WO2021171556A1 - 電動機、送風機及び空気調和装置 - Google Patents
電動機、送風機及び空気調和装置 Download PDFInfo
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- WO2021171556A1 WO2021171556A1 PCT/JP2020/008310 JP2020008310W WO2021171556A1 WO 2021171556 A1 WO2021171556 A1 WO 2021171556A1 JP 2020008310 W JP2020008310 W JP 2020008310W WO 2021171556 A1 WO2021171556 A1 WO 2021171556A1
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- Prior art keywords
- bearing
- outer ring
- holding portion
- peripheral surface
- motor according
- Prior art date
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Classifications
-
- 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
-
- 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
- H02K5/1732—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 radially supporting the rotary shaft at both ends of the rotor
-
- 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
- H02K21/14—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets with magnets rotating within the armatures
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/27—Rotor cores with permanent magnets
- H02K1/2706—Inner rotors
- H02K1/272—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis
- H02K1/274—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis the rotor consisting of two or more circumferentially positioned magnets
- H02K1/2746—Inner rotors the magnetisation axis of the magnets being perpendicular to the rotor axis the rotor consisting of two or more circumferentially positioned magnets the rotor consisting of magnets arranged with the same polarity, e.g. consequent pole type
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K2213/00—Specific aspects, not otherwise provided for and not covered by codes H02K2201/00 - H02K2211/00
- H02K2213/03—Machines characterised by numerical values, ranges, mathematical expressions or similar information
Definitions
- This disclosure relates to motors, blowers and air conditioners.
- the motor of Patent Document 1 further has a bearing that supports the rotating shaft of the rotor and a bearing holding portion that holds the bearing.
- the outer ring of the bearing may be fixed to the bearing holding portion by a clearance fit.
- the object of the present disclosure is to prevent the occurrence of creep in bearings in an electric motor having a concave pole type rotor.
- the motor according to one aspect of the present disclosure includes a stator, a concave pole type rotor having a rotating shaft, a bearing which is a rolling bearing that supports the rotating shaft, and a bearing fixed to the stator of the bearing. Prevents creep that is arranged between the bearing holding portion that holds the outer ring and the outer ring of the bearing and the bearing holding portion, and increases the frictional resistance of the outer ring between the outer ring of the bearing and the bearing holding portion in the circumferential direction. Has a bearing.
- FIG. It is a block diagram which shows the partial cross section and the side surface of the electric motor which concerns on Embodiment 1.
- FIG. It is sectional drawing which cut
- FIG. It is a schematic diagram for demonstrating the creep of a bearing in an electric motor.
- FIG. It is an enlarged cross-sectional view which shows the structure around the bearing on the load side of the motor shown in FIG.
- FIG. 5 is an enlarged cross-sectional view showing a configuration around a bearing on the load side of the motor according to the second embodiment.
- FIG. 5 is an enlarged cross-sectional view showing a configuration around a bearing on the load side of the motor according to the third embodiment. It is an enlarged cross-sectional view which shows the structure around the bearing on the load side of the electric motor which concerns on the modification of Embodiment 3.
- (A) is an enlarged cross-sectional view showing the configuration around the bearing on the load side of the motor according to the fourth embodiment.
- FIG. 5 is an enlarged cross-sectional view showing a configuration around a bearing on the load side of the motor according to the fifth embodiment. It is a block diagram which shows the partial cross section and the side surface of the electric motor which concerns on Embodiment 6. It is a block diagram which shows the partial cross section and the side surface of the electric motor which concerns on the modification 1 of Embodiment 6.
- FIG. 15 is an enlarged cross-sectional view showing a configuration around a bearing on the opposite load side of the motor shown in FIG. It is a block diagram which shows the partial cross section and the side surface of the electric motor which concerns on the modification 2 of Embodiment 6.
- FIG. 6 It is a block diagram which shows the partial cross section and the side surface of the electric motor which concerns on the modification 3 of Embodiment 6. It is a figure which shows the structure of the air conditioner to which the motor which concerns on one of Embodiments 1-6 is applied. It is sectional drawing which shows the structure of the outdoor unit shown in FIG.
- the drawing shows the xyz Cartesian coordinate system for easy understanding of the description.
- the z-axis is a coordinate axis parallel to the axis of the rotor.
- the x-axis is a coordinate axis orthogonal to the z-axis.
- the y-axis is a coordinate axis orthogonal to both the x-axis and the z-axis.
- FIG. 1 is a configuration diagram showing a partial cross section and side surfaces of the motor 100 according to the first embodiment.
- the electric motor 100 has a rotor 1 and a mold stator 9 as a stator.
- the rotor 1 is arranged inside the mold stator 9. That is, the electric motor 100 is an inner rotor type electric motor.
- the rotor 1 has a shaft 15 as a rotation axis.
- the rotor 1 is rotatable about the axis C1 of the shaft 15.
- the shaft 15 projects from the mold stator 9 toward the + z axis.
- a fan of the blower that is, an impeller 704 of the outdoor blower 150 described later
- the tip portion 15a of the shaft 15 is referred to as the "circumferential direction" (for example, the arrow R1 shown in FIG. 2).
- the z-axis direction is referred to as "axial direction”, and the direction orthogonal to the axial direction is referred to as “diameter direction”.
- the protruding side of the shaft 15 (that is, the + z-axis side) is referred to as a "load side”, and the side opposite to the load side of the shaft 15 is referred to as a "counter-load side”.
- the motor 100 further includes a bearing 21 that supports the load side of the shaft 15 and a bearing 22 that supports the opposite load side of the shaft 15.
- the bearing 21 and the bearing 22 are arranged on opposite sides of the stator core 50 of the mold stator 9.
- the bearing 21 supports a portion 15c of the shaft 15 on the load side of the mold stator 9.
- the bearing 22 supports the end portion (that is, the portion on the counterload side) 15b of the shaft 15 on the ⁇ z axis side via the insulating sleeve 60.
- the bearing 21 and the bearing 22 are rolling bearings, for example, ball bearings.
- the insulating sleeve 60 is arranged between the end portion 15b of the shaft 15 on the ⁇ z axis side and the bearing 22.
- the insulating sleeve 60 is, for example, substantially cylindrical.
- the insulating sleeve 60 is made of, for example, a thermosetting resin.
- the insulating sleeve 60 is formed of a BMC (Bulk Molding Compound) resin.
- the shaft 15 and the bearing 22 are insulated from each other. Therefore, the shaft current that generates electrolytic corrosion is prevented from flowing from the shaft 15 to the bearing 22. Further, by preventing the axial current from flowing to the bearing 22, it is also possible to prevent the axial current from flowing to the bearing 21 via the bearing 22, the mold stator 9, and the metal bracket 6.
- the insulating sleeve 60 may be arranged between the shaft 15 and the bearing 21, or may be arranged both between the shaft 15 and the bearing 21 and between the shaft 15 and the bearing 22. ..
- the motor 100 further has a cap 8.
- the cap 8 is fixed to the shaft 15 so as to cover a part of the metal bracket 6.
- the cap 8 is a member that prevents foreign matter (for example, water) from entering the inside of the electric motor 100.
- FIG. 2 is a cross-sectional view of the rotor 1 and the mold stator 9 shown in FIG. 1 cut along the A2-A2 line. In FIG. 2, the mold resin portion 56 of the mold stator 9 is not shown.
- the mold stator 9 has a stator core 50, a coil 55 wound around the stator core 50, and a mold resin portion 56 that covers the stator core 50. ..
- the stator core 50 has an annular yoke 51 centered on the axis C1 and a plurality of teeth 52 extending radially inward from the yoke 51.
- the plurality of teeth 52 are arranged at regular intervals in the circumferential direction R1.
- the tip of each of the plurality of teeth 52 faces the rotor 1 in the radial direction via an air gap.
- the coil 55 is wound around the teeth 52 via an insulator 53.
- the mold resin portion 56 is formed of, for example, a thermosetting resin such as BMC resin.
- the mold resin portion 56 has an opening 56a.
- the opening 56a is formed on the + z-axis side of the mold resin portion 56.
- a metal bracket 6 as a bearing holding portion is fixed to the opening 56a.
- a bearing 21 on the load side is held in the metal bracket 6. That is, in the first embodiment, the bearing holding portion that holds the bearing 21 on the load side is made of metal. As shown in FIG. 17 or 18 described later, the bearing holding portion that holds the bearing 21 may be made of resin.
- the mold resin portion 56 further has a holding portion 56b formed on the ⁇ z axis side.
- the bearing 22 is held in the holding portion 56b. That is, in the first embodiment, the bearing holding portion for holding the bearing 22 on the counterload side is made of resin. As shown in FIGS. 15 to 17 described later, the bearing holding portion for holding the bearing 22 may be made of metal.
- the circuit board 7 is embedded inside the mold resin portion 56.
- a power supply lead wire or the like for supplying electric power to the coil 55 is connected to the circuit board 7.
- FIG. 3 is an enlarged cross-sectional view showing the configuration of the rotor 1 shown in FIG.
- the rotor 1 has a rotor core 10 and a shaft 15.
- the rotor core 10 is an annular member centered on the axis C1.
- the rotor core 10 is formed by fixing a plurality of electromagnetic steel sheets laminated in the axial direction to each other by, for example, caulking.
- the rotor core 10 is provided with a permanent magnet 40.
- the permanent magnet 40 is embedded in the rotor core 10. That is, the rotor 1 has an IPM (Interior Permanent Magnet) structure.
- the rotor 1 may have an SPM (Surface Permanent Magnet) structure in which a permanent magnet 40 is attached to the outer periphery of the rotor core 10.
- the rotor core 10 has a first iron core portion 11 to which the permanent magnet 40 is attached and a second iron core portion 12 to which the permanent magnet 40 is not attached.
- the rotor core 10 has a plurality of (for example, five) first iron core portions 11 and a plurality of (for example, five) second iron core portions 12.
- the plurality of first iron core portions 11 and the plurality of second iron core portions 12 are alternately arranged in the circumferential direction R1.
- the first iron core portion 11 has a magnet insertion hole 11a.
- the magnet insertion hole 11a is formed radially inside the outer circumference of the first iron core portion 11.
- the shape of the magnet insertion hole 11a is, for example, linear in a plan view.
- one permanent magnet 40 is inserted into one magnet insertion hole 11a.
- the shape of the magnet insertion hole 11a may be a V shape having a convex shape in the radial direction or a convex shape in the radial direction in a plan view. Further, two or more permanent magnets 40 may be inserted into one magnet insertion hole 11a.
- the permanent magnet 40 is, for example, a rare earth magnet.
- the permanent magnet 40 is a neodymium rare earth magnet containing, for example, Nd (neodymium) -Fe (iron) -B (boron).
- the plurality of permanent magnets 40 have magnetic poles (for example, N poles) having the same polarity as each other on the outer side in the radial direction.
- the magnet magnetic pole P1 is formed on the outer circumference of the first iron core portion 11.
- a straight line extending in the radial direction through the center (that is, the pole center) of the magnetic pole P1 in the circumferential direction R1 is referred to as a "pole center line M1" (see FIG. 6).
- the plurality of permanent magnets 40 have magnetic poles (for example, S poles) having the same polarity inside each other in the radial direction.
- a virtual magnetic pole P2 (for example, an S pole) is formed on the radial outer side of the second iron core portion 12 by the magnetic flux emitted from the radial inside of the permanent magnet 40 flowing into the second iron core portion 12. .. Therefore, the plurality of second iron core portions 12 have virtual magnetic poles P2 having the same polarity as each other on the outer side in the radial direction.
- the rotor 1 is a concave pole type rotor in which magnet magnetic poles P1 and virtual magnetic poles P2 are alternately arranged in the circumferential direction R1.
- the number of permanent magnets 40 can be halved as compared with the non-consequent pole type rotor 1 having the same number of poles. As a result, the manufacturing cost of the rotor 1 is reduced.
- the number of poles of the rotor 1 is 10, but the number of poles is not limited to 10, and it may be an even number of 2 or more.
- the magnet magnetic pole P1 may be the S pole and the virtual magnetic pole P2 may be the N pole.
- the first iron core portion 11 further has a plurality of flux barriers 11b as leakage flux suppression holes.
- the flux barrier 11b is formed on both sides of the magnet insertion hole 11a in the circumferential direction R1. Since the portion between the flux barrier 11b and the outer circumference of the first iron core portion 11 is thin, the leakage flux between the adjacent magnet magnetic poles P1 and the virtual magnetic pole P2 is suppressed.
- the second iron core portion 12 has a caulking portion 14.
- the caulking portion 14 is a caulking mark formed when a plurality of electromagnetic steel sheets laminated in the axial direction are fixed by caulking.
- the shape of the crimped portion 14 when viewed in the axial direction is, for example, a circular shape.
- the shape of the crimped portion 14 is not limited to a circular shape, and may be another shape such as a rectangular shape.
- the rotor 1 further has a connecting portion 30 that connects the rotor core 10 and the shaft 15.
- the connecting portion 30 is formed of a resin material having an electrically insulating property.
- the connecting portion 30 is formed of, for example, a thermoplastic resin such as PBT (Poly Butene terephlate).
- PBT Poly Butene terephlate
- the connecting portion 30 has an inner cylinder portion 31, a plurality of ribs 32, and an outer cylinder portion 33.
- the inner cylinder portion 31 has an annular shape and is in contact with the outer peripheral surface 15d of the shaft 15.
- the outer cylinder portion 33 is in contact with the inner peripheral surface 10a of the rotor core 10.
- the plurality of ribs 32 connect the inner cylinder portion 31 and the outer cylinder portion 33.
- the plurality of ribs 32 extend radially outward from the inner cylinder portion 31.
- the plurality of ribs 32 are arranged at equal intervals in the circumferential direction R1 with the axis C1 as the center.
- a cavity 35 penetrating in the axial direction is formed between the plurality of ribs 32 adjacent to each other in the circumferential direction R1.
- the rotor core 10 and the shaft 15 may be directly fixed without the connection portion 30.
- the rotor 1 further has a sensor magnet 16.
- the sensor magnet 16 is attached to, for example, the ⁇ z axis side of the rotor core 10 and faces the circuit board 7.
- a magnetic sensor (not shown) provided on the circuit board 7, the position of the rotor 1 in the circumferential direction R1 is detected.
- FIG. 4 is a cross-sectional view showing the configuration of the metal bracket 6.
- the metal bracket 6 is formed of, for example, a galvanized steel plate.
- the metal bracket 6 is not limited to the galvanized steel plate, and may be formed of another metal material such as an aluminum alloy.
- the metal bracket 6 has a cylindrical portion 61, a flange portion 62, a fixing portion 63, and a bottom surface portion 64.
- the cylindrical portion 61 extends substantially parallel to the axis C1.
- the flange portion 62 is formed integrally with the cylindrical portion 61, and extends radially outward from the end portion of the cylindrical portion 61 on the counterload side.
- the fixing portion 63 extends from the radial outer end of the flange portion 62 toward the + z axis side.
- the fixing portion 63 is a portion of the metal bracket 6 that is fixed to the mold resin portion 56 (see FIG. 1).
- the fixing portion 63 is fixed to, for example, the mold resin portion 56 by press fitting.
- the bottom surface portion 64 is formed integrally with the cylindrical portion 61, and extends radially inward from the end of the cylindrical portion 61 on the load side.
- the cylindrical portion 61, the flange portion 62, and the bottom surface portion 64 are formed, for example, by drawing the above-mentioned galvanized steel sheet.
- a shaft penetrating portion 65 through which the shaft 15 (see FIG. 1) is penetrated is formed on the bottom surface portion 64.
- the shaft penetrating portion 65 projects toward the + z axis side from the radial inner end portion of the bottom surface portion 64.
- the outer ring 21b of the bearing 21 shown in FIG. 1 is fixed to the cylindrical portion 61 by a clearance fit. If a load is applied to the outer ring 21b while the motor 100 is rotating while the outer ring 21b is fixed to the cylindrical portion 61 by a clearance fit, creep may occur in which the outer ring 21b rotates with respect to the cylindrical portion 61. ..
- FIG. 5 is a schematic diagram for explaining creep in the bearing 21.
- the bearing 21 is formed between the inner ring 21a that supports the shaft 15, the outer ring 21b that is fixed to the cylindrical portion 61 of the metal bracket 6 via the clearance ⁇ , and the inner ring 21a and the outer ring 21b. It has a ball 21c as an arranged rolling element.
- the clearance ⁇ is exaggerated, but the size of the clearance ⁇ is about 10 ⁇ m.
- the circumferential length of the outer ring 21b is shorter than the circumferential length of the cylindrical portion 61.
- the load Fr acting on the outer ring 21b is generated as a radial load that touches around when the shaft 15 of the rotor 1 is eccentric, for example.
- the shaft 15 of the rotor 1 depends on the difference between the surface magnetic flux density of the magnet magnetic pole P1 and the surface magnetic flux density of the virtual magnetic pole P2. Eccentricity is likely to occur.
- FIG. 6 is a magnetic flux diagram showing a simulation result of the flow of magnetic flux in the motor 100.
- reference numerals 40a, 40b, 40c, 40d, and 40e are attached to the permanent magnets in order to facilitate understanding of the description.
- the magnetic flux emitted from the radial inside of the permanent magnet 40a flows into the second iron core portions 12 located on both sides of the circumferential direction R1 with reference to the polar center line M1, thereby causing the virtual magnetic pole P2. (See FIG. 3) is formed.
- the magnetic flux density varies between the second iron core portions 12 located on both sides of the circumferential direction R1 with reference to the polar center line M1. In some cases. Therefore, in the circumferential direction R1 of the rotor 1, the difference between the surface magnetic flux density at the magnet magnetic pole P1 and the surface magnetic flux density at the virtual magnetic pole P2 may become large.
- the magnitude of the magnetic attraction acting between the stator core 50 and the rotor 1 becomes unbalanced in the circumferential direction R1. Therefore, the axis C1 of the shaft 15 is eccentric and a radial excitation force acts on the rotor 1. Therefore, in the motor 100 according to the first embodiment, the radial excitation force acts on the bearing 21 or the bearing 22 that supports the shaft 15 of the rotor 1 as the load Fr shown in FIG.
- the creep prevention portion for preventing the occurrence of creep in the bearing 21 (in the first embodiment, the annular elastic body 23 shown in FIG. 1 or 7) will be described.
- FIG. 7 is an enlarged cross-sectional view showing the configuration around the bearing 21 of the motor 100 shown in FIG.
- the electric motor 100 has an annular elastic body 23 as an elastic member which is a creep prevention portion.
- the annular elastic body 23 is arranged between the outer peripheral surface 21f of the outer ring 21b and the inner peripheral surface 61a of the cylindrical portion 61, and is compressed in the radial direction.
- the coefficient of friction between the annular elastic body 23 and the cylindrical portion 61 is larger than the coefficient of friction between the outer ring 21b and the cylindrical portion 61. That is, by providing the annular elastic body 23 between the outer ring 21b and the cylindrical portion 61, the frictional resistance in the circumferential direction R1 between the outer peripheral surface 21f of the outer ring 21b and the inner peripheral surface 61a of the cylindrical portion 61 (that is, that is, Friction force) goes up. As a result, the outer ring 21b is less likely to rotate with respect to the cylindrical portion 61, so that the occurrence of creep in the bearing 21 can be suppressed.
- FIG. 8 (A) is a plan view showing the annular elastic body 23 shown in FIG. 7, and FIG. 8 (B) is a cross-sectional view showing the annular elastic body 23 shown in FIG. 8 (A).
- the annular elastic body 23 is an annular elastic member centered on the axis C1.
- the cross-sectional shape of the annular elastic body 23 is, for example, circular.
- the annular elastic body 23 is an O-ring.
- the cross-sectional shape of the annular elastic body 23 is not limited to a circle, and may be another shape such as a quadrangle.
- the coefficient of friction between the O-ring and the mating surface is, for example, a value included in the range of 1.03 to 1.25.
- the coefficient of friction between the iron forming the outer ring 21b and the metal bracket 6 and the mating surface is about 0.2. Therefore, the coefficient of friction between the O-ring and the mating surface is larger than the coefficient of friction between the iron and the mating surface.
- the annular elastic body 23 is, for example, a rubber containing a thermosetting elastomer.
- the rubber containing the thermosetting elastomer is, for example, fluororubber, silicon rubber, ethylene propylene rubber, nitrile rubber and the like.
- the annular elastic body 23 is arranged in the groove portion 21d formed on the outer peripheral surface 21f of the outer ring 21b.
- the groove portion 21d is a long groove extending in the circumferential direction R1 on the outer peripheral surface 21f.
- the groove portion 21d may be formed on the inner peripheral surface 61a of the cylindrical portion 61.
- the groove portion 21d is formed on the outer peripheral surface 21f at a position deviated from the axial center position P of the ball 21c to one side in the axial direction (+ z axis side in FIG. 7).
- the annular elastic body 23 can be arranged on the outer ring 21b while ensuring a sufficient wall thickness at the central portion in the axial direction.
- the groove portion 21d may be formed on the outer peripheral surface 21f at a position deviated toward the ⁇ z axis side with respect to the central position P in the axial direction of the ball 21c.
- the annular elastic body 23 is arranged between the outer ring 21b and the cylindrical portion 61 on the bottom surface portion 64 side with reference to the axial center position P of the ball 21c.
- the cylindrical portion 61, the flange portion 62, and the bottom surface portion 64 are formed, for example, by drawing a galvanized steel sheet.
- the mold that is, punch
- the flange portion 62 side of the inner peripheral surface 61a of the cylindrical portion 61 tends to expand in diameter outward in the radial direction as compared with the bottom surface portion 64 side. That is, the closer the inner peripheral surface 61a of the cylindrical portion 61 is to the bottom surface portion 64, the higher the dimensional accuracy can be easily obtained.
- the motor 100 further has a preload spring 45 arranged between the bottom surface portion 64 of the metal bracket 6 and the bearing 21.
- the preload spring 45 applies a force that presses the end surface 21i of the outer ring 21b in the axial direction toward the mold stator 9 shown in FIG. As a result, the internal clearance in the bearing 21 becomes a negative clearance, so that the rigidity of the bearing 21 is increased.
- the preload spring 45 has a through hole 45a through which the shaft 15 penetrates.
- the preload spring 45 is, for example, a wave washer.
- the annular elastic body 23 that increases the frictional resistance in the circumferential direction R1 between the outer peripheral surface 21f of the outer ring 21b of the bearing 21 and the inner peripheral surface 61a of the cylindrical portion 61 of the metal bracket 6. Is placed. This makes it possible to prevent the occurrence of creep in the bearing 21. Therefore, in the motor 100, it is possible to prevent problems such as vibration and noise caused by creep, and the quality of the motor 100 is improved.
- the groove portion 21d in which the annular elastic body 23 is arranged is located at a position shifted to one side in the axial direction with reference to the axial center position P of the ball 21c. It is formed.
- the annular elastic body 23 can be arranged while ensuring a sufficient wall thickness at the central portion in the axial direction.
- the annular elastic body 23 is arranged between the outer ring 21b and the cylindrical portion 61 on the bottom surface portion 64 side with reference to the axial center position P of the ball 21c.
- the metal bracket 6 is formed by drawing, the closer the metal bracket 6 is to the bottom surface 64 on the inner peripheral surface 61a of the cylindrical portion 61, the higher the dimensional accuracy can be easily obtained. Therefore, when the annular elastic body 23 is arranged on the bottom surface portion 64 side between the outer ring 21b and the cylindrical portion 61, the compressive force acting on the annular elastic body 23 is stabilized. As a result, the frictional force that prevents the outer ring 21b from rotating with respect to the cylindrical portion 61 is also stabilized, so that the occurrence of creep in the bearing 21 can be further prevented.
- the bearing holding portion for holding the bearing 21 on the load side is a metal bracket 6 formed of a galvanized steel plate. Since the galvanized steel sheet can easily obtain high dimensional accuracy as compared with resin, the dimensional accuracy between the outer ring 21b of the bearing 21 and the metal bracket 6 can be managed with high accuracy. Further, since the bearing holding portion (that is, the holding portion 56b) that holds the bearing 22 on the counterload side is formed of BMC resin, the manufacturing cost of the motor 100 can be reduced.
- the annular elastic body 23 for preventing the occurrence of creep in the bearing 21 in which creep is likely to occur is provided. This makes it possible to reduce the cost of the motor 100 as compared with a configuration that prevents the occurrence of creep in both the bearing 21 and the bearing 22.
- the sequential pole type rotor 1 when a radial excitation force acts on the bearings 21 and 22 supporting the shaft 15, it is formed between the ball 21c and the raceway ring (inner ring 21a or outer ring 21b).
- the oil film may break.
- the ball 21c and the raceway ring are in direct contact with each other without passing through the oil film, electrolytic corrosion is likely to occur when the axial current flows through the bearings 21 and 22.
- the insulating sleeve 60 is arranged between the end portion 15b of the shaft 15 on the ⁇ z axis side and the bearing 22. As a result, the flow of the axial current to the bearings 21 and 22 that support the shaft 15 is prevented, so that the occurrence of electrolytic corrosion can be prevented.
- the connecting portion 30 formed of the resin material having an electrically insulating property connects the rotor core 10 and the shaft 15, the rotor core 10 and the connecting portion 30 are connected to the rotor core 10. Axial current is prevented from flowing between the shaft 15 and the shaft 15. As a result, the shaft current is prevented from flowing through the rotor core 10 and the shaft 15 to the bearings 21 and 22, so that galvanic corrosion can be prevented from occurring.
- FIG. 9 is an enlarged cross-sectional view showing the configuration around the bearing 221 on the load side of the motor 200 according to the second embodiment.
- components that are the same as or correspond to the components shown in FIG. 7 are designated by the same reference numerals as those shown in FIG.
- the motor 200 according to the second embodiment is characterized in that a plurality of annular elastic bodies 23 and 24 are arranged between the outer ring 221b of the bearing 221 on the load side and the cylindrical portion 61 of the metal bracket 6. It is different from the electric motor 100 according to the above.
- the electric motor 200 includes a load-side bearing 221 that supports the load-side of the shaft 15, a metal bracket 6 that holds the load-side bearing 221 and a plurality of electric motors 200 as creep prevention portions (in FIG. 9). It has two) annular elastic bodies 23 and 24.
- the plurality of annular elastic bodies 23 and 24 are arranged between the outer peripheral surface 221f of the outer ring 221b and the inner peripheral surface 61a of the cylindrical portion 61.
- the number of annular elastic bodies 23 and 24 arranged between the outer ring 221b and the cylindrical portion 61 is not limited to two, and may be three or more.
- the outer ring 221b includes a first groove portion 21d and a second groove portion 221e formed at different positions in the axial direction on the outer peripheral surface 221f.
- the first groove portion 21d and the second groove portion 221e are arranged at positions symmetrical with respect to, for example, the axial center position P of the ball 21c.
- An annular elastic body 23 is arranged in the first groove portion 21d.
- An annular elastic body 24 is arranged in the second groove portion 221e.
- the annular elastic body 24 is, like the annular elastic body 23, a rubber containing, for example, a thermosetting elastomer. Further, the annular elastic body 24 is an O-ring like the annular elastic body 23, for example.
- the coefficient of friction between the annular elastic body 24 and the cylindrical portion 61 is larger than the coefficient of friction between the outer ring 21b and the cylindrical portion 61. Therefore, when the plurality of annular elastic bodies 23, 24 arranged between the outer peripheral surface 21f of the outer ring 21b and the inner peripheral surface 61a of the cylindrical portion 61 are compressed in the radial direction, the annular elastic bodies 23, 24 are formed.
- the frictional resistance in the circumferential direction R1 between the outer ring 21b and the cylindrical portion 61 increases. As a result, the outer ring 21b is less likely to rotate with respect to the cylindrical portion 61, so that the occurrence of creep in the bearing 21 can be prevented.
- a plurality of annular elastic bodies 23 and 24 are arranged between the outer peripheral surface 221f of the outer ring 221b and the inner peripheral surface 61a of the cylindrical portion 61.
- the frictional resistance in the circumferential direction R1 between the outer peripheral surface 221f of the outer ring 221b and the inner peripheral surface 61a of the cylindrical portion 61 is further increased. Therefore, it is possible to further prevent the occurrence of creep in the bearing 221 on the load side.
- the plurality of annular elastic bodies 23 and 24 are arranged at positions symmetrical with respect to the axial center position P of the ball 21c.
- a plurality of annular elastic bodies 23 and 24 can be arranged while ensuring a sufficient wall thickness at the central portion in the axial direction on which the load from the ball 21c acts.
- the motor 200 according to the second embodiment is the same as the motor 100 according to the first embodiment.
- FIG. 10 is an enlarged cross-sectional view showing the configuration around the bearing 321 on the load side of the motor 300 according to the third embodiment.
- components that are the same as or correspond to the components shown in FIG. 7 are designated by the same reference numerals as those shown in FIG.
- the electric motor 300 is different from the electric motors 100 and 200 according to the first or second embodiment in the configuration of the creep prevention portion.
- the motor 300 includes a load-side bearing 321 that supports the load-side of the shaft 15, a metal bracket 6 that holds the load-side bearing 321 and a resin member 323 as a creep prevention portion. doing.
- the resin member 323 is arranged between the outer peripheral surface 321f of the outer ring 321b of the bearing 321 on the load side and the inner peripheral surface 61a of the cylindrical portion 61 of the metal bracket 6.
- the resin member 323 is formed of, for example, a thermoplastic elastomer.
- the resin member 323 is preliminarily fixed to the outer ring 321b by being integrated with the outer ring 321b by, for example, integral molding.
- the resin member 323 may be fixed to the outer ring 321b in advance with an adhesive or the like. Further, the resin member 323 may be fixed to the metal bracket 6 in advance.
- the coefficient of friction between the resin member 323 and the cylindrical portion 61 is larger than the coefficient of friction between the outer ring 321b and the cylindrical portion 61. That is, when the resin member 323 is arranged between the outer peripheral surface 321f of the outer ring 321b and the inner peripheral surface 61a of the cylindrical portion 61, the frictional resistance in the circumferential direction R1 between the outer ring 321b and the cylindrical portion 61 is increased. As a result, the outer ring 321b is less likely to rotate with respect to the cylindrical portion 61, so that it is possible to prevent the occurrence of creep in the bearing 321 on the load side.
- the resin member 323 that increases the frictional resistance in the circumferential direction R1 between the outer ring 321b and the cylindrical portion 61 is arranged.
- the outer ring 321b is less likely to rotate with respect to the cylindrical portion 61, so that it is possible to prevent the occurrence of creep in the bearing 321 on the load side.
- the third embodiment is the same as either the first or the second embodiment.
- FIG. 11 is an enlarged cross-sectional view showing the configuration around the bearing 321 on the load side of the electric motor 300A according to the modified example of the third embodiment.
- the same or corresponding components as those shown in FIG. 7 or 10 are designated by the same reference numerals as those shown in FIG. 7 or 10.
- the electric motor 300A is different from the electric motor according to any one of the first to third embodiments in the configuration of the creep prevention portion.
- the adhesive 323A is interposed between the outer ring 321b of the bearing 321 on the load side and the inner peripheral surface of the cylindrical portion 61 of the metal bracket 6.
- the outer peripheral surface 321f of the outer ring 321b and the inner peripheral surface 61a of the cylindrical portion 61 are fixed to each other by the adhesive 323A. This makes it difficult for the outer ring 321b to rotate with respect to the cylindrical portion 61.
- the adhesive 323A is interposed between the outer peripheral surface 321f of the outer ring 321b and the inner peripheral surface 61a of the cylindrical portion 61, and the outer ring 321b
- the outer peripheral surface 321f and the inner peripheral surface 61a of the cylindrical portion 61 are fixed to each other.
- the outer ring 321b is less likely to rotate with respect to the cylindrical portion 61, so that it is possible to prevent the occurrence of creep in the bearing 321 on the load side.
- FIG. 12A is an enlarged cross-sectional view showing the configuration around the bearing 400 on the load side of the motor 400 according to the fourth embodiment.
- FIG. 12B is a partial front view of the outer peripheral surface 421f of the outer ring 421b shown in FIG. 12A.
- components that are the same as or correspond to the components shown in FIG. 7 are designated by the same reference numerals as those shown in FIG.
- the electric motor 400 is different from the electric motor according to any one of the first to third embodiments in the configuration of the creep prevention portion.
- the motor 400 includes a load-side bearing 421 that supports the load-side of the shaft 15, a metal bracket 6 that holds the load-side bearing 421, and a creep prevention portion. It has an uneven surface 423 as a surface.
- the uneven surface 423 is formed on the outer peripheral surface 421f of the outer ring 421b.
- the uneven surface 423 is formed, for example, on the entire outer peripheral surface 421f in the axial direction.
- the uneven surface 423 may be formed on at least a part of the outer peripheral surface 421f.
- the uneven surface 423 has a convex portion 423 g and a concave portion 423 h.
- the uneven surface 423 is formed by, for example, shot blasting the outer peripheral surface 421f of the outer ring 421b.
- the surface roughness Ra of the uneven surface 423 on the outer peripheral surface 421f after processing is larger than the surface roughness Ra of the outer peripheral surface 421f before processing.
- the surface roughness Ra of the outer peripheral surface 421f before processing is, for example, 0.025 ⁇ m to 0.2 ⁇ m.
- the surface roughness Ra of the outer peripheral surface 421f after processing is, for example, 0.2 ⁇ m to 20 ⁇ m.
- the surface roughness Ra is the "arithmetic mean roughness" defined in JIS B0601: 2013.
- the coefficient of friction between the uneven surface 423 and the inner peripheral surface 61a of the cylindrical portion 61 is the friction between the outer peripheral surface 421f (that is, the surface other than the uneven surface 423) before processing and the inner peripheral surface 61a of the cylindrical portion 61. Greater than the coefficient. As a result, the frictional resistance in the circumferential direction R1 between the outer ring 421b and the cylindrical portion 61 increases.
- the uneven surface 423 that increases the frictional resistance in the circumferential direction R1 between the outer ring 421b and the cylindrical portion 61 is formed on the outer peripheral surface 421f of the outer ring 421b.
- the outer ring 421b is less likely to rotate with respect to the cylindrical portion 61, so that it is possible to prevent the occurrence of creep in the bearing 421 on the load side.
- the fourth embodiment is the same as any one of the first to third embodiments.
- FIG. 13 is an enlarged cross-sectional view showing the configuration around the bearing 521 on the load side of the motor 500 according to the fifth embodiment.
- the same or corresponding components as those shown in FIG. 7 are designated by the same reference numerals as those shown in FIG.
- the electric motor 500 is different from the electric motor according to any one of the first to fourth embodiments in that the creep prevention portion is configured.
- the motor 500 includes a load-side bearing 521 that supports the load-side of the shaft 15, a metal bracket 6 that holds the load-side bearing 521, and a metal bracket 6 and a load-side bearing 521. It has a preload spring 45 arranged between the bearings and a resin member 546 as a creep prevention portion.
- the resin member 546 is arranged between the bearing 521 on the load side and the preload spring 45.
- the resin member 546 is in contact with the preload spring 45 and the end surface 521i of the outer ring 521b.
- the preload spring 45 applies a force for pressing the end surface 521i of the outer ring 521b toward the mold stator 9 (see FIG. 1) via the resin member 546.
- the resin member 546 is formed of, for example, a thermoplastic elastomer.
- the resin member 546 is, for example, an annular member centered on the axis C1.
- the resin member 546 has a through hole 546a through which the shaft 15 penetrates.
- the coefficient of friction between the resin member 546 and the outer ring 521b is larger than the coefficient of friction between the outer ring 521b and the preload spring 45.
- the frictional resistance between the outer ring 521b and the preload spring 45 increases.
- the pressing force of the preload spring 45 is stabilized, so that the frictional resistance of the outer ring 521b in the circumferential direction R1 also increases between the outer ring 521b and the cylindrical portion 61. Therefore, it is possible to prevent the occurrence of creep in the bearing 521 on the load side, which makes it difficult for the outer ring 521b to rotate with respect to the cylindrical portion 61.
- the creep prevention portion arranged between the bearing 521 on the load side and the preload spring 45 is not limited to the resin member 546, but is another elastic body (for example, rubber) or an adhesive. It may be a member.
- a creep prevention portion for example, a resin member 546) that increases the frictional resistance between the outer ring 521b and the preload spring 45 between the outer ring 521b and the preload spring 45. ) Is placed.
- the frictional resistance in the circumferential direction R1 between the outer ring 521b and the cylindrical portion 61 also increases. Therefore, since it becomes difficult for the outer ring 521b to rotate with respect to the cylindrical portion 61, it is possible to prevent the occurrence of creep in the bearing 521 on the load side.
- the fifth embodiment is the same as any of the first to fourth embodiments.
- FIG. 14 is a configuration diagram showing a partial cross section and side surfaces of the motor 600 according to the sixth embodiment.
- components that are the same as or correspond to the components shown in FIG. 1 are designated by the same reference numerals as those shown in FIG.
- the motor 600 is different from the motor 100 according to the first embodiment in that it further has a second creep prevention portion for preventing creep in the bearing 622 on the counterload side.
- the electric motor 600 includes an annular elastic body 23 as a first creep prevention portion and a plurality of (two in FIG. 14) annular elastic bodies 623 and 624 as a second creep prevention portion. And have.
- the plurality of annular elastic bodies 623 and 624 are arranged between the outer ring 622b of the bearing 622 and the holding portion 56b of the mold resin portion 56.
- Each of the plurality of annular elastic bodies 623 and 624 is a rubber containing, for example, a thermosetting elastomer.
- each of the plurality of annular elastic bodies 623 and 624 is, for example, an O-ring, similarly to the annular elastic body 23.
- the number of annular elastic bodies 623 and 624 arranged between the outer ring 622b and the holding portion 56b is not limited to two, and may be one or more.
- the sixth embodiment is the same as any one of the first to fifth embodiments.
- FIG. 15 is a configuration diagram showing a partial cross section and side surfaces of the electric motor 600A according to the first modification of the sixth embodiment.
- components that are the same as or correspond to the components shown in FIG. 14 are designated by the same reference numerals as those shown in FIG.
- the motor 600A relates to the sixth embodiment in terms of the material of the holding portion 82 that holds the bearing 622 on the load side and the number of annular elastic bodies 624 arranged between the bearing 622 and the holding portion 82. It is different from the electric motor 600.
- the motor 600A has a cover member 80 fixed to the end portion of the mold resin portion 56 on the ⁇ z axis side.
- the cover member 80 is made of metal.
- the cover member 80 is formed of, for example, a hot-dip galvanized aluminum-magnesium alloy plated steel sheet. Fused zinc-aluminum-magnesium alloy plated steel sheet has good workability because it can be pressed, so it is easy to obtain high dimensional accuracy and high thermal conductivity compared to general resins such as BMC and PBT. ..
- the cover member 80 has a flange portion 81 fixed to the mold resin portion 56 and a holding portion 82 located radially inside the flange portion 81.
- the holding portion 82 holds the bearing 622. That is, in the first modification of the sixth embodiment, the holding portion 82 as the second holding portion for holding the bearing 622 on the counterload side is formed of metal.
- FIG. 16 is an enlarged cross-sectional view showing the configuration around the bearing 622 of the motor 600A shown in FIG.
- the bearing 622 includes an inner ring 622a that supports the end portion 15b of the shaft 15 on the ⁇ z axis side via an insulating sleeve 60, and an outer ring 622b that is fixed to the holding portion 82 by clearance fitting. It has a ball 622c as a rolling element arranged between the inner ring 622a and the outer ring 622b.
- the flange portion 81 has a first surface 81a in contact with the axial end surface of the end portion 556b on the ⁇ z axis side of the mold resin portion 56, and a second surface 81b in contact with the inner surface of the end portion 556b. ..
- the holding portion 82 has a cylindrical surface 83, a contact surface 84, and a separation surface 85.
- the cylindrical surface 83 faces a part of the outer peripheral surface 622f of the outer ring 622b in the radial direction.
- the contact surface 84 is in contact with the end surface 622g of the outer ring 622b on the ⁇ z axis side in the axial direction.
- the separation surface 85 is separated from the inner ring 622a and the shaft 15 of the bearing 622 in the radial direction of the contact surface 84 and is separated from the shaft 15 on the ⁇ z axis side. That is, the holding portion 82 abuts on the outer ring 622b, but does not abut on the inner ring 622a and the shaft 15. As a result, the shaft current flowing through the shaft 15 is suppressed from passing through the ball 622c via the holding portion 82 and the inner ring 622a.
- An annular elastic body 624 is arranged between the outer peripheral surface 622f of the outer ring 622b and the cylindrical surface 83 of the holding portion 82.
- the annular elastic body 624 is arranged in the groove portion 622d formed on the outer peripheral surface 622f of the outer ring 622b.
- the groove portion 622d is formed on the outer peripheral surface 622f on the ⁇ z axis side with reference to the axial position of the center of the ball 622c.
- the coefficient of friction between the annular elastic body 624 and the cylindrical surface 83 is larger than the coefficient of friction between the outer peripheral surface 622f and the cylindrical surface 83. That is, when the annular elastic body 624 is arranged between the outer peripheral surface 622f and the cylindrical surface 83, the frictional resistance in the circumferential direction R1 between the outer ring 622b and the cylindrical surface 83 of the holding portion 82 increases. As a result, the outer ring 622b is less likely to rotate with respect to the holding portion 82, and creep in the bearing 622 can be prevented from occurring.
- both the bearing holding portion that holds the bearing 21 on the load side and the bearing holding portion that holds the bearing 622 on the non-load side are formed of metal. In this case, it is possible to prevent the occurrence of creep in each of the bearing 21 on the load side and the bearing 622 on the non-load side.
- FIG. 17 is a configuration diagram showing a partial cross section and side surfaces of the electric motor 600B according to the second modification of the sixth embodiment.
- components that are the same as or correspond to the components shown in FIG. 15 are designated by the same reference numerals as those shown in FIG.
- the motor 600B has the sixth embodiment in terms of the material of the holding portion 556c that holds the bearing 21 on the load side and the number of annular elastic bodies 23 and 24 arranged between the bearing 21 and the holding portion 556c. It is different from the electric motor 600A according to the first modification of the above.
- the mold stator 9 of the motor 600B has a mold resin portion 556 that covers the stator core 50.
- the mold resin portion 556 has a holding portion 556c as a first holding portion formed on the + z-axis side.
- the bearing 21 is held in the holding portion 556c. That is, in the second modification of the sixth embodiment, the bearing holding portion that holds the bearing 21 on the load side is made of resin.
- a preload spring 45 that applies a force that presses the end face of the outer ring 21b on the + z-axis side toward the mold stator 9 is arranged between the bearing 21 and the holding portion 556c.
- a plurality of (two in FIG. 17) annular elastic bodies 23 and 24 are arranged between the outer ring 21b of the bearing 21 and the holding portion 556c.
- the coefficient of friction between the annular elastic bodies 23, 24 and the holding portion 556c is larger than the coefficient of friction between the outer ring 21b and the holding portion 556c. That is, when the annular elastic bodies 23 and 24 are arranged between the outer ring 21b and the holding portion 556c, the frictional resistance in the circumferential direction R1 between the outer ring 21b and the holding portion 556c increases. As a result, the outer ring 21b is less likely to rotate with respect to the holding portion 556c, so that the occurrence of creep in the bearing 21 can be prevented.
- the number of annular elastic bodies 23 and 24 arranged between the outer ring 21b and the holding portion 556c is not limited to two, and may be one or more.
- the bearing holding portion that holds the bearing 21 on the load side is formed of resin, and the bearing holding portion that holds the bearing 622 on the counterload side is formed.
- the bearing holding portion that holds the bearing 622 on the counterload side is formed.
- the holding portion 556c for holding the bearing 21 on the load side is formed of resin, and when creep occurs in the bearing 21, the holding portion 556c is likely to be worn. According to the motor 600B according to the second modification of the sixth embodiment, the occurrence of creep in the bearing 21 is prevented, so that the wear of the holding portion 556c can be prevented.
- FIG. 18 is a configuration diagram showing a partial cross section and side surfaces of the electric motor 600C according to the third modification of the sixth embodiment.
- components that are the same as or correspond to the components shown in FIG. 14 are designated by the same reference numerals as those in FIG.
- the motor 600C is implemented in terms of the material of the bearing holding portion (resin bracket 90 described later) that holds the bearing 21, and the number of annular elastic bodies 23 and 24 arranged between the bearing 21 and the holding portion 556c. It is different from the electric motor 600 according to the sixth embodiment.
- the motor 600C has a resin bracket 90 as a first holding portion for holding the bearing 21. It is fixed to the opening 56a of the mold resin portion 56.
- the resin bracket 90 is fixed to the opening 56a by press fitting, for example.
- the resin bracket 90 is made of, for example, a BMC resin.
- the resin bracket 90 has a cylindrical portion 91 that faces the outer ring 21b of the bearing 21 in the radial direction.
- the cylindrical portion 91 extends substantially parallel to the axis C1.
- a preload spring 45 that applies a force that presses the end face of the outer ring 21b on the + z-axis side toward the mold stator 9 is arranged between the bearing 21 and the resin bracket 90.
- the shape of the resin bracket 90 is not limited to the shape shown in FIG. 18, and may be any other shape as long as it has a cylindrical portion 91 that faces the outer ring 21b in the radial direction.
- a plurality of (two in FIG. 18) annular elastic bodies 23 and 24 are arranged between the outer ring 21b of the bearing 21 and the cylindrical portion 91 of the resin bracket 90. This prevents creep from occurring in the bearing 21.
- the number of annular elastic bodies 23 and 24 arranged between the outer ring 21b and the cylindrical portion 91 is not limited to two, and may be one or more.
- the bearing holding portion for holding the bearing 21 on the load side and the counterload When the bearing holding portion for holding the side bearing 622 is formed of resin, it is possible to prevent creep from occurring in each of the load side bearing 21 and the counterload side bearing 622.
- Air conditioner 700 to which the motor according to any one of the above-described embodiments 1 to 6 is applied will be described.
- the air conditioner 700 to which the motor 100 according to the first embodiment is applied will be described as an example.
- FIG. 19 is a diagram showing the configuration of the air conditioner 700.
- the air conditioner 700 has an outdoor unit 701, an indoor unit 702, and a refrigerant pipe 703 that connects the outdoor unit 701 and the indoor unit 702.
- an operation such as a cooling operation in which cold air is blown from the indoor unit 702 or a heating operation in which warm air is blown can be performed.
- the outdoor unit 701 has an outdoor blower 150 as a blower, a frame 707 that supports the outdoor blower 150, and a housing 708 that covers the outdoor blower 150 and the frame 707.
- FIG. 20 is a cross-sectional view showing the configuration of the outdoor unit 701 shown in FIG.
- the outdoor blower 150 of the outdoor unit 701 has an electric motor 100 attached to the frame 707 and an impeller 704 attached to the shaft 15 of the electric motor 100.
- the impeller 704 has a boss portion 705 fixed to the shaft 15 and blades 706 provided on the outer periphery of the boss portion 705.
- the impeller 704 is, for example, a propeller fan.
- the impeller 704 rotates and an air flow is generated.
- the outdoor blower 150 can blow air.
- the heat released when the refrigerant compressed by the compressor (not shown) is condensed by the condenser (not shown) is blown to the outside by the blower of the outdoor blower 150. discharge.
- the electric motor according to any one of the first to sixth embodiments may be provided in a blower other than the outdoor blower 150 of the outdoor unit 701 (for example, the indoor blower of the indoor unit 702). Further, the electric motor according to any one of the first to sixth embodiments may be provided in a home electric appliance other than the air conditioner.
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- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Motor Or Generator Frames (AREA)
- Control Of Direct Current Motors (AREA)
Abstract
Description
〈電動機〉
図1は、実施の形態1に係る電動機100の部分断面及び側面を示す構成図である。電動機100は、回転子1と、固定子としてのモールド固定子9とを有している。回転子1は、モールド固定子9の内側に配置されている。つまり、電動機100は、インナーロータ型の電動機である。
次に、図1及び2を用いて、モールド固定子9の構成について、説明する。図2は、図1に示される回転子1及びモールド固定子9をA2-A2線で切断した断面図である。なお、図2では、モールド固定子9のモールド樹脂部56の図示が省略されている。
次に、図2及び3を用いて、回転子1の構成について説明する。図3は、図2に示される回転子1の構成を示す拡大断面図である。図2及び3に示されるように、回転子1は、回転子鉄心10と、シャフト15とを有している。
次に、図4を用いて、金属ブラケット6の構成について説明する。図4は、金属ブラケット6の構成を示す断面図である。金属ブラケット6は、例えば、亜鉛メッキ鋼板によって形成されている。なお、金属ブラケット6は、亜鉛メッキ鋼板に限らず、アルミニウム合金などの他の金属材料によって形成されていてもよい。
以上に説明した実施の形態1に係る電動機100によれば、以下に示す効果が得られる。
図9は、実施の形態2に係る電動機200の負荷側の軸受221周辺の構成を示す拡大断面図である。図9において、図7に示される構成要素と同一又は対応する構成要素には、図7に示される符号と同じ符号が付されている。実施の形態2に係る電動機200は、負荷側の軸受221の外輪221bと金属ブラケット6の円筒部61との間に、複数の環状弾性体23,24が配置されている点で実施の形態1に係る電動機100と相違する。
図10は、実施の形態3に係る電動機300の負荷側の軸受321周辺の構成を示す拡大断面図である。図10において、図7に示される構成要素と同一又は対応する構成要素には、図7に示される符号と同じ符号が付されている。電動機300は、クリープ防止部の構成の点で、実施の形態1又は2に係る電動機100,200と相違する。
図11は、実施の形態3の変形例に係る電動機300Aの負荷側の軸受321周辺の構成を示す拡大断面図である。図11において、図7又は10に示される構成要素と同一又は対応する構成要素には、図7又は10に示される符号と同じ符号が付されている。電動機300Aは、クリープ防止部の構成の点で、実施の形態1~3のいずれかに係る電動機と相違する。
図12(A)は、実施の形態4に係る電動機400の負荷側の軸受400周辺の構成を示す拡大断面図である。図12(B)は、図12(A)に示される外輪421bの外周面421fの部分正面図である。図12(A)において、図7に示される構成要素と同一又は対応する構成要素には、図7に示される符号と同じ符号が付されている。電動機400は、クリープ防止部の構成の点で、実施の形態1~3のいずれかに係る電動機と相違する。
図13は、実施の形態5に係る電動機500の負荷側の軸受521周辺の構成を示す拡大断面図である。図13において、図7に示される構成要素と同一又は対応する構成要素には、図13に示される符号と同じ符号が付されている。電動機500は、クリープ防止部の構成の点で、実施の形態1~4のいずれかに係る電動機と相違する。
図14は、実施の形態6に係る電動機600の部分断面及び側面を示す構成図である。図14において、図1に示される構成要素と同一又は対応する構成要素には、図1に示される符号と同じ符号が付されている。電動機600は、反負荷側の軸受622におけるクリープを防止する第2のクリープ防止部を更に有している点で、実施の形態1に係る電動機100と相違する。
次に、実施の形態6の変形例1について説明する。図15は、実施の形態6の変形例1に係る電動機600Aの部分断面及び側面を示す構成図である。図15において、図14に示される構成要素と同一又は対応する構成要素には、図14に示される符号と同じ符号が付されている。電動機600Aは、負荷側の軸受622を保持する保持部82の材質の点、及び軸受622と保持部82との間に配置される環状弾性体624の数の点で、実施の形態6に係る電動機600と相違する。
次に、実施の形態6の変形例2について説明する。図17は、実施の形態6の変形例2に係る電動機600Bの部分断面及び側面を示す構成図である。図17において、図15に示される構成要素と同一又は対応する構成要素には、図15に示される符号と同じ符号が付されている。電動機600Bは、負荷側の軸受21を保持する保持部556cの材質の点、及び軸受21と保持部556cとの間に配置される環状弾性体23,24の数の点で、実施の形態6の変形例1に係る電動機600Aと相違する。
次に、実施の形態6の変形例3について説明する。図18は、実施の形態6の変形例3に係る電動機600Cの部分断面及び側面を示す構成図である。図18において、図14に示される構成要素と同一又は対応する構成要素には、図14と同じ符号が付されている。電動機600Cは、軸受21を保持する軸受保持部(後述する樹脂ブラケット90)の材質の点、及び軸受21と保持部556cとの間に配置される環状弾性体23,24の数の点で実施の形態6に係る電動機600と相違する。
次に、上述した実施の形態1~6のいずれかに係る電動機が適用される空気調和装置700について説明する。なお、以下の説明では、実施の形態1に係る電動機100が適用された空気調和装置700を例にして説明する。
Claims (20)
- 固定子と、
回転軸を有するコンシクエントポール型の回転子と、
前記回転軸を支持する転がり軸受である軸受と、
前記固定子に固定され、前記軸受の外輪を保持する軸受保持部と、
前記外輪と前記軸受保持部との間に配置され、前記外輪と前記軸受保持部との間の前記外輪の周方向の摩擦抵抗を上げるクリープ防止部と
を有する電動機。 - 前記クリープ防止部は、前記外輪の外周面と前記軸受保持部の内周面との間に配置された弾性部材を有する
請求項1に記載の電動機。 - 前記外輪は、前記外周面に形成された溝部を有し、
前記弾性部材は、前記溝部内に配置されている
請求項2に記載の電動機。 - 前記弾性部材は、Oリングである
請求項2又は3に記載の電動機。 - 前記クリープ防止部は、前記外輪の外周面と前記軸受保持部の内周面との間に配置された樹脂部材を有する
請求項1から4のいずれか1項に記載の電動機。 - 前記クリープ防止部は、前記外輪の外周面と前記軸受保持部の内周面との間に配置された接着剤を有する
請求項1から5のいずれか1項に記載の電動機。 - 前記クリープ防止部は、前記外輪の外周面と前記軸受保持部の内周面との間において、前記軸受の転動体の中心を基準に前記回転軸の軸方向一方側にずれた位置に配置されている
請求項1から6のいずれか1項に記載の電動機。 - 前記軸受保持部は、前記回転軸の径方向において前記外輪と対向する円筒部と、前記円筒部から前記径方向の内側に延びる底面部とを有し、
前記クリープ防止部は、前記外輪の外周面と前記円筒部の内周面との間において、前記軸受の転動体の軸方向の中心位置を基準に前記底面部側に配置されている
請求項1から7のいずれか1項に記載の電動機。 - 前記クリープ防止部は、前記外輪の外周面に形成され、前記軸受保持部の内周面に接する凹凸面を有する
請求項1から8のいずれか1項に記載の電動機。 - 前記凹凸面と前記軸受保持部の内周面との間の第1の摩擦係数は、前記外輪の前記凹凸面以外の面と前記軸受保持部の内周面との間の第2の摩擦係数よりも大きい
請求項9に記載の電動機。 - 前記軸受と前記軸受保持部との間に配置され、前記回転軸の軸方向における前記外輪の端面を前記固定子に向けて押し付ける力を付与する予圧バネを更に有し、
前記クリープ防止部は、前記外輪の前記端面と前記予圧バネとの間に配置されている部材を有する
請求項1から10のいずれか1項に記載の電動機。 - 前記軸受は、前記回転軸における負荷側の部分又は反負荷側の部分を支持する
請求項1から11のいずれか1項に記載の電動機。 - 前記軸受保持部は、金属及び樹脂の少なくとも一方から形成されている
請求項1から12のいずれか1項に記載の電動機。 - 前記軸受は、前記固定子を挟んで互いに反対側に配置された第1の軸受と第2の軸受とを含み、
前記軸受保持部は、前記第1の軸受の第1の外輪を保持する第1の保持部と、前記第2の軸受の第2の外輪を保持する第2の保持部とを含み、
前記クリープ防止部は、前記第1の外輪と前記第1の保持部との間の前記第1の外輪の前記周方向の前記摩擦抵抗を上げる第1のクリープ防止部と、前記第2の外輪と前記第2の保持部との間の前記第2の外輪の前記周方向の前記摩擦抵抗を上げる第2のクリープ防止部とを含む
請求項1から13のいずれか1項に記載の電動機。 - 前記第1の保持部は、金属から形成されていて、
前記第2の保持部は、樹脂から形成されている
請求項14に記載の電動機。 - 前記第1の保持部は、亜鉛メッキ鋼板によって形成されていて、
前記第2の保持部は、BMC樹脂によって形成されている
請求項14又は15に記載の電動機。 - 前記第1の保持部及び前記第2の保持部はいずれも、金属から形成されている
請求項14に記載の電動機。 - 前記第1の保持部及び前記第2の保持部はいずれも、樹脂から形成されている
請求項14に記載の電動機。 - 請求項1から18のいずれか1項に記載の電動機と、
前記電動機によって回転する羽根車と
を有する送風機。 - 室外機と、
前記室外機に冷媒配管によって接続された室内機と
を有し、
前記室外機及び前記室内機の少なくとも一方は、請求項19に記載の送風機を有する
空気調和装置。
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000156952A (ja) * | 1998-11-17 | 2000-06-06 | Mitsubishi Electric Corp | 回転電機 |
JP2003309953A (ja) | 2002-04-15 | 2003-10-31 | Denso Corp | インナーロータ型回転電機の永久磁石ロータ |
JP2007255515A (ja) * | 2006-03-22 | 2007-10-04 | Ntn Corp | 焼結含油軸受及びモータ |
JP2008175337A (ja) * | 2007-01-22 | 2008-07-31 | Matsushita Electric Ind Co Ltd | 軸受構造 |
JP2012235671A (ja) * | 2011-04-20 | 2012-11-29 | Asmo Co Ltd | モータ |
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JP2000192979A (ja) * | 1998-12-24 | 2000-07-11 | Nsk Ltd | 転がり軸受 |
CN109314418A (zh) * | 2016-06-22 | 2019-02-05 | 三菱电机株式会社 | 交替极型转子、电动机及空气调节机 |
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Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000156952A (ja) * | 1998-11-17 | 2000-06-06 | Mitsubishi Electric Corp | 回転電機 |
JP2003309953A (ja) | 2002-04-15 | 2003-10-31 | Denso Corp | インナーロータ型回転電機の永久磁石ロータ |
JP2007255515A (ja) * | 2006-03-22 | 2007-10-04 | Ntn Corp | 焼結含油軸受及びモータ |
JP2008175337A (ja) * | 2007-01-22 | 2008-07-31 | Matsushita Electric Ind Co Ltd | 軸受構造 |
JP2012235671A (ja) * | 2011-04-20 | 2012-11-29 | Asmo Co Ltd | モータ |
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