Compressor and refrigeration apparatus

Abstract

The application discloses a compressor and a refrigeration device, and relates to the technical field of refrigeration devices, wherein 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 p1, the density of the upper and lower cast aluminum ends is p2, 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 end cast aluminum is r2, the radius of the inner periphery of the lower end cast aluminum 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 above parameters meet the requirements of corresponding formulas. The technical scheme provided by the application increases the rigidity of the rotor system and reduces the noise generated by the motor.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration equipment, in particular to a compressor and refrigeration equipment. BACKGROUND

[0002] The low height and small volume design of the compressor is the trend led by the demand of the portable terminal market in recent years, however, the small volume of the compressor is easy to deteriorate the noise, which is specifically shown as follows: the concentrated airflow formed by the high-pressure refrigerant through the top exhaust will directly impact the rotor assembly, causing axial oscillation and dynamic load fluctuation of the shaft system, and then causing the deterioration of the shaft noise and the influence on the performance. SUMMARY

[0003] The main purpose of the present application is to provide a compressor and refrigeration equipment, which aims to increase the stiffness of the rotor system and reduce the noise generated by the motor.

[0004] To achieve the above purpose, the compressor provided by the present application comprises:

[0005] a shell;

[0006] a motor, the motor comprising a rotor, the rotor comprising a rotor core, an upper cast aluminum end, a lower cast aluminum end, an upper balance block and a lower balance block, the upper cast aluminum end and the lower cast aluminum end being fixed to the upper end and the lower end of the rotor core in the axial direction respectively, the upper balance block being connected to the upper cast aluminum end, the lower balance block being connected to the lower cast aluminum end, the radius of the outer periphery of the rotor core being r1, the height of the rotor core in the axial direction being T0, the density of the rotor core being p1, the density of the upper cast aluminum end and the lower cast aluminum end being p2, the height of the upper cast aluminum end in the axial direction being T1, the height of the lower cast aluminum end in the axial direction being T2, the inner periphery radius of the upper end cast aluminum being r2, the inner periphery radius of the lower end cast aluminum being r3, the mass of the upper balance block being M1, and the mass of the lower balance block being M2; and

[0007] a pump body assembly connected to the shell, the pump body assembly comprising an upper bearing, a lower bearing, a cylinder and a crankshaft, the crankshaft comprising a fixed segment and a penetrating segment connected in sequence, the fixed segment being fixedly connected with the rotor, the penetrating segment sequentially penetrating through the upper bearing, the cylinder and the lower bearing, the radius of the outer periphery of the fixed segment being r0, the elastic modulus of the crankshaft being E, and satisfying: 1800 ≤3000, >1, r1

[0008] In an embodiment, the motor further comprises a stator, the stator comprising a stator core and a stator winding, the stator core being provided with stator slots, the stator winding comprising an upper protruding section, a main body section and a lower protruding section, the main body section being arranged around the stator core, the upper protruding section and the lower protruding section protruding from the stator core, and the upper protruding section and the lower protruding section being located on the upper side and the lower side of the stator core respectively.

[0009] In an embodiment, 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, and the following conditions are satisfied: ≥ 1.2.

[0010] In an embodiment, the housing comprises 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 being provided with a welding point, and the pump body assembly being welded at the welding point.

[0011] In an embodiment, the shortest height between the upper end surface of the stator and the lower end surface of the upper housing is H1, the shortest height between the welding point and the lower end surface of the stator is H2, the height of the upper housing along the axial direction 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 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, and the following conditions are satisfied: .

[0012] In an 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 surface of the stator and the lower end surface of the upper housing is H1, and the height of the upper housing along the axial direction of the stator is H3, and the following condition is satisfied: 0.4 ≤ ≤ 0.6.

[0013] In an embodiment, the height of the lower protruding section along the axial direction of the stator core is h2, the shortest height between the welding point and the lower end surface of the stator is H2, and the following condition is satisfied: 0.6 ≤ ≤ 0.9.

[0014] In an embodiment, the radius of the outer periphery of the upper protruding section is R1, and the maximum radius of the inner periphery of the upper housing is R6, and the following condition is satisfied: 0.8 ≤ ≤ 0.95.

[0015] In an embodiment, the radius of the outer periphery of the lower protruding section is R3, and the minimum radius of the inner periphery of the main housing is R5, satisfying: 0.8≤R3 / R5≤0.95.

[0016] The application also provides a refrigeration device comprising the compressor as described above.

[0017] In the technical solution of the application, by >1, r1≤30mm, r0≤10mm, mainly to indicate that the improvement in the technical solution of the application is on a small-volume compressor in this size range, define f= , f is the first formula of the radial bending mode of the rotor and the crankshaft combination as a whole, f represents the anti-deformation ability of the compressor rotor and crankshaft system, if f>3000, at this time, although the rigidity of the rotor system is larger, the damping capacity is stronger, and the frequency offset effect of the radial electromagnetic excitation of the compressor motor is more significant, but the radius of the crankshaft is increased, which leads to the increase of the resistance of the crankshaft, at the same time, the magnetic circuit of the motor rotor lamination cannot achieve the optimal design, thereby reducing the energy efficiency of the motor. If f<1800, at this time, the rigidity of the rotor system is insufficient, the amplitude of the radial electromagnetic excitation of the motor is easy to excite the system resonance to produce noise vibration problem, thereby increasing the noise of the compressor, therefore, by 1800≤f≤3000, the rigidity of the rotor system is increased, the vibration of the motor is reduced, the noise of the compressor is reduced, and the energy efficiency of the motor is improved. BRIEF DESCRIPTION OF DRAWINGS

[0018] In order to more clearly illustrate the technical solutions in the embodiments of the application or the prior art, the drawings needed to be used in the embodiments or prior art description will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the application, and other drawings can be obtained by those skilled in the art without creative labor based on the drawings shown.

[0019] Figure 1 The structure schematic diagram of the compressor provided by the application is installed with the pump body assembly;

[0020] Figure 2 The structure schematic diagram of the compressor in Figure 1 is removed from the structure schematic diagram of the compressor in

[0021] Figure 3 The trend chart of f value of the compressor in Figure 1 , motor vibration and energy efficiency improvement;

[0022] Figure 4 The cross-sectional view of the rotor and the pump body assembly in Figure 1 after assembly;

[0023] Figure 5 Fig. 1 is a perspective view of the pump; Figure 4 Fig. 2 is a sectional view of the middle rotor;

[0024] Figure 6 Fig. 3 is a perspective view of the pump body assembly; Figure 1 Fig. 4 is a schematic view of the assembly of the middle rotor and the pump body assembly;

[0025] Figure 7 Fig. 5 is a top view of the middle rotor; Figure 1 Fig. 6 is a sectional view of the middle rotor;

[0026] Figure 8 Fig. 7 is a sectional view of the middle stator winding. Figure 1 BRIEF DESCRIPTION OF THE DRAWINGS

[0027] 10, housing; 11, main housing; 111, welding spot; 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.

[0028] The purposes, functional features and advantages of the present application will be further described with reference to the embodiments and the accompanying drawings.

[0029] DETAILED DESCRIPTION

[0030] The technical solutions in the embodiments of the present application will be clearly and completely described with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only some of the embodiments of the present application, but not all the embodiments. Based on the embodiments in the present application, all the other embodiments obtained by those skilled in the art without creative work fall within the protection scope of the present application.

[0031] It should be noted that if the embodiments of the present application involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement condition, etc. between the components in a certain posture, and if the certain posture changes, the directional indications also change accordingly.

[0032] ​In addition, if the description of "first", "second" and the like is involved in the embodiments of the present application, the description of "first", "second" and the like is only for the purpose of description, and cannot be understood as indicating or implying the relative importance of the indicated technical features or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first", "second" can be explicitly or implicitly included at least one of the features. In addition, if "and / or" or "and / or" appears throughout the text, it means that the three parallel schemes are included, for example, "A and / or B" includes A scheme, or B scheme, or A and B scheme. In addition, the technical solutions of each embodiment can be combined with each other, but it must be based on the realization of the ordinary skilled in the art, when the combination of technical solutions appears contradictory or unachievable, it should be considered that the combination of technical solutions does not exist, and is not within the scope of protection required by the present application.

[0033] Reference Figures 1 to 7 The present application provides a compressor, comprising:

[0034] A housing 10;

[0035] A motor 30, the motor 30 comprising a rotor 31, the rotor 31 comprising 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 fixed to the upper end and the lower end of the rotor core 311 in the axial direction respectively, the upper balance block 314 is connected to the upper cast aluminum end 312, 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 r1, the height of the rotor core 311 in the axial direction is T0, the density of the rotor core 311 is p1, the density of the upper cast aluminum end 312 and the lower cast aluminum end 313 is p2, the height of the upper cast aluminum end 312 in the axial direction is T1, the height of the lower cast aluminum end 313 in the axial direction is T2, the radius of the inner periphery of the upper end cast aluminum is r2, the radius of the inner periphery of the lower end cast aluminum is r3, the mass of the upper balance block is M1, the mass of the lower balance block 315 is M2; and

[0036] A pump body assembly 20 connected to the housing 10, the pump body assembly 20 comprising an upper bearing 21, a lower bearing 23, a cylinder 22 and a crankshaft 24, the crankshaft 24 comprising a fixed segment and a penetrating segment connected in sequence, the fixed segment is fixedly connected with the rotor 31, the penetrating segment sequentially penetrates through the upper bearing 21, the cylinder 22 and the lower bearing 23, the radius of the outer periphery of the fixed segment is r0, the elastic modulus of the crankshaft 24 is E, and satisfies: 1800≤ ≤3000, >1, r1≤30mm, r0≤10mm.

[0037] Referring to Figure 3 , the technical solution of the present application is to improve the r0≤10 mm, mainly to indicate that the improvement in the technical solution of the present application is on a small-volume compressor in this size range, and f is defined as , f is the first-order formula of the radial bending mode of the rotor 31 and the crankshaft 24 combination, f represents the anti-deformation ability of the compressor rotor and crankshaft system, if f>3000, at this time the vibration of the motor 30 is always below the vibration qualified line, which meets the requirements, but at this time the motor 30 energy efficiency is significantly reduced; because, at this time, although the rigidity of the rotor system is large, the damping ability is strong, and the effect of the radial electromagnetic excitation of the compressor motor 30 is more obvious, but the radius of the crankshaft 24 is increased, which leads to the increase of the resistance of the crankshaft 24, and the magnetic circuit of the rotor 31 of the motor 30 cannot be optimally designed, thereby reducing the energy efficiency of the motor 30. If f<1800, the energy efficiency of the motor 30 is improved, but the vibration of the motor 30 is at a high level; because, at this time, the rigidity of the rotor system is insufficient, the amplitude of the radial electromagnetic excitation of the motor 30 is easy to excite the system resonance to produce noise vibration problem, thereby easily increasing the noise of the compressor, therefore, by 1800≤f≤3000, the rigidity of the rotor system is increased, the vibration of the motor 30 is reduced, the noise of the compressor is reduced, and the energy efficiency of the motor 30 is also improved.

[0038] Wherein, E, ρ1 and ρ2 are constants, in an embodiment, E=200GPa, ρ1=7800kg / m 3 , ρ2=2700kg / m 3 , of course, the values of E, ρ1 and ρ2 will also change according to the corresponding materials and processing methods, the units of r0, r1, r2, r3, 、 and are all millimeters mm, and the units of M1 and M2 are kilograms kg.

[0039] The measurement method of r0 is: select two points on the outer periphery of the fixed section of the crankshaft 24, the connecting line between the two points is consistent with the radial direction of the crankshaft 24, and passes through the center of the plane, and then the distance between the two points is measured as r0.

[0040] The measurement method of r1 is: select two points on the outer periphery of the rotor 31, the connecting line between the two points is consistent with the radial direction of the rotor 31, and passes through the center of the plane, and then the distance between the two points is measured as r1.

[0041] The measurement method of T0 is: selecting one point on each of the two end faces of the axial direction of the rotor 31, the connecting line between the two points is consistent with the axial direction of the rotor 31, and then the distance between the two points is measured as T0.

[0042] r2, r3, And The measurement method is referred to the above measurement, and it needs to be emphasized that when measuring the above parameters, the points corresponding to the corners of the rotor 31 and the crankshaft 24 should not be selected. These points also meet the above requirements, but will cause the final calculation result to be smaller.

[0043] Specifically, the motor 30 further comprises a stator 32, the stator 32 comprises a stator core and a stator winding 33, the stator core is provided with a stator slot, the stator winding 33 comprises an upper protruding section 331, a main body section 332 and a lower protruding section 333, the main body section 332 is wound on the stator core, the upper protruding section 331 and the lower protruding section 333 protrude from the stator core, and the upper protruding section 331 and the lower protruding section 333 are located on the upper side and the lower side of the stator core respectively. Understandably, during the winding of the stator winding 33 in the stator slot, part of the stator winding 33 always protrudes from the stator core, wherein the protruding part of the stator winding 33 away from the pump body assembly 20 is the upper protruding section 331, and the protruding part of the stator winding 33 towards the pump body assembly 20 is the lower protruding section 333.

[0044] Referring to Figure 8 Further, 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, and the following conditions are met: ≥1.2. Wherein, represents the volume of the upper protruding section 331, represents the volume of the lower protruding section 333, and it needs to be explained that the factor that the stator winding 33 at the corner is arc-shaped during the winding of the stator winding 33 is not considered here.

[0045] The cavity formed by the upper end face of the stator core, the main shell 11 and the upper shell 12 is the upper cavity 13, and the cavity formed between the lower end face of the stator core, the main shell 11 and the upper bearing 21 is the lower cavity 14, wherein 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, so that the volume of the upper convex section 331 is greater than the volume of the lower convex section 333, thereby reducing the volume of the upper cavity 13 and increasing the volume of the lower cavity 14, so as to balance the pressure of the upper cavity 13 and the lower cavity 14, reduce the impact force on the rotor 31 caused by the exhaust gas flow or pressure fluctuation, suppress the excitation source in the exhaust stage, thereby reducing the vibration of the rotor 31, and further reducing the noise of the compressor and improving the energy efficiency of the compressor. If <1.2, it is equivalent to increasing the volume of the upper cavity 13 and reducing the volume of the lower cavity 14, which will cause the gas pressure in the lower cavity 14 to be much greater than the gas pressure in the upper cavity 13, thereby causing the gas pressure to change too much when the gas flow in the upper cavity 13 and the lower cavity 14 exchanges during the exhaust process, and further causing the impact force on the rotor 31 to be too large, thereby increasing the probability and amplitude of the vibration of the rotor 31, and further increasing the noise of the compressor.

[0046] The path of the gas flow between the upper cavity 13 and the lower cavity 14 has three paths, the first: the upper cavity 13 and the lower cavity 14 are connected through the air gap between the rotor 31 and the stator 32; the second: the upper cavity 13 and the lower cavity 14 are connected through the gap between the outer periphery of the stator 32 and the inner periphery of the main housing 11; the third: the upper cavity 13 and the lower cavity 14 are connected through the through hole in the middle of the crankshaft 24, the upper end of the crankshaft 24 is connected with the upper cavity 13, and the crankshaft 24 is provided with a hole (not shown in the figure) connected with the lower cavity 14.

[0047] The measurement method of R1 is: select two points on the outer periphery of the upper convex section 331, the line between the two points passes through the center of the stator core, and the line between the two points is consistent with the radial direction of the stator core, then measure half of the distance between the two points, which is R1.

[0048] The measurement method of R2 is: select two points on the inner periphery of the upper convex section 331, the line between the two points passes through the center of the stator core, and the line between the two points is consistent with the radial direction of the stator core, then measure half of the distance between the two points, which is R2.

[0049] The measurement method of h1 is: select a point on the end face of the upper convex section 331 away from the stator core, then measure the shortest distance between the point and the side (upper end face) of the stator core away from the pump body assembly 20, which is h1.

[0050] Further, the measurement methods of R3, R4 and h2 are consistent with the above measurement methods, which will not be described in detail here. It should be reminded that the points at the chamfer and corner should be avoided during the measurement process, which will cause the measurement result to be smaller. The units of R1, R2, R3, R4, h1 and h2 are all millimeters (mm).

[0051] Optionally, the shell 10 comprises a main shell 11 and an upper shell 12, the upper shell 12 is connected to the main shell 11 and located on the upper side of the main shell 11, the main shell 11 is provided with a welding point 111, and the pump body assembly 20 is welded to the welding point 111. By welding the pump body assembly 20 to the main shell 11, the welding method is stable and reliable, the process is mature, and the reliability is high, thereby improving the stability of the pump body assembly 20, and further improving the service life of the compressor.

[0052] With reference to Figure 1 , Figure 2 and Figure 8 , further, the shortest height between the upper end surface of the stator 32 and the lower end surface of the upper shell 12 is H1, the shortest height between the welding point 111 and the lower end surface of the stator 32 is H2, the height of the upper shell 12 in the axial direction is H3, the minimum radius of the inner periphery of the main shell 11 is R5, the maximum radius of the inner periphery of the upper shell 12 is R6, the height of the upper protruding section 331 in 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 in 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: .

[0053] With reference to Figure 1 , it can be seen that the diameter of the upper shell 12 gradually decreases towards the stator core, that is, the side wall of the upper shell 12 in the circumferential direction gradually shrinks inwardly, therefore, the actual volume of the upper shell 12 is a little larger; and the radius of the connection between the main shell 11 and the upper shell 12 is larger than R5, therefore, the volume between the upper end surface of the stator core and the upper end surface of the main shell 11 is a little smaller; the sum of the volume between the upper end surface of the stator core and the upper end surface of the main shell 11 and the volume of the upper shell 12 is the volume of the upper cavity 13, that is a little larger, a little smaller, therefore, which can be roughly equivalent to the volume of the upper cavity 13 in the cavity state; and which represents the remaining volume after placing the upper protruding section 331 in the upper cavity 13. Similarly, which represents the volume of the lower cavity 14 in the cavity state, which represents the remaining volume after placing the lower protruding section 333 in the lower cavity 14.

[0054] Therefore, if , or , it indicates that the air pressure in the upper cavity 13 and the lower cavity 14 is not balanced, which easily leads to that the air pressure in the upper cavity 13 and the lower cavity 14 changes too much during the exhaust process, thus leading to that the impact force on the rotor 31 is too large, and further increasing the vibration probability and amplitude of the rotor 31, and further leading to that the noise of the compressor is too large. Therefore, by , the volume of the upper cavity 13 and the lower cavity 14 is further optimized, and further the pressure balance in the upper cavity 13 and the lower cavity 14 is optimized, and further the impact force on the rotor 31 caused by the exhaust airflow or pressure fluctuation is reduced, and further the excitation source in the exhaust stage is inhibited, and further the vibration of the rotor 31 is reduced, and further the noise of the compressor is reduced, and further the energy efficiency of the compressor is improved.

[0055] Wherein, the units of H1, H2, H3, R5 and R6 are millimeters mm. The measurement method refers to R1, R2 and h1. However, when measuring R6, the point of the upper shell 12 close to the upper end face and not at the corner can be selected as much as possible, because It is only approximately indicates the volume of the upper cavity 13 in the cavity state, which is only an approximate value, and the rate of change of the radius of the upper shell 12 is not large, so the influence on the final calculation result is within the expected range.

[0056] Specifically, the height of the upper convex 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 shell 12 is H1, and the height of the upper shell 12 along the axial direction of the stator 32 is H3, and satisfy: 0.4≤ ≤0.6. It actually represents the limit of the distance between the upper end face of the upper convex section 331 and the lower end face of the upper shell 12. If >0.6, it indicates that the distance between the upper end face of the upper convex section 331 and the lower end face of the upper shell 12 is relatively too large, which leads to that the airflow on the outer side of the upper convex section 331 is difficult to flow to the inner side of the upper convex section 331, thus leading to that the air pressure exchange speed is low, which easily leads to that the air pressure changes too much, and further increasing the impact force on the rotor 31, and further increasing the vibration of the rotor 31, and further increasing the noise generated by the rotor 31 and the compressor. If <0.4, it indicates that h1 is relatively too small at this time, although the exchange rate of the airflow on the outer side of the upper convex section 331 to the inner side of the upper convex section 331 is high at this time, but it is equivalent to reducing the volume of the upper cavity 13, and increasing the volume of the lower cavity 14, thus leading to that the air pressure in the upper cavity 13 and the lower cavity 14 is not balanced, and further increasing the impact force on the rotor 31, and further leading to that the noise of the compressor is too large. Therefore, by 0.4≤ ≤0.6, so as to increase the air flow exchange rate in the upper cavity 13, balance the air pressure balance between the upper cavity 13 and the lower cavity 14, and further reduce the impact force on the rotor 31, thereby reducing the noise generated by the compressor.

[0057] Further, the height of the lower protruding section 333 along the axial direction of the stator core is h2, the shortest height between the welding point 111 and the lower end surface of the stator 32 is H2, and 0.6≤ ≤0.9. In fact, it is intended to limit the gap between the end surface (lower end surface) of the lower protruding section 333 away from the motor 30 and the pump body assembly 20, so if >0.9, it means that h2 is relatively too large, i.e., the gap between the lower end surface of the lower protruding section 333 and the pump body assembly 20 is too small, so that the air flow exchange rate on the inner and outer sides of the lower protruding section 333 in the lower cavity 14 is low, which easily leads to a large change in air pressure, thereby increasing the impact force on the rotor 31, further increasing the vibration of the rotor 31, and increasing the noise generated by the rotor 31 and the compressor. If <0.6, it is relatively too small, which will cause the lower cavity 14 to be too large and the upper cavity 13 to be too small, resulting in an imbalance in air pressure in the upper cavity 13 and the lower cavity 14, thereby increasing the impact force on the rotor 31, and further causing the noise of the compressor to be too large. Therefore, 0.6≤ ≤0.9, so as to increase the air flow exchange rate in the lower cavity 14, balance the air pressure balance between the upper cavity 13 and the lower cavity 14, and further reduce the impact force on the rotor 31, thereby reducing the noise generated by the compressor. The welding point 111 can be a welding hole, and can also be a welding groove, etc.

[0058] Specifically, the radius of the outer periphery of the upper protruding section 331 is R1, and the maximum radius of the inner periphery of the upper shell 12 is R6, and 0.8≤ ≤0.95. Among them, It is intended to limit the gap between the outer periphery of the upper protruding section 331 and the inner periphery of the upper shell 12, so if >0.95, it means that R1 is relatively too large, which means that the gap between the outer periphery of the upper protruding section 331 and the inner periphery of the upper shell 12 is too small, resulting in a low air flow exchange rate on the outer sides of the upper protruding section 331 in the upper cavity 13, which easily leads to a large change in air pressure, thereby increasing the impact force on the rotor 31, further increasing the vibration of the rotor 31, and increasing the noise generated by the rotor 31 and the compressor. If <0.8, it means that R6 is relatively too large, i.e. the radius of the outer periphery of the upper shell 12 is too large, which leads to the size of the compressor in the radial direction being too large, and thus is not conducive to the miniaturization of the compressor. Therefore, 0.8≤ ≤0.95, so as to reduce the size of the compressor while increasing the exchange rate of the airflow in the upper cavity 13, thereby reducing the impact force on the rotor 31, and thus reducing the noise generated by the compressor.

[0059] Specifically, the radius of the outer periphery of the lower protruding section 333 is R3, and the minimum radius of the inner periphery of the main shell 11 is R5, and 0.8≤R3 / R5≤0.95 is satisfied. Wherein, The gap between the outer periphery of the lower protruding section 333 and the inner periphery of the main shell 11 is limited, and thus, if >0.95, it means that R3 is relatively too large, i.e. the gap between the outer periphery of the lower protruding section 333 and the inner periphery of the main shell 11 is too small, which leads to the exchange rate of the airflow on both sides of the lower protruding section 333 in the lower cavity 14 being too low, thereby easily leading to a large change in air pressure, and thus increasing the impact force on the rotor 31, and thus increasing the vibration of the rotor 31, and increasing the noise generated by the rotor 31 and the compressor. And if <0.8, it means that the main shell 11 is relatively too large, which leads to the size of the compressor in the radial direction being too large, and thus is not conducive to the miniaturization of the compressor. Therefore, 0.8≤ ≤0.95, so as to reduce the size of the compressor while increasing the exchange rate of the airflow in the lower cavity 14, thereby reducing the impact force on the rotor 31, and thus reducing the noise generated by the compressor.

[0060] The application also provides a refrigeration device comprising the compressor, and the specific structure of the compressor is as described above. Since the refrigeration device of the application adopts all the technical solutions of the above-mentioned embodiments, it at least has all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, and thus will not be described here.

[0061] The above-mentioned is only an exemplary embodiment of the application, and does not limit the protection scope of the application. Any equivalent structural transformation made by using the content of the specification and drawings, or direct / indirect application in other related technical fields is included in the protection scope of the application.

Claims

1. A compressor characterized by, The compressor comprises: a shell; a motor comprising a rotor, the rotor comprising a rotor core, an upper cast aluminum end, a lower cast aluminum end, an upper balance block and a lower balance block, the upper cast aluminum end and the lower cast aluminum end being fixed to upper and lower ends of the rotor core in an axial direction respectively, the upper balance block being connected to the upper cast aluminum end, the lower balance block being connected to the lower cast aluminum end, a radius of an outer periphery of the rotor core being r1, a height of the rotor core in the axial direction being T0, a density of the rotor core being p1, a density of the upper and lower cast aluminum ends being p2, a height of the upper cast aluminum end in the axial direction being T1, a height of the lower cast aluminum end in the axial direction being T2, a radius of an inner periphery of the upper end cast aluminum being r2, a radius of an inner periphery of the lower end cast aluminum being r3, a mass of the upper balance block being M1, and a mass of the lower balance block being M2; and A pump body assembly connected to the housing, the pump body assembly comprising an upper bearing, a lower bearing, a cylinder and a crankshaft, the crankshaft comprising a fixed section and a penetrating section connected in sequence, the fixed section being fixedly connected with the rotor, the penetrating section penetrating through the upper bearing, the cylinder and the lower bearing in sequence, a radius of an outer periphery of the fixed section being r0, an elastic modulus of the crankshaft being E, satisfying: 1800≤ ≤3000, >1, r1≤30mm, r0≤10mm.

2. The compressor of claim 1, wherein, the motor further comprising a stator, the stator comprising a stator core and a stator winding, the stator core being provided with a stator slot, the stator winding comprising an upper protruding section, a main body section and a lower protruding section, the main body section being wound around the stator core, the upper and lower protruding sections protruding from the stator core, and the upper and lower protruding sections being located on upper and lower sides of the stator core respectively.

3. The compressor of claim 2, wherein, A height of the upper protruding section in the axial direction of the stator core is h1, a radius of an outer periphery of the upper protruding section is R1, a radius of an inner periphery of the upper protruding section is R2, a height of the lower protruding section in the axial direction of the stator core is h2, a radius of an outer periphery of the lower protruding section is R3, and a radius of an inner periphery of the lower protruding section is R4, and the following conditions are satisfied: ≥ 1.

2.

4. The compressor of claim 2, wherein, The shell comprises a main shell and an upper shell, the upper shell being connected to the main shell and located on an upper side of the main shell, the main shell being provided with a welding point, and the pump body assembly being welded to the welding point.

5. The compressor of claim 4, wherein, The shortest height between the upper end surface of the stator and the lower end surface of the upper housing is H1, the shortest height between the solder joint and the lower end surface of the stator is H2, the height of the upper housing in the axial direction 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 protruding section in 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 in the axial direction of the stator core is h2, the radius of the outer periphery of the lower protruding section is R3, the radius of the inner periphery of the lower protruding section is R4, and the following is satisfied: .

6. The compressor of claim 4, wherein, The height of the upper convex section in the axial direction of the stator core is h1, the shortest height between the upper end surface of the stator and the lower end surface of the upper housing is H1, and the height of the upper housing in the axial direction of the stator is H3, satisfying: 0.4 ≤ h1 / H1 ≤ 0.

6. ≤ 0.

6.

7. The compressor of claim 4 wherein, The height of the lower protruding section along the axial direction of the stator core is h2, the shortest height between the welding point and the lower end surface of the stator is H2, and the following is satisfied: 0.6≤H2 / h2≤0.

9. ≤0.

9.

8. The compressor of claim 4 wherein, The radius of the outer periphery of the upper convex section is R1, and the maximum radius of the inner periphery of the upper housing is R6, satisfying: 0.8≤R1 / R6≤0.

95. ≤0.

95.

9. The compressor of claim 4 wherein, A radius of an outer periphery of the lower protruding section is R3, a minimum radius of an inner periphery of the main shell is R5, and 0.8≤R3 / R5≤0.95 is satisfied.

10. A refrigeration appliance characterized in that, The compressor comprises any one of claims 1 to 9.

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