WO2021256156A1 - Moteur équipé d'un frein - Google Patents

Moteur équipé d'un frein Download PDF

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Publication number
WO2021256156A1
WO2021256156A1 PCT/JP2021/019141 JP2021019141W WO2021256156A1 WO 2021256156 A1 WO2021256156 A1 WO 2021256156A1 JP 2021019141 W JP2021019141 W JP 2021019141W WO 2021256156 A1 WO2021256156 A1 WO 2021256156A1
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WO
WIPO (PCT)
Prior art keywords
brake disc
slinger
armature
bearing
brake
Prior art date
Application number
PCT/JP2021/019141
Other languages
English (en)
Japanese (ja)
Inventor
修平 大村
登史 小川
清次 西尾
Original Assignee
パナソニックＩｐマネジメント株式会社
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 パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to JP2022532408A priority Critical patent/JPWO2021256156A1/ja
Priority to CN202180041811.4A priority patent/CN115699535A/zh
Publication of WO2021256156A1 publication Critical patent/WO2021256156A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/28—Brakes with only one rotating disc
    • 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
    • H02K7/08—Structural association with bearings
    • 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

Definitions

  • This disclosure relates to a motor with a brake.
  • Patent Document 1 discloses an elevator hoist having a motor, a sheave in which a brake disc is integrally formed, and an oil guide structure.
  • the posture of the motor itself may change when it is incorporated in a device or the like.
  • the oil guide structure as in Patent Document 1 when the posture of the motor is changed, the oil leaked from the bearing portion adheres to the brake disc.
  • an object of the present disclosure is to provide a motor with a brake that can suppress oil from adhering to the brake disc.
  • the motor with a brake includes a rotating shaft to which a rotor is attached, a bearing that rotatably supports the rotating shaft, and a brake disc provided at a position different from the bearing in the axial direction of the rotating shaft.
  • An intermediate member provided between the bearing and the brake disc, which has a first through hole through which the rotating shaft is inserted so as to rotate, and an intermediate member for braking the rotation of the rotating shaft, and the bearing.
  • a slinger provided between the and the intermediate member is provided, and the slinger is attached to the rotation shaft and rotates together with the rotation shaft, and the slinger is attached to the rotation shaft in the radial direction of the rotation shaft from the outer peripheral surface of the rotation shaft. Protrude.
  • FIG. 1 is a cross-sectional view showing a motor with a brake according to an embodiment.
  • FIG. 2 is a cross-sectional view showing the vicinity of the brake portion of the motor with a brake of FIG.
  • FIG. 3 is a cross-sectional view taken along the line III-III of FIG.
  • FIG. 4 is a sectional view taken along line IV-IV of FIG.
  • FIG. 5A is a front view showing another example of the slinger.
  • 5B is a sectional view taken along line VV of FIG. 5A.
  • FIG. 6A is a front view showing still another example of the slinger.
  • FIG. 6B is a sectional view taken along line VI-VI of FIG. 6A.
  • FIG. 7A is a front view showing still another example of the slinger.
  • FIG. 7B is a sectional view taken along line VII-VII of FIG. 7A.
  • FIG. 8 is a cross-sectional view showing the vicinity of the brake portion of the motor with
  • each figure is a schematic diagram and is not necessarily exactly illustrated.
  • the same reference numerals are given to substantially the same configurations, and duplicate explanations will be omitted or simplified.
  • FIG. 1 is a cross-sectional view showing a motor 10 with a brake according to an embodiment.
  • FIG. 1 shows a state in which the side plate 40 and the armature 46 are pressing the brake disc 38.
  • the motor with brake 10 includes a motor unit 12, a brake unit 14, and an encoder unit 16.
  • the brake unit 14 is a portion that brakes the rotation of the rotation shaft 26 of the motor unit 12.
  • the encoder unit 16 is a portion that detects the rotation of the rotation shaft 26 of the motor unit 12.
  • the axial direction indicates the axial direction of the rotating shaft 26 (see the arrow X in FIGS. 1 and 2).
  • FIG. 3 is a cross-sectional view taken along the line III-III of FIG.
  • FIG. 4 is a sectional view taken along line IV-IV of FIG.
  • the motor unit 12 has a first case 18, a motor cover 20, a stator 22, a rotor 24, a rotating shaft 26, and a first bearing 28.
  • the first case 18 is a case for accommodating the stator 22 and the rotor 24 and the like.
  • the first case 18 has a cylindrical shape, and both ends of the first case 18 in the axial direction are open.
  • a brake portion 14 is provided on one end side of the first case 18, and a motor cover 20 is provided on the other end side of the first case 18.
  • the motor cover 20 is attached to the other end of the first case 18 in the axial direction.
  • the motor cover 20 is provided with a first bearing 28 that rotatably supports the rotating shaft 26.
  • the stator 22 is attached to the inside of the first case 18.
  • the stator 22 has a cylindrical shape.
  • a rotating shaft 26 and a rotor 24 are rotatably inserted inside the stator 22.
  • a magnetic field acting on the rotor 24 is generated.
  • the rotor 24 is provided inside the stator 22 in a state of being attached to the rotating shaft 26.
  • the rotor 24 is rotatable with respect to the stator 22. Specifically, the rotor 24 can rotate together with the rotating shaft 26 with the axis A of the rotating shaft 26 as the center of rotation.
  • a magnetic field is generated in the rotor 24 by supplying electric power to the coil 23 of the stator 22.
  • the rotor 24 receives the magnetic field and rotates together with the rotating shaft 26.
  • the rotating shaft 26 has a rod shape and is rotatably supported by the first bearing 28 and the second bearing 34 with the axis A as the center of rotation.
  • An encoder unit 16 is provided at one end of the rotating shaft 26 in the axial direction. The other end of the rotating shaft 26 in the axial direction protrudes outward from the motor cover 20.
  • FIG. 2 is a cross-sectional view showing the vicinity of the brake portion 14 of the motor 10 with a brake of FIG. FIG. 2 shows a state in which the side plate 40 and the armature 46 do not press the brake disc 38.
  • the brake portion 14 includes a second case 32, a second bearing 34, a hub 36, a brake disc 38, a side plate 40, a field core 42, a coil 44, and an armature 46. It has a plurality of springs 48, a slinger 50, and a suction member 54.
  • the braking unit 14 brakes the rotation of the rotating shaft 26. Specifically, the brake unit 14 reduces the rotational speed of the rotating shaft 26. The brake unit 14 stops the rotation of the rotating shaft 26.
  • the second case 32, the second bearing 34, the hub 36, the brake disc 38, the side plate 40, the field core 42, the coil 44, the armature 46, the plurality of springs 48, the slinger 50, and the suction member 54 rotate in the axial direction. It is provided on one side of the child 24.
  • the brake disc 38, the side plate 40, the field core 42, the coil 44, the armature 46, and the plurality of springs 48 constitute a braking mechanism for braking the rotation of the rotating shaft 26.
  • the side plate 40, the field core 42, the coil 44, the armature 46, and the plurality of springs 48 are members for braking (controlling) the rotation of the brake disc 38.
  • the side plate 40, the field core 42, the coil 44, the armature 46, and the plurality of springs 48 brake the rotation of the rotating shaft 26 by braking the rotation of the brake disc 38.
  • the second case 32 is a case for accommodating the second bearing 34, the slinger 50, the field core 42, and the like.
  • the second case 32 has a main body 56 and a wall portion 58.
  • the main body 56 has a cylindrical shape.
  • a wall portion 58 is provided at one end of the main body 56 in the axial direction.
  • the other end of the main body 56 in the axial direction is attached to the first case 18.
  • the main body 56 has an inner peripheral surface 57 facing the outer peripheral surface 43 of the field core 42 at a distance in the radial direction.
  • the wall portion 58 projects inward in the radial direction from one end of the main body 56 in the axial direction.
  • a second bearing 34 is provided on the inner peripheral surface of the wall portion 58 in the radial direction.
  • the second bearing 34 rotatably supports the rotating shaft 26.
  • Oil is stored inside the second bearing 34.
  • the oil is a bearing grease and contains, for example, a base oil, a thickener, an additive and the like.
  • the hub 36 is provided between the second bearing 34 and the rotor 24.
  • the hub 36 is annular, and a rotating shaft 26 is inserted inside the hub 36.
  • the hub 36 is attached to the rotating shaft 26 and rotates together with the rotating shaft 26.
  • the hub 36 is made of, for example, mild steel.
  • the annular shape includes a shape in which a through hole is formed in the central portion of the disk-shaped member.
  • the brake disc 38 is provided at a position different from that of the first bearing 28 and the second bearing 34 in the axial direction. Specifically, the brake disc 38 is provided on the side opposite to the first bearing 28 with respect to the rotor 24. The brake disc 38 is provided on the rotor 24 side of the second bearing 34. The brake disc 38 is annular. A rotating shaft 26 and a hub 36 are inserted inside the brake disc 38. The brake disc 38 is attached to the hub 36 so as to be movable in the axial direction with respect to the hub 36. The brake disc 38 projects outward from the hub 36 in the radial direction. The brake disc 38 has a plate shape having a main surface intersecting the axial direction. The brake disc 38 rotates with the hub 36 and the rotating shaft 26 about the axis A as the center of rotation. For example, the brake disc 38 is a friction plate and is made of resin or the like.
  • the side plate 40 is provided on the rotor 24 side of the brake disc 38 in the axial direction.
  • the side plate 40 is provided on the side opposite to the armature 46 with respect to the brake disc 38.
  • the side plate 40 is an annular shape having a through hole 60 through which the rotating shaft 26 and the hub 36 are rotatably inserted.
  • the side plate 40 is attached to the second case 32.
  • the side plate 40 has a plate shape having a main surface intersecting the axial direction.
  • the side plate 40 faces the main surface of the brake disc 38 in the axial direction.
  • the side plate 40 does not rotate with the rotating shaft 26.
  • the side plate 40 is made of mild steel or the like.
  • the field core 42 is located on the second bearing 34 side of the brake disc 38 in the axial direction, and is provided between the brake disc 38 and the second bearing 34.
  • the field core 42 is an annular shape having a through hole 62 through which the rotating shaft 26 is rotatably inserted, and is attached to the second case 32.
  • the field core 42 extends in the axial direction.
  • the field core 42 has a cylindrical shape. In the radial direction, a gap is formed between the inner peripheral surface 63 of the through hole 62 and the outer peripheral surface 27 of the rotating shaft 26, and the field core 42 does not rotate together with the rotating shaft 26.
  • a plurality of springs 48 are connected to the field core 42.
  • the field core 42 is made of mild steel or the like.
  • the field core 42 corresponds to the intermediate member
  • the through hole 62 corresponds to the first through hole.
  • the coil 44 is provided inside the field core 42. By supplying electric power to the coil 44, the field core 42 is magnetized.
  • the armature 46 is located on the second bearing 34 side of the brake disc 38 in the axial direction.
  • the armature 46 is provided between the brake disc 38 and the field core 42.
  • the armature 46 is an annular shape having a through hole 64 through which the rotating shaft 26 is rotatably inserted.
  • the armature 46 is connected to the field core 42 via a plurality of springs 48.
  • the armature 46 is axially movable with respect to the field core 42.
  • the armature 46 has a plate shape having a main surface intersecting the axial direction, and faces the main surface of the brake disc 38 in the axial direction. In the radial direction, a gap is formed between the inner peripheral surface 65 of the through hole 64 and the outer peripheral surface 27 of the rotating shaft 26.
  • the armature 46 does not rotate with the rotation shaft 26.
  • the armature 46 is made of mild steel or the like.
  • the armature 46 is pushed out to the brake disc 38 side by a plurality of springs 48 in a state where power is not supplied to the coil 44.
  • the armature 46 and the side plate 40 press the brake disc 38 (see FIG. 1).
  • the rotation of the brake disc 38 is damped, and the rotation of the rotating shaft 26 is damped.
  • FIG. 3 illustrations other than the rotating shaft 26, the slinger 50, and the field core 42 are omitted.
  • the slinger 50 is located on the second bearing 34 side of the field core 42 in the axial direction.
  • the slinger 50 is provided between the second bearing 34 and the field core 42.
  • the slinger 50 faces the second bearing 34 at a distance in the axial direction.
  • the slinger 50 faces the field core 42 at a distance.
  • the slinger 50 is an annular shape having a through hole 66 through which the rotating shaft 26 is closely inserted, and is attached to the rotating shaft 26. That is, the slinger 50 is provided over the entire circumference of the outer peripheral surface 27 of the rotating shaft 26 in the circumferential direction.
  • the rotary shaft 26 is press-fitted into the through hole 66, the rotary shaft 26 is brought into close contact with the through hole 66.
  • the slinger 50 rotates together with the rotation shaft 26.
  • the slinger 50 is made of mild steel or the like.
  • the through hole 66 corresponds to the second through hole.
  • the slinger 50 projects radially from the outer peripheral surface 27 of the rotating shaft 26. Specifically, the slinger 50 projects radially outward from the outer peripheral surface of the second bearing 34.
  • the diameter (outer diameter) D1 of the slinger 50 in the radial direction is larger than the diameter (outer diameter) D2 of the second bearing 34 in the radial direction, and the second bearing 34 has a diameter larger than that of the slinger 50 when viewed from the axial direction.
  • the slinger 50 overlaps with the second bearing 34 so as not to protrude outward in the direction.
  • the slinger 50 projects radially outward from the inner peripheral surface 63 of the through hole 62 of the field core 42.
  • the diameter D1 of the slinger 50 is larger than the diameter D3 of the through hole 62.
  • the diameter D1 of the slinger 50 overlaps with the through hole 62 so that the through hole 62 does not protrude radially outward from the slinger 50 when viewed from the axial direction. Further, when viewed from the axial direction, the slinger 50 overlaps the entire gap between the outer peripheral surface 27 of the rotating shaft 26 and the inner peripheral surface 63 of the through hole 62.
  • the slinger 50 does not project radially outward from the outer peripheral surface 43 of the field core 42.
  • the diameter D1 of the slinger 50 is smaller than the diameter (outer diameter) D4 of the field core 42.
  • the field core 42 protrudes radially outward from the slinger 50.
  • the slinger 50 is a plate shape having a main surface intersecting the axial direction.
  • the slinger 50 has an inclined surface 68 connected to the radial outer end of the main surface 67 on the second bearing 34 side of the slinger 50.
  • the inclined surface 68 is inclined so as to be located on the field core 42 side as it goes outward in the radial direction. That is, the end portion of the inclined surface 68 on the field core 42 side is located radially outward from the end portion of the inclined surface 68 on the second bearing 34 side.
  • the adsorption member 54 is a member that adsorbs the oil leaked from the second bearing 34.
  • FIG. 4 illustrations other than the rotating shaft 26, the field core 42, the coil 44, the suction member 54, and the second case 32 are omitted.
  • the suction member 54 is annular.
  • the suction member 54 is provided between the outer peripheral surface 43 of the field core 42 and the inner peripheral surface 57 of the second case 32.
  • the suction member 54 is between the outer peripheral surface 43 and the inner peripheral surface 57 so as to fill the gap between the outer peripheral surface 43 of the field core 42 and the inner peripheral surface 57 of the second case 32 when viewed from the axial direction. It is provided in.
  • the adsorption member 54 is made of, for example, polyurethane or the like.
  • the oil contained in the second bearing 34 may leak out.
  • the base oil of the oil (bearing grease) sealed inside the second bearing 34 is vaporized by the pushing action by stirring inside the second bearing 34 or the heat generation, and the vaporized base oil is the second bearing 34. It may leak from the seal.
  • a slinger 50 is provided between the second bearing 34 and the field core 42.
  • the slinger 50 can dam the oil leaking from the second bearing 34 and prevent the oil from entering the gap between the through hole 62 of the field core 42 and the rotating shaft 26. As a result, it is possible to prevent the oil from adhering to the brake disc 38 through the gap.
  • the oil leaked from the second bearing 34 is blown outward along the slinger 50 in the radial direction due to the centrifugal force generated by the rotation of the rotating shaft 26 (see arrow B in FIG. 2).
  • the oil blown outward in the radial direction is adsorbed by the adsorbing member 54.
  • the motor 10 with a brake according to the embodiment has been described above.
  • the motor 10 with a brake includes a rotating shaft 26 to which the rotor 24 is attached, a second bearing 34 corresponding to a bearing that supports the rotating shaft 26 so as to rotate, and a second bearing 34 in the axial direction of the rotating shaft 26.
  • the brake disc 38 provided at a position different from that of the two bearings 34 and the through hole 62 through which the rotating shaft 26 is inserted so as to rotate are provided between the second bearing 34 and the brake disc 38, and the rotating shaft 26 is provided.
  • a field core 42 corresponding to an intermediate member for braking the rotation of the second bearing 34 and a slinger 50 provided between the second bearing 34 and the field core 42 are provided.
  • the slinger 50 is attached to the rotary shaft 26, rotates together with the rotary shaft 26, and projects in the radial direction of the rotary shaft 26 from the outer peripheral surface 27 of the rotary shaft 26.
  • a slinger 50 attached to the rotating shaft 26 and protruding in the radial direction of the rotating shaft 26 from the outer peripheral surface 27 of the rotating shaft 26 is provided between the second bearing 34 and the field core 42. .. Therefore, it is possible to prevent the oil leaking from the second bearing 34 from entering the gap between the through hole 62 and the rotating shaft 26 by being dammed by the slinger 50. As a result, it is possible to prevent the oil leaking from the second bearing 34 from adhering to the brake disc 38 through the gap between the through hole 62 and the rotating shaft 26.
  • the slinger 50 attached to the rotating shaft 26 also rotates, and the oil leaked from the second bearing 34 can be blown outward by centrifugal force. As a result, it is possible to prevent the oil leaking from the second bearing 34 from adhering to the brake disc 38 through the gap between the through hole 62 and the rotating shaft 26.
  • the slinger 50 is an annular shape having a through hole 66 through which the rotating shaft 26 is closely inserted.
  • the slinger 50 projects radially outward from the inner peripheral surface 63 of the through hole 62.
  • the second bearing 34 is used. Even if the leaked oil gets over the slinger 50 and flows downward, it can be prevented from entering the gap between the through hole 62 and the rotating shaft 26. As a result, it is possible to further suppress the oil from adhering to the brake disc 38.
  • the slinger 50 has an inclined surface 68 connected to the radial outer end portion of the main surface 67 on the second bearing 34 side of the slinger 50, and the inclined surface 68 has an inclined surface 68. It is inclined so as to be located on the field core 42 side corresponding to the intermediate member as it goes outward in the radial direction.
  • the oil leaked from the second bearing 34 can be easily guided outward in the radial direction by moving it along the inclined surface 68. It is possible to further prevent the oil from entering the gap between the through hole 62 and the rotating shaft 26. As a result, it is possible to further suppress the oil leaking from the second bearing 34 from adhering to the brake disc 38.
  • the motor 10 with a brake has an inner peripheral surface 57 facing the outer peripheral surface 43 of the field core 42 corresponding to the intermediate member in the radial direction.
  • the second case 32 of the motor 10 with a brake includes a second case 32 accommodating a second bearing 34, a slinger 50, and a field core 42, an outer peripheral surface 43 of the field core 42, and an inner peripheral surface 57 of the second case 32. It is further provided with a suction member 54 for adsorbing oil leaked from the second bearing 34, which is provided between the two bearings.
  • the slinger 50 does not project radially outward from the outer peripheral surface 43 of the field core 42.
  • the slinger 50 does not protrude outward in the radial direction from the outer peripheral surface 43 of the field core 42. Therefore, by rotating the slinger 50, the oil leaked from the second bearing 34 can be easily blown off between the outer peripheral surface 43 of the field core 42 and the inner peripheral surface 57 of the second case 32. .. Since the motor 10 with a brake includes a suction member 54, the blown oil can be sucked by the suction member 54. As a result, it is possible to further suppress the oil leaking from the second bearing 34 from adhering to the brake disc 38.
  • the motor 10 with a brake has a coil 44 provided inside a field core 42 corresponding to an intermediate part, a spring 48 connected to the field core 42, an armature 46, and an armature 46 opposite to the brake disc 38. It further includes a side plate 40 provided on the side.
  • the armature 46 is provided between the field core 42 and the brake disc 38 and is connected to the field core 42 via a spring 48.
  • the brake disc 38 rotates together with the rotating shaft 26 and satisfies the following (i). (I) In a state where power is not supplied to the coil 44, the armature 46 is pushed toward the brake disc 38 by the spring 48, and the armature 46 and the side plate 40 press the brake disc 38. While power is being supplied to the coil 44, the armature 46 is attracted to the field core 42 side, and the armature 46 and the side plate 40 do not press the brake disc 38.
  • the rotation of the rotating shaft 26 can be braked by using the field core 42, the armature 46, the side plate 40, and the like. Further, it is possible to prevent the oil leaked from the second bearing 34 from adhering to the brake disc 38 through the gap between the field core 42 and the rotating shaft 26.
  • the motor 10 with a brake may satisfy the following (ii) instead of the above (i).
  • the motor 10 with a brake may satisfy the following (ii) instead of the above (i).
  • (Ii) In a state where power is not supplied to the coil 44, the armature 46 is attracted to the field core 42 side by a spring, and the armature 46 and the side plate 40 do not press the brake disc 38. While power is being supplied to the coil 44, the armature 46 is pushed toward the brake disc 38, and the armature 46 and the side plate 40 press the brake disc 38.
  • the armature 46 and the field core 42 are connected with a pull spring or the like instead of the spring 48, the armature 46 is attracted to the field core 42 side by the pull spring or the like in a state where power is not supplied to the coil 44.
  • the armature 46 and the side plate 40 do not press the brake disc 38.
  • the armature 46 is pushed toward the brake disc 38 while the coil 44 is being powered, and the armature 46 and The side plate 40 presses the brake disc 38.
  • FIG. 5A is a front view showing the slinger 50a, which is another example of the slinger.
  • 5B is a sectional view taken along line VV of FIG. 5A.
  • the slinger 50a is mainly different from the slinger 50 in that it does not have an inclined surface 68.
  • the slinger 50a is an annular shape having a through hole 66a through which the rotating shaft 26 is closely inserted.
  • the radial outer end surface 69 of the slinger 50a is a surface parallel to the axial direction.
  • the through hole 66a corresponds to the second through hole.
  • FIG. 6A is a front view showing the slinger 50b, which is another example of the slinger.
  • FIG. 6B is a sectional view taken along line VI-VI of FIG. 6A.
  • the slinger 50b is an annular shape having a through hole 66b corresponding to a second through hole through which the rotating shaft 26 is closely inserted.
  • the slinger 50b has a first portion 80 that constitutes the peripheral edge portion of the through hole 66b, and a second portion 82 that is located radially outward from the first portion 80.
  • the axial thickness T2 of the second portion 82 is smaller than the axial thickness T1 of the first portion 80.
  • the slinger 50b is mainly different from the slinger 50 in that the axial thickness T2 of the second portion 82 is smaller than the axial thickness T1 of the first portion 80.
  • the gap between the through hole 62 of the field core 42 and the rotating shaft 26 overlaps with the first portion 80 when viewed from the axial direction. It may overlap with the second part, or may overlap with both the first part 80 and the second part 82.
  • the through hole 66b corresponds to the second through hole.
  • the slinger 50b is located radially outward from the first portion 80 constituting the peripheral edge portion of the through hole 66b and the first portion 80. It has two portions 82, and the axial thickness T2 of the second portion 82 is smaller than the axial thickness T1 of the first portion 80.
  • the axial thickness T2 of the second portion 82 is made smaller than the axial thickness T1 of the first portion 80, it is possible to suppress a decrease in the contact area between the rotating shaft 26 and the slinger 50b. However, the weight of the slinger 50b can be reduced.
  • FIG. 7A is a front view showing the slinger 50c, which is still another example of the slinger.
  • FIG. 7B is a sectional view taken along line VII-VII of FIG. 7A.
  • the slinger 50c is mainly different from the slinger 50 in that it has a first groove portion 84 and a plurality of second groove portions 86a, 86b, 86c, 86d.
  • the slinger 50c is an annular shape having a through hole 66c through which the rotating shaft 26 is closely inserted.
  • the slinger 50c has a first groove portion 84 formed on the main surface 67c of the slinger 50c and a plurality of second groove portions 86a, 86b, 86c, 86d.
  • the slinger 50c is attached to the rotating shaft 26 so that the main surface 67c faces the second bearing 34.
  • first groove portion 84 and the plurality of second groove portions 86a, 86b, 86c, 86d are provided on the main surface 67c of the slinger 50c on the second bearing 34 side in a state where the slinger 50c is attached to the rotating shaft 26.
  • the first groove portion 84 is provided along the outer peripheral portion of the through hole 66c and communicates with the through hole 66c.
  • the first groove portion 84 extends in the circumferential direction and is annular in a state where the slinger 50c is attached to the rotating shaft 26.
  • the plurality of second groove portions 86a, 86b, 86c, 86d are provided at equal intervals in the circumferential direction in a state where the slinger 50c is attached to the rotating shaft 26. Further, in this state, each of the plurality of second groove portions 86a, 86b, 86c, 86d is connected to the first groove portion 84 and extends radially outward from the first groove portion 84.
  • the slinger 50c has second groove portions 86a to 86d provided on the main surface 67c on the second bearing 34 side of the slinger 50c.
  • the second groove portions 86a to 86d extend in the radial direction.
  • the oil leaked from the second bearing 34 can be easily guided outward in the radial direction through the second groove portion 86a. Therefore, it is possible to further prevent the oil from entering the gap between the through hole 62 and the rotating shaft 26. As a result, it is possible to further suppress the oil leaking from the second bearing 34 from adhering to the brake disc 38.
  • FIG. 8 is a cross-sectional view showing the vicinity of the brake portion 14a of the motor with brake 10a according to another embodiment.
  • the brake disc 38a may not rotate together with the rotating shaft 26. Note that FIG. 8 shows a state in which the armature 46a is pressing the brake disc 38a.
  • the motor 10a with a brake includes a brake portion 14a different from the brake portion 14.
  • the brake portion 14a includes a second case 32, a second bearing 34, a hub 36a, a brake disc 38a, a field core 42a, a coil 44, an armature 46a, a spring 48a, a slinger 50, and a suction member 54. And brakes the rotation of the rotating shaft 26.
  • the hub 36a, the brake disc 38a, the field core 42a, the coil 44, the armature 46a, and the spring 48a are members constituting a braking mechanism for braking the rotation of the rotating shaft 26.
  • the second case 32, the second bearing 34, the coil 44, the slinger 50, and the suction member 54 detailed description thereof will be omitted here by referring to the description in the above-described embodiment.
  • the hub 36a is a so-called armature hub, and is provided on the side opposite to the field core 42a with respect to the brake disc 38a.
  • the hub 36a has a cylindrical portion 88 and a disk portion 90.
  • the cylindrical portion 88 has a cylindrical shape.
  • a rotating shaft 26 is inserted in close contact with the inside of the cylindrical portion 88.
  • the disk portion 90 projects radially outward from one end of the cylindrical portion 88 in the axial direction.
  • the disk portion 90 has a plate shape having a main surface intersecting the axial direction.
  • the hub 36a is attached to the rotating shaft 26 and rotates together with the rotating shaft 26.
  • a spring 48a is connected to the hub 36a. Specifically, the spring 48a is connected to the main surface of the disk portion 90 on the brake disc side.
  • the hub 36a is made of mild steel or the like.
  • the brake disc 38a is provided at a position different from that of the first bearing 28 and the second bearing 34 in the axial direction. Specifically, the brake disc 38a is provided on the side opposite to the first bearing 28 with respect to the rotor 24. Further, the brake disc 38a is provided on the rotor 24 side of the second bearing 34.
  • the brake disc 38a is annular.
  • the brake disc 38a has a rotating shaft 26 inserted inside the brake disc 38a.
  • the brake disc 38a is attached to the end surface of the field core 42a opposite to the second bearing 34.
  • the brake disc 38a does not rotate together with the rotating shaft 26.
  • the brake disc 38a has a plate shape having a main surface intersecting the axial direction.
  • the brake disc 38a is a friction plate (brake lining) and is made of resin or the like.
  • the field core 42a is located on the second bearing 34 side of the brake disc 38a in the axial direction.
  • the field core 42a is provided between the brake disc 38a and the second bearing 34.
  • the field core 42a is an annular shape having a through hole 62a through which the rotating shaft 26 is rotatably inserted.
  • the field core 42a is attached to the second case 32.
  • the field core 42a extends in the axial direction.
  • the field core 42a has a cylindrical shape. In the radial direction, a gap is formed between the inner peripheral surface 63a of the through hole 62a and the outer peripheral surface 27 of the rotating shaft 26, and the field core 42a does not rotate together with the rotating shaft 26.
  • the field core 42a is made of mild steel or the like.
  • the field core 42a corresponds to the intermediate member
  • the through hole 62a corresponds to the first through hole.
  • the armature 46a is provided between the hub 36a and the brake disc 38a in the axial direction.
  • the armature 46a is an annular shape having a through hole 64a through which the rotating shaft 26 is inserted, and is connected to the hub 36a via a spring 48a.
  • the spring 48a is an annular leaf spring that can expand and contract in the axial direction.
  • the armature 46a is axially movable with respect to the hub 48a.
  • the spring 48a is a constant load shaped leaf spring.
  • the spring connecting the hub 36a and the armature 46a may not be a leaf spring, but may be a coil spring or the like.
  • the armature 46a has a plate shape having a main surface intersecting the axial direction, and faces the main surface of the brake disc 38a in the axial direction.
  • the armature 46a rotates about the axis A as the center of rotation together with the rotation shaft 26, the hub 36a, and the spring 48a.
  • the armature 46a is made of mild steel or the like.
  • the armature 46a When power is not supplied to the coil 44, the armature 46a is attracted to the hub 36a side by the spring 48a, a gap is formed between the armature 46a and the brake disc 38a, and the armature 46a presses the brake disc 38a. (See the two-point chain line in FIG. 8), the brake portion 14a does not brake the rotation of the rotating shaft 26.
  • the armature 46a is on the brake disk 38a side (in a state where the electric power is supplied to the coil 44).
  • the armature 46a presses the brake disc 38a while being attracted to the field core 42a side). Since the brake disc 38a does not rotate together with the rotating shaft 26, the rotation of the rotating shaft 26 is damped by the armature 46a pressing the brake disc 38a.
  • the motor 10a with a brake according to another embodiment has been described above.
  • the motor 10a with a brake includes a coil 44 provided inside a field core 42a corresponding to an intermediate member, a hub 36a provided on the side opposite to the field core 42a with respect to the brake disc 38a, and the hub 36a.
  • a spring 48a connected to the hub 36a and an armature 46a are further provided.
  • the armature 46a is provided between the brake disc 38a and the hub 36a and is connected to the hub 36a via a spring 48a.
  • the brake disc 38a is attached to the field core 42a, does not rotate with the rotating shaft 26, and the armature 46a is pulled toward the hub 36a by the spring 48a and does not press the brake disc 38a in a state where power is not supplied to the coil 44. .. While the electric power is being supplied to the coil 44, the armature 46a is attracted to the brake disc 38a side and presses the brake disc 38a.
  • the rotation of the rotating shaft 26 can be braked by using the brake disc 38a, the field core 42a, the armature 46a, and the like. Further, it is possible to prevent the oil leaked from the second bearing 34 from adhering to the brake disc 38a through the gap between the field core 42a and the rotating shaft 26.
  • the slinger 50 is annular
  • the present invention is not limited to this.
  • the slinger has a substantially C-shape in a cross section orthogonal to the axial direction, and may be attached to the rotating shaft 26 by sandwiching the rotating shaft 26.
  • the slinger 50 is attached to the rotary shaft 26 by press-fitting the rotary shaft 26 into the through hole 66 of the slinger 50 has been described, but the present invention is not limited to this.
  • the slinger may be attached to the rotating shaft 26 by an adhesive or the like.
  • the slinger 50b shown in FIG. 6 may be provided with a plurality of second groove portions 86a, 86b, 86c, 86d of the slinger 50c shown in FIG. 7.
  • the motor with a brake according to the present disclosure can be used for various motors such as a motor for driving a joint portion of an arm robot.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Braking Arrangements (AREA)

Abstract

La présente invention concerne un moteur équipé d'un frein qui comprend : un arbre rotatif auquel est fixé un rotor ; un palier qui supporte de manière rotative l'arbre rotatif ; un disque de frein disposé à une position différente de la position du palier dans la direction axiale de l'arbre rotatif ; un élément intermédiaire qui a un trou traversant dans lequel l'arbre rotatif est inséré de manière rotative, est disposé entre le palier et le disque de frein, et est destiné à freiner la rotation de l'arbre rotatif ; et une bague d'étanchéité disposée entre le palier et l'élément intermédiaire, la bague d'étanchéité étant fixée à l'arbre rotatif, tourne conjointement avec l'arbre rotatif, et fait saillie dans une direction radiale de l'arbre rotatif à partir d'une surface circonférentielle externe de l'arbre rotatif.
PCT/JP2021/019141 2020-06-19 2021-05-20 Moteur équipé d'un frein WO2021256156A1 (fr)

Priority Applications (2)

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JP2022532408A JPWO2021256156A1 (fr) 2020-06-19 2021-05-20
CN202180041811.4A CN115699535A (zh) 2020-06-19 2021-05-20 带制动器的马达

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JP2020-106225 2020-06-19

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01236189A (ja) * 1988-03-14 1989-09-21 Hitachi Ltd エレベータ巻上機
JPH0416487A (ja) * 1990-05-09 1992-01-21 Mitsubishi Electric Corp エレベーター用巻上機の封油装置
JPH06262565A (ja) * 1993-03-11 1994-09-20 Hitachi Ltd ブレーキ装置及びマニピュレータ装置
JP2000304075A (ja) * 1999-04-22 2000-10-31 Toshiba Corp クラッチ式ディスクブレーキ
JP2011093669A (ja) * 2009-10-30 2011-05-12 Hitachi Ltd エレベータ装置及び巻上機
WO2017090080A1 (fr) * 2015-11-24 2017-06-01 三菱電機株式会社 Machine tournante et machine de levage d'ascenseur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01236189A (ja) * 1988-03-14 1989-09-21 Hitachi Ltd エレベータ巻上機
JPH0416487A (ja) * 1990-05-09 1992-01-21 Mitsubishi Electric Corp エレベーター用巻上機の封油装置
JPH06262565A (ja) * 1993-03-11 1994-09-20 Hitachi Ltd ブレーキ装置及びマニピュレータ装置
JP2000304075A (ja) * 1999-04-22 2000-10-31 Toshiba Corp クラッチ式ディスクブレーキ
JP2011093669A (ja) * 2009-10-30 2011-05-12 Hitachi Ltd エレベータ装置及び巻上機
WO2017090080A1 (fr) * 2015-11-24 2017-06-01 三菱電機株式会社 Machine tournante et machine de levage d'ascenseur

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CN115699535A (zh) 2023-02-03

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