Rotary compressor and refrigeration device with same

Abstract

The utility model discloses a rotary compressor and a refrigeration device with the same, the rotary compressor comprises a shell, a motor and a compression component, the motor and the compression component are both arranged in the shell, the motor comprises a stator and a rotor, and the stator and the rotor are arranged in the shell. The rotor is connected with the compression part and is used for driving the compression part to compress gas; the rotary compressor meets the following conditions: LCM (Q, P) is greater than or equal to 30; q is the number of stator slots of the stator, P is the number of poles of the rotor, T1 is the notch width of the stator slots of the stator, and D1 is the outer diameter of a rotor core of the rotor. According to the rotary compressor provided by the utility model, by limiting the least common multiple of the pole number and the slot number of the motor and the rigidity of the stator, the inherent frequency of the stator is limited, the risk that the inherent frequency of the stator is overlapped with the inherent frequency of other parts of the rotary compressor is reduced, and the noise of the rotary compressor is effectively reduced.

Description

Technical Field

[0001] This application relates to the technical field of compressors, and in particular to a rotary compressor and a refrigeration device having the same. Background Art

[0002] With the development of compressor technology, the miniaturization and light weight of rotary compressors have gradually become the mainstream development trend. In related technologies, in order to improve the performance of rotary compressors, the number of poles of the motor is increased. However, the increase in the number of poles will lead to the weakening of the rotor magnetic field and the increase in iron loss. In order to improve the problem of the weakening of the rotor magnetic field, the stator slots of the stator need to have a larger volume to accommodate more windings. However, as the volume of the stator slots increases, the stiffness of the stator gradually weakens, resulting in a decrease in the natural frequency of the stator. The decreased natural frequency of the stator is likely to overlap with the natural frequencies of other components of the rotary compressor, thereby increasing the noise and vibration of the rotary compressor. Summary of the Utility Model

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. For this purpose, the utility model provides a rotary compressor, by restricting the least common multiple of the number of poles and slots of the motor and the stiffness of the stator, the natural frequency of the stator is restricted, the risk of the natural frequency of the stator overlapping with the natural frequencies of other components of the rotary compressor is reduced, and the noise of the rotary compressor is effectively reduced.

[0004] This application also provides a refrigeration device including the above rotary compressor.

[0005] The rotary compressor according to an embodiment of the utility model includes: a housing, a motor, and a compression component. The motor and the compression component are both disposed in the housing. The motor includes a stator and a rotor. The rotor is connected to the compression component to drive the compression component to compress gas. The rotary compressor satisfies: LCM(Q, P) ≥ 30; Wherein, Q is the number of stator slots of the stator, P is the number of poles of the rotor, LCM(Q, P) is the least common multiple of Q and P, T1 is the notch width of the stator slots of the stator, and D1 is the outer diameter of the rotor core of the rotor.

[0006] For the rotary compressor according to an embodiment of the utility model, LCM(Q, P) ≥ 30 of the motor reduces the amplitude of torque fluctuation, improves the stability of the rotor, and thus improves the operating stability of the rotary compressor; in addition, the rotary compressor also satisfies The natural frequency of the stator is restricted to 1900 Hz to 2500 Hz, the risk of the natural frequency of the stator overlapping with the natural frequencies of other components of the rotary compressor is reduced, and the noise of the rotary compressor is effectively reduced.

[0007] In some embodiments, the rotary compressor satisfies: 36 mm ≤ T1 × Q ≤ 70 mm.

[0008] In some embodiments, the rotary compressor satisfies: wherein, T2 is the tooth width of the stator.

[0009] In some embodiments, an exhaust valve assembly is provided at the exhaust hole of the compression component. The exhaust valve assembly includes an exhaust valve plate and a limiter for restricting the stroke of the exhaust valve plate. The rotary compressor satisfies: 1.9 ≤ wherein, t1 is the thickness of the exhaust valve plate, and t2 is the thickness of the limiter.

[0010] In some embodiments, the natural frequency of the stator is f1, the natural frequency of the limiter is f2, and the rotary compressor satisfies: |f2 - f1| ≥ 200 Hz.

[0011] In some embodiments, the rotor includes a rotor core, and the rotor core is provided with a flow-through hole. The total area of the flow-through holes is S1, and the area enclosed by the outer circle and the inner circle of the rotor core is S2. The rotary compressor satisfies:

[0012]

[0013] In some embodiments, the natural frequency of the stator is f1, the natural frequency of the limiter is f2, and the natural frequency of the rotor assembly is f3, where f1 ≠ f2 ≠ f3. The rotor assembly includes the rotor of the motor, the crankshaft of the compression component, and the piston.

[0014] In some embodiments, f2 > f1 > f3.

[0015] In some embodiments, f1 - f3 ≥ 200 Hz; and / or, f2 - f3 ≥ 200 Hz.

[0016] In some embodiments, the number of poles P of the rotor satisfies: 10 ≤ P ≤ 12; the number of slots Q of the stator satisfies: 15 ≤ Q ≤ 18.

[0017] In some embodiments, the rotary compressor satisfies: wherein, m is the number of phases of the motor.

[0018] The refrigeration device according to an embodiment of the present invention includes the rotary compressor described in the above technical solution.

[0019] The additional aspects and advantages of the present invention will be partially given in the following description, partially become apparent from the following description, or be understood through the practice of the present invention. Description of the Drawings

[0020] The above and / or additional aspects and advantages of the present utility model will become apparent and be readily understood from the description of the embodiments in conjunction with the following drawings, where:

[0021] Figure 1 is a schematic diagram of a rotary compressor according to an embodiment of the present utility model;

[0022] Figure 2 is a schematic diagram of the cooperation between the rotor and the compression component;

[0023] Figure 3 is a schematic diagram of the motor;

[0024] Figure 4 is a schematic diagram of the stator core;

[0025] Figure 5 is a schematic diagram of the curve change of the natural frequency of the stator elliptical mode;

[0026] Figure 6 is a schematic diagram of the curve change of the natural frequency of the stator elliptical mode;

[0027] Figure 7 is a schematic diagram of the exhaust valve assembly.

[0028] Reference numerals: 100, rotary compressor; 1, housing; 2, motor; 21, stator; 211, stator core; 212, stator slot; 22, rotor; 221, rotor core; 222, permanent magnet; 223, flow hole; 3, compression component; 31, crankshaft; 32, piston; 33, exhaust valve assembly; 331, exhaust valve plate; 332, limiter. Detailed Embodiment

[0029] The embodiments of the present utility model will be described in detail below. Examples of the embodiments are shown in the drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are only used to explain the present utility model and should not be construed as a limitation of the present utility model.

[0030] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation to the present utility model. In addition, the features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, the meaning of "a plurality" is two or more.

[0031] In the description of the present utility model, it should be noted that unless otherwise clearly defined and limited, the terms "installation", "connection", and "coupling" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific situations.

[0032] The following refers to Figures 1-7 to describe the rotary compressor 100 according to an embodiment of the present utility model.

[0033] Referring to Figure 1 , Figure 2 and Figure 3 , the rotary compressor 100 according to an embodiment of the present utility model includes: a housing 1, a motor 2, and a compression component 3. The motor 2 and the compression component 3 are both disposed inside the housing 1. The motor 2 includes a stator 21 and a rotor 22. The rotor 22 is connected to the compression component 3 to drive the compression component 3 to compress gas.

[0034] The motor 2 includes a stator 21 and a rotor 22. The stator 21 can be sleeved on the outer periphery of the rotor 22. The crankshaft 31 of the compression component 3 can be connected to the rotor 22. The rotor 22 includes a rotor core 221 and a permanent magnet 222. The permanent magnet 222 can be disposed inside the rotor core 221 to generate a permanent magnetic field in the rotor 22. The stator 21 includes a stator core 211. The stator core 211 has a plurality of stator slots 21 for placing stator windings. After the stator windings are energized, the stator windings can generate a rotating magnetic field in the stator 21. The rotating magnetic field of the stator 21 can drive the permanent magnetic field of the rotor 22 to rotate, so as to drive the rotor 22 to rotate relative to the stator 21, thereby driving the crankshaft 31 to rotate, and ensuring the normal operation of the motor 2.

[0035] Among them, the number of poles of the rotor 22 is P, the number of stator slots 21 is Q, LCM(Q, P) is the least common multiple of the number of stator slots 21, Q, and the number of poles of the rotor 22, P, and LCM(Q, P) can represent the torque ripple of the motor 2. For example, when LCM(Q, P)=30, when the rotor 22 rotates one week, the torque of the rotor 22 will have 30 fluctuations. The larger LCM(Q, P) is, the more fluctuations in the torque of the rotor 22 within one cycle, that is, the torque ripple moves towards high frequency, the number of torque ripples is larger, the LCM(Q, P) -th harmonic corresponding to the torque fluctuation, the smaller the amplitude of the torque ripple, and the higher the stability of the rotor 22.

[0036] In the embodiment of the present application, the rotary compressor 100 satisfies: LCM(Q, P)≥30. Compared with the motors with 9 slots and 6 poles and 12 slots and 8 poles in the related art, the least common multiple of the motor with 9 slots and 6 poles is 18, and the least common multiple of the motor with 12 slots and 8 poles is 24. In the embodiment of the present application, the least common multiple LCM(Q, P) of the rotary compressor 100≥30, the amplitude of the torque fluctuation is smaller, the stability of the rotor 22 is higher, and the operating stability of the rotary compressor 100 is also better.

[0037] When the LCM(Q, P) of the motor 2 changes, the structure and natural frequency of its stator 21 will also change. In order to avoid the situation where the natural frequency of the stator 21 overlaps with the natural frequencies of other components of the rotary compressor 100 (such as structures like the rotor 22 and the limiter 332 of the exhaust valve assembly 33), it is necessary to limit the natural frequency of the stator 21. The natural frequency of the stator 21 is proportional to the stiffness of the stator 21. Therefore, the natural frequency of the stator 21 can be adjusted by adjusting the stiffness of the stator 21.

[0038] Each permanent magnet 222 has its own south pole and north pole, but each permanent magnet 222 has only one end face (south pole or north pole) facing the stator 21 and interacting with the stator 21. Therefore, the number of poles of the rotor 22 is equal to the number of permanent magnets 222. When the number of poles P of the rotor 22 changes, the number of permanent magnets also changes, and the outer diameter D1 of the rotor 22 also changes accordingly. The outer diameter D1 of the rotor 22 is related to the inner diameter of the stator 21. When the outer diameter D1 of the rotor 22 changes, the inner diameter of the stator 21 also changes. When the outer diameter of the stator 21 remains unchanged and the inner diameter of the stator 21 decreases, the stiffness of the stator 21 will be reduced; when the number of poles P of the rotor 22 changes, in order to make the stator 21 more adaptable to the rotor 22, the number Q and volume of the stator slots 21 of the stator 21 need to be changed accordingly. For example, the more the number of poles P of the rotor 22, the more the number Q of the stator slots 21 of the stator 21 needs to be increased correspondingly, and the volume of the stator slots 21 also needs to be increased correspondingly to accommodate more windings; the fewer the number of poles P of the rotor 22, the fewer the number Q of the stator slots 21 of the stator 21 can be reduced correspondingly, and the volume of the stator slots 21 can also be reduced correspondingly.

[0039] Both the number Q of the stator slots 21 and the volume of the stator slots 21 affect the stiffness of the stator 21. Among them, referring to Figure 4 , the width T1 of the opening of the stator slot 21 affects the volume of the stator slot 21, thereby affecting the stiffness of the stator 21.

[0040] Above, the stiffness of the stator 21 can be adjusted by adjusting the value, so as to adjust the natural frequency of the stator 21.

[0041] In the embodiment of the present application, the rotary compressor satisfies:

[0042] The spatial structure modal vibration mode of the stator 21 is an elliptical shape. Since the natural frequency of the stator 21 is distributed between 1000 Hz and 3500 Hz, this frequency band has a greater impact on both the total compressor noise value and the noise auditory sensation. Therefore, the structural design of the stator and the selection of the natural frequency are very important. As Figure 5 shown, Figure 5 is a schematic diagram of the curve change of the natural frequency of the stator elliptical mode. It can be seen that as increases, the natural frequency of the stator elliptical mode shows a downward trend. When is between 1.8 and 5.5, the natural frequency of the stator elliptical mode is distributed between 1900 Hz and 2500 Hz. When the natural frequency of the stator 21 is within this range, the risk of the natural frequency of the stator 21 overlapping with the natural frequencies of other components of the rotary compressor 100 is reduced, and the noise of the rotary compressor 100 is effectively reduced.

[0043] Specifically, It can be any point value among 1.8, 2, 2.3, 3.6, 4.7, 5, 5.5 or the range value between any two of them.

[0044] For the rotary compressor 100 according to the embodiment of the present utility model, LCM(Q, P) of the motor 2 ≥ 30, which reduces the amplitude of torque fluctuation, improves the stability of the rotor 22, and thus improves the operating stability of the rotary compressor 100; in addition, the rotary compressor 100 also satisfies The natural frequency of the stator 21 is limited to 1900 Hz - 2500 Hz, reducing the risk of overlap between the natural frequency of the stator 21 and the natural frequencies of other components of the rotary compressor 100, and effectively reducing the noise of the rotary compressor 100.

[0045] In some embodiments, the rotary compressor 100 satisfies: 36 mm ≤ T1 × Q ≤ 70 mm.

[0046] Wherein, T1 is the width of the opening of the stator slot 21, Q is the number of stator slots 21 of the stator 21, T1 × Q can be defined as the total length of the openings of multiple stator slots of the stator on the inner circle of the stator, T1 × Q is an influencing factor of the stiffness of the stator, the larger T1 × Q is, the poorer the stiffness of the stator is, and the lower the natural frequency of the stator is. T1 × Q has a greater influence on the stiffness of the stator. In the embodiment of the present application, the range of T1 × Q is limited, so that the number of poles P of the rotor and the outer diameter D1 of the rotor have a larger design space.

[0047] Specifically, T1 × Q can be any point value among 36 mm, 42 mm, 48 mm, 56 mm, 64 mm, 70 mm or the range value between any two of them.

[0048] In the embodiment of the present application, T1 × Q is limited to 36 mm - 70 mm, so that The value can be more easily within the range of 1.8 - 5.5, and the natural frequency of the stator 21 can be more easily within the range of 1900 Hz - 2500 Hz, reducing the risk of overlap between the natural frequency of the stator 21 and the natural frequencies of other components of the rotary compressor 100, and effectively reducing the noise of the rotary compressor 100.

[0049] Referring to Figure 4 and Figure 6 , in some embodiments, the rotary compressor satisfies: Wherein, T2 is the tooth width of the stator 21.

[0050] Because the tooth width T2 of the stator is also an influencing factor of the stiffness of the stator, in the embodiment of the present application, by limiting The value further ensures the stability of the natural frequency of the stator within the range of 1900 Hz to 2500 Hz. As Figure 6 shown, Figure 6 is a schematic diagram of the curve change of the natural frequency of the elliptical mode of the stator. It can be seen that as increases, the natural frequency of the elliptical mode of the stator shows a downward trend. When is between 6.9 and 13.5, the natural frequency of the elliptical mode of the stator is distributed between 1900 Hz and 2500 Hz.

[0051] In the embodiment of the present application, by limiting the value of , the stability of the natural frequency of the stator within the range of 1900 Hz to 2500 Hz is further ensured, the risk of overlap between the natural frequency of the stator and the natural frequencies of other components of the rotary compressor is further reduced, and the noise of the rotary compressor is effectively reduced.

[0052] Referring to Figure 1 and Figure 7 In some embodiments, an exhaust valve assembly 33 is provided at the exhaust hole of the compression component 3. The exhaust valve assembly 33 includes an exhaust valve plate 331 and a stopper 332 for restricting the stroke of the exhaust valve plate 331.

[0053] When the rotary compressor 100 operates, the stator 21 drives the rotor 22 to rotate. The rotor 22 drives the piston 32 to perform an eccentric motion through the crankshaft 31 of the compression component 3. The piston 32 compresses the gas in the compression cavity of the compression component 3. When the gas in the compression cavity reaches the set pressure, the exhaust valve plate 331 at the exhaust hole is pushed open to discharge the compression cavity.

[0054] When the gas pushes open the exhaust valve plate 331, the exhaust valve plate 331 deforms in the direction away from the compression cavity and collides with the stopper 332. The stroke of the exhaust valve plate 331 is restricted by the stopper 332, so that the exhaust valve plate 331 can be restored to the state of closing the exhaust hole in time, ensuring the reliability of the operation of the rotary compressor 100.

[0055] In order to reduce the risk of overlap between the natural frequency of the stator 21 and the natural frequency of the stopper 332, it is also necessary to limit the natural frequency of the stopper 332. The natural frequency of the stopper 332 is proportional to the stiffness of the stopper 332. Therefore, the natural frequency of the stopper 332 can be adjusted by adjusting the stiffness of the stopper 332.

[0056] The stiffness of the stopper 332 is positively correlated with the thickness of the stopper 332. When designing the thickness t2 of the stopper 332, the thickness t1 of the exhaust valve plate 331 needs to be considered so that the stopper 332 can withstand the impact of the exhaust valve plate 331. In addition, LCM(Q, P) will affect the design of the thickness t1 of the exhaust valve plate 331. Because the larger LCM(Q, P) is, the more fluctuations there are in the torque of the rotor 22 within one cycle, that is, the torque pulsation moves towards high frequency, the larger the torque pulsation is, the larger the pulsation of the compressed gas is, and the more times the gas impacts the exhaust valve plate 331, the thicker the thickness t1 of the exhaust valve plate 331 needs to be designed.

[0057] Above, the stiffness of the stopper 332 can be adjusted by adjusting the value, so as to adjust the natural frequency of the stopper 332.

[0058] In the embodiments of the present application, the rotary compressor satisfies: so that the natural frequency of the stopper 332 is limited within the range of 2300 Hz to 2800 Hz.

[0059] Specifically, can be any one of the point values of 2, 2.3, 3.6, 4.6 or the range value between any two of them.

[0060] Through the above formula, the natural frequency of the stator 21 and the natural frequency of the stopper 332 can be adjusted respectively, reducing the risk of overlap between the natural frequency of the stator 21 and the natural frequency of the stopper 332, and effectively reducing the noise of the rotary compressor 100.

[0061] In some embodiments, the natural frequency of the stator 21 is f1, the natural frequency of the stopper 332 is f2, and the rotary compressor 100 satisfies: |f2 - f1| ≥ 200 Hz.

[0062] It can be f2 - f1 ≥ 200 Hz, or it can be f1 - f2 ≥ 200 Hz. As long as the difference between the natural frequency f1 of the stator and the natural frequency f2 of the stopper is not less than 200 Hz, the risk of overlap between the natural frequency of the stator and the natural frequency of the stopper is further reduced.

[0063] In some embodiments, in order to reduce the risk of overlap between the natural frequency of the stator 21, the natural frequency of the stopper 332, and the natural frequency of the rotor assembly, it is also necessary to limit the natural frequency of the rotor assembly. The rotor assembly includes: the rotor 22 of the motor 2, the crankshaft 31 of the compression component 3, and the piston 32. The rotor 22 is adapted to drive the piston 32 to rotate through the crankshaft 31. The natural frequency of the rotor assembly is related to the natural frequency of the rotor 22, and the natural frequency of the rotor 22 is proportional to the stiffness of the rotor 22.

[0064] The rotor 22 includes a rotor core 221. The rotor core 221 is provided with a circulation hole 223. The total area of the circulation hole 223 is S1, and the area enclosed by the outer circle and the inner circle of the rotor core 221 is S2. It can be adjusted by the ratio to adjust the stiffness of the rotor. The larger the , the larger the proportion of the circulation hole 223, and the smaller the stiffness of the rotor; the smaller the

[0065] In the embodiment of the present application, the rotary compressor satisfies: to limit the natural frequency of the rotor assembly within the range of 1500 Hz to 1800 Hz.

[0066] Specifically, can be any one of 0.04, 0.07, 0.1, 0.12 or the range value between any two of them.

[0067] Through the above formula, the natural frequencies of the stator 21, the limiter 332 and the rotor assembly can be adjusted respectively, reducing the risk of overlap of the natural frequencies of the stator 21, the limiter 332 and the rotor assembly, and effectively reducing the noise of the rotary compressor 100.

[0068] In some embodiments, the natural frequency of the stator 21 is f1, the natural frequency of the limiter 332 is f2, and the natural frequency of the rotor assembly is f3. The rotary compressor 100 satisfies: f1≠f2≠f3, reducing the risk of overlap of the natural frequencies of the stator 21, the limiter 332 and the rotor assembly.

[0069] In some specific embodiments, the rotary compressor satisfies: f2>f1>f3, f2 - f1≥200 Hz, f1 - f3≥200 Hz.

[0070] Exemplarily, the natural frequency f1 of the stator is 2500 Hz, the natural frequency f2 of the limiter is 2800 Hz, and the natural frequency f3 of the rotor assembly is 1800 Hz; or, the natural frequency f1 of the stator is 2000 Hz, the natural frequency f2 of the limiter is 2400 Hz, and the natural frequency f3 of the rotor assembly is 1600 Hz; or, the natural frequency f1 of the stator is 1900 Hz, the natural frequency f2 of the limiter is 2300 Hz, and the natural frequency f3 of the rotor assembly is 1500 Hz. It should be understood that the natural frequencies of the stator, the limiter and the rotor assembly can also be other values.

[0071] Through the above technical solution, the risk of the overlap of the natural frequencies of the stator, the limiter, and the rotor assembly is further reduced.

[0072] In some other specific embodiments, the rotary compressor satisfies: f1 > f2 > f3, f1 - f2 ≥ 200 Hz, and f2 - f3 ≥ 200 Hz.

[0073] Exemplarily, the natural frequency f1 of the stator is 2500 Hz, the natural frequency f2 of the limiter is 2300 Hz, and the natural frequency f3 of the rotor assembly is 1800 Hz.

[0074] Through the above technical solution, the risk of the overlap of the natural frequencies of the stator, the limiter, and the rotor assembly is further reduced.

[0075] In some embodiments, the number of poles P of the rotor 22 satisfies: 10 ≤ P ≤ 12; the number of slots Q of the stator 21 satisfies: 15 ≤ Q ≤ 18.

[0076] Through the above technical solution, in the embodiments of the present application, the motor 2 is a 15-slot 10-pole motor 2 or an 18-slot 12-pole motor 2. By limiting the number of poles of the rotor 22 and the number of slots of the stator 21, it is avoided that the values of the number of poles of the rotor 22 and the number of slots of the stator 21 are too large, the production difficulty of the motor 2 is reduced, and the cost of the rotary compressor 100 is reduced.

[0077] In some embodiments, the number of phases of the motor 2 is m, and under each magnetic pole, the number of slots occupied by each phase winding is By defining The motor 2 can use fractional slots, which is beneficial to saving energy, improving work efficiency, reducing noise, and the fractional slots can adopt concentrated windings, which is beneficial to improving the regularity of automatic winding, can improve the utilization rate of the space in the stator slot 212, and can make the variable loss and constant loss of the motor 2 at a relatively average level, thereby improving the work efficiency of the motor 2 and the power density of the motor 2.

[0078] The refrigeration device according to the embodiment of the present invention includes: the rotary compressor 100 in the above technical solution.

[0079] According to the refrigeration device of the embodiment of the present invention, the least common multiple LCM(Q, P) of the motor of the rotary compressor is ≥ 30, which reduces the amplitude of the torque fluctuation, improves the stability of the rotor, and thus improves the operating stability of the rotary compressor; in addition, the rotary compressor also satisfies The natural frequency of the stator is limited to 1900 Hz - 2500 Hz, which reduces the risk of the overlap of the natural frequency of the stator and the natural frequencies of other components of the rotary compressor, effectively reduces the noise of the rotary compressor, that is, reduces the noise of the refrigeration device.

[0080] In the description of this specification, the description referring to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present utility model. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0081] Although the embodiments of the present utility model have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present utility model, and the scope of the present utility model is defined by the claims and their equivalents.

Claims

1. A rotary compressor, characterized in that: include: A housing, a motor and a compression component, wherein the motor and the compression component are both arranged in the housing, the motor comprises a stator and a rotor, and the rotor is connected to the compression component to drive the compression component to compress gas; the rotary compressor meets the following requirements: Among them, Q is the number of stator slots of the stator, P is the number of poles of the rotor, LCM (Q, P) is the least common multiple of Q and P, T1 is the slot width of the stator slot of the stator, and D1 is the outer diameter of the rotor core of the rotor.

2. The rotary compressor according to claim 1, characterized in that: The rotary compressor satisfies: 36mm≤T1×Q≤70mm.

3. The rotary compressor according to claim 1, characterized in that: The rotary compressor meets the following requirements: Wherein, T2 is the tooth width of the stator.

4. The rotary compressor according to claim 1, characterized in that: An exhaust valve assembly is provided at the exhaust hole of the compression component, and the exhaust valve assembly includes an exhaust valve plate and a limiter for limiting the travel of the exhaust valve plate. The rotary compressor meets the following requirements: Wherein, t1 is the thickness of the exhaust valve sheet, and t2 is the thickness of the limiter.

5. The rotary compressor according to claim 4, characterized in that: The natural frequency of the stator is f1, the natural frequency of the limiter is f2, and the rotary compressor satisfies: |f2-f1|≥200Hz.

6. The rotary compressor according to claim 5, characterized in that: The rotor comprises a rotor core, the rotor core is provided with flow holes, the total area of ​​the flow holes is S1, the area enclosed by the outer circle and the inner circle of the rotor core is S2, and the rotary compressor satisfies:

7. The rotary compressor according to claim 1, characterized in that: The natural frequency of the stator is f1, the natural frequency of the limiter of the compression component is f2, and the natural frequency of the rotor assembly is f3, f1≠f2≠f3, wherein the rotor assembly includes the rotor of the motor, the crankshaft of the compression component, and the piston.

8. The rotary compressor according to claim 7, characterized in that: f2>f1>f3.

9. The rotary compressor according to claim 7, characterized in that: f1-f3 ≥ 200Hz; And / or, f2-f3≥200Hz.

10. The rotary compressor according to any one of claims 1 to 9, characterized in that: The number of poles P of the rotor satisfies: 10≤P≤12; the number of slots Q of the stator satisfies: 15≤Q≤18.

11. The rotary compressor according to claim 10, characterized in that: The rotary compressor meets the following requirements: Wherein, m is the number of phases of the motor.

12. A refrigeration device, characterized in that: include: A rotary compressor according to any one of claims 1 to 11.

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