WO2024209552A1 - 回転子、電動機、密閉型圧縮機、および冷凍サイクル装置 - Google Patents

回転子、電動機、密閉型圧縮機、および冷凍サイクル装置 Download PDF

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Publication number
WO2024209552A1
WO2024209552A1 PCT/JP2023/013962 JP2023013962W WO2024209552A1 WO 2024209552 A1 WO2024209552 A1 WO 2024209552A1 JP 2023013962 W JP2023013962 W JP 2023013962W WO 2024209552 A1 WO2024209552 A1 WO 2024209552A1
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WIPO (PCT)
Prior art keywords
rotor
rotor core
suppression member
axial direction
distortion suppression
Prior art date
Application number
PCT/JP2023/013962
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English (en)
French (fr)
Japanese (ja)
Inventor
修一 北野
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2025512256A priority Critical patent/JPWO2024209552A1/ja
Priority to PCT/JP2023/013962 priority patent/WO2024209552A1/ja
Publication of WO2024209552A1 publication Critical patent/WO2024209552A1/ja

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    • 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]

Definitions

  • This disclosure relates to rotors, electric motors, hermetic compressors, and refrigeration cycle devices.
  • rotors for rotating electric machines have permanent magnets placed in the magnet insertion section of the rotor core, and in order to prevent the rotor core from being distorted by the centrifugal force of the permanent magnets, support rods are pressed against the edges of the hollow section formed in the rotor core, and the support rods are fixed to end plates located on both ends of the rotor core. The centrifugal force of the permanent magnets is then supported by the support rods (see, for example, Patent Document 1).
  • the cross-sectional shape of the support rod is round or long in the circumferential direction, so it cannot optimally receive the centrifugal force of the permanent magnet, and there is an issue that distortion of the rotor core caused by the centrifugal force of the permanent magnet cannot be sufficiently suppressed.
  • This disclosure has been made to solve the above problems, and aims to provide a rotor, electric motor, hermetic compressor, and refrigeration cycle device that can suppress distortion of the rotor core caused by the centrifugal force of the permanent magnet more than ever before.
  • the rotor according to the present disclosure comprises a rotor core formed by laminating a plurality of steel plates, a magnet insertion hole formed in the axial direction of the rotor core, a permanent magnet arranged in the magnet insertion hole, mounting members provided at both ends of the rotor core in the axial direction to prevent the permanent magnet from jumping out of the magnet insertion hole, a distortion suppression member arrangement hole formed in the axial direction of the rotor core and arranged radially outward of the permanent magnet with respect to the axis of the rotor core, and a non-magnetic distortion suppression member arranged in the distortion suppression member arrangement hole and both ends fixed to the mounting members, the distortion suppression member abutting against the radially inner side surface of the distortion suppression member arrangement hole and formed in a plate shape that is longer in the radial direction than in the circumferential direction in a plan view.
  • the electric motor according to the present disclosure includes the rotor described above and a stator that is disposed on the outer periphery of the rotor and rotates the rotor by magnetic action.
  • the hermetic compressor according to the present disclosure includes the electric motor described above, a compression mechanism that is driven by the electric motor and compresses fluid drawn in from the outside, and a hermetic container that houses the electric motor and the compression mechanism.
  • the refrigeration cycle device includes the above-mentioned hermetic compressor, an outdoor heat exchanger, a pressure reducer, and an indoor heat exchanger.
  • the distortion suppression member abuts against the radially inner side surface of the distortion suppression member arrangement hole, and is formed into a plate shape that is longer in the radial direction than in the circumferential direction in plan view. In this way, by arranging the distortion suppression member so that it abuts against the radially inner side surface of the distortion suppression member arrangement hole, the repulsive force against the centrifugal force of the permanent magnet arranged in the magnet insertion hole can be increased.
  • the distortion suppression member into a plate shape that is longer in the radial direction than in the circumferential direction in plan view, the section modulus is larger than that of a conventional round shape or a shape that is long in the circumferential direction even with the same cross-sectional area, and resistance to distortion can be increased. Therefore, distortion of the rotor core due to the centrifugal force of the permanent magnet can be suppressed more than before.
  • FIG. 1 is a schematic diagram illustrating an example of an internal configuration of a hermetic compressor according to a first embodiment.
  • FIG. 1 is a schematic cross-sectional view of a compression mechanism of a hermetic compressor according to a first embodiment.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle device including a hermetic compressor according to a first embodiment.
  • FIG. 2 is a schematic cross-sectional view of a hermetic compressor of FIG. 1 taken along the line A-A' of the motor when viewed from the direction of the arrows.
  • 5 is a schematic longitudinal cross-sectional view of a rotor of the motor shown in FIG. 4 , taken along the C-O-C′ cross section.
  • FIG. 5 is a partial cross-sectional schematic diagram of a rotor according to embodiment 1, enlarging a portion of the electric motor viewed from arrow D in FIG. 4 .
  • FIG. 5 is an enlarged schematic partial cross-sectional view of a modified example of a rotor according to the first embodiment, taken along the line indicated by the arrow D in the electric motor of FIG. 4 .
  • FIG. 6 is a partial cross-sectional schematic diagram of the rotor according to the first embodiment, showing an enlarged view of the rotor as viewed from the arrow E in FIG. 5 .
  • FIG. 6 is a partial cross-sectional schematic diagram of a rotor according to embodiment 2, in which the portion of the rotor seen from arrow E in FIG. 5 is enlarged.
  • FIG. 6 is a partial cross-sectional schematic diagram of a modified example of a rotor according to embodiment 2, in which the portion of the rotor shown in FIG. 5 viewed from the arrow E is enlarged.
  • FIG. 5 is a partial cross-sectional schematic view of a rotor according to embodiment 3, showing an enlarged view of the portion of the electric motor shown in FIG. 4 as viewed from the arrow D.
  • hermetic compressor 100 and a refrigeration cycle device 200 will be described with reference to the drawings. Note that the present disclosure is not limited to the embodiments described below. In addition, the size relationships of the components in the following drawings may differ from the actual ones. In addition, in the following description, terms indicating directions (e.g., “upper”, “lower”, “right”, “left”, “front”, “rear”, etc.) are used as appropriate to facilitate understanding, but these terms are for the purpose of explanation and do not limit the present disclosure. Unless otherwise specified, these directional terms refer to the directions when the hermetic compressor 100 is viewed from the front side (front side). In addition, in each drawing, items with the same reference numerals are the same or equivalent, and this is common throughout the entire specification.
  • Fig. 1 is a schematic diagram showing an example of an internal configuration of a hermetic compressor 100 according to embodiment 1.
  • Fig. 2 is a schematic cross-sectional view of a compression mechanism 20 of the hermetic compressor 100 according to embodiment 1.
  • the hermetic compressor 100 is a one-cylinder rotary type, and has the function of drawing in a fluid such as a refrigerant, compressing it, and discharging it in a high-temperature, high-pressure state. As shown in FIG. 1, this hermetic compressor 100 has a hermetic container 10 that forms the outer shell. This hermetic container 10 is composed of an upper container 11 and a lower container 12.
  • a discharge pipe 102 is fixed through the top surface of the upper vessel 11 of the sealed vessel 10.
  • the discharge pipe 102 discharges high-pressure refrigerant gas to the outside of the sealed vessel 10.
  • the fixed portion between the discharge pipe 102 and the upper vessel 11 is joined by, for example, welding.
  • the sealed container 10 contains a compression mechanism 20, an electric motor 30, a rotating shaft 21, and other components.
  • the compression mechanism 20 is disposed below the sealed container 10, and the electric motor 30 is disposed above the sealed container 10.
  • the rotating shaft 21 is disposed between the electric motor 30 and the compression mechanism 20 in the center of the sealed container 10, and extends vertically through the center of the sealed container 10.
  • the compression mechanism 20 and the electric motor 30 are connected by a rotating shaft 21, which transmits the rotational motion of the electric motor 30 to the compression mechanism 20, where the refrigerant gas is compressed by the transmitted rotational force and discharged into the sealed container 10.
  • the sealed container 10 is filled with compressed high-temperature, high-pressure refrigerant gas, and refrigeration oil is stored below, i.e., at the bottom of, the sealed container 10 to lubricate the compression mechanism 20.
  • An oil pump (not shown) is provided below the rotating shaft 21, which pumps up the refrigeration oil stored at the bottom of the sealed container 10 as the rotating shaft 21 rotates, and supplies it to each sliding part of the compression mechanism 20. This ensures mechanical lubrication of the compression mechanism 20.
  • the refrigerant compressed by the hermetic compressor 100 may be, for example, any one of R1234yf, R1234ze, R32, or R290, or a mixture of two or more of these, or a mixture of any one of these with another refrigerant, a mixture containing R1132(E), or a mixture containing R1123. Further examples include mixed refrigerants of R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, and R459A.
  • the rotating shaft 21 is composed of a main shaft portion 21a, an eccentric shaft portion 21b, and a sub-shaft portion 21c, which are formed in the order of main shaft portion 21a, eccentric shaft portion 21b, and sub-shaft portion 21c from top to bottom in the axial direction.
  • An electric motor 30 is fixed to the main shaft portion 21a by shrink fitting or press fitting, and a cylindrical rolling piston 22 is fitted slidably into the eccentric shaft portion 21b.
  • the compression mechanism 20 compresses the low-pressure refrigerant gas sucked into the sealed container 10 into high-pressure refrigerant gas by the rotational driving force supplied from the electric motor 30, and discharges the compressed high-pressure refrigerant gas above the compression mechanism 20.
  • the compression mechanism 20 is composed of a rolling piston 22, a cylinder 23, an upper bearing 24, a lower bearing 25, and a vane 26.
  • the cylinder 23 has a cylindrical space, i.e., a cylinder chamber 23a, with both axial ends open.
  • the cylinder chamber 23a contains the eccentric shaft portion 21b of the rotating shaft 21 that performs eccentric motion within the cylinder chamber 23a, the rolling piston 22 that fits into the eccentric shaft portion 21b, and the vane 26 that partitions the space formed by the inner circumference of the cylinder chamber 23a and the outer circumference of the rolling piston 22.
  • the cylinder 23 is formed with a vane groove 23c, one side of which opens into the cylinder chamber 23a and the other side of which is provided with a back pressure chamber 23b.
  • the vane groove 23c houses a vane 26 that reciprocates radially within the vane groove 23c.
  • the vane 26 is shaped like a rectangular parallelepiped, with the circumferential thickness of the cylinder chamber 23a being smaller than the radial and axial lengths of the cylinder chamber 23a when attached to the vane groove 23c.
  • a vane spring (not shown) is provided in the back pressure chamber 23b of the vane groove 23c.
  • the force that moves the vane 26 radially causes one end of the vane 26, i.e., the end on the cylinder chamber 23a side, to abut against the cylindrical outer periphery of the rolling piston 22. This allows the space formed by the inner periphery of the cylinder 23 and the outer periphery of the rolling piston 22 to be partitioned.
  • the upper bearing 24 is fitted to the main shaft portion 21a of the rotating shaft 21 to rotatably support the main shaft portion 21a and closes one axial opening of the cylinder chamber 23a.
  • the lower bearing 25 is fitted to the counter shaft portion 21c of the rotating shaft 21 to rotatably support the counter shaft portion 21c and closes the other axial opening of the cylinder chamber 23a.
  • the cylinder 23 is provided with a suction port (not shown) that draws refrigerant gas from outside the sealed container 10 into the cylinder chamber 23a
  • the upper bearing 24 is provided with a discharge port (not shown) that discharges compressed refrigerant gas out of the cylinder chamber 23a.
  • the upper bearing 24 is approximately inverted T-shaped when viewed from the front
  • the lower bearing 25 is approximately T-shaped when viewed from the front.
  • a discharge valve (not shown) is provided in the discharge port of the upper bearing 24, and controls the discharge timing of the high-temperature, high-pressure refrigerant gas discharged from the cylinder 23 through the discharge port. That is, the discharge valve closes until the refrigerant gas compressed in the cylinder chamber 23a of the cylinder 23 reaches a predetermined pressure, and opens when the pressure exceeds the predetermined pressure to discharge the high-temperature, high-pressure refrigerant gas outside the cylinder chamber 23a.
  • a discharge muffler 27 is attached to the outside of the upper bearing 24, i.e., on the motor 30 side, so as to cover the upper bearing 24.
  • the discharge muffler 27 has a discharge hole (not shown) that connects the space formed by the discharge muffler 27 and upper bearing 24 to the inside of the sealed container 10. The refrigerant gas discharged from the cylinder 23 through the discharge port is first discharged into the space formed by the discharge muffler 27 and upper bearing 24, and then discharged from the discharge hole into the sealed container 10.
  • a suction muffler 101 is provided on the side of the sealed container 10 to prevent liquid refrigerant from being directly sucked into the cylinder chamber 23a of the cylinder 23.
  • the suction muffler 101 is fixed to the side of the sealed container 10 by welding or the like.
  • a mixture of low-pressure refrigerant gas and liquid refrigerant is sent to the sealed compressor 100 from the external refrigerant circuit to which it is connected.
  • the suction muffler 101 separates the liquid refrigerant from the refrigerant gas and sends only the refrigerant gas to the cylinder chamber 23a.
  • the suction muffler 101 is connected to the suction port (not shown) of the cylinder 23 by the suction connecting pipe 70, and the low-pressure refrigerant gas sent from the suction muffler 101 is sucked into the cylinder chamber 23a via the suction connecting pipe 70.
  • the compression mechanism 20 is constructed as described above, and the rotational motion of the rotary shaft 21 rotates the eccentric shaft portion 21b of the rotary shaft 21 inside the cylinder chamber 23a of the cylinder 23.
  • the working chamber which is partitioned by the inner circumference of the cylinder chamber 23a, the outer circumference of the rolling piston 22 fitted into the eccentric shaft portion 21b, and the vane 26, increases or decreases in volume as the rotary shaft 21 rotates.
  • the working chamber communicates with the suction port, and low-pressure refrigerant gas is sucked in.
  • the communication between the working chamber and the suction port is closed, and the refrigerant gas in the working chamber is compressed as the volume of the working chamber decreases.
  • the working chamber communicates with the discharge port, and after the refrigerant gas in the working chamber reaches a predetermined pressure, the discharge valve provided in the discharge port opens, and the compressed, high-pressure, high-temperature refrigerant gas is discharged outside the working chamber, i.e., outside the cylinder chamber 23a.
  • the high-pressure, high-temperature refrigerant gas discharged from the cylinder chamber 23a through the discharge muffler 27 into the sealed container 10 passes through the motor 30, rises inside the sealed container 10, and is discharged to the outside of the sealed container 10 from the discharge pipe 102 provided at the top of the sealed container 10.
  • a refrigerant circuit through which the refrigerant flows is configured outside the sealed container 10, and the discharged refrigerant circulates through the refrigerant circuit and returns to the suction muffler 101.
  • FIG. 3 is a schematic diagram of a refrigeration cycle device 200 equipped with a hermetic compressor 100 according to the first embodiment.
  • the refrigeration cycle device 200 is, for example, an air conditioner.
  • the refrigeration cycle device 200 includes a hermetic compressor 100 equipped with a suction muffler 101 connected to the suction side of the hermetic compressor 100, a flow path switching valve 103 connected to the discharge side of the hermetic compressor 100, an outdoor heat exchanger 104, a pressure reducer 105, and an indoor heat exchanger 106, which are connected in sequence via piping to form a refrigerant circuit in which the refrigerant circulates.
  • the indoor heat exchanger 106 is mounted in an indoor device, and the remaining hermetic compressor 100, the flow path switching valve 103, the outdoor heat exchanger 104, and the pressure reducer 105 are mounted in an outdoor device.
  • the flow path switching valve 103 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of the refrigerant flow. Note that the flow path switching valve 103 may be a combination of a two-way valve and a three-way valve instead of a four-way valve.
  • the pressure reducer 105 reduces the pressure of the refrigerant to expand it.
  • the pressure reducer 105 is, for example, an electronic expansion valve that can adjust the aperture, and by adjusting the aperture, the pressure of the refrigerant flowing into the indoor heat exchanger 106 during cooling operation is controlled, and the pressure of the refrigerant flowing into the outdoor heat exchanger 104 during heating operation is controlled.
  • the outdoor heat exchanger 104 functions as an evaporator or a condenser, and exchanges heat between the air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant.
  • the outdoor heat exchanger 104 functions as an evaporator during heating operation, and as a condenser during cooling operation.
  • the indoor heat exchanger 106 functions as an evaporator or a condenser, and exchanges heat between the air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant.
  • the indoor heat exchanger 106 functions as a condenser during heating operation and as an evaporator during cooling operation.
  • the flow path switching valve 103 is connected to the solid line side in FIG. 3.
  • the high-temperature, high-pressure refrigerant compressed by the hermetic compressor 100 flows to the indoor heat exchanger 106, condenses, and liquefies, and is then throttled by the pressure reducer 105 to become a two-phase state of low temperature and low pressure. It then flows to the outdoor heat exchanger 104, evaporates, gasifies, and passes through the flow path switching valve 103 and returns to the hermetic compressor 100 again.
  • the refrigerant circulates as shown by the solid arrows in FIG. 3.
  • the refrigerant exchanges heat with the outside air in the outdoor heat exchanger 104, which is an evaporator, and the refrigerant sent to the outdoor heat exchanger 104 absorbs heat, and the refrigerant that has absorbed heat is sent to the indoor heat exchanger 106, which is a condenser, and exchanges heat with the indoor air to warm the indoor air.
  • the flow switching valve 103 is connected to the dashed line side in FIG. 3.
  • the high-temperature, high-pressure refrigerant compressed by the hermetic compressor 100 flows to the outdoor heat exchanger 104, condenses, and liquefies, and is then throttled by the pressure reducer 105 to become a two-phase state of low temperature and low pressure. It then flows to the indoor heat exchanger 106, evaporates, gasifies, and returns to the flow switching valve 103 and the hermetic compressor 100.
  • the indoor heat exchanger 106 changes from a condenser to an evaporator
  • the outdoor heat exchanger 104 changes from an evaporator to a condenser.
  • the refrigerant circulates as shown by the dashed arrows in FIG. 3.
  • the indoor heat exchanger 106 which is an evaporator, exchanges heat with the indoor air, absorbing heat from the indoor air, i.e., cooling the indoor air, and the refrigerant that has absorbed heat is sent to the outdoor heat exchanger 104, which is a condenser, where it exchanges heat with the outdoor air and releases heat to the outdoor air.
  • FIG. 4 is a schematic cross-sectional view of the electric motor 30, seen from the direction of the arrows at the A-A' cross section of the hermetic compressor 100 in FIG. 1.
  • FIG. 5 is a schematic vertical cross-sectional view of the rotor 31, seen from the direction of the arrows at the C-O-C' cross section of the electric motor 30 in FIG. 4.
  • the electric motor 30 that transmits rotational force to the compression mechanism 20 will be described with reference to FIGS. 4 and 5.
  • the electric motor 30 has a substantially cylindrical stator 51 fixed to the inner circumferential surface of the hermetic container 10, and a substantially cylindrical rotor 31 arranged inside the stator 51.
  • the rotor 31 has a rotor core 32 formed by laminating multiple steel plates (thin electromagnetic steel plates). Magnet insertion holes 33 are formed in the axial direction of the rotor core 32, and permanent magnets 34 such as ferrite magnets or rare earth magnets are inserted into the magnet insertion holes 33. The permanent magnets 34 form magnetic poles on the rotor 31.
  • the rotor 31 rotates due to the interaction between the magnetic flux created by the magnetic poles on the rotor 31 and the magnetic flux created by the stator windings 54 of the stator 51.
  • a shaft hole 39 through which the rotating shaft 21 passes is provided in the center of the rotor core 32, and the main shaft portion 21a of the rotating shaft 21 is fastened by shrink fitting or the like. This transmits the rotational motion of the rotor 31 to the rotating shaft 21.
  • Air holes 35 and rivet insertion holes 38 are provided around the shaft hole 39, and high-pressure, high-temperature refrigerant compressed by the compression mechanism 20 below the electric motor 30 passes through the air holes 35. Note that the refrigerant compressed by the compression mechanism 20 also passes through the air gap between the rotor 31 and stator 51 and the gaps in the stator windings 54, in addition to the air holes 35.
  • mounting members 37 are provided at both axial ends of the rotor core 32 to prevent the permanent magnets 34 from jumping out of the magnet insertion holes 33.
  • the mounting members 37 pass through rivet insertion holes 38 in the rotor core 32 and are fixed by rivets 60 extending in the axial direction.
  • the mounting members 37 may also be something like a balance weight or an end plate.
  • FIG. 6 is a partial cross-sectional schematic diagram of the rotor 31 according to embodiment 1, enlarging the portion of the motor 30 in FIG. 4 as viewed from the arrow D.
  • the distortion suppression member 40 that suppresses distortion of the rotor core 32 due to the centrifugal force of the permanent magnets 34 will be described with reference to FIGS. 5 and 6.
  • the rotor core 32 has a hollow portion 36 and a distortion suppression member arrangement hole 41 that are formed in the axial direction of the rotor core 32 and are disposed radially outward from the permanent magnets 34 with respect to the axial center of the rotor core 32.
  • a non-magnetic distortion suppression member 40 is inserted into the distortion suppression member arrangement hole 41.
  • the distortion suppression member 40 is formed in a plate shape that is longer in the radial direction than in the circumferential direction in a plan view, and is disposed so as to abut against the radially inner side surface of the distortion suppression member arrangement hole 41.
  • the hole into which the distortion suppression member 40 is inserted is the distortion suppression member arrangement hole 41, and the hole into which the distortion suppression member 40 is not inserted is the hollow portion 36. Note that in FIG. 6, only one distortion suppression member arrangement hole 41 is formed, but multiple distortion suppression member arrangement holes 41 may be formed in the circumferential direction, and it is sufficient that at least one is formed within the range of the circumferential width of the permanent magnet 34.
  • the distortion suppression member 40 by arranging the distortion suppression member 40 so that it abuts against the radially inner side surface of the distortion suppression member arrangement hole 41, the repulsive force against the centrifugal force of the permanent magnet 34 arranged in the magnet insertion hole 33 can be increased. Also, by making the distortion suppression member 40 into a plate shape that is longer in the radial direction than in the circumferential direction in a plan view, the section modulus, that is, the resistance to stress that bends the cross section (bending moment) is greater than that of a conventional round shape or a shape that is long in the circumferential direction, even with the same cross-sectional area, and resistance to distortion can be increased. Therefore, distortion of the rotor core 32 due to the centrifugal force of the permanent magnet 34 can be suppressed more than before.
  • the radial length L1 of the distortion suppression member 40 is longer than the circumferential length L2 of the distortion suppression member arrangement hole 41.
  • FIG. 7 is a partial cross-sectional schematic diagram of a modified rotor 31 according to embodiment 1, enlarging the portion of the motor 30 in FIG. 4 viewed from the arrow D.
  • the radial length L1 of the distortion suppression member 40 may be configured to be shorter than the circumferential length L2 of the distortion suppression member arrangement hole 41.
  • the radial length L1 of the distortion suppression member 40 is configured to be longer than the circumferential length L2 of the distortion suppression member arrangement hole 41 as shown in FIG. 6, the repulsive force against the centrifugal force of the permanent magnet 34 arranged in the magnet insertion hole 33 can be increased compared to the case where the radial length L1 of the distortion suppression member 40 is configured to be shorter than the circumferential length L2 of the distortion suppression member arrangement hole 41 as shown in FIG. 7, and therefore distortion of the rotor core 32 due to the centrifugal force of the permanent magnet 34 can be further suppressed.
  • FIG. 8 is a partial cross-sectional schematic diagram of the rotor 31 according to embodiment 1, which is an enlarged view of the rotor 31 in FIG. 5 as viewed from the arrow E.
  • the mounting members 37 provided at both ends of the rotor core 32 in the axial direction are provided with grooves 37a into which the ends of the distortion suppression members 40 are inserted, and the grooves 37a have a first side surface 37b on the radially outer side and a second side surface 37c on the radially inner side.
  • the first side surface 37b and the second side surface 37c face each other.
  • the first side surface 37b and the second side surface 37c are formed in a straight line along the axial direction. In other words, the grooves 37a are formed in a concave shape.
  • the ends of the distortion suppression members 40 are pressed between the first side surface 37b and the second side surface 37c. In this way, by pressing the ends of the distortion suppression members 40 into the concave grooves 37a, the distortion suppression members 40 can be fixed, and the movement of the distortion suppression members 40 in the distortion suppression member arrangement holes 41 can be suppressed.
  • the first side surface 37b on the radially outer side in a straight line along the axial direction, when centrifugal force is applied to the strain suppression member 40, the end of the strain suppression member 40 abuts against the first side surface 37b along the axial direction, so that the abutting area can be increased compared to when the first side surface 37b is formed at an angle. Therefore, the first side surface 37b can better absorb the centrifugal force of the strain suppression member 40 along the axial direction, and the movement of the strain suppression member 40 within the strain suppression member arrangement hole 41 can be further suppressed.
  • the rotor 31 includes a rotor core 32 formed by laminating a plurality of steel plates, a magnet insertion hole 33 formed in the axial direction of the rotor core 32, a permanent magnet 34 arranged in the magnet insertion hole 33, mounting members 37 provided at both ends of the axial direction of the rotor core 32 to prevent the permanent magnet 34 from jumping out of the magnet insertion hole 33, a distortion suppression member arrangement hole 41 formed in the axial direction of the rotor core 32 and arranged radially outward from the permanent magnet 34 with respect to the axis of the rotor core 32, and a non-magnetic distortion suppression member 40 arranged in the distortion suppression member arrangement hole 41 and both ends fixed to the mounting member 37.
  • the distortion suppression member 40 abuts against the radial inner side surface of the distortion suppression member arrangement hole 41 and is formed in a plate shape that is longer in the radial direction than in the circumferential direction when viewed in a plane.
  • the distortion suppression member 40 abuts against the radially inner side surface of the distortion suppression member arrangement hole 41, and is formed into a plate shape that is longer in the radial direction than in the circumferential direction in a plan view. In this way, by arranging the distortion suppression member 40 so that it abuts against the radially inner side surface of the distortion suppression member arrangement hole 41, the repulsive force against the centrifugal force of the permanent magnet 34 arranged in the magnet insertion hole 33 can be increased.
  • the distortion suppression member 40 by making the distortion suppression member 40 into a plate shape that is longer in the radial direction than in the circumferential direction in a plan view, the section modulus is larger than that of a conventional round shape or a shape that is long in the circumferential direction even with the same cross-sectional area, and the resistance to distortion can be increased. Therefore, the distortion of the rotor core 32 due to the centrifugal force of the permanent magnet 34 can be suppressed more than before.
  • the radial length L1 of the distortion suppression member 40 is longer than the circumferential length L2 of the distortion suppression member arrangement hole 41.
  • the radial length L1 of the distortion suppression member 40 is longer than the circumferential length L2 of the distortion suppression member arrangement hole 41. This increases the repulsive force of the permanent magnet 34 arranged in the magnet insertion hole 33 against the centrifugal force, compared to when the radial length L1 of the distortion suppression member 40 is shorter than the circumferential length L2 of the distortion suppression member arrangement hole 41. This makes it possible to better suppress distortion of the rotor core 32 due to the centrifugal force of the permanent magnet 34.
  • the mounting member 37 is provided with a groove portion 37a into which the end of the distortion suppression member 40 is inserted.
  • the end of the distortion suppression member 40 can be pressed into the groove portion 37a to fix the distortion suppression member 40, thereby suppressing the movement of the distortion suppression member 40 within the distortion suppression member placement hole 41.
  • the electric motor 30 includes the rotor 31 and a stator 51 that is disposed on the outer periphery of the rotor 31 and rotates the rotor 31 by magnetic action.
  • the electric motor 30 according to the first embodiment can achieve the same effect as the rotor 31 described above.
  • the hermetic compressor 100 includes the electric motor 30, a compression mechanism 20 that is driven by the electric motor 30 and compresses fluid drawn in from the outside, and a hermetic container 10 that houses the electric motor 30 and the compression mechanism 20.
  • the hermetic compressor 100 according to embodiment 1 can achieve the same effects as the rotor 31 described above.
  • the refrigeration cycle device 200 includes the above-mentioned hermetic compressor 100, an outdoor heat exchanger 104, a pressure reducer 105, and an indoor heat exchanger 106.
  • the refrigeration cycle device 200 according to the first embodiment can achieve the same effects as the rotor 31 described above.
  • Embodiment 2 Hereinafter, the second embodiment will be described, but explanations of parts that overlap with the first embodiment will be omitted, and parts that are the same as or equivalent to the first embodiment will be given the same reference numerals.
  • FIG. 9 is a partial cross-sectional schematic diagram of the rotor 31 according to embodiment 2, which is an enlarged view of the rotor 31 in FIG. 5 as viewed from the arrow E.
  • the mounting members 37 provided at both ends of the rotor core 32 in the axial direction are provided with grooves 37a into which the ends of the distortion suppression members 40 are inserted, and the grooves 37a have a first side surface 37b on the radially outer side and a second side surface 37c on the radially inner side.
  • the first side surface 37b and the second side surface 37c face each other.
  • the first side surface 37b is formed in a straight line along the axial direction
  • the second side surface 37c is formed in an inclined shape that is radially outward (or toward the first side surface 37b) as it moves away from the rotor core 32.
  • the grooves 37a are formed in a tapered shape.
  • the distortion suppression members 40 are pressed into between the first side surface 37b and the second side surface 37c. In this way, by pressing the end of the strain suppression member 40 into the tapered groove 37a, it is possible to achieve closer adhesion than when the end of the strain suppression member 40 is pressed into the concave groove 37a. Therefore, the strain suppression member 40 can be fixed more firmly, and the movement of the strain suppression member 40 in the strain suppression member arrangement hole 41 can be further suppressed.
  • FIG. 10 is a partial cross-sectional schematic diagram of a modified rotor 31 according to embodiment 2, enlarging the E-arrow portion of the rotor 31 in FIG. 5.
  • the first side surface 37b is formed linearly along the axial direction
  • the second side surface 37c is formed in an inclined shape that approaches radially outward as it moves away from the rotor core 32, but this is not limited to the above.
  • the first side surface 37b is formed in an inclined shape that approaches radially inward (or toward the second side surface 37c) as it moves away from the rotor core 32
  • the second side surface 37c may be formed in a linear shape along the axial direction.
  • one of the first side surface 37b and the second side surface 37c is formed in a linear shape along the axial direction, and the other side surface is formed in an inclined shape that approaches the one side surface as it moves away from the rotor core 32.
  • the first side surface 37b can better absorb the centrifugal force of the strain suppression member 40 along the axial direction, and the movement of the strain suppression member 40 within the strain suppression member arrangement hole 41 can be further suppressed.
  • the groove portion 37a has a first side surface 37b provided on the radially outer side and a second side surface 37c that faces the first side surface 37b and is provided on the radially inner side, and one of the first side surface 37b and the second side surface 37c is formed in a straight line along the axial direction, and the other side surface is formed in an inclined manner so as to approach the one side surface as it moves away from the rotor core 32 in the axial direction.
  • the end of the distortion suppression member 40 can be pressed into the tapered groove 37a, which allows for closer adhesion compared to when the end of the distortion suppression member 40 is pressed into the concave groove 37a. This allows the distortion suppression member 40 to be fixed more firmly, and the movement of the distortion suppression member 40 within the distortion suppression member placement hole 41 to be more effectively suppressed.
  • the first side surface 37b is formed linearly along the axial direction
  • the second side surface 37c is formed obliquely so as to approach the first side surface 37b as it moves away from the rotor core 32 in the axial direction.
  • the first side surface 37b on the radially outer side is formed in a straight line along the axial direction, so that when centrifugal force is applied to the strain suppression member 40, the end of the strain suppression member 40 abuts against the first side surface 37b along the axial direction, and the abutting area can be increased compared to when the first side surface 37b is formed at an angle. Therefore, the first side surface 37b can better absorb the centrifugal force of the strain suppression member 40 along the axial direction, and the movement of the strain suppression member 40 within the strain suppression member arrangement hole 41 can be further suppressed.
  • Embodiment 3 Hereinafter, the third embodiment will be described, but explanations of parts that overlap with the first and second embodiments will be omitted, and parts that are the same as or equivalent to the first and second embodiments will be given the same reference numerals.
  • FIG. 11 is a partial cross-sectional schematic diagram of the rotor 31 according to embodiment 3, which is an enlarged view of the portion of the motor 30 in FIG. 4 as viewed from the arrow D.
  • the rotor core 32 has an inner rotor core 32a, which is a member on the radial inner side of the permanent magnet 34, and an outer rotor core 32b, which is a member on the radial outer side of the permanent magnet 34.
  • the inner rotor core 32a and the outer rotor core 32b are each constructed as separate bodies, and are arranged with a gap in the radial direction. In other words, the rotor core 32 does not have a bridge.
  • the distortion suppression member arrangement hole 41 is formed in the outer rotor core 32b.
  • the inner rotor core 32a and the outer rotor core 32b with a gap therebetween, there is no bridge, which is a portion connecting the inner rotor core 32a and the outer rotor core 32b. This reduces magnetic leakage from the bridge and reduces magnetic loss.
  • the rotor 31 is disposed inside the stator 51, and as shown in FIG. 5, mounting members 37 are provided on both axial ends of the rotor core 32, which is a component of the rotor 31, and these mounting members 37 pass through rivet insertion holes 38 in the rotor core 32 and are fixed by rivets 60 extending in the axial direction. Therefore, even if the rotor core 32, which is a component of the rotor 31, is composed of separate inner rotor core 32a and outer rotor core 32b, the inner rotor core 32a and outer rotor core 32b do not come apart and remain in their designated positions.
  • the rotor core 32 has an inner rotor core 32a, which is a member on the radially inner side of the permanent magnet 34, and an outer rotor core 32b, which is a member on the radially outer side of the permanent magnet 34 and has a distortion suppression member arrangement hole 41 formed therein.
  • the inner rotor core 32a and the outer rotor core 32b are each constructed separately and are arranged with a gap in the radial direction.
  • the inner rotor core 32a and the outer rotor core 32b are arranged with a gap between them, and there is no bridge connecting the inner rotor core 32a and the outer rotor core 32b. This reduces magnetic leakage from the bridge, and reduces magnetic loss.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2023/013962 2023-04-04 2023-04-04 回転子、電動機、密閉型圧縮機、および冷凍サイクル装置 WO2024209552A1 (ja)

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PCT/JP2023/013962 WO2024209552A1 (ja) 2023-04-04 2023-04-04 回転子、電動機、密閉型圧縮機、および冷凍サイクル装置

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0397354U (enrdf_load_stackoverflow) * 1990-01-23 1991-10-07
JPH07123615A (ja) * 1993-10-19 1995-05-12 Toshiba Corp 永久磁石付き回転子
JP2009095109A (ja) * 2007-10-05 2009-04-30 Toyota Central R&D Labs Inc 回転電機の回転子及び回転電機
JP2016077032A (ja) * 2014-10-02 2016-05-12 株式会社日本自動車部品総合研究所 積層コア、同期電動機、および電動圧縮機
JP2016226262A (ja) * 2015-05-27 2016-12-28 エルジー イノテック カンパニー リミテッド ロータおよびこれを含むモータ
JP2018046590A (ja) * 2016-09-12 2018-03-22 株式会社日立製作所 回転電機
WO2020090007A1 (ja) * 2018-10-30 2020-05-07 三菱電機株式会社 コンシクエントポール型回転子、電動機、送風機、及び冷凍空調装置、並びにコンシクエントポール型回転子の製造方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0397354U (enrdf_load_stackoverflow) * 1990-01-23 1991-10-07
JPH07123615A (ja) * 1993-10-19 1995-05-12 Toshiba Corp 永久磁石付き回転子
JP2009095109A (ja) * 2007-10-05 2009-04-30 Toyota Central R&D Labs Inc 回転電機の回転子及び回転電機
JP2016077032A (ja) * 2014-10-02 2016-05-12 株式会社日本自動車部品総合研究所 積層コア、同期電動機、および電動圧縮機
JP2016226262A (ja) * 2015-05-27 2016-12-28 エルジー イノテック カンパニー リミテッド ロータおよびこれを含むモータ
JP2018046590A (ja) * 2016-09-12 2018-03-22 株式会社日立製作所 回転電機
WO2020090007A1 (ja) * 2018-10-30 2020-05-07 三菱電機株式会社 コンシクエントポール型回転子、電動機、送風機、及び冷凍空調装置、並びにコンシクエントポール型回転子の製造方法

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