Compressor and refrigeration equipment

Abstract

The invention discloses a compressor and refrigeration equipment, and belongs to the technical field of compressors, the compressor comprises a crankshaft and a rotor assembly, and the crankshaft is provided with a main shaft section; the rotor assembly comprises a rotor iron core and permanent magnets arranged on the rotor iron core, the rotor iron core is connected with the main shaft section, the rotor assembly is provided with a plurality of magnetic poles, a plurality of permanent magnets are arranged below each magnetic pole, the sum of the lengths of the plurality of permanent magnets in the direction perpendicular to the magnetizing direction is L1, the diameter of the main shaft section is D, and L1 / D is larger than or equal to 1.9 and smaller than or equal to 2.1. According to the compressor, by optimizing the size proportional relation between the permanent magnet and the crankshaft main shaft section, the overall rigidity of the compressor is enhanced, the vibration and noise reduction performance of the compressor is improved, the stability and reliability of the compressor are improved, the working efficiency of the compressor can be improved, energy consumption is reduced, and good balance between energy efficiency and cost is achieved.

Description

Technical Field

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

[0002] As a core power component in refrigeration equipment such as air conditioners and refrigerators, the compressor's performance and efficiency directly determine the overall energy efficiency and user experience of the appliance. With technological advancements and improved living standards, the energy efficiency of home appliances has received increasing attention from all sectors of society. In particular, the release of the new national Level 1 energy efficiency standard and the continuous promotion of energy conservation and emission reduction policies in recent years have placed higher demands on compressor energy efficiency. In related technologies, improving compressor energy efficiency often involves increasing the refrigerant charge, optimizing system circulation, and improving heat exchange efficiency. However, while these methods improve energy efficiency, they often come at the cost of significantly increased costs or decreased reliability, making it difficult to gain a competitive edge in the market. Therefore, improving compressor energy efficiency while maintaining controllable costs and ensuring reliability has become an important direction for current compressor technology development. Summary of the Invention

[0003] This application aims to at least solve one of the technical problems existing in the prior art. To this end, one object of this application is to provide a compressor that can enhance the overall rigidity of the compressor, improve the compressor's vibration and noise reduction performance, improve the compressor's stability and reliability, and also improve the compressor's working efficiency and save energy consumption by optimizing the dimensional ratio between the permanent magnet and the crankshaft main shaft section, thereby achieving a good balance between energy efficiency and cost.

[0004] This application also proposes a refrigeration device having the above-mentioned compressor.

[0005] According to a first aspect embodiment of the compressor of this application, the compressor includes: a crankshaft and a rotor assembly, the crankshaft having a main shaft section; the rotor assembly includes: a rotor core and permanent magnets disposed on the rotor core, the rotor core being connected to the main shaft section, the rotor assembly having a plurality of magnetic poles, and a plurality of permanent magnets being disposed under each magnetic pole, the sum of the lengths of the plurality of permanent magnets perpendicular to the magnetization direction being L1, and the diameter of the main shaft section being D, satisfying 1.9≤L1 / D≤2.1.

[0006] According to the compressor of this application, by optimizing the dimensional ratio between the permanent magnet in the rotor assembly and the main shaft section in the crankshaft, the overall rigidity of the compressor can be enhanced, the vibration and noise reduction performance of the compressor can be improved, the stability and reliability of the compressor can be increased, the working efficiency of the compressor can be improved, and energy consumption can be saved, thus achieving a good balance between energy efficiency and cost.

[0007] According to some embodiments of this application, the number of permanent magnets under each magnetic pole is an odd number. Each permanent magnet includes an intermediate magnet and a plurality of lateral magnets symmetrically arranged relative to the intermediate magnet. The intermediate magnet and the lateral magnets surround the magnetic pole, and the sum of the lengths of the intermediate magnet and the lateral magnets in the direction perpendicular to the magnetization direction is L1.

[0008] Furthermore, there are three permanent magnets under each magnetic pole, the three permanent magnets surround the magnetic pole, and the lengths of the three permanent magnets perpendicular to the magnetization direction are A1, A2, and A3, respectively, and A1+A2+A3=L1.

[0009] In some embodiments, the rotor core has a flow passage with an area of ​​S, and the radius of the rotor core is R1, satisfying 0.95 ≤ 100 * S / (π * R1) 2 ) / D≤1.3.

[0010] According to some embodiments of this application, the rotor core has a shaft hole, and the main shaft section is connected to the rotor core within the shaft hole.

[0011] Furthermore, the inner diameter of the shaft hole is R2, and satisfies 0.15≤R2 / R1≤0.45.

[0012] In some embodiments, the weight of the rotor assembly is W1, the weight of the crankshaft is W2, and the condition 7.5 ≤ W1 / W2 ≤ 8 is met.

[0013] According to some embodiments of this application, 10mm ≤ D ≤ 12.5mm.

[0014] According to some embodiments of this application, the axial dimension of the rotor core is L2, and satisfies 3≤L2 / D≤5.

[0015] According to a second aspect of this application, the refrigeration apparatus includes a compressor as described in any of the above embodiments.

[0016] Additional aspects and advantages of this application 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 this application. Attached Figure Description

[0017] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0018] Figure 1 This is a schematic diagram of the compressor structure according to an embodiment of this application;

[0019] Figure 2This is a schematic diagram of the fit between the rotor assembly and the stator assembly according to an embodiment of this application;

[0020] Figure 3 This is a schematic diagram of a rotor assembly according to an embodiment of this application;

[0021] Figure 4 This is a cross-sectional view of a crankshaft according to an embodiment of this application;

[0022] Figure 5 This is a schematic diagram illustrating the change of compressor COP with L1 / D value according to an embodiment of this application;

[0023] Figure 6 This is a comparison diagram of the COP of a compressor according to an embodiment of this application and a compressor in related technologies.

[0024] Figure label:

[0025] 1000, Compressor;

[0026] 10. Crankshaft; 12. Main shaft section; 14. Eccentric section; 16. Countershaft section;

[0027] 20. Rotor assembly;

[0028] 22. Rotor core; 22a. Flow hole; 22b. Shaft hole; 22c. Permanent magnet slot;

[0029] 24. Permanent magnet; 242. First permanent magnet; 244. Second permanent magnet; 246. Third permanent magnet;

[0030] 30. Stator assembly; 40. Winding; 50. Cylinder; 60. Bearing; 70. Liquid reservoir. Detailed Implementation

[0031] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0032] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the description of this application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms "comprising" and "having," and any variations thereof, in the description, claims, and accompanying drawings of this application are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the description, claims, or accompanying drawings of this application are used to distinguish different objects, not to describe a specific order or hierarchy.

[0033] In this application, the reference to "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment that is mutually exclusive with other embodiments.

[0034] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "attachment" 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 direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0035] In this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent three cases: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, in this application, the character " / " generally indicates that the preceding and following related objects have an "or" relationship.

[0036] In the embodiments of this application, the same reference numerals denote the same components, and for the sake of brevity, detailed descriptions of the same components are omitted in different embodiments. It should be understood that the thickness, length, width, and other dimensions of various components in the embodiments of this application shown in the accompanying drawings, as well as the overall thickness, length, width, and other dimensions of the integrated device, are merely illustrative and should not constitute any limitation on this application.

[0037] In the description of this application, 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", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application 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 this application.

[0038] In the description of this application, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or it may include the first and second features not being in direct contact but being in contact through another feature between them.

[0039] In the description of this application, the terms "above," "over," and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0040] In this application, "multiple" means two or more (including two).

[0041] The following is for reference. Figures 1-6 This application describes a compressor 1000 and a refrigeration device according to embodiments thereof.

[0042] like Figure 1 As shown, according to a first aspect embodiment of the present application, the compressor 1000 includes a crankshaft 10 and a rotor assembly 20.

[0043] The crankshaft 10 has a main shaft section 12; the rotor assembly 20 includes a rotor core 22 and permanent magnets 24 disposed on the rotor core 22. The rotor core 22 is connected to the main shaft section 12. The rotor assembly 20 has multiple magnetic poles, and multiple permanent magnets 24 are disposed under each magnetic pole. The sum of the lengths of the multiple permanent magnets 24 perpendicular to the magnetization direction is L1. The diameter of the main shaft section 12 is D, and satisfies 1.9≤L1 / D≤2.1.

[0044] Specifically, the crankshaft 10 may include a main shaft section 12, an eccentric section 14, and a secondary shaft section 16 arranged sequentially along the axial direction. The main shaft section 12 is the main load-bearing and transmission part. The main shaft section 12 is connected to the rotor core 22 of the rotor assembly 20. When the rotor assembly 20 is running, it can drive the main shaft section 12 to rotate. The eccentric section 14 can be arranged eccentrically relative to the center line of the main shaft section 12. The secondary shaft section 16 further assists the main shaft section 12 and the eccentric section 14 in completing the power transmission, so as to transmit the rotational power of the crankshaft 10 to the connecting rod and piston in the compressor 1000, so that the connecting rod and piston can reciprocate to realize the compression work of the compressor 1000. The rotor core 22 can be formed by axially stacking multiple rotor laminations to enhance the structural strength and rigidity. The rotor laminations can have one or more permanent magnet slots 22c. The permanent magnet slots 22c are used to accommodate permanent magnets 24, so that one or more permanent magnets 24 are set on the rotor core 22. The rotor assembly 20 has multiple magnetic poles, with multiple permanent magnets 24 arranged under each magnetic pole to ensure uniform magnetic field distribution and good magnetic flux.

[0045] It should be noted that the ratio between the length L1 of the multiple permanent magnets 24 arranged under each magnetic pole in the direction perpendicular to the magnetization direction and the diameter D of the main shaft section 12 of the crankshaft 10 must satisfy 1.9 ≤ L1 / D ≤ 2.1. If the ratio of the length of the multiple permanent magnets 24 in the direction perpendicular to the magnetization direction to the diameter of the main shaft section 12 is too large, the permanent magnets 24 will be too long and the diameter of the main shaft section 12 will be too small, resulting in an increase in the weight of the rotor assembly 20 and an excessively thin crankshaft 10. This reduces the overall rigidity of the rotor assembly 20 and the crankshaft 10, and makes the crankshaft 10 prone to wobbling during rotation, leading to increased energy consumption to drive the crankshaft 10 and reduced energy efficiency of the compressor 1000. For example, as... Figure 5 When L1 / D takes values ​​of 2.2, 2.4, or 2.5, the coefficient of performance (COP) of the compressor 1000 is relatively small, resulting in low energy efficiency and high operating costs. Conversely, when the ratio of the length of the multiple permanent magnets 24 perpendicular to the magnetization direction to the diameter of the main shaft section 12 is too small, the permanent magnets 24 become too short, weakening the magnetic field strength and affecting the compressor 1000's energy efficiency. Simultaneously, it results in an excessively large diameter of the main shaft section 12, increasing material costs and requiring more space within the rotor assembly 20. This reduces the available space for the permanent magnets 24 and for liquid flow, ultimately worsening the performance and flow capacity of the rotor assembly 20. For example, as... Figure 5When L1 / D is 1.5, 1.6, or 1.8, the COP of compressor 1000 is relatively small, resulting in low energy efficiency and high operating costs. In this embodiment, the ratio of the length of multiple permanent magnets 24 perpendicular to the magnetization direction to the diameter of the main shaft section 12 is set in the range of 1.9 to 2.1. This ensures a suitable ratio, allowing for optimization of the magnetic field layout and flux while maintaining the overall rigidity of the rotor assembly 20 and crankshaft 10, thereby improving the rigidity and optimizing the energy efficiency of compressor 1000. For example, as... Figure 5 When L1 / D takes values ​​of 1.9, 2, or 2.1, the COP value of compressor 1000 is relatively large, indicating that compressor 1000 has high energy utilization efficiency.

[0046] According to the compressor 1000 of this application, by optimizing the dimensional ratio between the permanent magnet 24 in the rotor assembly 20 and the main shaft section 12 in the crankshaft 10, the overall rigidity of the compressor 1000 can be enhanced, the vibration and noise reduction performance of the compressor 1000 can be improved, the stability and reliability of the compressor 1000 can be increased, the working efficiency of the compressor 1000 can be improved, and energy consumption can be saved, thus achieving a good balance between energy efficiency and cost.

[0047] In addition, in some specific embodiments of this application, the compressor 1000 also includes a stator assembly 30, which is sleeved on the outer periphery of the rotor assembly 20. The stator assembly 30 is provided with a winding 40. The stator assembly 30, the winding 40, the rotor assembly 20 and the others work together to realize the conversion of electrical energy into mechanical energy in the compressor 1000, thereby driving the load to rotate.

[0048] like Figure 2 and Figure 3 As shown, according to some embodiments of this application, the number of permanent magnets 24 under each magnetic pole is an odd number. The permanent magnet 24 includes an intermediate magnet and a plurality of lateral magnets symmetrically arranged relative to the intermediate magnet. The intermediate magnet and the lateral magnets surround the magnetic pole, and the sum of the lengths of the intermediate magnet and the lateral magnets perpendicular to the magnetization direction is L1.

[0049] Specifically, the number of permanent magnets 24 under each magnetic pole is an odd number, such as three or five. The odd number of permanent magnets 24 includes an intermediate magnet and lateral magnets surrounding the magnetic pole. The lateral magnets are constructed as multiple magnets symmetrically arranged about the intermediate magnet. This can be understood as the lateral magnets located on one side of the intermediate magnet and the lateral magnets located on the other side of the intermediate magnet being symmetrically arranged. The sum of the lengths of the intermediate magnet and the lateral magnets in the direction perpendicular to the magnetization direction is L1. In this embodiment, an odd number of permanent magnets 24 are used, and the lateral magnets are symmetrically arranged on both sides of the intermediate magnet to optimize the layout of the permanent magnets 24. This can reduce the non-uniform area in the magnetic field and ensure good magnetic flux, thereby improving the uniformity of the magnetic field distribution, reducing eddy current loss and magnetic reluctance loss, and thus effectively improving the operating efficiency and stability of the compressor 1000. Furthermore, the ratio of the sum of the lengths L1 of the intermediate magnet and the lateral magnet in the direction perpendicular to the magnetization direction to the diameter D of the crankshaft 10 main shaft section 12 is limited to the range of 1.9 to 2.1, which also ensures that the intermediate magnet and the lateral magnet have appropriate lengths in the direction perpendicular to the magnetization direction, so as to optimize the length of the permanent magnet 24, which can further make the electromagnetic force distribution more uniform, thereby reducing noise and vibration levels and improving the overall performance of the compressor 1000.

[0050] like Figure 3 As shown, according to some embodiments of this application, there are three permanent magnets 24 under each magnetic pole, the three permanent magnets 24 surround the magnetic pole, and the lengths of the three permanent magnets 24 perpendicular to the magnetization direction are A1, A2, and A3, respectively, and A1+A2+A3=L1.

[0051] Specifically, the three permanent magnets 24 can be respectively constructed as a first permanent magnet 242, a second permanent magnet 244 disposed on one side of the first permanent magnet 242, and a third permanent magnet 246 disposed on the other side of the first permanent magnet 242. The length of the first permanent magnet 242 perpendicular to the magnetization direction is A1, the length of the second permanent magnet 244 perpendicular to the magnetization direction is A2, and the length of the third permanent magnet 246 perpendicular to the magnetization direction is A3, where A1 + A2 + A3 = L1. By constructing three permanent magnets 24 under each magnetic pole, the number and length of the permanent magnets 24 under each magnetic pole are appropriate. This ensures that the permanent magnets 24 form a uniform and stable magnetic field around the magnetic pole, which can improve the operating stability of the rotor assembly 20 and save energy. At the same time, it can avoid the possibility of excessive magnetic flux density concentration in local areas due to an excessive number of permanent magnets 24, which would cause uneven magnetic flux density distribution and affect the operating efficiency of the compressor 1000. Furthermore, an excessive number of permanent magnets 24 means that more materials and more complex processing are required, which will increase manufacturing costs. In this embodiment, the number of permanent magnets 24 is set to three, which is also conducive to controlling manufacturing costs.

[0052] It should be noted that the sizes of A1, A2, and A3 mentioned above can be the same or different. That is, the lengths of the first permanent magnet 242, the second permanent magnet 244, and the third permanent magnet 246 perpendicular to the magnetization direction can be equal or unequal. This embodiment does not impose any limitation on this. Allowing the first permanent magnet 242, the second permanent magnet 244, and the third permanent magnet 246 to have different lengths allows for more arrangement possibilities of the permanent magnets 24, providing more flexibility in the design of the compressor 1000. The length of the permanent magnets 24 can be adjusted according to different needs to optimize the performance parameters of the rotor assembly 20 and the crankshaft 10, such as torque, power factor, and efficiency. When the lengths of the first permanent magnet 242, the second permanent magnet 244, and the third permanent magnet 246 are not equal in the direction perpendicular to the magnetization direction, although the length of each permanent magnet 24 is different, their sum (L1) is determined. The ratio of their sum L1 to the diameter D of the main shaft section 12 is always kept within a suitable range. Therefore, even when the lengths of different permanent magnets 24 are not equal in the direction perpendicular to the magnetization direction, sufficient magnetic field strength and magnetic field uniformity of the rotor assembly 20 can still be guaranteed.

[0053] like Figure 2 and Figure 3 As shown, according to some embodiments of this application, the rotor core 22 has a flow passage 22a with an area of ​​S and a radius of R1, satisfying 0.95 ≤ 100*S / (π*R1). 2 ) / D≤1.3.

[0054] Specifically, multiple flow holes 22a can be formed on the rotor core 22, the total area of ​​the multiple flow holes 22a is S, and the area S of the flow holes 22a, the radius R1 of the rotor core 22, and the diameter D of the main shaft section 12 satisfy 0.95≤100*S / (π*R1) 2 ) / D≤1.3. When the area S of the flow passage 22a on the rotor core 22 is too small, it will weaken the flow capacity of the flow passage 22a, resulting in poor heat dissipation of the compressor 1000 and reducing its long-term stability and reliability. When the area S of the flow passage 22a on the rotor core 22 is too large, it means that the material of the rotor core 22 is reduced, which will reduce the structural strength of the rotor core 22, increase the risk of deformation of the rotor core 22 under high-speed rotation and load, and increase the vibration and noise of the rotor core 22, which will affect the stability, reliability and life of the compressor 1000.

[0055] In this embodiment, the proportional relationship between the area S of the flow hole 22a, the radius R1 of the rotor core 22, and the diameter D of the main shaft section 12 is set to 0.95≤100*S / (π*R1). 2The ratio S / D ≤ 1.3 ensures that the proportions of the flow orifice 22a, the radius R1 of the rotor core 22, and the diameter D of the main shaft section 12 are appropriate. This guarantees that the area ratio of the flow orifice 22a on the rotor core 22 matches the diameter of the main shaft section 12. Specifically, this compatibility means that if the flow field requirements of the rotor assembly 20 are relatively low, the area ratio of the flow orifice 22a on the rotor core 22 is relatively small. In this case, the weakening of the structural strength of the rotor core 22 by the opening of the flow orifice 22a is relatively small, and the diameter of the main shaft section 12 is also set within a relatively small range, i.e., meeting the condition 0.95 ≤ 100*S / (π*R1). 2 Within the range of 0.95 / D ≤ 1.3, the rotor core 22 can still have good rigidity and strength performance. If the flow field requirements of the rotor assembly 20 are relatively high, the area ratio of the flow holes 22a on the rotor core 22 is relatively large. In this case, the opening of the flow holes 22a will significantly weaken the structural strength of the rotor core 22. Therefore, the diameter of the main shaft section 12 should be set within a relatively large range, i.e., it should meet the condition 0.95 ≤ 100*S / (π*R1). 2 Within the range of ) / D≤1.3, the main shaft section 12 with a relatively large diameter, after being connected to the rotor core 22, can play a certain role in enhancing the structural stiffness and strength of the rotor core 22. Thus, the main shaft section 12's enhancement effect on the rotor core 22 at least partially compensates for the weakening of the rotor core 22's structural strength to meet sufficient flow area. Therefore, it can also ensure the stiffness of the rotor core 22, thereby achieving a good balance between stiffness and flow performance in optimizing the rotor assembly 20.

[0056] like Figure 2 and Figure 3 As shown, according to some embodiments of this application, the rotor core 22 has a shaft hole 22b, and the main shaft section 12 is connected to the rotor core 22 within the shaft hole 22b.

[0057] Specifically, the rotor core 22 may have an axially extending shaft hole 22b. The main shaft section 12 of the crankshaft 10 can be connected to the rotor core 22 within the shaft hole 22b. Through the connection between the main shaft section 12 and the rotor core 22, during the operation of the compressor 1000, the rotation of the rotor core 22 can smoothly drive the crankshaft 10 to rotate, thereby realizing the overall operation of the compressor 1000. The direct connection between the main shaft section 12 and the rotor core 22 helps to improve the operating efficiency of the compressor 1000 and helps to reduce noise and vibration caused by loose or unstable connections. Furthermore,

[0058] The main shaft section 12 and the shaft hole 22b can be configured as an interference fit connection. This connection method can ensure a tight fit and stable connection between the main shaft section 12 and the rotor core 22, enhance the connection strength between the crankshaft 10 and the rotor core 22, and thus enhance the overall structural rigidity, working stability and reliability of the compressor 1000.

[0059] like Figure 3 As shown, according to some embodiments of this application, the inner diameter of the shaft hole 22b is R2, and satisfies 0.15≤R2 / R1≤0.45.

[0060] Specifically, when the ratio of the inner diameter of the shaft hole 22b to the radius of the rotor core 22 is too small, for example, R2 / R1 is 0.13, 0.11, or 0.1, the material cost and weight of the rotor core 22 will increase. An excessively heavy rotor core 22 will increase swaying during rotation, leading to increased vibration and noise. When the ratio of the inner diameter of the shaft hole 22b to the radius of the rotor core 22 is too large, for example, R2 / R1 is 0.5, 0.54, or 0.6, the shaft hole 22b is relatively large. Firstly, this will reduce the structural strength of the rotor core 22, making it prone to deformation and damage. Secondly, the relatively large shaft hole 22b will limit the space available for the arrangement of permanent magnets 24 and flow holes 22a in the rotor core 22. The reduced space will affect the efficiency and flow performance of the rotor assembly 20; thirdly, the relatively large shaft hole 22b also requires a corresponding increase in the diameter of the main shaft section 12 that mates with the shaft hole 22b, thereby increasing material and manufacturing costs; in this embodiment, by setting the ratio of the inner diameter R2 of the shaft hole 22b of the rotor core 22 to the radius R1 of the rotor core 22 in the range of 0.15 to 0.45, for example, the value of R2 / R1 can be 0.15, 0.2, 0.3 or 0.45, etc., so that the inner diameter of the shaft hole 22b and the radius of the rotor core 22 have a reasonable ratio range, which is conducive to ensuring that the rotor core 22 has good rigidity, flow performance and working performance, and also helps to save the production cost of the compressor 1000.

[0061] like Figure 3 and Figure 4 As shown, according to some embodiments of this application, the weight of the rotor assembly 20 is W1, the weight of the crankshaft 10 is W2, and the condition 7.5≤W1 / W2≤8 is met.

[0062] Specifically, the ratio of the weight W1 of the rotor assembly 20 to the weight W2 of the crankshaft 10 can be set in the range of 7.5 to 8. For example, the value of W1 / W2 can be 7.5, 7.6, 7.8 or 8, etc. By setting the ratio of the weight of the rotor assembly 20 to the weight of the crankshaft 10 in the above range, the weight distribution of the rotor assembly 20 and the crankshaft 10 can be optimized. Within this weight ratio range, the stability of the rotor assembly 20 during rotation can be increased, and the deformation caused by centrifugal force and inertial force can be reduced, thereby improving the overall rigidity of the compressor 1000. At the same time, a reasonable weight ratio between the rotor assembly 20 and the crankshaft 10 can maintain the dynamic balance of the system, reduce the vibration caused by uneven weight distribution, and thus improve the vibration reduction and noise reduction performance and energy efficiency of the compressor 1000. Furthermore, setting the weight ratio of the rotor assembly 20 to the crankshaft 10 within the aforementioned range ensures that the rotor assembly 20 maintains a stable trajectory during high-speed rotation, reducing swaying caused by weight imbalance. This helps extend the service life of the compressor 1000 and further reduces noise and vibration during compressor 1000 operation.

[0063] like Figure 4 As shown, according to some embodiments of this application, 10mm ≤ D ≤ 12.5mm.

[0064] Specifically, if the diameter of the crankshaft 10 main shaft section 12 is too small, for example, a diameter of 9mm, 8mm, or 7mm, the crankshaft 10 will have insufficient rigidity, easily increasing vibration and noise. If the diameter of the crankshaft 10 main shaft section 12 is too large, for example, a diameter of 13mm, 14mm, or 15mm, it will increase material consumption and manufacturing costs, and will also make the overall size of the compressor 1000 too large, which is not conducive to compact design. In this embodiment, the diameter of the crankshaft 10 main shaft section 12 is set at 1mm. Within the range of 0mm to 12.5mm, for example, the diameter of the main shaft section 12 can be constructed as 10mm, 11mm, 12mm or 12.5mm, which helps to ensure the bending and torsional stiffness of the crankshaft 10, reduce the deformation of the crankshaft 10 caused by centrifugal force, gas pressure and other factors during high-speed operation, thereby maintaining a good fit between the rotor assembly 20 and components such as the cylinder 50 of the compressor 1000, effectively reducing vibration and noise, while also saving materials and manufacturing costs, and facilitating the optimization of the overall volume of the compressor 1000.

[0065] Furthermore, in some specific embodiments of this application, the crankshaft 10 is made of steel. Steel has advantages such as high strength, good wear resistance, and good fatigue resistance. The use of steel in the crankshaft 10 helps it withstand the enormous pressure and torque generated during the operation of the compressor 1000, and also helps to effectively resist performance degradation caused by vibration and wear, thereby helping to improve the operational stability and service life of the compressor 1000.

[0066] like Figures 1-4 As shown, according to some embodiments of this application, the axial dimension of the rotor core 22 is L2, and satisfies 3≤L2 / D≤5.

[0067] Specifically, the axial dimension of the rotor core 22 is L2, which can be understood as the thickness of the rotor core 22 being L2. The axial dimension L2 of the rotor core 22 and the diameter D of the crankshaft 10 main shaft section 12 satisfy 3≤L2 / D≤5. When the ratio of the axial dimension of the rotor core 22 to the diameter of the crankshaft 10 main shaft section 12 is too large, for example, L2 / D is 5.5, 6, or 6.5, it will cause the end of the rotor core 22 that is axially away from the crankshaft 10 to be too long, and increase the overall weight of the rotor core 22. This will easily aggravate its sway amplitude during high-speed rotation, increase the vibration and noise of the compressor 1000, and affect the smooth operation and durability of the compressor 1000. Furthermore, excessive vibration may also adversely affect other components of the compressor 1000 (such as cylinder 50), shortening the service life of the entire compressor 1000. If the ratio of the axial dimension of the core 22 to the diameter of the crankshaft 10 main shaft section 12 is too small, for example, L2 / D is 2.5, 2 or 1, the axial dimension of the rotor core 22 will be too small, which will sacrifice the rigidity and performance of the rotor core 22, and thus affect the energy efficiency and performance of the compressor 1000. Therefore, in this embodiment, the ratio of L2 / D is set in the range of 3 to 5, so as to ensure that the rotor core 22 has sufficient rigidity while avoiding the problems of excessive weight and increased vibration, thereby improving the overall performance and efficiency of the compressor 1000, and facilitating the stable operation and extended life of the compressor 1000 under various working conditions.

[0068] like Figure 6 As shown, in some specific embodiments, the compressor 1000 according to the present application embodiment improves energy efficiency by 1.31%, 0.96%, and 0.94% respectively compared with the compressor in the related art under SEER30, SEER60, and SEER90 operating conditions, that is, at speeds of 30 rpm, 60 rpm, and 90 rpm. The compressor 1000 according to the present application embodiment has better energy efficiency performance under different operating conditions than the compressor used in the related art.

[0069] Furthermore, in some specific embodiments of this application, the compressor 1000 also includes a bearing 60 and a liquid receiver 70. The bearing 60 is fitted onto the crankshaft 10, suitable for supporting the crankshaft 10 and reducing friction and wear during rotation, thus contributing to improved operational smoothness and extended service life. The liquid receiver 70 serves to store, separate gas and liquid, filter, silence, and buffer refrigerant within the compressor 1000, ensuring the normal operation of the compressor 1000.

[0070] like Figures 1-5 As shown, the refrigeration device according to the second aspect of this application includes: the compressor 1000 as described in any of the above embodiments, and the resulting technical effects are the same as those in the above embodiments, and will not be repeated here.

[0071] 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 this application. 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.

[0072] Although embodiments of this application 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 this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, include: Crankshaft, the crankshaft having a main shaft section; A rotor assembly, comprising: a rotor core and permanent magnets disposed on the rotor core, the rotor core being connected to the main shaft section, the rotor assembly having multiple magnetic poles, and multiple permanent magnets disposed under each magnetic pole, the sum of the lengths of the multiple permanent magnets perpendicular to the magnetization direction being L1, the diameter of the main shaft section being D, and satisfying 1.9≤L1 / D≤2.

1.

2. The compressor according to claim 1, characterized in that, The number of permanent magnets under each magnetic pole is odd. Each permanent magnet includes an intermediate magnet and a plurality of lateral magnets symmetrically arranged relative to the intermediate magnet. The intermediate magnet and the lateral magnets surround the magnetic pole, and the sum of the lengths of the intermediate magnet and the lateral magnets in the direction perpendicular to the magnetization direction is L1.

3. The compressor according to claim 2, characterized in that, The number of permanent magnets under each magnetic pole is three. The three permanent magnets surround the magnetic pole, and the lengths of the three permanent magnets perpendicular to the magnetization direction are A1, A2, and A3, respectively, and A1+A2+A3=L1.

4. The compressor according to any one of claims 1-3, characterized in that, The rotor core has a flow passage with an area of ​​S and a radius of R1, satisfying 0.95 ≤ 100 * S / (π * R1) 2 ) / D≤1.

3.

5. The compressor according to claim 4, characterized in that, The rotor core has a shaft hole, and the main shaft section is connected to the rotor core within the shaft hole.

6. The compressor according to claim 5, characterized in that, The inner diameter of the shaft hole is R2, and satisfies 0.15≤R2 / R1≤0.

45.

7. The compressor according to any one of claims 1-3, characterized in that, The weight of the rotor assembly is W1, the weight of the crankshaft is W2, and the condition 7.5≤W1 / W2≤8 is met.

8. The compressor according to any one of claims 1-3, characterized in that, 10mm≤D≤12.5mm.

9. The compressor according to any one of claims 1-3, characterized in that, The axial dimension of the rotor core is L2, and it satisfies 3≤L2 / D≤5.

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

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