Rotary compressor and refrigeration apparatus

Abstract

The application discloses a rotary compressor and a refrigeration equipment, the rotary compressor comprises a shell, a motor and a compression mechanism, the motor and the compression mechanism are arranged in the shell, the motor comprises a stator and a rotor, the compression mechanism comprises a crankshaft, the crankshaft is connected with the rotor, the rotary compressor satisfies 5<=GCD(Q,P)<=6; wherein, Q is the slot number of the stator, P is the pole number of the rotor, 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. The rotary compressor provided by the application adopts reasonable ratio settings for 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 core and the diameter d of the crankshaft, thereby improving the operation stability and energy efficiency of the rotary compressor.

Description

Technical Field

[0001] This application relates to the field of rotary compressor technology, and in particular to a rotary compressor and refrigeration equipment. Background Technology

[0002] Currently, compressor miniaturization research has gradually become one of the important directions in compressor technology development. In related technologies, some compressors require motors with a diameter of less than 112mm, typically employing 9-slot 6-pole motors or 12-slot 8-pole motors.

[0003] Further research into compressor miniaturization revealed that when the motor thickness is less than 30mm, the aforementioned rotary compressor suffers from problems such as large torque fluctuations, poor operational stability, and low energy efficiency. Summary of the Invention

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes 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, thereby improving the operational stability and energy efficiency of the rotary compressor.

[0005] This application also proposes a refrigeration device comprising the aforementioned rotary compressor.

[0006] A rotary compressor according to an embodiment of the present invention includes: 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, and the compression mechanism includes a crankshaft 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, and d is the diameter of the crankshaft.

[0007] According to the rotary compressor of the present invention, 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 set in the above-mentioned reasonable ratios. This can ensure the rotational inertia of the rotor while reducing the motor thickness, thereby improving the stability of the rotary compressor operation and 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: 80mm ≤ D1 ≤ 150mm.

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

[0013] In some embodiments, the compression mechanism further includes at least one cylinder and a piston, the piston being located within the cylinder, and the eccentric portion of the crankshaft being connected to the piston to drive the piston to rotate eccentrically; the rotary compressor also satisfies: Where H is the cylinder height 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: 10mm ≤ H ≤ 30mm.

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

[0017] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0018] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

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

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

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

[0022] Figure 4 yes The relationship between the value of the crankshaft deflection and COP is shown in the graph.

[0023] Figure 5 This is a schematic diagram of the gas resistance torque of the pump body in a rotary compressor;

[0024] Figure 6 yes The relationship between the value of the rotational inertia and COP is shown in the graph.

[0025] Figure label:

[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

[0027] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein 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 with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0028] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0029] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0030] The following is for reference. Figures 1-6 A rotary compressor 100 according to an embodiment of the present invention is described.

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

[0032] When the rotary compressor 100 is working, 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 in the cylinder 32.

[0033] The rotary compressor 100 of this embodiment satisfies the following:

[0034] 5≤GCD(Q,P)≤6, where Q is the number of slots in stator 21 (i.e., the number of stator slots 212), P is the number of poles in rotor 22, rotor 22 is provided with multiple 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 stator 21 and interacting with stator 21, so the number of poles in 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, meaning that the number of slots Q of the stator 21 can be 15, 18, 20, 24, 54, etc. Compared with the related technologies of 9-slot 6-pole motors or 12-slot 8-pole motors, in the rotary compressor 100 of this application, the motor 2 increases the number of slots of the stator 21, so that the stator 21 can provide a more uniform magnetic field distribution, reduce the non-uniformity of the magnetic field, and help improve the output power of the motor 2, thereby improving the operational stability of the rotary compressor 100. The number of poles P of the rotor 22 can be 10, 12, 20, 24, etc. Compared with the related technologies of 9-slot 6-pole motors or 12-slot 8-pole motors, the motor 2 provided in this application increases the number of poles of the rotor 22. The more poles of the rotor 22, the lower the speed of the rotor 22, the greater the torque that can be provided, and the smoother the rotation of the rotor 22, effectively improving the working stability of the motor 2, that is, improving the operational stability of the rotary compressor 100.

[0036] GCD(Q, P) can also represent the order of the minimum electromagnetic force generated by motor 2. The vibration of motor 2 is approximately inversely proportional to the fourth power of the order of the electromagnetic force of motor 2. If the order of the electromagnetic force of motor 2 is too small, the vibration of motor 2 will be too large, affecting the stability of motor 2's operation and easily generating large noise. If the order of the electromagnetic force of motor 2 is too large, it will easily increase the complexity of the electrical control of motor 2 and affect the reliability of motor 2's operation.

[0037] Therefore, Q, P, and GCD(Q, P) can be determined according to actual design requirements. For example, GCD(Q, P) can be limited to 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 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 rotor 22 can be 12 and the number of stator slots 212 can be 18. This is beneficial to reduce the vibration of motor 2, reduce the noise of motor 2, improve the stability of motor 2 operation, simplify the electrical control of motor 2, and improve the reliability of motor 2 operation.

[0038] In the further miniaturization design of the rotary compressor 100, it is necessary to reduce the thickness of the motor 2. However, reducing the thickness of the motor 2 will lead to a decrease in the rotational inertia of the rotor 22. If the rotational inertia of the rotor 22 is too small, it will be difficult for the rotor 22 to drive the piston 33 to overcome the resistance torque of the pump body when the rotary compressor 100 is running at low frequency. It is necessary to add torque compensation in the motor control, but adding torque compensation will increase the current and affect the energy efficiency of the rotary compressor 100. In order to improve the above technical problems, the rotary compressor 100 of the present invention also satisfies:

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

[0040] With the outer diameter D1 of stator 21 remaining unchanged The larger the ratio, the larger the inner diameter D2 of the stator 21, which means the larger the outer diameter of the rotor 22. The larger the outer diameter of the rotor 22, the greater the moment of inertia of the rotor 22. In other words, the motor 2 can completely or partially offset the effect of the reduction in the thickness on the moment of inertia of the rotor 22 by increasing the outer diameter of the rotor 22, thereby reducing the torque fluctuation when the rotary compressor 100 is running, improving the stability of the motor 2 when the thickness is low, and improving the energy efficiency of the rotary compressor 100 when running at low frequencies.

[0041] However, if If the ratio is too large, the cross-sectional area of ​​stator 21 will be too small, resulting in excessive iron losses in motor 2 and affecting the efficiency of motor 2. The ratio needs to be set within a reasonable range. This application will... The ratio is limited to This not only increases the rotational inertia of the rotor 22 but also avoids the problem of the stator 21 having too small a cross-sectional area, 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 values ​​such as 0.58, 0.6, 0.63, 0.67, 0.7, etc.

[0042] To further improve the stability and energy efficiency of motor 2, the rotary compressor 100 of this embodiment of the invention also satisfies the following requirements:

[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 rotor 22 is connected to crankshaft 31, the radial wobbling of rotor 22 will affect the deflection of crankshaft 31. If the value of D1*T1 is larger, the volume of stator 21 will be larger, and the volume of rotor 22 can also be designed to be larger. The greater the influence of rotor 22 on crankshaft deflection when it rotates. If the value of D1*T1 is smaller, the volume of stator 21 will be smaller, the volume of rotor 22 will also be smaller, the influence of rotor 22 on crankshaft deflection when it rotates will be smaller, and the better the stability of rotary compressor 100 operation. If the diameter d of crankshaft 31 is larger, the crankshaft 31 has stronger anti-interference ability, which will lead to smaller crankshaft deflection and better stability of rotary compressor 100 operation. The larger the number of poles P of rotor 22, the smoother the rotor 22 rotates, the smaller the wobbling of rotor 22, that is, the smaller the crankshaft deflection, and the better the stability of rotary compressor 100 operation.

[0045] However, if the value of D1*T1 is too small, the rotor 22 will be too small, affecting its moment of inertia. If the diameter d of the crankshaft 31 is too large, the cost of the rotary compressor 100 will increase. If the number of poles P of the rotor 22 is too large, the machining difficulty of the motor 2 will increase, further increasing the cost of the rotary compressor 100. Therefore, the values ​​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] As described above, the value of D1*T1, the diameter d of crankshaft 31, and the number of poles P of rotor 22 are all related to crankshaft deflection. Therefore, it can be determined through... Evaluate crankshaft deflection.

[0047] Reference Figure 4 , Figure 4 for The graph shows the relationship between the value of the crankshaft and crankshaft deflection and COP (Coefficient of Performance).

[0048] Reference Figure 4 It can be seen that, The larger the value, the greater the deflection of crankshaft 31. At that time, the crankshaft 31 has relatively small deflection, and the rotary compressor 100 has good operational stability. At that time, the COP of the rotary compressor 100 is at a high value, which effectively improves the cooling capacity of the rotary compressor 100.

[0049] According to the rotary compressor 100 of the present invention, 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 are set in the above-mentioned reasonable ratios. This can ensure the rotational inertia of the rotor 22 while reducing the thickness of the motor 2, thereby improving the operational stability of the rotary compressor 100 and improving the energy efficiency of the rotary compressor 100.

[0050] In some further embodiments, the rotary compressor 100 satisfies: Reference Figure 4 It can be seen that, Within the range of 15-18, while ensuring stable operation of the rotary compressor, the rotary compressor has a higher coefficient of performance (COP), which further improves the cooling capacity of the rotary compressor 100.

[0051] In some specific embodiments, The value is 18, in other embodiments, It can also be a number such as 15, 15.6, 16, 16.8, 17, etc.

[0052] In some embodiments, the number of poles P of rotor 22 satisfies: 10≤P≤12; the number of slots Q of stator 21 satisfies: 15≤Q≤18.

[0053] Through the above technical solutions, in the embodiments of this 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, the values ​​of the number of poles of the rotor 22 and the number of slots of the stator 21 are not too large, which reduces the production difficulty of the motor 2 and reduces 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 embodiment of this application is a fractional slot motor 2. The fractional slot motor 2 has the advantages of high efficiency, high power density, and low rotational pulsation, which effectively improves the energy efficiency and stability of the rotary compressor 100.

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

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

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

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

[0060] In this embodiment, the outer diameter D1 of the stator 21 is limited to 80mm≤D1≤150mm, which satisfies the miniaturization design of the rotary compressor 100 while reducing the processing cost of the motor 2.

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

[0062] In some embodiments, the rotary compressor 100 of the present invention further satisfies: Where 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 part 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 more easily overcomes the gas resistance torque of the pump body. (Refer to...) Figure 5The larger the value of H*e, the greater the peak value of the pump body gas resistance torque. This makes it more difficult for piston 33 to overcome the pump body gas resistance torque when the rotary compressor 100 operates at low frequencies. Conversely, the larger the number of poles P of rotor 22, the greater the torque provided by rotor 22. This makes it easier for piston 33 to overcome the pump body gas resistance torque when the rotary compressor 100 operates at low frequencies. Therefore, the value of H*e, the thickness T2 of the rotor 22's iron core, and the number of poles P of rotor 22 all need to be controlled within a reasonable range.

[0064] Reference Figure 6 , Figure 6 for The graph shows the relationship between the value of the rotational inertia and the COP (Coefficient of Performance).

[0065] Reference Figure 6 It can be seen that, with As the moment of inertia increases, the coulombic angle (COP) first increases and then decreases. At the same time, the COP and moment of inertia of the rotary compressor 100 are within a reasonable range, which effectively improves the stability and energy efficiency of the rotary compressor 100.

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

[0067] In this embodiment of the application, The value is limited to a more preferred range, which further improves the energy efficiency of the rotary compressor 100 while ensuring stable operation of the rotary compressor 100.

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

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

[0070] In this embodiment, the cylinder height H of cylinder 32 is limited to 10mm≤H≤30mm. While ensuring the cooling capacity of rotary compressor 100, the peak value of pump body gas resistance torque is reduced, effectively improving the energy efficiency of rotary compressor 100 in low-frequency operation.

[0071] In some embodiments, the rotary compressor 100 satisfies: T1≤T2, and 20mm≤T1≤80mm, 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 this embodiment, 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 in driving the rotor 22 to rotate.

[0073] If the thickness T1 of the stator 21 core is less than 20mm, it will increase the processing cost of the motor 2 and affect the power of the motor 2. If the thickness T1 of the stator 21 core is greater than 80mm, 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.

[0074] In this embodiment, the thickness T1 of the stator 21 core is limited to 20mm≤T1≤80mm, which satisfies the miniaturization design of the rotary compressor 100 while reducing the processing cost of the motor 2.

[0075] The refrigeration apparatus according to an embodiment of the present invention includes: the rotary compressor 100 described above.

[0076] According to the refrigeration device of the present invention, in its rotary compressor 100, the number of slots Q of stator 21, the number of poles P of rotor 22, the outer diameter D1 of stator 21, the inner diameter D2 of stator 21, the thickness T1 of stator 21 core, and the diameter d of crankshaft 31 are set in the above-mentioned reasonable ratios. This can ensure the rotational inertia of rotor 22 while reducing the thickness of motor 2, thereby improving the operational stability of rotary compressor 100, improving the energy efficiency of rotary compressor 100, and thus improving the operational stability and energy efficiency of refrigeration device.

[0077] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0078] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A rotary compressor, characterized in that, include: The rotary compressor comprises 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, and the compression mechanism includes a crankshaft connected to the rotor; the rotary compressor satisfies: 5 ≤ GCD(Q, P) ≤ 6; 0.55≤ ≤0.7；13≤ ≤25； 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, 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: <1, 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: 0.6 ≤ ≤0.

65.

5. The rotary compressor according to claim 4, characterized in that, The rotary compressor meets the following requirements: 80mm≤D1≤150mm.

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

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 being located inside the cylinder, and the eccentric portion of the crankshaft being connected to the piston to drive the piston to rotate eccentrically; The rotary compressor also satisfies: 0.015 ≤ ≤0.085, where H is the cylinder height, e is the eccentricity of the eccentric part, and T2 is the thickness of the rotor core.

8. The rotary compressor according to claim 7, characterized in that, The rotary compressor further satisfies: 0.025 ≤ ≤0.

036.

9. The rotary compressor according to claim 7, characterized in that, The rotary compressor meets the following requirements: 10mm≤H≤30mm.

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

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