WO2023139637A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2023139637A1
WO2023139637A1 PCT/JP2022/001568 JP2022001568W WO2023139637A1 WO 2023139637 A1 WO2023139637 A1 WO 2023139637A1 JP 2022001568 W JP2022001568 W JP 2022001568W WO 2023139637 A1 WO2023139637 A1 WO 2023139637A1
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WO
WIPO (PCT)
Prior art keywords
stator
rotating shaft
rotary compressor
rotor
center
Prior art date
Application number
PCT/JP2022/001568
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English (en)
Japanese (ja)
Inventor
貴裕 水田
盛幸 枦山
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.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/001568 priority Critical patent/WO2023139637A1/fr
Priority to JP2023574897A priority patent/JPWO2023139637A1/ja
Publication of WO2023139637A1 publication Critical patent/WO2023139637A1/fr

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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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • 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

Definitions

  • This application relates to a rotary compressor.
  • a rotary compressor consists of an electric motor section that has a rotating mechanism, and a compression mechanism section that takes in, compresses, and discharges refrigerant in synchronization with the rotation of the electric motor section.
  • the torque required for the compression mechanism is close to zero when refrigerant is sucked, and becomes maximum from compression to discharge of refrigerant.
  • the electric motor section is designed with the maximum value of the load torque of the compression mechanism section. Therefore, the electric motor section becomes large.
  • a rotary compressor equipped with an auxiliary magnetic circuit has been disclosed as a conventional rotary compressor that addresses the problem of increasing the size of the electric motor.
  • the auxiliary magnetic circuit is configured such that the positive torque is maximized when the average torque during one rotation is zero and the load torque of the compression mechanism is maximized (see, for example, Patent Document 1).
  • the load torque of the compression mechanism and the torque of the auxiliary magnetic circuit are canceled to reduce the maximum torque required for the electric motor.
  • a rotary compressor having a two-cylinder compression mechanism is disclosed (see, for example, Patent Documents 2 and 3). In this rotary compressor, the load torque pulsations generated in the two cylinders are mutually canceled to reduce the maximum torque required for the electric motor section.
  • a rotary compressor that intentionally generates torque pulsation by making the magnetic force of the rotor of the electric motor section and the number of turns of the stator coil asymmetrical (see, for example, Patent Document 4).
  • the torque pulsation generated in the electric motor section and the load torque pulsation of the compression mechanism section are canceled to reduce the maximum torque required for the electric motor section.
  • the present application was made to solve the above-mentioned problems, and aims to provide a compact rotary compressor that can suppress the generation of vibration and noise and can reduce the torque required for the electric motor section.
  • the rotary compressor of the present application includes a closed container, an electric motor unit having a rotating shaft installed in the closed container, and a compression mechanism unit installed in the closed container that sucks and compresses refrigerant gas in conjunction with the rotation of the rotating shaft.
  • the electric motor section has a cylindrical stator and a cylindrical rotor that is arranged on the inner peripheral side of the stator and is rotatably supported along with the rotating shaft relative to the stator. Magnets that generate magnetic flux radially outward and magnets that generate magnetic flux radially inward are alternately arranged in the rotor in the circumferential direction. and vanes that press against the peripheral surface.
  • ⁇ is the angle between a straight line connecting the center of the rotating shaft and the center of the magnet that generates the magnetic flux toward the outside in the radial direction of the magnetomotive force distribution
  • ⁇ is the angle formed by the straight line connecting the center of the rotating shaft and the point on the outer diameter of the piston that is farthest from the center of the rotating shaft.
  • the rotary compressor of the present application is configured to satisfy the above equation, it is possible to suppress the generation of vibration and noise and reduce the torque required for the electric motor section.
  • the rotary compressor of the present application does not require additional parts for reducing the torque required for the electric motor section, so that the size of the apparatus can be reduced.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1;
  • FIG. 2 is a cross-sectional view of a compression mechanism portion of the rotary compressor according to Embodiment 1.
  • FIG. 4 is an explanatory diagram for defining a rotation angle of a rotating shaft in Embodiment 1.
  • FIG. 4 is a characteristic diagram showing load torque in the rotary compressor according to Embodiment 1.
  • FIG. 2 is a cross-sectional view of the electric motor portion of the rotary compressor according to Embodiment 1;
  • FIG. 4 is an explanatory diagram of permeance waveforms between the stator and rotor in the rotary compressor according to Embodiment 1.
  • FIG. 2 is an explanatory diagram showing an electric motor section and a compression mechanism section in the rotary compressor according to Embodiment 1, which are superimposed;
  • FIG. 2 is an explanatory diagram showing an electric motor section and a compression mechanism section in the rotary compressor according to Embodiment 1, which are superimposed;
  • FIG. 4 is a characteristic diagram showing a load torque waveform in steady operation of the rotary compressor according to Embodiment 1;
  • 4 is a characteristic diagram showing load torque, cogging torque, and torque obtained by subtracting the cogging torque from the load torque of the rotary compressor according to Embodiment 1.
  • FIG. FIG. 4 is a cross-sectional view of an electric motor portion of a rotary compressor of a comparative example according to Embodiment 1;
  • FIG. 4 is a cross-sectional view of an electric motor portion of a rotary compressor of a comparative example according to Embodiment 1;
  • FIG. 8 is a cross-sectional view of an electric motor portion of a rotary compressor according to Embodiment 2;
  • FIG. 9 is a characteristic diagram showing the magnetomotive force of magnets in the rotary compressor according to Embodiment 2;
  • FIG. 11 is a cross-sectional view of an electric motor portion of a rotary compressor according to Embodiment 3;
  • Embodiment 1. 1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1.
  • FIG. A rotary compressor 100 of the present embodiment includes a closed container 1 , an electric motor section 10 arranged inside the closed container 1 , and a compression mechanism section 20 driven by the electric motor section 10 .
  • the rotary compressor 100 is a so-called high-pressure shell-type rotary compressor in which the internal space of the sealed container 1 is filled with compressed high-pressure refrigerant during operation.
  • the electric motor section 10 has an annular stator 11 fixed inside the sealed container 1, a cylindrical rotor 12 arranged on the inner peripheral side of the stator 11, and a rotating shaft 13 fastened to the center of the rotor 12.
  • the rotor 12 is rotatably arranged with respect to the stator 11 .
  • the rotary shaft 13 extends from the electric motor section 10 to the compression mechanism section 20 .
  • the longitudinal direction of the rotating shaft 13 will be referred to as the axial direction
  • the direction orthogonal to the axial direction will be referred to as the radial direction
  • the rotating direction of the rotating shaft 13 will be referred to as the circumferential direction.
  • FIG. 2 is a cross-sectional view of the rotary compressor according to this embodiment.
  • FIG. 2 is a cross-sectional view of the compression mechanism section 20 taken along line AA of FIG.
  • the compression mechanism portion 20 includes an annular cylinder 21 fixed inside the sealed container 1, an eccentric shaft portion 22 arranged on the inner peripheral side of the cylinder 21, an annular piston 23 slidably fitted to the outer periphery of the eccentric shaft portion 22, an upper bearing 24, and a lower bearing 25.
  • a compression chamber 26 is formed inside the cylinder 21 by an upper bearing 24 arranged in contact with the upper surface of the cylinder 21 and a lower bearing 25 arranged in contact with the lower surface of the cylinder 21 .
  • the eccentric shaft portion 22 and the piston 23 are arranged inside the compression chamber 26 .
  • the eccentric shaft portion 22 is fastened to the rotating shaft 13 and rotates inside the compression chamber 26 as the rotating shaft 13 rotates.
  • the piston 23 rotates inside the compression chamber 26 integrally with the eccentric shaft portion 22 .
  • the piston 23 rotates with the outer peripheral surface of the piston 23 farthest from the center of the rotating shaft 13 always in contact with the inner peripheral surface of the cylinder 21 .
  • a suction pipe 2 for sucking refrigerant gas is connected to the side surface of the sealed container 1 .
  • the other end of the suction pipe 2 is connected to the suction muffler 3 .
  • Refrigerant gas is sucked into the compression chamber 26 of the compression mechanism section 20 via the suction muffler 3 and the suction pipe 2 .
  • a discharge pipe 4 for discharging the refrigerant gas compressed inside the closed container 1 is connected to the upper portion of the closed container 1 .
  • the upper bearing 24 has an inverted T-shaped cross section, closes the upper opening of the compression chamber 26, and rotatably supports the rotating shaft 13. As shown in FIG.
  • the upper bearing 24 is provided with a discharge port 24a for discharging the compressed high-temperature, high-pressure refrigerant gas from the compression chamber 26 to the outside.
  • a discharge muffler 27 is attached to the upper part of the upper bearing 24 to cover the discharge port 24a.
  • the discharge muffler 27 is provided to reduce the pulsating noise of the refrigerant gas intermittently discharged from the discharge port 24a.
  • the discharge muffler 27 is provided with a discharge hole that communicates the space formed between the discharge muffler 27 and the upper bearing 24 with the inside of the sealed container 1 .
  • a discharge valve 24b is provided at the outlet of the discharge port 24a on the side of the discharge muffler 27 so as to openably close the discharge port 24a.
  • Refrigerant gas discharged from the compression chamber 26 through the discharge port 24a is once discharged into the space formed between the discharge muffler 27 and the upper bearing 24, and then discharged into the sealed container 1 through the discharge hole.
  • the lower bearing 25 closes the lower opening of the compression chamber 26 and rotatably supports the rotating shaft 13 .
  • the cylinder 21 is provided with a suction port 21a for drawing refrigerant gas from the suction pipe 2 into the compression chamber 26, a back pressure chamber 21b into which the refrigerant in the sealed container 1 flows, and a vane groove portion 21c that communicates the back pressure chamber 21b and the compression chamber 26.
  • a vane 28 made of a spring member is inserted into the vane groove portion 21c so as to reciprocate in the radial direction of the cylinder 21.
  • the end of the vane 28 on the side of the compression chamber 26 is pressed against the outer peripheral surface of the piston 23 by the pressing force of the spring member toward the piston 23 and the pressure of the high-temperature, high-pressure refrigerant gas flowing into the back pressure chamber 21b.
  • the vane 28 divides the compression chamber 26 into a low pressure side compression chamber 26a and a high pressure side compression chamber 26b.
  • the operation of the rotary compressor thus configured will be described.
  • the electric motor section 10 is driven and the rotating shaft 13 rotates.
  • the piston 23 in the compression chamber 26 rotates.
  • the rotational motion of the piston 23 is counterclockwise.
  • the volume of the low-pressure side compression chamber 26a and the volume of the high-pressure side compression chamber 26b partitioned by the vane 28 increase or decrease.
  • the low-pressure side compression chamber 26a and the suction port 21a are communicated with each other, and low-pressure refrigerant gas is sucked into the low-pressure side compression chamber 26a.
  • the rotation of the piston 23 reduces the volume of the high-pressure side compression chamber 26b, compressing the refrigerant gas in the high-pressure side compression chamber 26b and increasing the temperature and gas pressure of the refrigerant gas.
  • the discharge valve 24b of the upper bearing 24 opens.
  • the high-temperature and high-pressure refrigerant gas is discharged from the discharge port 24a toward the discharge muffler 27 and discharged into the sealed container 1 through the discharge holes of the discharge muffler 27. As shown in FIG.
  • the pressure difference between the high-pressure side compression chamber 26b and the closed container 1 and the elastic force of the discharge valve 24b close the discharge valve 24b.
  • the high-temperature, high-pressure refrigerant gas released into the closed container 1 rises inside the closed container 1 and is discharged to the outside from a discharge pipe 4 provided at the top of the closed container 1 .
  • FIG. 3 is an explanatory diagram for defining the rotation angle of the rotating shaft in this embodiment.
  • the angle between a straight line connecting the center 13c of the rotating shaft 13 and the point 23c on the outer diameter of the piston 23 farthest from the center 13c of the rotating shaft 13 and a straight line connecting the center 13c of the rotating shaft 13 and the center 28c of the vane 28 is defined as the rotation angle of the rotating shaft.
  • the rotation angle of the rotation shaft at the position where the center 13c of the rotation shaft 13, the point 23c on the outer diameter of the piston 23 farthest from the center 13c of the rotation shaft 13, and the center 28c of the vane 28 are aligned is defined as 0°.
  • the compression chamber 26 is not divided into the low-pressure side compression chamber and the high-pressure side compression chamber 26b.
  • the rotation angle of the rotating shaft 13 in FIG. 3 is assumed to be positive when counterclockwise.
  • Fig. 4 is a characteristic diagram showing the load torque in a general rotary compressor.
  • the horizontal axis is the rotation angle of the rotating shaft
  • the vertical axis is the load torque required for the electric motor section to drive the compression mechanism section.
  • the load torque is positive when the rotating shaft rotates clockwise.
  • the suction of refrigerant gas into the low-pressure side compression chamber and the compression and discharge of refrigerant gas in the high-pressure side compression chamber are repeated as the piston rotates.
  • the load torque required for the electric motor portion is almost zero when the refrigerant gas is sucked, the load torque required for the electric motor portion increases as the refrigerant gas is compressed in the high-pressure side compression chamber.
  • the discharge valve opens and the high-temperature and high-pressure refrigerant gas is discharged, so the load torque required for the electric motor portion is reduced.
  • the load torque required for the electric motor unit during intake, compression, and discharge greatly increases and decreases as the piston rotates.
  • the electric motor section is designed according to the maximum value of the load torque, so the electric motor section becomes larger than when there is no pulsation of the load torque.
  • FIG. 5 is a cross-sectional view of the rotary compressor according to this embodiment.
  • FIG. 5 is a cross-sectional view of the electric motor section 10 taken along BB in FIG.
  • the electric motor unit 10 has an annular stator 11 fixed inside the sealed container 1, a cylindrical rotor 12 disposed on the inner peripheral side of the stator 11 with a gap therebetween, and a rotating shaft 13 fastened to the center of the rotor 12.
  • the rotor 12 has a rotor core 12a made of magnetic material and configured by laminating magnetic steel sheets in the axial direction, and a plurality of magnets 12b embedded in the rotor core 12a.
  • the rotor core 12a is fastened to the rotating shaft 13 by shrink fitting or press fitting.
  • the white arrow indicates the magnetization direction of the magnet 12b.
  • magnets 12b magnetized to generate magnetic flux radially outward and magnets 12b magnetized to generate magnetic flux radially inward are alternately arranged in the circumferential direction.
  • a spatial primary component exists in the circumferential magnetomotive force distribution between the stator and the rotor resulting from such arrangement of the magnets.
  • the stator 11 has a magnetic stator core 11a composed of magnetic steel sheets laminated in the axial direction, and a stator coil 11b.
  • the stator core 11a is composed of a cylindrical core back 11c and a plurality of teeth 11d protruding radially inward from the inner peripheral side of the core back 11c.
  • a stator slot 11e which is a space opened radially inward of the stator core 11a, is formed between the teeth 11d.
  • a stator coil 11b is arranged in the stator slot 11e.
  • the stator coil 11b is wound around the tooth 11d by concentrated winding.
  • a radially inner end of each tooth 11d is provided with a flange portion 11f protruding in the circumferential direction.
  • the inner diameter of the stator 11 shown in FIG. 5 is elliptical with the major axis extending in the lateral direction of the paper. That is, the stator 11 has shape anisotropy in one direction. Further, the outer diameter of the rotor 12 shown in FIG. 5 is a perfect circle. Therefore, the magnetic gap, which is the radial distance between the outer peripheral surface of the rotor 12 and the inner peripheral surface of the stator 11, changes with the position in the circumferential direction. As shown in FIG. 5, the angle between the magnetization direction of the magnet 12b and the straight line connecting the center 13c of the rotating shaft 13 and the center 28c of the vane 28 in FIG. 3 is defined as the rotation angle of the rotor. Henceforth, the rotation angle of the rotor 12 is assumed to be positive in the counterclockwise direction.
  • FIG. 6 is an explanatory diagram of the permeance waveform between the stator and rotor.
  • the horizontal axis is the rotation angle of the rotor, and the vertical axis is the permeance.
  • the solid line is the permeance between the stator and rotor in the motor section shown in FIG. Permeance.
  • Permeance is the ease with which magnetic flux passes. Since the inner diameter of the stator is elliptical, the permeance increases at positions where the distance between the stator and rotor is short, and decreases at positions where the distance between the stator and rotor is long. Therefore, the permeance waveform has two peaks during one rotation of the rotor.
  • the permeance waveform between the stator and rotor is a waveform obtained by synthesizing a waveform with two peaks and a waveform with three peaks.
  • the permeance pulsation of the three peaks caused by the teeth can be reduced.
  • the permeance waveform is dominated by two-peak components caused by the elliptical inner diameter of the stator. That is, the circumferential permeance distribution between the stator and the rotor has a spatial secondary component caused by the unidirectional shape anisotropy of the stator 11 .
  • the permeance resulting from the elliptical inner diameter of the stator and the permeance resulting from the shape of the teeth are approximated by a sine wave.
  • FIG. 7 is an explanatory view showing the eccentric shaft portion, piston, back pressure chamber and vanes of the compression mechanism portion 20 taken along AA of FIG.
  • FIG. 8 is an explanatory diagram emphasizing that the inner diameter of the stator in FIG. 7 is elliptical. Note that the stator coils and stator slots of the stator are omitted in FIG. 8 to avoid complication.
  • a straight line connecting the center 13c of the rotating shaft and the center 28c of the vane 28 is defined as a straight line C. As shown in FIG. The straight line C coincides with the direction in which the rotation angle of the rotating shaft defined in FIG. 3 is 0°. In FIG. 8, the counterclockwise angle from straight line C is defined as the positive direction.
  • a straight line D is defined as a straight line in the direction of the rotation angle that minimizes the permeance. Since the inner diameter of the stator is elliptical, the direction of this straight line D coincides with the major axis direction of the ellipse.
  • the circumferential angle from the straight line C to the straight line D with the straight line C as a reference is ⁇ .
  • a straight line E is defined as a straight line connecting the center of the magnet 12b that generates a magnetic flux radially outward and the center 13c of the rotating shaft.
  • a straight line F is defined as a straight line connecting a point 23c on the outer diameter of the piston 23 farthest from the center 13c of the rotation shaft and the center 13c of the rotation shaft.
  • the angle in the circumferential direction from the straight line E to the straight line F with the straight line E as a reference is ⁇ .
  • ⁇ since the straight line F is positioned counterclockwise with respect to the straight line E, ⁇ has a positive value.
  • ⁇ becomes a negative value.
  • the rotary compressor of the present embodiment is characterized in that the following formula (1) holds.
  • k is a natural number.
  • the permeance P( ⁇ ) is represented by the following formula (3).
  • the magnetic flux density B( ⁇ , t) of the magnetic gap is the product of the magnetomotive force and the permeance, and is given by the following equation (4).
  • Magnetic energy E g (t) is given by the following equation (5).
  • the direction in which the rotor of the electric motor section rotates counterclockwise is considered positive.
  • load torque generated in the compression mechanism will be described.
  • the clockwise rotation of the rotor of the electric motor section is positive.
  • the waveform of the load torque is approximated by a sinusoidal waveform including a DC offset for convenience. Since the magnitude of the load torque is determined by the phase difference between the vane and the piston, that is, the phase difference between straight lines C and F in FIG. 8, the load torque T L (t) can be approximated by the following equation (9).
  • ⁇ is the phase term of the load torque waveform, and is a parameter that indicates the range in which the rotation angle at which the load torque peaks varies depending on the operating conditions, as will be described later. Comparing equations (8) and (9), in order for the peaks of T C (t) and T L (t) to match, the following equations (10) and (11) must hold.
  • FIG. 9 is a characteristic diagram showing a load torque waveform in steady operation by simulation.
  • the horizontal axis is the rotation angle of the rotating shaft
  • the vertical axis is the load torque of the compression mechanism.
  • the gas pressure of the high-pressure side compression chamber is 350% or more of the gas pressure of the low-pressure side compression chamber
  • the discharge valve opens at a relatively small rotation angle during operation under intermediate conditions, but the discharge valve opens at a larger rotation angle during operation under rated conditions.
  • ⁇ which is the phase term of the load torque waveform, is greater than 180° and less than 250° in steady operation. Therefore, if the range of ⁇ given by equation (12) is set as shown in the following equation (13), the cogging torque of the electric motor section and the load torque of the compression mechanism section cancel each other out during steady operation, and the maximum torque required for the electric motor section can be reduced.
  • the horizontal axis is the rotation angle of the rotor
  • the vertical axis is the torque.
  • the broken line indicates the load torque of the compression mechanism
  • the dashed line indicates the cogging torque of the electric motor
  • the solid line indicates the torque obtained by subtracting the cogging torque from the load torque.
  • the peak of the torque waveform obtained by subtracting the cogging torque from the load torque is smaller than the peak of the load torque waveform. That is, by satisfying the condition of formula (1), the cogging torque of the electric motor section and the load torque of the compression mechanism section cancel each other out, and the maximum torque required for the electric motor section can be reduced.
  • FIG. 11 is a cross-sectional view of a motor portion of a rotary compressor of a comparative example according to the present embodiment.
  • the electric motor section 10 of the comparative example shown in FIG. 11 has six poles and nine stator slots.
  • the right side of the rotor 12 is area A
  • the left side is area B.
  • the right side of the stator 11 is defined as a region C
  • the left side thereof is defined as a region D.
  • the area A and the area B rotate.
  • the magnetic force of the magnets 12b present in the region B of the rotor 12 is smaller than the magnetic force of the magnets 12b present in the region A of the rotor 12 .
  • the number of turns of the stator coil 11b existing in the region D of the stator 11 is smaller than the number of turns of the stator coil 11b existing in the region C of the stator 11 .
  • this electric motor section in which the magnetic force of the rotor and the number of turns of the stator coil are made asymmetrical one torque pulsation occurs per one rotation. With such a configuration, the torque pulsation generated in the electric motor section can cancel the pulsation of the load torque of the compression mechanism section, so that the maximum torque required for the electric motor section can be reduced.
  • the electric motor section of the rotary compressor of this comparative example has a problem of large noise and vibration.
  • the rotor region A and the stator region C face each other, and the rotor region B and the stator region D face each other.
  • the attractive force or repulsive force acting between the regions B and D is smaller than the attractive force or repulsive force acting between the regions A and C. Therefore, in this positional relationship, a force is generated that makes the rotating shaft 13 eccentric in the horizontal direction of the paper surface.
  • the rotor 12 rotates 180° as shown in FIG.
  • the rotor area A and the stator area D face each other, and the rotor area B and the stator area C face each other.
  • the attractive force or repulsive force acting between the regions A and D and the attractive force or repulsive force acting between the regions B and C are substantially the same. Therefore, in this positional relationship, almost no force is generated to eccentrically move the rotating shaft 13 in the horizontal direction of the drawing. Therefore, in the electric motor portion of the rotary compressor of the comparative example, a force that eccentrically moves the rotating shaft is periodically generated, which causes noise and vibration.
  • the magnetomotive forces of the two magnets positioned opposite each other by 180° have the same magnitude and direction.
  • the permeance between the stator and rotor has a waveform of two peaks as shown in FIG. Therefore, when an attractive force acts on one magnet, the same attractive force acts on the magnet located 180 degrees opposite to it. Similarly, when a repulsive force acts on one magnet, the same repulsive force acts on the magnet located opposite to it by 180°.
  • no force is generated to eccentrically move the rotating shaft, so noise and vibration can be suppressed.
  • the spatial secondary component exists in the circumferential permeance distribution between the stator and the rotor
  • the spatial primary component exists in the circumferential magnetomotive force distribution generated by the magnets.
  • the angle between the straight line connecting the center of the rotating shaft and the center of the vane and the straight line extending from the center of the rotating shaft in the direction of the smallest permeance distribution is ⁇
  • the angle between the straight line connecting the center of the rotating shaft and the point on the outer diameter of the piston farthest from the center of the rotating shaft and the straight line connecting the center of the rotating shaft and the center of the magnet that generates the magnetic flux radially outward of the magnetomotive force distribution is ⁇ .
  • the rotary compressor of the present embodiment can suppress the generation of vibration and noise, and can reduce the torque required for the electric motor section. As a result, an increase in the size of the electric motor section can be suppressed. Furthermore, the rotary compressor of the present embodiment does not require additional parts for reducing the torque required for the electric motor section, so that the size of the apparatus can be reduced.
  • the structure of the electric motor section has two poles and three stator slots, but the structure is not limited to this.
  • the rotor of the present embodiment is a so-called embedded magnet rotor in which magnets are embedded in the rotor core, but may be a surface magnet rotor.
  • Embodiment 2 The configuration of the rotary compressor according to the second embodiment is the same as the configuration of the rotary compressor shown in the first embodiment, but differs in the configuration of the electric motor section.
  • FIG. 13 is a cross-sectional view of the rotary compressor according to this embodiment.
  • FIG. 13 is a cross-sectional view of the electric motor section.
  • the electric motor section 10 of the rotary compressor according to the present embodiment has six poles and nine stator slots.
  • the inner diameter of the stator 11 is elliptical, and the outer diameter of the rotor 12 is circular. Therefore, the magnetic gap, which is the radial distance between the outer peripheral surface of the rotor 12 and the inner peripheral surface of the stator 11, changes with the position in the circumferential direction.
  • the six-pole magnets 12b are evenly arranged in the circumferential direction.
  • the respective magnets 12b are called magnet A, magnet B, magnet C, magnet D, magnet E and magnet F in counterclockwise direction. Also, let the magnetomotive forces of the respective magnets be M A , M B , M C , M D , M E and M F .
  • the white arrow indicates the magnetization direction of the magnet 12b. That is, in the rotor 12 of the present embodiment, the magnets 12b magnetized so as to generate a magnetic flux radially outward and the magnets 12b magnetized so as to generate a magnetic flux radially inward are alternately arranged in the circumferential direction.
  • the magnetomotive force of magnet A is the same as the magnetomotive force of magnet D located opposite magnet A by 180°, and the magnetomotive forces of other magnets are the same and smaller than those of magnets A and D. That is, the relationship of the following formula (14) holds.
  • FIG. 14 is a characteristic diagram showing the magnetomotive force of the magnet in this embodiment.
  • the horizontal axis is the position in the circumferential direction
  • the vertical axis is the magnetomotive force of the magnet.
  • the magnetomotive force on the vertical axis is positive when the direction of the magnetomotive force is radially outward.
  • the solid line indicates the magnetomotive force distribution by each magnet.
  • the magnetomotive force distribution of each magnet is approximated by a rectangular wave.
  • the magnetomotive forces of magnet A and magnet D are greater than those of the other magnets. Therefore, the actual magnetomotive force distribution by each magnet becomes a magnetomotive force distribution corresponding to two poles.
  • FIG. 14 the horizontal axis is the position in the circumferential direction
  • the vertical axis is the magnetomotive force of the magnet.
  • the magnetomotive force on the vertical axis is positive when the direction of the magnetomotive force is radially outward.
  • the dashed line indicates the magnetomotive force distribution corresponding to two poles. That is, the shape of the actual magnetomotive force distribution by each magnet is the same shape as the magnetomotive force distribution corresponding to two poles shown by the dashed line.
  • the spatial primary component exists in the circumferential magnetomotive force distribution between the stator and the rotor due to the arrangement of the magnets.
  • the number of poles is set to 2 to generate a 2-pole magnetomotive force distribution. Even if the number of poles is six like the rotary compressor of this embodiment, it is possible to generate a magnetomotive force distribution equivalent to two poles.
  • the cogging torque of the electric motor section and the load torque of the compression mechanism section cancel each other out by satisfying the condition of formula (1) as in the first embodiment, and the maximum torque required for the electric motor section can be reduced.
  • a straight line E is a straight line connecting the center 13c of the rotating shaft and the center of the magnet A that generates a magnetic flux directed radially outward in the magnetomotive force distribution corresponding to two poles.
  • a magnetomotive force distribution corresponding to 2 poles is generated by satisfying the relationship of Expression (14) in the 6-pole rotor.
  • the magnetomotive force of at least one pole should be different from the magnetomotive force of the other poles.
  • a magnetomotive force distribution corresponding to 2 poles can be generated if the following equation (15) holds.
  • the magnetomotive force of one magnet that generates a magnetic flux radially outward must be the same as the magnetomotive force of a magnet placed at a position 180° opposite. If the magnetomotive forces of these magnets are different, a force is periodically generated that causes the rotating shaft to be eccentric with respect to the rotor. Also, if all the magnets have the same magnetomotive force, a magnetomotive force distribution corresponding to two poles cannot be generated.
  • Embodiment 3 The configuration of the rotary compressor according to Embodiment 3 is the same as the configuration of the rotary compressor shown in Embodiment 1, but the configuration of the electric motor section is different.
  • FIG. 15 is a cross-sectional view of the rotary compressor according to this embodiment.
  • FIG. 15 is a cross-sectional view of the electric motor section.
  • the electric motor section 10 of the rotary compressor according to the present embodiment has two poles and three stator slots.
  • the inner diameter of the stator 11 is circular, and the outer diameter of the rotor 12 is also circular. Therefore, the magnetic gap, which is the radial distance between the outer peripheral surface of the rotor 12 and the inner peripheral surface of the stator 11, is constant at positions in the circumferential direction.
  • the stator core 11a of the rotary compressor of the present embodiment is formed by stacking and integrating electromagnetic steel sheets rolled in the horizontal direction of the paper surface of FIG. It is known that a rolled electrical steel sheet has a higher relative permeability in the rolling direction than in a direction perpendicular to the rolling direction. Therefore, in the stator core 11a shown in FIG. 15, the relative magnetic permeability in the horizontal direction of the paper is large and the relative magnetic permeability in the vertical direction of the paper is small. That is, the stator 11 has magnetic anisotropy in one direction. In the electric motor section of the rotary compressor configured in this manner, permeance pulsation having two peaks between the stator 11 and the rotor 12 can be generated.
  • the circumferential permeance distribution between the stator and the rotor has a spatial secondary component due to the unidirectional magnetic anisotropy of the stator. Therefore, in the rotary compressor configured as described above, the cogging torque of the electric motor section and the load torque of the compression mechanism section cancel each other out by satisfying the condition of formula (1) as in the first embodiment, and the maximum torque required for the electric motor section can be reduced.
  • a straight line D is a straight line in the direction of the rotation angle that minimizes the permeance.
  • the straight line D is perpendicular to the rolling direction of the electromagnetic steel sheets.
  • the magnetic steel sheets used for the stator core may be either non-oriented magnetic steel sheets or grain-oriented magnetic steel sheets.
  • the difference between the relative magnetic permeability in the rolling direction and the relative magnetic permeability in the direction perpendicular to the rolling direction is greater in grain-oriented electrical steel sheets than in non-oriented electrical steel sheets. Therefore, using a grain-oriented magnetic steel sheet for the stator core increases the permeance pulsation having two peaks, thereby increasing the effect of reducing the maximum torque required for the electric motor section.
  • the inner diameter of the stator 11 is perfectly circular, but it may be elliptical.
  • the minor axis direction of the ellipse and the rolling direction of the magnetic steel sheet are the same.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur rotatif compact qui supprime la génération de vibrations et de bruit et est en mesure de réduire le couple requis pour une unité de moteur électrique.　Ce compresseur rotatif comprend : une unité de moteur électrique ayant un arbre rotatif ; et une unité de mécanisme de compression. 135°+k×180°<α+β<205°+k×180° est établie lorsque : α représente un angle formé par une ligne droite C, qui relie le centre (13c) d'un arbre rotatif et le centre (28c) d'une aube et une ligne droite D, qui s'étend à partir du centre de l'arbre rotatif dans la direction de la plus petite distribution de perméance ; β représente un angle formé par une ligne droite E, qui relie le centre de l'arbre rotatif et le centre d'un aimant (12b) qui génère un flux magnétique radialement vers l'extérieur et une ligne droite F, qui relie le centre de l'arbre rotatif et un point (23c) sur une section de diamètre externe d'un piston le plus éloigné du centre de l'arbre rotatif ; et k représente un nombre naturel.
PCT/JP2022/001568 2022-01-18 2022-01-18 Compresseur rotatif WO2023139637A1 (fr)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004048912A (ja) * 2002-07-12 2004-02-12 Hitachi Industrial Equipment Systems Co Ltd 永久磁石式回転電機およびそれを用いた圧縮機
JP2015065758A (ja) * 2013-09-25 2015-04-09 日立アプライアンス株式会社 圧縮機
JP2020184836A (ja) * 2019-05-08 2020-11-12 パナソニックＩｐマネジメント株式会社 固定子およびモータ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004048912A (ja) * 2002-07-12 2004-02-12 Hitachi Industrial Equipment Systems Co Ltd 永久磁石式回転電機およびそれを用いた圧縮機
JP2015065758A (ja) * 2013-09-25 2015-04-09 日立アプライアンス株式会社 圧縮機
JP2020184836A (ja) * 2019-05-08 2020-11-12 パナソニックＩｐマネジメント株式会社 固定子およびモータ

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