Compressor and refrigeration equipment

Abstract

The invention discloses a compressor and refrigeration equipment, and relates to the technical field of refrigeration equipment.The compressor comprises a shell, a pump body assembly and a motor, the radius of the outer periphery of a rotor core is r1, the height of the rotor core in the axial direction is T0, the density of the rotor core is rho1, and the density of an upper cast aluminum end and the density of a lower cast aluminum end are rho2, the height of the upper cast aluminum end in the axial direction is T1, the height of the lower cast aluminum end in the axial direction is T2, the radius of the inner periphery of the upper cast aluminum end is r2, the radius of the inner periphery of the lower cast aluminum end is r3, the mass of the upper balance block is M1, the mass of the lower balance block is M2, the radius of the outer periphery of the fixed section is r0, the elastic modulus of the crankshaft is E, and the parameters meet the requirements of corresponding formulas. According to the technical scheme, the rigidity of the rotor system is improved, and noise generated by the motor is reduced.

Description

Technical Field

[0001] This invention relates to the technical field of refrigeration equipment, and particularly to a compressor and refrigeration equipment. Background Technology

[0002] The compact design of compressors with low height and small volume has been a trend driven by the demand in the portable terminal market in recent years. However, the small capacity of the compressor can easily lead to worsening noise. Specifically, the concentrated airflow formed when the high-pressure refrigerant is discharged from the top will directly impact the rotor assembly, causing axial oscillation of the shaft system and dynamic load fluctuations, which in turn leads to deterioration of shaft noise and performance impact. Summary of the Invention

[0003] The main objective of this invention is to provide a compressor and refrigeration equipment that aims to increase the rigidity of the rotor system and reduce the noise generated by the motor.

[0004] To achieve the above objectives, the compressor proposed in this invention comprises: case; An electric motor, comprising a rotor, the rotor including a rotor core, an upper cast aluminum end, a lower cast aluminum end, an upper balance block, and a lower balance block. The upper and lower cast aluminum ends are respectively fixed to the upper and lower ends of the rotor core in the axial direction. The upper balance block is connected to the upper cast aluminum end, and the lower balance block is connected to the lower cast aluminum end. The radius of the outer periphery of the rotor core is r1, the height of the rotor core in the axial direction is T0, the density of the rotor core is ρ1, the density of the upper and lower cast aluminum ends is ρ2, the height of the upper cast aluminum end in the axial direction is T1, the height of the lower cast aluminum end in the axial direction is T2, the inner periphery radius of the upper cast aluminum end is r2, the inner periphery radius of the lower cast aluminum end is r3, the mass of the upper balance block is M1, and the mass of the lower balance block is M2. A pump body assembly is connected to the housing. The pump body assembly includes an upper bearing, a lower bearing, a cylinder, and a crankshaft. The crankshaft includes a fixed section and an insert section connected to each other. The fixed section is fixedly connected to the rotor. The insert section passes sequentially through the upper bearing, the cylinder, and the lower bearing. The radius of the outer periphery of the fixed section is r0. The elastic modulus of the crankshaft is E, satisfying: 1800 ≤ ≤3000, >1, r1≤30mm, r0≤10mm.

[0005] In one embodiment, the motor further includes a stator, which includes a stator core and a stator winding. The stator core is provided with stator slots. The stator winding includes an upper protruding section, a main body section, and a lower protruding section. The main body section is wound around the stator core. The upper protruding section and the lower protruding section both protrude from the stator core, and the upper protruding section and the lower protruding section are located on the upper side and the lower side of the stator core, respectively.

[0006] In one embodiment, the height of the upper protrusion along the axial direction of the stator core is h1, the radius of the outer periphery of the upper protrusion is R1, the radius of the inner periphery of the upper protrusion is R2, the height of the lower protrusion along the axial direction of the stator core is h2, the radius of the outer periphery of the lower protrusion is R3, and the radius of the inner periphery of the lower protrusion is R4, satisfying: ≥1.2.

[0007] In one embodiment, the housing includes a main housing and an upper housing, the upper housing being connected to the main housing and located on the upper side of the main housing, the main housing having weld points, and the pump body assembly being welded to the weld points.

[0008] In one embodiment, the shortest height between the upper end face of the stator and the lower end face of the upper housing is H1, the shortest height between the weld point and the lower end face of the stator is H2, the axial height of the upper housing is H3, the minimum radius of the inner periphery of the main housing is R5, the maximum radius of the inner periphery of the upper housing is R6, the height of the upper protrusion along the axial direction of the stator core is h1, the radius of the outer periphery of the upper protrusion is R1, the radius of the inner periphery of the upper protrusion is R2, the height of the lower protrusion along the axial direction of the stator core is h2, the radius of the outer periphery of the lower protrusion is R3, and the radius of the inner periphery of the lower protrusion is R4, satisfying: .

[0009] In one embodiment, the height of the upper protruding section along the axial direction of the stator core is h1, the shortest height between the upper end face of the stator and the lower end face of the upper housing is H1, and the height of the upper housing along the axial direction of the stator is H3, satisfying: 0.4 ≤ ≤0.6.

[0010] In one embodiment, the height of the lower protrusion along the axial direction of the stator core is h2, and the shortest distance between the weld point and the lower end face of the stator is H2, satisfying: 0.6 ≤ ≤0.9.

[0011] In one embodiment, the radius of the outer periphery of the upper protrusion is R1, and the maximum radius of the inner periphery of the upper shell is R6, satisfying: 0.8 ≤ ≤0.95.

[0012] In one embodiment, the radius of the outer periphery of the lower protrusion is R3, and the minimum radius of the inner periphery of the main housing is R5, satisfying: 0.8≤R3 / R5≤0.95.

[0013] The present invention also proposes a refrigeration device, including the compressor described above.

[0014] In the technical solution of the present invention, by >1, r1≤30mm, r0≤10mm, mainly to indicate that the improvements in the technical solution of this application are all made on small-capacity compressors within this size range. f is defined as... Let f be the first-order formula for the radial bending mode of the rotor and crankshaft assembly, representing the deformation resistance of the compressor rotor-crankshaft system. If f > 3000, although the rotor system has high rigidity and strong vibration reduction capability, and the frequency misalignment effect with the radial electromagnetic excitation of the compressor motor is significant, the increased crankshaft radius leads to increased crankshaft rotation resistance. Simultaneously, the magnetic circuit of the motor rotor laminations cannot achieve optimal design, resulting in reduced motor efficiency. If f < 1800, the rotor system lacks rigidity, and the amplitude of the motor's radial electromagnetic excitation easily triggers system resonance, causing noise and vibration problems, thus increasing compressor noise. Therefore, by setting 1800 ≤ f ≤ 3000, the rotor system rigidity is increased, motor vibration is reduced, compressor noise is lowered, and motor efficiency is also improved. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0016] Figure 1 This is a schematic diagram of the structure of a compressor with a pump body assembly installed in it, provided by the present invention. Figure 2 for Figure 1 A structural diagram excluding the pump body assembly; Figure 3 for Figure 1 The trend chart of the compressor's f-value and motor vibration and energy efficiency improvement; Figure 4 for Figure 1 Cross-sectional view of the central rotor and pump body assembly after assembly; Figure 5 for Figure 4 Cross-sectional view of the central rotor; Figure 6 for Figure 1 A schematic diagram of the assembled rotor and pump body assembly; Figure 7 for Figure 1 Top view of the central rotor; Figure 8 for Figure 1 Cross-sectional view of the middle stator winding.

[0017] Explanation of icon numbers: 10. Housing; 11. Main housing; 111. Welding point; 12. Upper housing; 13. Upper cavity; 14. Lower cavity; 20. Pump body assembly; 21. Upper bearing; 22. Cylinder; 23. Lower bearing; 24. Crankshaft; 30. Motor; 31. Rotor; 311. Rotor core; 312. Upper cast aluminum end; 313. Lower cast aluminum end; 314. Upper balance block; 315. Lower balance block; 32. Stator; 33. Stator winding; 331. Upper protruding section; 332. Main body section; 333. Lower protruding section.

[0018] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0019] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0020] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0021] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0022] Reference Figures 1 to 7 The present invention proposes a compressor, comprising: Casing 10; The motor 30 includes a rotor 31, which comprises a rotor core 311, an upper cast aluminum end 312, a lower cast aluminum end 313, an upper balance block 314, and a lower balance block 315. The upper cast aluminum end 312 and the lower cast aluminum end 313 are respectively fixed to the upper and lower ends of the rotor core 311 in the axial direction. The upper balance block 314 is connected to the upper cast aluminum end 312, and the lower balance block 315 is connected to the lower cast aluminum end 313. The radius of the outer periphery of the rotor core 311 is... Let r1 be the height of the rotor core 311 along the axial direction, T0 be the height of the rotor core 311, ρ1 be the density of the rotor core 311, ρ2 be the density of the upper cast aluminum end 312 and the lower cast aluminum end 313, T1 be the height of the upper cast aluminum end 312 along the axial direction, T2 be the height of the lower cast aluminum end 313 along the axial direction, r2 be the inner circumference radius of the upper cast aluminum end, r3 be the inner circumference radius of the lower cast aluminum end, M1 be the mass of the upper balance block, and M2 be the mass of the lower balance block 315; and Pump body assembly 20 is connected to housing 10. Pump body assembly 20 includes an upper bearing 21, a lower bearing 23, a cylinder 22, and a crankshaft 24. Crankshaft 24 includes a fixed section and an interpenetrating section connected to each other. The fixed section is fixedly connected to rotor 31, and the interpenetrating section passes sequentially through the upper bearing 21, cylinder 22, and lower bearing 23. The radius of the outer periphery of the fixed section is r0. The elastic modulus of crankshaft 24 is E, satisfying: 1800 ≤ ≤3000, >1, r1≤30mm, r0≤10mm.

[0023] Reference Figure 3 In the technical solution of the present invention, by... >1, r1≤30mm, r0≤10mm, mainly to indicate that the improvements in the technical solution of this application are all made on small-capacity compressors within this size range. f is defined as... f is the first-order formula for the radial bending mode of the rotor 31 and crankshaft 24 as a whole. f represents the deformation resistance of the compressor rotor-crankshaft system. If f > 3000, the vibration of motor 30 is always below the vibration qualification line and meets the requirements, but the energy efficiency of motor 30 is significantly reduced. This is because, although the rigidity of the rotor system is large and the vibration reduction capacity is strong, and the frequency misalignment effect with the radial electromagnetic excitation of compressor motor 30 is significant, the increased radius of crankshaft 24 will lead to increased resistance when crankshaft 24 rotates. At the same time, the magnetic circuit of the rotor 31 lamination of motor 30 cannot reach the optimal design, which in turn leads to a reduction in the energy efficiency of motor 30. If f < 1800, the energy efficiency improvement of motor 30 is relatively high, but the vibration of motor 30 is at a relatively high level. This is because the rigidity of the rotor system is insufficient, and the amplitude of the radial electromagnetic excitation of motor 30 is prone to triggering system resonance, resulting in noise and vibration problems, which easily increases the noise of the compressor. Therefore, by 1800 ≤ f ≤ 3000, the rigidity of the rotor system is increased, the vibration of motor 30 is reduced, the noise of the compressor is reduced, and the energy efficiency of motor 30 is also improved.

[0024] Where E, ρ1, and ρ2 are all constants, in one embodiment, E = 200 GPa and ρ1 = 7800 kg / m³. 3 ρ2=2700kg / m 3 Of course, the values ​​of E, ρ1, and ρ2 can also vary depending on the corresponding material and processing method, as can r0, r1, r2, r3, , as well as The units for all are millimeters (mm), while the units for M1 and M2 are kilograms (kg).

[0025] The method for measuring r0 is as follows: Select two points on the outer periphery of the fixed section of crankshaft 24. The line connecting these two points is consistent with the radial direction of crankshaft 24 and passes through the center of the plane. Then measure the distance between these two points, which is r0.

[0026] The method for measuring r1 is as follows: select two points on the outer periphery of rotor 31, the line connecting these two points is consistent with the radial direction of rotor 31 and passes through the center of the plane, and then measure the distance between these two points, which is r1.

[0027] The method for measuring T0 is as follows: select one point on each of the two end faces of the rotor 31 in the axial direction, the line connecting these two points is consistent with the axial direction of the rotor 31, and then measure the distance between these two points, which is T0.

[0028] r2, r3, as well as The measurement method can be the same as described above. At the same time, it should be emphasized that when measuring the above parameters, do not select the points at the corners of the rotor 31 and crankshaft 24. Although these points also meet the above requirements, they will cause the final measurement result to be too small.

[0029] Specifically, the motor 30 further includes a stator 32, which includes a stator core and a stator winding 33. The stator core has stator slots, and the stator winding 33 includes an upper protruding section 331, a main body section 332, and a lower protruding section 333. The main body section 332 is wound around the stator core. The upper protruding section 331 and the lower protruding section 333 both protrude from the stator core, and the upper protruding section 331 and the lower protruding section 333 are located on the upper and lower sides of the stator core, respectively. Understandably, during the winding of the stator winding 33 within the stator slots, a portion of the stator winding 33 will always protrude from the stator core. The protruding portion of the stator winding 33 facing away from the pump body assembly 20 is the upper protruding section 331, and the protruding portion of the stator winding 33 facing the pump body assembly 20 is the lower protruding section 333.

[0030] Reference Figure 8 Furthermore, the height of the upper protruding section 331 along the axial direction of the stator core is h1, the radius of the outer periphery of the upper protruding section 331 is R1, the radius of the inner periphery of the upper protruding section 331 is R2, the height of the lower protruding section 333 along the axial direction of the stator core is h2, the radius of the outer periphery of the lower protruding section 333 is R3, and the radius of the inner periphery of the lower protruding section 333 is R4, satisfying: ≥1.2. Among them, This indicates the volume of the protruding segment 331. This indicates the volume of the lower protruding section 333. It should be noted that this does not take into account the fact that the stator windings 33 of the upper protruding section 331 and the lower protruding section 333 are arc-shaped at the corners during the winding process of the stator winding 33.

[0031] The cavity formed by the upper end face of the stator core, the main housing 11, and the upper housing 12 is the upper cavity 13, and the cavity formed by the lower end face of the stator core, the main housing 11, and the upper bearing 21 is the lower cavity 14. The upper protruding section 331 is located in the upper cavity 13, and the lower protruding section 333 is located in the lower cavity 14. Therefore, by... ≥1.2, thus making the volume of the upper protruding section 331 larger than the volume of the lower protruding section 333, thereby reducing the volume of the upper cavity 13 and increasing the volume of the lower cavity 14, thereby achieving pressure balance between the upper cavity 13 and the lower cavity 14, reducing the impact force on the rotor 31 caused by exhaust airflow or pressure fluctuations, suppressing the excitation source in the exhaust stage, and thus reducing the vibration of the rotor 31, thereby reducing the noise of the compressor and improving the energy efficiency of the compressor. However, if If the volume is less than 1.2, it is equivalent to increasing the volume of the upper chamber 13 and decreasing the volume of the lower chamber 14. This will result in the air pressure in the lower chamber 14 being much greater than the air pressure in the upper chamber 13. Consequently, during the exhaust process, the air pressure changes too much when the airflow in the upper chamber 13 and the lower chamber 14 exchanges, which in turn leads to excessive impact on the rotor 31. This increases the probability and amplitude of rotor 31 vibration, and thus increases the noise of the compressor.

[0032] There are three airflow paths between the upper cavity 13 and the lower cavity 14. The first is that the upper cavity 13 and the lower cavity 14 are connected by the air gap between the rotor 31 and the stator 32. The second is that the upper cavity 13 and the lower cavity 14 are connected by the gap between the outer periphery of the stator 32 and the inner periphery of the main housing 11. The third is that the upper cavity 13 and the lower cavity 14 are connected by the flow hole in the middle of the crankshaft 24. The upper end of the crankshaft 24 is connected to the upper cavity 13, and the crankshaft 24 is provided with a hole (not shown in the figure) that is connected to the lower cavity 14.

[0033] The method for measuring R1 is as follows: Select two points on the outer periphery of the upper protruding section 331. The line connecting these two points passes through the center of the stator core, and the line connecting these two points is consistent with the radial direction of the stator core. Then, measure half of the distance between these two points, which is R1.

[0034] The method for measuring R2 is as follows: Select two points on the inner periphery of the upper protruding section 331. The line connecting these two points passes through the center of the stator core, and the line connecting these two points is consistent with the radial direction of the stator core. Then, measure half of the distance between these two points, which is R2.

[0035] The measurement method for h1 is as follows: select a point on the end face of the upper protruding section 331 that is away from the stator core, and then measure the shortest distance between this point and the side of the stator core away from the pump body assembly 20 (upper end face), which is h1.

[0036] Furthermore, the measurement methods for R3, R4, and h2 are the same as those described above, and will not be elaborated further here. It should be noted that points at chamfered edges or corners should be avoided during measurement, as this will lead to underestimating the value. The units for R1, R2, R3, R4, h1, and h2 are all millimeters (mm).

[0037] Optionally, the housing 10 includes a main housing 11 and an upper housing 12. The upper housing 12 is connected to the main housing 11 and located on the upper side of the main housing 11. The main housing 11 is provided with weld points 111, and the pump body assembly 20 is welded to the weld points 111. By welding the pump body assembly 20 to the main housing 11, the welding method is stable and reliable, and the process is mature and highly reliable, thereby improving the stability of the pump body assembly 20 and thus increasing the service life of the compressor.

[0038] Reference Figure 1 , Figure 2 as well as Figure 8 Furthermore, the shortest height between the upper end face of the stator 32 and the lower end face of the upper housing 12 is H1, the shortest height between the weld point 111 and the lower end face of the stator 32 is H2, the axial height of the upper housing 12 is H3, the minimum radius of the inner periphery of the main housing 11 is R5, the maximum radius of the inner periphery of the upper housing 12 is R6, the height of the upper protruding section 331 along the axial direction of the stator core is h1, the radius of the outer periphery of the upper protruding section 331 is R1, the radius of the inner periphery of the upper protruding section 331 is R2, the height of the lower protruding section 333 along the axial direction of the stator core is h2, the radius of the outer periphery of the lower protruding section 333 is R3, and the radius of the inner periphery of the lower protruding section 333 is R4, satisfying: .

[0039] Reference Figure 1 It can be seen that the diameter of the upper shell 12 gradually decreases towards the stator core, that is, the sidewalls of the upper shell 12 in the circumferential direction gradually taper inward. Therefore, It is slightly larger than the actual volume of the shell 12; and the radius of the connection between the main shell 11 and the upper shell 12 is greater than R5, therefore, The volume between the upper end face of the stator core and the upper end face of the main housing 11 is smaller than the actual volume between them; the sum of the volume between the upper end face of the stator core and the upper end face of the main housing 11, and the volume of the upper housing 12, is the volume of the upper cavity 13. Too big Too small, therefore This is roughly equivalent to the volume of the upper cavity 13 when it is in a hollow state; and This indicates the remaining volume after the protruding section 331 is placed inside the upper cavity 13. Similarly, This indicates the volume of the lower cavity 14 when it is in an empty cavity state. This indicates the remaining volume after the lower protruding section 333 is placed in the lower cavity 14.

[0040] Therefore, if ,or This indicates an imbalance in air pressure between the upper chamber 13 and the lower chamber 14, which can easily lead to excessive pressure changes during exhaust, resulting in excessive impact on the rotor 31. This, in turn, increases the probability and amplitude of rotor 31 vibration, leading to excessive compressor noise. Therefore, by... This further optimizes the volume of the upper cavity 13 and the lower cavity 14, thereby further optimizing the pressure balance between the upper cavity 13 and the lower cavity 14. This reduces the impact force on the rotor 31 caused by exhaust airflow or pressure fluctuations, suppresses the excitation source in the exhaust stage, reduces the vibration of the rotor 31, reduces the noise of the compressor, and improves the energy efficiency of the compressor.

[0041] The units for H1, H2, H3, R5, and R6 are all millimeters (mm). Their measurement methods are the same as for R1, R2, and h1. However, when measuring R6, it is best to select a point on the upper shell 12 close to the upper end face, but not at a corner, because... Originally, this only roughly represents the volume of the upper cavity 13 when it is in an empty state. This is just an approximate value, and the rate of change of the radius of the upper shell 12 is not large. Therefore, the impact on the final calculation result is within the expected range.

[0042] Specifically, the height of the upper protruding section 331 along the axial direction of the stator core is h1, the shortest height between the upper end face of the stator 32 and the lower end face of the upper housing 12 is H1, and the height of the upper housing 12 along the axial direction of the stator 32 is H3, satisfying: 0.4 ≤ ≤0.6. In fact, it indicates the limitation of the distance between the upper end face of the protruding section 331 and the lower end face of the upper shell 12. >0.6 indicates If the distance is too large, it indicates that the gap between the upper end face of the upper protruding section 331 and the lower end face of the upper housing 12 is too small. This makes it difficult for the airflow on the outward side of the upper protruding section 331 to flow to the inward side, resulting in a lower air pressure exchange rate. This can easily lead to excessive air pressure changes, which in turn increases the impact force on the rotor 31, thereby increasing the vibration of the rotor 31 and the noise generated by the rotor 31 and the compressor. If h1 is less than 0.4, it indicates that h1 is relatively small. While the airflow on the outward side of the upper protruding section 331 is difficult to reach the inward side, resulting in a higher airflow exchange rate, it effectively reduces the volume of the upper cavity 13 and increases the volume of the lower cavity 14. This leads to a pressure imbalance between the upper and lower cavities, increasing the impact on the rotor 31 and causing excessive compressor noise. Therefore, by using h1 ≤ 0.4... The pressure is ≤0.6, which increases the airflow exchange rate in the upper cavity 13 and balances the air pressure between the upper cavity 13 and the lower cavity 14, thereby reducing the impact on the rotor 31 and reducing the noise generated by the compressor.

[0043] Furthermore, the height of the lower protruding section 333 along the axial direction of the stator core is h2, and the shortest distance between the weld point 111 and the lower end face of the stator 32 is H2, satisfying: 0.6 ≤ ≤0.9. This is actually intended to define the gap between the end face (lower end face) of the lower protruding section 333 facing away from the motor 30 and the pump body assembly 20. Therefore, if If h2 > 0.9, it indicates that h2 is relatively large, meaning the gap between the lower end face of the lower protruding section 333 and the pump body assembly 20 is too small. This results in a low airflow exchange rate between the inner and outer sides of the lower protruding section 333 within the lower cavity 14, easily leading to excessive air pressure changes. This, in turn, increases the impact force on the rotor 31, thereby increasing the vibration of the rotor 31 and the noise generated by the rotor 31 and the compressor. <0.6, then If the size is too small, the lower chamber 14 will be too large and the upper chamber 13 too small, resulting in an imbalance of air pressure in the upper chamber 13 and lower chamber 14. This increases the impact force on the rotor 31, leading to excessive compressor noise. Therefore, by using 0.6≤ The pressure is ≤0.9, which increases the airflow exchange rate in the lower cavity 14 while balancing the air pressure between the upper cavity 13 and the lower cavity 14, thereby reducing the impact on the rotor 31 and reducing the noise generated by the compressor. The weld point 111 can be a weld hole or a weld groove, etc.

[0044] Specifically, the radius of the outer periphery of the upper protrusion 331 is R1, and the maximum radius of the inner periphery of the upper shell 12 is R6, satisfying: 0.8 ≤ ≤0.95. Among them, To indicate the limitation of the gap between the outer periphery of the upper protrusion 331 and the inner periphery of the upper shell 12, therefore, if If R1 > 0.95, it indicates that R1 is relatively large, meaning the gap between the outer periphery of the upper protrusion 331 and the inner periphery of the upper housing 12 is too small. This results in a low airflow exchange rate on both sides of the upper protrusion 331 within the upper cavity 13, easily leading to excessive air pressure changes. This, in turn, increases the impact force on the rotor 31, thereby increasing the vibration of the rotor 31 and the noise generated by the rotor 31 and the compressor. If... If R6 is less than 0.8, it indicates that R6 is relatively large, meaning the radius of the outer perimeter of the upper casing 12 is too large, resulting in an excessively large radial dimension of the compressor, which is detrimental to compressor miniaturization. Therefore, 0.8 ≤ The value is ≤0.95, which reduces the size of the compressor while increasing the air exchange rate in the upper cavity 13, thereby reducing the impact force on the rotor 31 and thus reducing the noise generated by the compressor.

[0045] Specifically, the radius of the outer periphery of the lower protrusion 333 is R3, and the minimum radius of the inner periphery of the main shell 11 is R5, satisfying: 0.8 ≤ R3 / R5 ≤ 0.95. To indicate the limitation of the gap between the outer periphery of the lower protrusion 333 and the inner periphery of the main shell 11, therefore, if If R3 is greater than 0.95, it indicates that R3 is relatively large, meaning the gap between the outer periphery of the lower protrusion 333 and the inner periphery of the main housing 11 is too small. This results in a low airflow exchange rate on both sides of the lower protrusion 333 within the lower cavity 14, easily leading to excessive air pressure changes. This, in turn, increases the impact force on the rotor 31, thereby increasing the vibration of the rotor 31 and the noise generated by the rotor 31 and the compressor. If... If the value is less than 0.8, it indicates that the main housing 11 is relatively too large, which would result in an excessively large radial dimension of the compressor, hindering its miniaturization. Therefore, 0.8 ≤ The value is ≤0.95, which reduces the size of the compressor while increasing the air exchange rate in the lower cavity 14, thereby reducing the impact force on the rotor 31 and thus reducing the noise generated by the compressor.

[0046] The present invention also proposes a refrigeration device, which includes a compressor. The specific structure of the compressor is as described in the above embodiments. Since the refrigeration device in the present invention adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0047] The above description is merely an exemplary embodiment of the present invention and does not limit the scope of protection of the present invention. Any equivalent structural transformations made based on the technical concept of the present invention and the contents of the specification and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that, include: case; An electric motor, comprising a rotor, the rotor including a rotor core, an upper cast aluminum end, a lower cast aluminum end, an upper balance block, and a lower balance block. The upper and lower cast aluminum ends are respectively fixed to the upper and lower ends of the rotor core in the axial direction. The upper balance block is connected to the upper cast aluminum end, and the lower balance block is connected to the lower cast aluminum end. The radius of the outer periphery of the rotor core is r1, the height of the rotor core in the axial direction is T0, the density of the rotor core is ρ1, the density of the upper and lower cast aluminum ends is ρ2, the height of the upper cast aluminum end in the axial direction is T1, the height of the lower cast aluminum end in the axial direction is T2, the inner periphery radius of the upper cast aluminum end is r2, the inner periphery radius of the lower cast aluminum end is r3, the mass of the upper balance block is M1, and the mass of the lower balance block is M2. A pump body assembly is connected to the housing. The pump body assembly includes an upper bearing, a lower bearing, a cylinder, and a crankshaft. The crankshaft includes a fixed section and an insert section connected to each other. The fixed section is fixedly connected to the rotor. The insert section passes sequentially through the upper bearing, the cylinder, and the lower bearing. The radius of the outer periphery of the fixed section is r0. The elastic modulus of the crankshaft is E, satisfying: 1800 ≤ ≤3000, >1, r1≤30mm, r0≤10mm.

2. The compressor as described in claim 1, characterized in that, The motor also includes a stator, which includes a stator core and a stator winding. The stator core is provided with stator slots. The stator winding includes an upper protruding section, a main body section and a lower protruding section. The main body section is wound around the stator core. The upper protruding section and the lower protruding section both protrude from the stator core, and the upper protruding section and the lower protruding section are located on the upper side and the lower side of the stator core, respectively.

3. The compressor as described in claim 2, characterized in that, The height of the upper protruding section along the axial direction of the stator core is h1, the radius of the outer periphery of the upper protruding section is R1, the radius of the inner periphery of the upper protruding section is R2, the height of the lower protruding section along the axial direction of the stator core is h2, the radius of the outer periphery of the lower protruding section is R3, and the radius of the inner periphery of the lower protruding section is R4, satisfying: ≥1.

2.

4. The compressor as described in claim 2, characterized in that, The housing includes a main housing and an upper housing. The upper housing is connected to the main housing and located on the upper side of the main housing. The main housing has weld points, and the pump body assembly is welded to the weld points.

5. The compressor as described in claim 4, characterized in that, The shortest height between the upper end face of the stator and the lower end face of the upper housing is H1, the shortest height between the weld point and the lower end face of the stator is H2, the axial height of the upper housing is H3, the minimum radius of the inner periphery of the main housing is R5, the maximum radius of the inner periphery of the upper housing is R6, the height of the upper protrusion along the axial direction of the stator core is h1, the radius of the outer periphery of the upper protrusion is R1, the radius of the inner periphery of the upper protrusion is R2, the height of the lower protrusion along the axial direction of the stator core is h2, the radius of the outer periphery of the lower protrusion is R3, and the radius of the inner periphery of the lower protrusion is R4, satisfying: .

6. The compressor as described in claim 4, characterized in that, The height of the upper protruding section along the axial direction of the stator core is h1, the shortest height between the upper end face of the stator and the lower end face of the upper housing is H1, and the height of the upper housing along the axial direction of the stator is H3, satisfying: 0.4 ≤ ≤0.

6.

7. The compressor as claimed in claim 4, characterized in that, The height of the lower protruding section along the axial direction of the stator core is h2, and the shortest height between the weld point and the lower end face of the stator is H2, satisfying: 0.6 ≤ ≤0.

9.

8. The compressor as described in claim 4, characterized in that, The radius of the outer periphery of the upper protruding section is R1, and the maximum radius of the inner periphery of the upper shell is R6, satisfying: 0.8 ≤ ≤0.

95.

9. The compressor as claimed in claim 4, characterized in that, The radius of the outer periphery of the lower protrusion is R3, and the minimum radius of the inner periphery of the main shell is R5, satisfying: 0.8≤R3 / R5≤0.

95.

10. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 9.

Images