Crankshaft assembly and compressor having the same

Abstract

The present invention provides a crankshaft assembly and a compressor having the same, so as to solve the problem in the prior art that the crankshaft bends due to excessive centrifugal force of the rotor balance block during high-speed operation. A balance block is arranged on the crankshaft, and the balance block is formed by three component sections, wherein the thickness of the second component section along the axial direction of the crankshaft is set to be smaller than the thickness of the third component section along the axial direction of the crankshaft. Such an arrangement can effectively solve the problem of increased deflection of the crankshaft due to increased height of the pump body assembly, effectively reduce friction damage between the crankshaft and other components, and effectively improve the reliability and service life of the crankshaft assembly.

Description

Technical Field

[0001] The present invention relates to the technical field of compressor equipment, and in particular to a crankshaft assembly and a compressor having the same. Background Art

[0002] The structure of the rotary compressor is mainly composed of a housing assembly, a motor assembly, a pump assembly, a liquid distributor, etc., wherein the motor is composed of a stator and a rotor, and the pump assembly is composed of a crankshaft, a cylinder, a rolling piston, etc. Among them, the long axis end of the crankshaft cooperates with the motor rotor, and the electromagnetic force generated between the stator and the rotor causes the rotor to drive the crankshaft to rotate, and the eccentric part of the crankshaft cooperates with the rolling piston to rotate in the cylinder cavity to achieve the purpose of compressing and discharging the gas. With the continuous advancement of the compressor industry, miniaturization has become an important development direction. Miniaturization means that the cylinder diameter is limited under the same displacement, and the cylinder height increases accordingly, and the overall height of the pump body rotor assembly increases. The increase in the height of the pump body rotor assembly will increase the problem of increased crankshaft deflection.

[0003] As the height of the compressor pump rotor assembly increases, if the traditional compressor crankshaft balancing method is used, the mass of the rotor main and auxiliary balancing blocks must be increased. According to the centrifugal force formula F = mω 2 It can be inferred that the centrifugal force of the main and auxiliary balance blocks of the rotor of the compressor in the high-frequency state is likely to increase linearly, resulting in increased deflection and vibration of the crankshaft in the high-frequency state, and then problems such as friction loss and increased power consumption will occur, which will reduce the performance of the compressor and cause many problems such as reliability and noise.

[0004] The prior art CN203560100U and CN105673492A disclose a crankshaft balancing block structure, which is used together with the motor rotor auxiliary balancing block to balance the centrifugal force generated by the eccentric part of the crankshaft during rotation. The crankshaft balancing block is mainly arranged near the eccentric part, and a balancing cavity for the balancing block to rotate is arranged above or below the eccentric part to ensure space for the balancing block to rotate. However, in the technical solution of this patent, the crankshaft balancing block and the crankshaft are designed as an integrated unit, and the crankshaft balancing block is located close to the eccentric part, which greatly increases the difficulty of both the processing technology and the whole machine assembly process. In addition, the design of the balancing cavity will also occupy a certain space inside the compressor, resulting in a further increase in the height of the pump rotor assembly, which is not conducive to reducing costs and miniaturization goals.

[0005] The prior art CN103486036A discloses a crankshaft shaft end balance block structure, in which the shaft end balance block and the crankshaft are integrated. The technical solution is to set the balance block at the short shaft end of the crankshaft, which is much simpler than the technical solutions disclosed in CN203560100U and CN105673492A in the assembly process of the compressor pump assembly. The function of the shaft end balance block is basically the same as the technical content disclosed in CN203560100U and CN105673492A. However, according to the technical solution of CN103486036A, the shaft end balance block and the crankshaft are integrated, which is always a major change in the original whole machine assembly process, and it also poses a certain difficulty for the processing technology of the crankshaft. At the same time, the technical solution lengthens the short shaft end of the crankshaft to place the shaft end balance block, which is not good for the cost of the compressor.

[0006] Prior art CN208831239U discloses a rotary compressor structure, in which the motor part is equipped with a first rotor balancing block above the motor rotor and a second rotor balancing block below the motor rotor, and a bottom balancing block is installed at the tail end of the crankshaft. Since the crankshaft deflection increases continuously as it moves away from the eccentric part of the crankshaft, the technical solution does not significantly reduce the crankshaft deflection due to the presence of the first rotor balancing block.

[0007] The prior art JP02019667A discloses a rotary compressor, the crankshaft of the compressor is composed of an upper and a lower part connected by a coupling, and a balancing block is installed at the end of the lower shaft to balance the centrifugal force of the eccentric part of the crankshaft and the rolling piston. However, this technical solution can only be used for single-cylinder rotary compressors and cannot be used for double-cylinder and multi-cylinder compressors.

[0008] The above-mentioned prior art solutions obviously have problems such as poor processability, increased cost, suboptimal balancing effect and only applicable to single-cylinder compressors. Summary of the invention

[0009] The main purpose of the present invention is to provide a crankshaft assembly and a compressor having the same, so as to solve the problem in the prior art that the crankshaft is bent due to excessive centrifugal force of the rotor balance block during high-speed operation.

[0010] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, there is provided a crankshaft assembly, comprising: a crankshaft; a balancing block, the balancing block comprising: a first component segment, a first end of the first component segment is connected to the crankshaft; a second component segment, a first end of the second component segment is connected to the second end of the first component segment; a third component segment, the third component segment is connected to the second end of the second component segment, and the thickness of the second component segment along the axial direction of the crankshaft is less than the thickness of the third component segment along the axial direction of the crankshaft.

[0011] Furthermore, the crankshaft has a long shaft section and a short shaft section, a balancing groove is opened on the end surface of the short shaft section, and the first end of the first group section extends into the balancing groove along the axial direction of the crankshaft.

[0012] Furthermore, an eccentric portion is provided on the crankshaft, and the eccentric portion is located between the major axis section and the minor axis section, and the geometric center of the cross section of the balancing groove and the center of mass of the eccentric portion are symmetrically arranged about the axis of the crankshaft.

[0013] Furthermore, there are multiple eccentric parts, and the geometric center of the cross section of the balancing groove and the center of mass of at least one of the multiple eccentric parts are symmetrically arranged with respect to the axis of the crankshaft.

[0014] Furthermore, the thickness of the third group segment along the axial direction of the crankshaft is H, and the offset distance between the center of mass of the balancing block and the axis of the crankshaft is R5, wherein 0.05≤H / R5≤0.65.

[0015] Further, the thickness of the second group segment along the axial direction of the crankshaft is H0, wherein 0.1≤H0 / R5≤0.5.

[0016] Further, the thickness of the first group of segments along the radial direction of the crankshaft is H1, wherein 0.05≤H1 / R5≤0.1.

[0017] Further, the density of the balancing mass is greater than the density of the crankshaft.

[0018] Furthermore, the third component segment is a cylindrical structure, and the outer peripheral surface of the third component segment is connected to the second component segment.

[0019] Furthermore, the surface of the first component segment on the side away from the long axis section of the crankshaft, the surface of the second component segment on the side away from the long axis section of the crankshaft, and the surface of the third component segment on the side away from the long axis section of the crankshaft are arranged flush with each other.

[0020] Furthermore, the first assembly segment, the second assembly segment and the third assembly segment are integrally formed.

[0021] According to another aspect of the present invention, a compressor is provided, comprising a crankshaft assembly, wherein the crankshaft assembly is the above-mentioned crankshaft assembly.

[0022] Furthermore, the compressor comprises: a rotor, a rotor balancing weight is arranged on a side of the rotor facing the rotor, and the center of gravity of the balancing weight is arranged eccentrically with the center of gravity of the rotor balancing weight.

[0023] The technical solution of the present invention is applied, by arranging a balancing block on the crankshaft, and the balancing block is arranged and formed by three component sections, wherein the thickness of the second component section along the axial direction of the crankshaft is set to be smaller than the thickness of the third component section along the axial direction of the crankshaft. Such an arrangement can effectively solve the problem of increased deflection of the crankshaft due to increased height of the pump body assembly, effectively reduce friction damage between the crankshaft and other components, and effectively improve the reliability and service life of the crankshaft assembly. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0025] Figure 1 A schematic structural diagram of an embodiment of a crankshaft assembly according to the present invention is shown;

[0026] Figure 2 A schematic structural diagram of a first viewing angle of a first embodiment of a balancing weight according to the present invention is shown;

[0027] Figure 3 A schematic structural diagram of a second viewing angle of a first embodiment of a balancing weight according to the present invention is shown;

[0028] Figure 4 A schematic structural diagram of a first embodiment of a compressor according to the present invention is shown;

[0029] Figure 5 A schematic structural diagram of a second embodiment of a compressor according to the present invention is shown;

[0030] Figure 6 A structural schematic diagram showing a relationship curve between H0 / R5 and fatigue life of a compressor according to the present invention;

[0031] Figure 7 A schematic structural diagram of an embodiment of a compressor according to the present invention is shown.

[0032] The above drawings include the following reference numerals:

[0033] 10. crankshaft; 11. long shaft section; 12. short shaft section; 121. balance groove; 13. eccentric part;

[0034] 20. balancing block; 21. first group segment; 22. second group segment; 23. third group segment;

[0035] 30. rotor; 31. rotor balancing weight;

[0036] 40. Pump body assembly; 41. Piston;

[0037] 50. Refrigeration oil. DETAILED DESCRIPTION

[0038] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0039] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0040] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchangeable where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein, for example. In addition, the terms "including" and "having" and any of their variations are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units that are clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0041] Now, exemplary embodiments according to the present application will be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments may be implemented in a variety of different forms and should not be construed as being limited to the embodiments described herein. It should be understood that these embodiments are provided to make the disclosure of the present application thorough and complete, and to fully convey the concepts of these exemplary embodiments to those of ordinary skill in the art. In the accompanying drawings, for the sake of clarity, the thickness of the layers and regions may be enlarged, and the same reference numerals are used to represent the same devices, and thus their descriptions will be omitted.

[0042] Combination Figures 1 to 7 As shown, according to a specific embodiment of the present invention, a crankshaft assembly is provided.

[0043] Specifically, Figure 1As shown, the crankshaft assembly includes a crankshaft 10 and a balancing block 20. The balancing block 20 includes a first component segment 21, a second component segment 22, and a third component segment 23. The first end of the first component segment 21 is connected to the crankshaft 10. The first end of the second component segment 22 is connected to the second end of the first component segment 21. The third component segment 23 is connected to the second end of the second component segment 22. The thickness of the second component segment 22 along the axial direction of the crankshaft 10 is less than the thickness of the third component segment 23 along the axial direction of the crankshaft 10.

[0044] In this embodiment, a balancing block is arranged on the crankshaft, and the balancing block is formed by three component sections, wherein the thickness of the second component section along the axial direction of the crankshaft is set to be smaller than the thickness of the third component section along the axial direction of the crankshaft. Such an arrangement can effectively solve the problem of increased deflection of the crankshaft due to increased height of the pump body assembly, effectively reduce friction damage between the crankshaft and other components, and effectively improve the reliability and service life of the crankshaft assembly.

[0045] The crankshaft 10 has a long shaft section 11 and a short shaft section 12. A balancing groove 121 is provided on the end surface of the short shaft section 12, and the first end of the first group section 21 extends into the balancing groove 121 along the axial direction of the crankshaft 10. This arrangement can improve the connection stability between the balancing block and the crankshaft.

[0046] Furthermore, an eccentric portion 13 is provided on the crankshaft 10. The eccentric portion 13 is located between the long shaft section 11 and the short shaft section 12, and the geometric center of the cross section of the balancing groove 121 and the center of mass of the eccentric portion 13 are symmetrically arranged about the axis of the crankshaft 10. Such an arrangement can improve the stability of the crankshaft assembly.

[0047] The eccentric portion 13 may be provided in plurality, and the geometric center of the cross section of the balancing groove 121 and the center of mass of at least one of the plurality of eccentric portions 13 are symmetrically arranged with respect to the axis of the crankshaft 10. Figure 1 As shown, there are two eccentric parts 13, and the geometric center of the cross section of the balancing groove 121 and the center of mass of the eccentric part 13 arranged near the balancing block are arranged symmetrically about the axis of the crankshaft 10. This arrangement can make the crankshaft have good stability during rotation.

[0048] Specifically, Figure 5As shown, the thickness of the third component section 23 along the axial direction of the crankshaft 10 is H, and the offset distance between the center of mass of the balancing block 20 and the axis of the crankshaft 10 is R5, wherein 0.05≤H / R5≤0.65. The thickness of the second component section 22 along the axial direction of the crankshaft 10 is H0, wherein 0.1≤H0 / R5≤0.5. The thickness of the first component section 21 along the radial direction of the crankshaft 10 is H1, wherein 0.05≤H1 / R5≤0.1. Wherein A is the axis of the crankshaft 10. Such an arrangement can further improve the stability of the crankshaft during rotation.

[0049] Furthermore, the density of the balancing weight 20 is greater than the density of the crankshaft 10. This arrangement enables the balancing weight 20 to perform a good balancing effect in the process of rotating the crankshaft while following the rotation of the crankshaft.

[0050] Preferably, the third component segment 23 is a cylindrical structure, and the outer peripheral surface of the third component segment 23 is connected to the second component segment 22. Such an arrangement can improve the stability and reliability of the balancing weight 20.

[0051] like Figures 1 to 3 As shown, the surface of the first component segment 21 on the side away from the long shaft segment 11 of the crankshaft 10, the surface of the second component segment 22 on the side away from the long shaft segment 11 of the crankshaft 10, and the surface of the third component segment 23 on the side away from the long shaft segment 11 of the crankshaft 10 are arranged flush. Moreover, the first component segment 21, the second component segment 22 and the third component segment 23 are integrally formed. Such an arrangement can improve the stability and reliability of the balancing weight.

[0052] The crankshaft assembly in the above embodiment can also be used in the technical field of compressor equipment. That is, according to another aspect of the present invention, a compressor is provided, including a crankshaft assembly, and the crankshaft assembly is the crankshaft assembly in the above embodiment. Specifically, Figure 7 As shown, the compressor includes a rotor 30. A rotor balancing weight 31 is arranged on one side of the rotor 30 facing the rotor 30, and the center of gravity of the balancing weight 20 is eccentrically arranged with the center of gravity of the rotor balancing weight 31. The balancing weight 31 is completely immersed in the refrigeration oil 50.

[0053] Specifically, the compressor structure of the present application solves the problem of increased crankshaft deflection due to increased height of the pump body rotor assembly in the miniaturized design of the compressor, and also solves the problem of reduced mass of the balancing block after the height of the pump body rotor assembly is increased.

[0054] By configuring a balancing block at the lower end of the crankshaft to replace the auxiliary balancing block on the motor rotor away from the eccentric part, the distance between the balancing block and the eccentric part can be reduced, the mass of the balancing block can be reduced, and the problem of crankshaft bending caused by excessive centrifugal force of the rotor balancing block during high-speed operation can be solved. The dynamic deflection of the crankshaft is balanced, and the crankshaft wear and vibration noise problems can be reduced.

[0055] By achieving interference fit between the crankshaft balancing block and the crankshaft stub section, the crankshaft balancing block is pressed into the balancing groove on the end face of the crankshaft stub by cold pressing after the traditional pump body assembly process is completed. There is no need to change the traditional whole machine assembly process, thus saving the compressor assembly process cost.

[0056] The design of the balancing block is divided into the end portion, which is the third component, and the handle portion, which is the first component. The end portion is perpendicular to the handle portion, and the handle portion and the balance groove of the short shaft end face are interference fit in the axial direction (refer to Figure 1 ), it will not loosen or fall off due to centrifugal force during operation, and has high reliability.

[0057] Among them, the compressor is a rotary compressor, and a motor and a compression mechanism are arranged in a sealed shell. The motor includes a stator and a rotor. The compression mechanism includes a cylinder with a compression chamber, and a piston and a slide are arranged in the compression chamber. The crankshaft includes a long shaft section, an eccentric part and a short shaft section. The long shaft section is connected to the rotor, and the eccentric part drives the piston to rotate eccentrically. The upper bearing for supporting the long shaft section and the lower bearing for supporting the short shaft end are respectively arranged on the upper and lower sides of the cylinder. The motor part is only equipped with a rotor balancing block located below the rotor. The crankshaft includes a crankshaft balancing block, and the long shaft section, the eccentric part, the short shaft section, and the crankshaft balancing block are arranged in sequence. The center of gravity of the crankshaft balancing block is eccentrically arranged relative to the center of gravity of the rotor balancing block.

[0058] Figure 7 The schematic diagram of the rotary compressor structure of the present application is shown, which is mainly composed of a housing, a motor, and a pump assembly 40, wherein the pump assembly 40 is mainly composed of a crankshaft, a piston 41, a cylinder, a vane, a spring, and upper and lower bearings, and the motor is mainly composed of a stator, a rotor, and a rotor main balance block (close to the eccentric part). The crankshaft passes through the upper bearing, the rolling piston in the cylinder cavity, the lower bearing, etc. in sequence. The rotor cooperates with the long shaft section of the crankshaft to drive the crankshaft to operate stably, and then the process of suction, compression, and exhaust is completed through the cooperation of the eccentric part in the cylinder cavity with the vane, etc.

[0059] From the working process of the crankshaft structure of the rotary compressor, it can be known that the rotor cooperates with the long shaft section of the crankshaft, and the rotor drives the crankshaft to operate stably, which is a necessary condition to ensure the normal operation of the compressor. However, with the development trend of miniaturization of compressors, the inner diameter of the cylinder is limited. Under the premise of ensuring the displacement, the cylinder height must be increased, which increases the overall height of the pump rotor assembly, and then leads to increased deflection and vibration of the crankshaft under high frequency conditions, which not only increases friction loss and power consumption, but also reduces the performance of the compressor, and also leads to many problems such as reliability and noise, which greatly affects the user experience.

[0060] A crankshaft balancing block is added at the end of the short shaft section of the crankshaft, and a groove is opened on the end face of the short shaft so that the crankshaft balancing block and the short shaft are interference fit, the handle of the balancing block is interference fit with the short shaft groove, the handle length is greater than the length of the balancing groove, and the end of the balancing block is located below the refrigerant oil level at the bottom of the compressor, wherein the offset distance of the center of mass of the crankshaft balancing block relative to the rotation center is R5, and the thickness of the balancing block is H. In order to ensure that the contact area between the balancing block and the oil pool in the tangential direction of rotation should be reduced as much as possible, that is, the regional flattening design, but if it is too flat, it will also cause liquid surface oscillation, seriously affecting the reliability and noise of the compressor operation, so in order to design reasonable balancing block structural parameters, its thickness H and center of mass eccentricity R5 meet the conditions: 0.05≤H / R5≤0.65. In the technical solution of the present application, there is no need to provide a working space for the above-mentioned balancing block separately, nor is there a need to lengthen the crankshaft, saving the cost of the crankshaft. The crankshaft balancing block is used to ensure the torque balance of the crankshaft during high-speed operation, and to ensure the noise and reliability of the compressor.

[0061] During high-speed operation of the compressor, due to the principles of fluid dynamics, there will be a pressure difference between the upper and lower surfaces of the balance block end due to the oil level. The higher the operating frequency of the compressor, the greater the pressure difference, and the resulting unbalanced force will increase accordingly. In addition, the oil level is unstable, and this unbalanced force shows a fluctuating trend of amplitude changes as a whole. The effect of alternating stress on the balance block can easily cause fatigue fracture of the material. From the theory, it can be known that the maximum stress amplitude in cyclic alternating stress is generally much lower than the strength limit and yield limit of the material. For example, if the safety factor of traditional mechanics is used as the standard, and the reliability of the main force-bearing part of the balance block under the action of alternating stress cannot be guaranteed, through theoretical analysis and fatigue characteristics research, it is believed that the main force-bearing part of the crankshaft balance block should be guaranteed to be greater than the maximum amplitude of the alternating stress, such as Figure 6 As shown, the fatigue life corresponding to the ratio of the thickness H0 of the middle neck of the crankshaft balance block to its mass center eccentricity R5 is given. The present application provides an optimal method: 0.1≤H0 / R5≤0.5, and the shank thickness H1 and its mass center eccentricity R5 should meet the condition: 0.05≤H1 / R5≤0.1. Preferably, 0.073≤H1 / R5≤0.09. When the above relationship is met at the same time, the material's own performance can be fully utilized to ensure the reliability of the compressor.

[0062] As the height of the compressor increases, the rotor moves upward. In order to ensure the stability of the crankshaft's high-speed operation, the mass of the rotor counterweight at the upper end of the rotor must be increased. However, as the mass of the rotor counterweight increases, the long shaft section of the crankshaft is easily deformed due to the increased centrifugal force, causing problems such as crankshaft wear, vibration and noise, which is not conducive to the implementation of the crankshaft balancing system. Figure 4 An embodiment of a single cylinder compressor is shown, Figure 5 The embodiment shown. By removing the rotor counterweight above the rotor assembly of the traditional compressor and setting the crankshaft counterweight on the short shaft end face below the crankshaft, when the height of the compressor is increased, the mass of the counterweight can be reduced while meeting the stability and reliability of the balancing system, thereby reducing the compressor investment cost and achieving lightweight. At the same time, the crankshaft counterweight is assembled by interference fit with the balancing groove on the crankshaft end face, which has the characteristics of simplicity and easy implementation, and can ensure its processability without making major changes in the existing compressor assembly technology, thereby reducing the process investment cost.

[0063] In the present application, the compressor structure of the present application is adopted, so that the crankshaft balance block replaces the rotor auxiliary balance block of the traditional rotary compressor, and the distance between the balance block and the eccentric part of the crankshaft is reduced, so that the mass of the balance block counterweight can be reduced, so that the problem of crankshaft balance can be solved while reducing the mass of the balance block. It is possible to reduce noise and vibration, reduce power consumption, and ensure the working reliability of the compressor without increasing the weight of the compressor. The technical solution of the crankshaft compressor assembly provided in the present application is not only applicable to rotary compressors, but also to rotary fluid machinery with similar structures, such as rotary expanders, vane compressors, vane expanders, etc.

[0064] The difference between the proposed technology and the prior art lies in the assembly method and structure of the balancing block. The balancing block is assembled by interference fit at the end of the crankshaft stub shaft, which is simple to assemble and simplifies the process. There is no need to provide a separate working space for the balancing block, and the space above the cylinder is not occupied. The height of the compressor is reduced as much as possible. By replacing the rotor auxiliary balancing block, the static and dynamic balance equations of the crankshaft are guaranteed to hold when the masses of the rotor main balancing block and the crankshaft balancing block are reduced.

[0065] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0066] In addition to the above, it should be noted that "one embodiment", "another embodiment", "embodiment", etc. mentioned in this specification refer to the specific features, structures or characteristics described in conjunction with the embodiment included in at least one embodiment generally described in this application. The same expression appearing in multiple places in the specification does not necessarily refer to the same embodiment. Further, when describing a specific feature, structure or characteristic in conjunction with any embodiment, it is claimed that the realization of such feature, structure or characteristic in conjunction with other embodiments also falls within the scope of the present invention.

[0067] In the above embodiments, the description of each embodiment has its own emphasis. For parts that are not described in detail in a certain embodiment, reference can be made to the relevant descriptions of other embodiments.

[0068] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A crankshaft assembly, characterized in that: include: Crankshaft (10); A balancing weight (20), the balancing weight (20) comprising: A first component segment (21), wherein a first end of the first component segment (21) is connected to the crankshaft (10); A second component segment (22), wherein a first end of the second component segment (22) is connected to a second end of the first component segment (21); a third component segment (23), the third component segment (23) being connected to the second end of the second component segment (22), the thickness of the second component segment (22) along the axial direction of the crankshaft (10) being smaller than the thickness of the third component segment (23) along the axial direction of the crankshaft (10); The crankshaft (10) comprises a long shaft section (11) and a short shaft section (12); a balancing groove (121) is provided on an end surface of the short shaft section (12); and a first end of the first group section (21) extends into the balancing groove (121) along an axial direction of the crankshaft (10); The crankshaft (10) is provided with an eccentric portion (13), the eccentric portion (13) is located between the long shaft section (11) and the short shaft section (12), and the geometric center of the cross section of the balancing groove (121) and the center of mass of the eccentric portion (13) are symmetrically arranged about the axis of the crankshaft (10).

2. The crankshaft assembly according to claim 1, characterized in that There are a plurality of eccentric parts (13), and the geometric center of the cross section of the balancing groove (121) and the center of mass of at least one of the plurality of eccentric parts (13) are symmetrically arranged with respect to the axis of the crankshaft (10).

3. The crankshaft assembly according to claim 1, characterized in that The thickness of the third component segment (23) along the axial direction of the crankshaft (10) is H, and the offset distance between the center of mass of the balancing block (20) and the axis of the crankshaft (10) is R5, wherein 0.05≤H / R5≤0.

65.

4. The crankshaft assembly according to claim 1 or 3, characterized in that: The thickness of the second group segment (22) along the axial direction of the crankshaft (10) is H0, wherein 0.1≤H0 / R5≤0.

5.

5. The crankshaft assembly according to claim 4, characterized in that The thickness of the first group of segments (21) along the radial direction of the crankshaft (10) is H1, wherein 0.05≤H1 / R5≤0.

1.

6. The crankshaft assembly according to claim 1, characterized in that The density of the balancing block (20) is greater than the density of the crankshaft (10).

7. The crankshaft assembly according to claim 1, characterized in that The third component segment (23) is a cylindrical structure, and the outer peripheral surface of the third component segment (23) is connected to the second component segment (22).

8. The crankshaft assembly according to claim 1, characterized in that The surface of the first component segment (21) on the side away from the long axis segment (11) of the crankshaft (10), the surface of the second component segment (22) on the side away from the long axis segment (11) of the crankshaft (10), and the surface of the third component segment (23) on the side away from the long axis segment (11) of the crankshaft (10) are arranged flush with each other.

9. The crankshaft assembly according to claim 1, characterized in that The first assembly segment (21), the second assembly segment (22) and the third assembly segment (23) are integrally formed.

10. A compressor comprising a crankshaft assembly, characterized in that: The crankshaft assembly is the crankshaft assembly according to any one of claims 1 to 9.

11. The compressor according to claim 10, characterized in that The compressor comprises: A rotor (30), wherein a rotor balancing weight (31) is arranged on a side of the rotor (30) facing the rotor (30), and the center of gravity of the balancing weight (20) is eccentrically arranged with respect to the center of gravity of the rotor balancing weight (31).

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