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WO2011149245A2 - Structure d'un moteur de compresseur électrique - Google Patents

Structure d'un moteur de compresseur électrique Download PDF

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Publication number
WO2011149245A2
WO2011149245A2 PCT/KR2011/003793 KR2011003793W WO2011149245A2 WO 2011149245 A2 WO2011149245 A2 WO 2011149245A2 KR 2011003793 W KR2011003793 W KR 2011003793W WO 2011149245 A2 WO2011149245 A2 WO 2011149245A2
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
motor
stator
shoe
tooth
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/KR2011/003793
Other languages
English (en)
Korean (ko)
Other versions
WO2011149245A3 (fr
WO2011149245A9 (fr
Inventor
구인회
이건호
여형기
이제희
김현규
이정경
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Doowon Electronics Co Ltd
Doowon Technical College
Original Assignee
Doowon Electronics Co Ltd
Doowon Technical College
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
Priority claimed from KR1020100048267A external-priority patent/KR20110128681A/ko
Priority claimed from KR1020100051794A external-priority patent/KR20110132012A/ko
Application filed by Doowon Electronics Co Ltd, Doowon Technical College filed Critical Doowon Electronics Co Ltd
Publication of WO2011149245A2 publication Critical patent/WO2011149245A2/fr
Publication of WO2011149245A3 publication Critical patent/WO2011149245A3/fr
Publication of WO2011149245A9 publication Critical patent/WO2011149245A9/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • 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
    • H02K1/148—Sectional cores
    • 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
    • H02K29/00—Motors or generators having non-mechanical commutating devices, e.g. discharge tubes or semiconductor devices
    • H02K29/03—Motors or generators having non-mechanical commutating devices, e.g. discharge tubes or semiconductor devices with a magnetic circuit specially adapted for avoiding torque ripples or self-starting problems

Definitions

  • the present invention relates to a structure of an electric compressor electric motor.
  • the electric compressor is powered by electricity, a stator including a housing in which refrigerant is introduced and discharged, a stator including a plurality of slots accommodated in the housing, arranged in an annular arrangement, and wound with coils, It includes an electric motor having a rotor located inside and having a permanent magnet, the center of the rotor is coupled to the drive shaft that rotates while interlocking with the rotor integrally.
  • the conventional electric compressor motor has a problem in that cogging torque and torque ripple are generated due to rapid magnetic flux density fluctuation near the magnetic pole conversion of the rotor.
  • the electric motor of such an electric compressor manufactures the shape of the back EMF in a trapezoidal or sinusoidal shape according to the drive method of the inverter, and the shape of the back EMF has a great influence on the controllability and efficiency of the motor, and further, the target back EMF of the sine wave drive inverter Depending on the degree of square wave, sine wave, etc., not sinusoidal wave, noise and vibration also affect efficiency.
  • the motor of the electric compressor needs to be designed and manufactured so that the form of back electromotive force is excellent in terms of efficiency and minimized in terms of noise, vibration, and the like. There was a problem that does not meet.
  • the present invention can reduce the cogging torque and torque ripple by relieving the abrupt magnetic flux density generated near the magnetic pole conversion of the rotor, and the shape of the counter electromotive force so that the counter electromotive force waveform can be as close to the sine wave as possible for driving the sinusoidal wave.
  • the purpose of the present invention is to provide the structure of an electric scroll compressor motor that can minimize the noise and vibration as well as improve the efficiency of the motor by selecting the interval between slots, which is a main variable in the optimum condition.
  • the present invention includes a housing having a refrigerant suction port through which a refrigerant is sucked in and a refrigerant discharge port through which the sucked refrigerant is compressed and discharged, a stator disposed in an annular shape within the housing, and a rotor rotating inside the stator.
  • the stator includes a shoe having one side facing the rotor, an integrally extending radially from the other side of the shoe, a tooth wound with a coil, and an inner circumferential surface thereof.
  • the outer circumferential surface is integrally formed on the outer side and includes a head portion facing the inner surface of the housing, and the angle formed by the other side of the shoe and the side of the tooth mitigates the abrupt magnetic flux density generated near the magnetic pole conversion portion of the rotor. It can be formed at an obtuse angle.
  • the present invention can optimally form the shape of the stator to mitigate the abrupt magnetic flux density generated near the magnetic pole conversion of the rotor, thereby reducing cogging torque and torque ripple, and can mitigate noise and vibration Can be.
  • the present invention can take the shape of the back EMF waveform as close to the sine wave as possible, by selecting the interval between the slots, which is the main variable in the shape of the back EMF as the optimum conditions to improve the efficiency of the motor, as well as smooth the motor Driving can be implemented and noise and vibration can be reduced.
  • FIG. 1 is a front sectional view showing an electric scroll compressor motor according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view taken along the line II-II of FIG. 1.
  • FIG. 3 is a view illustrating the shoe watch in the stator of FIG. 2.
  • FIG. 4 is a graph illustrating a cogging torque ratio according to the angle of the shoe and the tooth of FIG. 3.
  • FIG. 5 is a diagram illustrating slot opening between stator slots in the motor of FIG. 2.
  • FIG. 6 is a graph illustrating a counter electromotive force waveform according to the slot opening of FIG. 5.
  • FIG. 7 is a graph illustrating a distortion rate of the back EMF waveform according to the slot opening of FIG. 5.
  • FIG. 8 is a graph illustrating performance characteristics of the motor according to the slot open of FIG. 5.
  • the motor-driven compressor 800 is supplied with a driving force by electricity, and includes a housing 100 and a drive shaft 580, and the housing 100. It includes an electric motor 500 is accommodated therein and the drive shaft 580 is coupled and a rotational force is generated, and a scroll compression unit 700 receives the rotational force from the electric motor 500 to compress the refrigerant.
  • the electric compressor 800 is a scroll compressor including a scroll compressor as an embodiment, but is not limited thereto.
  • the housing 100 has a coolant inlet 110 through which a coolant flows in one upper portion, and a coolant discharge port 120 through which the coolant introduced in one front side is compressed and discharged.
  • the scroll compression unit 700 includes a swing scroll 200 and a fixed scroll 300.
  • the swinging scroll 200 is accommodated in the housing 100 to rotate by the driving force transmitted from the electric motor 500, and has a spiral swinging wrap 210.
  • the fixed scroll 300 is fixed to its position in combination with the housing 100 in the housing 100, and between the orbiting wrap 210 during the pivoting movement of the orbiting scroll 200
  • a spiral fixed wrap (310) corresponding to the pivot wrap (210) is provided.
  • the motor 500 and the swinging scroll 200 further includes an eccentric operation unit 400 which is provided at one end of the driving shaft 580 to induce the swinging movement of the swinging scroll 200.
  • the eccentric operation unit 400 is coupled so that the rotation center is eccentric with respect to the rotation center of the drive shaft 580 to perform a rotational movement in conjunction with the drive shaft 580 integrally in accordance with the rotation of the drive shaft 580 and At the same time, the pivoting movement of the swinging scroll 200 is induced by the rotational rotational movement while the relative sliding movement with respect to the drive shaft 580.
  • the eccentric operating unit 400, the sliding bush is eccentrically coupled to the drive shaft 580 as shown with the swing scroll 200 as an example, this is a crank pin as an embodiment
  • any configuration may be provided between the driving shaft 580 and the turning scroll 200 such as an eccentric bush to induce a turning motion of the turning scroll 200.
  • reference numeral 410 denotes a rotation preventing means.
  • the electric motor 500 is supplied with a driving force by electricity, and includes a stator 530, a rotor 570, and a drive shaft 580.
  • the stator 530 is a stator.
  • the stator 530 is located in the housing 100 and has an annular shape having a space in the center thereof.
  • the stator 530 includes a coil 510 and slots 520 in which the coils 510 are wound and formed in plural and coupled to each other in an annular shape.
  • the rotor 570 is a rotor, the rotor core 540 and the rotor core 540 which is rotatably arranged with a space (A) at a predetermined interval inside the stator 530, and in the circumferential direction of the rotor core 540 It includes a plurality of permanent magnets 550 are arranged alternately to the other pole and spaced apart along the outer circumferential direction of the rotor core 540. In this case, spacers 560 of a predetermined space are formed at both ends of the permanent magnet 550 to increase magnetic resistance to prevent magnetic flux leakage.
  • the drive shaft 580 is axially coupled to the central portion of the rotor core 540 and rotates integrally with the rotor 570. At this time, the drive shaft 580 is rotated in a state in which the eccentric operation unit 400 is eccentrically coupled to one end thereof so as to be loaded with an eccentric load by the eccentric operation unit 400.
  • the rotor 220 the eight permanent magnets 222 so that the N pole S poles are alternately spaced apart along the outer circumferential direction of the rotor 220.
  • the stator 210 is a structure of 8 pole-12 slots 212 in which 12 slots 212 are arranged in an annular arrangement.
  • the stator 530 may include a plurality of slots 520 that are annularly arranged inside the housing 100. And the slot 520 has a substantially laterally divided 'H' shape, a shoe 521, a tooth 522 radially coupled to the shoe 521, and the tooth. And a head portion 523 coupled with 522.
  • the shoe 521 is formed such that one side (inner circumferential surface) faces the outer circumferential surface of the rotor 570, and both sides protrude from the tooth 522.
  • the tooth 522 protrudes integrally in the radial direction from the other side of the shoe 521 and the coil 510 is wound to the outside.
  • the head portion 523 has an inner circumferential surface formed integrally with the outside of the tooth 522, an arc-shaped outer circumferential surface facing the inner circumferential surface of the housing 100, and both sides have a concave and convex coupling with neighboring slots 520.
  • Coupling grooves 525 (see FIG. 5) and coupling protrusions 524 are formed, respectively.
  • the motor 500 of the electric scroll compressor 800 is a structure that can reduce the cogging torque, it can reduce the abrupt magnetic flux density generated near the magnetic pole conversion of the permanent magnet 550
  • the shape of the slot 520 is optimally formed.
  • the cogging torque is as follows.
  • the cogging torque is generated by a force to return to the stable position when the permanent magnet 550 is out of the stable position, and is caused by a magnetic flux acting on the side of the stator 530 tooth 522.
  • the cogging torque is generated. That is, cogging torque does not occur when the magnetic flux acting on the side of the tooth 522 is in a balanced position, but when the magnetic flux acting on the side of the tooth 522 is in an UnAligned position. Cogging torque is generated. However, since the magnetic flux tends to take a path in which the reluctance is minimum, the magnitude of the cogging torque and the like change according to the shape of the side of the tooth 522. Thus, the cogging torque is minimal when the optimum shape is to balance the magnetic flux acting on the side of the tooth 522.
  • the teeth 522 and the shoe 521 are formed along a dimension set in a predetermined space in the housing 100, and the other side surface of the shoe 521. And a change in the angle formed by the side of the tooth 522 affects the area change of the protruding portions of both ends of the shoe 521.
  • the other side of the shoe 521 and the side of the tooth 522 The larger the angle formed, the smaller the end area of the shoe 521 is.
  • the angle formed between the other side of the shoe 521 and the side of the tooth 522 affects the shape and the area including the shape and the length of the shoe 521 and the tooth 522.
  • the shape and area of the shoe 521 and the tooth 522 are factors that change the size and shape of the cogging torque.
  • abrupt magnetic flux density generated near the magnetic poles of the rotor 570, especially the permanent magnet 550, is alleviated, thereby suppressing cogging torque and torque ripple, and at the same time increasing the drop rate of the slot 520.
  • an angle formed between the other side of the shoe 521 and the side of the tooth 522 is formed to an optimal obtuse angle.
  • the angle ⁇ formed between the other side surface of the shoe 521 and the side surface of the tooth 522 is set to 115 degrees to 120 degrees.
  • the reason for this is that when the inclination angle ⁇ formed between the shoe 521 and the tooth 522 exceeds 120 degrees, a magnetic force line is concentrated at the end of the shoe 521, which affects magnetic saturation and cogging. This is because the torque ratio may be increased, whereas when the inclination angle ⁇ is less than 115 degrees, the stator winding rate may fall and affect the output.
  • the maximum set angle is 120 degrees, as shown in the graph of Figure 4, the magnetic flux generated due to the magnetic saturation of the shoe from the inclination angle of the tooth and shoe from 121 degrees This is because the cogging torque suddenly changes due to the imbalance of.
  • the present embodiment sets the inclination angle of the tooth and shoe on the basis of 120 degrees, and measures the ratio of the cogging torque to the reference angle, that is, the cogging torque at 120 degrees, for each inclination angle.
  • the optimum inclination angle of teeth and shoes was set.
  • the cogging torque ratio is greater than 1, the cogging torque is increased because the magnetic influence of the shoe is large. If the cogging torque ratio is less than 1, the cogging torque is reduced because of the small magnetic influence of the shoe.
  • the cogging torque ratio is 0.99 to 1 as an optimal setting range, and based on this, the inclination angle of the tooth and the shoe
  • the optimal minimum was set at 115. That is, in this embodiment, the inclination angles of the teeth and the shoes are set at 115 degrees to 120 degrees, which is an optimal range with little magnetic influence on the shoes and little change in cogging torque.
  • the Y axis of the graph represents a cogging torque ratio
  • the cogging torque ratio at this time represents (cogging torque at an angle of inclination) / (120 degrees cogging torque)
  • the X axis represents angles of teeth and shoes.
  • the present embodiment is 11.52mm in the circumferential width of the shoe, 1.3mm in the longitudinal direction of the shoe, 7.2mm in the circumferential width of the tooth, and 10.01mm in the longitudinal direction of the tooth, The optimum inclination angle of the tooth and shoe was set.
  • the present invention can take the shape of the back EMF waveform as close to the sine wave as possible, by selecting the interval between the slots, which is the main variable in the shape of the back EMF as the optimum conditions to improve the efficiency of the motor, as well as smooth the motor Driving can be implemented and noise and vibration can be reduced.
  • the plurality of slots 520 that are arranged in an annular shape are spaced apart from each other by shoe openings 521 of the slots 520 having a slot opening (SO) at a predetermined interval.
  • the slot open is one of the main variables for the shape of the counter electromotive force, and in the present embodiment, the noise and vibration of the motor 500 with the optimum interval of the slot open having a major influence on the shape of the counter electromotive force. It can be reduced, as well as to improve the efficiency of the motor, which will be described in detail with reference to the graph of Figures 6 to 8 as follows.
  • the electric motor 500 is a permanent magnet synchronous motor, and the shoe 521 and the tooth 522. And a head portion 523, the angle formed by the side of the tooth 522 and the side of the shoe 521 has a structure of 120 degrees, and the electric motor 500 has 12 slots 520 arranged in an annular shape.
  • the permanent magnet 550 is an 8-pole 12-slot structure in which eight are inserted in an annular shape while alternating poles.
  • the main parameters are the distortion rate and the cogging torque directly related to the performance of the motor. This is because the distortion rate is a factor that affects the difficulty of control, output reduction, vibration and noise when the distortion rate is increased based on the sine wave, and cogging torque has a great influence on the vibration and noise of the motor.
  • the slot open OS which is an interval between the slots 520, is a variable in which the shape and size of the counter electromotive force are changed according to the degree.
  • the slot open is large, the distance between the slots 520 is increased.
  • the shorter the distance between the slots 520 the more favorable for the noise, but the output is low, in order to drive the sine wave of the electric motor 500, the present embodiment, the reverse electromotive force waveform to the sine wave as possible
  • the test motor 500 having the above-described structure so as to be close to the shape, the optimum range of the slot opening was set by experimenting the performance, noise and vibration characteristics of the motor 500 over the range of the slot open distance.
  • the optimum value of the interval between adjacent slots 520 along the circumferential direction of the rotor 540, that is, the slot open, in consideration of the distortion rate and cogging torque is greater than 0 mm and less than 2.0 mm.
  • FIG. 6 which shows a waveform according to each slot open
  • the reason why the slot open is set larger than 0 mm is that the slot open becomes 0 mm so that the distortion ratio is large on the waveform when the slots are closed.
  • FIG. 7 which shows the calculated distortion distribution, it can be seen that the value of the distortion rate is rapidly large under the condition that the slot open becomes 0 mm.
  • the minimum range condition is set to more than 0 mm in consideration of the distortion rate described above.
  • the distortion of the waveform is 5 or less as the use region based on the sine wave, and the distortion is obtained by Equation (1).
  • Vref Bemf voltage size at maximum rpm
  • V_ (slot open) is Bemf voltage size according to slot open
  • ⁇ is 0 degree ⁇ 360 degrees
  • n is the number of data according to ⁇
  • FIG. 8 shows the performance characteristics of the motor according to the slot open.
  • the reason why the slot opening is set to be less than or equal to 2 mm is that the slot opening is greater than 2 mm and the instant the cogging torque is greater than 2.0 mm. This is due to a sharp increase and a steady rise.
  • the reason why the cogging torque increases sharply when the slot open exceeds 2.0 mm is that the cogging torque increases during rotation as the magnetic flux becomes stronger due to magnetic saturation on the shoe 521.
  • the cogging torque was maintained at a relatively low value in the range between the slot opening of 0 mm and 2 mm or less.
  • the cogging torque is increased as the noise and vibration of the motor 500 increases. Therefore, in the present embodiment, the maximum opening is set to the same or smaller range than 2 mm in view of the cogging torque.
  • the embodiment of the present invention realizes smooth driving of the motor 500 by satisfying both the distortion ratio and the optimum condition of the cogging torque based on the sine wave with the slot opening greater than 0 mm and less than 2.0 mm.
  • the electromagnetic noise and vibration of the electric motor 500 can be reduced, so that the efficiency and performance of the electric motor 500 can be improved as a whole.
  • the electric motor 500 of the electric scroll compressor 800 can be miniaturized, lightweight in terms of volume and weight, can achieve high efficiency and high performance, response to the input is fast and speed BLDC motor (brushless DC motor) that can be easily controlled, in detail brushless DC of IPM (Interior permanent magnet type) BLDCM is inserted a plurality of permanent magnets 550 inside the rotor 570 motor) or PMSM (Permanent Magnet Synchronous Motor).
  • BLDC motor brushless DC motor
  • IPM Interior permanent magnet type
  • PMSM Permanent Magnet Synchronous Motor
  • the electric scroll compressor 800 and the electric motor 500 according to the present embodiment may reduce the size to the capacity, and the stator 530 may be moved to the housing 100 of the housing 100 in order to improve the output and the spot ratio of the winding. It is formed of a plurality of slots 520 arranged in an annular shape inside, and uses a concentrated winding system. Further, this embodiment has a hermetic structure and is applied to a vehicle air conditioning system.
  • the electric scroll compressor 800, the motor 500 according to the present embodiment, the other of the shoe 521 of the slot 520 to mitigate the sudden magnetic flux density generated near the magnetic pole conversion of the rotor 570 By forming the side surface and the side surface of the tooth 522 at an obtuse angle, the cogging torque and the torque ripple is reduced to make an optimal structure that can mitigate noise and vibration.
  • the present invention can be used in a vehicle air conditioning system.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Compressor (AREA)
  • Permanent Field Magnets Of Synchronous Machinery (AREA)

Abstract

La présente invention porte sur un corps comportant un orifice d'aspiration de fluide frigorigène à travers lequel un fluide frigorigène est aspiré et un orifice de sortie de fluide frigorigène servant à évacuer le fluide frigorigène aspiré qui a été comprimé; un stator disposé de manière annulaire à l'intérieur du corps; et un rotor qui est disposé au niveau du côté intérieur du stator et qui tourne. Le stator comprend des patins ayant des premières surfaces latérales situées en face du rotor, des dents monobloc qui s'étendent depuis des secondes surfaces latérales des patins dans une direction radiale et sur lesquelles sont enroulés des bobinages, les parties supérieures comportant des surfaces circonférentielles internes entièrement formées sur l'extérieur des dents et des surfaces circonférentielles externes faisant face à la surface interne du corps. L'angle entre la seconde surface latérale de chacun des patins et la surface latérale de chacune des dents peut former un angle obtus afin de réduire la densité de flux magnétique se formant rapidement à proximité de la région de conversion de pôle magnétique du rotor. Par conséquent, le fait de façonner le stator avec une forme optimale pour réduire ainsi la densité de flux magnétique se formant rapidement à proximité de la région de conversion de pôle magnétique du rotor réduit le couple de crantage et l'ondulation du couple, et réduit également le bruit et les vibrations de ce dernier. En outre, l'établissement de la condition optimale pour l'intervalle entre les fentes, qui est la variable principale dans la forme d'une force électromotrice non seulement améliore le rendement du moteur mais assure également son fonctionnement plus régulier et réduit le bruit et les vibrations dudit moteur.
PCT/KR2011/003793 2010-05-24 2011-05-24 Structure d'un moteur de compresseur électrique Ceased WO2011149245A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR10-2010-0048267 2010-05-24
KR1020100048267A KR20110128681A (ko) 2010-05-24 2010-05-24 전동식스크롤압축기 전동기의 구조
KR10-2010-0051794 2010-06-01
KR1020100051794A KR20110132012A (ko) 2010-06-01 2010-06-01 전동식압축기 모터의 구조

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WO2011149245A2 true WO2011149245A2 (fr) 2011-12-01
WO2011149245A3 WO2011149245A3 (fr) 2012-03-01
WO2011149245A9 WO2011149245A9 (fr) 2012-04-19

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CN109643915A (zh) * 2016-09-05 2019-04-16 Lg伊诺特有限公司 定子和包括定子的马达
CN114072987A (zh) * 2019-07-17 2022-02-18 三菱电机株式会社 定子、马达、压缩机以及空气调节机
EP4270732A2 (fr) * 2023-08-22 2023-11-01 Pfeiffer Vacuum Technology AG Pompe à vide à spirales avec moteur synchrone à aimants permanents et procédé de fabrication de la pompe à vide à spirales

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JP4068051B2 (ja) * 2003-12-26 2008-03-26 本田技研工業株式会社 電動機
JP2010041851A (ja) * 2008-08-06 2010-02-18 Daikin Ind Ltd 固定子とケーシングとの固定構造及びそれを備えた圧縮機
JP2010041852A (ja) * 2008-08-06 2010-02-18 Daikin Ind Ltd 固定子、モータ、及び圧縮機
JP2010115019A (ja) * 2008-11-06 2010-05-20 Nippon Densan Corp ポンプ用モータ

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Publication number Priority date Publication date Assignee Title
CN109643915A (zh) * 2016-09-05 2019-04-16 Lg伊诺特有限公司 定子和包括定子的马达
US20190199147A1 (en) * 2016-09-05 2019-06-27 Lg Innotek Co., Ltd. Stator, and motor comprising same
EP3509187A4 (fr) * 2016-09-05 2019-09-11 LG Innotek Co., Ltd. Stator et moteur le comprenant
CN109643915B (zh) * 2016-09-05 2021-09-03 Lg伊诺特有限公司 定子和包括定子的马达
CN106528948A (zh) * 2016-10-19 2017-03-22 江苏航天动力机电有限公司 一种基于教与学算法的永磁同步电机设计的计算方法
WO2018072296A1 (fr) * 2016-10-19 2018-04-26 钱伟 Procédé de calcul basé sur un algorithme d'enseignement et d'apprentissage pour la conception d'un moteur synchrone à aimant permanent
CN114072987A (zh) * 2019-07-17 2022-02-18 三菱电机株式会社 定子、马达、压缩机以及空气调节机
EP4002646A4 (fr) * 2019-07-17 2022-07-13 Mitsubishi Electric Corporation Stator, moteur, compresseur et climatiseur
AU2019457513B2 (en) * 2019-07-17 2023-04-27 Mitsubishi Electric Corporation Stator, motor, compressor, and air conditioner
EP4270732A2 (fr) * 2023-08-22 2023-11-01 Pfeiffer Vacuum Technology AG Pompe à vide à spirales avec moteur synchrone à aimants permanents et procédé de fabrication de la pompe à vide à spirales

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