Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment, the compressor comprises a motor, the motor comprises a rotor, the rotor is provided with an assembly hole penetrating through the rotor along the axial direction of the rotor; the crankshaft is provided with a matching section, the matching section is located in the assembling hole and connected with the rotor, at least one of the inner circumferential wall of the assembling hole and the outer circumferential wall of the matching section is provided with a section difference groove, the section difference groove extends in the circumferential direction of the matching section, in the axial direction of the rotor, the total length of the section difference groove is L, the height of the rotor is H, and when H is larger than 25 mm, L / H is larger than or equal to 0.3 and smaller than or equal to 0.75; when 15 < = H < = 25mm, 0.1 < = L / H < = 0.3 is satisfied. According to the compressor, the assembling reliability of the crankshaft and the rotor is guaranteed, meanwhile, the problem that the crankshaft and the rotor deform due to the fact that the sleeving distance is long in the assembling process is effectively solved, and the energy efficiency and the performance stability are guaranteed.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, and more specifically, to a compressor and a refrigeration device. Background Art

[0002] In the related art, with the development of miniaturization technology of compressors and compressor motors, the volume of the motor rotor is reduced, thereby reducing the structural strength of the rotor. As a result, when the crankshaft and rotor of the compressor are assembled, the relative displacement generated during the assembly process increases the deformation and wear of the crankshaft and the rotor, reduces the matching accuracy, and is prone to loosening and other problems, thereby affecting the working performance and reliability of the compressor, and is prone to noise, vibration and other problems. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, one purpose of the utility model is to provide a compressor that effectively avoids the problem of deformation of the crankshaft and the rotor due to a long sleeve distance during the assembly process while ensuring the reliability of the assembly of the crankshaft and the rotor, thereby ensuring energy efficiency and performance stability.

[0004] Another object of the present invention is to provide a refrigeration device having the above compressor.

[0005] A compressor according to an embodiment of the utility model includes: a motor, the motor includes a rotor, the rotor is provided with an assembly hole that passes through the rotor along the axial direction of the rotor; a crankshaft, the crankshaft has a mating section, the mating section is located in the assembly hole and connected to the rotor, at least one of the inner circumferential wall of the assembly hole and the outer circumferential wall of the mating section is provided with a step groove, the step groove extends along the circumferential direction of the mating section, wherein along the axial direction of the rotor, the total length of the step groove is L, the height of the rotor is H, when H>25mm, it satisfies: 0.3≤L / H≤0.75; when 15≤H≤25mm, it satisfies: 0.1≤L / H≤0.3.

[0006] According to the compressor of the embodiment of the utility model, the mating section of the crankshaft is located in the assembly hole of the rotor and is connected to the rotor. At least one of the inner circumferential wall of the assembly hole and the outer circumferential wall of the mating section is provided with a step groove, and the step groove extends along the circumferential direction of the mating section. Along the axial direction of the rotor, the total length of the step groove is L, and the height of the rotor is H. When H>25mm, it satisfies: 0.3≤L / H≤0.75; when 15≤H≤25mm, it satisfies: 0.1≤L / H≤0.3, which can reduce the fitting distance between the rotor and the crankshaft. While ensuring the reliability of the assembly of the crankshaft and the rotor, it can effectively avoid the problem of deformation of the crankshaft and the rotor due to the long fitting distance during the assembly process, and can meet the assembly requirements of different rotors, reduce the wear of the rotor and the crankshaft, ensure the assembly stability and precision of the crankshaft, and help improve the energy efficiency and performance stability of the compressor.

[0007] In addition, the compressor according to the above embodiment of the utility model may also have the following additional technical features:

[0008] According to the compressor of some embodiments of the utility model, the inner circumferential wall of the assembly hole is provided with the step difference groove, and the diameter of the matching segment remains unchanged along the axial direction of the rotor; or, the outer circumferential wall of the matching segment is provided with the step difference groove, and the inner diameter of the rotor remains unchanged along the axial direction of the rotor; or, the step difference groove is multiple and includes a first groove and a second groove, the first groove is provided on the inner circumferential wall of the assembly hole, and the second groove is provided on the outer circumferential wall of the matching segment, and the first groove and the second groove are opposite to and connected; or, the step difference groove is multiple and includes a first groove and a second groove, the inner circumferential wall of the assembly hole is provided with the first groove, and the outer circumferential wall of the matching segment is provided with the second groove, and the first groove and the second groove are at least partially staggered.

[0009] According to some embodiments of the present invention, in a direction toward a groove bottom wall of the step groove, two inner side walls of the step groove that are opposite to each other in the axial direction of the rotor are inclined toward each other.

[0010] According to some embodiments of the present utility model, the step difference groove extends in a ring shape along the circumferential direction of the mating segment.

[0011] According to some embodiments of the present invention, the mass of the rotor is M, the normal contact pressure between the rotor and the mating section is F, and the following condition is satisfied: F≥500Mg, where g is the acceleration due to gravity.

[0012] According to some embodiments of the present invention, the inner diameter of the rotor is d, the diameter of the fitting section is D, the interference between the rotor and the fitting section is S, S=Dd, and satisfies: 0.02mm≤S≤0.25mm.

[0013] According to some embodiments of the present invention, the normal contact force between the rotor and the mating section is F, the inner diameter of the rotor is d, the diameter of the mating section is D, the interference between the rotor and the mating section is S, S=Dd, and satisfies: F≥S / (1.26×D)×10 5 .

[0014] According to some embodiments of the present invention, the outer diameter of the rotor is φ, and satisfies: 1.4≤φ / H≤2.5.

[0015] According to some embodiments of the present invention, the step groove is spaced apart from both ends of the rotor in the axial direction.

[0016] According to some embodiments of the present invention, the step groove is one or a plurality of step grooves spaced apart along the axial direction of the rotor.

[0017] According to some embodiments of the present invention, the crankshaft and the rotor are fitted by cold press.

[0018] According to some embodiments of the present invention, the compressor is a rotary compressor.

[0019] The refrigeration device according to the embodiment of the utility model includes the compressor according to the embodiment of the utility model.

[0020] According to the refrigeration equipment of the embodiment of the utility model, the mating section of the crankshaft is located in the assembly hole of the rotor and is connected to the rotor. At least one of the inner circumferential wall of the assembly hole and the outer circumferential wall of the mating section is provided with a step groove, and the step groove extends along the circumferential direction of the mating section. Along the axial direction of the rotor, the total length of the step groove is L, and the height of the rotor is H. When H>25mm, it satisfies: 0.3≤L / H≤0.75; when 15≤H≤25mm, it satisfies: 0.1≤L / H≤0.3, which can reduce the fitting distance between the rotor and the crankshaft. While ensuring the reliability of the assembly of the crankshaft and the rotor, it can effectively avoid the problem of deformation of the crankshaft and the rotor due to the long fitting distance during the assembly process, and can meet the assembly requirements of different rotors, reduce the wear of the rotor and the crankshaft, ensure the assembly stability and precision of the crankshaft, and help improve the energy efficiency and performance stability of the compressor.

[0021] Additional aspects and advantages of the present invention will be given in part in the following description, and in part will become apparent from the following description, or will be learned through the practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0023] Figure 1is a schematic diagram of the structure of a compressor according to some embodiments of the utility model;

[0024] Figure 2 is a partial structural schematic diagram of a compressor according to some embodiments of the utility model;

[0025] Figure 3 is a schematic structural diagram of a crankshaft of a compressor according to some embodiments of the utility model;

[0026] Figure 4 is a schematic structural diagram of a rotor of a compressor according to some embodiments of the utility model;

[0027] Figure 5 is a schematic structural diagram of a compressor according to other embodiments of the utility model;

[0028] Figure 6 It is a partial structural schematic diagram of a compressor according to other embodiments of the utility model;

[0029] Figure 7 is a schematic structural diagram of a rotor of a compressor according to other embodiments of the utility model;

[0030] Figure 8 It is a partial structural schematic diagram of a compressor according to some other embodiments of the utility model.

[0031] Reference numerals:

[0032] 100. Compressor;

[0033] 10. Motor; 11. Rotor; 12. Stator; 111. Assembly hole;

[0034] 20. crankshaft; 21. mating section; 22. eccentric portion; 23. main shaft; 24. secondary shaft;

[0035] 30. step groove; 31. first groove; 32. second groove;

[0036] 40, housing; 41, compression assembly; 42, exhaust pipe; 411, pump chamber; 412, piston; 413, cylinder;

[0037] 50. Liquid reservoir;

[0038] 61. Upper bearing; 62. Lower bearing. DETAILED DESCRIPTION

[0039] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0040] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0041] In the description of the present invention, "first feature" and "second feature" may include one or more such features, "plurality" means two or more, the first feature "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 another feature between them, the first feature "above", "above" and "above" the second feature may include the first feature being directly above and diagonally above the second feature, or may simply mean that the first feature is at a higher level than the second feature.

[0042] The compressor 100 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0043] Reference Figure 1-Figure 8 As shown, the compressor 100 according to the embodiment of the present invention may include: a motor 10 and a crankshaft 20 .

[0044] Specifically, the motor 10 includes a rotor 11, and the rotor 11 is provided with an assembly hole 111. The assembly hole 111 is along the axial direction of the rotor 11 (for example Figure 2 ) passes through the rotor 11, the crankshaft 20 has a matching section 21, the matching section 21 is located in the assembly hole 111, and the matching section 21 is connected to the rotor 11, so that the crankshaft 20 and the rotor 11 can be connected. Therefore, when the rotor 11 rotates, the rotor 11 can drive the crankshaft 20 to rotate along the central axis of the rotor 11, thereby meeting the working requirements of the compressor 100.

[0045] In addition, if Figure 1-Figure 3 , Figure 5-Figure 8As shown, at least one of the inner circumferential wall of the assembly hole 111 and the outer circumferential wall of the matching section 21 is provided with a step groove 30, that is, the inner circumferential wall of the assembly hole 111 is provided with a step groove 30, or the outer circumferential wall of the matching section 21 is provided with a step groove 30, or the inner circumferential wall of the assembly hole 111 and the outer circumferential wall of the matching section 21 are provided with a step groove 30, and the step groove 30 extends along the circumferential direction of the matching section 21. The step groove 30 can reduce the fitting distance between the rotor 11 and the crankshaft 20, avoid the problem of deformation of the crankshaft 20 and the rotor 11 due to the long fitting distance during the assembly process, improve the assembly efficiency, reduce the resistance and friction during assembly, effectively reduce the wear of the rotor 11 and the crankshaft 20, thereby ensuring the assembly stability and accuracy of the crankshaft 20, which is conducive to improving the energy efficiency and performance stability of the compressor 100.

[0046] At the same time, if Figure 3 , Figure 4 and Figure 7 As shown, along the axial direction of the rotor 11, the total length of the step groove 30 is L, and the height of the rotor 11 is H. When H>25mm, it satisfies: 0.3≤L / H≤0.75; when 15≤H≤25mm, it satisfies: 0.1≤L / H≤0.3. Thus, while ensuring the assembly reliability of the crankshaft 20 and the rotor 11, the problem of deformation of the crankshaft 20 and the rotor 11 due to the long fitting distance during the assembly process is effectively avoided, and the wear of the rotor 11 and the crankshaft 20 can be reduced, which is beneficial to improving the energy efficiency and performance stability of the compressor 100. While ensuring the structural strength of the rotor 11, it can meet the assembly requirements of different rotors 11, avoid reducing the strength of the rotor 11 and easily causing the deformation of the rotor 11, and meet the required structural strength requirements.

[0047] For example, in some specific embodiments, when H>25 mm, that is, the height H of the rotor 11 can be 28 mm, 30 mm, 35 mm, 40 mm, 45 mm, 50 mm, etc., and L / H can be 0.3, 0.35, 0.4, 0.45, 0.5, 0.55, 0.6, 0.65, 0.7, 0.75, etc. For example, in some specific embodiments, when 15≤H≤25 mm, that is, the height H of the rotor 11 can be 15 mm, 18 mm, 20 mm, 23 mm, 25 mm, etc., and L / H can be 0.1, 0.13, 0.15, 0.18, 0.2, 0.23, 0.25, 0.28, 0.3, etc.

[0048] It should be noted that, for the convenience of description, the directions such as "up and down directions" in the present invention are based on the directions shown in the drawings, but are not limitations on the directions in actual application.

[0049] In some embodiments, the rotor 11 and the mating section 21 are interference fit, which can ensure that the rotor 11 and the crankshaft 20 fit reliably, and prevent the rotor 11 from falling off the crankshaft 20 when the rotor 11 rotates, thereby ensuring the working reliability of the compressor 100.

[0050] According to the compressor 100 of the embodiment of the utility model, the matching section 21 of the crankshaft 20 is located in the assembly hole 111 of the rotor 11 and connected to the rotor 11, and at least one of the inner circumferential wall of the assembly hole 111 and the outer circumferential wall of the matching section 21 is provided with a step difference groove 30, and the step difference groove 30 extends along the circumferential direction of the matching section 21. Along the axial direction of the rotor 11, the total length of the step difference groove 30 is L, and the height of the rotor 11 is H. When H>25mm, it satisfies: 0.3≤L / H≤0.75; when 15≤ When H≤25mm, it satisfies: 0.1≤L / H≤0.3, which can reduce the fitting distance between the rotor 11 and the crankshaft 20. While ensuring the assembly reliability of the crankshaft 20 and the rotor 11, it can effectively avoid the deformation of the crankshaft 20 and the rotor 11 due to the long fitting distance during the assembly process. It can also meet the assembly requirements of different rotors 11, reduce the wear of the rotor 11 and the crankshaft 20, ensure the assembly stability and accuracy of the crankshaft 20, and is beneficial to improving the energy efficiency and performance stability of the compressor 100.

[0051] In some embodiments of the present invention, Figure 5-Figure 7 As shown, the inner peripheral wall of the assembly hole 111 is provided with a step difference groove 30, and the diameter of the matching segment 21 remains unchanged along the axial direction of the rotor 11; or Figure 1-Figure 4 As shown, a step difference groove 30 is provided on the outer circumferential wall of the matching segment 21, and the inner diameter of the rotor 11 remains unchanged along the axial direction of the rotor 11; or, there may be a plurality of step difference grooves 30, and the plurality of step difference grooves 30 include a first groove 31 and a second groove 32, the first groove 31 is provided on the inner circumferential wall of the assembly hole 111, and the second groove 32 is provided on the outer circumferential wall of the matching segment 21, the first groove 31 and the second groove 32 are opposite, and the first groove 31 and the second groove 32 are connected; or, as Figure 8 As shown, there can be multiple step grooves 30, and the multiple step grooves 30 include a first groove 31 and a second groove 32. The first groove 31 is provided on the inner circumferential wall of the assembly hole 111, and the second groove 32 is provided on the outer circumferential wall of the matching section 21. The first groove 31 and the second groove 32 are at least partially staggered, which can achieve the requirement of reducing the fitting distance between the rotor 11 and the crankshaft 20, and can achieve diversified designs to meet different setting requirements.

[0052] It should be noted that when the first grooves 31 and the second grooves 32 are at least partially staggered, the total length L of the step groove 30 is the length between the two ends of the first grooves 31 and the second grooves 32 that are away from each other.

[0053] According to some embodiments of the present invention, Figure 2 , Figure 3 , Figure 6 and Figure 7 As shown, in the direction toward the bottom wall of the step groove 30, the two inner walls of the step groove 30 that are opposite to each other in the axial direction of the rotor 11 are inclined toward each other, which is convenient for processing and manufacturing the step groove 30 and can avoid problems such as stress concentration, which is beneficial to improving the pressure resistance and structural stability of the step groove 30, avoiding deformation of the crankshaft 20, and ensuring the normal operation of the compressor 100.

[0054] In some embodiments of the present invention, Figure 1-Figure 3 , Figure 6 and Figure 7 As shown, the step groove 30 extends in a ring shape along the circumferential direction of the mating segment 21, which is convenient for processing and manufacturing the step groove 30. The ring-shaped step groove 30 can reduce the fitting pressure between the rotor 11 and the crankshaft 20 in the circumferential direction, further avoiding the problem of deformation of the crankshaft 20 and the rotor 11 due to the long fitting distance during the assembly process, improving the assembly efficiency, and further reducing the resistance and friction during assembly, effectively reducing the wear of the rotor 11 and the crankshaft 20, and ensuring the energy efficiency and performance stability of the compressor 100.

[0055] According to some embodiments of the present invention, the mass of the rotor 11 is M, the normal contact pressure between the rotor 11 and the mating section 21 is F, and the following is satisfied: F ≥ 500Mg, where g is the gravitational acceleration. Thus, by selecting rotors 11 of different masses to satisfy the above formula, the tightness of the connection between the rotors 11 of different masses and the crankshaft 20 can be ensured, so that the rotor 11 is not easy to loosen, and the stability and reliability of the compressor 100 are effectively improved.

[0056] It should be noted that the unit of the mass M of the rotor 11 is kg, and the unit of the normal contact pressure F between the rotor 11 and the matching section 21 is N, which can meet the unit requirements defined by the above formula.

[0057] In some embodiments, Figure 3 , Figure 4 and Figure 7As shown, the inner diameter of the rotor 11 is d, the diameter of the mating section 21 is D, the interference between the rotor 11 and the mating section 21 is S, S=Dd, and satisfies: 0.02mm≤S≤0.25mm. Therefore, within the above range, it is possible to ensure that the connection between the rotor 11 and the crankshaft 20 is tight and not easy to loosen, meet the required clamping force requirements, and avoid problems such as assembly difficulties or damage caused by excessive interference, meet the required assembly requirements, and ensure that the performance of the compressor 100 is stable and reliable. For example, in some specific embodiments, the interference S between the rotor 11 and the mating section 21 can be 0.02mm, 0.05mm, 0.08mm, 0.1mm, 0.15mm, 0.20mm, 0.25mm, etc.

[0058] In some embodiments of the present invention, the normal contact force between the rotor 11 and the mating section 21 is F, the inner diameter of the rotor 11 is d, the diameter of the mating section 21 is D, the interference between the rotor 11 and the mating section 21 is S, S=Dd, and satisfies: F≥S / (1.26×D)×10 5 Since the materials used for the crankshaft 20 and the rotor 11 are common materials, a rigidity coefficient is introduced between the normal contact force F between the rotor 11 and the mating section 21, the interference amount S between the rotor 11 and the mating section 21, and the diameter D of the mating section 21, and the rigidity coefficient is 1.26. Therefore, by satisfying the above formulas, the normal contact force F between the rotor 11 and the mating section 21, the interference amount S between the rotor 11 and the mating section 21, and the diameter D of the mating section 21 can ensure that the connection between the rotor 11 and the crankshaft 20 is tight and not easy to loosen, meet the required clamping force requirements, and ensure that the performance of the compressor 100 is stable and reliable.

[0059] According to some embodiments of the present invention, Figure 4 and Figure 7 As shown, the outer diameter of the rotor 11 is φ, and satisfies: 1.4≤φ / H≤2.5, and the moment of inertia of the rotor 11 is obtained by φ / H. When the moment of inertia of the rotor 11 is within the above range, when the compressor 100 is working, the rotor 11 can be prevented from coming off the crankshaft 20, ensuring that the rotor 11 is reliably fixed on the crankshaft 20, and the efficiency of the motor 10 can be ensured, so that the performance of the compressor 100 is stable and reliable. For example, in some specific embodiments, φ / H can be 1.4, 1.5, 1.8, 2, 2.2, 2.4, 2.5, etc.

[0060] In some embodiments, Figure 1-Figure 3 , Figure 6-Figure 8As shown, the step groove 30 is spaced apart from both ends of the rotor 11 in the axial direction, which can prevent the step groove 30 from affecting the structural integrity of the rotor 11 or the crankshaft 20, thereby ensuring the structural strength of the rotor 11 and the crankshaft 20, and at the same time ensuring that the step groove 30 can meet the required setting requirements, effectively reducing the assembly resistance and friction, and avoiding the problem of deformation of the crankshaft 20 and the rotor 11 due to the long fitting distance during the assembly process.

[0061] According to some embodiments of the present invention, Figure 1-Figure 3 , Figure 6-Figure 8 As shown, there may be one step slot 30, and the length of one step slot 30 along the axial direction of the rotor 11 is L; or, there may be multiple step slots (greater than or equal to two), and the multiple step slots are arranged at intervals along the axial direction of the rotor 11, and the total length of the multiple step slots 30 along the axial direction of the rotor 11 is L. Therefore, under the condition that the requirement of reducing the sleeve distance between the rotor 11 and the crankshaft 20 can be achieved, the length and distribution of the step slots 30 can be adjusted according to actual needs, so that the design is more flexible and can meet different setting requirements.

[0062] In some embodiments of the utility model, the crankshaft 20 and the rotor 11 are cold-pressed together to ensure that the rotor 11 and the crankshaft 20 are tightly connected and reliably fixed, and the connection method is simple and effective, which is conducive to reducing assembly difficulty and production costs.

[0063] In some embodiments, in order to achieve the miniaturization requirement of the compressor 100, the volume of the compressor 100 is reduced, thereby reducing the space occupied by the motor 10, and thus it is necessary to reduce the height of the rotor 11 along the axial direction of the rotor 11, which leads to a reduction in the structural strength of the rotor 11. The inventor of the present application found that in the related art, due to the reduction in the structural strength of the rotor, when the crankshaft and the rotor are assembled by shrink sleeve, the rotor is affected by the ultra-high temperature of the shrink sleeve process, which easily increases the thermal deformation, reduces the reliability of the motor, and thus affects the assembly efficiency of the motor and the reliability of the compressor.

[0064] Therefore, in order to solve the problem of increased thermal deformation of the rotor 11 during assembly, in the utility model, the crankshaft 20 and the rotor 11 are cold-pressed to ensure a tight and reliable connection between the rotor 11 and the crankshaft 20, while avoiding the problems of low assembly efficiency, attenuated compressor energy efficiency, and worsening noise caused by thermal deformation of the rotor and the crankshaft through shrink fitting in the related technology, effectively reducing the thermal deformation of the rotor 11 and the crankshaft 20, which is beneficial to improving the efficiency of the motor 10, improving the overall energy efficiency level of the compressor 100, and facilitating the miniaturization of the compressor 100 to meet the required usage requirements.

[0065] In some embodiments, with the development of miniaturization technology of compressor 100 and motor 10, the assembly process of rotor 11 and crankshaft 20 through cold press fitting has gradually become the main application direction. In order to achieve the miniaturization demand of compressor 100, the volume of compressor 100 is reduced, thereby reducing the occupied space of motor 10, and thus it is necessary to reduce the height of rotor 11 along the axial direction of rotor 11, so that the structural strength of rotor 11 is reduced, resulting in an increase in the deformation of crankshaft 20 and rotor 11 during the cold press fitting process. At the same time, the relative displacement generated during the cold press fitting process of rotor 11 will cause wear on the outer surface of crankshaft 20, increase the deformation of rotor 11, thereby affecting the working performance of compressor 100 and problems such as noise and vibration.

[0066] Therefore, in the present invention, at least one of the inner peripheral wall of the assembly hole 111 and the outer peripheral wall of the matching section 21 is provided with a step difference groove 30. Along the axial direction of the rotor 11, the total length of the step difference groove 30 is L, and the height of the rotor 11 is H. When H>25mm, it satisfies: 0.3≤L / H≤0.75; when 15≤H≤25mm, it satisfies: 0.1≤L / H≤0.3. It can reduce the sleeve distance between the rotor 11 and the crankshaft 20, and while ensuring the assembly reliability of the crankshaft 20 and the rotor 11, it avoids the problem of deformation of the crankshaft 20 and the rotor 11 due to the long sleeve distance during the assembly process, and can improve the assembly efficiency, reduce the resistance and friction during assembly, effectively reduce the wear of the rotor 11 and the crankshaft 20, and while ensuring the structural strength of the rotor 11, it can meet the assembly requirements of different rotors 11, ensure the assembly stability and precision of the crankshaft 20, and is conducive to improving the energy efficiency and performance stability of the compressor 100.

[0067] According to some embodiments of the present invention, the compressor 100 may be a rotary compressor 100, which has the advantages of high efficiency, stability, reliability, etc., can reduce the loss of energy conversion, ensure reliable operation, and is quieter during operation, can reduce vibration and noise, and is conducive to improving the user experience. For example, the rotary compressor 100 may be a single-cylinder rotary compressor 100.

[0068] In some embodiments, Figure 1 , Figure 2 , Figure 5 , Figure 6 and Figure 8As shown, the compressor 100 includes a compression assembly 41, the motor 10 includes a stator 12, the rotor 11 is rotatably disposed in the stator 12, and the compression assembly 41 cooperates with the crankshaft 20. Therefore, when the stator 12 generates a rotating magnetic field, the rotor 11 can rotate in the rotating magnetic field, and the rotation of the rotor 11 can drive the crankshaft 20 to rotate along the central axis of the rotor 11. The rotation of the crankshaft 20 can drive the compression assembly 41 to work, so as to transmit the output force of the motor 10 to the compression assembly 41, so as to realize the operation of the compressor 100.

[0069] In some embodiments, Figure 1-Figure 3 , Figure 5 , Figure 6 and Figure 8 As shown, the crankshaft 20 includes an eccentric portion 22, a main shaft 23 and a secondary shaft 24, and the main shaft 23 and the secondary shaft 24 are respectively located on two opposite sides of the eccentric portion 22 (for example Figure 2 The mating surface is arranged on the main shaft 23, and the main shaft 23 is penetrated in the rotor 11, which can ensure that the crankshaft 20 is reliably connected to the rotor 11 and facilitate the processing and manufacturing of the crankshaft 20.

[0070] In addition, if Figure 1 , Figure 2 , Figure 5 , Figure 6 and Figure 8 As shown, the compressor 100 further includes an upper bearing 61 and a lower bearing 62. The upper bearing 61 is sleeved on one end of the main shaft 23 close to the eccentric portion 22 (for example Figure 2 The lower end shown in FIG. 1 ), the lower bearing 62 is sleeved on the secondary shaft 24. Therefore, when the crankshaft 20 rotates, the upper bearing 61 supports the main shaft 23, and the lower bearing 62 supports the secondary shaft 24, which can ensure that the crankshaft 20 rotates on a predetermined track, thereby ensuring the stability and reliability of the crankshaft 20.

[0071] In some embodiments, Figure 1 , Figure 2 , Figure 5 , Figure 6 and Figure 8 As shown, the compression assembly 41 also includes a cylinder 413, a piston 412 and a vane. The crankshaft 20 passes through the cylinder 413. The cylinder 413 has a pump chamber 411. The eccentric portion 22 is located in the pump chamber 411. The cylinder 413 is formed with a liquid inlet and a liquid outlet that are connected to the pump chamber 411. The cylinder 413 is provided with a vane groove. The piston 412 is sleeved on the outer peripheral side of the eccentric portion 22, and the piston 412 is located in the pump chamber 411. The vane is slidably arranged in the vane groove, and one end of the vane is always in contact with the piston 412. The upper bearing 61 and the lower bearing 62 are respectively located in the axial direction of the cylinder 413 (for example, Figure 2 Both sides of the up and down direction shown in .

[0072] When the motor 10 is working, the rotor 11 drives the crankshaft 20 to rotate, so that the crankshaft 20 drives the piston 412 to rotate, and one end of the sliding plate is always in contact with the piston 412. The sliding plate and the piston 412 cooperate to separate the space in the pump chamber 411 into a liquid inlet chamber and a liquid discharge chamber. The liquid inlet hole of the cylinder 413 is connected to the liquid inlet chamber, and the liquid outlet hole of the cylinder 413 is connected to the liquid discharge chamber. During the rotation of the piston 412, the volume of the liquid inlet chamber and the liquid discharge chamber changes. During the process of increasing the volume of the liquid inlet chamber, the refrigerant is sucked into the liquid inlet chamber through the liquid inlet hole. During the process of decreasing the volume of the liquid discharge chamber, the refrigerant in the liquid discharge chamber is pressed out and discharged from the cylinder 413 through the liquid outlet hole, thereby realizing the compression work of the compressor 100.

[0073] In some embodiments, Figure 1 and Figure 5 As shown, the compressor 100 includes a shell 40, and the compression component 41, the motor 10 and the crankshaft 20 are all arranged in the shell 40. The shell 40 can protect the compression component 41, the motor 10 and the crankshaft 20 to avoid damage caused by exposure of the compression component 41, the motor 10 and the crankshaft 20, and the shell 40 can achieve sealing of structures such as the compression component 41, the motor 10 and the crankshaft 20, thereby ensuring the normal operation of the compressor 100 and helping to increase the service life.

[0074] In some embodiments, Figure 1 and Figure 5 As shown, the compressor 100 further includes a liquid reservoir 50, which is connected to the compression assembly 41. When the compressor 100 is working, the low-temperature and low-pressure refrigerant to be compressed can enter the compression assembly 41 through the liquid reservoir 50, and the low-temperature and low-pressure refrigerant is compressed by the compression assembly 41 to form a high-temperature and high-pressure refrigerant, which can be discharged from the shell 40 through the exhaust pipe 42 connected to the shell 40, thereby realizing the compression work of the compressor 100. At the same time, the refrigerant can be separated into gas and liquid through the liquid reservoir 50, ensuring that the refrigerant is reliably compressed in the compression assembly 41, and ensuring the reliable operation of the compressor 100.

[0075] The refrigeration device according to the embodiment of the utility model includes the compressor 100 according to the embodiment of the utility model. Since the compressor 100 according to the embodiment of the utility model has the above-mentioned beneficial technical effects, the refrigeration device according to the embodiment of the utility model, through the matching section 21 of the crankshaft 20 is located in the assembly hole 111 of the rotor 11 and connected to the rotor 11, at least one of the inner peripheral wall of the assembly hole 111 and the outer peripheral wall of the matching section 21 is provided with a step difference groove 30, the step difference groove 30 extends along the circumferential direction of the matching section 21, along the axial direction of the rotor 11, the total length of the step difference groove 30 is L, the height of the rotor 11 is H, when H>25mm, it satisfies: 0. 3≤L / H≤0.75; when 15≤H≤25mm, it satisfies: 0.1≤L / H≤0.3, which can reduce the fitting distance between the rotor 11 and the crankshaft 20. While ensuring the assembly reliability of the crankshaft 20 and the rotor 11, it can effectively avoid the deformation of the crankshaft 20 and the rotor 11 due to the long fitting distance during the assembly process, and can meet the assembly requirements of different rotors 11, reduce the wear of the rotor 11 and the crankshaft 20, ensure the assembly stability and accuracy of the crankshaft 20, and is beneficial to improving the energy efficiency and performance stability of the compressor 100.

[0076] The other structures and operations of the compressor 100 and the refrigeration device according to the embodiment of the utility model are well known to those skilled in the art and will not be described in detail here.

[0077] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0078] In the description of this specification, the description with reference to the terms "embodiment", "specific embodiment", "example", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0079] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that: include: A motor, the motor comprising a rotor, the rotor being provided with an assembly hole penetrating the rotor along the axial direction of the rotor; A crankshaft, wherein the crankshaft has a matching section, the matching section is located in the assembly hole and connected to the rotor, at least one of the inner peripheral wall of the assembly hole and the outer peripheral wall of the matching section is provided with a step difference groove, and the step difference groove extends along the circumferential direction of the matching section, Wherein, along the axial direction of the rotor, the total length of the step groove is L, and the height of the rotor is H. When H>25mm, it satisfies: 0.3≤L / H≤0.75; when 15≤H≤25mm, it satisfies: 0.1≤L / H≤0.

3.

2. The compressor according to claim 1, characterized in that The inner peripheral wall of the assembly hole is provided with the step difference groove, and the diameter of the matching section remains unchanged along the axial direction of the rotor; Or, the step difference groove is provided on the outer peripheral wall of the matching segment, and the inner diameter of the rotor remains unchanged along the axial direction of the rotor; Or, the step grooves are multiple and include a first groove and a second groove, the first groove is provided on the inner peripheral wall of the assembly hole, the second groove is provided on the outer peripheral wall of the matching section, and the first groove and the second groove are opposite and connected; Alternatively, the step difference grooves are multiple and include a first groove and a second groove, the first groove is provided on the inner peripheral wall of the assembly hole, the second groove is provided on the outer peripheral wall of the matching section, and the first groove and the second groove are at least partially staggered.

3. The compressor according to claim 1 or 2, characterized in that: In a direction toward a groove bottom wall of the step groove, two inner side walls of the step groove that are opposite to each other in the axial direction of the rotor are inclined toward a direction approaching each other.

4. The compressor according to claim 1, characterized in that The step difference groove extends in a ring shape along the circumferential direction of the matching segment.

5. The compressor according to claim 1, characterized in that The mass of the rotor is M, the normal contact pressure between the rotor and the mating section is F, and the following condition is satisfied: F≥500Mg, where g is the acceleration due to gravity.

6. The compressor according to claim 1, characterized in that The inner diameter of the rotor is d, the diameter of the matching section is D, the interference between the rotor and the matching section is S, S=Dd, and the following condition is satisfied: 0.02mm≤S≤0.25mm.

7. The compressor according to claim 1, characterized in that The normal contact force between the rotor and the mating section is F, the inner diameter of the rotor is d, the diameter of the mating section is D, the interference between the rotor and the mating section is S, S=Dd, and satisfies: F≥S / (1.26×D)×10 5 .

8. The compressor according to claim 1, characterized in that The outer diameter of the rotor is φ, and satisfies: 1.4≤φ / H≤2.

5.

9. The compressor according to claim 1, characterized in that The step groove is spaced apart from both ends of the rotor in the axial direction.

10. The compressor according to claim 1, characterized in that The step groove is one or a plurality of step grooves spaced apart along the axial direction of the rotor.

11. The compressor according to claim 1, characterized in that The crankshaft and the rotor are fitted by cold press.

12. The compressor according to claim 1, characterized in that The compressor is a rotary compressor.

13. A refrigeration device, characterized in that: Comprising a compressor according to any one of claims 1-12.

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