Compressor and refrigeration equipment

Abstract

The utility model discloses a compressor and refrigeration equipment, and relates to the technical field of compressors, the compressor comprises a shell, a motor assembly and a pump body assembly, the motor assembly comprises a stator and a rotor; the pump body assembly comprises an air cylinder, a first bearing, a second bearing, a roller and a crankshaft, the air cylinder is provided with a compression cavity, the roller is rotationally arranged in the compression cavity, the crankshaft comprises a guide section, a first shaft section, an eccentric part and a second shaft section which are sequentially connected, the first shaft section is fixedly connected with the rotor and rotationally matched with the first bearing, and the eccentric part is connected with the roller; the second shaft section is rotationally matched with the second bearing; the guide section protrudes out of one side, deviating from the pump body assembly, of the rotor; the maximum outer diameter of the guide section is D1, the maximum outer diameter of the first shaft section is D2, and the formula that D2-D1 is larger than or equal to 0.1 mm and smaller than or equal to 0.5 mm is met. According to the compressor, the rotor can be smoothly pressed to the first shaft section, the press-in force of the rotor is reduced, the risk of deformation of the crankshaft is reduced, and therefore the reliability of the compressor is improved.

Description

Technical Field

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

[0002] During compressor assembly, the rotor is press-fitted onto the crankshaft from the top using a cold-jacketing process. To facilitate this pressing, a guide structure is typically provided at the end of the crankshaft, guiding the rotor to the crankshaft's main shaft. However, existing crankshaft guide structures in related technologies have poor guiding performance. Excessive pressing force during rotor pressing can cause crankshaft deformation, affecting compressor reliability. Utility Model Content

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a compressor that enables the rotor to be smoothly pressed into the first shaft section, reducing the pressing force on the rotor, reducing the risk of crankshaft deformation, and thus improving the reliability of the compressor.

[0004] This utility model also provides a refrigeration device having the above-mentioned compressor.

[0005] A compressor according to a first aspect of the present invention includes a housing; a motor assembly disposed within the housing, the motor assembly including a stator and a rotor, the rotor being rotatably disposed within the inner hole of the stator; and a pump body assembly disposed within the housing and located on one axial side of the motor assembly, the pump body assembly including a cylinder, a first bearing, a second bearing, rollers, and a crankshaft, the cylinder having a compression chamber, the rollers being rotatably disposed within the compression chamber, the first bearing being disposed on the side of the cylinder near the motor assembly, the second bearing being disposed on the side of the cylinder away from the motor assembly, the crankshaft including a guide section, a first shaft section, an eccentric portion, and a second shaft section connected in sequence, the first shaft section being fixedly connected to the rotor and rotatably engaged with the first bearing, the eccentric portion being connected to the rollers, the second shaft section being rotatably engaged with the second bearing, and the guide section protruding from the side of the rotor away from the pump body assembly; wherein the maximum outer diameter of the guide section is D1, and the maximum outer diameter of the first shaft section is D2, satisfying: 0.1mm ≤ D2 - D1 ≤ 0.5mm.

[0006] The compressor according to the first aspect of the present invention has at least the following beneficial effects: by limiting the maximum outer diameter D1 of the guide section and the maximum outer diameter D2 of the first shaft section to 0.1mm≤D2-D1≤0.5mm, the maximum outer diameter of the guide section is within a reasonable range. By reasonably reducing the maximum outer diameter of the guide section, the rotor is smoothly pressed into the first shaft section through the guide section without contact between the guide section and the rotor, thereby reducing the pressing force on the rotor. This effectively reduces the risk of crankshaft deformation during the pressing process of the rotor. At the same time, it avoids the failure of the guide section to guide the rotor to the first shaft section due to the maximum outer diameter of the guide section being too small, thereby improving the reliability of the compressor.

[0007] According to some embodiments of the present invention, along the axial direction of the crankshaft, the length of the crankshaft is L1, the length of the guide section is L2, and the length of the second shaft section is L3, satisfying: 0.05≤L2 / (L1-L3)≤0.09.

[0008] According to some embodiments of the present invention, the guide segment includes a first guide portion and a second guide portion connected to each other. The first guide portion is connected to one end of the second guide portion away from the first shaft segment. The outer diameter of the first guide portion decreases in the direction away from the first shaft segment. The outer diameter of the second guide portion is equal everywhere. Along the axial direction of the crankshaft, the length of the second guide portion is L4, which satisfies: 0.3≤L4 / L2≤0.8.

[0009] According to some embodiments of the present invention, the first shaft segment and the rotor are interference fit, the outer diameter of the first shaft segment is D2, the inner diameter of the rotor is D3, and the interference S between the first shaft segment and the rotor is D2-D3. The interference S satisfies: 0.011mm≤S≤0.029mm.

[0010] According to some embodiments of the present invention, along the axial direction of the crankshaft, the fitting length between the first shaft segment and the rotor is L5, satisfying: 20mm≤L5≤29mm.

[0011] According to some embodiments of the present invention, the thickness of the oil film between the outer peripheral wall of the first shaft segment and the inner peripheral wall of the rotor is t, which satisfies: 0 < t ≤ 0.1 mm.

[0012] According to some embodiments of the present invention, the length of the oil film along the axial direction of the crankshaft is in the range of 26mm-35mm, and the length of the oil film along the axial direction of the crankshaft is greater than or equal to the mating length between the first shaft segment and the rotor.

[0013] According to some embodiments of the present invention, the second shaft segment protrudes from the side of the second bearing away from the motor assembly. Along the axial direction of the crankshaft, the length of the second shaft segment is L3, and the height of the second bearing is H, satisfying: 0.5mm≤L3-H≤5mm.

[0014] According to some embodiments of the present invention, the circular runout of the end face of the second shaft segment facing away from the eccentric part is 'a', which satisfies: 0≤a≤0.05mm.

[0015] The refrigeration device according to a second aspect of the present invention includes the compressor of the first aspect of the present invention.

[0016] The refrigeration equipment according to the second aspect of the present invention has at least the following beneficial effects: Since the refrigeration equipment uses the aforementioned compressor, by limiting the maximum outer diameter D1 of the guide section and the maximum outer diameter D2 of the first shaft section to 0.1mm ≤ D2 - D1 ≤ 0.5mm, the maximum outer diameter of the guide section is kept within a reasonable range. By reasonably reducing the maximum outer diameter of the guide section, the rotor is smoothly pressed into the first shaft section via the guide section, without contact between the guide section and the rotor, thus reducing the pressing force on the rotor. This effectively reduces the risk of crankshaft deformation during rotor pressing. Simultaneously, it avoids the failure of the guide section to guide the rotor to the first shaft section due to an excessively small maximum outer diameter, thereby improving the reliability of the compressor.

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

[0018] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0019] Figure 1 This is a cross-sectional view of the compressor in an embodiment of this utility model;

[0020] Figure 2 This is a cross-sectional view of the pump body assembly, rotor and support plate combination in an embodiment of this utility model;

[0021] Figure 3 This is a schematic diagram of the crankshaft in an embodiment of this utility model;

[0022] Figure 4 This is a schematic diagram of the rotor in an embodiment of this utility model;

[0023] Figure 5 This is a schematic diagram of the rotor and crankshaft assembly in some other embodiments of this utility model;

[0024] Figure 6This is a schematic diagram of the rotor and crankshaft assembly in some other embodiments of this utility model.

[0025] Figure label:

[0026] Casing 100; Liquid receiver 110; Refrigerant pipe 120;

[0027] Motor assembly 200; stator 210; rotor 220; mounting hole 221; first stepped hole 222; second stepped hole 223;

[0028] Pump body assembly 300; cylinder 310; compression chamber 311; suction port 312; first bearing 320; second bearing 330; roller 340; crankshaft 350; guide section 351; first guide part 3511; second guide part 3512; first shaft section 352; eccentric part 353; second shaft section 354;

[0029] Support plate 400. Detailed Implementation

[0030] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0031] In the description of this utility model, it should be understood that the directional descriptions, such as up, down, front, back, left, right, etc., indicate the directional or positional relationship based on the directional or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0032] In the description of this utility model, "several" means one or more, "multiple" means two or more, "greater than," "less than," and "exceeding" are understood to exclude the stated number, while "above," "below," and "within" are understood to include the stated number. If "first" or "second" is used in the description, it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0033] In the description of this utility model, unless otherwise explicitly defined, terms such as setting, installing, connecting, assembling, and cooperating should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this utility model in conjunction with the specific content of the technical solution.

[0034] The compressor rotor is typically press-fitted onto the crankshaft from the top using a cold-jacketing process. To facilitate rotor press-fitting, a guide structure is usually provided at the end of the crankshaft to guide the rotor during press-fitting. In related technologies, improper dimensions of the guide structure result in poor guiding effect. During the rotor press-fitting process, excessive pressing force can lead to crankshaft deformation, affecting the reliability of the compressor.

[0035] Therefore, referring to Figures 1 to 6 As shown, the first aspect of this utility model provides a compressor for use in refrigeration equipment, such as air conditioners, beverage coolers, etc.

[0036] Reference Figure 1 As shown, the compressor includes a housing 100, a pump assembly 300, and a motor assembly 200. It also includes a liquid receiver 110 and a refrigerant pipe 120 connecting the liquid receiver 110 and the housing 100. Specifically, the housing 100 is generally cylindrical and has an internal cavity. The pump assembly 300 and the motor assembly 200 are both installed within the internal cavity of the housing 100, and the liquid receiver 110 is located radially outward from the housing 100. The housing 100 can be arranged horizontally or vertically.

[0037] It is easy to understand that if the casing 100 is arranged vertically, the compressor is a vertical compressor. If the casing 100 is arranged horizontally, the compressor is a horizontal compressor.

[0038] It is easy to understand that different compressor layouts can be selected based on the available space within the heat pump air conditioner, thereby improving applicability.

[0039] Reference Figure 1 As shown, it can be understood that in this embodiment, the compressor is a vertical compressor, and the motor assembly 200 is located above the pump body assembly 300, that is, the pump body assembly 300 is located on the axial side of the motor assembly 200.

[0040] Reference Figure 1 As shown, the pump assembly 300 can be a single-cylinder, double-cylinder, or multi-cylinder structure. Specifically, the pump assembly 300 includes a cylinder 310, a first bearing 320, a second bearing 330, rollers 340, and a crankshaft 350. The number of cylinders 310 differs between single-cylinder, double-cylinder, and multi-cylinder pump assemblies 300. When there are two or more cylinders 310, they are arranged sequentially in a vertical direction. It is easy to understand that the number of rollers 340 is equal to the number of cylinders 310. The single-cylinder, double-cylinder, and multi-cylinder pump assemblies 300 correspond to compressors with different displacements.

[0041] Reference Figure 1As shown, it can be understood that in this embodiment, the pump body assembly 300 is a single-cylinder structure. Specifically, the cylinder 310 is provided with a compression chamber 311, which extends through the upper and lower end faces of the cylinder 310. The roller 340 has a cylindrical structure and is rotatably disposed in the compression chamber 311, with the central axis of the roller 340 offset from the central axis of the compression chamber 311. The first bearing 320 is located on the upper side of the cylinder 310 and covers the upper opening of the compression chamber 311, that is, the first bearing 320 is located on the side of the cylinder 310 closer to the motor assembly 200. The second bearing 330 is located on the lower side of the cylinder 310 and covers the lower opening of the compression chamber 311, that is, the second bearing 330 is located on the side of the cylinder 310 away from the motor assembly 200.

[0042] Reference Figure 1 As shown, it can be understood that the cylinder 310 is also provided with an intake port 312, which is connected to the compression chamber 311. It is easy to understand that the refrigerant pipe 120 connecting the housing 100 and the reservoir 110 is connected to the intake port 312, so that the low-pressure refrigerant in the reservoir 110 enters the compression chamber 311 through the refrigerant pipe 120 and the intake port 312, whereby the rollers 340 compress the refrigerant to perform work.

[0043] Reference Figure 1 and Figure 3 As shown, the crankshaft 350 is arranged vertically. Specifically, the crankshaft 350 includes a guide section 351, a first shaft section 352, an eccentric portion 353, and a second shaft section 354 connected sequentially from top to bottom. The first shaft section 352 passes through and rotatably engages with the first bearing 320. The eccentric portion 353 is located within the compression chamber 311 and rotatably connected to the roller 340. The second shaft section 354 passes through and rotatably engages with the second bearing 330. Therefore, the first bearing 320 and the second bearing 330 provide radial support to the crankshaft 350 to ensure its rotational stability.

[0044] Reference Figure 1 As shown, it can be understood that the motor assembly 200 is located above the first bearing 320. Specifically, the motor assembly 200 includes a stator 210 and a rotor 220. The stator 210 is fixedly connected to the inner peripheral wall of the housing 100, and the rotor 220 is rotatably disposed in the inner hole of the stator 210. A first shaft section 352 passes through the rotor 220 and is fixedly connected to the rotor 220. A guide section 351 protrudes upward from the upper end face of the rotor 220, that is, the guide section 351 protrudes from the side of the rotor 220 away from the pump body assembly 300. In this embodiment, the guide section 351 is located above the rotor 220.

[0045] Therefore, during the operation of the compressor, the motor assembly 200 drives the crankshaft 350 to rotate, and the crankshaft 350 drives the roller 340 to rotate eccentrically in the compression chamber 311, thereby compressing the refrigerant in the compression chamber 311 to perform work.

[0046] Reference Figure 3 As shown, it can be understood that the maximum outer diameter of the guide segment 351 is defined as D1, and the maximum outer diameter of the first shaft segment 352 is defined as D2. Generally speaking, the outer diameter of the first shaft segment 352 is equal at all points. The maximum outer diameter D1 of the guide segment 351 and the maximum outer diameter D2 of the first shaft segment 352 satisfy: 0.1mm ≤ D2 - D1 ≤ 0.5mm. That is, the maximum outer diameter of the guide segment 351 is smaller than the maximum outer diameter of the first shaft segment 352, and the difference between the two is between 0.1mm and 0.5mm.

[0047] Understandably, the maximum outer diameter of the guide section 351 is generally smaller than the inner diameter of the mounting hole 221 of the rotor 220. During the press-fitting of the rotor 220 onto the crankshaft 350, the crankshaft 350 is fixed, allowing the rotor 220 to move downwards. The rotor 220 first fits into the guide section 351, which initially positions the rotor 220 radially, bringing its central axis nearly to coincide with the central axis of the first shaft section 352. Guided by the guide section 351, as the rotor 220 moves further downwards, the guide section 351 guides the rotor 220 to the first shaft section 352, thus smoothly pressing the rotor 220 into the first shaft section 352.

[0048] Reference Figure 3As shown, it is understandable that if D2-D1 < 0.1mm, the maximum outer diameter of the guide section 351 is too close to the maximum outer diameter of the first shaft section 352. During the press-fitting of the rotor 220, this will cause the guide section 351 to come into contact with the rotor 220, resulting in excessive pressing force on the rotor 220, increasing assembly difficulty, and easily causing deformation of the crankshaft 350. If D2-D1 > 0.5mm, the maximum outer diameter of the guide section 351 is too small, resulting in poor initial radial positioning of the rotor 220 by the guide section 351, affecting the guiding effect of the guide section 351 on the press-fitting of the rotor 220 to the first shaft section 352, which is not conducive to the installation of the rotor 220. Therefore, by ensuring that 0.1mm ≤ D2 - D1 ≤ 0.5mm, for example, D2 - D1 being 0.1mm, 0.25mm, 0.3mm, or 0.5mm, the maximum outer diameter of the guide section 351 is kept within a reasonable range. By reasonably reducing the maximum outer diameter of the guide section 351, the rotor 220 is smoothly pressed into the first shaft section 352 via the guide section 351, without contact between the guide section 351 and the rotor 220. This reduces the pressing force on the rotor 220 by approximately 1kN-2kN, effectively reducing the risk of crankshaft 350 deformation during the pressing process of the rotor 220. At the same time, it avoids the failure of the guide section 351 to guide the rotor 220 to the first shaft section 352 due to an excessively small maximum outer diameter, thereby improving the reliability of the compressor.

[0049] Reference Figure 3As shown, it can be understood that along the axial direction of crankshaft 350, the length of crankshaft 350 is defined as L1, the length of guide section 351 as L2, and the length of second shaft section 354 as L3, satisfying: 0.05≤L2 / (L1-L3)≤0.09. L2 / (L1-L3) is the proportion of the length of guide section 351 to the length of the shaft sections of crankshaft 350 excluding second shaft section 354. Given a fixed length for crankshaft 350 and second shaft segment 354, if L2 / (L1-L3) < 0.05, the length of guide segment 351 is too small. When guide segment 351 initially positions rotor 220 radially, the length of guide segment 351 inserted into rotor 220 is too small, resulting in poor positioning of rotor 220. This can easily lead to excessive tilt of the central axis of rotor 220 relative to the central axis of first shaft segment 352, making it difficult for guide segment 351 to guide rotor 220 to first shaft segment 352 and increasing installation difficulty. If L2 / (L1-L3) > 0.09, the length of guide segment 351 is too large, and the length of guide segment 351 protruding upward from rotor 220 is too large, which will increase the height of compressor. Therefore, 0.05 ≤ L2 / (L1-L3) ≤ 0.09 is ensured. For example, the value of L2 / (L1-L3) is 0.05, 0.07, 0.08, or 0.09, etc., so that the length of the guide section 351 is within a reasonable range. This improves the positioning and guiding effect of the guide section 351 on the rotor 220, reduces the pressing force on the rotor 220 and the installation difficulty, and avoids the disadvantage of the guide section 351 causing the compressor to be too tall. In this embodiment, L2 also satisfies: 3mm ≤ L2 ≤ 8mm.

[0050] Reference Figure 2 and Figure 3 As shown, it can be understood that the guide segment 351 includes a first guide portion 3511 and a second guide portion 3512 connected sequentially from top to bottom, that is, the first guide portion 3511 is connected to the end of the second guide portion 3512 away from the first shaft segment 352. The outer diameter of the first guide portion 3511 decreases from bottom to top, that is, the outer diameter of the first guide portion 3511 decreases in the direction away from the first shaft segment 352. The outer diameter of the second guide portion 3512 is equal everywhere. It is easy to understand that the outer peripheral wall of the second guide portion 3512 is connected to the outer peripheral wall of the first shaft segment 352 through a slope or arc surface transition. This slope or arc surface transition connection structure is neither part of the structure of the guide segment 351 nor part of the structure of the second guide portion 3512. Therefore, the first guide portion 3511 with a gradually changing outer diameter can reduce the difficulty of fitting the rotor 220 into the guide section 351 and guide the rotor 220 to the second guide portion 3512. The second guide portion 3512 with an equal outer diameter at all points can position the rotor 220 radially and guide the rotor 220 to the first shaft section 352, thereby reducing the installation difficulty of the rotor 220.

[0051] Reference Figure 3As shown, it can be understood that the length of the second guide portion 3512 along the axial direction of the crankshaft 350 is defined as L4, satisfying: 0.3≤L4 / L2≤0.8. That is, the ratio of the length of the second guide portion 3512 to the length of the guide segment 351 is 0.3-0.8. Given a fixed length of the guide segment 351, if L4 / L2<0.3, the length of the second guide portion 3512 is too small, resulting in poor positioning of the rotor 220 and potentially causing excessive inclination of the rotor 220's central axis relative to the central axis of the first shaft segment 352. This makes it difficult for the second guide portion 3512 to guide the rotor 220 to the first shaft segment 352, increasing installation difficulty. If L4 / L2>0.8, the length of the second guide portion 3512 is too large, resulting in the first guide portion 3511 being too small, leading to a poorer guiding effect on the rotor 220 and hindering installation. Therefore, by ensuring that 0.3≤L4 / L2≤0.8, for example, the value of L4 / L2 is 0.3, 0.5, 0.7 or 0.8, the length ratio of the first guide portion 3511 and the second guide portion 3512 is within a reasonable range, thereby reducing the installation difficulty of the rotor 220 and allowing the rotor 220 to be pressed onto the first shaft section 352 more smoothly.

[0052] Reference Figure 3 and Figure 4 As shown, it can be understood that the first shaft segment 352 and the rotor 220 are interference-fitted, ensuring a stable and reliable connection. Specifically, the inner diameter of the rotor 220 is D3, which is the inner diameter of the mounting hole 221 of the rotor 220. The interference amount S between the first shaft segment 352 and the rotor 220 is S = D2 - D3, and the interference amount S satisfies: 0.011mm ≤ S ≤ 0.029mm. This ensures that the interference amount between the first shaft segment 352 and the rotor 220 is within a reasonable range, for example, S is 0.011mm, 0.018mm, 0.021mm, 0.025mm, or 0.029mm, etc. This avoids the drawbacks of excessive pressing force on the rotor 220 due to excessive interference amount, which could lead to deformation of the crankshaft 350 during the pressing process of the rotor 220. At the same time, it avoids the drawbacks of unstable connection between the first shaft segment 352 and the rotor 220, noise generation, and decreased reliability due to insufficient interference amount.

[0053] like Figure 2 As shown, it can be understood that along the axial direction of the crankshaft 350, the mating length between the first shaft segment 352 and the rotor 220 is L5. This mating length is the length of the contact portion between the first shaft segment 352 and the rotor 220 on the crankshaft 350. In this embodiment, the mating length L5 between the first shaft segment 352 and the rotor 220 is the axial height of the mounting hole 221 of the rotor 220.

[0054] Reference Figure 5As shown, it can be understood that in some embodiments, the lower end of the inner wall of the mounting hole 221 of the rotor 220 is provided with a first stepped hole 222, and the inner peripheral wall of the first stepped hole 222 does not contact the outer peripheral wall of the first shaft segment 352. Therefore, the mating length L5 between the first shaft segment 352 and the rotor 220 is the difference between the axial height of the mounting hole 221 of the rotor 220 and the axial height of the first stepped hole 222.

[0055] Reference Figure 6 As shown, it can be understood that in some embodiments, the lower end of the inner wall of the mounting hole 221 of the rotor 220 is provided with a first stepped hole 222, and the upper end of the inner wall of the mounting hole 221 of the rotor 220 is provided with a second stepped hole 223. The inner peripheral walls of the first stepped hole 222 and the second stepped hole 223 do not contact the outer peripheral wall of the first shaft segment 352. Therefore, the mating length L5 between the first shaft segment 352 and the rotor 220 is the difference between the axial height of the mounting hole 221 of the rotor 220 and the axial heights of the first stepped hole 222 and the second stepped hole 223.

[0056] Reference Figure 2 As shown, it can be understood that the mating length L5 between the first shaft segment 352 and the rotor 220 satisfies: 20mm ≤ L5 ≤ 29mm. If L5 < 20mm, the mating force between the first shaft segment 352 and the rotor 220 will be too small, even lower than the requirement of 500 times the self-weight of the rotor 220, resulting in poor reliability. If L5 > 29mm, the pressing force of the rotor 220 will be too large during the pressing process, causing the crankshaft 350 to deform, also resulting in poor reliability. Therefore, 20mm ≤ L5 ≤ 29mm is ensured. For example, L5 can be 20mm, 22mm, 25mm, 27mm, 28mm, or 29mm, etc., to reduce the pressing force of the rotor 220 while maintaining the mating force between the first shaft segment 352 and the rotor 220, thus avoiding crankshaft 350 deformation and improving reliability.

[0057] Understandably, to further reduce the pressing force on the rotor 220, lubricating oil is applied between the outer peripheral wall of the first shaft section 352 and the inner peripheral wall of the mounting hole 221 of the rotor 220. Specifically, lubricating oil is applied to the crankshaft 350 using a sponge to ensure more uniform oil distribution. The thickness of the oil film between the first shaft section 352 and the rotor 220 is defined as t, satisfying 0 < t ≤ 0.1 mm. By appropriately setting the thickness of the oil film between the first shaft section 352 and the rotor 220, the frictional force during the pressing process of the rotor 220 can be reduced, which helps to reduce the pressing force on the rotor 220, lowers the risk of crankshaft 350 deformation, and improves reliability.

[0058] Reference Figure 2As shown, it can be understood that the length of the oil film between the first shaft section 352 and the rotor 220 along the axial direction of the crankshaft 350 is greater than or equal to the mating length L5 between the first shaft section 352 and the rotor 220. This ensures that there is lubricating oil at the contact position between the first shaft section 352 and the rotor 220 during the press-fitting of the rotor 220, thereby reducing friction, reducing the pressing force of the rotor 220, reducing the risk of deformation of the crankshaft 350, improving reliability, and reducing the installation difficulty of the rotor 220.

[0059] Understandably, in this embodiment, the length of the oil film between the first shaft segment 352 and the rotor 220 along the axial direction of the crankshaft 350 ranges from 26mm to 35mm. If the length of the oil film is less than 26mm, the lubrication range is insufficient, resulting in a larger pressing force on the rotor 220 during the press-fitting process, increasing the risk of crankshaft 350 deformation. If the length of the oil film is greater than 35mm, the length of the oil film is much greater than the mating length between the first shaft segment 352 and the rotor 220, leading to lubricant waste. Therefore, by making the length of the oil film between the first shaft segment 352 and the rotor 220 along the axial direction of the crankshaft 350 range from 26mm to 35mm, the pressing force on the rotor 220 is reduced, the risk of crankshaft 350 deformation is reduced, reliability is improved, and lubricant waste is reduced.

[0060] Reference Figure 2 As shown, it can be understood that the second shaft segment 354 passes through the second bearing 330 and protrudes downward from the lower end face of the second bearing 330, that is, the second shaft segment 354 protrudes from the end face of the second bearing 330 on the side opposite to the motor assembly 200. It is easy to understand that when installing the rotor 220, the second shaft segment 354 passes through the second bearing 330, and the lower end of the second shaft segment 354 abuts against the support plate 400 used to support the crankshaft 350, the support plate 400 being a tooling fixture. By making the lower end of the second shaft segment 354 protrude downward from the lower end face of the second bearing 330, during the pressing of the rotor 220 onto the crankshaft 350, the second shaft segment 354 becomes the force-bearing part, avoiding the disadvantage of deformation of the second bearing 330 due to stress, thereby helping to ensure the structural stability of the second bearing 330 and improving the reliability of the compressor.

[0061] Understandably, the hardness of the upper surface of the support plate 400 is greater than that of the crankshaft 350 to ensure stable support for the crankshaft 350. Specifically, the hardness of the upper surface of the support plate 400 meets the requirement of 55-60 HRC. Simultaneously, during the press-fitting of the rotor 220, to ensure the stability of the crankshaft 350, the flatness of the upper surface of the support plate 400 is less than 0.05 mm, preventing the crankshaft 350 from tilting during the press-fitting process and improving safety.

[0062] Reference Figure 2 and Figure 3As shown, it can be understood that the axial height of the second bearing 330 on the crankshaft 350 is defined as H. The height H of the second bearing 330 and the length L3 of the second shaft segment 354 satisfy: 0.5mm ≤ L3-H ≤ 5mm. L3-H is the length of the second shaft segment 354 protruding from the lower end face of the second bearing 330. If L3-H < 0.5mm, the length of the second shaft segment 354 protruding from the lower end face of the second bearing 330 is too small, which may result in the second bearing 330 contacting the support plate 400 and bearing a force on the second bearing 330, causing the second bearing 330 to deform under stress. If L3-H > 5mm, the length of the crankshaft 350 is too large, resulting in an increase in the height of the compressor. Therefore, the length of L3-H is kept between 0.5mm and 5mm, for example, L3-H is 0.5mm, 1.8mm, 2mm, 3.5mm, 4mm or 5mm, to prevent deformation of the second bearing 330, improve reliability, and avoid the disadvantage of the second shaft section 354 causing the compressor to be too tall.

[0063] It is understandable that the circular runout of the end face of the second shaft segment 354 away from the eccentric part 353 is 'a', that is, the circular runout of the lower end face of the second shaft segment 354 is 'a', satisfying: 0≤a≤0.05mm. By setting the circular runout of the lower end face of the second shaft segment 354 within a reasonable range, the flatness of the lower end face of the second shaft segment 354 is ensured to be small, thereby making the contact surface between the second shaft segment 354 and the support plate 400 smoother, thus improving the stability of the crankshaft 350, preventing the crankshaft 350 from tilting during the press-fitting of the rotor 220, and improving safety.

[0064] The refrigeration equipment of the second aspect of this utility model includes the compressor of the first aspect of this utility model. The refrigeration equipment can be an air conditioner, a cold drink machine, etc.

[0065] Since the refrigeration equipment adopts all the technical solutions of the compressor in the above embodiments, it has at least all the beneficial effects brought about by the technical solutions in the above embodiments.

[0066] The embodiments of the present utility model have been described in detail above with reference to the accompanying drawings. However, the present utility model is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present utility model.

Claims

1. A compressor, characterized in that, include: case; A motor assembly is disposed within the housing, the motor assembly including a stator and a rotor, the rotor being rotatably disposed within the inner hole of the stator; A pump body assembly is disposed within the housing and located on one axial side of the motor assembly. The pump body assembly includes a cylinder, a first bearing, a second bearing, rollers, and a crankshaft. The cylinder has a compression chamber, and the rollers are rotatably disposed in the compression chamber. The first bearing is disposed on the side of the cylinder close to the motor assembly, and the second bearing is disposed on the side of the cylinder away from the motor assembly. The crankshaft includes a guide section, a first shaft section, an eccentric portion, and a second shaft section connected in sequence. The first shaft section is fixedly connected to the rotor and rotatably engaged with the first bearing. The eccentric portion is connected to the rollers. The second shaft section rotatably engages with the second bearing. The guide section protrudes from the side of the rotor away from the pump body assembly. Wherein, the maximum outer diameter of the guide section is D1, and the maximum outer diameter of the first shaft section is D2, satisfying: 0.1mm≤D2-D1≤0.5mm.

2. The compressor according to claim 1, characterized in that: Along the axial direction of the crankshaft, the length of the crankshaft is L1, the length of the guide section is L2, and the length of the second shaft section is L3, satisfying: 0.05≤L2 / (L1-L3)≤0.

09.

3. The compressor according to claim 2, characterized in that: The guide section includes a first guide portion and a second guide portion connected to each other. The first guide portion is connected to the end of the second guide portion away from the first shaft section. The outer diameter of the first guide portion decreases in the direction away from the first shaft section. The outer diameter of the second guide portion is equal everywhere. Along the axial direction of the crankshaft, the length of the second guide portion is L4, which satisfies: 0.3≤L4 / L2≤0.

8.

4. The compressor according to claim 1, characterized in that: The first shaft segment and the rotor are interference fit. The outer diameter of the first shaft segment is D2, the inner diameter of the rotor is D3, and the interference S between the first shaft segment and the rotor is S = D2 - D3. The interference S satisfies: 0.011mm ≤ S ≤ 0.029mm.

5. The compressor according to claim 4, characterized in that: Along the axial direction of the crankshaft, the mating length between the first shaft segment and the rotor is L5, satisfying: 20mm≤L5≤29mm.

6. The compressor according to claim 4 or 5, characterized in that: The thickness of the oil film between the outer peripheral wall of the first shaft segment and the inner peripheral wall of the rotor is t, which satisfies: 0 < t ≤ 0.1 mm.

7. The compressor according to claim 6, characterized in that: The length of the oil film along the axial direction of the crankshaft ranges from 26mm to 35mm, and the length of the oil film along the axial direction of the crankshaft is greater than or equal to the mating length between the first shaft segment and the rotor.

8. The compressor according to claim 1, characterized in that: The second shaft segment protrudes from the side of the second bearing away from the motor assembly. Along the axial direction of the crankshaft, the length of the second shaft segment is L3, and the height of the second bearing is H, satisfying: 0.5mm≤L3-H≤5mm.

9. The compressor according to claim 8, characterized in that: The circular runout of the end face of the second shaft segment opposite to the eccentric part is 'a', which satisfies: 0 ≤ a ≤ 0.05 mm.

10. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 9.

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