WO2022244733A1 - アキシャルギャップモータ、及びアキシャルギャップモータの製造方法 - Google Patents

アキシャルギャップモータ、及びアキシャルギャップモータの製造方法 Download PDF

Info

Publication number
WO2022244733A1
WO2022244733A1 PCT/JP2022/020391 JP2022020391W WO2022244733A1 WO 2022244733 A1 WO2022244733 A1 WO 2022244733A1 JP 2022020391 W JP2022020391 W JP 2022020391W WO 2022244733 A1 WO2022244733 A1 WO 2022244733A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
shaft
rotor
axial gap
gap motor
Prior art date
Application number
PCT/JP2022/020391
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
勇太 榎園
大地 東
達哉 齋藤
Original Assignee
住友電気工業株式会社
住友電工焼結合金株式会社
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 住友電気工業株式会社, 住友電工焼結合金株式会社 filed Critical 住友電気工業株式会社
Priority to JP2023522658A priority Critical patent/JPWO2022244733A1/ja
Publication of WO2022244733A1 publication Critical patent/WO2022244733A1/ja

Links

Images

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K21/00—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets
    • H02K21/12—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets
    • H02K21/24—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets with magnets axially facing the armatures, e.g. hub-type cycle dynamos
    • 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
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings

Definitions

  • the present disclosure relates to an axial gap motor and a method of manufacturing an axial gap motor.
  • This application claims priority based on Japanese Patent Application No. 2021-086466 filed in Japan on May 21, 2021, and incorporates all the contents described in the Japanese application.
  • the axial gap type rotary electric machine of Patent Document 1 includes a case, a stator, a rotor, a shaft, and a bearing.
  • the case includes a cylindrical peripheral wall portion and a pair of disk-shaped plates. A pair of plates are attached to both ends of the peripheral wall. A through hole is formed in the center of the pair of plates. A shaft is provided in the through hole.
  • the stator and rotor are arranged to face each other in the axial direction of the shaft within the case.
  • the stator is arranged on the plate.
  • the rotor is provided with a gap from the stator.
  • the shaft is the axis of rotation of the rotor.
  • the bearing rotatably supports the shaft.
  • the axial gap motor of the present disclosure is a rotor; a stator arranged with a gap of design length in the rotational axis direction of the rotor; a shaft that is the rotation axis of the rotor; a first bearing rotatably supporting the shaft; a case having a first plane on which the stator rests; an adjustment member supporting the first bearing; the adjustment member has a thread threadedly coupled to the case; The first bearing moves in the axial direction of the shaft as the adjustment member rotates.
  • the manufacturing method of the axial gap motor of the present disclosure includes: preparing parts for an axial gap motor; comprising a step of assembling the parts,
  • the parts are a rotor; a stator; a shaft that is the rotation axis of the rotor; a bearing that rotatably supports the shaft; a case having a first plane on which the stator rests; an adjustment member that is screwed to the case to support the bearing;
  • the stator is a stator core having a yoke and a plurality of teeth; a coil arranged on each of the plurality of teeth,
  • the length of the gap between the rotor and the stator is set as a design length by rotating the adjustment member with respect to the case to move the shaft up and down via the bearing, The amount of rotation of the adjustment member is determined based on the induced voltage value generated in the coil.
  • FIG. 1 is a schematic cross-sectional view showing an outline of an axial gap motor according to Embodiment 1.
  • FIG. FIG. 2 is a schematic cross-sectional view showing an enlarged area A of FIG.
  • FIG. 3 is a cross-sectional schematic diagram showing another example of the region A in FIG. 1 in an enlarged manner.
  • FIG. 4 is a schematic cross-sectional view showing an enlarged region B in FIG.
  • FIG. 5 is a schematic cross-sectional view showing an enlarged region C of FIGS. 2 and 3.
  • FIG. 6 is a schematic cross-sectional view for explaining the method of manufacturing the axial gap motor according to the first embodiment.
  • FIG. 7 is a diagram showing a graph showing changes in the induced voltage value.
  • FIG. 1 is a schematic cross-sectional view showing an outline of an axial gap motor according to Embodiment 1.
  • FIG. 2 is a schematic cross-sectional view showing an enlarged area A of FIG.
  • FIG. 3 is a cross-sectional schematic diagram
  • FIG. 8 is a graph showing changes in induced voltage values.
  • FIG. 9 is a schematic cross-sectional view illustrating a method of manufacturing an axial gap motor according to a modification.
  • FIG. 10 is a schematic plan view showing an outline of a circuit board.
  • FIG. 11 is a cross-sectional schematic diagram showing an enlarged part of the axial gap motor according to the second embodiment.
  • One of the purposes of the present disclosure is to provide an axial gap motor with excellent assembly accuracy.
  • Another object of the present disclosure is to provide a method of manufacturing an axial gap motor that is excellent in manufacturability of the axial gap motor.
  • the axial gap motor of the present disclosure has excellent assembly accuracy.
  • the manufacturing method of the axial gap motor of the present disclosure is excellent in manufacturability of the axial gap motor of the present disclosure.
  • Axial gap motors are manufactured through, for example, two assembly steps of temporary assembly and final assembly of axial gap motor parts.
  • the reason for temporarily assembling the parts is that it is difficult to make the length of the gap between the stator and the rotor the design length if the parts are assembled only once.
  • the design length of the gap is a target value of the designed gap length determined based on the specifications of the axial gap motor. Therefore, the length of the gap of the axial gap motor manufactured by temporary assembly is measured. A difference between the measured length of the gap obtained by measurement and the design length of the gap is obtained. After obtaining the measured length of the gap, disassemble the axial gap motor.
  • the parts are assembled.
  • a shim is placed between the bearing and the plate.
  • the placement of the shim moves the bearing away from the plate by the thickness of the shim.
  • the shaft supported by the bearings is displaced in the axial direction of the shaft.
  • Misalignment of the shaft separates the rotor from the stator.
  • the separation of the rotor causes the length of the gap to be longer than the measured length. That is, the length of the gap is longer than the measured length by the thickness of the shim. Since the thickness of the shim is the same as the above difference, the length of the gap can be the designed length.
  • the parts are assembled twice, so the manufacturing work becomes complicated. Moreover, in the manufacturing method described above, the number of parts increases by the number of shims. Also, the use of shims may increase mechanical losses due to increased bearing preload.
  • the inventors diligently studied a method of manufacturing an axial gap motor that does not use shims. As a result, the inventors have developed a manufacturing method that enables the length of the gap between the stator and rotor to be substantially the same as the design length in a single assembly of the parts.
  • the embodiments of the present disclosure are listed and described.
  • An axial gap motor includes a rotor; a stator arranged with a gap of design length in the rotational axis direction of the rotor; a shaft that is the rotation axis of the rotor; a first bearing rotatably supporting the shaft; a case having a first plane on which the stator rests; an adjustment member supporting the first bearing; the adjustment member has a thread threadedly coupled to the case; The first bearing moves in the axial direction of the shaft as the adjustment member rotates.
  • the above axial gap motor has excellent assembly accuracy.
  • Rotating the adjustment member with respect to the case during the manufacturing process causes the first bearing to move in the axial direction of the shaft. Since the shaft is supported by the first bearing, movement of the first bearing in the axial direction causes the shaft to move in the axial direction. Since the shaft is the axis of rotation of the rotor, movement of the shaft in the axial direction causes the rotor to move in the axial direction. That is, the rotor can be easily moved to a position where the length of the gap is the designed length. Since the adjusting member and the case are screwed together, the rotor does not move in the axial direction unless the adjusting member is rotated. Therefore, the rotor is positioned at a position where the length of the gap is the designed length.
  • the above axial gap motor does not have shims, so it is possible to suppress an increase in the number of parts. Moreover, since the axial gap motor can suppress an increase in the preload of the first bearing, an increase in mechanical loss can be suppressed.
  • a pitch of the thread of the adjustment member may be 2.5 mm or less.
  • the above axial gap motor is excellent in assembly accuracy because the gap length can be finely adjusted by the adjusting member.
  • a second bearing that rotatably supports the shaft and faces the first bearing with the rotor interposed therebetween; and an elastic member that presses the second bearing toward the first bearing.
  • the first bearing is a radial bearing having an inner race and an outer race;
  • the adjustment member may support the outer race without contacting the inner race.
  • the above axial gap type motor can suppress an increase in mechanical loss. This is because friction does not increase because the adjustment member does not contact the inner race.
  • a washer may be provided between the outer race and the adjustment member.
  • the washer is arranged between the outer race and the adjusting member, so that the bearing can be easily supported by the adjusting member.
  • the adjustment member can be made of a solid body. This is because the contact between the adjusting member and the inner race can be prevented by the washer even if the adjusting member is made of a solid body. Therefore, the axial gap motor can suppress an increase in mechanical loss even if the adjusting member is made of a solid body.
  • the stator is a stator core having a yoke configured in the shape of an annular plate and a plurality of teeth protruding from the yoke; a coil arranged on each of the plurality of teeth,
  • the stator core may be fixed to the first plane.
  • the above axial gap motor has excellent assembly accuracy for double-stator/single-rotor or single-stator/single-rotor motors.
  • the stator core may be composed of a compacted body.
  • the above axial gap motor is excellent in assembly accuracy even when it is equipped with a stator core made of a compacted body with lower dimensional accuracy than a stator core made of electromagnetic steel sheets.
  • the number of stators and the number of rotors may be one each.
  • the above axial gap motor is a single stator/single rotor type.
  • the above axial gap motor is excellent in assembly accuracy.
  • a method for manufacturing an axial gap motor includes: preparing parts for an axial gap motor; comprising a step of assembling the parts,
  • the parts are a rotor; a stator; a shaft that is the rotation axis of the rotor; a bearing that rotatably supports the shaft; a case having a first plane on which the stator rests; an adjustment member that is screwed to the case to support the bearing;
  • the stator is a stator core having a yoke and a plurality of teeth; a coil arranged on each of the plurality of teeth,
  • the length of the gap between the rotor and the stator is set as a design length by rotating the adjustment member with respect to the case to move the shaft up and down via the bearing, The amount of rotation of the adjustment member is determined based on the induced voltage value generated in the coil.
  • the position of the rotor can be adjusted because the shaft is moved up and down by the adjusting member. Therefore, the axial gap motor manufacturing method can set the length of the gap to the design length by assembling the parts only once. Therefore, the axial gap motor manufacturing method described above is excellent in the productivity of the axial gap motor with excellent assembly accuracy without using shims.
  • FIG. 1 is a sectional view of the axial gap motor 1 taken along a plane parallel to the axial direction of the shaft 4.
  • FIG. 1 illustrates a single-stator/single-rotor axial gap motor 1 .
  • the single-stator/single-rotor axial gap motor 1 is a motor having one stator 2 and one rotor 3 .
  • An axial gap motor 1 is a motor in which a stator 2 and a rotor 3 face each other with a gap in the axial direction of a shaft 4 .
  • the axial gap motor 1 of this embodiment includes a stator 2, a rotor 3, a shaft 4, a first bearing 51, and a case 7.
  • the axial gap motor 1 has a stator 2 , a rotor 3 and a shaft 4 housed in a case 7 .
  • the stator 2 and the rotor 3 in the case 7 face each other with a gap in the axial direction of the shaft 4 .
  • the length of this gap along the axial direction satisfies the design length G1.
  • the design length G1 is a target value of the designed gap length determined based on the specifications of the axial gap motor 1 .
  • the design length G1 has a certain allowable width.
  • One of the features of the axial gap motor 1 of this embodiment is that it has an adjusting member 6 screwed to the case 7 .
  • the stator 2 is arranged on the first plane 71f of the case 7, as shown in FIG.
  • the stator 2 includes a stator core 21 and a plurality of coils 25, as shown in FIG.
  • the stator core 21 includes an annular plate-shaped yoke 22 and a plurality of columnar teeth 23 .
  • the yoke 22 magnetically couples adjacent teeth 23 among the teeth 23 arranged in the circumferential direction of the yoke 22 .
  • the yoke 22 has a planar first surface 22f, a planar second surface 22s, an outer peripheral surface, and an inner peripheral surface.
  • the first surface 22f and the second surface 22s are surfaces connecting the outer peripheral surface and the inner peripheral surface.
  • the first surface 22f is in contact with the first plane 71f.
  • the second surface 22 s is a surface connected to the side surface of the tooth 23 .
  • the teeth 23 are provided with coils 25 as shown in FIG.
  • the number of teeth 23 is plural.
  • Each tooth 23 is arranged at predetermined intervals in the circumferential direction of the yoke 22 .
  • Each tooth 23 protrudes so as to be orthogonal to the second surface 22s of the yoke 22 shown in FIG.
  • Each of the teeth 23 and the yoke 22 of the present embodiment are configured as an integrated compacted body.
  • Each tooth 23 has the same shape and size.
  • the shape of each tooth 23 is prismatic or cylindrical.
  • Each tooth 23 has a side surface and an end surface 23a.
  • the side surface is a surface connected to the second surface 22s of the yoke 22 .
  • the end surface 23a is a surface connected to the side surface.
  • the end surface 23a faces magnets 35 of the rotor 3, which will be described later.
  • the stator core 21 has a hole as shown in FIG. A fastening member 91 is provided in this hole.
  • the fastening member 91 fixes the stator core 21 to the first plane 71f.
  • the fastening member 91 suppresses misalignment between the stator 2 and the first plane 71f.
  • An example of the fastening member 91 is a screw or bolt.
  • the hole is formed halfway through the tooth 23 from the first surface 22f.
  • the number of holes may be less than the number of teeth 23 or may be the same as the number of teeth 23 .
  • a compacted body that constitutes the stator core 21 is composed of an aggregate of a plurality of coated particles 24 shown in FIG. Coated particles 24 have metal particles 241 and insulating coatings 242 .
  • the metal particles 241 are made of a soft magnetic material.
  • Soft magnetic materials are pure iron or iron-based alloys.
  • Pure iron has a purity of 99% or more. That is, pure iron has an iron (Fe) content of 99% by mass or more.
  • the saturation magnetic flux density of pure iron is higher than that of iron-based alloys. Therefore, if the metal particles 241 of the powder compact are made of pure iron, the saturation magnetic flux density of the compact is likely to be improved. Also, the formability of pure iron is superior to iron-based alloys. Therefore, if the metal particles 241 of the compacted body are made of pure iron, the relative density of the compacted body tends to increase.
  • An iron-based alloy is one that contains additional elements, with the balance being Fe and unavoidable impurities. Iron-based alloys contain the most Fe.
  • the iron-based alloy is, for example, at least selected from the group consisting of Fe—Si (silicon) alloys, Fe—Al (aluminum) alloys, Fe—Si—Al alloys, and Fe—Ni (nickel) alloys. It is one kind.
  • Fe—Si based alloys is silicon steel.
  • An example of the Fe--Si--Al alloy is sendust.
  • An example of the Fe—Ni alloy is permalloy.
  • the electrical resistance of iron-based alloys is greater than that of pure iron.
  • the iron-based alloy easily reduces iron loss such as eddy current loss. Therefore, if the metal particles 241 of the powder compact are made of an iron-based alloy, the loss of the powder compact can be easily reduced.
  • the powder compact may contain both metal particles 241 composed of pure iron and metal particles 241 composed of an iron-based alloy.
  • the insulating coating 242 covers the metal particles 241 .
  • the insulating coating 242 can reduce iron loss such as eddy current loss.
  • a powder compact provided with the insulating coating 242 tends to reduce loss.
  • the material of the insulating coating 242 is, for example, oxide. Examples of oxides are phosphates, silica, magnesium oxide or aluminum oxide. Phosphate has excellent adhesion to the metal particles 241 and also has excellent deformability. Therefore, if the insulating coating 242 is made of phosphate, the insulating coating 242 is likely to deform following the deformation of the metal particles 241 in the process of producing the compact. Therefore, the insulating coating 242 is less likely to be damaged. Since the insulating coating 242 is less likely to be damaged, the loss of the powder compact can be easily reduced.
  • the relative density of the compact may be 90% or more.
  • a green compact having a relative density of 90% or more can easily improve the saturation magnetic flux density.
  • a green compact having a relative density of 90% or more is likely to improve mechanical properties such as strength.
  • the relative density may be 93% or higher, or even 95% or higher.
  • the relative density may be 99% or less.
  • a compacted body having a relative density of 99% tends to have a stable induced voltage value measured in the manufacturing method described later.
  • “Relative density of the compact” refers to the ratio (%) of the actual density of the compact to the true density of the compact. That is, the relative density of the compact is obtained by [(actual density of compact/true density of compact) ⁇ 100].
  • the actual density of the green compact is obtained by immersing the green compact in oil and impregnating the green compact with oil, [oil-impregnated density x (mass of green compact before oil impregnation / pressure after oil impregnation (Mass of powder compact)].
  • the oil-impregnated density is (mass of compacted product after impregnated with oil/volume of compacted product after impregnated with oil).
  • the actual density of the green compact can be determined by (mass of green compact before oil impregnation/volume of green compact after oil impregnation).
  • the volume of the compacted body after impregnation with oil can typically be measured by a liquid displacement method.
  • the true density of the powder compact is the theoretical density when voids are not included inside.
  • Each coil 25 has a tubular portion.
  • the cylindrical portion is configured by spirally winding a wire.
  • the coil 25 of this embodiment is an edgewise wound coil.
  • a covered rectangular wire is used for the winding of the coil 25 .
  • Each coil 25 is arranged on the outer circumference of the side surface of the tooth 23 .
  • the cross-sectional shape of the cylindrical portion of each coil 25 is, for example, a shape corresponding to the cross-sectional shape of the teeth 23 .
  • the axial length of the cylindrical portion is slightly shorter than the length of the teeth 23 .
  • FIG. 1 only the cylindrical portion is shown, and the illustration of both end portions of the winding is omitted.
  • the rotor 3 is provided with a gap from the stator 2 .
  • the rotor 3 comprises a rotor body 31 and at least one magnet 35 .
  • the rotor body 31 is rotatably supported by the shaft 4 with respect to the case 7 .
  • the rotor body 31 is an annular member.
  • the rotor body 31 is provided with a through hole in the center.
  • a third shaft portion 43 of the shaft 4, which will be described later, is provided in this through hole.
  • the rotor main body 31 and the shaft 4 are combined by press-fitting the shaft 4 into the through hole. The press-fitting tends to reduce the deflection of the rotor 3 .
  • the position of the rotor body 31 along the axial direction of the shaft 4 is determined by the rotor body 31 coming into contact with a second end surface 42s of the second shaft portion 42, which will be described later.
  • the rotor body 31 has a first surface 31f, a second surface 31s, an inner peripheral surface and an outer peripheral surface.
  • the first surface 31f and the second surface 31s connect the inner peripheral surface and the outer peripheral surface.
  • the first surface 31f is a surface facing the stator 2 .
  • the second surface 31s is a surface facing the second bearing 55 shown in FIG. The second bearing 55 will be described later.
  • a concave portion 32 is provided on the first surface 31f of the present embodiment.
  • the recess 32 opens toward the stator 2 .
  • a magnet 35 is fixed to the bottom surface 32 a of the recess 32 .
  • the inner peripheral surface of the rotor body 31 is in contact with the third shaft portion 43 of the shaft 4 .
  • the outer peripheral surface of the rotor body 31 is not in contact with the inner peripheral surface of the peripheral wall portion 73 of the case 7, as shown in FIG. A space is provided between the outer peripheral surface of the rotor body 31 and the inner peripheral surface of the peripheral wall portion 73 of the case 7 .
  • the number of magnets 35 may be one or plural. If the number of magnets 35 is one, compared with the case where the number of magnets 35 is plural, the number of parts is small and the rotor 3 is easy to manufacture. Therefore, it is easy to improve the manufacturability of the axial gap motor 1 . Moreover, it is easy to manufacture the axial gap motor 1 with excellent assembly accuracy.
  • the shape of the magnets 35 is annular.
  • One sheet of magnet 35 has S poles and N poles alternately arranged in the circumferential direction.
  • the specific number of magnets 35 is the same as the number of teeth 23 .
  • the plurality of magnets 35 are arranged at regular intervals in the circumferential direction of the rotor body 31 .
  • the shape of each magnet 35 is, for example, a flat plate shape.
  • the planar shape of each magnet 35 is the same as the planar shape of the end face 23a of the tooth 23, for example.
  • Each magnet 35 is magnetized in the axial direction of the rotating shaft of the rotor 3 .
  • the magnetization directions of the magnets 35 adjacent to each other in the circumferential direction of the rotor body 31 are opposite to each other.
  • the magnet 35 repeats attraction and repulsion with respect to each tooth 23 by the rotating magnetic field generated by the stator 2 , thereby rotating the rotor 3 .
  • the magnet 35 is a permanent magnet.
  • permanent magnets are ferrite magnets, neodymium magnets, samarium-cobalt magnets, or bonded magnets.
  • neodymium magnets and samarium-cobalt magnets have strong magnetic forces.
  • a shaft 4 is a rotating shaft of the rotor 3 .
  • the shaft 4 is composed of a solid round bar-shaped body.
  • the shaft 4 has a plurality of shaft portions with different outer diameters, as shown in FIG.
  • the plurality of shaft portions are configured integrally.
  • the shaft 4 of the present embodiment has a first shaft portion 41, a second shaft portion 42, a third shaft portion 43, and a fourth shaft portion in order from the first plate portion 71 of the case 7 toward the second plate portion 72. 44 and a fifth shaft portion 45 .
  • the first shaft portion 41 is provided inside the first bearing 51 as shown in FIG.
  • the outer peripheral surface of the first shaft portion 41 is in contact with the inner peripheral surface of the inner race 52 of the first bearing 51, as shown in FIG.
  • the second shaft portion 42 has a diameter larger than that of the first shaft portion 41, as shown in FIG.
  • the second shaft portion 42 as shown in FIG. 2, has a first end surface 42f and a second end surface 42s.
  • the first end surface 42 f contacts the first end surface 52 f of the inner race 52 .
  • the first end face 42f is not in contact with the outer race 53 of the first bearing 51.
  • the second end surface 42s is in contact with the first surface 31f.
  • the third shaft portion 43 is provided in the through hole of the rotor body 31, as shown in FIG.
  • the outer peripheral surface of the third shaft portion 43 is in contact with the inner peripheral surface of the rotor body 31 as shown in FIG.
  • the third shaft portion 43 has a diameter smaller than that of the second shaft portion 42, as shown in FIG.
  • the third shaft portion 43 has an end face 43a, as shown in FIG.
  • the end face 43 a contacts the first end face of the inner race 56 of the second bearing 55 .
  • the fourth shaft portion 44 is provided inside the second bearing 55 as shown in FIG.
  • the outer peripheral surface of the fourth shaft portion 44 is in contact with the inner peripheral surface of the inner race 56 .
  • the fourth shaft portion 44 has a smaller diameter than the diameter of the third shaft portion 43 .
  • the fifth shaft portion 45 is provided inside the through hole 72h. 72 h of through-holes are provided in the 2nd plate part 72 mentioned later. The outer peripheral surface of the fifth shaft portion 45 is not in contact with the inner peripheral surface of the second plate portion 72 .
  • the fifth shaft portion 45 has a smaller diameter than the diameter of the fourth shaft portion 44 .
  • the first bearing 51 and the second bearing 55 rotatably support the shaft 4 .
  • the first bearing 51 is attached to the first shaft portion 41 .
  • the second bearing 55 is attached to the fourth shaft portion 44 .
  • the configurations of the first bearing 51 and the second bearing 55 may be the same configuration as each other, or may be different configurations.
  • the first bearing 51 is a radial bearing having an inner race 52 and an outer race 53, as shown in FIGS.
  • the radial bearing of this embodiment is a ball bearing in which balls 54 are arranged between an inner race 52 and an outer race 53 .
  • the inner peripheral surface of the inner race 52 is in contact with the outer peripheral surface of the first shaft portion 41 .
  • the outer peripheral surface of the outer race 53 is in contact with a first projecting portion 71a, which will be described later.
  • the inner race 52 has a first end face 52f and a second end face 52s.
  • the outer race 53 has a first end face 53f and a second end face 53s.
  • the first end surface 52f is in contact with the first end surface 42f.
  • the second end face 52s is not in contact with the case 7 and the adjusting member 6, which will be described later.
  • the second end face 52s is in contact with a fixing member (not shown).
  • This fixing member mechanically fixes the first bearing 51 and the first shaft portion 41 .
  • An example of this fixing member is a retaining ring or a shaft nut. When a shaft nut is used as the fixing member, it is preferable to form a threaded portion on the outer peripheral surface of the first shaft portion 41 . This fixing member may not be used. In that case, the inner race 52 and the first shaft portion 41 are fixed by being fitted together.
  • the first end surface 53f is not in contact with the shaft 4.
  • the second end surface 53 s is in contact with the adjusting member 6
  • FIG. 2 shows an example in which the first end face 52f and the first end face 53f are not displaced along the axial direction of the first bearing 51.
  • FIG. 3 shows an example in which the first end face 52f and the first end face 53f are shifted along the axial direction of the first bearing 51. As shown in FIG. The first end surface 52 f and the first end surface 53 f may be shifted along the axial direction of the first bearing 51 .
  • the deviation between the first end face 52f and the first end face 53f is caused by the load acting on the inner race 52 due to the weight of the shaft 4 and the rotor 3 and the load acting on the inner race 52 due to the attractive force of the magnet 35 to the stator 2. . Further, the deviation is further caused by the load acting on the inner race 52 due to the weight of the second bearing 55, and the load acting on the inner race 52 due to the pressing force of the elastic member 8 pressing the second bearing 55 toward the first bearing 51. caused by
  • a load due to the weight of the shaft 4 and the rotor 3 and a load due to the attraction of the magnet 35 to the stator 2 are mainly applied to the inner race 52 .
  • At least one of the load due to the weight of the second bearing 55 and the load due to the pressing force of the elastic member 8 pressing the second bearing 55 toward the first bearing 51 acts on the inner race 52 .
  • the first end surface 52f may be displaced from the first end surface 53f.
  • the displacement of the first end surface 52f is greatly affected by the attractive force of the magnet 35. As shown in FIG. That is, the stronger the magnetic force of the magnet 35, the more the first end surface 52f is displaced.
  • the configuration of the second bearing 55 is the same as that of the first bearing 51. That is, the second bearing 55 is a radial bearing having an inner race 56 and an outer race 57, as shown in FIGS.
  • the inner peripheral surface of the inner race 56 is in contact with the outer peripheral surface of the fourth shaft portion 44 .
  • the outer peripheral surface of the outer race 57 is in contact with the inner peripheral surface of the recess 72a.
  • the recess 72 a is provided in the second plate portion 72 .
  • Each of the inner race 56 and the outer race 57 has a first end face and a second end face. A first end surface of the inner race 56 is in contact with the end surface 43a.
  • a second end surface of the inner race 56 is not in contact with the elastic member 8 and the case 7, which will be described later.
  • the second end face of the inner race 56 may be in contact with a fixed member similar to the first bearing 51, or may not be in contact with the fixed member. This is because the outer race 57 is pressed in the direction toward the rotor 3 by the elastic member 8 . A first end face of the outer race 57 is not in contact with the rotor 3 and the shaft 4 . A second end face of the outer race 57 is in contact with the elastic member 8 shown in FIG.
  • At least one of the first bearing 51 and the second bearing 55 may be an angular ball bearing, unlike the present embodiment.
  • the elastic member 8 presses the second bearing 55 toward the rotor 3 .
  • the elastic member 8 facilitates suppressing rattling between the second protruding portion 71b and the adjusting member 6 .
  • the elastic member 8 is arranged between the outer race 57 and the bottom of the recess 72a.
  • An example of the elastic member 8 is a spring washer, a disc spring washer, a corrugated washer, or a rubber O-ring.
  • the case 7 accommodates the stator 2, the rotor 3, a portion of the shaft 4, the first bearing 51, and the second bearing 55 inside.
  • the case 7 includes a first plate portion 71 , a second plate portion 72 and a peripheral wall portion 73 .
  • the peripheral wall portion 73 and the second plate portion 72 of this embodiment are integrally formed.
  • the peripheral wall portion 73 and the first plate portion 71 of the present embodiment are configured separately.
  • the peripheral wall portion 73 and the first plate portion 71 may be configured integrally, and the peripheral wall portion 73 and the second plate portion 72 may be configured separately.
  • the peripheral wall portion 73, the first plate portion 71, and the second plate portion 72 may be configured separately.
  • the peripheral wall portion 73 and the first plate portion 71 of this embodiment are fixed to each other by a fastening member 92 .
  • An example of the fastening member 92 is a screw or bolt, like the fastening member 91 .
  • the peripheral wall portion 73 surrounds the outer peripheries of the stator 2 and the rotor 3 .
  • a hole is provided in the end surface of the peripheral wall portion 73 .
  • a fastening member 92 is provided in this hole.
  • the first plate portion 71 has a first plane 71f, a second plane 71s, a first projecting portion 71a, a second projecting portion 71b, a first through hole, a second through hole, and a third through hole.
  • the first plane 71f is provided inside the case 7.
  • the stator 2 is arranged on the first plane 71f.
  • the second plane 71 s is provided outside the case 7 .
  • the second plane 71s is provided on the side opposite to the first plane 71f.
  • the first projecting portion 71 a is provided between the stator 2 and the first bearing 51 .
  • the shape of the first projecting portion 71a is, for example, cylindrical.
  • the first projecting portion 71a is connected to the first plane 71f.
  • the outer peripheral surface of the first projecting portion 71a may or may not be in contact with the inner peripheral surface of the yoke 22 .
  • the inner peripheral surface of the first projecting portion 71a is connected to the inner peripheral surface of the second projecting portion 71b.
  • the inner peripheral surface of the first projecting portion 71 a is in contact with the outer peripheral surface of the outer race 53 .
  • the first protrusion 71 a can be used for positioning the first bearing 51 .
  • the shape of the second protrusion 71b is cylindrical.
  • the outer peripheral surface of the second projecting portion 71b is connected to the second plane 71s.
  • the inner peripheral surface of the second protruding portion 71b is connected to the inner peripheral surface of the first protruding portion 71a.
  • a threaded portion 711 is provided on the inner peripheral surface of the second projecting portion 71b.
  • the adjustment member 6 is screwed to the inner peripheral surface of the second projecting portion 71b.
  • a part of the first shaft portion 41 is provided in the first through hole.
  • a fastening member 91 is provided in the second through hole.
  • the second through hole is provided at a portion of the stator core 21 corresponding to the hole portion.
  • a fastening member 92 is provided in the third through hole.
  • the third through hole is provided at a portion of the peripheral wall portion 73 corresponding to the hole portion.
  • the second plate portion 72 has a recess 72a in the center.
  • a through hole 72h is provided at the bottom of the recess 72a.
  • a fifth shaft portion 45 is provided in the through hole 72h.
  • the inner diameter of the through hole 72 h is larger than the outer diameter of the fifth shaft portion 45 . Therefore, the shaft 4 rotates without contacting the inner peripheral surface of the through hole 72h and the fourth shaft portion 44 .
  • the adjustment member 6 supports the first bearing 51 .
  • the shape of the adjusting member 6 of this embodiment is cylindrical.
  • the inner dimension of the adjusting member 6 of this embodiment is greater than the outer diameter of the inner race 52 and equal to or less than the inner diameter of the outer race 53 .
  • the inner dimension is the diameter of the inscribed circle of the inner peripheral surface of the adjusting member 6 .
  • the adjusting member 6 has a first end surface 61f, a second end surface 61s, an inner peripheral surface and an outer peripheral surface.
  • the first end surface 61f is in direct contact with the second end surface 53s.
  • the first end surface 61f is not in contact with the second end surface 52s. Therefore, an increase in mechanical loss can be suppressed. This is because the adjustment member 6 is not in contact with the inner race 52, so the friction does not increase.
  • the second end surface 61 s is not in contact with the first end surface 61 f and the first plate portion 71 .
  • a threaded portion 611 is provided on the outer peripheral surface of the adjusting member 6 .
  • the outer peripheral surface of the adjusting member 6 is screwed to the inner peripheral surface of the second projecting portion 71b.
  • the pitch of the thread of the threaded portion 611 can be selected as appropriate. The smaller the pitch, the easier it is to finely adjust the gap length with the adjusting member 6 during the manufacturing process.
  • the pitch may be, for example, 2.5 mm or less.
  • the pitch may also be 1.5 mm or less, in particular 1.0 mm or less.
  • the lower pitch limit may be, for example, 0.5 mm. That is, the pitch may be 0.5 mm or more and 2.5 mm or less, further 0.5 mm or more and 1.5 mm or less, especially 0.5 mm or more and 1.0 mm or less.
  • a tool is fitted on the inner peripheral surface of the adjusting member 6 .
  • the tool rotates the adjustment member 6 during the manufacturing process.
  • the inner peripheral surface of the adjusting member 6 is configured in a polygonal shape. If the inner peripheral surface of the adjusting member 6 is configured, for example, in a hexagonal shape, a hexagonal bar spanner can be used as the tool.
  • the axial gap motor 1 of this embodiment has excellent assembly accuracy.
  • the first bearing 51 can be moved in the axial direction of the shaft 4 by rotating the adjusting member 6 with respect to the second projecting portion 71 b during the manufacturing process. Since the first end surface 52f and the first end surface 42f are in contact with each other, the movement of the first bearing 51 in the axial direction allows the shaft 4 to move in the axial direction. Since the second end surface 42s and the first surface 31f are in contact with each other, the movement of the shaft 4 in the axial direction causes the rotor 3 to move in the axial direction. That is, the position of the rotor 3 can be easily moved to the position where the length of the gap becomes the designed length.
  • the rotor 3 Since the adjusting member 6 and the second projecting portion 71b are screwed together, the rotor 3 does not move in the axial direction unless the adjusting member 6 is rotated. Therefore, the rotor 3 is positioned at a position where the length of the gap is the designed length G1.
  • FIG. 1 A method of manufacturing the axial gap motor of the first embodiment will be described mainly with reference to FIGS. 6 to 8.
  • FIG. The manufacturing method of the axial gap motor of this embodiment includes a process A and a process B. As shown in FIG. Process A prepares the parts of the axial gap motor. Process B assembles the parts.
  • the parts prepared in process A are the parts of the axial gap motor 1 described above with reference to FIG.
  • the parts include stator 2 , rotor 3 , shaft 4 , first bearing 51 , second bearing 55 , adjusting member 6 , case 7 , elastic member 8 , fastening member 91 and fastening member 92 .
  • Step B In step B of assembling the parts, each member is fixed at a predetermined position. Through the process B, the axial gap motor 1 as shown in FIG. 1 is manufactured.
  • the order in which the parts are assembled is, for example, the following steps B1 to B7 in order.
  • step B1 the second projecting portion 71b of the first plate portion 71 and the adjusting member 6 are screwed together.
  • the adjusting member 6 By rotating the adjusting member 6 with respect to the second protruding portion 71b, it is possible to adjust the position of the first end surface 61f of the adjusting member 6 to be arranged. The position of the first end surface 61f will be described later.
  • step B2 the first plate portion 71 and the stator 2 are fixed, and the first bearing 51 is arranged.
  • the order of the fixation and arrangement is not limited.
  • the fixing is performed as follows.
  • the stator 2 is arranged on the first plane 71 f of the first plate portion 71 .
  • the fastening member 91 is fastened to the second through hole of the first plate portion 71 and the hole portion of the stator 2 .
  • the arrangement is performed as follows.
  • the first bearing 51 is fitted in the first projecting portion 71 a of the first plate portion 71 .
  • the second end surface 53s of the outer race 53 of the first bearing 51 is brought into contact with the first end surface 61f of the adjusting member 6. As shown in FIG.
  • step B3 the first shaft portion 41 of the shaft 4 is placed inside the first bearing 51.
  • a rotor assembly in which the rotor 3 and the shaft 4 are combined is prepared in advance.
  • step B3 the first shaft portion 41 of the rotor assembly is placed inside the first bearing 51 .
  • step B4 is performed without step B31.
  • the step B31 is performed before the step B4.
  • step B31 the rotor 3 is fitted to the shaft 4 with the first shaft portion 41 arranged in the first bearing 51 .
  • step B4 the second bearing 55 is fitted to the fourth shaft portion 44 of the shaft 4.
  • step B5 the elastic member 8 is placed on the second bearing 55.
  • step B6 the fifth shaft portion 45 of the shaft 4 is fitted into the through hole 72h of the second plate portion 72, and the end face of the peripheral wall portion 73 and the first plate portion 71 are butted against each other. Then, the first plate portion 71 and the peripheral wall portion 73 are fixed by the fastening member 92 .
  • the fastening member 92 is provided in the third through hole of the first plate portion 71 and the hole portion of the peripheral wall portion 73 .
  • step B1 the position of the first end face 61f of the adjusting member 6 is arranged so that "gap length>design length G1" or "gap length ⁇ design length G1" after step B6. .
  • FIG. 6 shows a state in which the adjustment member 6 is arranged at a position where gap length>design length G1.
  • step B7 the length of the gap is set to the design length G1.
  • step B7 procedure 1 and procedure 2 are performed in order.
  • step 1 the adjustment member 6 is rotated with respect to the second projecting portion 71b.
  • a tool (not shown) is fitted in the adjusting member 6 .
  • the tool is rotated.
  • the rotation of the tool causes the adjustment member 6 to rotate with respect to the second projecting portion 71b.
  • the first end surface 61 f and the second end surface 53 s are in contact with each other, so that the rotation of the adjusting member 6 causes the first bearing 51 to move in the axial direction of the shaft 4 . Since the first end face 52f and the first end face 42f are in contact with each other, the shaft 4 is moved in the axial direction of the shaft 4 by the movement of the first bearing 51 in the axial direction.
  • the axial movement of the shaft 4 causes the rotor 3 to move in the axial direction of the shaft 4 .
  • the axial movement of the rotor 3 changes the length of the gap between the end surface 23a and the first end surface 35f.
  • the amount of rotation of the adjustment member 6 in Procedure 1 can be selected as appropriate.
  • the amount of rotation of the adjusting member 6 is determined based on the induced voltage value generated in the coil 25.
  • the induced voltage value can be measured by the voltmeter 110.
  • FIG. The induced voltage value decreases as the gap length increases, and increases as the gap length decreases.
  • a target value of the design induced voltage value determined based on the specifications of the axial gap motor 1 is defined as a design voltage value.
  • the design voltage value has a certain allowable width.
  • the gap length based on this design voltage value is the design length G1. That is, if the measured induced voltage value satisfies the design voltage value, it can be seen that the gap length satisfies the design length G1.
  • Procedure 2 measures the induced voltage value.
  • the measurement of the induced voltage value may be performed after the adjustment member 6 has finished rotating, or may be performed while the adjustment member 6 is being rotated.
  • the induced voltage value is measured without exciting the coil 25 .
  • Procedures 1 and 2 are repeated until the measured induced voltage value satisfies the design voltage value.
  • the graphs in FIGS. 7 and 8 show an example in which procedure 1 and procedure 2 were performed four times.
  • the induced voltage value (V) on the vertical axis on the left side of FIGS. 7 and 8 is the induced voltage value when the rotor 3 is moved to a predetermined position according to Procedure 1.
  • FIG. The length of the gap on the vertical axis on the right side of FIGS. 7 and 8 is the length of the gap when the rotor 3 is moved to a predetermined position according to procedure 1.
  • FIG. The number of times on the horizontal axis in FIGS. 7 and 8 is the number of times that procedure 1 and procedure 2 were performed.
  • the gap length is gradually increased by repeating steps 1 and 2 from the state in which the adjusting member 6 is placed at a position where "gap length>design length G1" as shown in FIG.
  • An example of shortened design length G1 is shown.
  • the gap length is adjusted by repeating steps 1 and 2 from the state where the adjustment member 6 is positioned so that "gap length ⁇ design length G1".
  • An example in which the design length is gradually increased to G1 is shown.
  • the measured induced voltage value increases as the number of times step 1 is performed increases. This is because the gap length is gradually shortened.
  • the measured induced voltage value decreases as the number of times of performing procedure 1 increases. This is because the gap length is gradually increasing.
  • the induced voltage value does not satisfy the range of the design voltage value when the number of times of performing the procedure 1 and the procedure 2 is 1 to 3 times.
  • the induced voltage value satisfies the design voltage value range. That is, in the example shown in FIGS. 7 and 8, the gap length becomes the design length G1 by performing Procedure 1 and Procedure 2 four times.
  • Step B7 may be performed between steps B4 and B5.
  • the position of the rotor 3 can be adjusted by the adjustment member 6 after assembling the parts.
  • the method of manufacturing the axial gap motor of this embodiment can adjust the position of the rotor 3 by the adjusting member 6 while assembling the parts. Therefore, in the method of manufacturing the axial gap motor of the present embodiment, the length of the gap can be set to the design length G1 by assembling the parts only once. Therefore, the method of manufacturing the axial gap motor of the present embodiment is excellent in productivity of the axial gap motor 1 excellent in assembly accuracy without using shims.
  • FIG. 9 A modified axial gap motor will be described with reference to FIGS. 9 and 10.
  • FIG. The axial gap motor of this example uses a circuit board 120, a sensor 130, a magnet 140, and a cover 160, as shown in FIG.
  • the circuit board 120 is for passing a current of an appropriate magnitude to each coil 25 at an appropriate timing when using the axial gap motor.
  • the circuit board 120 is attached to the second plane 71s.
  • the shape of the circuit board 120 is annular.
  • the circuit board 120 has a waveform conversion element group 121, a waveform control IC (Integrated Circuit) 122, and a phase detection circuit 123, as shown in FIG.
  • the waveform conversion element group 121 is connected to a power source (not shown) and the coil 25 shown in FIG.
  • Waveform conversion element group 121 converts the waveform of the power supply into an arbitrary drive waveform. Examples of drive waveforms are three-phase sinusoidal, square, full wave and half wave waveforms.
  • the power supply is a DC power supply or a single-phase AC power supply.
  • the waveform control IC 122 takes in signals indicating the rotational speed of the rotor 3 and the torque of the axial gap motor 1 from an external device, and controls the amplitude and frequency of the waveform of the current or voltage flowing through the coil 25 . Examples of external devices are resolvers, Hall sensors, rotary encoders.
  • a waveform control IC 122 is connected to the waveform conversion element group 121 and the phase detection circuit 123 .
  • a phase detection circuit 123 detects the rotational position of the rotor 3 and controls the phase timing of the waveform of the current or voltage flowing through the coil 25 .
  • Phase detection circuit 123 is connected to sensor 130 .
  • the sensor 130 is provided so as to face the magnet 140 .
  • One example of a type of sensor 130 is a Hall sensor.
  • the magnet 140 is attached to the outer peripheral surface of the jig 141 .
  • the jig 141 is attached to the end surface of the first shaft portion 41 . Therefore, when the shaft 4 rotates, the jig 141 rotates.
  • the jig 141 has a cylindrical shape.
  • the shape of the magnet 140 is cylindrical, and the magnet 140 has S poles and N poles alternately arranged in the circumferential direction.
  • the cover 160 protects the circuit board 120.
  • the cover 160 has a plate portion 161 and a peripheral wall portion 162 .
  • the plate portion 161 and the peripheral wall portion 162 are integrally formed.
  • the plate portion 161 is arranged to face the second plane 71s with the circuit board 120 interposed therebetween.
  • the plate portion 161 covers the circuit board 120 .
  • the shape of the plate portion 161 is an annular plate.
  • a through hole is provided in the center of the plate portion 161 .
  • the inner diameter of the plate portion 161 is larger than the inner diameter of the adjusting member 6 . Therefore, it is easy to insert the tool into the through hole of the plate portion 161 . Therefore, it is easy to rotate the adjusting member 6 with a tool.
  • the peripheral wall portion 162 has a cylindrical shape.
  • the peripheral wall portion 162 is provided outside the outer peripheral surface of the circuit board 120 .
  • the peripheral wall portion 162 is attached to the second plane 71s.
  • the axial gap motor of this example like the first embodiment, has excellent assembly accuracy without using shims.
  • the axial gap motor of Embodiment 2 has a washer 65 as shown in FIG.
  • the washer 65 is arranged between the second end surface 53s and the first end surface 61f.
  • the inner diameter of the washer 65 is greater than the outer diameter of the inner race 52 and equal to or less than the inner diameter of the outer race 53 .
  • the washer 65 can facilitate the support of the outer race 53 by the adjusting member 6 .
  • An example of the type of washer 65 is a flat washer or a disc spring washer.
  • the flat washer improves the compatibility between the second end surface 53s and the first end surface 61f.
  • the disc spring washer easily prevents the adjustment member 6 from loosening with respect to the second projecting portion 71b.
  • the shape of the adjusting member 6 of this embodiment is cylindrical, as in the first embodiment.
  • the lower limit of the inner dimension of the cylindrical adjusting member 6 can also be set to be equal to or greater than the inner diameter of the inner race 52 and equal to or less than the outer diameter of the inner race 52 . This is because the contact between the adjusting member 6 and the inner race 52 is prevented by the washer 65 . Therefore, the axial gap motor of this embodiment can suppress an increase in mechanical loss even if the inner dimension of the adjusting member 6 is equal to or larger than the inner diameter of the inner race 52 and equal to or smaller than the outer diameter of the inner race 52 .
  • the shape of the adjusting member 6 can also be cylindrical. This is because the washer 65 prevents contact between the inner race 52 and the adjustment member 6 which is a solid body such as a column. Therefore, the axial gap motor of this embodiment can suppress an increase in mechanical loss even if the shape of the adjusting member 6 is cylindrical.
  • the cylindrical adjustment member 6 has a first recess. The first recess is fitted with a tool.
  • the first concave portion is provided on the second end surface of the adjusting member 6 . As shown in FIG. 11, when the first shaft portion 41 protrudes beyond the second end surface 52s, the cylindrical adjusting member 6 has a second concave portion. The first shaft portion 41 is arranged in the second recess.
  • the second recess is provided on the first end surface of the adjusting member 6 .
  • the inner dimension of the second recess is such that the inner peripheral surface of the second recess and the outer peripheral surface of the first shaft portion 41 do not come into contact with each other.
  • the inner dimension is the diameter of the inscribed circle of the inner peripheral surface of the second recess.
  • the depth of the second recess is such that the bottom of the second recess and the end face of the first shaft portion 41 do not contact each other. If the end surface of the first shaft portion 41 and the second end surface 52s are substantially flush with each other, and the first shaft portion 41 and the columnar adjusting member 6 do not come into contact with each other, the second concave portion may be omitted.
  • the yoke may be configured by connecting a plurality of fan plate-shaped yoke pieces in an annular shape.
  • the number of teeth connected to each yoke piece may be one or plural.
  • the axial gap motor may be a double stator/single rotor type axial gap motor.
  • a double-stator/single-rotor axial gap motor is a motor having two stators and one rotor.
  • a double-stator/single-rotor type axial gap motor is assembled so that one rotor is sandwiched between two stators.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Manufacture Of Motors, Generators (AREA)
PCT/JP2022/020391 2021-05-21 2022-05-16 アキシャルギャップモータ、及びアキシャルギャップモータの製造方法 WO2022244733A1 (ja)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2023522658A JPWO2022244733A1 (enrdf_load_stackoverflow) 2021-05-21 2022-05-16

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2021-086466 2021-05-21
JP2021086466 2021-05-21

Publications (1)

Publication Number Publication Date
WO2022244733A1 true WO2022244733A1 (ja) 2022-11-24

Family

ID=84141565

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2022/020391 WO2022244733A1 (ja) 2021-05-21 2022-05-16 アキシャルギャップモータ、及びアキシャルギャップモータの製造方法

Country Status (2)

Country Link
JP (1) JPWO2022244733A1 (enrdf_load_stackoverflow)
WO (1) WO2022244733A1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024235693A1 (fr) * 2023-05-16 2024-11-21 Horse Powertrain Solutions, S.L. Ensemble d'elements d'un groupe motopropulseur

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5261714A (en) * 1975-11-15 1977-05-21 Matsushita Electric Works Ltd Synchronous motor
JPS59179478U (ja) * 1983-05-19 1984-11-30 ミツミ電機株式会社 モ−タ装置
JPH01116581U (enrdf_load_stackoverflow) * 1988-01-28 1989-08-07
JP2018082610A (ja) * 2016-11-07 2018-05-24 アスモ株式会社 車両用モータの取付構造及び車載機器

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5261714A (en) * 1975-11-15 1977-05-21 Matsushita Electric Works Ltd Synchronous motor
JPS59179478U (ja) * 1983-05-19 1984-11-30 ミツミ電機株式会社 モ−タ装置
JPH01116581U (enrdf_load_stackoverflow) * 1988-01-28 1989-08-07
JP2018082610A (ja) * 2016-11-07 2018-05-24 アスモ株式会社 車両用モータの取付構造及び車載機器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024235693A1 (fr) * 2023-05-16 2024-11-21 Horse Powertrain Solutions, S.L. Ensemble d'elements d'un groupe motopropulseur
FR3148876A1 (fr) * 2023-05-16 2024-11-22 Renault S.A.S Ensemble d’éléments d’un groupe motopropulseur

Also Published As

Publication number Publication date
JPWO2022244733A1 (enrdf_load_stackoverflow) 2022-11-24

Similar Documents

Publication Publication Date Title
US7960884B2 (en) Axial gap type rotating machine
EP3490120B1 (en) Rotary electric machine equipped with magnetic flux variable mechanism
KR101099894B1 (ko) 회전 전기 기계용 로터
US11888351B2 (en) Core, stator, and rotary electric machine
WO2020137549A1 (ja) コア、ステータ、及び回転電機
EP2867979B1 (en) Device and process for mounting permanent magnets in an electric motor rotor
JP4213798B2 (ja) 密閉型電動圧縮機
JP7730734B2 (ja) 部材、ステータコア、ステータ、及び回転電機
WO2022244733A1 (ja) アキシャルギャップモータ、及びアキシャルギャップモータの製造方法
US7777391B2 (en) Armature, motor and compressor and methods of manufacturing the same
JP2011015592A (ja) 分割ステータとその製造方法
CN211151651U (zh) 用于电机的转子和电机
WO2015004745A1 (ja) 回転電機、及びエレベータ用巻上機
WO2022244482A1 (ja) モータ、及びモータの製造方法
WO2022270397A1 (ja) モータ、およびモータの製造方法
JP2004304995A (ja) 励磁機、界磁機、およびそれを用いた電動機
JP7672427B2 (ja) モータの製造方法
JP2021100329A (ja) ステータコア、ステータ、回転電機、及びステータコアの製造方法
JP5985067B2 (ja) 回転電機、及びエレベータ用巻上機
JP7471619B1 (ja) 同期回転電機
US20240243645A1 (en) Axial air gap electric rotary motor
JP4531724B2 (ja) 多相クローポールモータ
CN113472107A (zh) 马达
JP2021176246A (ja) 埋め込み磁石型ロータ、モータ及び電気機器
JPH07123689A (ja) Ｐｍ型ステッピングモータ

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22804644

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2023522658

Country of ref document: JP

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 22804644

Country of ref document: EP

Kind code of ref document: A1