WO2015193963A1 - 圧縮機、冷凍サイクル装置、および空気調和機 - Google Patents
圧縮機、冷凍サイクル装置、および空気調和機 Download PDFInfo
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- WO2015193963A1 WO2015193963A1 PCT/JP2014/066008 JP2014066008W WO2015193963A1 WO 2015193963 A1 WO2015193963 A1 WO 2015193963A1 JP 2014066008 W JP2014066008 W JP 2014066008W WO 2015193963 A1 WO2015193963 A1 WO 2015193963A1
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- rotor
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- 239000003507 refrigerant Substances 0.000 claims abstract description 17
- 230000006835 compression Effects 0.000 claims abstract description 15
- 238000007906 compression Methods 0.000 claims abstract description 15
- 238000005057 refrigeration Methods 0.000 claims description 16
- 238000010586 diagram Methods 0.000 description 30
- 230000004323 axial length Effects 0.000 description 21
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- 230000000694 effects Effects 0.000 description 13
- 230000009467 reduction Effects 0.000 description 7
- 238000003780 insertion Methods 0.000 description 5
- 230000037431 insertion Effects 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000004804 winding Methods 0.000 description 4
- 229910001369 Brass Inorganic materials 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 3
- 239000010951 brass Substances 0.000 description 3
- 230000006837 decompression Effects 0.000 description 3
- 230000005484 gravity Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000011218 segmentation Effects 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 230000005347 demagnetization Effects 0.000 description 2
- 230000004907 flux Effects 0.000 description 2
- 239000011521 glass Substances 0.000 description 2
- 239000000696 magnetic material Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
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- 238000010030 laminating Methods 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/02—Compressor arrangements of motor-compressor units
- F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- 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
- H02K1/12—Stationary parts of the magnetic circuit
- H02K1/14—Stator cores with salient poles
- H02K1/146—Stator cores with salient poles consisting of a generally annular yoke with salient poles
-
- 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
-
- 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
- H02K1/2753—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 or groups of magnets arranged with alternating polarity
- H02K1/276—Magnets embedded in the magnetic core, e.g. interior permanent magnets [IPM]
-
- 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
- H02K21/16—Synchronous motors having permanent magnets; Synchronous generators having permanent magnets with stationary armatures and rotating magnets with magnets rotating within the armatures having annular armature cores with salient poles
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
- H02K7/075—Means for converting reciprocating motion into rotary motion or vice versa using crankshafts or eccentrics
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/12—Vibration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/13—Noise
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/13—Vibrations
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K2201/00—Specific aspects not provided for in the other groups of this subclass relating to the magnetic circuits
- H02K2201/03—Machines characterised by aspects of the air-gap between rotor and stator
-
- 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
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
Definitions
- the present invention relates to a compressor, a refrigeration cycle apparatus, and an air conditioner.
- the balance weight has a large specific gravity, and a non-magnetic material is generally used for the balance weight because it does not reduce the magnetic force of the motor. Therefore, the conventional compressor represented by the above-mentioned Patent Document 1 has a problem that it cannot meet the need to reduce vibration and noise during rotation of the rotor without using a balance weight.
- the present invention has been made in view of the above, and an object thereof is to obtain a compressor, a refrigeration cycle apparatus, and an air conditioner that can suppress vibration while suppressing cost.
- the present invention is configured such that the axis of the rotation shaft that transmits the rotation of the rotor to the compression unit that compresses the refrigerant is offset from the radial center of the rotor,
- the rotor has a first portion located on a direction side from the axial center toward the radial center of the rotor with respect to a radial center of the rotor, and a direction from the radial center of the rotor toward the axial center.
- the magnetic force of the first portion is stronger than the magnetic force of the second portion.
- FIG. 1 is a cross-sectional view of a compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a cross-sectional view of the rotor shown in FIG.
- FIG. 3 is a view for explaining a first portion and a second portion of the rotor shown in FIG. 2.
- FIG. 4 is a side view of the rotor.
- FIG. 5 is a cross-sectional view of the rotor shown in FIG.
- FIG. 6 is a cross-sectional view of a motor used in a conventional compressor.
- FIG. 7 is a cross-sectional view of the motor shown in FIG.
- FIG. 8 is a diagram illustrating a first configuration example in which the magnetic force of the magnet provided in the rotor of FIG. 2 is changed.
- FIG. 9 is a diagram illustrating a second configuration example in which the magnetic force of the magnet provided in the rotor of FIG. 2 is changed.
- FIG. 10 is a diagram illustrating an example in which the circumferential width of the magnet provided in the rotor of FIG. 2 is changed.
- FIG. 11 is a diagram showing an example in which the radial width of the magnet provided in the rotor of FIG. 2 is changed.
- 12 is a diagram showing an example in which the axial length of the magnet provided in the rotor of FIG. 2 is changed.
- FIG. 13 is a cross-sectional view of the first divided rotor used in the compressor according to Embodiment 2 of the present invention.
- FIG. 10 is a diagram illustrating an example in which the circumferential width of the magnet provided in the rotor of FIG. 2 is changed.
- FIG. 11 is a diagram showing an example in which the radial width of the magnet provided in the rotor of FIG. 2 is changed.
- 12 is a diagram showing an
- FIG. 14 is a cross-sectional view of a second divided rotor used in the compressor according to Embodiment 2 of the present invention.
- 15 is a side view of the first divided rotor of FIG. 13 and the second divided rotor of FIG.
- FIG. 16 is a side view of a conventional rotor having two balance weights.
- FIG. 17 is a side view of a plurality of divided rotors divided into three in the axial direction of the rotating shaft.
- 18 is a cross-sectional view of the divided rotor located at the center in the axial direction of FIG.
- FIG. 19 is a diagram illustrating a configuration example in which the magnetic force of the magnet provided in the divided rotor of FIG. 13 is changed.
- FIG. 20 is a diagram illustrating a configuration example in which the magnetic force of the magnet provided in the split rotor of FIG. 14 is changed.
- FIG. 21 is a side view of the divided rotor shown in FIGS. 19 and 20.
- FIG. 22 is a diagram illustrating an example in which the axial length of the magnet provided in each divided rotor in FIG. 15 is changed.
- FIG. 23 is a diagram illustrating an example in which the circumferential width of the magnet provided in the divided rotor of FIG. 13 is changed.
- FIG. 24 is a diagram illustrating an example in which the circumferential width of the magnet provided in the divided rotor of FIG. 14 is changed.
- FIG. 25 is a diagram illustrating an example in which the radial width of the magnet provided in the split rotor of FIG.
- FIG. 26 is a diagram illustrating an example in which the radial width of the magnet provided in the divided rotor of FIG. 14 is changed.
- FIG. 27 is a side view of the divided rotor shown in FIGS. 25 and 26.
- FIG. 28 is a diagram illustrating an example in which the position of the magnet insertion hole of the divided rotor in FIG. 13 is changed.
- FIG. 29 is a diagram illustrating an example in which the position of the magnet insertion hole of the split rotor in FIG. 14 is changed.
- FIG. 30 is a side view of the divided rotor shown in FIGS. 28 and 29.
- FIG. 31 is a diagram illustrating a configuration example of a refrigeration cycle apparatus equipped with the compressor according to Embodiments 1 and 2 of the present invention.
- FIG. 1 is a cross-sectional view of a compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a cross-sectional view of the rotor shown in FIG.
- FIG. 3 is a view for explaining a first portion and a second portion of the rotor shown in FIG. 2.
- FIG. 4 is a side view of the rotor.
- FIG. 5 is a cross-sectional view of the rotor shown in FIG.
- FIG. 6 is a cross-sectional view of a motor used in a conventional compressor.
- FIG. 7 is a cross-sectional view of the motor shown in FIG.
- a motor 22 and a compression unit 40 are provided on the frame 16 of the compressor 11 shown in FIG.
- the motor 22 includes a stator 24, a rotor 1, and a rotating shaft 2, and is, for example, a brushless DC motor.
- the stator 24 includes a winding 18, an insulating portion 17, and a stator core 23, and the rotating shaft 2 is disposed near the center of the stator core 23.
- the motor 22 is used as the electric element of the hermetic compressor 11, but the motor 22 can also be applied as an electric element of any device other than the compressor 11.
- the compression unit 40 includes a cylinder 42 provided in a vertically stacked state, a piston 43 into which the rotating shaft 2 rotated by the motor 22 is inserted, and a pair of upper and lower members into which the rotating shaft 2 is inserted and closes the axial end surface of the cylinder 42.
- Frame upper frame 46 and lower frame 45
- an upper discharge muffler 41 attached to the upper frame 46
- a lower discharge muffler 44 attached to the lower frame 45.
- the frame 16 is formed into a cylindrical shape by drawing a steel plate having a predetermined thickness, and refrigeration oil (not shown) that lubricates the sliding portions of the compression unit 40 is stored at the bottom of the frame 16.
- the rotor 1 is disposed via gaps G1 and G2 (see FIG. 7) on the inner diameter side of the stator core 23.
- the rotating shaft 2 is held in a rotatable state by an upper frame 46 and a lower frame 45 provided at the lower portion of the compressor 11.
- the stator core 23 is held on the inner peripheral portion of the frame 16 by shrink fitting, for example. Electric power from the glass terminal 14 fixed to the frame 16 is supplied to the winding 18 wound around the stator core 23.
- FIG. 7 shows a stator core 23 disposed inside the frame 16, a rotor 1 disposed on an inner diameter portion of the stator core 23, and a rotating shaft 2.
- the rotor 1 includes four magnet groups (magnets) as an example. 3, magnet 4, magnet 5, and magnet 6) are inserted.
- the four magnets 3 to 6 are plate-shaped permanent magnets that are magnetized so that the north and south poles are alternately arranged.
- a shaft hole (not shown) is formed on the center side of the rotor 1, and the rotary shaft 2 is connected to the shaft hole by shrink fitting or press fitting.
- Gaps (G1, G2) are formed between the outer peripheral surface of the rotor 1 and the inner peripheral surface of the stator core 23, and a current having a frequency synchronized with the command rotational speed is supplied to the winding 18 (see FIG. 1) of the stator core 23. As a result, a rotating magnetic field is generated, and the rotor 1 rotates.
- the stator core 23 is formed by punching electromagnetic steel plates having a predetermined thickness into a predetermined shape and laminating a plurality of punched electromagnetic steel plates while caulking them.
- stator core 23 nine teeth 25 are provided in the stator core 23 and four magnets 3 to 6 are provided in the rotor 1.
- the number of teeth and the number of magnets are not limited to the illustrated example.
- an IPM (Interior Permanent Magnet) type motor 22 is used as an example, but a motor other than the IPM type may be used.
- the axis 2a of the rotating shaft 2 is deviated from the radial center of the rotor 1 (rotor center 1a). Further, the rotor 1 has a first portion C located on the direction side (left side in the example of FIG. 2) from the axis 2a toward the rotor center 1a with respect to the rotor center 1a, and the rotor 1 with respect to the rotor center 1a.
- the magnetic force of the first part C is the same as that of the second part D. It is configured to be stronger than the magnetic force.
- a plane that is perpendicular to the line 8 passing through the rotor center 1a and the axis 2a and that includes the rotor center 1a is a boundary. Let it be surface 7. At this time, the side opposite to the axis 2a side from the boundary surface 7 is the first portion C, and the axis 2a side from the boundary surface 7 is the second portion D.
- the axis 2a of the rotating shaft 2 is deviated from the rotor center 1a. Therefore, as shown in FIG. 7, the gap G1 on the first portion C side is narrower than the gap G2 on the second portion D side.
- the magnetic attractive force on the gap G1 side is larger than the magnetic attractive force on the gap G2 side, a non-uniform magnetic attractive force is generated in the rotor 1. Due to this non-uniform magnetic attractive force, it is possible to obtain the same effect as that of the rotor 1 (see FIG. 16) provided with balance weights 30 and 31, which will be described later. For example, it is possible to suppress vibrations that occur with the rotation of the eccentric part (not shown) of the compression part 40 shown in FIG. 1 and to reduce noise.
- the magnetic force of the first portion C of the rotor 1 is larger than the magnetic force of the second portion D, the magnetic attractive force generated between the first portion C and the stator core 23 is further increased, and the rotor 1 The magnetic attractive force attracted to the gap G1 side is further increased, and further noise reduction can be expected.
- FIG. 8 is a diagram showing a first configuration example in which the magnetic force (residual magnetic flux density Br) of the magnet provided in the rotor of FIG. 2 is changed.
- the magnetic force (Br) of the magnet 3 is higher than the magnetic forces (Br) of the other three magnets 4 to 6, whereby the magnetic force of the first portion C of the rotor 1 is the second magnetic force. It becomes higher than the magnetic force of the part D, and a non-uniform magnetic attractive force can be generated in the rotor 1.
- FIG. 9 is a diagram showing a second configuration example in which the magnetic force of the magnet provided in the rotor of FIG. 2 is changed.
- two magnets 3 and 6 are provided in the first portion C, and two magnets 4 and 5 are provided in the second portion D.
- the magnetic force (Br) of at least one of the magnets 3 and 6 is higher than the magnetic force (Br) of each of the magnets 4 and 5.
- increasing the magnetic force of the rotor 1 is not limited to the method of increasing the magnetic force (Br) of the magnet, but can also be realized by increasing the volume of the magnet. A specific example will be described below.
- FIG. 10 is a diagram showing an example in which the circumferential width of the magnet provided in the rotor of FIG. 2 is changed.
- the circumferential width W 1 of the magnet 3 provided in the first portion C is formed to be wider than the circumferential width W 2 of the other three magnets 4 to 6.
- the display of the circumferential widths of the magnet 4 and the magnet 6 is omitted.
- these circumferential widths are narrower than the circumferential width of the magnet 3.
- the volume of the magnet 3 becomes larger than the volume of each of the other three magnets 4 to 6, It leads to the high magnetic force of the 1st part C, and can anticipate the effect of noise reduction.
- FIG. 11 is a diagram showing an example in which the radial width of the magnet provided in the rotor of FIG. 2 is changed.
- the radial width T1 of the magnet 3 provided in the first portion C is formed to be wider than the radial width T2 of the other three magnets 4-6.
- the radial widths of the magnet 4 and the magnet 6 are not shown for convenience of explanation, but these radial widths are narrower than the radial width of the magnet 3.
- the volume of the magnet 3 becomes larger than the volume of each of the other three magnets 4 to 6, It leads to the high magnetic force of the 1st part C, and can anticipate the effect of noise reduction. Furthermore, the radial width T1 of the magnet 3, that is, the magnet width is increased, so that it is strong against a demagnetizing field, and an improvement in demagnetization resistance can be expected.
- FIG. 12 is a diagram showing an example in which the axial length of the magnet provided in the rotor of FIG. 2 is changed.
- the axial length L 1 of the magnet 3 provided in the first portion C is formed to be longer than the axial length L 2 of the other three magnets 4 to 6.
- the display of the magnet 4 and the magnet 6 is omitted, but the axial length thereof is shorter than the axial length L ⁇ b> 1 of the magnet 3.
- the volume of the magnet 3 is larger than the volume of each of the other three magnets 4 to 6, It leads to the high magnetic force of the 1st part C, and can anticipate the effect of noise reduction.
- the examples of increasing the magnetic force shown in FIGS. 10 to 12 can also be combined. By combining the examples, a higher effect can be obtained than in the case of increasing the magnetic force.
- the axis 2a of the rotating shaft 2 that transmits the rotation of the rotor 1 to the compression unit 40 that compresses the refrigerant is the center in the radial direction of the rotor 1 (rotor center).
- the rotor 1 is offset from 1a), and the rotor 1 has a first portion C located on the direction side from the axis 2a toward the rotor center 1a with respect to the rotor center 1a, and a direction from the rotor center 1a toward the axis 2a.
- the magnetic force of the first portion C is configured to be stronger than the magnetic force of the second portion D.
- FIG. FIG. 13 is a cross-sectional view of the first divided rotor used in the compressor according to Embodiment 2 of the present invention.
- FIG. 14 is a cross-sectional view of a second divided rotor used in the compressor according to Embodiment 2 of the present invention.
- 15 is a side view of the first divided rotor of FIG. 13 and the second divided rotor of FIG.
- the difference from the first embodiment is that the rotor is divided into two rotors divided in the axial direction of the rotary shaft 2, and each rotor has a magnetic force of the first portion C higher than that of the second portion D.
- the first portion C of one rotor (1-1) and the first portion C of the other rotor (1-2) are arranged symmetrically with respect to the axis 2a of the rotating shaft 2. It is a point.
- the same reference numerals are given to the same parts as those in the first embodiment, and the description thereof is omitted, and only different parts will be described here.
- the first divided rotor 1-1 is located on one side in the axial direction of the rotating shaft 2, and the second divided rotor 1-2 is located on the other side in the axial direction of the rotating shaft 2.
- the axis 2a is offset from the rotor center 1a, and the first divided rotor 1-1 is configured such that the magnetic force of the first portion C is stronger than the magnetic force of the second portion D ( (See FIG. 13).
- the left side of the boundary surface 7 is the first portion C
- the right side of the boundary surface 7 is the second portion D.
- the second divided rotor 1-2 is configured such that the magnetic force of the first portion C is stronger than the magnetic force of the second portion D (see FIG. 14).
- FIG. 14 In the example of FIG.
- the right side of the boundary surface 7 is the first portion C
- the left side of the boundary surface 7 is the second portion D.
- the first portion C of the first divided rotor 1-1 and the first portion C of the second divided rotor 1-2 are arranged at positions symmetrical with respect to the axis 2a of the rotating shaft 2. (See FIG. 15).
- the rotor center 1a of the first divided rotor 1-1 is offset to the left from the axis 2a
- the rotor center 1a of the second divided rotor 1-2 is offset to the right from the axis 2a.
- the magnetic force of each rotor is increased in the offset side portion, that is, the first portion C.
- FIG. 16 is a side view of a conventional rotor having two balance weights.
- the rotor 1 shown in FIG. 16 is the same as the rotor 1 shown in FIG. 6, and the position of the rotor center 1a coincides with the position of the shaft center 2a as described above. For this reason, the dimensions of the gaps G1 and G2 are constant, and the magnetic attractive force generated between the rotor 1 and the stator core 23 is uniform. Therefore, in order to suppress the deflection of the rotating shaft 2 due to the rotation of the eccentric portion of the compression portion 40, the balance weight 30 is provided at one end of the rotor 1, and the balance weight 31 is provided at the other end of the rotor 1. Must take measures.
- Each of the two balance weights has an unbalanced shape at the center of gravity, and is attached in a direction that cancels the deflection of the rotating shaft 2.
- the centrifugal force of the upper balance weight 30 works in the left direction
- the centrifugal force of the lower balance weight 31 works in the right direction.
- these balance weights 30 and 31 are desirably made of a material having a large specific gravity and impervious to magnetic flux generated from the rotor 1 (low permeability).
- brass is used.
- brass is expensive and a method that does not use brass is desirable for cost reduction.
- the first split rotor 1-1 shown in FIG. 15 has a relatively large leftward magnetic attractive force
- the second divided rotor 1-2 has a relatively right magnetic attractive force. Becomes larger. Therefore, it is possible not only to obtain the same effect as when the balance weights 30 and 31 are provided, but also to reduce the cost because it is not necessary to use an expensive material.
- FIG. 17 is a side view of a plurality of divided rotors divided into three in the axial direction of the rotating shaft.
- 18 is a cross-sectional view of the divided rotor located at the center in the axial direction of FIG.
- the third divided rotor 1-3 is formed such that the rotor center 1a coincides with the axis 2a.
- the third divided rotor 1-3 is disposed between the first divided rotor 1-1 and the second divided rotor 1-2.
- the number of divided rotors used in the compressor 11 of the present embodiment is not limited to two, and three divided cores as shown in FIG. 17 may be used, or four or more divided cores may be used. You may comprise using.
- FIG. 19 is a diagram showing a configuration example in which the magnetic force of the magnet provided in the divided rotor of FIG. 13 is changed.
- FIG. 20 is a diagram illustrating a configuration example in which the magnetic force of the magnet provided in the split rotor of FIG. 14 is changed.
- FIG. 21 is a side view of the divided rotor shown in FIGS. 19 and 20.
- the magnetic force (Br) of the magnet 3 is higher than the magnetic forces (Br) of the other three magnets 4 to 6, and thus the first divided rotor 1-1.
- the magnetic force of the first portion C becomes higher than the magnetic force of the second portion D, and a non-uniform magnetic attractive force can be generated in the first divided rotor 1-1.
- the magnetic force (Br) of the magnet 5 is higher than the magnetic forces (Br) of the other three magnets 3, 4, 6 and thus the second divided rotor 1
- the magnetic force of the first portion C of ⁇ 2 is higher than the magnetic force of the second portion D, and a non-uniform magnetic attractive force can be generated in the second divided rotor 1-2. Therefore, by arranging the first divided rotor 1-1 and the second divided rotor 1-2 as shown in FIG. 21, the same effect as the case where the balance weights 30 and 31 are provided can be expected.
- increasing the magnetic force of each divided rotor is not limited to the method of increasing the magnetic force (Br) of the magnet, but can also be realized by increasing the volume of the magnet. A specific example will be described below.
- FIG. 22 is a diagram showing an example in which the axial length of the magnet provided in each divided rotor in FIG. 15 is changed.
- the first divided rotor 1-1 is formed such that the axial length L1 of the magnet 3 provided in the first portion C is longer than the axial length L2 of the other three magnets 4-6. ing. Further, in the second divided rotor 1-2, the axial length L2 of the magnet 5 provided in the first portion C is longer than the axial length L1 of the other three magnets 3, 4, 6. It is formed as follows.
- the display of the magnet 4 and the magnet 6 is omitted, but the axial length of the magnet 4 and the magnet 6 provided in the first divided rotor 1-1 is the axial length of the magnet 3. It is assumed that it is shorter than L1. Similarly, it is assumed that the axial lengths of the magnet 4 and the magnet 6 provided in the second divided rotor 1-2 are shorter than the axial length L2 of the magnet 5.
- the volume of the magnet 3 provided in the first divided rotor 1-1 is the other three magnets 4 to 6.
- the volume of the magnet 5 provided in the second divided rotor 1-2 is larger than the volume of each of the other three magnets 3, 4, 6. This leads to an increase in the magnetic force of the first portion C of each divided rotor, and an effect of reducing noise can be expected.
- FIG. 23 is a diagram showing an example in which the circumferential width of the magnet provided in the divided rotor of FIG. 13 is changed.
- FIG. 24 is a diagram illustrating an example in which the circumferential width of the magnet provided in the divided rotor of FIG. 14 is changed.
- the circumferential width W1 of the magnet 3 provided in the first portion C is formed to be wider than the circumferential width W2 of the other three magnets 4-6.
- the circumferential width W2 of the magnet 5 provided in the first portion C is wider than the circumferential width W1 of the other three magnets 3, 4 and 6.
- the volume of the magnet 3 of the first divided rotor 1-1 is the same as that of the other three magnets 4 to 6, respectively.
- the volume of the magnet 5 of the second divided rotor 1-2 is larger than the volume of each of the other three magnets 3, 4, 6. This leads to an increase in the magnetic force of the first portion C of each divided rotor, and an effect of reducing noise can be expected.
- FIG. 25 is a diagram showing an example in which the radial width of the magnet provided in the divided rotor of FIG. 13 is changed.
- FIG. 26 is a diagram illustrating an example in which the radial width of the magnet provided in the divided rotor of FIG. 14 is changed.
- FIG. 27 is a side view of the divided rotor shown in FIGS. 25 and 26.
- the radial width T1 of the magnet 3 provided in the first portion C is formed to be wider than the radial width T2 of the other three magnets 4-6.
- the radial width T2 of the magnet 5 provided in the first portion C is wider than the radial width T1 of the other three magnets 3, 4, and 6. It is formed as follows.
- the volume of the magnet 3 of the first divided rotor 1-1 is the same as that of the other three magnets 4 to 6, respectively.
- the volume of the magnet 5 of the second divided rotor 1-2 is larger than the volume of each of the other three magnets 3, 4, 6. This leads to higher magnetic force in the first portion C, and the effect of reducing noise can be expected.
- the radial width T1 of the magnet 3 of the first divided rotor 1-1 and the radial width T2 of the magnet 5 of the second divided rotor 1-2 are increased, it is strong against a demagnetizing field and improves the demagnetization resistance. Can also be expected.
- FIG. 28 is a diagram showing an example in which the position of the magnet insertion hole of the divided rotor in FIG. 13 is changed.
- FIG. 29 is a diagram illustrating an example in which the position of the magnet insertion hole of the split rotor in FIG. 14 is changed.
- FIG. 30 is a side view of the divided rotor shown in FIGS. 28 and 29.
- the magnet insertion holes of the rotor core 1b are formed so that the lengths from the four magnets 3 to 6 to the axis 2a are equal to each other. Is formed.
- each divided rotor can share four magnets 3-6. That is, a magnet in which the magnet 3 of the first divided rotor 1-1 and the magnet 3 of the divided rotor 1-2 are integrally formed can be used, and the other three magnets 4 to 6 are the same. By using the four magnets 3 to 6 that are integrally formed, the number of magnets manufactured can be reduced.
- the integrally formed magnet 3 is manufactured such that its axial length is shorter than the length from one end of the first split rotor 1-1 to the other end of the second split rotor 1-2. Is done.
- the magnet 5 integrally formed is manufactured. Then, after inserting the magnet 3 and the magnet 5 into each divided core as shown in FIG.
- the magnet 3 is shifted to the axial end portion side of the first divided rotor 1-1, and the magnet 5 is moved to the second divided rotor 1. -2 Move to the axial end side.
- the compressor 11 is divided into two rotors in which the rotor is divided in the axial direction of the rotating shaft 2, and each rotor has the second portion having a magnetic force of the second portion C.
- the first portion C of the first divided rotor 1-1 and the first portion C of the second divided rotor 1-2 are stronger than the axis 2a of the rotating shaft 2. It is arranged in a symmetrical position. With this configuration, magnetic unbalance in different directions occurs in each divided rotor, and this magnetic unbalance acts in a direction that counteracts the force (moment) that swings around due to the rotation of the eccentric part, and vibration that occurs as the eccentric part rotates. Can be suppressed, and noise can be reduced.
- FIG. 31 is a diagram showing a configuration example of the refrigeration cycle apparatus 50 equipped with the compressors according to Embodiments 1 and 2 of the present invention.
- the refrigeration cycle apparatus 50 includes a compressor 11, a condenser 53, a decompression device 54, an evaporator 55, a temperature sensor 52, a bypass circuit 56, and a control circuit 51.
- a bypass circuit 56 configured by connecting the pressure reducing device 58 and the on-off valve 57 in series is interposed between the liquid refrigerant discharge port of the condenser 53 and the gas suction port of the compressor 11.
- the temperature sensor 52 is provided near the gas discharge port of the compressor 11 and detects the temperature of the refrigerant flowing through the gas discharge port. Further, the control circuit 51 controls the on-off valve 57 based on the detection result of the temperature sensor 52.
- the refrigeration cycle apparatus 50 is suitable for an air conditioner, for example.
- the refrigerant circulates in the order of the compressor 11, the condenser 53, the decompression apparatus 54, and the evaporator 55, and the refrigeration cycle returns to the compressor 11 again.
- the high-temperature and high-pressure refrigerant gas compressed in the compressor 11 is condensed by exchanging heat with air in the condenser 53 to become a liquid refrigerant.
- the liquid refrigerant expands in the decompression device 54 to become a low-temperature and low-pressure refrigerant gas, evaporates by exchanging heat with air in the evaporator 55 and is compressed again in the compressor 11 to become a high-temperature and high-pressure refrigerant gas.
- the refrigerant liquid that has not been completely evaporated by the evaporator 55 is separated, and the low-temperature and low-pressure refrigerant gas sucked into the compression unit 40 through the suction pipe 13 is compressed by the compression unit 40. .
- the refrigerant gas that has become high temperature and pressure in this manner is discharged from the discharge pipe 15 through a plurality of through holes (not shown) formed in the rotor 1 and gaps G1 and G2 (see FIG. 7).
- the configuration shown in the above embodiment is an example of the configuration of the present invention, and can be combined with another known technique, and a part thereof is omitted without departing from the gist of the present invention. Needless to say, it is possible to change the configuration.
- the present invention can be applied to a compressor, a refrigeration cycle apparatus, and an air conditioner, and is particularly useful as an invention capable of suppressing vibration while suppressing cost.
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Iron Core Of Rotating Electric Machines (AREA)
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Abstract
Description
図1は、本発明の実施の形態1に係る圧縮機の断面図である。図2は、図1に示されるロータの断面図である。図3は、図2に示されるロータの第1の部分と第2の部分を説明するための図である。図4は、ロータの側面図である。図5は、図2に示されるロータのB-B矢視断面図である。図6は、従来の圧縮機に用いられるモータの断面図である。図7は、図1に示されるモータのA-A矢視断面図である。
図13は、本発明の実施の形態2に係る圧縮機に用いられる第1の分割ロータの断面図である。図14は、本発明の実施の形態2に係る圧縮機に用いられる第2の分割ロータの断面図である。図15は、図13の第1の分割ロータと図14の第2の分割ロータの側面図である。実施の形態1との相違点は、ロータが回転軸2の軸方向に分割された2つのロータに区分され、各ロータは、第1の部分Cの磁力が第2の部分Dの磁力よりも強く、一方のロータ(1-1)の第1の部分Cと他方のロータ(1-2)の第1の部分Cは、回転軸2の軸心2aに対して対称な位置に配置されている点である。以下、実施の形態1と同一部分には同一符号を付してその説明を省略し、ここでは異なる部分についてのみ述べる。
Claims (7)
- 冷媒を圧縮する圧縮部にロータの回転を伝達する回転軸の軸心は、前記ロータの径方向中心からオフセットしており、
前記ロータは、前記ロータの径方向中心に対して、前記軸心から前記ロータの径方向中心へ向かう方向側に位置する第1の部分と、前記ロータの径方向中心から前記軸心へ向かう方向側に位置する第2の部分とに区分されるとき、前記第1の部分の磁力が、前記第2の部分の磁力よりも強い圧縮機。 - 前記ロータは、前記回転軸の軸方向に分割された2つのロータに区分され、
前記各ロータは、前記第1の部分の磁力が前記第2の部分の磁力よりも強く、
一方のロータの前記第1の部分と他方のロータの前記第1の部分は、前記回転軸の軸心に対して対称な位置に配置されている請求項1に記載の圧縮機。 - 前記一方のロータと前記他方のロータとの間には、前記ロータの径方向中心と前記回転軸の軸心とが一致するように形成されたロータが設けられている請求項2に記載の圧縮機。
- 前記第1の部分に配置される磁石の磁力は、前記第2の部分に配置される磁石の磁力よりも強い請求項1から3の何れか1項に記載の圧縮機。
- 前記第1の部分に配置される磁石の形状は、前記第1の部分の磁力が前記第2の部分の磁力よりも強くなるように、前記第2の部分に配置される磁石の形状と異なる請求項1から3の何れか1項に記載の圧縮機。
- 請求項1から5の何れか1項に記載の圧縮機を備えた冷凍サイクル装置。
- 請求項6に記載の冷凍サイクル装置を備えた空気調和機。
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US15/311,563 US10739046B2 (en) | 2014-06-17 | 2014-06-17 | Compressor, refrigeration cycle apparatus, and air conditioner |
CN201480079349.7A CN106464046B (zh) | 2014-06-17 | 2014-06-17 | 压缩机、制冷循环装置和空调机 |
JP2016528683A JP6195989B2 (ja) | 2014-06-17 | 2014-06-17 | 圧縮機、冷凍サイクル装置、および空気調和機 |
PCT/JP2014/066008 WO2015193963A1 (ja) | 2014-06-17 | 2014-06-17 | 圧縮機、冷凍サイクル装置、および空気調和機 |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2022085079A1 (ja) * | 2020-10-20 | 2022-04-28 | 三菱電機株式会社 | 回転子、電動機、圧縮機および冷凍サイクル装置 |
WO2023119455A1 (ja) * | 2021-12-21 | 2023-06-29 | 三菱電機株式会社 | 着磁方法、電動機、圧縮機および冷凍サイクル装置 |
Families Citing this family (3)
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---|---|---|---|---|
JP6297220B2 (ja) * | 2015-06-09 | 2018-03-20 | 三菱電機株式会社 | 圧縮機用電動機、圧縮機、および冷凍サイクル装置 |
CN113738645B (zh) * | 2020-05-29 | 2023-03-14 | 广东美芝精密制造有限公司 | 压缩机及空调系统 |
CN112003391B (zh) * | 2020-08-20 | 2021-07-20 | 珠海格力电器股份有限公司 | 定子铁芯、磁悬浮轴承、电机 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007018261A1 (ja) * | 2005-08-10 | 2007-02-15 | Namiki Seimitsu Houseki Kabushikikaisha | 直流モータ及び直流振動モータ |
JP2012137013A (ja) * | 2010-12-27 | 2012-07-19 | Daikin Industries Ltd | 圧縮機 |
WO2013073264A1 (ja) * | 2011-11-14 | 2013-05-23 | 株式会社安川電機 | モータおよびモータシステム |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DK170999B1 (da) | 1993-07-09 | 1996-04-15 | Smidth & Co As F L | Svingningskompensator til at modvirke vibrationer |
JP3689957B2 (ja) | 1996-01-16 | 2005-08-31 | ダイキン工業株式会社 | 永久磁石型dcモータ |
BR9904147A (pt) * | 1998-08-06 | 2000-09-05 | Mitsubishi Electric Corp | Compressor giratório, ciclo de refrigeração que utiliza o compressor, e refrigerador que utiliza o compressor |
JP3797122B2 (ja) * | 2001-03-09 | 2006-07-12 | 株式会社日立製作所 | 永久磁石式回転電機 |
JP2004215429A (ja) | 2003-01-07 | 2004-07-29 | Daikin Ind Ltd | 負荷トルク変動低減装置および電動機 |
KR100525412B1 (ko) | 2003-05-13 | 2005-11-02 | 엘지전자 주식회사 | 냉동 시스템의 압축기 제어 시스템 및 압축기의 제어방법 |
JP4285137B2 (ja) | 2003-07-23 | 2009-06-24 | ダイキン工業株式会社 | 流体機械 |
JP2006136126A (ja) * | 2004-11-05 | 2006-05-25 | Toyota Industries Corp | 電動モータ及び電動圧縮機 |
TWI348258B (en) * | 2006-11-10 | 2011-09-01 | Ind Tech Res Inst | A motor mechanism of dc frequency conversion of compressor |
BRPI0807008A2 (pt) * | 2007-02-06 | 2014-04-22 | Honda Motor Co Ltd | Motor, estrutura de rotor e máquina magnética |
CN102171909B (zh) * | 2008-11-19 | 2013-08-28 | 三菱电机株式会社 | 电动机的转子及电动机、送风机、压缩机 |
US8803395B2 (en) * | 2009-07-23 | 2014-08-12 | Daikin Industries, Ltd. | Rotor |
JP2011101544A (ja) | 2009-11-09 | 2011-05-19 | Daikin Industries Ltd | 回転電機 |
JP2012060799A (ja) * | 2010-09-10 | 2012-03-22 | Mitsubishi Electric Corp | 圧縮機用電動機及び圧縮機及び冷凍サイクル装置 |
JP2013034303A (ja) | 2011-08-02 | 2013-02-14 | Daikin Ind Ltd | 回転子及びその製造方法 |
GB2497721B (en) * | 2011-10-18 | 2017-07-05 | Control Techniques Ltd | Method of calibrating a drive system |
EP2602912A2 (en) * | 2011-12-05 | 2013-06-12 | Samsung Electronics Co., Ltd | Brushless motor |
JP5783898B2 (ja) * | 2011-12-28 | 2015-09-24 | 日立アプライアンス株式会社 | 永久磁石電動機及び圧縮機 |
CN103930677B (zh) * | 2012-01-11 | 2016-08-24 | 三菱电机株式会社 | 叶片型压缩机 |
JP2014110660A (ja) | 2012-11-30 | 2014-06-12 | Daikin Ind Ltd | モータ及び圧縮機 |
-
2014
- 2014-06-17 WO PCT/JP2014/066008 patent/WO2015193963A1/ja active Application Filing
- 2014-06-17 JP JP2016528683A patent/JP6195989B2/ja active Active
- 2014-06-17 US US15/311,563 patent/US10739046B2/en active Active
- 2014-06-17 CN CN201480079349.7A patent/CN106464046B/zh active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007018261A1 (ja) * | 2005-08-10 | 2007-02-15 | Namiki Seimitsu Houseki Kabushikikaisha | 直流モータ及び直流振動モータ |
JP2012137013A (ja) * | 2010-12-27 | 2012-07-19 | Daikin Industries Ltd | 圧縮機 |
WO2013073264A1 (ja) * | 2011-11-14 | 2013-05-23 | 株式会社安川電機 | モータおよびモータシステム |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2022085079A1 (ja) * | 2020-10-20 | 2022-04-28 | 三菱電機株式会社 | 回転子、電動機、圧縮機および冷凍サイクル装置 |
WO2023119455A1 (ja) * | 2021-12-21 | 2023-06-29 | 三菱電機株式会社 | 着磁方法、電動機、圧縮機および冷凍サイクル装置 |
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