Compressor and refrigeration equipment

Abstract

The invention discloses a compressor and refrigeration equipment. The compressor comprises a rotor assembly and a crankshaft, and a first through-flow hole is formed in the rotor assembly; the crankshaft is connected with the rotor assembly, a main bearing is arranged on the crankshaft, and a second through-flow hole communicated with the first through-flow hole is formed in the main bearing; a plurality of first through-flow holes are formed around the axis of the crankshaft in the circumferential direction, a plurality of second through-flow holes are formed around the axial direction of the crankshaft in the circumferential direction, the outer diameter of each first through-flow hole is D1, the inner diameter of each first through-flow hole is D2, the outer diameter of each second through-flow hole is D3, the inner diameter of each second through-flow hole is D4, and D2 * D3 / (D1 * D4) is larger than or equal to 0.55 and smaller than or equal to 0.95. According to the compressor, the deviation range of the relative positions of the first through-flow hole in the rotor assembly and the second through-flow hole in the main bearing in the radial direction can be optimized, the through-flow effect is enhanced while the structural strength of the rotor assembly and the main bearing is guaranteed, the oil liquid level and oil liquid circulation of the compressor are improved, and the service life of the compressor is prolonged. And the operation reliability, efficiency and service life of the compressor are improved.

Description

Technical Field

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

[0002] In refrigeration equipment such as air conditioners and refrigerators, the compressor transfers energy by compressing and circulating refrigerant. During this process, some oil in the oil sump at the bottom of the compressor circulates within the compressor, driven by the refrigerant, providing necessary lubrication, heat dissipation, and sealing for components such as the crankshaft, motor, and bearings. This is crucial for the compressor's operating efficiency and safety. However, in related technologies, the oil circulation within the compressor is often poor, making it difficult to maintain a good oil level. This leads to easy wear on the motor, bearings, and other components in the high-temperature, high-pressure environment, as well as poor heat dissipation and sealing performance, severely affecting the compressor's reliability, stability, and lifespan. Summary of the Invention

[0003] This application aims to at least solve one of the technical problems existing in the prior art. To this end, one object of this application is to provide a compressor that can optimize the radial deviation range of the relative positions of the first flow passage on the rotor assembly and the second flow passage on the main bearing, thereby enhancing the flow effect, improving the oil level and oil circulation of the compressor, and thus improving the operating reliability, efficiency and life of the compressor while ensuring the structural strength of the rotor assembly and the main bearing.

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

[0005] According to a first aspect embodiment of the compressor of this application, the compressor includes: a rotor assembly and a crankshaft, the rotor assembly having a first flow passage; the crankshaft is connected to the rotor assembly, and a main bearing is provided on the crankshaft, the main bearing having a second flow passage communicating with the first flow passage; wherein the first flow passage is configured as a plurality of holes arranged circumferentially around the axis of the crankshaft, the second flow passage is configured as a plurality of holes arranged axially around the crankshaft, the outer diameter of the first flow passage is D1 and the inner diameter is D2, the outer diameter of the second flow passage is D3 and the inner diameter is D4, and satisfies: 0.55≤D2*D3 / (D1*D4)≤0.95.

[0006] According to the compressor of this application, by optimizing the proportional relationship between the outer diameter of the first flow passage, the inner diameter of the first flow passage, the outer diameter of the second flow passage, and the inner diameter of the second flow passage, the relative radial position deviation range of the first flow passage on the rotor assembly and the second flow passage on the main bearing can be made reasonable. This enhances the flow effect while ensuring the structural rigidity and strength of the rotor assembly and the main bearing. As a result, while meeting the strength requirements of the main bearing and the rotor assembly, the compressor's oil level and oil circulation are effectively improved, thereby increasing the compressor's operational reliability, efficiency, and lifespan.

[0007] According to some embodiments of this application, 0.5 ≤ D2 / D1 ≤ 0.7.

[0008] According to some embodiments of this application, 0.7 ≤ D4 / D3 ≤ 0.9.

[0009] According to some embodiments of this application, the shortest distance between the rotor assembly and the main bearing is L, and satisfies: 20mm < D1 / D4*L < 32mm.

[0010] According to some embodiments of this application, the first flow passage is constructed as one or more of an oblong hole, a trapezoidal hole, or a circular hole.

[0011] According to a second aspect of this application, the refrigeration apparatus includes a compressor as described in any of the above embodiments.

[0012] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0013] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0014] Figure 1 This is a cross-sectional view of a compressor according to an embodiment of this application;

[0015] Figure 2 This is a cross-sectional view of the compressor portion structure according to an embodiment of this application;

[0016] Figure 3 This is a schematic diagram of the main bearing according to an embodiment of this application;

[0017] Figure 4 This is a schematic diagram of a rotor assembly according to an embodiment of the first aspect of this application;

[0018] Figure 5 This is a schematic diagram of a rotor assembly according to an embodiment of the second aspect of this application;

[0019] Figure 6 This is a schematic diagram of a rotor assembly according to an embodiment of a third aspect of this application.

[0020] Figure label:

[0021] 100. Compressor;

[0022] 10. Rotor assembly; 10a. First flow passage; 10b. Shaft hole;

[0023] 20. Crankshaft;

[0024] 30. Main bearing; 30a. Mounting hole; 30b. First oil groove;

[0025] 40. Piston; 50. Stator assembly; 60. Housing; 70. Cylinder; 80. Secondary bearing. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0027] Unless otherwise defined, all technical and scientific terms used in this application have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains; the terminology used in the description of this application is for the purpose of describing particular embodiments only and is not intended to limit the application; the terms "comprising" and "having," and any variations thereof, in the description, claims, and accompanying drawings of this application are intended to cover non-exclusive inclusion. The terms "first," "second," etc., in the description, claims, or accompanying drawings of this application are used to distinguish different objects, not to describe a specific order or hierarchy.

[0028] In this application, the reference to "embodiment" means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of this application. The appearance of this phrase in various places in the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment that is mutually exclusive with other embodiments.

[0029] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "attachment" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0030] In this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, in this application, the character " / " generally indicates that the preceding and following related objects have an "or" relationship.

[0031] In the embodiments of this application, the same reference numerals denote the same components, and for the sake of brevity, detailed descriptions of the same components are omitted in different embodiments. It should be understood that the thickness, length, width, and other dimensions of various components in the embodiments of this application shown in the accompanying drawings, as well as the overall thickness, length, width, and other dimensions of the integrated device, are merely illustrative and should not constitute any limitation on this application.

[0032] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0033] In the description of this application, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or the first and second features being in contact through another feature between them.

[0034] In the description of this application, the terms "above," "over," and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0035] In this application, "multiple" means two or more (including two).

[0036] The following is for reference. Figures 1-6This application describes a compressor 100 and a refrigeration device according to embodiments thereof.

[0037] like Figure 1 and Figure 2 As shown, according to a first aspect embodiment of the present application, the compressor 100 includes a rotor assembly 10 and a crankshaft 20.

[0038] The rotor assembly 10 has a first flow passage 10a; the crankshaft 20 is connected to the rotor assembly 10, and the crankshaft 20 is provided with a main bearing 30, which has a second flow passage communicating with the first flow passage 10a; the first flow passage 10a is constructed in a plurality of configurations arranged around the axis of the crankshaft 20 in the circumferential direction, and the second flow passage is constructed in a plurality of configurations arranged around the axis of the crankshaft 20 in the circumferential direction. The outer diameter of the first flow passage 10a is D1 and the inner diameter is D2, and the outer diameter of the second flow passage is D3 and the inner diameter is D4, and the following condition is met: 0.55≤D2*D3 / (D1*D4)≤0.95.

[0039] Specifically, the rotor assembly 10 may have a shaft hole 10b. At least a portion of the crankshaft 20 is connected to the rotor assembly 10 and housed within the shaft hole 10b. When the rotor assembly 10 is in operation, it can drive the crankshaft 20 to rotate. The crankshaft 20 can transmit rotational power to the connecting rod and piston 40 in the compressor 100, causing the connecting rod and piston 40 to reciprocate, thereby realizing the compression operation of the compressor 100. The rotor assembly 10 may have multiple first flow holes 10a. The first flow holes 10a can provide a channel for the flow of fluid (such as oil) in the rotor assembly 10, so as to guide the oil to circulate in the rotor assembly 10, thereby achieving good lubrication and cooling. Multiple first flow holes 10a are arranged circumferentially around the axis of the crankshaft 20 to improve the uniformity of oil distribution during rotor rotation. The multiple first flow holes 10a can be spaced apart or arranged in an array around the rotor assembly 10. At least another part of the main shaft section of the crankshaft 20 is provided with a main bearing 30. The main bearing 30 is sleeved on the crankshaft 20 and spaced apart from the rotor assembly 10 in the axial direction. The main bearing 30 can support the crankshaft 20. Multiple second flow holes can be formed on the main bearing 30. The second flow holes can provide channels for the flow of oil in the main bearing 30. Furthermore, the second flow holes are connected to the first flow holes 10a to form a preset oil flow path. The multiple second flow holes are arranged circumferentially around the axis of the crankshaft 20 to improve the uniformity of fluid distribution in the bearing.

[0040] It should be noted that the outer diameter of the first flow passage 10a on the rotor assembly 10 is D1 and the inner diameter of the first flow passage 10a is D2, and the outer diameter of the second flow passage on the main bearing 30 is D3 and the inner diameter of the second flow passage is D4. When the value of D2*D3 / (D1*D4) is too small or too large, for example, when the value of D2*D3 / (D1*D4) is set to 0.5, 0.4, 1, 1.2, etc., the radial deviation between the first flow hole 10a on the rotor assembly 10 and the second flow hole on the main bearing 30 will be too large, increasing the oil flow resistance, reducing the oil circulation efficiency and flow effect, thereby reducing the reliability and efficiency of the compressor 100. Furthermore, when the value of D2*D3 / (D1*D4) is too small or too large, the unreasonable arrangement of the first flow hole 10a and the second flow hole will also affect the structural strength and rigidity of the rotor assembly 10 and the bearing, thereby reducing the load-bearing capacity and stable operation of the rotor assembly 10 and the bearing, further aggravating the energy consumption and safety problems of the compressor 100. In this embodiment, the proportional relationship between the outer diameter D1 of the first flow passage 10a, the inner diameter D2 of the first flow passage 10a, the outer diameter D3 of the second flow passage, and the inner diameter D4 of the second flow passage is set within the range of 0.55 ≤ D2 * D3 / (D1 * D4) ≤ 0.95. For example, the value of D2 * D3 / (D1 * D4) can be constructed as 0.55, 0.6, 0.8, or 0.95, etc. In this way, the radial deviation between the positions of the first flow passage 10a and the second flow passage can be limited, so that the relative radial positions of the first flow passage 10a on the rotor assembly 10 and the second flow passage on the main bearing 30 are appropriate, thereby optimizing the oil flow path, improving the smoothness and efficiency of oil flow, and ensuring that the rotor assembly 10 and the main bearing 30 have good structural rigidity and strength.

[0041] According to the compressor 100 of this application, by optimizing the proportional relationship between the outer diameter of the first flow passage 10a, the inner diameter of the first flow passage 10a, the outer diameter of the second flow passage, and the inner diameter of the second flow passage, the relative radial position deviation range of the first flow passage 10a on the rotor assembly 10 and the second flow passage on the main bearing 30 can be made reasonable. This enhances the flow effect while ensuring the structural rigidity and strength of the rotor assembly 10 and the main bearing 30. As a result, while meeting the strength requirements of the main bearing 30 and the rotor assembly 10, the oil level and oil circulation of the compressor 100 are effectively improved, thereby increasing the operational reliability, efficiency, and lifespan of the compressor 100.

[0042] Furthermore, in some specific embodiments of this application, the crankshaft 20 includes a main shaft section, an eccentric section, and a secondary shaft section arranged axially away from the rotor assembly 10. The main shaft section is the main load-bearing part, at least a portion of which is connected to the rotor assembly 10, and at least another portion of which is connected to the main bearing 30. When the rotor assembly 10 is running, it can drive the main shaft section to rotate. The eccentric section can be arranged eccentrically relative to the center line of the main shaft section. The secondary shaft section further assists the main shaft section and the eccentric section in completing the power transmission so as to transmit the rotational power of the crankshaft 20 to the connecting rod and piston 40 in the compressor 100, so that the connecting rod and piston 40 can reciprocate.

[0043] like Figure 4 As shown, according to some embodiments of this application, 0.5 ≤ D2 / D1 ≤ 0.7.

[0044] Specifically, when the ratio of the inner diameter D2 to the outer diameter D1 of the first flow passage 10a is too small, for example, D2 / D1 is configured to be 0.4, 0.3, or 0.2, the area of ​​the first flow passage 10a on the rotor assembly 10 will be too large, thereby reducing the magnetic flux in the yoke of the rotor assembly 10 (i.e., the non-channel part of the rotor assembly 10) and causing a decrease in the uniformity of magnetic flux distribution, which in turn reduces the working efficiency and stability of the compressor 100. When the ratio of the inner diameter D2 to the outer diameter D1 of the first flow passage 10a is too large, for example, D2 / D1 is configured to be 0.75, 0.8, or 0.9, the area of ​​the first flow passage 10a will be too small, thereby increasing the resistance of oil flowing through the first flow passage 10a and causing poor oil flowability. The flow effect deteriorates, thereby reducing the cooling and lubrication effects of the rotor assembly 10. In this embodiment, the ratio of the inner diameter D2 of the first flow hole 10a to the outer diameter D1 of the first flow hole 10a is set in the range of 0.5 to 0.7. For example, the value of D2 / D1 can be 0.5, 0.6 or 0.7, etc., so that the ratio of the inner diameter of the first flow hole 10a to the outer diameter of the first flow hole 10a is reasonable. This can improve the smoothness of oil flow, improve the oil circulation path, and prevent the rotor assembly 10 from being too thin locally, which would lead to problems such as reduced magnetic flux and poor strength. This can ensure the sufficient supply and uniform distribution of key working media such as oil in the compressor 100, thereby ensuring the normal operation and high efficiency of the compressor 100, and ensuring the reliability and durability of the compressor 100.

[0045] like Figure 3 As shown, according to some embodiments of this application, 0.7 ≤ D4 / D3 ≤ 0.9.

[0046] Specifically, when the ratio of the inner diameter D4 to the outer diameter D3 of the second flow orifice is too small, for example, D4 / D3 is configured to be 0.6, 0.5, or 0.4, the area of ​​the second flow orifice on the main bearing 30 will be too large, severely weakening the structural strength and rigidity of the main bearing 30. This results in poor load-bearing capacity of the main bearing 30, making it unable to withstand the weight and rotational force of components such as the crankshaft 20 and the rotor assembly 10, thereby affecting the operational reliability of the crankshaft 20 and the rotor assembly 10. When the ratio of the inner diameter D4 to the outer diameter D3 of the second flow orifice is too large, for example, D4 / D3 is configured to be 0.93, 0.95, or 0. Similarly, a small area of ​​the second flow orifice will increase the resistance of the oil flowing through it, resulting in poor flowability and flow effect of the oil in the main bearing 30, and reducing the cooling and lubrication effects of the internal components of the compressor 100. In this embodiment, by setting the ratio of the inner diameter D4 of the second flow orifice to the outer diameter D3 of the second flow orifice in the range of 0.7 to 0.9, the ratio of the inner diameter to the outer diameter of the second flow orifice is reasonable, which can satisfy the main bearing 30 to have good flowability and structural strength, achieve a good balance between support strength and fluid flowability, and thus improve the efficiency, performance and life of the compressor 100.

[0047] Furthermore, in some specific embodiments of this application, the main bearing 30 has an axially penetrating mounting hole 30a, the crankshaft 20 passes through the mounting hole 30a to mate with the main bearing 30, the outer peripheral wall of the crankshaft 20 has a first oil hole, the main bearing 30 has a first oil groove 30b, and an oil storage cavity is formed between the outer peripheral wall of the crankshaft 20 and the inner wall of the mounting hole 30a of the main bearing 30 to connect the first oil hole and the first oil groove 30b. During the operation of the compressor 100, oil can flow to the first oil hole on the crankshaft 20, and the first oil hole and the first oil groove 30b are connected through the oil storage cavity, so that oil can flow from the first oil hole to the first oil groove 30b. The first oil groove 30b can guide and store the oil, thus ensuring the oil supply to the friction pair formed by the crankshaft 20 and the main bearing 30, effectively reducing frictional power consumption, and thereby improving the energy efficiency and reliability of the compressor 100.

[0048] like Figure 2 As shown, according to some embodiments of this application, the shortest distance between the rotor assembly 10 and the main bearing 30 is L, and satisfies: 20mm < D1 / D4*L < 32mm.

[0049] Specifically, the shortest distance L between the rotor assembly 10 and the main bearing 30 can be understood as the shortest distance between the first flow passage 10a on the rotor assembly 10 and the second flow passage on the main bearing 30. By setting the dimensional relationship between the outer diameter D1 of the first flow passage 10a, the inner diameter D4 of the second flow passage, and the shortest distance L between the rotor assembly 10 and the main bearing 30 within the above range, for example, D1 / D4*L can be set to 24mm, 28mm, or 30mm, etc., so that the dimensional relationship between the outer diameter of the first flow passage 10a, the inner diameter of the second flow passage, and the distance between the two flow passages can be set within a suitable range. This effectively controls the circulation path of the oil inside the compressor 100, ensures that the oil fully lubricates each component, and avoids excessively long paths that could lead to oil surface fluctuations and increased flow resistance. In this way, the maximum flow effect of the flow path can be ensured, which helps to optimize the oil circulation efficiency of the entire compressor 100.

[0050] like Figures 4-6 As shown, according to some embodiments of this application, the first flow hole 10a is constructed as one or more of an oblong hole, a trapezoidal hole, or a circular hole.

[0051] Specifically, the outer contours (i.e., the projected contours in the axial direction of the rotor assembly 10) of the plurality of first flow passages 10a on the rotor assembly 10 can be identical. For example, the outer contours of the plurality of first flow passages 10a can all be constructed as an oblong shape as shown in Figure 4, where the oblong shape can be understood as approximately elliptical. The outer contours of the plurality of first flow passages 10a can also all be constructed as trapezoids as shown in Figure 5, where the trapezoid shape can be understood as approximately trapezoidal, not an absolute trapezoidal shape. Furthermore, the outer contours of the plurality of first flow passages 10a can all be constructed as... Figure 6 The circular shape shown; the outer contours of the plurality of first flow holes 10a may also be different. The outer contours of the plurality of first flow holes 10a may include a variety of shapes such as circular, waist-shaped and trapezoidal. For example, at least a portion of the outer contours of the first flow holes 10a may be constructed as circular, and at least another portion of the outer contours of the first flow holes 10a may be constructed as waist-shaped or trapezoidal, etc.

[0052] Among them, the circular orifice has good hydrodynamic performance, which can reduce fluid flow resistance and allow fluid to pass through with minimal energy loss, ensuring sufficient fluid flow in the rotor assembly 10 while reducing heat accumulation caused by fluid resistance. The oblong orifice can provide a relatively large flow area, which helps to improve efficiency in applications requiring directional fluid flow. For example, when enhanced cooling in a specific direction is needed, the oblong orifice can more effectively guide fluid flow, ensuring that the rotor assembly 10 receives sufficient cooling in that direction. The trapezoidal orifice can provide a more uniform fluid flow pattern under certain specific fluid distribution requirements, improving the uniformity of oil distribution. By combining the use of first flow orifices 10a of different shapes, uniform fluid distribution can be achieved on the rotor assembly 10, and the direction and speed of fluid flow can be adjusted as needed, which helps to ensure that all areas around the rotor assembly 10 receive sufficient fluid support. Therefore, by constructing the first flow passage 10a as one or more of the following: waist-shaped, trapezoidal, or circular, optimization can be achieved in terms of fluid dynamics efficiency, fluid distribution uniformity, and design flexibility, ensuring good flow performance and flow effect of the rotor assembly 10, and improving the overall performance and energy efficiency of the compressor 100.

[0053] It should be noted that the above-mentioned waist-shaped hole, trapezoidal hole and circular hole are exemplary descriptions. The first flow hole 10a according to this application can be constructed as one or more of waist-shaped hole, trapezoidal hole or circular hole. For example, in some other specific embodiments, the first flow hole 10a can also be constructed as a rectangular hole, etc. Rectangular holes can be relatively easily aligned with other rectangular or straight structures in the compressor 100, which is beneficial to improving manufacturing convenience and saving production costs.

[0054] In addition, such as Figure 1As shown, in some specific embodiments of this application, the compressor 100 further includes: a stator assembly 50, a housing 60, a cylinder 70, and a secondary bearing 80. The stator assembly 50 is fitted outside the rotor assembly 10, and the housing 60 is fitted outside the stator assembly 50. The stator assembly 50 can generate a magnetic field through electromagnetic induction. The magnetic field generated by the rotor assembly 10 and the stator assembly 50 can cooperate to generate electromagnetic torque, thereby driving the crankshaft 20 to rotate. The housing 60 is fitted outside the stator assembly 50 and the rotor assembly 10, and can play a good role in fixing and protecting the stator assembly 50, the rotor assembly 10, the crankshaft 20, and other components inside the compressor 100. The cylinder 70 and the auxiliary bearing 80 are both fitted around the outer periphery of the crankshaft 20. The cylinder 70 is located on the side of the main bearing 30 that is axially away from the rotor assembly 10, and the auxiliary bearing 80 is located on the side of the cylinder 70 that is axially away from the main bearing 30. The auxiliary bearing 80 and the main bearing 30 can support the crankshaft 20 at different positions and reduce friction and wear during rotation, which helps to improve the smooth operation of the compressor 100. A piston 40 is installed inside the cylinder 70. The piston 40 is connected to the crankshaft 20. The rotation of the crankshaft 20 can drive the piston 40 to reciprocate within the cylinder 70, thereby ensuring that the compression work of the compressor 100 is effectively completed and saving energy.

[0055] like Figures 1-6 As shown, the refrigeration device according to the second aspect of this application includes: the compressor 100 as described in any of the above embodiments, and the resulting technical effects are the same as those in the above embodiments, and will not be repeated here.

[0056] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0057] Although embodiments of this application have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the claims and their equivalents.

Claims

1. A compressor, characterized in that, include: A rotor assembly, wherein a first flow passage is provided on the rotor assembly; A crankshaft is connected to the rotor assembly, and a main bearing is provided on the crankshaft. The main bearing has a second flow hole communicating with the first flow hole. The first flow passage is constructed as a plurality of holes arranged circumferentially around the axis of the crankshaft, and the second flow passage is constructed as a plurality of holes arranged circumferentially around the axis of the crankshaft. The outer diameter of the first flow passage is D1 and the inner diameter is D2, and the outer diameter of the second flow passage is D3 and the inner diameter is D4, and satisfies: 0.55≤D2*D3 / (D1*D4)≤0.

95.

2. The compressor according to claim 1, characterized in that, 0.5≤D2 / D1≤0.

7.

3. The compressor according to claim 1, characterized in that, 0.7≤D4 / D3≤0.

9.

4. The compressor according to claim 1, characterized in that, The shortest distance between the rotor assembly and the main bearing is L, and satisfies: 20mm < D1 / D4*L < 32mm.

5. The compressor according to any one of claims 1-4, characterized in that, The first flow passage is constructed as one or more of the following: a waist-shaped hole, a trapezoidal hole, or a circular hole.

6. A refrigeration device, characterized in that, include: The compressor according to any one of claims 1-5.

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