bei dem das über die Rutschkupplung übertragbare Drehmoment von der Axialkraft des Motors unabhängig ist und im Stillstand keine Belastung der Rutsch­kupplung durch Bremskräfte auftritt.Proceeding from this, it is an object of the invention to provide an electric train with a sliding anchor, in which the torque which can be transmitted via the slip clutch is independent of the axial force of the motor and when the standstill is not loaded by braking forces.

Erfindungsgemäß wird diese Aufgabe durch den Elektro­zug mit den Merkmalen des Anspruches 1 gelöst.According to the invention, this object is achieved by the electric train with the features of claim 1.

Dadurch, daß die Bremse im zweiten, d.h. im abtriebs­seitigen Teilantriebsstrang eingreift, braucht über die Rutschkupplung kein Bremsmoment übertragen zu werden. Die Rutschkupplung kann deswegen ausschließ­lich nach Sicherheitsgesichtspunkten eingestellt wer­den, während die Bremse so ausgelegt wird, daß sie auch bei dynamischen Überlastspitzen nicht aus dem Haftreibungszustand gelangt. Andererseits werden keine zusätzlichen Räume benötigt, um Betätigungs­einrichtungen für die Bremse unterzubringen, sondern die Betätigung der Bremse erfolgt unmittelbar durch den Anker, was auch die Steuerung entsprechend vereinfacht. Zusätzliche Stromversorgungen werden nicht benötigt.Due to the fact that the brake engages in the second, that is to say in the drive train on the output side, no braking torque needs to be transmitted via the slip clutch. The slip clutch can therefore only be adjusted according to safety considerations, while the brake is designed so that it does not come out of the static friction state even with dynamic overload peaks. On the other hand, no additional spaces are required to accommodate actuators for the brake, but rather the brake is actuated directly by the armature, which is also the control accordingly simplified. Additional power supplies are not required.

Besonders einfache räumliche Verhältnisse ergeben sich, wenn das drehbare Bremsglied drehbar und axial unverschieblich auf der Ankerwelle des Ver­schiebeankers gelagert ist.Particularly simple spatial conditions result when the rotatable brake member is rotatably and axially immovably mounted on the armature shaft of the displacement anchor.

Das Drehmomentübertragungsvermögen der Rutsch­kupplung kann klein sein, wenn das antriebsseitige Reibkupplungsglied unmittelbar mit der Ankerwelle verbunden ist, da dort die kleinsten Drehmomente auftreten. Dementsprechend klein kann auch die Rutschkupplung dimensioniert sein. Sinngemäß das Gleiche gilt auch für die Bremse, die umso kleiner sein kann, je dicter sie getrieblich am Motor an­geordnet ist.The torque transmission capacity of the slip clutch can be small if the friction clutch element on the drive side is connected directly to the armature shaft, since the smallest torques occur there. The slip clutch can also be dimensioned accordingly small. The same applies analogously to the brake, which can be smaller the more it is geared to the motor.

Dabei werden die gesamten Platzanforderungen be­sonders gering und die Herstellung sehr einfach, wenn das abtriebsseitige Reibkupplungsglied und das drehbare Bremsglied einstückig miteinander verbunden sind.The overall space requirements are particularly small and the manufacture is very simple if the friction clutch member on the output side and the rotatable brake member are integrally connected to one another.

Die Kupplung des Bremsgliedes mit dem abtriebs­seitigen Teilantriebsstrang geschieht im einfach­sten Falle durch ein Zahnrad, das drehfest mit dem Bremsglied verbunden ist und getrieblich mit diesem Teilantriebsstrang in Verbindung steht. Eine andere Möglichkeit besteht darin, die Antriebsleistung durch das Bremsglied hindurchzuleiten, so daß das Bremsglied im Leistungsfluß liegt. Eine solche Anordnung ergibt sich, wenn, wie oben ausgeführt, das eine Reibkupplungsglied und das Bremsglied einstückig sind.In the simplest case, the coupling of the brake member to the partial drive train on the output side takes place by means of a gearwheel that is connected to the brake member in a rotationally fixed manner and is connected to this partial drive train in a geared manner. Another option is the drive power to pass through the brake member so that the brake member is in the power flow. Such an arrangement is obtained if, as stated above, the one friction clutch member and the brake member are in one piece.

Im übrigen sind Weiterbildungen der Erfindung Ge­genstand von Unteransprüchen.For the rest, further developments of the invention are the subject of dependent claims.

In der Zeichnung ist ein Ausführungsbeispiel des Gegenstandes der Erfindung dargestellt. Es zeigen:

  • Fig. 1 einen erfindungsgemäßen Elektrozug, in einem Axialschnitt, und
  • Fig. 2 einen Ausschnitt aus Fig. 1, unter ver­größerter Veranschaulichung des die Rutsch­kupplung und die Bremse enthaltenden Bereiches.
In the drawing, an embodiment of the object of the invention is shown. Show it:
  • Fig. 1 shows an electric train according to the invention, in an axial section, and
  • FIG. 2 shows a detail from FIG. 1, with an enlarged illustration of the area containing the slip clutch and the brake.

In der Fig. 1 ist ein Elektrokettenzug 1 in einem Längsschlitz dargestellt. Er enthält einen Elektro­motor 2, ein Untersetzungsstirnradgetriebe 3, so­wie eine Überlastrutschkupplung 4, über die die mechanische Leistung von dem Elektromotor 2 auf das Getriebe 3 übertragen wird,und eine Bremse 5.In Fig. 1, an electric chain hoist 1 is shown in a longitudinal slot. It contains an electric motor 2, a reduction spur gear 3, and an overload slip clutch 4, via which the mechanical power is transmitted from the electric motor 2 to the gear 3, and a brake 5.

Der Elektromotor 2 weist ein etwa topfförmiges Motorgehäuse 6 auf, das mit seiner offenen Vorder­seite an einen Zwischengehäuseflansch 7 mittels Schrauben 8 angeflanscht ist. In dem so allseitig geschlossenen Innenraum befindet sich eine Stator­wicklung 9 sowie ein auf einer Ankerwelle 11 dreh­fest sitzender konusförmiger Anker 12, der als Kurzschlußläufer ausgebildet ist. Der Anker 12 und die Bohrung des Stators 9 begrenzen, wie bei Ver­schiebeankermotoren üblich, einen kegelförmigen Luft­spalt 13, dessen größerer Durchmesser dem Zwischen­gehäuseflansch 7 zugekehrt ist.The electric motor 2 has an approximately cup-shaped motor housing 6, which is flanged with its open front to an intermediate housing flange 7 by means of screws 8. In the interior closed on all sides there is a stator winding 9 and a cone-shaped armature 12 which is seated in a rotationally fixed manner on an armature shaft 11 and is designed as a short-circuit rotor. The armature 12 and the bore of the stator 9, as is customary in the case of displacement armature motors, delimit a conical air gap 13, the larger diameter of which faces the intermediate housing flange 7.

Das Motorgehäuse 6 enthält in seinem dem Zwischen­flanschgehäuse 7 abliegenden Ende eine Stufenbohrung 14, in der,von außen nach innen gesehen, eingesetzt sind: eine Wellendichtung 14 sowie ein Rillenkugel­lager 16, in dem unter Zwischenlage einer Gleit­büchse 17 die Ankerwelle 11 drehbar und axial ver­schieblich gelagert ist. An einer Ringschulter 18 der Gleitbüchse 17 stützt sich eine als Schrauben­feder ausgebildete Druckfeder 19 einenends ab, deren anderes Ende an der benachbarten Stirnseite des Ankers 12 anliegt. Die Ankerwelle 11 wird auf diese Weise von der Druckfeder 19 in Richtung auf den Zwischengehäuseflansch 7 zu vorgespannt.The motor housing 6 contains, in its end remote from the intermediate flange housing 7, a stepped bore 14, in which, seen from the outside inwards, are inserted: a shaft seal 14 and a deep groove ball bearing 16 in which, with the interposition of a sliding bush 17, the armature shaft 11 is rotatably and axially displaceably mounted is. On an annular shoulder 18 of the sliding bush 17, a compression spring 19 designed as a helical spring is supported at one end, the other end of which rests on the adjacent end face of the armature 12. The armature shaft 11 is in this way by the compression spring 19 in the direction of Intermediate housing flange 7 too biased.

Auf dem auf der Rückseite des Motorgehäuses 6 herausragenden Ende der Ankerwelle 11 sitzt,mit Hilfe einer Paßfeder gesichert, ein Kühlluft erzeugender Lüfter 21.On the rear of the motor housing 6 protruding end of the armature shaft 11, secured by means of a feather key, sits a fan 21 that generates cooling air.

Das andere Ende der Ankerwelle 11 ist in einer Stufenbohrung 22 gelagert, die in einer dem Motorgehäuse 6 benachbarten Wand 23 des Zwischen­gehäuseflansches ausgebildet ist. In die Stufen­bohrung 22 sind eine Wellendichtung 24 sowie ein Nadellager 25 eingesetzt, so daß die Ankerwelle 11 auch in dem Zwischengehäuseflansch 7 axial ver­schieblich und abgedichtet gelagert ist.The other end of the armature shaft 11 is mounted in a stepped bore 22 which is formed in a wall 23 of the intermediate housing flange adjacent to the motor housing 6. In the stepped bore 22, a shaft seal 24 and a needle bearing 25 are inserted, so that the armature shaft 11 is also axially displaceably and sealed in the intermediate housing flange 7.

Auf der dem Motorgehäuse 6 abgewandten Stirnseite des Zwischengehäuseflansches 7 ist ein schalen­förmiger Gehäusedeckel 26 abgedichtet aufgeschraubt, der zusammen mit dem Zwischengehäuseflansch 7 ein Getriebegehäuse bildet, in dem das Stirnradgetriebe 3 untergebracht ist.On the end of the intermediate housing flange 7 facing away from the motor housing 6, a shell-shaped housing cover 26 is screwed on in a sealed manner, which together with the intermediate housing flange 7 forms a gear housing in which the spur gear 3 is accommodated.

Unterhalb der Ankerwelle 11 sind zwischen dem Gehäuse­deckel 26 und dem Zwischengehäuseflansch 7 eine Vor­gelegewelle 27 und eine Ausgangswelle 28 mittels orts­fest gehalterten Wälzlagern 29, 31 bzw. 32, 33 achs­parallel zu der Ankerwelle 11 gelagert. Die Vorgelege­welle 27 trägt ein großes Stirnzahnrad 34 sowie ein drehfest damit verbundenes Ritzel 35, das mit einem Stirnzahnrad 36 kämmt, das drehfest auf der Ausgangs­welle 28 aufgekeilt ist. Die Ausgangswelle 28 ragt mit einem Abschnitt 37 durch eine Bohrung 38 in dem Zwischengehäuseflansch 7 unterhalb des Motorgehäuses 6 heraus und trägt eine darauf drehfest sitzende Kettennuß 39 für eine nicht weiter veranschaulichte Kette.Below the armature shaft 11, a countershaft 27 and an output shaft 28 are mounted between the housing cover 26 and the intermediate housing flange 7 by means of roller bearings 29, 31 and 32, 33 held in a stationary manner parallel to the armature shaft 11. The countershaft 27 carries a large spur gear 34 and a pinion 35 connected to it in a rotationally fixed manner, which meshes with a spur gear 36 which is non-rotatably wedged on the output shaft 28. The output shaft 28 protrudes with a portion 37 through a bore 38 in the intermediate housing flange 7 below the motor housing 6 and carries a non-rotatably seated thereon Chain nut 39 for a chain, not shown.

Wie ausgeführt, wird die mechanische Leistung von der Ankerwelle 11 über die Rutschkupplung 4 zu der Ketten­nuß 39 übertragen. Diese Rutschkupplung 4 ist zusam­men mit der Bremseinrichtung 5, wie Fig. 2 vergrößert zeigt, in einer becherförmigen Vertiefung 41 angeord­net, die in dem Gehäusedeckel 26 in Richtung auf den Zwischengehäuseflansch 7 in Verlängerung der Ankerwelle 11 ausgebildet ist. Die zylindrische Ver­tiefung 41 ist in ihrer zurückspringenden Bodenwand 42 mit einer zu der Ankerwelle 11 koaxialen Stufen­bohrung 43 versehen, die einen Sitz für eine darin angeordnete Wellendichtung 44 bildet. Durch diese Stufenbohrung 43 erstreckt sich ein Wellenabschnitt 45 der Ankerwelle 11. Auf dem Wellenabschnitt 45, der im Durchmesser kleiner ausgebildet ist als die Ankerwelle 11 im Bereich des Nadellagers 25, ist durch zwei Büchsen 46 und 47 eine Nabe 48 dreh­bar gelagert. Die Nabe 48 führt durch die Stufen­bohrung 43 hindurch und ist dort mit einer zylindri­schen Außenumfangsfläche versehen, gegen die die Wellendichtung 44 abdichtend anliegt. Das dem Zwi­schengehäuseflansch 7 benachbarte Ende der Nabe 48 ist mit einer Ritzelverzahnung 49 versehen und kämmt mit dem großen Zahnrad 34 der Vorgelegewelle 28. Um die Büchsen 46 und 47 nach außen hin abzu­dichten, enthält die Nabe 48 auf ihrem nach außen durch die Bodenfläche 42 hindurchführenden Ende eine Ausdrehung 51, in der eine weitere Wellendichtung 52 eingesetzt ist, die die Nabe 48 gegenüber dem Ankerwellenabschnitt 45 abdichtet.As stated, the mechanical power is transmitted from the armature shaft 11 to the chain sprocket 39 via the slip clutch 4. This slip clutch 4 is arranged together with the braking device 5, as shown in FIG. 2, in a cup-shaped recess 41 which is formed in the housing cover 26 in the direction of the intermediate housing flange 7 in the extension of the armature shaft 11. The cylindrical recess 41 is provided in its recessed bottom wall 42 with a stepped bore 43 which is coaxial with the armature shaft 11 and which forms a seat for a shaft seal 44 arranged therein. A shaft section 45 of the armature shaft 11 extends through this stepped bore 43. A hub 48 is rotatably supported by two bushes 46 and 47 on the shaft section 45, which is smaller in diameter than the armature shaft 11 in the region of the needle bearing 25. The hub 48 passes through the stepped bore 43 and is provided there with a cylindrical outer circumferential surface against which the shaft seal 44 lies sealingly. The end of the hub 48 adjacent to the intermediate housing flange 7 is provided with a pinion toothing 49 and meshes with the large gear 34 of the countershaft 28 End of a recess 51, in which a further shaft seal 52 is inserted, which seals the hub 48 against the armature shaft section 45.

Auf diesem die Wellendichtung 52 enthaltenden Ende ist auf der Nabe 48 eine kreisförmige Scheibe 53 starr befestigt, die mit einer als Bremsfläche dienenden kegelstumpfförmigen Außenumfangsfläche 54 sowie einer planen, von der Bodenfläche 42 wegweisenden Ringfläche 55 ausgestattet ist. Beide Flächen sind zu der Anker­welle 11 koaxial, wobei letztere als abtriebsseitiges Reibkupplungsglied der Überlastrutschkupplung 4 dient. Das andere antriebsseitige Reibkupplungsglied besteht aus einer kreisförmigen planen Scheibe 56, die der Reibfläche 55 gegenüberliegend auf einem Profilwel­lenabschnitt 57 drehfest und axial verschieblich auf­gesteckt ist. Der Profilwellenabschnitt 57 ist ein­stückiger Bestandteil der Ankerwelle 11 und er schließt sich nach außen hin an den Ankerwellenabschnitt 45 an, wobei er, wie gezeigt, ein Stück weit nach außen über das Reibkupplungsglied 56 hinaussteht. Auf die­sem überstehenden Teil stecken eine Reihe von Teller­federn 58, die mittels eines Distanzstückes 59,einer Beilagscheibe 61 sowie einer Druckschraube 62 gegen das Reibkupplungsglied 56 abgestützt sind. Es wird hier­durch das Reibkupplungsglied, das drehfest und axial verschieblich auf dem Profilwellenabschnitt 57 sitzt, gegen die Scheibe 53 vorgespannt, die sich ihrerseits über die Nabe 48 gegen eine zwischen dem Ankerwellen­abschnitt 45 und dem dahinter befindlichen Bereich der Ankerwelle 11 ausgebildete Schulter 63 abstützt.On this end containing the shaft seal 52, a circular disk 53 is rigidly fastened on the hub 48 and is equipped with a frustoconical outer peripheral surface 54 serving as a braking surface and a flat ring surface 55 pointing away from the bottom surface 42. Both surfaces are coaxial with the armature shaft 11, the latter serving as an output-side friction clutch member of the overload slip clutch 4. The other drive-side friction clutch member consists of a circular, flat disk 56 which, opposite the friction surface 55, is mounted on a profile shaft section 57 in a rotationally fixed and axially displaceable manner. The profile shaft section 57 is an integral part of the armature shaft 11 and it adjoins the armature shaft section 45 to the outside, and, as shown, protrudes a little to the outside beyond the friction clutch member 56. On this protruding part are a number of disc springs 58, which are supported by means of a spacer 59, a washer 61 and a pressure screw 62 against the friction clutch member 56. As a result, the friction clutch member, which sits on the profiled shaft section 57 in a rotationally fixed and axially displaceable manner, is prestressed against the disk 53, which in turn is supported via the hub 48 against a shoulder 63 formed between the armature shaft section 45 and the region of the armature shaft 11 located behind it.

Gegenüber der konischen Bremsfläche 54 befindet sich das zweite Bremsglied in Gestalt des konischen Brems­ringes 64, der von einem Einsatzstück 65 sowie durch Schrauben 66 in der zylindrischen Vertiefung 41 orts­fest gehaltert ist. Die Halterung 65 ist schließlich durch eine lösbare Kappe 67 verschlossen. Die kleinste lichte Weite des konischen Bremsringes 64 ist, wie gezeigt, geringfügig größer als der Außendurchmesser der planen Scheibe 56 und außerdem erweitert sich die konische Bremsfläche 68 in Richtung auf den Boden 42 entsprechend der Durchmesservergrößerung der Schei­be 53.Opposite the conical brake surface 54 is the second brake member in the form of the conical brake ring 64, which is held in place by an insert 65 and by screws 66 in the cylindrical recess 41. The holder 65 is finally closed by a detachable cap 67. As shown, the smallest clear width of the conical brake ring 64 is slightly larger than the outer diameter of the flat disk 56 and also the conical braking surface 68 widens in the direction of the floor 42 in accordance with the diameter increase of the disk 53.

Der beschriebene Elektrozug 1 arbeitet folgendermaßen: Im stromlosen oder Ruhezustand wird der Anker 12 nebst der Ankerwelle 11 durch die Druckfeder 19 nach links bezogen auf die Figuren geschoben, wodurch die Scheibe 53 mit der konischen Bremsfläche 54 in der Reibein­griffsstellung mit der konischen Bremsreibfläche 68 gehalten ist. Hierdurch wird auch das Vorgelegezahn­rad 34, das mit dem Ritzel 49 kämmt, festgebremst und über den weiteren Getriebezug die Ausgangswelle 37 mit der Kettennuß 39 gegen Drehen aufgrund der angehängten Last gebremst.The electric cable 1 described works as follows: in the de-energized or idle state, the armature 12, together with the armature shaft 11, is pushed to the left by the compression spring 19 with reference to the figures, as a result of which the disk 53 with the conical braking surface 54 is held in the frictionally engaged position with the conical braking friction surface 68 . As a result, the countershaft gear 34, which meshes with the pinion 49, is braked and, via the further gear train, the output shaft 37 with the chain sprocket 39 is braked against rotation due to the attached load.

Die Haltekraft der Bremseinrichtung 5 ergibt sich aus der Materialpaarung des Bremsringes 64 und der Schei­be 53 in Kombination mit der Vorschubkraft der Druck­feder 19.The holding force of the braking device 5 results from the material pairing of the brake ring 64 and the disk 53 in combination with the feed force of the compression spring 19.

Wenn der Strom für den Elektrokettenzug 1 eingeschal­tet wird, zieht der Stator 9 den Anker 12 unter Ver­ringerung des Luftspaltes 13 gegen die Wirkung der Druckfeder 19 an, wodurch die mit dem Anker 12 starr verbundene Ankerwelle 11 ebenfalls mit nach rechts verschoben wird. Die an der Reibfläche 55 anliegen de Scheibe 56 drückt dabei die Scheibe 53 mit nach rechts, wodurch die beiden Bremsflächen 54 und 68 voneinander getrennt werden. Die Bremseinrichtung 5 ist gelüftet und wirkt nicht mehr auf den Antriebs­strang zwischen der Ankerwelle 11 und der Ausgangswelle 37 ein. Da durch den eingeschalteten Strom gleich­zeitig der Anker 12 sich zu drehen beginnt, wird auch die Ausgangswelle 37 in Umdrehungen versetzt und das nicht veranschaulichte Huborgan angehoben oder abge­senkt, je nachdem, wie herum der Anker 12 läuft. Entsteht an dem Hebezeug eine Überlast, die einen vorgegebenen Grenzwert überschreitet, beispielsweise weil sich das Hebezeug verhakt, dann dreht der Anker die drehfest mit ihm verbundene Scheibe 56 weiter, während die Abtriebsseite der Rutschkupplung, näm­lich die Scheibe 53, stehen bleibt. Das über die Rutschkupplung 4 übertragbare Drehmoment ist durch mehr oder weniger weites Eindrehen der Druckschraube 62 betriebsmäßig einstellbar und unabhängig von der Kraft, die der Verschiebeanker aufzubringen vermag. Im Überlastfall dreht sich der Ankerwellenabschnitt 45 innerhalb der auf ihr gelagerten Nabe 48, während die beiden Bremsflächen 54 und 68 von der axialen Komponente des Ankerzugs außer Eingriff gehalten werden.When the power for the electric chain hoist 1 is switched on, the stator 9 pulls the armature 12 while reducing the air gap 13 against the action of the compression spring 19, as a result of which the armature shaft 11 rigidly connected to the armature 12 is also displaced to the right. The abutting on the friction surface 55 de disk 56 presses the disk 53 to the right, whereby the two braking surfaces 54 and 68 are separated from each other. The braking device 5 is released and no longer acts on the drive train between the armature shaft 11 and the output shaft 37. Since the armature 12 begins to rotate at the same time as a result of the current being switched on the output shaft 37 rotated and the lifting element, not shown, raised or lowered, depending on how the armature 12 runs. If an overload occurs on the hoist that exceeds a predetermined limit value, for example because the hoist gets caught, the armature continues to rotate the disk 56 connected to it in a rotationally fixed manner, while the driven side of the slip clutch, namely the disk 53, remains stationary. The torque which can be transmitted via the slip clutch 4 can be set in operation by turning the pressure screw 62 to a greater or lesser extent and is independent of the force which the displacement anchor can exert. In the event of an overload, the armature shaft section 45 rotates within the hub 48 mounted on it, while the two braking surfaces 54 and 68 are held out of engagement by the axial component of the armature cable.

Wird der Strom für den Elektrozug 1 abgeschaltet, so drückt umgehend die Druckfeder 19 die Ankerwelle 11 samt Anker 12 nach links, solange, bis eine wei­tere Verschiebebewegung durch die formschlüssige An­lage zwischen den Bremsflächen 54 und 68 blockiert ist. Das Vorschieben der Scheibe 53 erfolgt aufgrund der formschlüssigen Verbindung der Nabe 48 mit der Ringschulter 63. Beim Vorschieben der Ankerwelle 11 gleitet auch die Nabe 48 entsprechend ein Stück weit nach links, wobei die auf der Nabe 48 vorhandene Ritzelverzahnung 49 entsprechend durch die Zähne des Zahnrades 34 in Zahnlängsrichtung gleitet.If the current for the electric train 1 is switched off, the compression spring 19 immediately presses the armature shaft 11 together with the armature 12 to the left until a further displacement movement is blocked by the form-fitting system between the braking surfaces 54 and 68. The disk 53 is pushed forward due to the positive connection of the hub 48 to the ring shoulder 63. When the armature shaft 11 is pushed forward, the hub 48 also slides accordingly to the left, the pinion toothing 49 on the hub 48 correspondingly through the teeth of the gearwheel 34 slides in the tooth longitudinal direction.

Da die Bremseinrichtung 5 in dem Antriebsstrang zwi­schen der Kupplungsfläche 55 und der Ausgangswelle 37 liegt, hat die Vorspannung, mit der die Scheibe 56 gegen die Reibfläche 55 der Scheibe 53 gepreßt wird, keinen Einfluß auf die Haltekraft bzw. das Bremsmoment, das von der Bremseinrichtung 5 ent­sprechend der Untersetzung auf die Ausgangswelle 37 wirkt.Since the braking device 5 lies in the drive train between the clutch surface 55 and the output shaft 37, the pretension with which the disk 56 is pressed against the friction surface 55 of the disk 53 has no influence on the holding force or the braking torque which is generated by the braking device 5 acts on the output shaft 37 in accordance with the reduction.

Claims (12)

1. Elektrozug mit einem Gehäuse, in dem ein Elektro­motor mit einem eine in dem Gehäuse drehbar und axial verschieblich gelagerte Ankerwelle enthal­tenden Verschiebeanker sowie ein von dem Elektro­motor angetriebenes Untersetzungsgetriebe ange­ordnet sind, dessen Ausgangswelle mit einer Mit­nahmeeinrichtung für ein Hebezeug drehfest ge­kuppelt ist, mit einer in dem Antriebsstrang zwi­schen dem Elektromotor und der Ausgangswelle an­geordneten Überlast-Rutschkupplung, die zwei in Reibschlußverbindung miteinander vorgespannte Reibkupplungsglieder aufweist und den Antriebs­strang in zwei Teilantriebsstränge aufteilt, von denen der erste zwischen dem antriebsseitigen Reibkupplungsglied sowie dem Motor und der zweite zwischen dem abtriebsseitigen Reibkupplungsglied und der Ausgangswelle liegt, und mit einer ein Bremsmoment für die Ausgangswelle erzeugenden Bremseinrichtung, die ein drehfest in dem Gehäuse verankertes Bremsglied sowie ein mit dem Antriebs­strang gekuppeltes drehbares Bremsglied aufweist, das in die Reibeingriffsstellung mit dem fest­stehenden Bremsglied federelastisch vorgespannt und durch den Verschiebeanker aus der Reibein­griffsstellung lüftbar ist, dadurch gekennzeichnet, daß das drehbare Bremsglied (54) mit dem zweiten Teilantriebsstrang gekuppelt ist.1.Electric cable with a housing in which an electric motor is arranged with a sliding armature containing an armature shaft which is rotatably and axially displaceably mounted in the housing and a reduction gear driven by the electric motor, the output shaft of which is rotatably coupled to a driving device for a hoist, with a the drive train between the electric motor and the output shaft arranged overload clutch, which has two friction clutch members biased in a frictional connection and divides the drive train into two sub-drive trains, the first between the drive-side friction clutch member and the motor and the second between the output-side friction clutch member and the output shaft lies, and with a braking torque for the output shaft generating braking device, a non-rotatably anchored in the housing brake member and a rotatable with the drive train rotatable Bremsgli ed, which is spring-biased in the friction engagement position with the fixed brake member and can be released from the friction engagement position by the displacement anchor, characterized in that the rotatable brake member (54) is coupled to the second partial drive train. 2. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß das drehbare Bremsglied (54) drehbar und axial unverschieblich auf der Ankerwelle (11) des Verschiebeankers (12) gelagert ist.2. Electric train according to claim 1, characterized in that the rotatable brake member (54) is rotatably and axially immovable on the armature shaft (11) of the displacement anchor (12). 3. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß das antriebsseitige Reibkupplungsglied (56) unmittelbar drehfest mit der Ankerwelle (11) verbunden ist.3. Electric train according to claim 1, characterized in that the drive-side friction clutch member (56) is directly connected to the armature shaft (11) in a rotationally fixed manner. 4. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß das abtriebsseitige Reibkupplungsglied (55) unmittelbar drehfest mit dem drehbaren Brems­glied (54) verbunden ist.4. Electric train according to claim 1, characterized in that the output-side friction clutch member (55) is directly non-rotatably connected to the rotatable brake member (54). 5. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß das antriebsseitige Reibkupplungsglied (56) axial verschieblich auf der Ankerwelle (11) sitzt und durch eine an der Ankerwelle (11) ab­gestützte Federeinrichtung (58) in die Reibein­griffsstellung mit dem abtriebsseitigen Reib­kupplungsglied (55) vorgespannt ist.5. Electric train according to claim 1, characterized in that the drive-side friction clutch member (56) is axially displaceably on the armature shaft (11) and by a spring device (58) supported on the armature shaft (11) in the frictionally engaged position with the output-side friction clutch member (55) is biased. 6. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß beide Reibkupplungsglieder (55, 56) plane, ständig miteinander in Eingriff stehende Kupplungsflächen tragen.6. Electric train according to claim 1, characterized in that both friction clutch members (55, 56) carry flat, constantly engaging coupling surfaces. 7. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß beide Bremsglieder konus- oder kegel­förmige Bremsflächen (54, 68) aufweisen.7. Electric train according to claim 1, characterized in that both brake members have conical or conical braking surfaces (54, 68). 8. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß die Bremsflächen (54, 68) zu der Achse der Ankerwelle (11) koaxial sind.8. Electric train according to claim 1, characterized in that the braking surfaces (54, 68) to the axis of the armature shaft (11) are coaxial. 9. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß das abtriebsseitige Reibkupplungsglied (55) und das drehbare Bremsglied (54) miteinander einstückig sind.9. Electric train according to claim 1, characterized in that the output-side friction clutch member (55) and the rotatable brake member (54) are in one piece. 10. Elektrozug nach Anspruch 1, dadurch gekennzeich­net, daß das drehbare Bremsglied (54) drehfest mit einem Zahnrad (49) verbunden ist.10. Electric train according to claim 1, characterized in that the rotatable brake member (54) is rotatably connected to a gear (49). 11. Elektrozug nach Anspruch 10, dadurch gekennzeich­net, daß das drehfest mit dem Bremsglied (54) ver­bundene Zahnrad (49) Teil des zweiten Antriebs­stranges ist.11. Electric train according to claim 10, characterized in that the rotationally fixed to the brake member (54) connected gear (49) is part of the second drive train. 12. Elektrozug nach Anspruch 10, dadurch gekennzeich­net, daß das Zahnrad (49) auf einer Nabe (48) aus­gebildet ist, die starr und drehfest mit dem drehbaren Bremsglied (54) und/oder dem abtriebs­seitigen Reibkupplungsglied (55) verbunden ist.12. Electric train according to claim 10, characterized in that the gear (49) is formed on a hub (48) which is rigidly and non-rotatably connected to the rotatable brake member (54) and / or the output-side friction clutch member (55).
EP88103243A 1987-03-28 1988-03-03 Electric hoist Expired - Lifetime EP0284807B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88103243T ATE94148T1 (en) 1987-03-28 1988-03-03 ELECTRIC TRAIN.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3710332 1987-03-28
DE3710332A DE3710332C1 (en) 1987-03-28 1987-03-28 Electric train

Publications (3)

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EP0284807A2 true EP0284807A2 (en) 1988-10-05
EP0284807A3 EP0284807A3 (en) 1990-03-07
EP0284807B1 EP0284807B1 (en) 1993-09-08

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EP (1) EP0284807B1 (en)
AT (1) ATE94148T1 (en)
DE (2) DE3710332C1 (en)

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EP0684206A1 (en) * 1994-05-26 1995-11-29 Grapha-Holding Ag Hand or motor-driven hoisting device
WO1999032390A1 (en) * 1997-12-22 1999-07-01 Turco, Joe A winching apparatus
WO1999050169A1 (en) * 1998-03-27 1999-10-07 Hek Manufacturing B.V. Braking device
EP0950632A2 (en) * 1998-04-17 1999-10-20 R. Stahl Fördertechnik GmbH Chain hoist
DE4440420C3 (en) * 1994-11-07 2003-07-24 Demag Cranes & Components Gmbh Method and device for monitoring and / or controlling the speed of an electric drive with frequency converter for hoists
EP1505032A3 (en) * 2003-08-01 2006-05-17 Demag Cranes & Components GmbH Chain hoist
CN116199150A (en) * 2023-03-23 2023-06-02 台州市索立机械有限公司 Electric hoist for heat treatment

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DE19507191C1 (en) * 1995-03-02 1996-10-02 Stahl R Foerdertech Gmbh Hoist with a clutch adjustable by the brake
DE19507190C1 (en) * 1995-03-02 1996-08-29 Stahl R Foerdertech Gmbh Lifting device with a brake acting on both sides of the coupling
DE10237700B4 (en) * 2002-02-27 2005-10-27 Demag Cranes & Components Gmbh Hoist, especially chain hoist

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FR1355145A (en) * 1963-04-06 1964-03-13 Demag Zug Gmbh Electric hoist
DE1963647A1 (en) * 1969-02-28 1970-10-08 Suhl Hebezeugwerk Mechanized spur gear train
DE2808750A1 (en) * 1977-03-11 1978-09-14 Wurzen Foerdertech COUPLING, ESPECIALLY FOR SMALL ELECTRIC CABLES
DE3330528A1 (en) * 1982-08-25 1984-03-08 Kabushiki Kaisha Kito, Kawasaki, Kanagawa Hoist

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DE3142473A1 (en) * 1981-10-27 1983-05-11 R. Stahl GmbH & Co , Elektrozugwerk, 7118 Künzelsau ELECTRIC CHAIN HOIST

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DE804951C (en) * 1949-04-22 1951-05-04 Arthur Graef Encapsulated log winch
DE1020780B (en) * 1953-03-26 1957-12-12 Swf Sueddeutsche Waggon Und Fo Electrically powered work equipment, in particular a hoist, with a multi-stage speed switch caused by lifting off the friction surface
FR1355145A (en) * 1963-04-06 1964-03-13 Demag Zug Gmbh Electric hoist
DE1963647A1 (en) * 1969-02-28 1970-10-08 Suhl Hebezeugwerk Mechanized spur gear train
DE2808750A1 (en) * 1977-03-11 1978-09-14 Wurzen Foerdertech COUPLING, ESPECIALLY FOR SMALL ELECTRIC CABLES
DE3330528A1 (en) * 1982-08-25 1984-03-08 Kabushiki Kaisha Kito, Kawasaki, Kanagawa Hoist

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0684206A1 (en) * 1994-05-26 1995-11-29 Grapha-Holding Ag Hand or motor-driven hoisting device
CH687874A5 (en) * 1994-05-26 1997-03-14 Grapha Holding Ag Hand- or motor-operated hoist.
DE4440420C3 (en) * 1994-11-07 2003-07-24 Demag Cranes & Components Gmbh Method and device for monitoring and / or controlling the speed of an electric drive with frequency converter for hoists
WO1999032390A1 (en) * 1997-12-22 1999-07-01 Turco, Joe A winching apparatus
US6607182B1 (en) 1997-12-22 2003-08-19 Joe Turco Winching apparatus
WO1999050169A1 (en) * 1998-03-27 1999-10-07 Hek Manufacturing B.V. Braking device
EP0950632A2 (en) * 1998-04-17 1999-10-20 R. Stahl Fördertechnik GmbH Chain hoist
EP0950632A3 (en) * 1998-04-17 2003-05-07 R. Stahl Fördertechnik GmbH Chain hoist
EP1505032A3 (en) * 2003-08-01 2006-05-17 Demag Cranes & Components GmbH Chain hoist
CN116199150A (en) * 2023-03-23 2023-06-02 台州市索立机械有限公司 Electric hoist for heat treatment
CN116199150B (en) * 2023-03-23 2024-02-23 台州市索立机械有限公司 Electric hoist for heat treatment

Also Published As

Publication number Publication date
EP0284807A3 (en) 1990-03-07
EP0284807B1 (en) 1993-09-08
ATE94148T1 (en) 1993-09-15
DE3710332C1 (en) 1988-07-21
DE3883820D1 (en) 1993-10-14

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