Compressor and refrigeration equipment

Abstract

The utility model 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 technical field of compressors, and more particularly to a compressor and a refrigeration device. Background Art

[0002] As the core power component in household appliances such as refrigeration devices like air conditioners and refrigerators, the performance and efficiency of the compressor directly determine the energy efficiency performance and user experience of the entire household appliance product. With the progress of technology and the improvement of people's living standards, the energy efficiency issue of household appliances has attracted extensive attention from all sectors of society. In particular, in recent years, the release of the new first-level energy efficiency standard in the country and the continuous promotion of energy conservation and emission reduction policies have put forward higher requirements for the energy efficiency of compressors. In related technologies, in order to improve energy efficiency, compressors often adopt methods such as increasing the refrigerant dosage, optimizing the system cycle, and improving the heat exchange efficiency. However, while these methods improve energy efficiency, they are often accompanied by a significant increase in cost or a decrease in reliability, making it difficult to gain an advantage in the market competition. Therefore, how to improve the energy efficiency of compressors while keeping the cost controllable and ensuring reliability has become an important direction in the current development of compressor technology. Summary of the Utility Model

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

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

[0005] The compressor according to the first aspect embodiment of this application includes: a crankshaft and a rotor assembly. The crankshaft has a main shaft section. The rotor assembly includes: a rotor core and permanent magnets provided on the rotor core. The rotor core is connected to the main shaft section. The rotor assembly has a plurality of magnetic poles, and a plurality of the permanent magnets are provided under each magnetic pole. The sum of the lengths of the plurality of permanent magnets in the direction perpendicular to the magnetization direction is L1, and the diameter of the main shaft section is D, and 1.9 ≤ L1 / D ≤ 2.1 is satisfied.

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

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

[0008] Further, the number of permanent magnets under each of the magnetic poles is three. The three permanent magnets surround the magnetic pole, and the lengths of the three permanent magnets in the direction 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 current-carrying hole with an area of S, and the radius of the rotor core is R1, and 0.95 ≤ 100*S / (π*R1 2 ) / D ≤ 1.3.

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

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

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

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

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

[0015] The refrigeration device according to the embodiments of the second aspect of the present application includes a compressor as described in any one of the above embodiments.

[0016] The additional aspects and advantages of the present application will be partially given in the following description, partially become apparent from the following description, or be understood through the practice of the present application. Description of the Drawings

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

[0018] Figure 1 is a schematic structural diagram of a compressor according to an embodiment of the present application;

[0019] Figure 2It is a schematic diagram of the cooperation between the rotor assembly and the stator assembly according to an embodiment of the present application;

[0020] Figure 3 It is a schematic diagram of the rotor assembly according to an embodiment of the present application;

[0021] Figure 4 It is a cross-sectional view of the crankshaft according to an embodiment of the present application;

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

[0023] Figure 6 It is a comparison diagram of the compressor COP between the compressor according to an embodiment of the present application and the compressor in the related art.

[0024] Reference numerals:

[0025] 1000, compressor;

[0026] 10, crankshaft; 12, main shaft section; 14, eccentric section; 16, auxiliary shaft section;

[0027] 20, rotor assembly;

[0028] 22, rotor core; 22a, current-carrying 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 accumulator. Detailed implementation manners

[0031] To make the objectives, technical solutions, and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly described below with reference to the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are some, but not all, of the embodiments of the present application. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present application without creative efforts shall fall within the protection scope of the present 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 technical field to which this application pertains; the terms used in the description of this application in the specification are only for the purpose of describing specific embodiments and are not intended to limit this application; the terms "including" and "having" and any variations thereof in the description and claims of this application and the above drawings are intended to cover non-exclusive inclusion. The terms "first", "second", etc. in the description and claims of this application or the above drawings are used to distinguish different objects and not to describe a specific order or primary-secondary relationship.

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

[0034] In the description of this application, it should be noted that unless otherwise clearly specified and limited, the terms "installed", "connected", "coupled", and "attached" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0035] The term "and / or" in this application is merely a description of the association relationship of associated objects, indicating that there can be three relationships. For example, A and / or B can represent: A exists alone, A and B exist simultaneously, and B exists alone. In addition, the character " / " in this application generally represents an "or" relationship between the associated objects before and after.

[0036] In the embodiments of this application, the same reference numerals represent the same components, and for the sake of brevity, the detailed description of the same components is omitted in different embodiments. It should be understood that the thickness, length, width, etc. of various components shown in the drawings of the embodiments of this application, as well as the overall thickness, length, width, etc. of the integrated device are only for illustrative purposes and should not constitute any limitation to this application.

[0037] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present application.

[0038] In the description of the present application, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or may include the first and second features not being in direct contact but being in contact through additional features therebetween.

[0039] In the description of the present application, the first feature being "above", "over" and "on top of" the second feature includes the first feature being directly above and obliquely above the second feature, or merely indicating that the first feature has a higher horizontal height than the second feature.

[0040] The term "plurality" as used in the present application refers to two or more (including two).

[0041] Reference is made below to Figures 1 - 6 Describe the compressor 1000 and the refrigeration equipment according to the embodiments of the present application.

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

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

[0044] Specifically, the crankshaft 10 may include a main shaft section 12, an eccentric section 14, and a secondary shaft section 16 arranged axially in sequence. Among them, 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 operates, 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 to complete power transmission, so as to transmit the rotational power of the crankshaft 10 to the connecting rod and piston in the compressor 1000, etc., enabling the connecting rod and piston to perform reciprocating motions to achieve the compression work of the compressor 1000. The rotor core 22 can be axially laminated by multiple rotor punching sheets to enhance the structural strength and stiffness. One or more permanent magnet slots 22c can be provided on the rotor punching sheet, and the permanent magnet slots 22c are used to accommodate the permanent magnets 24 to achieve the setting of one or more permanent magnets 24 on the rotor core 22. The number of magnetic poles of the rotor assembly 20 is configured as multiple, and multiple permanent magnets 24 are arranged under each magnetic pole to ensure uniform magnetic field distribution and good magnetic flux.

[0045] It should be noted that the proportional relationship between the sum of the lengths 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 needs to satisfy 1.9 ≤ L1 / D ≤ 2.1. When the ratio of the sum of the lengths 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, it will cause the length of the permanent magnet 24 to be too long and the diameter of the main shaft section 12 to be too small, resulting in an increase in the weight of the rotor assembly 20 and the crankshaft 10 being too thin, thereby reducing the overall rigidity of the rotor assembly 20 and the crankshaft 10, and causing the crankshaft 10 to be prone to shaking during rotation, resulting in an increase in the energy consumed to drive the rotation of the crankshaft 10 and a reduction in the energy efficiency of the compressor 1000. Exemplarily, when Figure 5 the value of L1 / D is 2.2, 2.4, or 2.5, etc., the coefficient of performance (COP) value of the compressor 1000 is relatively small, the energy utilization efficiency of the compressor 1000 is low, and the operating cost is high. When the ratio of the sum of the lengths 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 small, it will cause the length of the permanent magnet 24 to be too short, resulting in a weakening of the magnetic field strength, affecting the energy efficiency of the compressor 1000. At the same time, it also makes the diameter of the main shaft section 12 too large, resulting in an increase in material costs, and the main shaft section 12 needs to occupy more space when connected to the rotor assembly 20, thereby reducing the available space for setting the permanent magnets 24 and for liquid circulation, and further deteriorating the performance of the rotor assembly 20 and the flow field circulation ability. Exemplarily, when Figure 5When the value of L1 / D is 1.5, 1.6, 1.8, etc., the COP value of the compressor 1000 is relatively small, so the energy utilization efficiency of the compressor 1000 is low and the operating cost is high. In the embodiments of the present application, the ratio of the sum of the lengths of the plurality of permanent magnets 24 in the direction perpendicular to the magnetization direction to the diameter of the main shaft section 12 is set within the range of 1.9 to 2.1, so that the ratio of the sum of the lengths of the plurality of permanent magnets 24 in the direction perpendicular to the magnetization direction to the diameter of the main shaft section 12 is appropriate, which can optimize the magnetic field layout and magnetic flux while ensuring the overall stiffness of the rotor assembly 20 and the crankshaft 10, and further improve the rigidity and energy efficiency of the compressor 1000. Exemplarily, such as Figure 5 When the value of L1 / D is 1.9, 2, 2.1, etc., the COP value of the compressor 1000 is relatively large, so the energy utilization efficiency of the compressor 1000 is high.

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

[0047] In addition, in some specific embodiments of the present application, the compressor 1000 further includes a stator assembly 30. The stator assembly 30 is sleeved on the outer periphery of the rotor assembly 20. A winding 40 is provided on the stator assembly 30. The stator assembly 30, the winding 40, the rotor assembly 20, etc. cooperate to realize the conversion of electrical energy into mechanical energy in the compressor 1000, so as to drive the load to rotate.

[0048] Such as Figure 2 and Figure 3 As shown, according to some embodiments of the present 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 enclose 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.

[0049] Specifically, the number of permanent magnets 24 under each magnetic pole is configured as an odd number, such as three or five, etc. The odd number of permanent magnets 24 includes a middle magnet and lateral magnets surrounding the magnetic pole. The lateral magnets are configured as multiple magnets symmetrically arranged with respect to the middle magnet. It can be understood that the lateral magnets located on one side of the middle magnet and the lateral magnets located on the other side of the middle magnet are symmetrically arranged. Among them, the sum of the lengths of the middle magnet and the lateral magnets in the direction perpendicular to the magnetization direction is L1. In the embodiments of the present application, an odd number of permanent magnets 24 are used, and the lateral magnets are symmetrically arranged on both sides of the middle magnet to optimize the layout of the permanent magnets 24, which can reduce the uneven regions in the magnetic field and ensure good magnetic flux, thereby improving the uniformity of the magnetic field distribution, reducing eddy current loss and magnetic resistance loss, and further effectively improving the operating efficiency and stability of the compressor 1000. Moreover, the ratio of the sum of the lengths L1 of the middle magnet and the lateral magnets in the direction perpendicular to the magnetization direction to the diameter D of the main shaft section 12 of the crankshaft 10 is limited within the range of 1.9 to 2.1, which also ensures that the middle magnet and the lateral magnets have appropriate lengths in the direction perpendicular to the magnetization direction to optimize the length of the permanent magnets 24, and can further make the electromagnetic force distribution more uniform, thereby reducing the noise and vibration levels and improving the overall performance of the compressor 1000.

[0050] As Figure 3 shown, according to some embodiments of the present application, the number of permanent magnets 24 under each of the magnetic poles is three. The three permanent magnets 24 surround the magnetic pole, and the lengths of the three permanent magnets 24 in the direction 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 configured 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 in the direction perpendicular to the magnetization direction is A1, the length of the second permanent magnet 244 in the direction perpendicular to the magnetization direction is A2, and the length of the third permanent magnet 246 in the direction perpendicular to the magnetization direction is A3, and A1 + A2 + A3 = L1. By configuring the number of permanent magnets 24 under each magnetic pole to be three, the number and length of the permanent magnets 24 under each magnetic pole are appropriate. In this way, it can be ensured 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 consumption. At the same time, it can avoid the excessive concentration of the magnetic flux density in local areas caused by too many permanent magnets 24, thus resulting in uneven distribution of the magnetic flux density and affecting the operating efficiency of the compressor 1000. Moreover, too many permanent magnets 24 means more materials and more complex processing processes, which will increase the manufacturing cost. In the embodiments of the present application, setting the number of permanent magnets 24 to three is also beneficial to controlling the manufacturing cost.

[0052] It should be noted that the sizes of the above A1, A2, and A3 may 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 in the direction perpendicular to the magnetization direction may be equal or unequal, and this is not limited in this embodiment. Allowing the lengths of the first permanent magnet 242, the second permanent magnet 244, and the third permanent magnet 246 to be different can make the permanent magnet 24 have more permutation possibilities, providing more flexibility for the design of the compressor 1000. The length of the permanent magnet 24 can be adjusted correspondingly according to different requirements to optimize the performance parameters of the rotor assembly 20, the crankshaft 10, etc., such as torque, power factor, efficiency, etc. When the lengths of the first permanent magnet 242, the second permanent magnet 244, and the third permanent magnet 246 in the direction perpendicular to the magnetization direction are unequal, although the lengths of each permanent magnet 24 are different, their sum (L1) is determined, and the ratio of their sum L1 to the diameter D of the main shaft section 12 always remains within a suitable range. Therefore, when the lengths of different permanent magnets 24 in the direction perpendicular to the magnetization direction are unequal, sufficient magnetic field strength and magnetic field uniformity of the rotor assembly 20 can also be ensured.

[0053] Such as Figure 2 and Figure 3 shown, according to some embodiments of the present application, the rotor core 22 has a current-carrying hole 22a, the area of the current-carrying hole 22a is S, the radius of the rotor core 22 is R1, and it satisfies 0.95 ≤ 100 * S / (π * R1 2 ) / D ≤ 1.3.

[0054] Specifically, a plurality of current-carrying holes 22a may be formed on the rotor core 22, the total area of the plurality of current-carrying holes 22a is S, and the area S of the current-carrying hole 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 current-carrying hole 22a on the rotor core 22 is too small, the current-carrying capacity of the current-carrying hole 22a will be weakened, resulting in a poor heat dissipation effect of the compressor 1000 and reducing its long-term operation stability and reliability; when the area S of the current-carrying hole 22a on the rotor core 22 is too large, it means a reduction in the material of the rotor core 22, 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 the embodiments of the present application, the proportional relationship range among the area S of the current-carrying 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 2) / D ≤ 1.3, such that the ratio among the area S of the flow-through hole 22a, the radius R1 of the rotor core 22, and the diameter D of the main shaft section 12 is appropriate, so as to ensure that the area ratio of the flow-through hole 22a on the rotor core 22 matches the size of the diameter of the main shaft section 12. The specific adaptability can be manifested as follows: if the flow field circulation requirement of the rotor assembly 20 is relatively low, the corresponding area ratio of the flow-through hole 22a on the rotor core 22 is relatively small. In this case, the opening of the flow-through hole 22a weakens the structural strength of the rotor core 22 relatively little, and then the diameter of the main shaft section 12 is also set within a relatively small range, that is, it conforms to 0.95 ≤ 100*S / (π*R1 2 ) / D ≤ 1.3, and it can also meet the requirements of the rotor core 22 having good stiffness and strength performance; if the flow field circulation requirement of the rotor assembly 20 is relatively high, the corresponding area ratio of the flow-through hole 22a on the rotor core 22 is relatively large. In this case, the opening of the flow-through hole 22a weakens the structural strength of the rotor core 22 relatively greatly, and then the diameter of the main shaft section 12 is set within a relatively large range, that is, it conforms to 0.95 ≤ 100*S / (π*R1 2 ) / D ≤ 1.3. After the main shaft section 12 with a relatively large diameter is connected to the rotor core 22, it can play a certain role in enhancing the structural stiffness and strength of the rotor core 22. Thus, at least part of the enhancing effect of the main shaft section 12 on the rotor core 22 compensates for the structural strength of the rotor core 22 weakened to meet the sufficient flow-through area. Therefore, the stiffness of the rotor core 22 can also be ensured, and then a good balance between the stiffness and the flow-through performance of the optimized rotor assembly 20 is achieved.

[0056] As Figure 2 and Figure 3 shown, according to some embodiments of the present 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 a shaft hole 22b extending axially, and the main shaft section 12 of the crankshaft 10 may 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 rotor core 22 rotates, which can smoothly drive the crankshaft 10 to rotate, and then realize 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 operation efficiency of the compressor 1000 and helps to reduce the noise and vibration generated due to loose or unstable connection. In addition,

[0058] the connection between the main shaft section 12 and the shaft hole 22b can be configured as an interference fit connection. This connection method can ensure the close 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 then can enhance the overall structural rigidity, working stability, and reliability of the compressor 1000.

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

[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, the value of R2 / R1 is 0.13, 0.11 or 0.1, etc., it will cause an increase in the material cost and weight of the rotor core 22, and the overweight of the rotor core 22 is likely to increase the shaking during rotation, resulting in an increase in 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, the value of R2 / R1 is 0.5, 0.54 or 0.6, etc., the shaft hole 22b is relatively large. On the one hand, it will cause a reduction in the structural strength of the rotor core 22, resulting in easy deformation and damage of the rotor core 22. On the other hand, the relatively large shaft hole 22b leads to a reduction in the space available for arranging the permanent magnet 24 and the through-flow hole 22a in the rotor core 22, which will affect the efficiency and through-flow performance of the rotor assembly 20; on the third hand, the relatively large shaft hole 22b also makes the diameter of the main shaft section 12 that cooperates with the shaft hole 22b need to be increased accordingly, thereby bringing an increase in material and manufacturing costs; in the embodiments of the present application, 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 within 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., it makes the inner diameter of the shaft hole 22b and the radius of the rotor core 22 have a reasonable ratio range, which is beneficial to ensuring that the rotor core 22 has good stiffness, through-flow performance and working performance, and is conducive to saving the production cost of the compressor 1000.

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

[0062] Specifically, the ratio of the weight W1 of the rotor assembly 20 to the weight W2 of the crankshaft 10 can be set within the range of 7.5 to 8. Exemplarily, 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 within the above range, the weight distribution between 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 with the crankshaft 10 can maintain the dynamic balance of the system, and the vibration caused by uneven weight distribution can be reduced, thereby improving the vibration reduction, noise reduction performance, and energy efficiency of the compressor 1000. In addition, when the weight ratio of the rotor assembly 20 to the crankshaft 10 is set within the above range, it can also ensure that the rotor assembly 20 maintains a stable trajectory during high-speed rotation, and the yaw phenomenon caused by weight imbalance can be reduced. In this way, it helps to extend the service life of the compressor 1000 and further reduce the noise and vibration during the operation of the compressor 1000.

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

[0064] Specifically, when the diameter of the main shaft section 12 of the crankshaft 10 is too small, for example, the diameter structure of the main shaft section 12 is 9 mm, 8 mm, or 7 mm, etc., it will cause insufficient stiffness of the crankshaft 10 and is likely to increase vibration and noise. When the diameter of the main shaft section 12 of the crankshaft 10 is too large, for example, the diameter structure of the main shaft section 12 is 13 mm, 14 mm, or 15 mm, etc., it will increase material consumption and manufacturing costs, and at the same time, it is likely to make the overall size of the compressor 1000 too large, which is not conducive to compact design. In the embodiments of the present application, the diameter of the main shaft section 12 of the crankshaft 10 is set within the range of 10 mm to 12.5 mm. Exemplarily, the diameter of the main shaft section 12 can be structured as 10 mm, 11 mm, 12 mm, or 12.5 mm, etc. This is beneficial to ensuring the bending and torsional stiffness of the crankshaft 10, reducing the deformation of the crankshaft 10 caused by factors such as centrifugal force and gas pressure 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. At the same time, it can also save materials and manufacturing costs and is conducive to optimizing the overall volume of the compressor 1000.

[0065] In addition, in some specific embodiments of the present application, the material of the crankshaft 10 is structured as steel. Steel materials have the advantages of high strength, good wear resistance, and good fatigue resistance. Structuring the material of the crankshaft 10 as steel is beneficial for the crankshaft 10 to withstand the huge pressure and torque generated during the operation of the compressor 1000, and is also conducive to effectively resisting the performance degradation caused by vibration and wear, thereby helping to improve the operation stability and service life of the compressor 1000.

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

[0067] Specifically, the dimension of the rotor core 22 in the axial direction is L2. It can be understood that the thickness of the rotor core 22 is L2. The axial dimension L2 of the rotor core 22 and the diameter D of the main shaft section 12 of the crankshaft 10 satisfy 3 ≤ L2 / D ≤ 5. When the ratio of the axial dimension of the rotor core 22 to the diameter of the main shaft section 12 of the crankshaft 10 is too large, for example, the value of L2 / D is 5.5, 6, or 6.5, etc., it will cause the end of the rotor core 22 axially away from the crankshaft 10 to be too long, and increase the overall weight of the rotor core 22, thereby easily exacerbating the swing amplitude during its high-speed rotation, increasing the vibration and noise of the compressor 1000, and affecting the smooth operation and durability of the compressor 1000. Moreover, excessive vibration may also have an adverse impact on other components of the compressor 1000 (such as the cylinder 50, etc.), shortening the service life of the entire compressor 1000; when the ratio of the axial dimension of the rotor core 22 to the diameter of the main shaft section 12 of the crankshaft 10 is too small, for example, the value of L2 / D is 2.5, 2, or 1, etc., resulting in too small an axial dimension of the rotor core 22, it will sacrifice the stiffness and performance of the rotor core 22, thereby affecting the energy efficiency and performance of the compressor 1000; therefore, in the embodiments of the present application, the ratio of L2 / D is set within the range of 3 to 5 to avoid the problems of excessive weight and increased vibration while ensuring sufficient stiffness of the rotor core 22, 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] As Figure 6 shown, in some specific embodiments, the compressor 1000 according to the embodiments of the present application has improved by 1.31%, 0.96%, and 0.94% respectively compared with the compressor in the related art under the SEER30, SEER60, and SEER90 working conditions, that is, under the working conditions of 30 revolutions per second, 60 revolutions per second, and 90 revolutions per second. The compressor 1000 according to the embodiments of the present application has better energy efficiency performance under different working conditions compared with the compressors used in the related art.

[0069] In addition, in some specific embodiments of the present application, the compressor 1000 further includes: a bearing 60 and a liquid receiver 70. Among them, the bearing 60 is sleeved on the crankshaft 10 and is adapted to support the crankshaft 10 and reduce the friction and wear during its rotation, which helps to improve the running smoothness and extend the service life; the liquid receiver 70 is used to play the roles of storage, gas-liquid separation, filtration, silencing, and refrigerant buffering in the compressor 1000 to ensure the normal operation of the compressor 1000.

[0070] AsFigures 1 - 5 As shown, the refrigeration device according to the second aspect embodiment of the present application includes the compressor 1000 described in any one of the above embodiments, and the technical effects generated are the same as those in the above embodiments, which will not be elaborated here.

[0071] 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 application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

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

Claims

1. A compressor, characterized in that, Comprising: A crankshaft having a main shaft section; A rotor assembly including a rotor core and permanent magnets disposed on the rotor core. The rotor core is connected to the main shaft section. The rotor assembly has a plurality of magnetic poles, and a plurality of the permanent magnets are provided under each magnetic pole. The sum of the lengths of the plurality of permanent magnets in a direction perpendicular to the magnetization direction is L1, the diameter of the main shaft section is D, and 1.9 ≤ L1 / D ≤ 2.1 is satisfied.

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

3. The compressor according to claim 2, characterized in that, The number of the permanent magnets under each magnetic pole is three. The three permanent magnets enclose the magnetic pole, and the lengths of the three permanent magnets in a direction 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 to 3, characterized in that, The rotor core has a current-carrying hole with an area of S, and the radius of the rotor core is R1, and it satisfies 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 0.15 ≤ R2 / R1 ≤ 0.45 is satisfied.

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

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

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

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

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