WO2024170199A1 - Frein à actionnement électromagnétique et moteur électrique équipé d'un frein à actionnement électromagnétique - Google Patents

Frein à actionnement électromagnétique et moteur électrique équipé d'un frein à actionnement électromagnétique Download PDF

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Publication number
WO2024170199A1
WO2024170199A1 PCT/EP2024/051076 EP2024051076W WO2024170199A1 WO 2024170199 A1 WO2024170199 A1 WO 2024170199A1 EP 2024051076 W EP2024051076 W EP 2024051076W WO 2024170199 A1 WO2024170199 A1 WO 2024170199A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring magnet
lining carrier
shaft
brake
axial direction
Prior art date
Application number
PCT/EP2024/051076
Other languages
German (de)
English (en)
Inventor
Gerolf Fichtner-Pflaum
Alexander Stahl
Original Assignee
Sew-Eurodrive Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sew-Eurodrive Gmbh & Co. Kg filed Critical Sew-Eurodrive Gmbh & Co. Kg
Publication of WO2024170199A1 publication Critical patent/WO2024170199A1/fr

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/102—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction brakes
    • H02K7/1021—Magnetically influenced friction brakes
    • H02K7/1023—Magnetically influenced friction brakes using electromagnets
    • H02K7/1025—Magnetically influenced friction brakes using electromagnets using axial electromagnets with generally annular air gap
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/15—Mounting arrangements for bearing-shields or end plates

Definitions

  • the invention relates to an electromagnetically actuated brake and an electric motor with an electromagnetically actuated brake.
  • a brake motor has a motor with a brake, where the brake is applied when activated and released when released.
  • a magnetic braking system is known from US 3 579 003 A.
  • the invention is therefore based on the object of carrying out the operation of a brake motor with the highest possible safety.
  • the object is achieved in the brake according to the features specified in claim 1 and in the electric motor according to the features specified in claim 14.
  • a lining carrier of the brake is connected to a shaft in a rotationally fixed manner, and the lining carrier is arranged to be movable relative to the shaft in the axial direction, in particular parallel to the direction of the axis of rotation of the shaft, wherein an armature disk of the brake is rotationally connected to a magnetic body of the brake, wherein the armature disk is arranged to be movable in the axial direction, wherein magnetic bar magnets, in particular magnetized in the axial direction, are accommodated in the lining carrier, wherein a first ring magnet is arranged on a bearing plate of the electric motor, wherein a second ring magnet is arranged on the armature disk.
  • the advantage here is that safe operation of the brake motor can be guaranteed.
  • the armature disk When the brake is applied, the armature disk is axially retracted from the lining carrier, so that the lining carrier with its brake pads is retracted from the braking surfaces against which the brake pads were in frictional contact.
  • the ring magnets and the bar magnets enable the lining carrier to be axially centered between the bearing plate and the armature disk.
  • the detachment of the lining carrier with its brake pad from the braking surface formed on the bearing plate is supported by the magnetic repulsion between the first ring magnet and the bar magnets.
  • the pad carrier is axially spaced quickly, efficiently and safely using the magnets.
  • the radial direction and the circumferential direction are always related to the axis of rotation of the shaft; the axial direction is parallel to the direction of the axis of rotation of the shaft.
  • the second ring magnet is accommodated in an annular recess in the armature disk and/or is integrally connected, in particular adhesively connected, to the armature disk.
  • the ring axis of the first ring magnet is aligned coaxially to the axis of rotation of the shaft.
  • the advantage here is that it is more difficult for the lining carrier to tilt. This ensures trouble-free operation.
  • the ring axis of the second ring magnet is aligned coaxially to the axis of rotation of the shaft. The advantage here is that it is more difficult for the lining carrier to tilt. This ensures trouble-free operation.
  • the bar magnets are spaced apart from one another in the circumferential direction, in particular evenly spaced from one another.
  • the advantage here is that the lining carrier only needs to be equipped with a few bar magnets. This means that the bar magnets of the lining carrier are axially centered between the first and second ring magnets.
  • the bar magnets each have the same radial distance from the axis of rotation of the shaft and/or are each arranged at the same axial location.
  • the advantage here is that the lining carrier can be centered as precisely as possible between the two ring magnets by the magnetically repelling bar magnets.
  • the respective bar magnet has the same type of pole, for example north pole, on its side facing the first ring magnet as the first ring magnet on its side facing the bar magnet.
  • the respective bar magnet has the same type of pole, for example south pole, on its side facing the second ring magnet as the second ring magnet on its side facing the respective bar magnet.
  • the radial distance areas covered by the bar magnets are identical to one another and/or the areas covered by the bar magnets in the axial direction are identical to one another.
  • the advantage here is that the bar magnets are all arranged at the same circumferential angular position and all have the same axial position.
  • the first ring magnet is magnetized in the axial direction
  • the second ring magnet is magnetized in the axial direction
  • the bar magnets are each magnetized opposite to the axial direction
  • the first ring magnet is magnetized opposite to the axial direction
  • the second ring magnet is magnetized opposite to the axial direction
  • the bar magnets are each magnetized in the axial direction.
  • the repulsive magnetic force between the bar magnets and the ring magnets is overcome and the brake pads arranged axially on both sides of the pad carrier are pressed onto the respective braking surfaces, in particular a first brake pad onto the first braking surface and a second brake pad onto the second braking surface.
  • the bar magnets are each arranged in a respective recess that runs through the lining carrier in the axial direction and/or are integrally connected, in particular adhesively bonded, to the lining carrier.
  • tab areas punched out and/or formed on the lining carrier at least partially encompass the bar magnets and thus limit them axially.
  • the advantage here is that a positive axial securing is made possible, in particular in addition.
  • the pad carrier has brake pads axially on both sides, with the brake pads being arranged radially outside the bar magnets, the first ring magnet and/or the second ring magnet.
  • the first ring magnet is designed to be uninterrupted in the circumferential direction, in particular with respect to the axis of rotation of the shaft. It is advantageous here that that simple assembly is possible.
  • the lining carrier can be axially centered between the first and second ring magnets, regardless of the rotational position of the lining carrier.
  • the second ring magnet is designed to be uninterrupted in the circumferential direction, particularly in relation to the axis of rotation of the shaft.
  • the advantage here is that it enables simple assembly.
  • the lining carrier can be axially centered in the middle between the first and second ring magnets, regardless of the rotational position of the lining carrier.
  • a coil winding is arranged in the magnet body, in particular in an annular recess of the magnet body, in particular the winding axis of which is aligned coaxially to the axis of rotation of the shaft, wherein spring elements supported on the magnet body press on the armature disk, wherein a first braking surface is formed on the bearing plate on the side of the lining carrier facing the lining carrier or a friction disk is connected to the bearing plate, which provides a first braking surface on its side of the lining carrier facing the lining carrier, in particular wherein the armature disk provides a second braking surface on its side facing the lining carrier.
  • the advantage here is that in the event of a power failure, the brake is automatically applied, since the spring force generated by the spring elements presses the armature disk towards the lining carrier and thus presses it onto the first braking surface formed on the bearing plate. Only when the coil winding is energized does the attractive magnetic force acting on the armature disk overcome the spring force generated by the spring elements, so that the armature disk is moved towards the magnetic body and the lining carrier is thus released from the braking surfaces. In this case, especially when the lining carrier is released, the magnetic repulsive force between the bar magnets and the ring magnets assists.
  • the shaft protrudes through a recess in the
  • the magnetic body and is located on the side of the The magnet body is connected to a fan.
  • the advantage of this is that it is easy to dissipate heat from the magnet body and thus also from the brake.
  • the brake has a plate part which is rotatably mounted on the magnet body.
  • the radial distance area covered by the bar magnets overlaps with the radial distance area covered by the first ring magnet or is identical to it.
  • the advantage here is that the lining carrier can be magnetically centered in the axial direction. This is because the bar magnets are in the same radial position as the ring magnets. The repulsive force is therefore sufficiently strong.
  • the radial distance range covered by the bar magnets overlaps with the radial distance range covered by the second ring magnet or is identical to it, in particular wherein the bar magnets are arranged in the axial direction between the first ring magnet and the second ring magnet.
  • the advantage here is that centering in the axial direction is magnetically possible.
  • the lining carrier has an internal toothing which is placed on the external toothing of an annular driver, wherein the driver is connected to the shaft in a rotationally fixed manner, in particular by means of a key connection. It is advantageous that the lining carrier is connected to the driver in a rotationally fixed manner and at the same time is arranged to be axially displaceable.
  • the shaft is a rotor shaft of the electric motor.
  • the bearing shield accommodates a floating bearing, the inner ring of which is placed on the shaft and the outer ring of which is accommodated in the bearing shield,
  • the bearing shield is connected to a stator housing of the electric motor, a bearing flange on the side of the stator housing facing away from the bearing shield is connected to the stator housing and accommodates a fixed bearing, which together with the floating bearing supports the shaft so that it can rotate.
  • the advantage here is that the floating bearing is accommodated in the bearing shield and thus thermally induced changes in the length of the shaft can be compensated.
  • the lining carrier is also designed to compensate for the
  • Length change suitably movable on the shaft or the driver.
  • Figure 1 shows a longitudinal section through an electric motor according to the invention with an electromagnetically actuated brake.
  • Figure 2 shows an enlarged section of Figure 1.
  • the electric motor has a rotatably mounted rotor shaft 2, which is rotatably mounted by means of a bearing 1 which is accommodated in a bearing plate 15.
  • bearing 1 is designed as a floating bearing.
  • the bearing shield is connected to a stator housing which, on its side axially remote from the bearing shield 15, is connected to a bearing flange in which a further bearing, in particular a fixed bearing, is accommodated for the rotatable mounting of the rotor shaft 2.
  • An annular driver 4 is placed on the rotor shaft 2 and is connected to the rotor shaft 2 in a rotationally fixed manner by means of a feather key 3.
  • the driver 4 has an external toothing onto which a lining carrier 7 is placed with its internal toothing.
  • the lining carrier 7 is thus connected to the driver 4 in a rotationally fixed manner and is nevertheless arranged to be displaceable in the axial direction relative to the rotor shaft 2.
  • the pad carrier 7 is provided with brake pads on both axial sides.
  • an armature disk 9 is arranged, which is connected to a magnetic body 10 in a rotationally fixed manner and is arranged to be displaceable in the axial direction.
  • bolts are preferably fastened to or in the magnetic body, each of which protrudes through a respective recess in the armature disk 9, so that the armature disk 9 is arranged in a rotationally fixed manner but is axially movable relative to the magnetic body 10.
  • the magnetic body 10 is connected to the bearing plate 15.
  • An annular recess is arranged in the magnetic body 10, in which an electrically energizable coil winding 11 is accommodated.
  • the coil winding 11 is preferably designed as a ring winding, wherein the ring axis of the ring winding is aligned coaxially to the axis of rotation of the rotor shaft 2.
  • the armature disk 9 is arranged axially between the magnet body 10 and the lining carrier 7.
  • the armature disk 9 is made of a ferromagnetic material.
  • Spring elements in particular ring springs, supported on the magnet body 10 press on the armature disk 9.
  • the armature disk 9 is pressed by the spring elements onto the lining carrier, in particular onto the brake pad arranged on the side of the lining carrier facing the armature disk, so that the lining carrier, in particular the brake pad arranged on the side of the lining carrier facing away from the armature disk, is pressed on its side facing away from the armature disk 9 onto a braking surface formed on the bearing plate 15, in particular a flat ground one, or onto a friction disk fastened to the bearing plate 15 and arranged axially between the bearing plate and the lining carrier.
  • the magnet body 10 and the armature disk 9 each have a centrally arranged recess through which the rotor shaft 2 projects.
  • a fan wheel is connected in a rotationally fixed manner to the rotor shaft 2 on the side of the magnetic body 10 axially facing away from the armature disk 9.
  • a plate part 13 is provided which is rotatably mounted on the magnet body 10 and whose rotational position can be adjusted using a release lever 12 which is firmly connected to the plate part 13.
  • the armature disk 9 is arranged axially between the lining carrier 7 and the magnet body 10.
  • the armature disk 9 When the coil winding 11 is energized, the armature disk 9 is drawn towards the magnet body 10 while overcoming the spring force generated by the spring elements. In this way, the lining carrier 7 is released from the braking surface on the bearing plate 15 or from the friction plate and can move in the axial direction so that the brake runs freely.
  • a first ring magnet 5 is arranged on the bearing plate 15, in particular on the side of the bearing plate 15 axially facing the lining carrier, and a second ring magnet 8 is arranged on the side of the armature disk 9 facing the lining carrier 7.
  • the ring axis of the first ring magnet 5 is aligned coaxially to the axis of rotation of the rotor shaft 2.
  • the first ring magnet 5 is magnetized in the axial direction, in particular so that the first ring magnet 5 has a south pole on its side facing the lining carrier 7.
  • the ring axis of the second ring magnet 8 is aligned coaxially to the axis of rotation of the rotor shaft 2.
  • the second ring magnet 8 is magnetized in the axial direction, in particular so that the second ring magnet 8 has a north pole on its side facing the lining carrier 7.
  • the two ring magnets (5, 8) have in particular the same ring diameter; preferably they are therefore the same size.
  • Bar magnets 6 are accommodated in the lining carrier 7, which are magnetized in the axial direction such that they each have a south pole on their side facing the bearing plate 15 and a north pole on their side facing the armature disk 9.
  • the bar magnets 6 are spaced apart from one another in the circumferential direction, in particular regularly spaced apart from one another in the circumferential direction.
  • the bar magnets 6 are all arranged at the same radial distance from the axis of rotation of the rotor shaft 2.
  • the radial distance range covered by the bar magnets 6 overlaps with the radial distance range covered by the first ring magnet 5 and with the radial distance range covered by the second ring magnet 8.
  • the bar magnets 6 are axially spaced from both the first ring magnet 5 and the second ring magnet 8. Preferably, the distance to the respective ring magnet (5, 8) is the same.
  • the bar magnets 6 are arranged in the lining carrier 7 in a way that prevents them from moving.
  • the bar magnets 6 are preferably connected to the lining carrier 7 in a material-locking manner, in particular adhesively bonded.
  • a positive connection is also advantageous, whereby for this purpose tabs are formed on the lining carrier, in particular punched out, which at least partially encompass the bar magnet and at least axially secure it.
  • the bar magnets 6 are arranged radially inside the brake pads. The brake pads are thus attached as far radially outward as possible on the pad carrier 7.
  • the magnetic force acting as an attraction on the armature disk 9 when the coil winding 11 is energized is preferably at least ten times greater than the magnetic force acting as a repulsion on the bar magnets 6 from the first ring magnet 5.
  • the coil winding 11 is preferably accommodated in a coil body, which is preferably made of plastic, in particular as a plastic injection-molded part, wherein the coil body together with the coil winding 11 is accommodated in the pot-shaped or annular recess of the magnet body 10.
  • the second ring magnet 8 is accommodated in an annular recess in the bearing plate 15. If no friction plate is provided, a finely machined ring surface is formed on the bearing plate radially outside the second ring magnet 8, which serves as a braking surface on the side of the bearing plate 15 facing the lining carrier 7. If a friction plate is present as an alternative, this is preferably punched out of a sheet metal as a perforated disk.
  • the rotor shaft 2 is provided with external teeth instead of the driver 4 and the lining carrier 7 is fitted onto the rotor shaft with its internal teeth.
  • the driver 4 and the feather key 3 can thus be dispensed with.

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  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un frein à actionnement électromagnétique et un moteur électrique équipé d'un frein à actionnement électromagnétique, un support de garniture étant relié à un arbre de rotor du moteur électrique pour une rotation conjointe, et le support de garniture étant disposé de manière à pouvoir se déplacer dans la direction axiale par rapport à l'arbre de rotor, une plaque d'induit du frein étant reliée à un corps d'aimant du frein pour une rotation conjointe, la plaque d'induit étant disposée de manière à pouvoir se déplacer dans la direction axiale, des barres magnétiques étant reçues dans le support de garniture, un premier aimant annulaire étant disposé sur un flasque du moteur électrique, un second aimant annulaire étant disposé sur la plaque d'induit.
PCT/EP2024/051076 2023-02-15 2024-01-17 Frein à actionnement électromagnétique et moteur électrique équipé d'un frein à actionnement électromagnétique WO2024170199A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102023000504 2023-02-15
DE102023000504.5 2023-02-15

Publications (1)

Publication Number Publication Date
WO2024170199A1 true WO2024170199A1 (fr) 2024-08-22

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Family Applications (1)

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PCT/EP2024/051076 WO2024170199A1 (fr) 2023-02-15 2024-01-17 Frein à actionnement électromagnétique et moteur électrique équipé d'un frein à actionnement électromagnétique

Country Status (2)

Country Link
DE (1) DE102024000140A1 (fr)
WO (1) WO2024170199A1 (fr)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3579003A (en) 1969-07-31 1971-05-18 Robert C Gray Magnetic braking system
EP1011188B1 (fr) * 1998-12-16 2003-03-19 ZF FRIEDRICHSHAFEN Aktiengesellschaft Moteur électrique avec frein intégré actionné électromagnétiquement et sans jeu de rotation
EP1832778A2 (fr) * 2006-03-08 2007-09-12 Kendrion Binder Magnete GmbH Frein à pression de ressort doté de disques de frein comprenant des surfaces de friction aux parois latérales opposées les unes aux autres
DE102010049747A1 (de) 2010-10-29 2012-05-03 Sew-Eurodrive Gmbh & Co. Kg Bausatz zur Herstellung unterschiedlicher Elektromotoren einer Baureihe von Elektromotoren und Verfahren zur Herstellung
DE102010049744A1 (de) 2010-10-29 2012-05-03 Sew-Eurodrive Gmbh & Co. Kg Bremse
DE102010049748A1 (de) 2010-10-29 2012-05-03 Sew-Eurodrive Gmbh & Co. Kg Elektromotor
US20130186726A1 (en) * 2010-08-12 2013-07-25 Microtecnica S.R.L. Electromagnetic Brake or Clutch and Method of Operation
DE102012019415A1 (de) * 2012-10-04 2014-04-10 Sew-Eurodrive Gmbh & Co Kg Elektromotor, insbesondere mit einer redundanten Bremsanordnung
EP2514644B1 (fr) * 2011-04-19 2014-06-11 Robert Bosch GmbH Dispositif de verrouillage, en particulier pour verrouillage du volant

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3579003A (en) 1969-07-31 1971-05-18 Robert C Gray Magnetic braking system
EP1011188B1 (fr) * 1998-12-16 2003-03-19 ZF FRIEDRICHSHAFEN Aktiengesellschaft Moteur électrique avec frein intégré actionné électromagnétiquement et sans jeu de rotation
EP1832778A2 (fr) * 2006-03-08 2007-09-12 Kendrion Binder Magnete GmbH Frein à pression de ressort doté de disques de frein comprenant des surfaces de friction aux parois latérales opposées les unes aux autres
US20130186726A1 (en) * 2010-08-12 2013-07-25 Microtecnica S.R.L. Electromagnetic Brake or Clutch and Method of Operation
DE102010049747A1 (de) 2010-10-29 2012-05-03 Sew-Eurodrive Gmbh & Co. Kg Bausatz zur Herstellung unterschiedlicher Elektromotoren einer Baureihe von Elektromotoren und Verfahren zur Herstellung
DE102010049744A1 (de) 2010-10-29 2012-05-03 Sew-Eurodrive Gmbh & Co. Kg Bremse
DE102010049748A1 (de) 2010-10-29 2012-05-03 Sew-Eurodrive Gmbh & Co. Kg Elektromotor
EP2514644B1 (fr) * 2011-04-19 2014-06-11 Robert Bosch GmbH Dispositif de verrouillage, en particulier pour verrouillage du volant
DE102012019415A1 (de) * 2012-10-04 2014-04-10 Sew-Eurodrive Gmbh & Co Kg Elektromotor, insbesondere mit einer redundanten Bremsanordnung

Also Published As

Publication number Publication date
DE102024000140A1 (de) 2024-08-22

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