Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment, the compressor includes: a motor including a stator and a rotor rotatably arranged in the stator; the compression mechanism comprises a crankshaft and a lower bearing, the crankshaft comprises an eccentric part, a main shaft and an auxiliary shaft, the main shaft and the auxiliary shaft are located on the two opposite sides of the eccentric part respectively, the main shaft penetrates through the rotor and is connected with the rotor, the lower bearing is provided with a bearing hole, the auxiliary shaft penetrates through the bearing hole, and the end, away from the eccentric part, of the auxiliary shaft extends out of the bearing hole; in the axial direction of the crankshaft, the height of the lower bearing is H1, the length of the auxiliary shaft is L1, and the formula that L1-H1 is larger than or equal to 2mm and smaller than or equal to 8mm is met. According to the compressor disclosed by the utility model, the matching precision of the auxiliary shaft in the bearing hole and the lower bearing is ensured, so that the assembling stability and precision of the crankshaft are ensured, the efficiency of the compressor is ensured, the vibration and noise of the compressor are reduced, and the service life of the compressor is further prolonged.

Description

Technical Field

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

[0002] In the related art, the crankshaft and rotor of the compressor are difficult to assemble, and the crankshaft is prone to deformation and wear during the assembly process, which reduces the matching accuracy and is prone to loosening or wear, thereby affecting the working performance of the compressor. 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, which ensures the matching accuracy between the secondary shaft located in the bearing hole and the lower bearing, thereby ensuring the assembly stability and accuracy of the crankshaft, ensuring the efficiency of the compressor, and reducing the vibration and noise of the compressor.

[0004] The utility model also provides a refrigeration device, which comprises the above-mentioned compressor.

[0005] According to the compressor of the embodiment of the utility model, it includes: a motor, the motor includes a stator and a rotor rotatably arranged in the stator; a compression mechanism, the compression mechanism includes a crankshaft and a lower bearing, the crankshaft includes an eccentric portion, a main shaft and a secondary shaft, the main shaft and the secondary shaft are respectively located on two opposite sides of the eccentric portion, the main shaft is passed through the rotor and connected to the rotor, the lower bearing has a bearing hole, the secondary shaft is passed through the bearing hole, one end of the secondary shaft away from the eccentric portion extends out from the bearing hole, along the axial direction of the crankshaft, the height of the lower bearing is H1, the length of the secondary shaft is L1, and it satisfies: 2mm≤L1-H1≤8mm.

[0006] According to the compressor of the embodiment of the utility model, the motor includes a stator and a rotor rotatably arranged in the stator, the compression mechanism includes a crankshaft and a lower bearing, the crankshaft includes an eccentric part, a main shaft and a secondary shaft, the main shaft and the secondary shaft are respectively located on opposite sides of the eccentric part, the main shaft is inserted into the rotor and connected to the rotor, the lower bearing has a bearing hole, the secondary shaft is inserted into the bearing hole, and the secondary shaft extends from the bearing hole through one end of the secondary shaft away from the eccentric part, so that the secondary shaft located outside the bearing hole is used as a force-bearing part, effectively avoiding the secondary shaft located in the bearing hole from being deformed, ensuring the matching accuracy of the secondary shaft located in the bearing hole and the lower bearing, thereby ensuring the assembly stability and accuracy of the crankshaft, ensuring the efficiency of the compressor, reducing the vibration and noise of the compressor, and thus improving the service life of the compressor. At the same time, along the axial direction of the crankshaft, the height through the lower bearing is H1, the length of the secondary shaft is L1, and it satisfies: 2mm≤L1-H1≤8mm, while ensuring that the secondary shaft located in the bearing hole does not deform, it effectively avoids the excessive length of the secondary shaft located outside the bearing hole, resulting in an excessive volume of the compressor, and further improves the reliability of the compressor.

[0007] In some embodiments of the present invention, 2mm≤L1-H1≤5mm.

[0008] In some embodiments of the utility model, the secondary shaft includes a main body portion and a step portion, the step portion is located at one end of the main body portion away from the eccentric portion, the end of the main body portion away from the eccentric portion extends from the lower bearing, and along the axial direction of the crankshaft, the length of the step portion is L2, and satisfies: 1mm≤L2≤5mm.

[0009] In some embodiments of the present invention, 2mm≤L2≤4mm.

[0010] In some embodiments of the present invention, the diameter of the main body is D1, the diameter of the step portion is D2, and the following condition is satisfied: 0.1 mm ≤ D1 - D2 ≤ 0.5 mm.

[0011] In some embodiments of the present invention, the diameter of the main shaft is greater than or equal to the diameter of the secondary shaft.

[0012] In some embodiments of the present invention, the diameter of the main shaft is D3, and satisfies: D3≤13 mm.

[0013] In some embodiments of the utility model, the rotor is provided with an assembly hole that passes through the rotor along the axial direction of the rotor, the main shaft has a mating section, the mating section is located in the assembly hole and connected to the rotor, and 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 difference groove, and the step difference groove extends along the circumferential direction of the mating section.

[0014] In 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 crankshaft.

[0015] In some embodiments of the present invention, the diameter of the matching section at the step groove is D4, the diameter of the matching section is D5, and 0.05mm≤D5-D4≤0.5mm is satisfied.

[0016] In some embodiments of the present invention, the diameter of the main shaft is D3, the outer diameter of the rotor is D6, and the following condition is satisfied: 4.5≤D3 / D6≤6.5.

[0017] In some embodiments of the present invention, the number of stator slots of the stator is Q, the number of poles of the rotor is p, the number of phases of the motor is m, and the following condition is satisfied: Q / mp<1.

[0018] In some embodiments of the present invention, the number of poles of the rotor is an even number less than or equal to 10.

[0019] In some embodiments of the present invention, the diameter of the main shaft is D3, the inner diameter of the rotor is D7, the interference between the rotor and the main shaft is S, and the following condition is satisfied: 0.006mm≤D3-D7≤0.022mm.

[0020] In some embodiments of the present invention, the rotor includes a rotor core, and the rotor core is a silicon steel part.

[0021] The refrigeration equipment according to the embodiment of the utility model includes the above-mentioned compressor.

[0022] According to the refrigeration device of the embodiment of the utility model, a compressor is provided, the motor includes a stator and a rotor rotatably arranged in the stator, the compression mechanism includes a crankshaft and a lower bearing, the crankshaft includes an eccentric part, a main shaft and a secondary shaft, the main shaft and the secondary shaft are respectively located on two opposite sides of the eccentric part, the main shaft is penetrated in the rotor and connected to the rotor, the lower bearing has a bearing hole, the secondary shaft is penetrated in the bearing hole, and extends from the bearing hole through one end of the secondary shaft away from the eccentric part, so that the secondary shaft located outside the bearing hole serves as a force-bearing part, effectively avoiding deformation of the secondary shaft located in the bearing hole, ensuring the matching accuracy of the secondary shaft located in the bearing hole and the lower bearing, thereby ensuring the assembly stability and accuracy of the crankshaft, ensuring the efficiency of the compressor, reducing the vibration and noise of the compressor, and thereby improving the service life of the refrigeration equipment. At the same time, along the axial direction of the crankshaft, the height through the lower bearing is H1, the length of the secondary shaft is L1, and it satisfies: 2mm≤L1-H1≤8mm. While ensuring that the secondary shaft located in the bearing hole does not deform, it effectively avoids the secondary shaft located outside the bearing hole being too long, resulting in an excessively large volume of the compressor, thereby further improving the reliability of the refrigeration equipment.

[0023] 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

[0024] 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:

[0025] Figure 1 is a structural schematic diagram of a compressor according to an embodiment of the utility model;

[0026] Figure 2 is a partial structural schematic diagram of a compressor according to an embodiment of the utility model;

[0027] Figure 3 is a schematic structural diagram of a crankshaft according to an embodiment of the utility model;

[0028] Figure 4 yes Figure 3 Enlarged view of point A in the middle;

[0029] Figure 5 It is a schematic structural diagram of a rotor, a balancing block and an end plate according to an embodiment of the utility model.

[0030] Reference numerals:

[0031] 100. Compressor;

[0032] 1. Motor; 11. Rotor; 111. Assembly hole; 12. Stator; 13. Balance block; 14. End plate; 15. Cylinder; 151. Pump chamber; 16. Piston;

[0033] 2. Compression mechanism; 21. Crankshaft; 211. Eccentric portion; 212. Main shaft; 2121. Matching section; 2122. Step groove; 213. Secondary shaft; 2131. Main body; 2132. Step portion; 22. Lower bearing; 221. Bearing hole; 23. Upper bearing; 3. Housing. DETAILED DESCRIPTION

[0034] 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.

[0035] In the description of the present utility model, it is necessary to understand 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 positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model 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 cannot be understood as a limitation on the present utility model. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, "multiple" means two or more.

[0036] 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.

[0037] The compressor 100 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0038] like Figure 1-Figure 3 As shown, a compressor 100 according to an embodiment of the present utility model includes a motor 1 and a compression mechanism 2 .

[0039] The motor 1 includes a stator 12 and a rotor 11 rotatably disposed in the stator 12, and the compression mechanism 2 includes a crankshaft 21 and a lower bearing 22. The crankshaft 21 includes an eccentric portion 211, a main shaft 212 and a secondary shaft 213. The main shaft 212 and the secondary shaft 213 are respectively located on opposite sides of the eccentric portion 211. The main shaft 212 is penetrated in the rotor 11 and connected to the rotor 11. The lower bearing 22 has a bearing hole 221, and the secondary shaft 213 is penetrated in the bearing hole 221. Therefore, when the rotor 11 rotates, the rotor 11 can drive the crankshaft 21 to rotate along the central axis of the rotor 11, thereby meeting the working requirements of the compressor 100. At the same time, the secondary shaft 213 is supported by the lower bearing 22, thereby ensuring that the crankshaft 21 can rotate on a predetermined track, ensuring the stability and reliability of the crankshaft 21.

[0040] One end of the secondary shaft 213 away from the eccentric portion 211 extends out of the bearing hole 221. It is understandable that during the assembly of the crankshaft 21 and the rotor 11, the end of the secondary shaft 213 of the crankshaft 21 away from the main shaft 212 serves as a force-bearing part, causing the secondary shaft 213 to increase in diameter or bend. Thus, the end of the secondary shaft 213 away from the eccentric portion 211 extends out from the bearing hole 221, so that the secondary shaft 213 located outside the bearing hole 221 serves as the force-bearing part, effectively avoiding the secondary shaft 213 located in the bearing hole 221 from being deformed, ensuring the matching accuracy between the secondary shaft 213 located in the bearing hole 221 and the lower bearing 22, thereby effectively avoiding the secondary shaft 213 located in the bearing hole 221 from being deformed, resulting in uneven contact between the crankshaft 21 and the lower bearing 22 and generating excessive friction, effectively reducing the wear of the lower bearing 22 and the secondary shaft 213, thereby ensuring the assembly stability and accuracy of the crankshaft 21, ensuring the efficiency of the compressor 100, reducing the vibration and noise of the compressor 100, and thereby improving the reliability and service life of the compressor 100.

[0041] Along the axial direction of the crankshaft 21, the height of the lower bearing 22 is H1, the length of the secondary shaft 213 is L1, and they satisfy: 2mm≤L1-H1≤8mm. It can be understood that the length of the secondary shaft 213 outside the bearing hole 221 is L1-H1. Therefore, by limiting the length of the secondary shaft 213 outside the bearing hole 221, while ensuring that the secondary shaft 213 inside the bearing hole 221 does not deform, it is effectively avoided that the length of the secondary shaft 213 outside the bearing hole 221 is too long, resulting in an excessive volume of the compressor 100. For example, in some specific embodiments, the length of the secondary shaft 213 outside the bearing hole 221 can be 2mm, 3mm, 4mm, 5mm, 6mm, 7mm or 8mm.

[0042] Furthermore, if Figure 1 and Figure 4 As shown, the compression mechanism 2 further includes an upper bearing 23, which is sleeved on one end of the main shaft 212 close to the eccentric portion 211. Therefore, during the rotation of the crankshaft 21, the main shaft 212 is supported by the upper bearing 23, thereby ensuring that the crankshaft 21 can rotate on a predetermined track, thereby ensuring the stability and reliability of the crankshaft 21.

[0043] Furthermore, if Figure 1 and Figure 4As shown, the compression mechanism 2 further includes a cylinder 15, a piston 16, and a vane. The crankshaft 21 passes through the cylinder 15, the cylinder 15 has a pump chamber 151, the eccentric portion 211 is located in the pump chamber 151, the cylinder 15 is formed with a liquid inlet and a liquid outlet connected to the pump chamber 151, the cylinder 15 is provided with a vane groove, the piston 16 is sleeved on the outer peripheral side of the eccentric portion 211 and is located in the pump chamber 151, the vane is slidably arranged in the vane groove, one end of the vane is always in contact with the piston 16, and the upper bearing 23 is located on one axial side of the cylinder 15.

[0044] It is understandable that when the motor 1 is working, in the process of driving the crankshaft 21 to drive the piston 16 to rotate through the rotation of the rotor 11, one end of the sliding vane is always in contact with the piston 16, and the sliding vane and the piston 16 cooperate to separate the space in the pump chamber 151 into a liquid inlet chamber and a liquid discharge chamber, and the liquid inlet hole of the cylinder 15 is connected to the liquid inlet chamber, and the liquid outlet hole of the cylinder 15 is connected to the liquid discharge chamber. In the process of the rotation of the piston 16, the volume of the liquid inlet chamber and the liquid discharge chamber changes, and in the process of the volume of the liquid inlet chamber increasing, the liquid refrigerant is sucked into the liquid inlet chamber through the liquid inlet hole, and in the process of the volume of the liquid discharge chamber decreasing, the liquid refrigerant in the liquid discharge chamber is pressed out and discharged from the cylinder 15 through the liquid outlet hole, so that the compressor 100 pumps and transports the liquid refrigerant.

[0045] In some embodiments, Figure 5 As shown, the motor 1 further includes two balancing blocks 13 and two end plates 14. The two balancing blocks 13 are respectively arranged on the rotor 11 along the axial direction of the rotor 11 (such as Figure 5 At both ends of the first direction (shown in FIG. 1 ), two end plates 14 are respectively disposed between the two balancing blocks 13 and the rotor 11. Thus, when the rotor 11 and the crankshaft 21 rotate, the balancing blocks 13 rotate synchronously with the rotor 11, and the centrifugal force generated by the rotation of the balancing blocks 13 effectively reduces the load on the crankshaft 21, so that the deflection generated when the crankshaft 21 rotates is minimized, thereby improving reliability. At the same time, the end plates 14 are used to fix the magnetic parts in the rotor 11, thereby improving the reliability of the compressor 100.

[0046] In some embodiments, Figure 1 As shown, the compressor 100 includes a shell 3, and the compression mechanism 2 and the motor 1 are both arranged in the shell 3. The shell 3 can protect the compression mechanism 2 and the motor 1, effectively avoiding damage caused by exposure of the compression mechanism 2 and the motor 1, and the shell 3 can achieve sealing of structures such as the compression mechanism 2 and the motor 1, ensuring the normal operation of the compressor 100, which is beneficial to increasing the service life.

[0047] According to the compressor 100 of the embodiment of the utility model, the motor 1 includes a stator 12 and a rotor 11 rotatably arranged in the stator 12, the compression mechanism 2 includes a crankshaft 21 and a lower bearing 22, the crankshaft 21 includes an eccentric portion 211, a main shaft 212 and a secondary shaft 213, the main shaft 212 and the secondary shaft 213 are respectively located on opposite sides of the eccentric portion 211, the main shaft 212 is penetrated in the rotor 11 and connected to the rotor 11, the lower bearing 22 has a bearing hole 221, and the secondary shaft 213 is penetrated in the bearing hole 221. , through the end of the secondary shaft 213 away from the eccentric part 211 extending from the bearing hole 221, so that the secondary shaft 213 outside the bearing hole 221 is used as the force-bearing part, effectively avoiding the secondary shaft 213 located in the bearing hole 221 from being deformed, ensuring the matching accuracy between the secondary shaft 213 located in the bearing hole 221 and the lower bearing 22, thereby ensuring the assembly stability and accuracy of the crankshaft 21, ensuring the efficiency of the compressor 100, reducing the vibration and noise of the compressor 100, and thus improving the service life of the compressor 100. At the same time, along the axial direction of the crankshaft 21, the height of the lower bearing 22 is H1, the length of the secondary shaft 213 is L1, and it satisfies: 2mm≤L1-H1≤8mm, while ensuring that the secondary shaft 213 located in the bearing hole 221 does not deform, effectively avoiding the excessive length of the secondary shaft 213 located outside the bearing hole 221, which leads to an excessive volume of the compressor 100, and further improving the reliability of the compressor 100.

[0048] In some embodiments of the present invention, 2mm≤L1-H1≤5mm. It is understandable that the length of the secondary shaft 213 outside the bearing hole 221 is L1-H1. Therefore, by further limiting the length of the secondary shaft 213 outside the bearing hole 221, it is further ensured that the secondary shaft 213 inside the bearing hole 221 does not deform, and effectively avoids the excessive length of the secondary shaft 213 outside the bearing hole 221, which causes the volume of the compressor 100 to be too large. For example, in some specific embodiments, the length of the secondary shaft 213 outside the bearing hole 221 can be 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm or 5mm.

[0049] In some embodiments of the present invention, Figure 2 and Figure 3 As shown, the secondary shaft 213 includes a main body 2131 and a step portion 2132. The step portion 2132 is located at one end of the main body 2131 away from the eccentric portion 211. The end of the main body 2131 away from the eccentric portion 211 extends from the lower bearing 22 and extends along the axial direction of the crankshaft 21 (as shown in FIG. Figure 2 and Figure 3 In the first direction shown in the figure, the length of the step portion 2132 is L2, and satisfies: 1mm≤L2≤5mm.

[0050] It is understandable that, during the assembly process of the crankshaft 21 and the rotor 11, the step portion 2132 as the force-bearing part is first deformed by force. By limiting the length of the step portion 2132 along the axial direction of the crankshaft 21, while ensuring that the body portion 2131 does not deform as much as possible, it is effectively avoided that the length of the step portion 2132 outside the bearing hole 221 is too long, resulting in an excessive volume of the compressor 100. At the same time, since the step portion 2132 may become larger in diameter due to force, by setting the body portion 2131 outside the bearing hole 221, it is possible to effectively avoid friction between the step portion 2132 and the lower bearing 22, and effectively avoid deformation of the lower bearing 22, thereby ensuring the assembly stability and accuracy of the crankshaft 21, ensuring the efficiency of the compressor 100, reducing the vibration and noise of the compressor 100, and thus improving the service life of the compressor 100.

[0051] In addition, the deformation caused by a certain assembly error is further offset by the main body 2131 located outside the bearing hole 221, further ensuring that the main body 2131 located in the bearing hole 221 does not deform, further ensuring the assembly stability and accuracy of the crankshaft 21, thereby ensuring the efficiency of the compressor 100 and reducing the vibration and noise of the compressor 100.

[0052] In some embodiments of the present invention, 2mm≤L2≤4mm. Thus, by further limiting the length of the step portion 2132 along the axial direction of the crankshaft 21, it is further ensured that the body portion 2131 does not deform, and it is effectively prevented that the length of the step portion 2132 outside the bearing hole 221 is too long, resulting in an excessive volume of the compressor 100. For example, in some specific embodiments, the length of the step portion 2132 along the axial direction of the crankshaft 21 can be 2mm, 2.5mm, 3mm, 3.5mm or 4mm.

[0053] In some embodiments of the present invention, Figure 2 and Figure 3 As shown, the diameter of the main body 2131 is D1, the diameter of the step 2132 is D2, and they satisfy: 0.1mm≤D1-D2≤0.5mm. It is understandable that during the assembly of the crankshaft 21 and the rotor 11, the diameter of the step 2132 is smaller than the diameter of the main body 2131, so that the step 2132 is the main force-bearing part, reducing the force transmitted to the main body 2131, thereby ensuring that the main body 2131 does not deform.

[0054] At the same time, since the diameter of the step portion 2132 is larger than the diameter of the main body 2131, the rotation of the crankshaft 21 is affected, resulting in wear of the crankshaft 21, and since the diameter of the step portion 2132 is too small, the strength and rigidity are too small, resulting in the step portion 2132 being unable to fully withstand the stress deformation during the assembly process. Therefore, by limiting the difference between the diameter of the main body 2131 and the diameter of the step portion 2132, while ensuring that the step portion 2132 effectively shares the stress deformation of the main body 2131, the wear of the crankshaft 21 and the parts that cooperate with the crankshaft 21 is effectively avoided, which is conducive to improving the energy efficiency and performance stability of the compressor 100. For example, in some specific embodiments, the diameter of the main body 2131 minus the diameter of the step portion 2132 can be 0.1mm, 0.2mm, 0.3mm, 0.4mm or 0.5mm.

[0055] In some embodiments of the present invention, the diameter of the main shaft 212 is greater than or equal to the diameter of the secondary shaft 213. It can be understood that the main shaft 212 is inserted into the rotor 11 and connected to the rotor 11, so that the main shaft 212 bears the weight of the rotor 11 and the torque driving the rotation. Since the main shaft 212 is the main transmission component, by setting the diameter of the main shaft 212 to be greater than or equal to the diameter of the secondary shaft 213, it is helpful to balance the mass and rotational inertia of the entire crankshaft 21, so that the operation of the compressor 100 is more stable and efficient.

[0056] Furthermore, the diameter of the main shaft 212 is greater than or equal to the diameter of the main body portion. Thus, by limiting the diameter of the main shaft 212 , the diameters of the main body portion 2131 and the step portion 2132 are limited.

[0057] In some embodiments of the present invention, the diameter of the main shaft 212 is D3, and satisfies: D3 ≤ 13 mm. It is understandable that although the long diameter of the main shaft 212 can improve the rigidity of the main shaft 212, under high-speed rotation or high-load conditions, the main shaft 212 with a diameter that is too long is more likely to vibrate and jump, which will directly affect the processing accuracy or compression efficiency of the compressor 100 and increase the volume of the compressor 100. Therefore, by setting the upper limit of the diameter of the main shaft 212 to 13 mm, the main shaft 212 meets the performance requirements and usage requirements of the compressor 100. At the same time, since the diameter of the main shaft 212 is greater than or equal to the diameter of the secondary shaft 213, the size limit of the diameter of the secondary shaft 213 is achieved.

[0058] Furthermore, the diameter of the main shaft 212 is greater than or equal to the diameter of the main body portion. Thus, by limiting the diameter of the main shaft 212 , the diameters of the main body portion 2131 and the step portion 2132 are limited.

[0059] In some embodiments of the present invention, Figure 2 , Figure 3 and Figure 5 As shown, the rotor 11 is provided with an assembly hole 111 which passes through the rotor 11 along the axial direction of the rotor 11, the main shaft 212 has a mating section 2121, the mating section 2121 is located in the assembly hole 111 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 mating section 2121 is provided with a step difference groove 2122, and the step difference groove 2122 extends along the circumferential direction of the mating section 2121.

[0060] Thus, the fitting distance between the rotor 11 and the main shaft 212 can be reduced by the step difference groove 2122, effectively avoiding the problem of deformation of the crankshaft 21 and the rotor 11 due to the long fitting distance during the assembly process, improving the assembly efficiency, reducing the resistance and friction during assembly, and effectively reducing the wear of the rotor 11 and the crankshaft 21, thereby ensuring the assembly stability and accuracy of the crankshaft 21, which is beneficial to improving the energy efficiency and performance stability of the compressor 100. At the same time, the fitting distance between the rotor 11 and the main shaft 212 is reduced by the step difference groove 212, thereby reducing the deformation caused by the force on the end of the secondary shaft 213 away from the main shaft 212 during the pressing process, further ensuring the matching accuracy of the secondary shaft 213 located in the bearing hole 221 and the lower bearing 22, ensuring the efficiency of the compressor 100, reducing the vibration and noise of the compressor 100, and thus improving the reliability and service life of the compressor 100.

[0061] In some embodiments of the present invention, Figure 2 , Figure 3 and Figure 5 As shown, along the axial direction of the crankshaft 21, the total length of the step groove 2122 is L3, the height of the rotor 11 is H, and the following conditions are satisfied: 0.3≤L3 / H≤0.75, thereby effectively avoiding the problem of deformation of the crankshaft 21 and the rotor 11 due to the long sleeve distance during the assembly process while ensuring the assembly reliability of the main shaft 212 and the rotor 11, and reducing the wear of the rotor 11 and the crankshaft 21, which is beneficial to improving the energy efficiency and performance stability of the compressor 100. For example, in some specific embodiments, L3 / H can be 0.3, 0.35, 0.4, 0.45, 0.5, 0.55, 0.6, 0.65, 0.7, 0.75, etc.

[0062] In some embodiments, the rotor 11 and the mating section 2121 have an interference fit, which can ensure that the rotor 11 and the main shaft 212 fit reliably, and effectively prevent the rotor 11 from falling off the main shaft 212 when the rotor 11 rotates, thereby ensuring the working reliability of the compressor 100.

[0063] In some embodiments of the present invention, H satisfies: H>25mm. Within the above range, the structural strength of the rotor 11 can be ensured, and if a step groove 2122 is provided on the inner peripheral wall of the assembly hole 111, it effectively avoids reducing the strength of the rotor 11 and easily causing the rotor 11 to deform, and other problems, and meets the required structural strength requirements. For example, in some specific embodiments, the height H of the rotor 11 can be 28mm, 30mm, 35mm, 40mm, 45mm, 50mm, etc.

[0064] In some embodiments of the present invention, Figure 2 and Figure 3 As shown, there is one step difference groove 2122 or multiple step difference grooves 2122 spaced apart in the axial direction of the crankshaft 21. It can be understood that the total length of the step difference groove 2122 is L3. When there is one step difference groove 2122, the length of one step difference groove is L3. Or, when there are multiple step difference grooves 2122 spaced apart in the axial direction of the crankshaft 21, the total length of the multiple step difference grooves 2122 is L3. Therefore, in the case where the requirement of reducing the sleeve distance between the rotor 11 and the main shaft 212 can be achieved, the length and distribution of the step difference grooves 2122 can be adjusted according to actual needs, so that the design is more flexible and can meet different setting requirements.

[0065] In some embodiments of the present invention, Figure 2 As shown, the step groove 2122 is spaced apart from the two ends of the rotor 11 in the axial direction, which can effectively prevent the step groove 2122 from affecting the structural integrity of the rotor 11 or the crankshaft 21, thereby ensuring the structural strength of the rotor 11 and the crankshaft 21, while ensuring that the step groove 2122 can meet the required setting requirements, effectively reducing the assembly resistance and friction, and effectively avoiding the problem of deformation of the crankshaft 21 and the rotor 11 due to the long fitting distance during the assembly process.

[0066] In some embodiments of the present invention, Figure 2 and Figure 3As shown, the diameter of the mating section 2121 at the step groove 2122 is D4, and the diameter of the mating section 2121 is D5, and 0.05mm≤D5-D4≤0.5mm is satisfied. It can be understood that if the diameter of the mating section 2121 at the step groove 2122 is too small, it will affect the assembly of the main shaft 212 and the rotor 11, and if the diameter of the mating section 2121 at the step groove 2122 is too large, it will affect the structural integrity of the crankshaft 21. Therefore, by limiting the difference between the diameter of the mating section 2121 and the diameter of the mating section 2121 at the step groove 2122, while ensuring the assembly of the main shaft 212 and the rotor 11, it is effectively avoided to affect the structural integrity of the crankshaft 21. For example, in some specific embodiments, the diameter of the fitting segment 2121 minus the diameter of the fitting segment 2121 at the step groove 2122 is 0.05 mm, 0.1 mm, 0.15 mm, 0.2 mm, 0.25 mm, 0.3 mm, 0.35 mm, 0.4 mm, 0.45 mm or 0.5 mm.

[0067] In some embodiments of the present invention, Figure 2 , Figure 3 and Figure 5 As shown, the diameter of the main shaft 212 is D3, the outer diameter of the rotor 11 is D6, and they satisfy: 4.5≤D3 / D5≤6.5. It is understandable that, since the main shaft 212 is a key component that supports and drives the rotor 11, it needs to have sufficient structural strength and stability, and the main shaft 212 and the rotor 11 need to maintain dynamic balance during rotation to reduce vibration and noise and improve the operating efficiency of the compressor 100. Therefore, by limiting the ratio of the diameter of the main shaft 212 to the outer diameter of the rotor 11, the structural strength, stability and rotational dynamic balance of the compressor 100 are ensured, and the reliability of the compressor 100 is improved.

[0068] Furthermore, the diameter of the main shaft 212 is ≤13 mm. Thus, by setting the upper limit of the diameter of the main shaft 212 to 13 mm, the main shaft 212 can meet the performance requirements and usage requirements of the compressor 100 and achieve size limitation on the outer diameter of the rotor 11.

[0069] In some embodiments of the present invention, the number of slots of the stator 12 is Q, the number of poles of the rotor 11 is p, the number of phases of the motor 1 is m, and the following condition is satisfied: Q / mp<1. Thus, when the relationship between the number of slots of the stator, the number of phases of the motor 1, and the number of poles of the rotor 11 is reasonably controlled by the above formula, the electromagnetic field distribution will be more uniform, thereby reducing electromagnetic interference and noise, and improving the reliability of the compressor 100.

[0070] In some embodiments of the present invention, the number of poles of the rotor 11 is an even number less than or equal to 10. It is understandable that the number of poles of the rotor 11 may be 2, 4, 6, 8 or 10. Thus, the even number of poles of the rotor 11 helps to achieve a more symmetrical electromagnetic field distribution, thereby reducing electromagnetic imbalance and vibration, and thus improving the running stability and efficiency of the compressor 100. At the same time, since the number of slots of the stator slots of the stator 12 is Q, the number of poles of the rotor 11 is p, the number of phases of the motor 1 is m, and it satisfies: Q / mp<1, the number of poles p of the rotor 11 is an even number and less than or equal to 10, thereby limiting the upper limit of the number of slots Q of the stator slots, and limiting the number of slots of the stator slots, which helps to simplify the manufacturing process of the motor 1 and reduce the manufacturing cost. For example, in a three-phase motor, when the number of poles p of the rotor 11 is 10, the number of slots Q of the stator slots can be 15.

[0071] In some embodiments of the present invention, Figure 2 , Figure 3 and Figure 5 As shown, the diameter of the main shaft 212 is D3, the inner diameter of the rotor 11 is D7, the interference between the rotor 11 and the main shaft 212 is S, and it satisfies: 0.006mm≤D3-D7≤0.022mm. Therefore, within the above range, it can ensure that the connection between the rotor 11 and the crankshaft 21 is tight and not easy to loosen, meet the required clamping force requirements, and effectively 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 main shaft 212 can be 0.006mm, 0.01mm, 0.014mm, 0.018mm or 0.022mm, etc.

[0072] In some embodiments of the present invention, the rotor 11 includes a rotor core 11, and the rotor core 11 is a silicon steel part. It can be understood that since silicon steel has a lower magnetic permeability, the eddy current loss and hysteresis loss in the rotor core 11 are effectively reduced, and the noise is lower. Therefore, by using the rotor core 11 as a silicon steel part, the loss of the compressor 100 is reduced and the efficiency of the compressor 100 is improved.

[0073] The following describes an assembly method of the compressor 100 according to an embodiment of the present invention.

[0074] According to the assembly method of the compressor 100 of the embodiment of the utility model, the compressor 100, the crankshaft 21 and the rotor 11 are assembled by a cold pressing process. Therefore, by assembling the crankshaft 21 and the rotor 11 by the cold pressing process, it can be ensured that the rotor 11 and the crankshaft 21 are tightly connected and reliably fixed, and the connection method is simple and effective, which is conducive to reducing the difficulty of assembly and production costs.

[0075] At the same time, as the number of poles of the rotor 11 increases, the thickness of the magnetic bridge decreases, which results in poorer connection rigidity at the magnetic bridge. The inventor of the present application found in the experiment that when the number of poles of the rotor increases and the thickness of the magnetic bridge is less than 0.5 mm, when the rotor and the crankshaft are assembled using the existing shrink-fit process, the rotor is easily broken due to the influence of thermal stress deformation. Therefore, the crankshaft 21 and the rotor 11 of the present application are assembled through a cold pressing process to avoid the influence of thermal stress deformation on the rotor 11, thereby reducing the fracture of the rotor 11 during the assembly process of the rotor 11 and the crankshaft 21, and improving the reliability of the compressor 100.

[0076] 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 1, 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 has found that in the related art, due to the reduction in the structural strength of the rotor 11, when the crankshaft 21 and the rotor 11 are assembled by shrink fitting, the rotor 11 is affected by the ultra-high temperature of the shrink fitting process, which easily increases the thermal deformation, reduces the reliability of the motor 1, and thus affects the assembly efficiency of the motor 1 and the reliability of the compressor 100.

[0077] Therefore, in order to solve the problem of increased thermal deformation of the rotor 11 during assembly, in the utility model, the crankshaft 21 and the rotor 11 are cold-pressed to ensure a tight and reliable connection between the rotor 11 and the crankshaft 21. At the same time, the related art problem of thermal deformation of the rotor 11 and the crankshaft 21 resulting in low assembly efficiency, attenuation of energy efficiency of the compressor 100, and deterioration of noise is effectively avoided. The thermal deformation of the rotor 11 and the crankshaft 21 is effectively reduced, which is beneficial to improving the efficiency of the motor 1, improving the overall energy efficiency level of the compressor 100, and facilitating the miniaturization of the compressor 100 to meet the required usage requirements.

[0078] In some embodiments, the rotor 11 includes a rotor 11 core, and the rotor 11 core is a silicon steel part. Therefore, by using the rotor 11 core as a silicon steel part, the loss of the compressor 100 is reduced and the efficiency of the compressor 100 is improved. At the same time, since the silicon steel changes color after heating, and since the crankshaft 21 and the rotor 11 are assembled by a cold pressing process, the color of the rotor 11 core after assembly is consistent with the color of the unheated silicon steel. Therefore, by comparing whether the color of the rotor 11 core is consistent with the color of the unheated silicon steel, it can be determined whether the processing technology of the rotor 11 and the crankshaft 21 is a cold pressing process.

[0079] According to the assembly method of the compressor 100 of the embodiment of the utility model, the crankshaft 21 and the rotor 11 are assembled through a cold pressing process, which can ensure that the rotor 11 and the crankshaft 21 are tightly connected and reliably fixed, and the connection method is simple and effective, which is conducive to reducing assembly difficulty and production costs.

[0080] In some embodiments of the present invention, the pressing force of the rotor 11 into the crankshaft 21 is F, and satisfies: 6KN≤F≤14KN. It is understandable that if the pressing force of the rotor 11 into the crankshaft 21 is too large, the rotor 11, the main shaft 212 and the secondary shaft 213 will be severely deformed, and if the pressing force of the rotor 11 into the crankshaft 21 is too small, the rotor 11 will be disengaged from the main shaft 212 when the rotor 11 rotates. Therefore, by limiting the pressing force of the rotor 11 into the crankshaft 21, while ensuring that the deformation of the rotor 11, the main shaft 212 and the secondary shaft 213 is within a reasonable range, the rotor 11 and the main shaft 212 are reliably matched, and when the rotor 11 rotates, the rotor 11 is effectively prevented from being disengaged from the main shaft 212, thereby ensuring the working reliability of the compressor 100. For example, in some specific embodiments, the pressing force of the rotor 11 into the crankshaft 21 may be 6 KN, 7 KN, 8 KN, 9 KN, 10 KN, 11 KN, 12 KN, 13 KN or 14 KN.

[0081] The inventor of the present application found in the experimental process that, under the premise that the end of the secondary shaft 213 away from the main shaft 212 is completely located in the bearing hole 221, when the pressing force of the rotor 11 into the crankshaft 21 is 12KN, the deformation of the diameter of the secondary shaft 213 located in the bearing hole 221 is 0.002mm, and when the end of the secondary shaft 213 away from the eccentric part 211 is set to extend from the bearing hole 221, the deformation of the diameter of the secondary shaft 213 located in the bearing hole 221 is 0.002mm, and the pressing force of the rotor 11 into the crankshaft 21 can be 14KN. Therefore, by extending the end of the secondary shaft 213 away from the eccentric part 211 from the bearing hole 221, the secondary shaft 213 located outside the bearing hole 221 is used as the force-bearing part, which effectively reduces the deformation of the secondary shaft 213 located in the bearing hole 221.

[0082] In some embodiments of the present invention, the pressing speed of the rotor 11 into the crankshaft 21 is R, and satisfies: 10mm / s≤R≤60mm / s. It is understandable that if the pressing speed of the rotor 11 into the crankshaft 21 is too high, it will cause serious deformation of the rotor 11, the main shaft 212 and the secondary shaft 213, and if the pressing speed of the rotor 11 into the crankshaft 21 is too low, it will cause the rotor 11 to come off the main shaft 212 when the rotor 11 rotates. Therefore, by limiting the pressing speed of the rotor 11 into the crankshaft 21, while ensuring that the deformation of the rotor 11, the main shaft 212 and the secondary shaft 213 is within a reasonable range, it is ensured that the rotor 11 and the main shaft 212 are reliably matched, and when the rotor 11 rotates, the rotor 11 is effectively prevented from coming off the main shaft 212, thereby ensuring the working reliability of the compressor 100. For example, in some specific embodiments, the pressing speed of the rotor 11 into the crankshaft 21 can be 10 mm / s, 20 mm / s, 30 mm / s, 40 mm / s, 50 mm / s or 60 mm / s.

[0083] The refrigeration equipment of the embodiment of the utility model is described below.

[0084] The refrigeration device according to the embodiment of the present utility model includes a compressor 100 .

[0085] According to the refrigeration device of the embodiment of the utility model, a compressor 100 is provided, the motor 1 includes a stator 12 and a rotor 11 rotatably arranged in the stator 12, the compression mechanism 2 includes a crankshaft 21 and a lower bearing 22, the crankshaft 21 includes an eccentric portion 211, a main shaft 212 and a secondary shaft 213, the main shaft 212 and the secondary shaft 213 are respectively located on opposite sides of the eccentric portion 211, the main shaft 212 is penetrated in the rotor 11 and connected to the rotor 11, the lower bearing 22 has a bearing hole 221, and the secondary shaft 213 is penetrated in the bearing hole 221, through the end of the secondary shaft 213 away from the eccentric part 211 extending from the bearing hole 221, so that the secondary shaft 213 outside the bearing hole 221 is used as a force-bearing part, effectively avoiding the secondary shaft 213 located in the bearing hole 221 from being deformed, ensuring the matching accuracy of the secondary shaft 213 located in the bearing hole 221 and the lower bearing 22, thereby ensuring the assembly stability and accuracy of the crankshaft 21, ensuring the efficiency of the compressor 100, reducing the vibration and noise of the compressor 100, and thus improving the service life of the refrigeration equipment. At the same time, along the axial direction of the crankshaft 21, the height of the lower bearing 22 is H1, the length of the secondary shaft 213 is L1, and it satisfies: 2mm≤L1-H1≤8mm, while ensuring that the secondary shaft 213 located in the bearing hole 221 does not deform, effectively avoiding the excessive length of the secondary shaft 213 located outside the bearing hole 221, which leads to an excessive volume of the compressor 100, and further improving the reliability of the refrigeration equipment.

[0086] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" 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.

[0087] 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, comprising a stator and a rotor rotatably disposed in the stator; A compression mechanism, the compression mechanism comprises a crankshaft and a lower bearing, the crankshaft comprises an eccentric portion, a main shaft and a secondary shaft, the main shaft and the secondary shaft are respectively located on opposite sides of the eccentric portion, the main shaft is inserted into the rotor and connected to the rotor, the lower bearing has a bearing hole, the secondary shaft is inserted into the bearing hole, and one end of the secondary shaft away from the eccentric portion extends out of the bearing hole, Along the axial direction of the crankshaft, the height of the lower bearing is H1, the length of the secondary shaft is L1, and they satisfy: 2mm≤L1-H1≤8mm.

2. The compressor according to claim 1, characterized in that 2mm≤L1-H1≤5mm.

3. The compressor according to claim 1, characterized in that The secondary shaft includes a main body and a step portion, wherein the step portion is located at one end of the main body away from the eccentric portion, and the end of the main body away from the eccentric portion extends from the lower bearing. Along the axial direction of the crankshaft, the length of the step portion is L2, and satisfies: 1mm≤L2≤5mm.

4. The compressor according to claim 3, characterized in that 2mm≤L2≤4mm.

5. The compressor according to claim 3, characterized in that The diameter of the main body is D1, the diameter of the step portion is D2, and the following relationship is satisfied: 0.1 mm ≤ D1 - D2 ≤ 0.5 mm.

6. The compressor according to claim 1, characterized in that The diameter of the main shaft is greater than or equal to the diameter of the secondary shaft.

7. The compressor according to claim 6, characterized in that The diameter of the main shaft is D3, and satisfies: D3≤13mm.

8. The compressor according to claim 1, characterized in that The rotor is provided with an assembly hole that passes through the rotor along the axial direction of the rotor, the main shaft has a mating section, the mating section is located in the assembly hole and connected to the rotor, and 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 difference groove, and the step difference groove extends along the circumferential direction of the mating section.

9. The compressor according to claim 8, characterized in that The step groove is one or a plurality of step grooves spaced apart along the axial direction of the crankshaft.

10. The compressor according to claim 8, characterized in that The diameter of the matching section at the step groove is D4, the diameter of the matching section is D5, and 0.05mm≤D5-D4≤0.5mm is satisfied.

11. The compressor according to claim 1, characterized in that The diameter of the main shaft is D3, the outer diameter of the rotor is D6, and the following relationship is satisfied: 4.5≤D3 / D6≤6.

5.

12. The compressor according to claim 1, characterized in that The number of stator slots of the stator is Q, the number of poles of the rotor is p, the number of phases of the motor is m, and the following condition is satisfied: Q / mp<1.

13. The compressor according to claim 12, characterized in that The number of poles of the rotor is an even number less than or equal to 10.

14. The compressor according to claim 1, characterized in that The diameter of the main shaft is D3, the inner diameter of the rotor is D7, the interference between the rotor and the main shaft is S, and the following condition is satisfied: 0.006mm≤D3-D7≤0.022mm.

15. The compressor according to claim 1, characterized in that The rotor comprises a rotor core, and the rotor core is a silicon steel part.

16. A refrigeration device, characterized in that: Comprising a compressor according to any one of claims 1-15.

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