Rotary compressor and refrigeration equipment

Abstract

The utility model discloses a rotary compressor and refrigeration equipment, the rotary compressor comprises a shell, a motor and a compression mechanism, the motor and the compression mechanism are both arranged in the shell, the motor comprises a stator and a rotor, the compression mechanism comprises a crankshaft, and the crankshaft is connected with the rotor; the rotary compressor meets the following conditions: 5 < = GCD (Q, P) < = 6; q is the number of slots of the stator, P is the number of poles of the rotor, D2 is the inner diameter of the stator, D1 is the outer diameter of the stator, T1 is the thickness of a stator core of the stator, and d is the diameter of the crankshaft. According to the rotary compressor provided by the utility model, the slot number Q of the stator, the pole number P of the rotor, the outer diameter D1 of the stator, the inner diameter D2 of the stator, the thickness T1 of the stator iron core and the diameter d of the crankshaft are set according to reasonable ratios, so that the operation stability and the energy efficiency of the rotary compressor are improved.

Description

Technical Field

[0001] The present application relates to the technical field of rotary compressors, and more particularly to a rotary compressor and a refrigeration device. Background Art

[0002] At present, the research on the miniaturization of compressors has gradually become one of the important directions in the development of compressor technology. In related technologies, some compressors require motors with a motor diameter less than 112 mm, and usually 9-slot 6-pole motors or 12-slot 8-pole motors are used.

[0003] In the further research on the miniaturization of compressors, it is found that when the stack thickness of the motor is less than 30 mm, the above-mentioned rotary compressors have problems of large torque fluctuations, poor operating stability, and low energy efficiency. Utility Model Content

[0004] 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, in which the number of slots Q of the stator, the number of poles P of the rotor, the outer diameter D1 of the stator, the inner diameter D2 of the stator, the thickness T1 of the stator core, and the diameter d of the crankshaft are all set with reasonable ratios, improving the operating stability and energy efficiency of the rotary compressor.

[0005] The present application also provides a refrigeration device including the above-mentioned rotary compressor.

[0006] The rotary compressor according to an embodiment of the utility model includes: a housing, a motor, and a compression mechanism. The motor and the compression mechanism are both arranged in the housing. The motor includes a stator and a rotor. The compression mechanism includes a crankshaft, and the crankshaft is connected to the rotor. The rotary compressor satisfies: 5 ≤ GCD(Q, P) ≤ 6; Wherein, Q is the number of slots of the stator, P is the number of poles of the rotor, GCD(Q, P) is the greatest common divisor of Q and P, D2 is the inner diameter of the stator, D1 is the outer diameter of the stator, T1 is the thickness of the stator core of the stator, and d is the diameter of the crankshaft.

[0007] For the rotary compressor according to an embodiment of the utility model, by setting the number of slots Q of the stator, the number of poles P of the rotor, the outer diameter D1 of the stator, the inner diameter D2 of the stator, the thickness T1 of the stator core, and the diameter d of the crankshaft with the above-mentioned reasonable ratios, it is possible to ensure the moment of inertia of the rotor while reducing the stack thickness of the motor, improve the operating stability of the rotary compressor, and improve the energy efficiency of the rotary compressor.

[0008] In some embodiments, the number of poles P of the motor satisfies: 10 ≤ P ≤ 12; the number of slots Q of the stator satisfies: 15 ≤ Q ≤ 18.

[0009] In some embodiments, the rotary compressor satisfies: where m is the number of phases of the motor.

[0010] In some embodiments, the rotary compressor further satisfies:

[0011] In some embodiments, the rotary compressor satisfies: 80 mm ≤ D1 ≤ 150 mm.

[0012] In some embodiments, the rotary compressor satisfies: T1 ≤ T2, and 20 mm ≤ T1 ≤ 80 mm, where T2 is the thickness of the iron core of the rotor.

[0013] In some embodiments, the compression mechanism further includes at least one cylinder and a piston. The piston is located inside the cylinder, and the eccentric part of the crankshaft is connected to the piston to drive the piston to rotate eccentrically; the rotary compressor further satisfies: where H is the cylinder height of the cylinder, and e is the eccentricity of the eccentric part.

[0014] In some embodiments, the rotary compressor further satisfies:

[0015] In some embodiments, the rotary compressor satisfies: 10 mm ≤ H ≤ 30 mm.

[0016] The refrigeration device according to an embodiment of the present invention includes: the rotary compressor described in the above technical solution.

[0017] The additional aspects and advantages of the present invention will be partially given in the following description, partially become obvious from the following description, or be understood through the practice of the present invention. Description of the Drawings

[0018] The above and / or additional aspects and advantages of the present invention will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, where:

[0019] Figure 1 is a cross-sectional view of the rotary compressor according to an embodiment of the present invention;

[0020] Figure 2 is a cross-sectional view of a part of the structure in the rotary compressor according to an embodiment of the present invention;

[0021] Figure 3 is a top view of the motor;

[0022] Figure 4 is a graph showing the relationship between the value of and the crankshaft deflection and the COP;

[0023] Figure 5 It is a schematic diagram of the gas resistance moment of the pump body of a rotary compressor;

[0024] Figure 6 is a graph showing the relationship between the value and the moment of inertia as well as the COP.

[0025] Reference numerals:

[0026] 100, rotary compressor; 1, housing; 2, motor; 21, stator; 211, stator core; 212, stator slot; 22, rotor; 221, rotor core; 222, rotor magnet; 3, compression mechanism; 31, crankshaft; 311, eccentric part; 32, cylinder; 33, piston. Detailed implementation manners

[0027] The embodiments of the present invention will be described in detail below. The examples of the embodiments are shown in the drawings, where the same or similar reference numerals indicate the same or similar elements or elements with the same or similar functions throughout. The embodiments described below with reference to the drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation of the present invention.

[0028] In the description of the present invention, it should be understood that 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. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation of the present invention. 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 invention, unless otherwise stated, the meaning of "a plurality" is two or more.

[0029] In the description of the present invention, it should be noted that, unless otherwise clearly defined and limited, the terms "installed", "connected", "connected" should be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral connection; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0030] Next, refer toFigures 1-6 Describe a rotary compressor 100 according to an embodiment of the present utility model.

[0031] Refer to Figure 1 and Figure 2 and Figure 3 According to an embodiment of the present utility model, the rotary compressor 100 includes: a housing 1, a motor 2, and a compression mechanism 3. The motor 2 and the compression mechanism 3 are both disposed within the housing 1. The motor 2 includes a stator 21 and a rotor 22. The compression mechanism 3 includes a crankshaft 31, and the crankshaft 31 is connected to the rotor 22. The compression mechanism 3 further includes at least one cylinder 32 and a piston 33. The piston 33 is located within the cylinder 32, and an eccentric portion 311 of the crankshaft 31 is connected to the piston 33.

[0032] When the rotary compressor 100 operates, the stator 21 is energized to generate a magnetic field. The magnetic field generated by the stator 21 interacts with the magnetic field generated by the rotor 22 to drive the rotor 22 to rotate. The rotor 22 drives the piston 33 to rotate eccentrically through the crankshaft 31, thereby compressing the gas within the cylinder 32.

[0033] The rotary compressor 100 according to an embodiment of the present utility model satisfies:

[0034] 5 ≤ GCD(Q, P) ≤ 6, where Q is the number of slots of the stator 21 (i.e., the number of stator slots 212), P is the number of poles of the rotor 22. The rotor 22 is provided with a plurality of rotor magnets 222. Each rotor magnet 22 has its own south pole and north pole, but each rotor 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 rotor magnets 222, and GCD(Q, P) is the greatest common divisor of Q and P.

[0035] In the above technical solution, 5 ≤ GCD(Q, P) ≤ 6. That is to say, the number of slots Q of the stator 21 can be values such as 15, 18, 20, 24, 54, etc. Compared with the motors with 9 slots and 6 poles or 12 slots and 8 poles in the related art, in the rotary compressor 100 of the present application, by increasing the number of slots of the stator 21, the stator 21 can provide a more uniform magnetic field distribution, reduce the non-uniformity of the magnetic field, which is beneficial to improving the output power of the motor 2, thereby improving the operating stability of the rotary compressor 100; the number of poles P of the rotor 22 can be values such as 10, 12, 20, 24, etc. Compared with the motors with 9 slots and 6 poles or 12 slots and 8 poles in the related art, the motor 2 provided in the present application increases the number of poles of the rotor 22. The more the number of poles of the rotor 22, the lower the rotational speed of the rotor 22, the greater the torque that can be provided, and the higher the smoothness of the rotation of the rotor 22, effectively improving the operating stability of the motor 2, that is, improving the operating stability of the rotary compressor 100.

[0036] GCD(Q, P) can also represent the order of the minimum electromagnetic force generated by the motor 2. The vibration of the motor 2 is approximately inversely proportional to the fourth power of the order of the electromagnetic force of the motor 2. If the order of the electromagnetic force of the motor 2 is too small, the vibration of the motor 2 is too large, which affects the stability of the operation of the motor 2 and is prone to generate relatively large noise. If the order of the electromagnetic force of the motor 2 is too large, it is likely to increase the complexity of the electronic control of the motor 2, affecting the reliability of the operation of the motor 2.

[0037] Therefore, Q, P, and GCD(Q, P) can be determined according to actual design requirements. For example, GCD(Q, P) can be limited within the range of 5 - 6, that is, GCD(Q, P) can be 5 or 6. When GCD(Q, P) = 5, the number of poles of the rotor 22 can be 10, and the number of stator slots 212 can be 15. When GCD(Q, P) = 6, the number of poles of the rotor 22 can be 12, and the number of stator slots 212 can be 18. This is beneficial to reducing the vibration degree of the motor 2, beneficial to reducing the noise of the motor 2, can improve the stability of the operation of the motor 2, and at the same time is beneficial to simplifying the electronic control of the motor 2 and improving the reliability of the operation of the motor 2.

[0038] In the further design of miniaturizing the rotary compressor 100, it is necessary to reduce the product thickness of the motor 2. However, reducing the product thickness of the motor 2 will result in a decrease in the moment of inertia of the rotor 22. If the moment of inertia of the rotor 22 is too small, when the rotary compressor 100 operates at a low frequency, the rotor 22 will be difficult to drive the piston 33 to overcome the resistance torque of the pump body, and it is necessary to increase torque compensation in the motor control. However, increasing torque compensation will increase the current, affecting the energy efficiency of the rotary compressor 100. To improve the above technical problems, the rotary compressor 100 of the embodiment of the present utility model further satisfies:

[0039] Wherein, D2 is the inner diameter of the stator 21, and D1 is the outer diameter of the stator 21.

[0040] When the outer diameter D1 of the stator 21 remains unchanged, the larger the ratio, the larger the inner diameter D2 of the stator 21, that is, the larger the outer diameter of the rotor 22. The larger the outer diameter of the rotor 22, the larger the moment of inertia of the rotor 22. That is to say, the motor 2 can, by increasing the outer diameter of the rotor 22, completely offset or partially offset the influence of the reduction of the product thickness on the moment of inertia of the rotor 22, reduce the torque fluctuation during the operation of the rotary compressor 100, improve the stability of the operation of the motor 2 at a lower product thickness, and at the same time improve the energy efficiency of the rotary compressor 100 during low-frequency operation.

[0041] However, if the ratio is too large, it will result in too small a cross-sectional area of the stator 21, resulting in too large iron loss of the motor 2, affecting the efficiency of the motor 2. Therefore The ratio needs to be set within a reasonable range. In this application, the ratio is limited to which can not only increase the moment of inertia of the rotor 22, but also avoid the problem of too small cross-sectional area of the stator 21, effectively improving the stability and energy efficiency of the motor 2. In some specific embodiments, it can be 0.55. In other embodiments, it can also be numerical values such as 0.58, 0.6, 0.63, 0.67, 0.7, etc.

[0042] In order to further improve the stability and energy efficiency of the operation of the motor 2, the rotary compressor 100 of the embodiment of the present utility model further satisfies:

[0043] wherein, T1 is the thickness of the stator core 211 of the stator 21, and d is the diameter of the crankshaft 31.

[0044] Because the rotor 22 is connected to the crankshaft 31, the wobbling of the rotor 22 in the radial direction will affect the deflection of the crankshaft 31. If the value of D1*T1 is larger, the volume of the stator 21 is larger, and the volume of the rotor 22 can also be designed to be larger. The greater the influence of the rotation of the rotor 22 on the deflection of the crankshaft. If the value of D1*T1 is smaller, the volume of the stator 21 is smaller, and the volume of the rotor 22 is also smaller. The smaller the influence of the rotation of the rotor 22 on the deflection of the crankshaft, the better the stability of the operation of the rotary compressor 100; if the diameter d of the crankshaft 31 is larger, the anti-interference ability of the crankshaft 31 is stronger, which will result in a smaller deflection of the crankshaft 31, and the better the stability of the operation of the rotary compressor 100; the greater the number of poles P of the rotor 22, the higher the smoothness of the rotation of the rotor 22, the smaller the wobbling of the rotor 22, that is, the smaller the deflection of the crankshaft, and the better the stability of the operation of the rotary compressor 100.

[0045] However, if the value of D1*T1 is too small, it will cause the volume of the rotor 22 to be too small, affecting the moment of inertia of the rotor 22; if the diameter d of the crankshaft 31 is too large, it will increase the cost of the rotary compressor 100; if the number of poles P of the rotor 22 is too large, it will increase the processing difficulty of the motor 2 and increase the cost of the rotary compressor 100. Therefore, the value of D1*T1, the diameter d of the crankshaft 31, and the number of poles P of the rotor 22 all need to be controlled within a reasonable range.

[0046] According to the above description, it can be seen that the value of D1*T1, the diameter d of the crankshaft 31, and the number of poles P of the rotor 22 are all related to the crankshaft deflection. Therefore, the crankshaft deflection can be evaluated by judging the crankshaft deflection.

[0047] Referring to Figure 4 , Figure 4 is Graph showing the relationship between the value, the crankshaft deflection, and the COP (Coefficient Of Performance).

[0048] Referring to Figure 4 it can be seen that the larger the value, the greater the deflection of the crankshaft 31. When the case, the deflection of the crankshaft 31 is smaller, and the rotary compressor 100 operates with better stability. When the case, the COP energy efficiency of the rotary compressor 100 is at a relatively high value, effectively improving the refrigerating capacity of the rotary compressor 100.

[0049] For the rotary compressor 100 according to the embodiment of the present invention, with the number of slots Q of the stator 21, the number of poles P of the rotor 22, the outer diameter D1 of the stator 21, the inner diameter D2 of the stator 21, the thickness T1 of the stator 21 iron core, and the diameter d of the crankshaft 31, by adopting the above reasonable ratio settings, it is possible to ensure the moment of inertia of the rotor 22 while reducing the stack thickness of the motor 2, improve the operating stability of the rotary compressor 100, and improve the energy efficiency of the rotary compressor 100.

[0050] In some further embodiments, the rotary compressor 100 satisfies: Referring to Figure 4 it can be seen that when it is within the range of 15 - 18, while ensuring the stable operation of the rotary compressor, the refrigeration coefficient COP of the rotary compressor is higher, further improving the refrigerating capacity of the rotary compressor 100.

[0051] In some specific embodiments, is 18. In other embodiments, it can also be values such as 15, 15.6, 16, 16.8, 17, etc.

[0052] 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.

[0053] Through the above technical solutions, 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 restricting the number of poles of the rotor 22 and the number of slots of the stator 21, it is possible to avoid the values of the number of poles of the rotor 22 and the number of slots of the stator 21 from being too large, reducing the production difficulty of the motor 2 and the cost of the rotary compressor 100.

[0054] In some specific embodiments, the rotary compressor 100 satisfies: where m is the number of phases of the motor 2.

[0055] Through the above technical solution, the motor 2 in the embodiments of the present application is a fractional-slot motor 2, which has the advantages of high efficiency, high power density, low rotational pulsation, etc., effectively improving the energy efficiency and stability of the rotary compressor 100.

[0056] In some preferred embodiments, the rotary compressor 100 further satisfies:

[0057] In the embodiments of the present application, The value is limited to a more preferred range, while ensuring the stable operation of the rotary compressor 100, further improving the energy efficiency of the rotary compressor 100.

[0058] In some embodiments, the rotary compressor 100 satisfies: 80 mm ≤ D1 ≤ 150 mm.

[0059] If the outer diameter D1 of the stator 21 is less than 80 mm, the processing cost of the motor 2 will increase, affecting the power of the motor 2. If the outer diameter D1 of the stator 21 is greater than 150 mm, it will cause the motor 2 to occupy too much space inside the rotary compressor 100, which is not conducive to the miniaturization of the rotary compressor 100.

[0060] In the embodiments of the present application, the outer diameter D1 of the stator 21 is limited to 80 mm ≤ D1 ≤ 150 mm, while meeting the miniaturization design of the rotary compressor 100, reducing the processing cost of the motor 2.

[0061] In some specific embodiments, the outer diameter D1 of the stator 21 is 80 mm. In other embodiments, the outer diameter D1 of the stator 21 can also be 90 mm, 100 mm, 112 mm, 140 mm, 150 mm and other sizes.

[0062] In some embodiments, the rotary compressor 100 of the embodiments of the present utility model further satisfies: Wherein, T2 is the thickness of the rotor core 221 of the rotor 22, H is the cylinder height of the cylinder 32, and e is the eccentricity of the eccentric portion 311.

[0063] The greater the thickness T2 of the rotor core 221, the greater the moment of inertia of the rotor 22. When the rotary compressor 100 operates at low frequency, the piston 33 is more likely to overcome the gas resistance moment of the pump body; Refer to Figure 5, the greater the value of H*e, the greater the peak value of the gas resistance moment of the pump body. When the rotary compressor 100 operates at low frequency, the more difficult it is for the piston 33 to overcome the gas resistance moment of the pump body; the greater the number of poles P of the rotor 22, the greater the torque provided by the rotor 22, and when the rotary compressor 100 operates at low frequency, the easier it is for the piston 33 to overcome the gas resistance moment of the pump body. Therefore, the values of H*e, the thickness T2 of the iron core of the rotor 22, and the number of poles P of the rotor 22 all need to be controlled within a reasonable range.

[0064] Refer to Figure 6 , Figure 6 is a graph of the relationship between the value of and the moment of inertia and the COP (Coefficient of Performance).

[0065] Refer to Figure 6 It can be seen that as increases, the moment of inertia gradually increases, and the COP first increases and then decreases. When , both the COP and the moment of inertia of the rotary compressor 100 are within a reasonable range, effectively improving the operating stability and energy efficiency of the rotary compressor 100.

[0066] In some preferred embodiments, the rotary compressor 100 further satisfies:

[0067] In the embodiments of the present application, the value of is limited to a more preferred range, while ensuring the stable operation of the rotary compressor 100, further improving the energy efficiency of the rotary compressor 100.

[0068] In some embodiments, the rotary compressor 100 satisfies: 10mm ≤ H ≤ 30mm.

[0069] If the cylinder height H of the cylinder 32 is less than 10mm, it will cause the compression space in the cylinder 32 to be too small, affecting the refrigerating capacity of the rotary compressor 100. If the cylinder height H of the cylinder 32 is greater than 30mm, it will cause the peak value of the gas resistance moment of the pump body to be too large, which is not conducive to the energy efficiency of the rotary compressor 100 during low-frequency operation.

[0070] In the embodiments of the present application, the cylinder height H of the cylinder 32 is limited to 10mm ≤ H ≤ 30mm, while ensuring the refrigerating capacity of the rotary compressor 100, reducing the peak value of the gas resistance moment of the pump body, and effectively improving the energy efficiency of the rotary compressor 100 during low-frequency operation.

[0071] In some embodiments, the rotary compressor 100 satisfies: T1 ≤ T2, and 20 mm ≤ T1 ≤ 80 mm, where T1 is the thickness of the stator core 211 of the stator 21, and T2 is the thickness of the rotor core 221 of the rotor 22.

[0072] In the embodiments of the present application, the thickness T1 of the stator core 211 is less than the thickness T2 of the rotor core 221, which improves the efficiency of the stator 21 driving the rotor 22 to rotate.

[0073] If the thickness T1 of the stator 21 core is less than 20 mm, the processing cost of the motor 2 will increase, affecting the power of the motor 2. If the thickness T1 of the stator 21 core is greater than 80 mm, the motor 2 will occupy too much space inside the rotary compressor 100, which is not conducive to the miniaturization of the rotary compressor 100.

[0074] In the embodiments of the present application, the thickness T1 of the stator 21 core is limited to 20 mm ≤ T1 ≤ 80 mm, which reduces the processing cost of the motor 2 while meeting the miniaturization design of the rotary compressor 100.

[0075] The refrigeration device according to the embodiment of the present utility model includes: the rotary compressor 100 in the above technical solution.

[0076] In the rotary compressor 100 of the refrigeration device according to the embodiment of the present utility model, for the number of slots Q of the stator 21, the number of poles P of the rotor 22, the outer diameter D1 of the stator 21, the inner diameter D2 of the stator 21, the thickness T1 of the stator 21 core, and the diameter d of the crankshaft 31, adopting the above reasonable ratio settings can ensure the moment of inertia of the rotor 22 while reducing the stack height of the motor 2, improve the operating stability of the rotary compressor 100, improve the energy efficiency of the rotary compressor 100, thereby improving the operating stability of the refrigeration device and improving the energy efficiency of the refrigeration device.

[0077] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples" 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 descriptions 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 any one or more embodiments or examples in a suitable manner.

[0078] Although 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. The scope of the present utility model is defined by the claims and their equivalents.

Claims

1. A rotary compressor, characterized in that, including: A housing, a motor, and a compression mechanism, wherein the motor and the compression mechanism are both disposed within the housing, the motor includes a stator and a rotor, the compression mechanism includes a crankshaft, and the crankshaft is connected to the rotor; the rotary compressor satisfies: 5 ≤ GCD(Q, P) ≤ 6; wherein, Q is the number of slots of the stator, P is the number of poles of the rotor, GCD(Q, P) is the greatest common divisor of Q and P, D2 is the inner diameter of the stator, D1 is the outer diameter of the stator, T1 is the thickness of the stator core of the stator, and d is the diameter of the crankshaft.

2. The rotary compressor according to claim 1, 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.

3. The rotary compressor according to claim 2, characterized in that, The rotary compressor satisfies: where m is the number of phases of the motor.

4. The rotary compressor according to claim 1, characterized in that The rotary compressor further satisfies:

5. The rotary compressor according to claim 4, wherein The rotary compressor satisfies: 80 mm ≤ D1 ≤ 150 mm.

6. The rotary compressor according to claim 1, characterized in that, The rotary compressor satisfies: T1 ≤ T2, and 20 mm ≤ T1 ≤ 80 mm, wherein, T2 is the thickness of the rotor core of the rotor.

7. The rotary compressor according to any one of claims 1-6, characterized in that, The compression mechanism further includes at least one cylinder and a piston, the piston is located in the cylinder, and the eccentric part of the crankshaft is connected to the piston to drive the piston to rotate eccentrically; The rotary compressor further satisfies: wherein, H is the cylinder height of the cylinder, and e is the eccentricity of the eccentric part.

8. The rotary compressor according to claim 1, wherein, The rotary compressor further satisfies:

9. The rotary compressor according to claim 1, characterized in that, The rotary compressor satisfies: 10 mm ≤ H ≤ 30 mm.

10. A refrigeration device, characterized in that, including: The rotary compressor according to any one of claims 1-9.

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