Magnetic circuit component, air feeder, compressor and refrigeration device

Abstract

The magnetic circuit component (31) comprises an iron core (32) and a dynamic vibration absorber (50), the iron core (32) is made of soft magnetic materials and provided with an annular magnet yoke part (34), and the dynamic vibration absorber (50) is arranged on the iron core (32) and reduces vibration of the iron core (32). The dynamic absorber (50) is provided with a weight part (51) and a connecting part (52), and the connecting part (52) connects the weight part (51) and the magnet yoke part (34) and can generate elastic deformation. The dynamic vibration absorber (50) and the iron core (32) are integrally formed.

Description

Technical Field

[0001] The present invention relates to a magnetic circuit component, a blower, a compressor and a refrigeration device. Background Art

[0002] Conventionally, there is known a magnetic circuit consisting of a closed loop containing magnetic flux. In the magnetic circuit, vibration occurs due to changes in magnetic force. In the field of magnetic circuits, there is a problem of reducing this vibration.

[0003] Patent document 1 discloses an electric motor as a type of magnetic circuit. The electric motor of Patent document 1 has a stator core and a stator peripheral plate arranged on the periphery of the stator core. In the electric motor, a plurality of reinforcing plates are provided between the stator peripheral plate and the stator core. The reinforcing plate has a first beam member and a second beam member, and the first beam member and the second beam member are elastic. The first beam member and the second beam member are connected by a connecting member. With such a structure, the support rigidity of the stator core is reduced, and the electromagnetic vibration generated in the stator core is absorbed.

[0004] Prior art literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Publication No. 2009-254012 Summary of the invention

[0007] -Technical problem to be solved by the invention-

[0008] In the motor of Patent Document 1, vibration can be reduced by providing a plurality of reinforcing plates, but on the other hand, the cost increases with the addition of reinforcing plates. In addition, the manufacturing process also adds a step of assembling the reinforcing plates on the motor, which further increases the cost.

[0009] An object of the present disclosure is to reduce vibration generated in an iron core while suppressing an increase in product cost in a magnetic circuit component constituting a part of a magnetic circuit.

[0010] -Technical solutions for solving technical problems-

[0011] The first aspect relates to a magnetic circuit component, which constitutes a part of the magnetic circuit. The magnetic circuit component includes an iron core 32 and a dynamic vibration absorber 50. The iron core 32 is made of soft magnetic material and has an annular yoke portion 34. The dynamic vibration absorber 50 is arranged on the iron core 32 to reduce the vibration of the iron core 32. The dynamic vibration absorber 50 has a hammer portion 51 and a connecting portion 52. The connecting portion 52 connects the hammer portion 51 with the yoke portion 34 and can undergo elastic deformation. The dynamic vibration absorber 50 is formed as a whole with the iron core 32.

[0012] In the first aspect, a dynamic vibration absorber 50 for reducing the vibration of the core 32 is included, and the dynamic vibration absorber 50 is formed integrally with the core 32. Therefore, the vibration of the core 32 can be reduced without adding a new component. In addition, in this aspect, compared with the case where the dynamic vibration absorber 50 is composed of another component independent of the core 32, the work of assembling the dynamic vibration absorber 50 on the core 32 is not generated. As a result, the increase in the product cost of the magnetic circuit component 31 can be suppressed, and the vibration generated in the core 32 can be reduced.

[0013] According to a second aspect, in addition to the first aspect, the weight portion 51 extends along the circumferential direction of the yoke portion 34 .

[0014] In the second aspect, since the weight portion 51 is formed to extend along the circumferential direction of the annular yoke portion 34 , the magnetic path of the yoke portion 34 can be ensured, and the size of the entire core 32 can be reduced.

[0015] A third aspect is the first aspect or the second aspect, wherein the dynamic vibration absorber 50 is disposed on the outer periphery or inside of the yoke part 34 .

[0016] In the third aspect, the vibration of the core 32 is reduced by the dynamic vibration absorber 50 provided on the outer periphery or inside the yoke portion 34 .

[0017] According to a fourth aspect, based on any one of the first to third aspects, the iron core 32 is formed by a plurality of electromagnetic steel plates M stacked on top of each other, and the plurality of electromagnetic steel plates M are fastened together at the weight portion 51 .

[0018] In the fourth aspect, since the plurality of electromagnetic steel sheets M constituting the core 32 are fastened to each other at the weight portion 51, the fastened portion is formed at a portion where magnetic flux does not pass. Therefore, an increase in iron loss due to fastening can be suppressed.

[0019] In the fifth aspect, based on any one of the first to fourth aspects, the magnetic circuit includes a rotor 40 and a stator 31, the rotor 40 is configured to be rotatable around the axis of the rotating shaft 20, the stator 31 is arranged opposite to the rotor 40 in the radial direction of the rotating shaft 20, the stator 31 has a stator core 32 as the iron core 32 and a coil 33 wound on the stator core 32, and the dynamic vibration absorber 50 is arranged on the side opposite to the rotor 40 in the radial direction.

[0020] In the fifth aspect, the vibration of the core 32 is reduced by the dynamic vibration absorber 50 disposed on the side opposite to the rotor 40 in the radial direction of the rotating shaft 20 .

[0021] According to a sixth aspect, in any one of the first to fifth aspects, the magnetic circuit component constitutes a part of the motor (30).

[0022] In the sixth aspect, the increase in the product cost of the electric motor 30 can be suppressed, and the vibration of the iron core 32 can be reduced.

[0023] According to a seventh aspect, based on any one of the first to fifth aspects, the magnetic circuit component constitutes a part of a magnetic bearing.

[0024] In the seventh aspect, the increase in the product cost of the magnetic bearing can be suppressed, and the vibration of the iron core 32 can be reduced.

[0025] According to an eighth aspect, in any one of the first to fourth aspects, the magnetic circuit component constitutes a part of a reactor.

[0026] In the eighth aspect, the increase in the product cost of the reactor can be suppressed, and the vibration of the iron core 32 can be reduced.

[0027] The ninth aspect relates to an air blower, comprising an electric motor (30) and a fan, wherein the electric motor (30) comprises the magnetic circuit component of the sixth aspect, and the fan is driven by the electric motor (30).

[0028] In the ninth aspect, it is possible to provide a blower in which an increase in product cost is suppressed and vibration is reduced.

[0029] A tenth aspect relates to a compressor, comprising the magnetic circuit component of the sixth aspect or the seventh aspect.

[0030] In the tenth aspect, it is possible to provide a compressor in which an increase in product cost is suppressed and vibration is reduced.

[0031] The eleventh aspect relates to a refrigeration device including the compressor (10) according to the tenth aspect and a refrigerant circuit (R) through which the refrigerant compressed by the compressor (10) flows.

[0032] In the eleventh aspect, it is possible to provide a refrigeration device in which an increase in product cost is suppressed and vibration is reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 is a schematic diagram of a piping system of a refrigeration device according to a first embodiment;

[0034] Figure 2 is an axial cross-sectional view of a compressor according to a first embodiment;

[0035] Figure 3 is a cross-sectional view in a direction perpendicular to the axial direction, schematically showing the cross-sectional shape of the electric motor according to the first embodiment;

[0036] Figure 4 yes Figure 3 An enlarged view of Box IV;

[0037] Figure 5 is along Figure 4 The cross-sectional view observed by the V-V arrow;

[0038] Figure 6 is a graph showing simulation results;

[0039] Figure 7 is an enlarged view of a main part involved in Modification 1 of the first embodiment;

[0040] Figure 8 is an enlarged view of a main part involved in Modification 2 of the first embodiment;

[0041] Fig. 9 is an enlarged view of a main part involved in Modification 3 of the first embodiment;

[0042] Fig.10 is an enlarged view of a main part involved in Modification 4 of the first embodiment;

[0043] Fig.11 is an enlarged view of a main part involved in Modification 5 of the first embodiment;

[0044] Fig.12 This is equivalent to the modification example 6 of the first embodiment. Figure 5 's picture;

[0045] Fig.13 The modification example 7 of the first embodiment is equivalent to Figure 5 's picture;

[0046] Fig.14 is an enlarged view of a main part involved in Modification 8 of the first embodiment;

[0047] Fig.15 The second embodiment is equivalent to Figure 3 . DETAILED DESCRIPTION

[0048] The following is a detailed description of the embodiments of the present disclosure with reference to the accompanying drawings. It should be noted that the present disclosure is not limited to the embodiments shown below, and various changes can be made without departing from the technical concept of the present disclosure. The drawings are used to conceptually illustrate the present disclosure, so in order to facilitate understanding, the size, ratio or quantity is sometimes exaggerated or simplified as needed.

[0049] (First Embodiment)

[0050] The first embodiment will be described below. The magnetic circuit component 31 of the present disclosure constitutes a part of the electric motor 30. The electric motor 30 of the present embodiment is provided in the compressor 10 of the refrigeration device 1.

[0051] (1) Overview of Refrigeration Equipment

[0052] like Figure 1 As shown, the refrigeration device 1 includes a compressor 10. The refrigeration device 1 has a refrigerant circuit R filled with refrigerant. The refrigerant circuit R has the compressor 10, a radiator 2, a decompression mechanism 3, and an evaporator 4. The decompression mechanism 3 is an expansion valve. The refrigerant circuit R performs a vapor compression refrigeration cycle.

[0053] In the refrigeration cycle, the refrigerant compressed by the compressor 10 releases heat to the air in the radiator 2. The refrigerant after releasing the heat is decompressed by the decompression mechanism 3 and evaporates in the evaporator 4. The evaporated refrigerant is sucked into the compressor 10.

[0054] The refrigeration device 1 is an air conditioning device. The air conditioning device may also be a dedicated refrigeration machine, a dedicated heating machine, or an air conditioning device that switches between refrigeration and heating. In this case, the air conditioning device has a switching mechanism (such as a four-way reversing valve) that switches the circulation direction of the refrigerant. The refrigeration device 1 may also be a water heater, a cooling unit, a cooling device that cools the air in a warehouse, etc. The cooling device cools the air inside a cold storage, a freezer, a container, etc. The pressure reducing mechanism 3 may also be composed of an electronic expansion valve, a temperature-sensitive expansion valve, an expander, or a capillary tube.

[0055] (2) Compressor

[0056] like Figure 2 As shown, the compressor 10 has a housing 11, an electric motor 30, a drive shaft 20 and a compression mechanism 22. The compressor 10 is a rotary compressor. Strictly speaking, the compressor 10 is a swing piston compressor. The compressor 10 can also be a scroll compressor, a screw compressor or a turbo compressor.

[0057] (2-1) Shell

[0058] The housing 11 accommodates the electric motor 30, the drive shaft 20, and the compression mechanism 22. The housing 11 is a fully closed container. The high-pressure refrigerant discharged from the compression mechanism 22 fills the interior of the housing 11.

[0059] The shell 11 is made of a metal material. The shell 11 has a trunk 12, a bottom 13 and a top 14. The trunk 12 is a cylindrical member made of metal. Openings are formed at both axial ends of the trunk 12. In the present embodiment, the axial direction of the trunk 12 corresponds to the vertical direction. The bottom 13 closes the opening on the lower side of the trunk 12. The top 14 closes the opening on the upper side of the trunk 12.

[0060] (2-2) Electric motor

[0061] Figure 2 and Figure 3 The motor 30 shown is an example of a magnetic circuit. The motor 30 is arranged above the compression mechanism 22. The operating frequency of the motor 30 is controlled by an inverter. In other words, the compressor 10 is an inverter compressor whose operating frequency is variable.

[0062] like Figure 2 As shown, the motor 30 has a stator 31 and a rotor 40. The stator 31 is supported on the body 12 of the housing 11. The stator 31 corresponds to a magnetic circuit component of the present disclosure.

[0063] like Figure 3 As shown, the stator 31 includes a stator core 32, a coil 33 wound around the stator core 32, and a dynamic vibration absorber 50. The stator core 32 corresponds to the core of the present disclosure. The motor 30 is an electromagnetic device that generates a rotation torque in the rotor 40 by energizing the coil 33.

[0064] The stator core 32 is formed by stacking electromagnetic steel sheets M, which are soft magnetic materials, in the axial direction. The stator core 32 is formed in a cylindrical shape. Figure 3 As shown, the stator core 32 includes an annular yoke portion 34 and a plurality of (nine in the present embodiment) teeth portions 35 extending radially inward from the inner periphery of the yoke portion 34 .

[0065] The dynamic vibration absorber 50 is provided on the stator core 32. The dynamic vibration absorber 50 is used to reduce the vibration of the stator core 32. The details of the stator 31 will be described later.

[0066] The rotor 40 is arranged inside the stator core 32. The drive shaft 20 is fixed to the axis of the rotor 40. In other words, the stator core 32 is arranged opposite to the rotor 40 in the radial direction of the drive shaft 20. A plurality of permanent magnets 42 are embedded inside the rotor 40. An annular gap (so-called air gap) is formed between the teeth 35 of the stator 31 and the rotor 40 when viewed in the axial direction.

[0067] (2-3) Drive shaft

[0068] The drive shaft 20 extends in the vertical direction along the axis of the housing 11. The drive shaft 20 is driven to rotate by the motor 30. The drive shaft 20 is rotatably supported by bearings 21 and 29. The drive shaft 20 corresponds to the rotating shaft of the present disclosure.

[0069] (2-4) Compression mechanism

[0070] The compression mechanism 22 has a cylinder 23 and a piston 24 disposed inside the cylinder 23. A cylinder chamber 25 is formed between the inner peripheral surface of the cylinder 23 and the outer peripheral surface of the piston 24. In the cylinder chamber 25, the fluid is compressed by the piston 24, and the piston 24 is driven by the drive shaft 20.

[0071] (2-5) Suction pipe and discharge pipe

[0072] The compressor 10 has a suction pipe 26 and a discharge pipe 27. The suction pipe 26 penetrates the trunk 12 in the radial direction and communicates with the cylinder chamber 25. The low-pressure refrigerant in the refrigerant circuit R is sucked into the cylinder chamber 25 via the suction pipe 26. The discharge pipe 27 penetrates the top 14 in the axial direction and communicates with the internal space of the shell 11. The refrigerant compressed by the compression mechanism 22 flows through the air gap of the motor 30 and is sent to the refrigerant circuit R from the discharge pipe 27.

[0073] (3) Details of the stator

[0074] Reference Figure 3 to Figure 5 The details of the stator 31 are described below. It should be noted that, in the following description, unless otherwise specified, "axial direction", "circumferential direction" and "radial direction" respectively refer to the axial direction, circumferential direction and radial direction of the yoke portion 34 of the stator 31. Figure 2 As shown, the axial direction of the yoke portion 34 corresponds to the axial direction of the drive shaft 20 .

[0075] As described above, the stator 31 includes the stator core 32, the coil 33, and the dynamic vibration absorber 50. The stator core 32 includes the annular yoke portion 34 and the plurality of teeth portions 35.

[0076] The teeth 35 extend radially inward from the inner periphery of the yoke 34. The coil 33 is wound around each tooth 35 by, for example, concentrated winding. Coil slots 36 are formed between adjacent teeth 35 to accommodate the coil 33.

[0077] In the present embodiment, the plurality of electromagnetic steel sheets M constituting the stator core 32 are fastened together at the yoke portion 34. In the present embodiment, the electromagnetic steel sheets M are fastened together by riveting. It should be noted that as a method of fastening the electromagnetic steel sheets M, welding, bonding, etc. may be used in addition to riveting.

[0078] (3-1) Supporting part

[0079] like Figure 3 As shown, the stator core 32 has a plurality of (nine in the present embodiment) support portions 37. The stator core 32 is supported on the body portion 12 of the housing 11 by the support portions 37. The support portions 37 are arranged at predetermined intervals from each other in the circumferential direction. Each support portion 37 protrudes radially outward from the outer periphery of the yoke portion 34. Each support portion 37 is embedded and fixed in a manner of contacting the inner peripheral surface of the body portion 12. Thus, the stator core 32 is held on the housing 11.

[0080] (3-2) Dynamic vibration absorber

[0081] The stator 31 has a plurality of (eighteen in this embodiment) dynamic vibration absorbers 50. Each dynamic vibration absorber 50 is provided on the outer periphery of the yoke portion 34. Each dynamic vibration absorber 50 is arranged in a small gap G formed between the inner peripheral surface of the body portion 12 and the outer peripheral surface of the yoke portion 34. Each dynamic vibration absorber 50 is arranged on the side opposite to the rotor 40 in the radial direction.

[0082] Adjacent dynamic vibration absorbers 50 are arranged on both sides of the circumference with one support portion 37 between them. It should be noted that adjacent dynamic vibration absorbers 50 may also be adjacent to each other without one support portion 37 between them. Each dynamic vibration absorber 50 is arranged on the radially outer side of the coil slot 36. In addition, as Figure 5 As shown, each dynamic vibration absorber 50 is formed from one axial end to the other end of the stator core 32 .

[0083] like Figure 4 As shown, the dynamic vibration absorber 50 is configured to be L-shaped when viewed along the axial direction. The dynamic vibration absorber 50 has a hammer portion 51 and a connecting portion 52. The hammer portion 51 extends along the circumferential direction of the yoke portion 34. The hammer portion 51 is formed into a roughly rectangular parallelepiped shape. The hammer portion 51 is formed into a roughly rectangular shape with the circumferential direction as the long side and the radial direction as the short side when viewed along the axial direction. The hammer portion 51 does not contact the inner peripheral surface of the trunk portion 12. The hammer portion 51 also does not contact the outer peripheral surface of the yoke portion 34.

[0084] The connection portion 52 connects the hammer portion 51 and the yoke portion 34. Specifically, the connection portion 52 connects the outer periphery of the yoke portion 34 and one circumferential end of the hammer portion 51. The connection portion 52 extends in the radial direction. The connection portion 52 is formed in a substantially rectangular parallelepiped shape. The connection portion 52 is elastically deformable. Figure 4 As shown in FIG. 1 , the circumferential length W1 of the connecting portion 52 is extremely small compared to the circumferential length W2 of the plummet portion 51 . Therefore, the connecting portion 52 is more easily elastically deformed than the plummet portion 51 .

[0085] When the yoke portion 34 of the stator core 32 vibrates at a natural frequency, the dynamic vibration absorber 50 vibrates in a phase different from the vibration of the yoke portion 34 , thereby reducing the vibration of the stator core 32 .

[0086] It should be noted that "vibrating at a phase different from the vibration of the yoke part 34" mentioned here includes vibrating at a frequency different from the natural vibration frequency of the yoke part 34. In this case, the phase difference between the natural vibration of the yoke part 34 and the vibration of the dynamic vibration absorber 50 changes with time.

[0087] “Vibrating in a phase different from the vibration of the yoke portion 34” also includes a case where the yoke portion 34 vibrates at the same frequency as the natural vibration frequency and in a phase different from the phase of the natural vibration of the yoke portion 34. In this case, for example, when the phase difference between the natural vibration of the yoke portion 34 and the vibration of the dynamic vibration absorber 50 is 90 degrees to 270 degrees, the natural vibration of the yoke portion 34 and the vibration of the dynamic vibration absorber 50 vibrate in a manner of canceling each other out, thereby reducing the vibration of the stator core 32. For example, when the phase difference between the natural vibration of the yoke portion 34 and the vibration of the dynamic vibration absorber 50 is 0 degrees to 90 degrees, or 270 degrees to 360 degrees, the peak of the natural vibration of the yoke portion 34 and the peak of the vibration of the dynamic vibration absorber 50 are offset, thereby reducing the peak value of the vibration of the stator core 32.

[0088] When the rotor 40 rotates, a magnetic attraction force is generated between the rotor 40 and the stator 31. This force is called electromagnetic force. The electromagnetic force acts on the stator core 32, causing the stator core 32 to vibrate.

[0089] In the dynamic vibration absorber 50 of the present embodiment, when the stator core 32 vibrates, the connection portion 52 becomes a node, and the top end portion (the other end in the circumferential direction) of the weight portion 51 becomes an antinode and vibrates. In this way, the weight portion 51 vibrates in conjunction with the vibration of the stator core 32, and the radial vibration of the stator core 32 caused by the electromagnetic force can be reduced.

[0090] Here, the dynamic vibration absorber 50 of the present disclosure can be regarded as a cantilever beam structure. The natural vibration frequency f of the cantilever beam can be expressed by the following formula [Math. 1].

[0091] [Mathematical formula 1]

[0092]

[0093] In the above formula [Formula 1], m is the mass (kg) acting on the top of the beam, and k is the rigidity (N / m) of the cantilever beam. It should be noted that the rigidity k of the cantilever beam can be expressed by the following formula [Formula 2].

[0094] [Mathematical formula 2]

[0095]

[0096] In the above formula [Math. 2], E is Young's modulus, I is area moment of inertia, and L is the length of the beam.

[0097] According to the above formula [Formula 1], for example, if the circumferential length W1 of the connecting portion 52 is increased, the cross-sectional area of ​​the connecting portion 52 increases, and thus the area moment of inertia I increases. As a result, since the rigidity k of the connecting portion 52 increases, the natural vibration frequency f of the dynamic vibration absorber 50 can be increased. On the other hand, for example, if the circumferential length W2 of the hammer portion 51 is reduced, the mass m of the hammer portion 51 is reduced. Therefore, the natural vibration frequency f of the dynamic vibration absorber 50 in this case can be increased. In this way, in the dynamic vibration absorber 50 of the present embodiment, by changing the circumferential length W1 of the connecting portion 52 and the circumferential length W2 of the hammer portion 51, the natural vibration frequency f of the dynamic vibration absorber 50 can be set to a desired natural vibration frequency.

[0098] The dynamic vibration absorber 50 is formed integrally with the stator core 32. Specifically, the dynamic vibration absorber 50 is made of the same soft magnetic material as the stator core 32, and is made of the electromagnetic steel sheet M constituting the stator core 32. The dynamic vibration absorber 50 is formed by punching the electromagnetic steel sheet M using a die and stacking the punched electromagnetic steel sheets M by stamping or the like, and the shape of the die is such that the portion corresponding to the stator core 32 and the portion corresponding to the dynamic vibration absorber 50 are integrated. In other words, the dynamic vibration absorber 50 can be formed simultaneously in the process of forming the stator core 32.

[0099] According to the above, since the dynamic vibration absorber 50 is formed integrally with the stator core 32, the dynamic vibration absorber 50 can be provided without adding a new component to the stator 31. In addition, since there is no need to provide a process for assembling the dynamic vibration absorber 50 in addition to the process for manufacturing the stator core 32, the increase in the assembly process can be suppressed. As a result, the increase in the manufacturing cost of the stator 31 can be suppressed, and the vibration generated in the stator core 32 can be reduced.

[0100] According to the above configuration, since the process of assembling the dynamic vibration absorber 50 to the stator core 32 is not required, there is no variation in the assembly accuracy of the dynamic vibration absorber 50. Therefore, it is possible to suppress the performance of the dynamic vibration absorber 50 on each stator 31 from varying.

[0101] In addition, the dynamic vibration absorber 50 of the present embodiment is arranged in a small gap G between the inner peripheral surface of the housing 11 and the outer peripheral surface of the stator 31. Therefore, it is not necessary to enlarge the motor 30 itself or to reduce the size of the stator core 32 in order to provide the dynamic vibration absorber 50. As a result, in the present embodiment, the performance of the motor 30 can be maintained, and the vibration generated in the stator core 32 can be reduced.

[0102] (4) Simulation

[0103] A simulation performed to confirm the vibration reduction effect of the dynamic vibration absorber 50 of the present embodiment is described. This simulation is based on a 6-pole 9-slot motor. In this simulation, the acceleration of the outer peripheral surface of the stator core 32 when an excitation force of the natural vibration frequency (resonance frequency) of the stator 31 is applied to the stator 31 is investigated.

[0104] Figure 6 Graph showing frequency-acceleration of the outer peripheral surface of the stator core 32 obtained by this simulation. The solid line in the figure shows the result when an exciting force is applied to a conventional stator that does not include a dynamic vibration absorber. The dotted line in the figure shows the result when an exciting force is applied to a stator 31 including the dynamic vibration absorber 50 of this embodiment.

[0105] In the range of 3200 Hz to 3300 Hz in the figure, it is confirmed that the peak value of the acceleration of the stator 31 of the present embodiment is reduced by about 98% compared with the conventional stator. It is considered that this is because the dynamic vibration absorber 50 vibrates in a phase opposite to the vibration of the stator core 32, thereby reducing the vibration of the stator core 32. Based on this result, it can be confirmed that the stator 31 with reduced vibration of the stator core 32 can be realized by using the dynamic vibration absorber 50 of the present embodiment.

[0106] (5) Features

[0107] (5-1)

[0108] In the stator 31 of the present embodiment, the dynamic vibration absorber 50 is formed integrally with the stator core 32. Therefore, the vibration of the stator core 32 can be reduced without adding a new component. In addition, compared with the case where the dynamic vibration absorber 50 is composed of another component independent of the stator core 32, the work of assembling the dynamic vibration absorber 50 on the stator core 32 is not generated. As a result, the increase in the product cost of the stator 31 can be suppressed, and the vibration generated in the stator core 32 can be reduced.

[0109] (5-2)

[0110] The weight portion 51 of the present embodiment extends along the circumferential direction of the annular yoke portion 34. Therefore, the magnetic path of the yoke portion 34 can be ensured, and the size of the entire stator core 32 can be reduced.

[0111] (5-3)

[0112] The dynamic vibration absorber 50 of this embodiment is provided on the outer periphery of the yoke part 34. Thus, the vibration of the stator core 32 is reduced on the outer periphery of the yoke part 34. In addition, since the dynamic vibration absorber 50 is provided on the outer periphery of the yoke part 34, the dynamic vibration absorber 50 can be easily formed.

[0113] (5-4)

[0114] The dynamic vibration absorber 50 of the present embodiment is disposed on the radially opposite side to the rotor 40. Thus, the vibration of the stator core 32 is reduced in the radially opposite side to the rotor 40.

[0115] (5-5)

[0116] The stator 31 of the present embodiment constitutes a part of the electric motor 30. Therefore, it is possible to suppress an increase in the product cost of the electric motor 30 and reduce vibration of the stator core 32.

[0117] (5-6)

[0118] The dynamic vibration absorber 50 of this embodiment is arranged from one axial end to the other end on the stator core 32. Thus, the vibration generated in the axial direction can be reduced. The so-called vibration generated in the axial direction includes, for example, vibration caused by the central axis deviation of the drive shaft 20, the imbalance of electromagnetic force when eccentricity occurs, etc.

[0119] (5-7)

[0120] The dynamic vibration reducer 50 of the present embodiment is formed in an L-shape. In this way, since the circumferential length W2 of the weight 51 can be set relatively freely, the natural frequency of the dynamic vibration reducer 50 can be easily set to a desired natural frequency.

[0121] (5-8)

[0122] The dynamic vibration absorber 50 of the present embodiment is arranged radially outside the coil slot 36. Here, in the stator core 32, the portion located radially outside the coil slot 36 is more likely to vibrate than the portion located radially outside the tooth portion 35. Therefore, in the present embodiment, by arranging the dynamic vibration absorber 50 radially outside the coil slot 36, the vibration of the stator core 32 can be further reduced.

[0123] (6) Modification

[0124] The above-mentioned embodiment may also adopt the following modified examples. It should be noted that, in principle, in the following description, points different from the above-mentioned embodiment are described.

[0125] (6-1) Modification 1: Shape of the hammer

[0126] like Figure 7 As shown, in the dynamic vibration absorber 50 of the present embodiment, when viewed in the axial direction, the radial length of the weight 51 may not be the same from one circumferential end to the other. This modification also achieves the same effects as the above-mentioned embodiment.

[0127] Specifically, the hammer portion 51 includes a first hammer portion 51a and a second hammer portion 51b having different radial lengths. The first hammer portion 51a is a portion of the hammer portion 51 close to the connecting portion 52. The second hammer portion 51b is a portion of the hammer portion 51 far from the connecting portion 52. The first hammer portion 51a is connected to the second hammer portion 51b. The connecting portion 52 is connected to one circumferential end of the first hammer portion 51a. The radial length D2 of the second hammer portion 51b is longer than the radial length D1 of the first hammer portion 51a (D1<D2). In other words, the hammer portion 51 is configured such that its top end portion is heavier than the middle portion.

[0128] In this modification, for example, Figure 7 As shown in (a), the plummet 51 may be configured such that the outer edge of the first plummet 51a is located at the same position as the outer edge of the second plummet 51b in the radial direction. In this case, the inner edge of the second plummet 51b is located radially inward of the inner edge of the first plummet 51a.

[0129] In this variation, if Figure 7 As shown in (b), the plummet 51 may be configured such that the position of the outer edge of the first plummet 51a is different from the position of the outer edge of the second plummet 51b in the radial direction. Figure 7 In (b), the outer edge of the second weight portion 51b is located radially outward from the outer edge of the first weight portion 51a. In this case, the inner edge of the second weight portion 51b is located radially inward from the inner edge of the first weight portion 51a.

[0130] (6-2) Modification 2: Shape of the hammer

[0131] like Figure 8 As shown, the dynamic vibration absorber 50 of this embodiment can also be configured to be I-shaped when viewed along the axial direction. In this case, the connecting portion 52 is provided on the supporting portion 37 of the stator core 32. The connecting portion 52 connects the side edge of the supporting portion 37 with one circumferential end of the hammer portion 51. The connecting portion 52 extends in the circumferential direction. This modified example also has the same effect as the above-mentioned embodiment.

[0132] In this modification, for example, Figure 8 As shown in (a), the weight portion 51 may be configured such that, when viewed in the axial direction, the radial length D is the same from one end to the other end in the circumferential direction.

[0133] In this variation, if Figure 8 (b) and Figure 8 As shown in (c), similar to the above-mentioned modification 1, the plummet 51 may also include a first plummet 51a and a second plummet 51b having different radial lengths. Figure 8As shown in (b), the plummet 51 may also be configured such that, in the radial direction, the position of the outer edge of the first plummet 51a is the same as the position of the outer edge of the second plummet 51b. Figure 8 As shown in (c), the weight portions 51 may be configured such that the position of the outer edge portion of the first weight portion 51a and the position of the outer edge portion of the second weight portion 51b are different in the radial direction.

[0134] (6-3) Modification 3: Shape of the hammer

[0135] like Fig. 9 As shown, the dynamic vibration absorber 50 of this embodiment may also be configured to be T-shaped when viewed in the axial direction. In this case, the connecting portion 52 connects the outer peripheral surface of the yoke portion 34 and the circumferential center of the weight portion 51. This modification also has the same effects as the above embodiment.

[0136] In this modification, for example, Fig. 9 As shown in (a), the weight portion 51 may be configured such that, when viewed in the axial direction, the radial length D is the same from one end to the other end in the circumferential direction.

[0137] In this variation, if Fig. 9 (b) and Fig. 9 As shown in (c), similar to the above-mentioned modification example 1, the hammer portion 51 may also have a first hammer portion 51a and a second hammer portion 51b having different radial lengths. In this modification example, the hammer portion 51 has one first hammer portion 51a and two second hammer portions 51b. The first hammer portion 51a is a portion formed in the center of the hammer portion 51. Each second hammer portion 51b is a portion formed at both circumferential end portions of the first hammer portion 51a. The radial length D2 of the second hammer portion 51b is longer than the radial length D1 of the first hammer portion 51a (D1<D2). In other words, the hammer portion 51 is configured so that the top end portions on both sides of the circumference are heavier than the middle portion.

[0138] In this variation, if Fig. 9 As shown in (b), the plummet 51 may also be configured such that, in the radial direction, the position of the outer edge of the first plummet 51a is the same as the position of the outer edge of the second plummet 51b. Fig. 9 As shown in (c), the weight portions 51 may be configured such that the position of the outer edge portion of the first weight portion 51a and the position of the outer edge portion of the second weight portion 51b are different in the radial direction.

[0139] (6-4) Modification 4: Arrangement of dynamic vibration absorber

[0140] like Fig.10 As shown, the dynamic vibration absorber 50 may also be arranged radially outside the tooth portion 35. Fig.10In the embodiment, the adjacent dynamic vibration absorbers 50 are adjacent to each other without a support portion 37 therebetween, but in this modification, the adjacent dynamic vibration absorbers 50 may be arranged on both sides in the circumferential direction with a support portion 37 therebetween. In this modification, as in the above-mentioned embodiment, the increase in product cost can be suppressed, and the vibration generated in the stator core 32 can be reduced.

[0141] (6-5) Modification 5: Arrangement of dynamic vibration absorber

[0142] like Fig.11 As shown, the dynamic vibration absorber 50 may also be disposed inside the yoke portion 34. Specifically, a relatively small space is formed inside the yoke portion 34, and the dynamic vibration absorber 50 is accommodated in the space. In this modified example, as in the above-mentioned embodiment, the increase in product cost can be suppressed, and the vibration generated in the stator core 32 can be reduced. It should be noted that in Fig.11 In the figure, a dynamic vibration absorber 50 configured to be T-shaped when viewed in the axial direction is shown as an example, but the dynamic vibration absorber 50 may be configured to be L-shaped or I-shaped when viewed in the axial direction as in the above-mentioned embodiment and modified examples 1 and 2.

[0143] (6-6) Modification 6: Axial Arrangement of Dynamic Vibration Absorber

[0144] like Fig.12 As shown, the dynamic vibration absorber 50 may not be formed from one axial end to the other end of the stator core 32. In this case, the axial length of the dynamic vibration absorber 50 is shorter than the axial length of the stator core 32. In this modification, as in the above-mentioned embodiment, the increase in product cost can be suppressed, and the vibration generated in the stator core 32 can be reduced.

[0145] In this modification, for example, Fig.12 As shown in (a), one dynamic vibration absorber 50 may be arranged in the axial center. In this case, the dynamic vibration absorber 50 is not formed on the electromagnetic steel sheets M located on the upper and lower sides of the electromagnetic steel sheets M constituting the stator core 32.

[0146] In this variation, if Fig.12 As shown in (b), a plurality of (two in this modified example) dynamic vibration absorbers 50 may be arranged in the axial direction. In other words, the dynamic vibration absorber 50 does not need to be formed continuously in the axial direction. Fig.12 In (b), dynamic vibration absorbers 50 are formed on the electromagnetic steel sheets M located on the upper and lower sides of the electromagnetic steel sheets M constituting the stator core 32 .

[0147] According to this modification, the mass of the weight 51 is changed by changing the axial length of the weight 51. Thus, the natural frequency of the dynamic vibration absorber 50 can be changed to a desired natural frequency.

[0148] (6-7) Modification 7: Axial shape of the dynamic vibration absorber

[0149] like Fig.13 As shown, the dynamic vibration absorber 50 may also be configured to be T-shaped when viewed in a direction perpendicular to the axial direction. Specifically, in the dynamic vibration absorber 50 of this modified example, the axial length of the weight portion 51 is longer than the axial length of the connecting portion 52 .

[0150] In this modification, as in the above-mentioned embodiment, it is possible to suppress an increase in product cost and reduce the vibration generated in the stator core 32. In addition, as in the above-mentioned modification 6, the mass of the weight 51 is changed by changing the axial length of the weight 51. Thus, the natural vibration frequency of the dynamic vibration absorber 50 can be changed to a desired natural vibration frequency.

[0151] (6-8) Modification 8: Fastening position of electromagnetic steel sheet

[0152] like Fig.14 As shown in FIG. 1 , the plurality of electromagnetic steel sheets M constituting the stator core 32 may also be fastened together at the hammer portion 51 of the dynamic vibration absorber 50. In this modified example, the electromagnetic steel sheets M are fastened together by riveting. Fig.14 As shown by the dotted line, a fastening portion 38 formed by caulking is provided at the center portion of the hammer portion 51 .

[0153] According to this modification, since the plurality of electromagnetic steel sheets M constituting the stator core 32 are fastened together at the weight portion 51, the fastening portion 38 is formed at a portion where the magnetic flux does not pass. Therefore, it is possible to suppress an increase in iron loss due to fastening. It should be noted that when welding, bonding, etc. are used as a method for fastening the electromagnetic steel sheets M, the plurality of electromagnetic steel sheets M can also be fastened at the weight portion 51.

[0154] (Second Embodiment)

[0155] The second embodiment will be described below. The motor 30 of the first embodiment is an inner rotor type motor in which the rotor 40 is arranged on the inner side of the stator 31. In contrast, the motor 30 of the present embodiment is an outer rotor type motor in which the rotor 40 is arranged on the outer side of the stator 31. Here, the differences between the motor 30 of the present embodiment and the motor 30 of the first embodiment will be described.

[0156] like Fig.15As shown, the stator core 32 has an annular yoke portion 34 and a tooth portion 35 extending radially outward from the yoke portion 34. The tooth portion 35 has a coil 33. The stator core 32 also has a plurality of (four in this embodiment) support portions 37. The stator core 32 is supported on the shaft 28 by the support portions 37. Each support portion 37 protrudes radially inward from the inner periphery of the yoke portion 34. Each support portion 37 is fixed in contact with the outer peripheral surface of the shaft 28.

[0157] The stator 31 has a plurality of (eight in the present embodiment) dynamic vibration absorbers 50. Each dynamic vibration absorber 50 is disposed on the inner periphery of the yoke portion 34. Each dynamic vibration absorber 50 is disposed in a small gap G formed between the inner peripheral surface of the yoke portion 34 and the outer peripheral surface of the shaft 28. Each dynamic vibration absorber 50 is disposed on the side opposite to the rotor 40 in the radial direction. The structure of each dynamic vibration absorber 50 is the same as that of the first embodiment.

[0158] The dynamic vibration absorber 50 of this embodiment is also similar to the first embodiment. When the yoke portion 34 of the stator core 32 vibrates at the natural frequency, the dynamic vibration absorber 50 vibrates at a phase different from the vibration of the yoke portion 34. Thus, the vibration of the stator core 32 is reduced. In this way, the radial vibration of the stator core 32 caused by the electromagnetic force can be reduced by the vibration of the weight portion 51 in conjunction with the vibration of the stator core 32.

[0159] The dynamic vibration absorber 50 of this embodiment is formed integrally with the stator core 32. Therefore, the dynamic vibration absorber 50 can be provided without adding a new component to the stator 31. In addition, since there is no need to provide a process for assembling the dynamic vibration absorber 50 in addition to the process for manufacturing the stator core 32, the increase in the assembly process can be suppressed. As a result, the increase in the manufacturing cost of the stator 31 can be suppressed, and the vibration generated in the stator core 32 can be reduced.

[0160] According to the above structure, since there is no need to assemble the dynamic vibration absorber 50 on the stator core 32, there is no deviation in the assembly accuracy of the dynamic vibration absorber 50. Therefore, it is possible to suppress the performance of the dynamic vibration absorber 50 on each stator 31. It should be noted that in this embodiment, the modified examples 1 to 8 of the first embodiment can also be applied.

[0161] (Other embodiments)

[0162] The above-mentioned embodiment may also adopt the following structure.

[0163] The motor 30 of each of the above embodiments may also be applied to devices other than the compressor 10. For example, the motor 30 of each of the above embodiments may also be applied to a blower. The blower includes the motor 30 and a fan driven by the motor 30. The fan is not limited to a specific fan, and may be, for example, a multi-blade fan or a propeller fan.

[0164] The structures of the above-mentioned embodiments can also be applied to other electromagnetic devices as magnetic circuits. Specifically, other electromagnetic devices include magnetic bearings that generate a levitation force on the rotor by energizing the coil, and reactors that smooth current pulses by energizing the coil. Thus, as in the above-mentioned embodiments, it is possible to suppress the increase in product cost of the electromagnetic device and reduce the vibration of the iron core 32.

[0165] The above embodiments and variations are described, but it should be understood that various changes can be made to the form and specific matters without departing from the spirit and scope of the claims. In addition, the above embodiments, variations, and other embodiments may be appropriately combined or replaced.

[0166] The words "first", "second", "third", etc. mentioned above are only used to distinguish sentences containing the above words, and do not limit the number and order of the sentences.

[0167] - Industrial Applicability -

[0168] In summary, the present disclosure is useful for magnetic circuit components, blowers, compressors, and refrigeration devices.

[0169] - Explanation of symbols -

[0170] 1 Refrigeration unit

[0171] 10Compressor

[0172] 20 driving shaft (rotating shaft)

[0173] 30 Motor (magnetic circuit)

[0174] 31 stator (magnetic circuit component)

[0175] 32 stator core (iron core)

[0176] 33 coils

[0177] 34 yoke part

[0178] 40 rotors

[0179] 50 Dynamic Vibration Absorber

[0180] 51 Hammer

[0181] 52 connection part

[0182] M electromagnetic steel plate

[0183] R Refrigerant circuit

Claims

1. A magnetic circuit component, which constitutes a part of a magnetic circuit, characterized in that: The magnetic circuit component comprises an iron core (32) and a dynamic vibration absorber (50), The iron core (32) is made of soft magnetic material and has an annular yoke portion (34). The dynamic vibration absorber (50) is arranged on the iron core (32) to reduce the vibration of the iron core (32). The dynamic vibration absorber (50) comprises a hammer part (51) and a connecting part (52), wherein the connecting part (52) connects the hammer part (51) and the yoke part (34) and is elastically deformable. The dynamic vibration absorber (50) and the iron core (32) are formed as one body.

2. The magnetic circuit component according to claim 1, characterized in that: The hammer portion (51) extends along the circumferential direction of the yoke portion (34).

3. The magnetic circuit component according to claim 1 or 2, characterized in that: The dynamic vibration absorber (50) is arranged on the outer periphery or inside of the yoke part (34).

4. The magnetic circuit component according to any one of claims 1 to 3, characterized in that: The iron core (32) is composed of a plurality of electromagnetic steel plates (M) stacked on top of each other. The plurality of electromagnetic steel plates (M) are fastened together at the hammer portion (51).

5. The magnetic circuit component according to any one of claims 1 to 4, characterized in that: The magnetic circuit includes a rotor (40) and a stator (31), wherein the rotor (40) is configured to be rotatable around the axis of a rotating shaft (20), and the stator (31) is arranged opposite to the rotor (40) in the radial direction of the rotating shaft (20). The stator (31) has a stator core (32) as the core (32) and a coil (33) wound around the stator core (32). The dynamic vibration absorber (50) is arranged on a side opposite to the rotor (40) in the radial direction.

6. The magnetic circuit component according to any one of claims 1 to 5, characterized in that: The magnetic circuit component constitutes a part of the electric motor (30).

7. The magnetic circuit component according to any one of claims 1 to 5, characterized in that: The magnetic circuit component constitutes a part of the magnetic bearing.

8. The magnetic circuit component according to any one of claims 1 to 4, characterized in that: The magnetic circuit component constitutes a part of the reactor.

9. A blower, characterized in that: The blower includes a motor (30) and a fan, the motor (30) includes the magnetic circuit component according to claim 6, and the fan is driven by the motor (30).

10. A compressor, characterized in that: The compressor includes the magnetic circuit component according to claim 6 or 7.

11. A refrigeration device, characterized in that: The refrigeration device comprises the compressor (10) according to claim 10, and a refrigerant circuit (R) through which the refrigerant compressed by the compressor (10) flows.

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