Crankshaft assembly and compressor

Abstract

The invention relates to the technical field of compressors, in particular to a crankshaft assembly and a compressor. The crankshaft assembly includes: a crankshaft extending in a first direction, the crankshaft having an upper end and a lower end in the first direction; the eccentric part is arranged on the crankshaft, a balance groove is formed in the upper end face, facing the upper end, of the eccentric part, and the balance groove is formed along the circumferential edge of the eccentric part; and the balance part is arranged in the balance groove, and the balance part moves in the balance groove in the process that the eccentric part rotates along with the rotation of the crankshaft. According to the crankshaft, the balance groove in the eccentric part is matched with the balance piece, so that when the eccentric part rotates at a high speed along with the crankshaft, the balance piece generates component force opposite to the moving direction of the mass center of the eccentric part, and part of unbalance amount caused by eccentricity is compensated.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and more specifically, to a crankshaft assembly and a compressor. Background Technology

[0002] Currently, compressors are trending towards miniaturization and high frequency, with new product development focusing on expanding from small displacement to large displacement and from low energy efficiency to high energy efficiency. By reducing the material costs of compressors, the core competitiveness of air conditioning products in domestic and international markets can be improved.

[0003] In related technologies, the compressor pump body structure comprises a cylinder, a rolling piston, a crankshaft, vanes, springs, and flanges mounted at both ends of the cylinder. Due to the eccentric portion on the crankshaft, severe crankshaft deflection occurs when the crankshaft rotates at high speeds. To reduce crankshaft deflection, balance weights are fixedly installed on the crankshaft body or piston; however, this arrangement affects crankshaft rotation, increases friction losses, and reduces compression efficiency. Summary of the Invention

[0004] In view of this, this application provides a crankshaft assembly and a compressor to solve the problem of eccentricity generated during crankshaft assembly rotation while ensuring compression efficiency.

[0005] In a first aspect, this application provides a crankshaft assembly, comprising: a crankshaft extending along a first direction, the crankshaft having an upper end and a lower end along the first direction; an eccentric portion disposed on the crankshaft, the eccentric portion having a balancing groove formed on its upper end face facing the upper end, the balancing groove being disposed along the circumferential edge of the eccentric portion; and a balancing member disposed within the balancing groove, wherein the balancing member moves within the balancing groove as the eccentric portion rotates with the crankshaft.

[0006] By adopting the above technical solution, the weight and rotational inertia of the crankshaft assembly can be reduced by the cooperation of the balance groove and balance component set on the eccentric part. As the eccentric part rotates at high speed with the crankshaft, the balance component generates a component force opposite to the direction of movement of the center of mass of the eccentric part, so as to compensate for part of the imbalance caused by the eccentricity. This allows the compressor to maintain a lower vibration level and operating noise, thereby reducing crankshaft wear, extending service life and improving operational stability.

[0007] In an optional embodiment of the crankshaft assembly described above, the eccentric portion has a geometric center offset from the rotation center of the crankshaft assembly by a predetermined distance. The eccentric portion has a first edge portion located on the side of the geometric center away from the rotation center, and the balance groove is provided at least along the first edge portion. In another optional embodiment of the crankshaft assembly described above, the balance groove is an arc-shaped groove, the center of curvature of the extension trajectory of the balance groove coincides with the geometric center of the eccentric portion, and the balance groove is configured such that the balancing member moves within the balance groove along the extension direction of the balance groove.

[0008] In an optional embodiment of the crankshaft assembly described above, the central angle corresponding to the arc of the balance groove is greater than or equal to 120° and less than or equal to 270°.

[0009] In an optional embodiment of the crankshaft assembly described above, the balancer is spherical or cylindrical.

[0010] In an optional embodiment of the crankshaft assembly described above, the density of the balancer is greater than the density of the crankshaft.

[0011] In an optional embodiment of the crankshaft assembly described above, a lubricating medium is provided on the inner wall of the balance groove.

[0012] In an optional embodiment of the crankshaft assembly described above, the crankshaft has an oil guide channel extending along its own axial direction inside; the balance groove is provided with a plurality of oil guide holes distributed circumferentially, the oil guide holes communicating with the oil guide channel, and the oil guide channel being used to introduce lubricating oil into the balance groove through the oil guide holes during operation.

[0013] In an optional embodiment of the crankshaft assembly described above, the distance between the eccentric portion and the upper end is greater than the distance between the eccentric portion and the lower end, and the depth of the balance groove is greater than the height of the balance component.

[0014] Secondly, this application provides a compressor, comprising: a housing having a compression chamber therein; a rolling piston disposed in the compression chamber; and a crankshaft assembly as described above, wherein an eccentric portion of the crankshaft assembly is disposed within the rolling piston, the eccentric portion being configured to drive the rolling piston to roll.

[0015] By adopting the above technical solution, the weight and rotational inertia of the crankshaft assembly can be reduced by the cooperation of the balance groove and balance component set on the eccentric part. As the eccentric part rotates at high speed with the crankshaft, the balance component generates a centrifugal force component that is opposite to the direction of movement of the center of mass of the eccentric part. This compensates for part of the imbalance caused by the eccentricity, thereby enabling the compressor to maintain a lower vibration level and operating noise, which in turn reduces crankshaft wear, extends service life and improves operational stability. Attached Figure Description

[0016] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this application, illustrate exemplary embodiments of the invention and, together with their description, serve to explain the invention and do not constitute an undue limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the structure of a crankshaft assembly provided in this application; Figure 2 This is a cross-sectional schematic diagram of a crankshaft assembly provided in this application; Figure 3 This is a schematic diagram of another crankshaft assembly provided in this application; Figure 4 This is a cross-sectional schematic diagram of another crankshaft assembly provided in this application; Figure 5 This is a schematic diagram of the balancing principle of a balancing component provided in this application, where ω < ω n ; Figure 6 This is a schematic diagram of the balancing principle of another balancing component provided in this application, where ω>ω n ; Figure 7 This is a schematic diagram of a balancing component provided in this application when it is in a balanced state; Figure 8 This is a force diagram of a balancing component provided in this application; Figure 9 This is a cross-sectional schematic diagram of a compressor provided in this application.

[0017] Figure label: 10. Housing; 20. Rolling piston; 30. Rotor; 31. Stator; 41. Upper bearing; 42. Lower bearing; 50. Cylinder; 100, Crankshaft; 101, Oil guide channel; 110, Long shaft section; 120, Short shaft section; 200, Eccentric section; 201, First edge section; 210, Balance groove; 211, Oil guide hole; 300, Balance component. Detailed Implementation

[0018] The following specific embodiments illustrate the implementation of this application. Those skilled in the art can easily understand other advantages and effects of this application from the content disclosed in this specification. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0019] The terminology used in the embodiments of this application is for the purpose of describing particular embodiments only and is not intended to limit the application. The singular forms “a,” “said,” and “the” used in the embodiments of this application and the appended claims are also intended to include the plural forms, unless the context clearly indicates otherwise. “Multiple” generally includes at least two, but does not exclude the inclusion of at least one.

[0020] It should be understood that the term "and / or" used in this article 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, and B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0021] It should also be noted that the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a product or system comprising a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a product or system. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the product or system that includes said element.

[0022] The embodiments of this application are described in detail below. Examples of the embodiments are shown in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this application, but should not be construed as limiting this application.

[0023] As mentioned in the background, compressors are trending towards miniaturization and higher frequency operation. New product development is focused on covering a range from small to large displacements and from low to high energy efficiency, aiming to improve the core competitiveness of air conditioning products in domestic and international markets by reducing compressor material costs. The compressor in this related technology comprises a cylinder, rolling piston, crankshaft, vanes, springs, and flanges mounted at both ends of the cylinder. Due to the eccentricity of the crankshaft, severe crankshaft deflection occurs when it rotates at high speeds. To reduce crankshaft deflection, balance weights are fixed on the crankshaft body or piston; however, this arrangement affects crankshaft rotation, increases friction losses, and reduces compression efficiency.

[0024] To address the issue of eccentricity generated during crankshaft assembly rotation, this disclosure provides a crankshaft assembly that generates a centrifugal force component that moves in the opposite direction to the center of mass of the eccentric portion during crankshaft rotation, thereby automatically balancing the crankshaft's imbalance.

[0025] Firstly, combining Figures 1 to 9As shown, this application provides a crankshaft assembly, including a crankshaft 100, an eccentric portion 200, and a balancing component 300.

[0026] A crankshaft 100 extends along a first direction and has an upper end and a lower end along the first direction. An eccentric portion 200 is disposed on the crankshaft 100, and a balancing groove 210 is formed on the upper end surface of the eccentric portion 200 facing the upper end. The balancing groove 210 is disposed along the circumferential edge of the eccentric portion 200. A balancing member 300 is disposed within the balancing groove 210, and moves within the balancing groove 210 as the eccentric portion 200 rotates with the crankshaft 100.

[0027] The crankshaft assembly in this application is used in a compressor. Specifically, the compressor includes a housing 10, and a compression chamber is formed inside the housing 10. A rolling piston is disposed in the compression chamber and is connected to an eccentric portion 200. Thus, when the crankshaft 100 rotates, the rotation of the eccentric portion 200 drives the rolling piston to run, thereby compressing the refrigerant.

[0028] Optionally, a rotor is provided on the long shaft portion 110. A stator is provided inside the housing 10, which enables the rotor to rotate when the stator is energized. Furthermore, driven by the rotor, the long shaft portion 110 rotates around its own axis.

[0029] Optionally, the eccentric portion 200 is sleeved on the crankshaft 100, or the eccentric portion 200 is integrally formed on the crankshaft 100. A balance groove 210 is provided on the upper surface of the eccentric portion 200 facing upwards. The balance groove 210 reduces the mass of the eccentric portion 200 itself, thereby reducing the imbalance generated when the eccentric portion 200 rotates and improving the stability of the crankshaft assembly during operation.

[0030] Furthermore, the balancing groove 210 extends along the circumferential edge of the eccentric portion 200. A balancing element 300 is disposed within the balancing groove 210. Specifically, when the crankshaft 100 rotates, due to inertial forces, the crankshaft 100 exhibits two motion tendencies: one is the rotation of the shaft after dynamic deflection; the other is the rotation of the eccentric portion 200 on the crankshaft 100 around the crankshaft. During this process, the motion force of the balancing element 300 generates a component force, causing the direction of movement of the center of mass of the balancing element 300 to be opposite to the direction of movement of the center of mass of the eccentric portion 200. This counteracts a portion of the imbalance caused by eccentricity, thereby reducing the eccentricity. In this way, it can compensate for a portion of the imbalance generated during rotation due to the eccentricity of the eccentric portion, thereby reducing vibration and vibration noise, and also reducing crankshaft wear.

[0031] Specifically, the projection of the crankshaft 100's axis onto the reference plane is point O, the projection of the geometric center of the eccentric part 200 onto the reference plane is O1, and the projection of the center of mass of the eccentric part 200 onto the reference plane is point G. It should be noted that the cross-sectional shape of the eccentric part 200 is usually a regular shape, such as a circle or an ellipse. Therefore, the geometric center of the eccentric part 200 can be understood as the center of its cross-sectional shape. For example, if the cross-sectional shape of the eccentric part 200 is circular, then the geometric center of the eccentric part 200 is the center of that circle. The distance between point O and point O1 is r, and the eccentricity of the crankshaft is e; where, The rotational angular frequency of crankshaft 100 is ω, and the natural frequency of crankshaft 100 itself is ω. n ω is greater than ω n When the balancer 300 moves along the extension direction of the lower edge of the balance groove 210, it generates a centrifugal force component opposite to the direction of the center of mass movement of the eccentric part 200, so as to dynamically compensate for the eccentricity of the eccentric part 200 and reduce the eccentricity e. The reference plane is a plane perpendicular to the axis of the crankshaft 100.

[0032] When crankshaft 100 rotates at angular frequency ω, the inertial force generated by the mass eccentricity causes dynamic deflection, which manifests as synchronous rotation of geometric center O1 around rotation center O with radius r, i.e., deflection r. The motion characteristics of balancer 300 are determined by the frequency ratio ω / ω n Decision, in which ω n It is the natural frequency of the crankshaft. ω n = K is the crankshaft stiffness, and M is the equivalent mass.

[0033] Furthermore, a coordinate system is established in the reference plane with the rotation center point O as the origin. The distance OO1 is r, which is the deflection. The distance O1G is e, which is the eccentricity. Wherein, if the coordinates of point O1 are (x, y), then the coordinates of point G are (...). , The crankshaft has a stiffness of K in both the x and y directions. Therefore, the equation of motion for point G is:

[0034] Furthermore, it can be calculated that:

[0035] Furthermore, we can deduce that the distance to OO1 is r, i.e. .

[0036] When (ω / ω) n When (ω / ω) > 1, r < 0. This indicates that the deflection r is opposite to the eccentricity e, and the position of the center of mass G falls between OO and 1. nAs the value approaches infinity, r approaches -e, at which point point G on the surface coincides with point O. Point G coincides with point O, and point O1 continues to rotate around point O. That is, during the rotation of the eccentric part 200, the center of mass G moves closer to the center of rotation O. At this time, the balancing member 300, located in the balancing groove 210 of the eccentric part 200, begins to move freely. The center of mass of the balancing member 300 automatically finds the opposite position of the current combined center of mass of the system composed of the crankshaft 100 and the balancing member 300.

[0037] like Figure 6 As shown, the motion force F of the balancer 300 will generate a component force F along the OO1 direction. t Component force F t The direction of movement of the center of mass G of the eccentric part 200 is always opposite to the direction of movement of the center of mass G of the eccentric part 200. That is to say, the direction of movement of the center of mass of the balancing component 300 is opposite to the direction of movement of the center of mass G of the eccentric part 200, thereby compensating for part of the imbalance caused by the eccentricity, making the initial eccentricity O1G smaller. Since the effective eccentricity e of the system composed of crankshaft 100 and balancing component 300 is reduced, according to the dynamic equation, the reduction of eccentricity e will directly reduce the dynamic deflection r. Finally, the overall center of mass of the system composed of crankshaft 100 and balancing component 300 will be gradually corrected to the geometric center O1, thereby achieving the purpose of balancing the eccentric part 200.

[0038] Combination Figure 7 As shown, the eccentric force generated by the crankshaft system's motion is: F e =M1ω 2 e; Tangential force generated by the balance sphere: F t =mω 2 R*cosθ.

[0039] Where m is the mass of the balancing component 300, M1 is the mass of the crankshaft eccentric part, e is the eccentricity, and θ is the distance between F and F. t The included angle, R is the distance between the balancing component 300 and the center of rotation.

[0040] When the balance frame 300 is balanced, F e =F t, That is, M1ω 2 e=mω 2 R*cosθ, therefore, m / M1=e / R*cosθ. Since the ratio of R to e is set to approximately 10 / 1, the optimal range for the mass m of the balancing component 300 is between 0.1M1 and 0.2M1.

[0041] By adopting the above technical solution, the weight and rotational inertia of the crankshaft assembly can be reduced by the cooperation of the balance groove and balance component set on the eccentric part. As the eccentric part rotates at high speed with the crankshaft, the balance component generates a component force opposite to the direction of movement of the center of mass of the eccentric part, so as to compensate for part of the imbalance caused by the eccentricity. This allows the compressor to maintain a lower vibration level and operating noise, thereby reducing crankshaft wear, extending service life and improving operational stability.

[0042] In an optional embodiment of the crankshaft assembly described above, the eccentric portion 200 has a geometric center that is offset from the rotation center of the crankshaft assembly by a predetermined distance. The eccentric portion 200 has a first edge portion 201 located on the side of the geometric center away from the rotation center, and the balance groove 210 is provided at least along the first edge portion 201.

[0043] The first edge portion 201 is the part of the eccentric portion 200 that mainly forms the eccentricity. By setting the balance groove 210 on the first edge portion 201, the component force generated by the balance member 300 can be used more effectively to compensate for the imbalance caused by the eccentricity of the eccentric portion 200 during the high-speed rotation of the crankshaft. Because the first edge portion 201 has a larger mass, its eccentricity effect is more pronounced. By setting the balance groove 210 on the first edge portion 201, when the crankshaft 100 rotates, the balance member 300 moves along the extension direction of the balance groove 210, which can better dynamically balance the larger eccentricity generated by the first edge portion 201. This makes the direction of movement of the center of mass of the balance member 300 opposite to the direction of movement of the center of mass of the eccentric portion 200, thereby reducing the eccentricity and lowering the effective eccentricity of the system composed of the crankshaft 100 and the balance member 300. According to the dynamic equation, the reduction of the effective eccentricity will reduce the dynamic deflection. Ultimately, the overall center of mass of the system composed of the crankshaft 100 and the balance member 300 will be gradually corrected to a suitable position, achieving a better balance of the eccentric portion 200, improving the stability of the crankshaft assembly during operation, reducing vibration and noise, reducing wear of the crankshaft 100, and extending its service life.

[0044] In an optional embodiment of the crankshaft assembly described above, the balance groove 210 is an arc-shaped groove, the curvature center of the extension trajectory of the balance groove 210 coincides with the geometric center of the eccentric portion 200, and the balance groove 210 is configured such that the balance member 300 moves within the balance groove 210 along the extension direction of the balance groove 210.

[0045] In this design, by setting the balance groove 210 as an arc-shaped groove, with its center of curvature coinciding with the geometric center of the eccentric portion 200, it is ensured that when the balance member 300 moves along the extension direction of the balance groove 210, the trajectory of its center of mass is opposite to the direction of the center of mass offset of the eccentric portion 200. This ensures that the component force generated by the balance member 300 is always opposite to the direction of the inertial force caused by the eccentric mass, thus creating a dynamic balance effect. Specifically, when the crankshaft 100's rotational speed exceeds its natural frequency, the balance member 300 moves along the extension direction of the arc-shaped groove, and its center of mass position automatically adjusts to a position symmetrical to the center of mass of the eccentric portion 200. By continuously generating a counter-compensating force, it compensates for the imbalance caused by the eccentricity, thereby improving the smoothness and reliability of the compressor's operation.

[0046] Optionally, the width of the balancing groove 210 is greater than the width of the balancing component 300, but less than twice the width of the balancing component 300. This ensures that the balancing component 300 has sufficient room to move within the balancing groove 210 to meet the dynamic balancing requirements of the crankshaft 100 at different speeds, while also preventing the balancing component 300 from excessively shaking or getting stuck within the balancing groove 210.

[0047] When the crankshaft 100 rotates at high speed, the balancer 300 moves along the balance groove 210, and its range of movement is limited by the width of the balance groove 210. If the width of the balance groove 210 is too small, the balancer 300 may not be able to move freely to the appropriate position to generate sufficient counter-compensation force; while if the width of the balance groove 210 is too large, the balancer 300 may tilt or deviate from the expected trajectory during movement, affecting the balancing effect. Therefore, setting the width of the balance groove 210 within a range greater than the width of the balancer 300 but less than twice the width of the balancer 300 ensures that the balancer 300 moves stably and effectively within the balance groove 210, thereby achieving the best dynamic balancing effect, further improving the stability of the crankshaft assembly during operation, reducing vibration and noise, reducing wear on the crankshaft 100, and extending the service life of the compressor.

[0048] Optionally, the extension length of the balancing groove 210 from its upper end face to its lower end face is greater than the height or diameter of the balancing component 300. This ensures that the balancing component 300 has sufficient space to move freely within the balancing groove 210, responding to the unbalanced force generated by the rotation of the eccentric part 200, and promptly adjusting its position to generate a counter-compensating force, thus achieving effective dynamic balance. Furthermore, it provides a more stable installation space for the balancing component 300, making it less likely to derail when moving within the balancing groove 210, ensuring the stability of the dynamic balance effect. Alternatively, the extension length of the balancing groove 210 from its upper end face to its lower end face is greater than the height or diameter of the balancing component 300, and at least greater than half the height or half the diameter of the balancing component 300. This reduces the weight of the eccentric part 200, mitigating the initial imbalance caused by the mass of the eccentric part 200 itself, and also helps reduce material costs.

[0049] Optionally, the balancing groove 210 is configured in a wave shape along the circumference of the eccentric portion 200. Alternatively, the balancing groove 210 is configured in a V-shape.

[0050] Optionally, the extension length of the balancing groove 210 along its upper and lower surfaces can be uniform or non-uniform. If uniform, the manufacturing process is relatively simple, ensuring structural consistency throughout the balancing groove 210 and making the movement of the balancing component 210 within it more stable. If non-uniform, different thicknesses can be specifically set according to the stress and balancing requirements at different locations of the eccentric part. Specifically, a longer extension length is set in areas where the eccentric part 200 experiences greater stress or requires more precise balancing to enhance the balancing ability of that area, while a shorter extension length is set in areas where the stress is less or the balancing requirement is relatively lower to optimize the overall structure and reduce weight.

[0051] In an optional embodiment of the crankshaft assembly described above, the central angle corresponding to the arc of the balance groove 210 is greater than or equal to 120° and less than or equal to 270°.

[0052] In this design, the eccentric part 200 and the balance groove 210 are arranged coaxially.

[0053] By setting the central angle of the arc corresponding to the balancing groove 210 to be greater than or equal to 120° and less than or equal to 270°, it can be ensured that the balancing component 300 has sufficient movement space during the rotation of the crankshaft 100 to generate a centrifugal force component opposite to the direction of the center of mass movement of the eccentric part 200. Specifically, if the central angle is too small, the movement range of the balancing component 300 is limited, which may not be able to fully compensate for the imbalance caused by eccentricity; while if the central angle is too large, although the movement space of the balancing component 300 increases, it may lead to a decrease in the structural strength of the balancing groove 210, affecting the overall stability of the eccentric part 200. Therefore, setting the central angle between 120° and 270° can provide a suitable movement range for the balancing component 300 while ensuring the structural strength of the balancing groove 210, thereby achieving effective dynamic balance.

[0054] Preferably, the central angle corresponding to the arc of the balance groove 210 is 180°. This design allows the balance component 300 to move semi-circularly within the balance groove 210 when the crankshaft 100 rotates. This ensures that the balance component 300 has sufficient space to generate a centrifugal force component opposite to the direction of the center of mass movement of the eccentric part 200, while avoiding the problem of reduced structural strength of the balance groove 210 due to an excessively large central angle. Simultaneously, the 180° central angle design simplifies the machining of the balance groove 210, reducing production costs. In practical applications, this design significantly improves the stability of the crankshaft assembly during operation, reduces vibration and noise, reduces wear on the crankshaft 100, and thus extends the service life of the crankshaft assembly.

[0055] In addition, this arrangement can adapt to the speed changes of crankshaft 100 under different operating conditions, ensuring that the compressor can maintain a low vibration level and operating noise under various operating conditions, and extending the service life of the crankshaft assembly.

[0056] In an optional embodiment of the crankshaft assembly described above, the balancer 300 is spherical or cylindrical.

[0057] Specifically, when the balancer 300 is spherical, it is set to be a smooth sphere. When it moves in the balance groove 210, the friction force it experiences is relatively small. It can adjust its position more flexibly to quickly respond to the unbalanced force generated when the eccentric part 200 rotates, thereby more effectively generating a centrifugal force component that is opposite to the direction of the center of mass movement of the eccentric part 200, and better achieving the dynamic balance effect.

[0058] In addition, the spherical balance component 300 is subjected to relatively uniform force in all directions, and can maintain a relatively stable motion state under different speeds and operating conditions, which is conducive to improving the smoothness of the entire crankshaft assembly.

[0059] When the balancing component 300 is cylindrical, it has a certain length, providing a relatively large contact area when mating with the balancing groove 210. This enhances the interaction force between the balancing component 300 and the balancing groove 210, making the movement of the balancing component 300 within the balancing groove 210 more stable and reliable. The cylindrical balancing component 300 can be designed with different diameters and lengths according to actual needs to adapt to different specifications of the eccentric part 200 and the balancing groove 210, thus possessing a certain degree of flexibility and versatility.

[0060] In addition, the cylindrical balance component 300 is relatively easy to manufacture with guaranteed dimensional accuracy, which is beneficial for controlling product quality, thereby ensuring the stability of dynamic balance effect, reducing vibration and noise during crankshaft assembly operation, reducing crankshaft 100 wear, and improving the overall performance and service life of the compressor.

[0061] Alternatively, the balancer 300 may also be in other shapes that facilitate rolling or running within the balancer groove 210.

[0062] In an optional embodiment of the crankshaft assembly described above, the density of the balancer 300 is greater than the density of the crankshaft 100.

[0063] Furthermore, the density of the balancing component 300 is greater than the density of the eccentric part 200.

[0064] This ensures that the counter-compensation force generated by the balancer 300 under centrifugal force is more significant during the rotation of the crankshaft 100. Because higher density results in greater mass for the same volume, according to dynamic principles, a massless object generates a greater centrifugal force at the same angular velocity. Therefore, when the crankshaft 100 rotates and the eccentric part 200 causes eccentric motion leading to imbalance, the denser balancer 300 can more effectively generate a centrifugal force component opposite to the direction of the center of mass movement of the eccentric part 200 under centrifugal force. This more quickly and fully compensates for the imbalance caused by the eccentricity, thereby more effectively reducing the effective eccentricity of the system composed of the crankshaft 100 and the balancer 300. Specifically, according to the dynamic equation, the reduction of effective eccentricity will reduce dynamic deflection, and eventually the overall center of mass of the system composed of crankshaft 100 and balance component 300 will be gradually corrected to a suitable position, which will greatly improve the stability of crankshaft assembly during operation, effectively reduce vibration and noise, reduce wear of crankshaft 100, extend the overall service life of crankshaft assembly and compressor, improve the smoothness and reliability of compressor operation, adapt to the speed change of crankshaft 100 under different operating conditions, and ensure that the compressor can maintain good performance under various operating conditions.

[0065] Alternatively, the density of the balance component 300 is equal to the density of the crankshaft 100 / eccentric portion 200. Specifically, the balance component 300 is made of the same material as the crankshaft 100 / eccentric portion 200.

[0066] In an optional embodiment of the crankshaft assembly described above, a lubricating medium is provided on the inner wall of the balance groove 210.

[0067] By providing a lubricating medium on the inner wall of the balance groove 210, the frictional force experienced by the balance component 300 during its movement within the balance groove 210 can be effectively reduced, resulting in smoother movement of the balance component 300. This not only helps the balance component 300 respond more quickly to the unbalanced force generated by the rotation of the eccentric part 200 and adjust its position in time to generate a counter-compensating force, but also reduces the heat generated by friction, reduces the wear of the balance component 300 and the balance groove 210, and extends their service life. Simultaneously, the presence of the lubricating medium can reduce noise generation to some extent, making the crankshaft assembly quieter during operation and improving the overall operating quality of the compressor system.

[0068] In addition, a suitable lubricating medium can form a stable lubricating film between the inner wall of the balance groove 210 and the balance component 300, ensuring that the balance component 300 can maintain a good motion state under different speeds and operating conditions, further improving the smoothness and reliability of the crankshaft assembly operation.

[0069] Alternatively, the lubricating medium can be lubricating oil or lubricating grease.

[0070] If the lubricating medium is lubricating oil, it has good fluidity and can quickly form a uniform oil film between the inner wall of the balance groove 210 and the balance component 300, effectively reducing frictional resistance and making the movement of the balance component 300 more flexible and free. Moreover, the lubricating oil can also carry away some of the heat generated by friction during circulation, playing a certain cooling role and further protecting the balance component 300 and the balance groove 210.

[0071] Specifically, the lubricating oil is exactly the same as the lubricating oil circulating within the compressor system. This includes ester-based lubricating oils, ether-based lubricating oils, alkylbenzene glycerols, etc. Furthermore, the specific type selected is matched to the refrigerant used in the compressor.

[0072] If the lubricating medium is grease, it has good adhesion and can form a durable lubricating film on the inner wall of the balance groove 210 and the surface of the balance component 300. Even under high temperature and heavy load conditions, it can maintain good lubrication, reducing wear and noise. At the same time, compared to lubricating oil, grease has a lower risk of leakage and can maintain lubrication for a longer period, reducing maintenance costs. Depending on different operating environments and conditions, a suitable lubricating medium can be selected to optimize the performance of the crankshaft assembly.

[0073] Specifically, greases include calcium-based greases, lithium-based greases, etc. For example, lithium-based greases have good mechanical stability, oxidation stability, and rust prevention, can be used over a wide temperature range, and are suitable for the lubrication needs of most crankshaft components. Furthermore, the appropriate grease can be selected based on the specific operating conditions and requirements of the crankshaft component.

[0074] In the optional implementation of the crankshaft assembly described above, combined with Figure 4 As shown, the crankshaft 100 has an oil guide channel 101 extending along its own axial direction inside; the balance groove 210 has a plurality of oil guide holes 211 spaced apart along its own circumference. The oil guide holes 211 are connected to the oil guide channel 101. The oil guide channel 101 is used to introduce lubricating oil into the balance groove 210 through the oil guide holes 211 when the crankshaft 100 is running.

[0075] Specifically, the oil guide channel 101 extends along the axis of the crankshaft 100, and the oil guide channel 101 is mainly used to provide lubricating oil to the moving parts.

[0076] Optionally, the oil guide hole 211 is provided on the side wall of the balance groove 210 near the crankshaft 100. The oil guide hole 211 extends radially along the crankshaft 100, or extends radially inclined relative to the crankshaft 100.

[0077] Alternatively, the oil guide hole 211 is provided on the bottom wall of the balance groove 210. It may extend radially inclined relative to the crankshaft 100; or it may have at least a first section extending radially along the crankshaft 100 and a second section extending axially along the crankshaft 100, the first and second sections being connected.

[0078] By providing the oil guide hole 211, the lubricating oil in the oil guide channel 101 can be continuously introduced into the balance groove 210 during the operation of the crankshaft 100. In this way, no matter what speed and operating condition the crankshaft 100 is at, there will be a sufficient supply of lubricating oil in the balance groove 210, ensuring that the balance component 300 is always in a good lubricated state when moving in the balance groove 210.

[0079] Furthermore, sufficient lubricating oil can effectively reduce the friction between the balance component 300 and the inner wall of the balance groove 210, enabling the balance component 300 to respond more flexibly and quickly to the unbalanced force generated when the eccentric part 200 rotates, and to adjust its position in time to generate a reverse compensating force, thereby achieving dynamic balance more effectively and improving the stability of the crankshaft assembly. In addition, the continuously introduced lubricating oil can also remove the heat generated by friction, playing a cooling role, reducing the wear of the balance component 300 and the balance groove 210, extending their service life, reducing noise caused by wear, and improving the operating quality and reliability of the entire compressor system.

[0080] Furthermore, the oil guide hole 211 has a simple structure, is easy to process and manufacture, which helps to reduce production costs and improve the market competitiveness of the product.

[0081] Alternatively, oil guide hole 211 may not be provided.

[0082] In an optional embodiment of the crankshaft assembly described above, the distance between the eccentric portion 200 and the upper end is greater than the distance between the eccentric portion 200 and the lower end, and the depth of the balance groove 210 is greater than the height of the balance member 300.

[0083] By setting the distance between the eccentric portion 200 and the upper end to be greater than the distance between the eccentric portion 200 and the lower end, the portion between the eccentric portion 200 and the upper end of the crankshaft forms a long shaft portion, and the portion between the eccentric portion 200 and the lower end of the crankshaft 100 forms a short shaft portion. This allows for better mass distribution in the crankshaft assembly during operation, reducing the imbalance caused by the eccentric portion 200.

[0084] The depth of the balancing groove 210 is greater than the height of the balancing component 300. Optionally, the depth of the balancing groove 210 is greater than the height of the balancing component 300. That is, the extension length of the balancing groove 210 from the upper end face to the lower end face is greater than the height or diameter of the balancing component 300. On the one hand, this ensures that the balancing component 300 has sufficient room to move within the balancing groove 210, allowing it to move freely to respond to the unbalanced force generated by the rotation of the eccentric part 200, adjust its position in time to generate a reverse compensation force, and achieve effective dynamic balance. On the other hand, it provides a more stable installation space for the balancing component 300, making it less likely for the balancing component 300 to deviate from the track when moving within the balancing groove 210, thus ensuring the stability of the dynamic balance effect.

[0085] Secondly, this application provides a compressor, including: a housing 10, a compression chamber disposed therein; a rolling piston 20 disposed therein; and a crankshaft assembly as described above, wherein an eccentric portion 200 of the crankshaft assembly is disposed therein, and the eccentric portion 200 is configured to drive the rolling piston 20 to roll.

[0086] Specifically, the housing 10, as the core supporting component, has a compression chamber inside, providing a stable working space for the rolling piston 20. The rolling piston 20 is precisely fitted with the eccentric portion 200 of the crankshaft assembly. When the crankshaft 100 rotates, the eccentric portion 200 drives the rolling piston 20 to reciprocate within the compression chamber via mechanical transmission. This structural design makes the power transmission path of the compressor simple and efficient, directly converting the rotational motion of the eccentric portion 200 into the linear reciprocating motion of the rolling piston 20, reducing energy loss in intermediate transmission links. When the crankshaft 100 drives the eccentric portion 200 to rotate, the rolling piston 20 periodically changes its working volume within the compression chamber, thereby realizing the refrigerant intake, compression, and discharge process.

[0087] Furthermore, the compression chamber is equipped with a rotor 30 and a stator 31. The rotation of the crankshaft 100 is achieved through the cooperation of the stator 31 and the rotor 30. The crankshaft 100 and the rotor 30 are connected by a heat-shrink fitting. An upper bearing 41 and a lower bearing 42 are also provided within the compression chamber. The long shaft portion 110 is connected to the upper bearing 41, and the lower bearing 42 is connected to the short shaft portion 120, thereby achieving radial support and axial positioning of the crankshaft 100.

[0088] Among them, thermal fitting refers to the use of the physical properties of thermal expansion and contraction of materials to achieve a tight, keyless connection between the rotor and the crankshaft, which can achieve the effects of large torque transmission, compact structure, no stress concentration and excellent dynamic balance performance.

[0089] Furthermore, a cylinder 50 is provided inside the compression chamber, and a rolling piston 20 is installed inside the cylinder 50. The rolling piston 20 forms a precision fit with the eccentric part 200 of the crankshaft assembly. When the crankshaft 100 rotates, the eccentric part 200 drives the rolling piston 20 to reciprocate within the cylinder 50 through mechanical transmission.

[0090] By adopting the above technical solution, the weight and rotational inertia of the crankshaft assembly can be reduced by the cooperation of the balance groove and balance component set on the eccentric part. As the eccentric part rotates at high speed with the crankshaft, the balance component generates a centrifugal force component that is opposite to the direction of movement of the center of mass of the eccentric part. This compensates for part of the imbalance caused by the eccentricity, thereby enabling the compressor to maintain a lower vibration level and operating noise, which in turn reduces crankshaft wear, extends service life and improves operational stability.

[0091] The above description is only a preferred embodiment of this application. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of this application, and these improvements and modifications should also be considered within the scope of protection of this application.

Claims

1. A crankshaft assembly, characterized in that, include: A crankshaft extending along a first direction, the crankshaft having an upper end and a lower end along the first direction; An eccentric portion is provided on the crankshaft, and a balance groove is provided on the upper end surface of the eccentric portion facing the upper end. The balance groove is provided along the circumferential edge of the eccentric portion. A balancing component is disposed within the balancing groove. As the eccentric portion rotates with the crankshaft, the balancing component moves within the balancing groove.

2. The crankshaft assembly according to claim 1, characterized in that, The eccentric portion has a geometric center that is offset from the rotation center of the crankshaft assembly by a predetermined distance. The eccentric portion has a first edge portion located on the side of the geometric center away from the rotation center, and the balance groove is provided at least along the first edge portion.

3. The crankshaft assembly according to claim 1, characterized in that, The balancing groove is an arc-shaped groove, and the center of curvature of the extended trajectory of the balancing groove coincides with the geometric center of the eccentric portion. The balancing groove is configured such that the balancing member moves within the balancing groove along the extended direction of the balancing groove.

4. The crankshaft assembly according to claim 3, characterized in that, The central angle corresponding to the arc of the balancing groove is greater than or equal to 120° and less than or equal to 270°.

5. The crankshaft assembly according to any one of claims 1 to 4, characterized in that, The balancing component is spherical or cylindrical.

6. The crankshaft assembly according to any one of claims 1 to 4, characterized in that, The density of the balancing component is greater than the density of the crankshaft.

7. The crankshaft assembly according to any one of claims 1 to 4, characterized in that, The inner wall of the balance groove is provided with a lubricating medium.

8. The crankshaft assembly according to any one of claims 1 to 4, characterized in that, The crankshaft has an internal oil guide channel extending along its own axial direction; The balance groove is provided with a plurality of oil guide holes spaced apart along the circumference. The oil guide holes are connected to the oil guide channel, which is used to introduce lubricating oil into the balance groove through the oil guide holes during operation.

9. The crankshaft assembly according to any one of claims 1 to 4, characterized in that, The distance between the eccentric part and the upper end is greater than the distance between the eccentric part and the lower end, and the depth of the balancing groove is greater than the height of the balancing component.

10. A compressor, characterized in that, include: A housing, wherein a compression chamber is provided inside the housing; A rolling piston is disposed in the compression chamber; and, The crankshaft assembly as claimed in any one of claims 1 to 9, wherein an eccentric portion of the crankshaft assembly is disposed within the rolling piston, the eccentric portion being configured to drive the rolling piston to roll.

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