Rotor assembly and compressor

Abstract

The utility model provides a rotor assembly and a compressor, the rotor assembly comprises a rotor main body and a main balance block, the main balance block is installed at one end of the rotor main body, and a noise reduction part is constructed on the inner wall of the main balance block; the noise reduction part is configured to rotate along with the main balance block to cut airflow which flows in the axial direction of the rotor body and rotates at the position of the main balance block, so that airflow noise is reduced by reducing the size of airflow vortex generated by the rotating airflow through cutting. Based on the technical scheme of the utility model, the noise reduction part is arranged on the inner wall of the main balance block, and the noise reduction part is used for cutting the high-speed rotating air flow, so that a large air flow vortex formed by the rotating air flow can be destroyed and is changed into a small air flow vortex, the noise intensity can be reduced, and the noise reduction of the rotor assembly is realized. And the cutting effect of the noise reduction part on the rotating airflow can also reduce the wind resistance of the main balance block, and the rotating performance of the rotor assembly is optimized.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, and particularly to a rotor assembly and a compressor. Background Art

[0002] The rotor assembly is an important part of a compressor. Currently, the main body of the rotor assembly is a structure formed by stacking stamping sheets. A main balance weight and a sub-balance weight are respectively installed at both ends of the main body, and a flow passage is constructed inside the main body.

[0003] During the research and development of the rotor assembly and the compressor, it is found that there is obvious noise during the operation of the rotor assembly and even the compressor. Through further analysis, it is found that in addition to the noise generated by mechanical vibration, the noise also has other sources. Therefore, finding out the noise source of the rotor assembly and solving the noise problem are urgent problems to be solved in the current research and development work of the rotor assembly and the compressor. Summary of the Utility Model

[0004] In order to solve the noise problem existing in the existing rotor assembly, the utility model provides a rotor assembly and a compressor.

[0005] In a first aspect, a rotor assembly provided by the utility model includes:

[0006] A rotor main body; and

[0007] A main balance weight, which is installed at one end of the rotor main body, and a noise reduction part is constructed on the inner wall of the main balance weight;

[0008] Wherein, the noise reduction part is configured to cut the air flow flowing along the axial direction of the rotor main body and generating rotation at the main balance weight as the main balance weight rotates, so as to reduce the size of the air flow vortex generated by the rotating air flow through cutting and reduce the air flow noise.

[0009] In an embodiment, the noise reduction part is configured as ribs protruding from the inner wall of the main balance weight, and the ribs extend along the circumferential direction of the rotor main body on the inner wall of the main balance weight.

[0010] In an embodiment, the number of the ribs is one or more. When the number of the ribs is multiple, the multiple ribs are parallel to each other and are evenly and spaced apart in the axial direction of the rotor main body.

[0011] In an embodiment, the height range of the ribs protruding from the inner wall of the main balance weight is 1 mm to 3 mm.

[0012] In one embodiment, the rib has a projection in the plane where the axis of the rotor body is located, and the angle between the projection and the radial cross-section of the rotor body is 0° to 15°.

[0013] In one embodiment, the main balance weight includes a connecting portion and a protruding portion. The connecting portion is configured to connect the end of the rotor body. The protruding portion protrudes outward from the end of the rotor body relative to the connecting portion, and the noise reduction portion is configured on the inner wall of the protruding portion.

[0014] In one embodiment, a plurality of flow channels are formed inside the rotor body, and the flow channels extend from one end of the rotor body to the other end of the rotor body;

[0015] Among them, at least one variable-diameter channel is included in the plurality of flow channels, and the variable-diameter channel is configured to include a plurality of channel segments with inconsistent inner diameter sizes.

[0016] In one embodiment, the variable-diameter channel includes two first channel segments and a second channel segment located between the two first channel segments, and the inner diameter of the second channel segment is larger than that of the first channel segment.

[0017] In one embodiment, the dimensions of the first channel segment and the second channel segment satisfy the following relational expression:

[0018] f = C / (2×3.14)×SQRT[S1 / (S2×H2×H2)]×10 3 ;

[0019] Wherein, f is the target sound absorption frequency, C is the propagation speed of sound in the air, S1 is the radial cross-sectional area of the first channel segment, S2 is the radial cross-sectional area of the second channel segment, H2 is the axial length of the second channel segment, and SQRT represents taking the square root.

[0020] In one embodiment, the plurality of flow channels are evenly distributed along the circumferential direction of the rotor body, including a plurality of variable-diameter channels and a plurality of fixed-diameter channels. The fixed-diameter channel is configured such that the inner diameter size at any part in its axial direction is equal;

[0021] Among them, the plurality of variable-diameter channels and the plurality of fixed-diameter channels are rotationally symmetrically distributed about the axis of the rotor body.

[0022] In a second aspect, a compressor proposed by the present utility model includes the above-mentioned rotor assembly, and thus has all the technical effects possessed by it.

[0023] The above technical features can be combined in various suitable ways or replaced by equivalent technical features as long as the purpose of the present utility model can be achieved.

[0024] A rotor assembly and a compressor provided by the present utility model have at least the following beneficial effects compared with the prior art:

[0025] In the rotor assembly and the compressor of the present utility model, by providing a noise reduction portion on the inner wall of the main balance block, the high-speed rotating airflow is cut by the noise reduction portion, which can destroy the large airflow vortices formed by the rotating airflow and turn them into small airflow vortices, thereby reducing the noise intensity and achieving noise reduction and silencing of the rotor assembly. Moreover, the cutting effect of the noise reduction portion on the rotating airflow can also reduce the wind resistance of the main balance block and optimize the rotating performance of the rotor assembly. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Hereinafter, the present utility model will be described in more detail based on the embodiments with reference to the drawings. Among them:

[0027] Figure 1 A three-dimensional schematic diagram showing the external structure of the rotor assembly of the present utility model;

[0028] Figure 2 A cross-sectional view showing the rotor assembly of the present utility model in a three-dimensional perspective;

[0029] Figure 3 A schematic diagram showing the structure of the end face where the main balance block of the rotor assembly of the present utility model is located;

[0030] Figure 4 Shows Figure 2 A front projection schematic diagram of the structure shown;

[0031] Figure 5 Shows Figure 4 A schematic diagram after adopting another implementation manner for the rib in the structure shown;

[0032] Figure 6 Shows Figure 4 A schematic diagram after adopting other quantities for the rib in the structure shown;

[0033] Figure 7 Shows Figure 5 A schematic diagram after adopting other quantities for the rib in the structure shown;

[0034] Figure 8 A schematic diagram showing the structure of the end face where the auxiliary balance block of the rotor assembly of the present utility model is located;

[0035] Figure 9 A schematic diagram showing the internal structure of the rotor body of the rotor assembly of the present utility model;

[0036] Figure 10 Shows Figure 9Schematic diagram after adopting another implementation manner for the distribution mode of the flow channels in the shown structure;

[0037] Figure 11 Schematic diagram showing the variable-diameter channels of the rotor assembly of the present utility model;

[0038] Figure 12 Schematic diagram showing the dimensions of each channel section of the variable-diameter channels of the rotor assembly of the present utility model;

[0039] Figure 13 Schematic diagram showing the fixed-diameter channels of the rotor assembly of the present utility model.

[0040] In the drawings, the same components are denoted by the same reference numerals. The drawings are not drawn to actual scale.

[0041] Reference numerals:

[0042] 1 - Rotor body, 2 - Main balance weight, 21 - Connecting portion, 22 - Protruding portion, 3 - Rib, 4 - Auxiliary balance weight, 5 - Flow channel, 51 - Variable-diameter channel, 511 - First channel section, 512 - Second channel section, 52 - Fixed-diameter channel. Detailed implementation manners

[0043] The present utility model will be further described below with reference to the drawings.

[0044] Embodiment 1

[0045] An embodiment of the present utility model provides a rotor assembly, which includes a rotor body 1 and a main balance weight 2; the main balance weight 2 is installed at one end of the rotor body 1, and a noise reduction portion is constructed on the inner wall of the main balance weight 2; wherein, the noise reduction portion is constructed to be able to cut the airflow flowing along the axial direction of the rotor body 1 and generating rotation at the main balance weight 2 as the main balance weight 2 rotates, so as to reduce the size of the airflow vortices generated by the rotating airflow through cutting and reduce the airflow noise.

[0046] Specifically, as mentioned in the background art above, during the current R & D process, it has been found that there is a relatively obvious noise during the operation of the rotor assembly and even the compressor. In addition to the noise inevitably caused by general mechanical vibration, there are other sources of this noise. Through analysis and testing, it is found that the main source of another part of the noise is the air flow at the rotor assembly, which is the noise caused by the air flow. Further testing shows that the noise generated by the air flow is mainly concentrated at the air flow input end of the rotor assembly first, that is, the position where the main balance weight 2 is located. Combining with the principle of general air flow noise generation, it is judged that when the high-pressure gas enters the main balance weight 2 that rotates at a high speed with the rotor main body 1, the air flow rotates together with the main balance weight 2 that rotates at a high speed, and a vortex is formed here, thereby generating vortex noise. Therefore, the present utility model optimizes the structure at the main balance weight 2 for the vortex noise at the main balance weight 2 to solve this noise problem.

[0047] Specifically, the main body of the main balance weight 2 is usually designed to conform to the shape and structure of the rotor, as shown in the attached drawings Figure 1 As shown, the main balance weight 2 is integrally in an arc shape that is the same as the outer contour shape of the rotor main body 1 (the central angle corresponding to its arc is less than 180 degrees) and this arc is concentric with the rotor main body 1. The noise reduction part is constructed on the inner wall of the main balance weight 2. When the rotor assembly rotates, the noise reduction part also rotates around the axis of the rotor main body 1. The air flow transported to the rotor main body 1 through the vicinity of the main balance weight 2 will also rotate with the rotation of the rotor assembly under the influence of the main balance weight 2. And during the rotation process, the noise reduction part can cut the high-speed rotating air flow, which can destroy the large air flow vortices formed by the rotating air flow and turn them into small air flow vortices, thereby reducing the noise intensity and thus reducing the overall noise intensity of the rotor assembly. Moreover, the cutting action of the noise reduction part on the rotating air flow can also divide the flow direction of the air flow and disperse the air flow, so that the air flow does not gather at the concave part of the main balance weight, thereby reducing the wind resistance of the main balance weight 2 and optimizing the rotation performance of the rotor assembly.

[0048] Optionally, the noise reduction part is constructed as ribs 3 protruding from the inner wall of the main balance weight 2, and the ribs 3 extend along the circumferential direction of the rotor main body 1 on the inner wall of the main balance weight 2.

[0049] Specifically, the ribs 3 extend along the circumferential direction of the rotor main body 1, and thus the whole ribs 3 are also in an arc shape. During rotation, the ribs 3 protruding from the inner wall of the main balance weight 2 can cut the air flow inside the main balance weight like a blade, disperse the air flow and reduce the scale of the air flow vortices.

[0050] Optionally, the number of the ribs 3 is one or more. When the number of the ribs 3 is multiple, the multiple ribs 3 are parallel to each other and are evenly and spacedly distributed in the axial direction of the rotor main body 1.

[0051] Specifically, the number of the ribs 3 can be set as required. For example, as shown in the attached drawings Figure 4With Figure 6 The settings shown in 3 or 4 or any other feasible quantity (indicating the quantity that the area of the inner wall of the main balance weight 2 can bear), multiple ribs 3 can strengthen the cutting effect on the rotating airflow, so that large airflow vortices can be broken into smaller airflow vortices, ensuring the effect of reducing airflow noise.

[0052] Preferably, the height range of the rib 3 protruding from the inner wall of the main balance weight 2 is 1 mm to 3 mm, and the preferred value is 2 mm. This is because if the protruding height is too high, deep dead corners or grooves will be formed at the root of the rib 3 or between two adjacent ribs 3 among multiple ribs 3, resulting in the formation of eddy currents in the airflow here, instead stimulating the generation of noise. The top structure of the rib 3 is an arc surface to reduce the obstruction to the airflow. The length of the rib 3 in the circumferential direction of the rotor body 1 is as large as possible to ensure the cutting effect on the airflow, that is, the length is numerically as close as possible to the width of the inner wall of the main balance weight 2 in this direction.

[0053] Furthermore, the rib 3 has a projection in the plane where the axis of the rotor body 1 is located, and the angle between the projection and the radial cross-section of the rotor body 1 is 0° to 15° (as shown by the α angle in the attached drawing Figure 5 .

[0054] Specifically, the inclination angle of the rib 3 can be set as required. As shown in the attached drawing Figures 4 to 7 , from the perspective shown in the attached drawing, the rib 3 can be set to be horizontal (i.e., the inclination angle is 0°), or can be set to have a certain non-zero inclination angle. In this embodiment, the inclination angle is not greater than 15°, and more preferably the inclination angle is not greater than 10°. If the inclination angle is too large, the rib 3 will lose the cutting effect on the airflow.

[0055] In addition, in addition to being able to cut the airflow, the inclined rib 3 can also generate a force on the airflow in the axial direction of the rotor assembly, guiding the airflow to flow towards the rotor body. Therefore, in order to achieve the guiding effect on the airflow, the specific inclination direction of the rib 3 needs to be determined according to the rotation direction of the rotor assembly.

[0056] Furthermore, the main balance weight 2 includes a connecting portion 21 and a protruding portion 22. The connecting portion 21 is configured to connect the end of the rotor body 1, the protruding portion 22 protrudes outward from the end of the rotor body 1 relative to the connecting portion 21, and the noise reduction portion is constructed on the inner wall of the protruding portion 22.

[0057] Specifically, as shown in the attached drawing Figure 1 Figure 3 With Figure 4As shown, the connecting part 21 of the main balance weight 2 is constructed as an annular shape and is fixed to the end of the rotor body 1 by bolts. The protruding part 22 of the main balance weight 2 protrudes outward from the end of the rotor body 1 relative to the connecting part 21. The protruding part 22 is integrally arc-shaped and is the main body of the main balance weight 2. The noise reduction part is constructed on the inner wall of the protruding part 22.

[0058] In addition, a secondary balance weight 4 is provided at the other end of the rotor body 1. The structure of the secondary balance weight 4 is similar to that of the main balance weight 2, except that the protruding structure of the secondary balance weight 4 is symmetrically located on both sides of the center of the rotor body 1 with respect to the position of the protruding part 22 of the main balance weight 2.

[0059] Embodiment 2

[0060] An embodiment of the present utility model provides a rotor assembly, which includes a rotor body 1 and a main balance weight 2; the main balance weight 2 is installed at one end of the rotor body 1, and a noise reduction part is constructed on the inner wall of the main balance weight 2; wherein, the noise reduction part is constructed to cut the air flow that flows axially along the rotor body 1 and rotates at the main balance weight 2 as the main balance weight 2 rotates, so as to reduce the size of the air flow vortex generated by the rotating air flow through cutting and reduce the air flow noise.

[0061] Specifically, as mentioned in the background art above, during the current R & D process, it is found that there is obvious noise during the operation of the rotor assembly and even the compressor. In addition to the noise inevitably caused by general mechanical vibration, there are other sources of this noise. Through analysis and testing, it is found that another part of the noise source is mainly the air flow at the rotor assembly, which is the noise caused by the air flow. Further testing shows that the noise generated by the air flow is mainly concentrated at the air flow input end of the rotor assembly, that is, the position where the main balance weight 2 is located. Combining with the general principle of air flow noise generation, it is judged that when the high-pressure gas enters the main balance weight 2 that rotates at a high speed with the rotor body 1, the air flow rotates together with the main balance weight 2 that rotates at a high speed, and eddy currents are formed here, thereby generating eddy current noise. Therefore, the present utility model optimizes the structure at the main balance weight 2 for the eddy current noise at the main balance weight 2 to solve this noise problem.

[0062] Specifically, the main body of the main balance weight 2 is usually designed to follow the shape and structure of the rotor, such as in the attached drawing Figure 1As shown, the main balance weight 2 is integrally arc-shaped, which is consistent with the outer contour shape of the rotor body 1 (the central angle corresponding to its arc is less than 180 degrees), and the arc is concentric with the rotor body 1. The noise reduction part is constructed on the inner wall of the main balance weight 2. When the rotor assembly rotates, the noise reduction part also rotates around the axis of the rotor body 1. The airflow transported to the rotor body 1 near the main balance weight 2 will also rotate with the rotation of the rotor assembly under the influence of the main balance weight 2. During the rotation process, the noise reduction part can cut the high-speed rotating airflow, destroy the large airflow vortices formed by the rotating airflow, and turn them into small airflow vortices, thereby reducing the noise intensity and further reducing the overall noise intensity of the rotor assembly. Moreover, the cutting effect of the noise reduction part on the rotating airflow can also divide the flow direction of the airflow, disperse the airflow, so that the airflow does not gather in the concave part of the main balance weight, thereby reducing the wind resistance of the main balance weight 2 and optimizing the rotation performance of the rotor assembly.

[0063] Optionally, the noise reduction part is constructed as ribs 3 protruding from the inner wall of the main balance weight 2, and the ribs 3 extend along the circumferential direction of the rotor body 1 on the inner wall of the main balance weight 2.

[0064] Specifically, the ribs 3 extend along the circumferential direction of the rotor body 1, and thus the ribs 3 are also integrally arc-shaped. During rotation, the ribs 3 protruding from the inner wall of the main balance weight 2 can cut the airflow inside the main balance weight like blades, disperse the airflow, and reduce the scale of the airflow vortices.

[0065] Optionally, the number of the ribs 3 is one or more. When the number of the ribs 3 is multiple, the multiple ribs 3 are parallel to each other and are evenly and spacedly distributed in the axial direction of the rotor body 1.

[0066] Specifically, the number of the ribs 3 can be set as required. For example, as shown in the attached drawings Figure 4 and Figure 6 3 or 4 or any other feasible number is set (indicating the number that the area of the inner wall of the main balance weight 2 can bear). The multiple ribs 3 can enhance the cutting effect on the rotating airflow, so that the large airflow vortices can be broken into smaller airflow vortices, ensuring the noise reduction effect on the airflow noise.

[0067] Preferably, the height of the ribs 3 protruding from the inner wall of the main balance weight 2 ranges from 1 mm to 3 mm, and the preferred value is 2 mm. This is because if the protruding height is too high, deep dead corners or grooves will be formed at the root of the ribs 3 or between two adjacent ribs 3 among the multiple ribs 3, resulting in the formation of eddy currents of the airflow here and instead generating noise. The top of the ribs 3 is constructed as an arc surface to reduce the obstruction to the airflow. The length of the ribs 3 in the circumferential direction of the rotor body 1 is as large as possible to ensure the cutting effect on the airflow, that is, the length is numerically as close as possible to the width of the inner wall of the main balance weight 2 in this direction.

[0068] Furthermore, the rib 3 has a projection in the plane where the axis of the rotor body 1 lies, and the angle between the projection and the radial cross-section of the rotor body 1 is 0° to 15° (as shown by the α angle in the attached drawing Figure 5 .

[0069] Specifically, the inclination angle of the rib 3 can be set as required. As shown in the attached drawing Figures 4 to 7 , from the perspective shown in the attached drawing, the rib 3 can be set to be horizontal (i.e., the inclination angle is 0°), or can be set to have a non-zero inclination angle of a certain size. In this embodiment, the inclination angle is not greater than 15°, and more preferably, the inclination angle is not greater than 10°. If the inclination angle is too large, the rib 3 will lose the cutting effect on the air flow.

[0070] In addition, in addition to being able to cut the air flow, the inclined surface of the inclined rib 3 can also generate a force on the air flow in the axial direction of the rotor assembly to guide the air flow towards the rotor body. Therefore, in order to achieve the guiding effect on the air flow, the specific inclination direction of the rib 3 needs to be determined according to the rotation direction of the rotor assembly.

[0071] Furthermore, the main balance weight 2 includes a connecting portion 21 and a protruding portion 22. The connecting portion 21 is configured to connect the end of the rotor body 1, and the protruding portion 22 protrudes outward from the end of the rotor body 1 relative to the connecting portion 21, and the noise reduction portion is constructed on the inner wall of the protruding portion 22.

[0072] Specifically, as shown in the attached drawing Figure 1 Figure 3 and Figure 4 , the connecting portion 21 of the main balance weight 2 is configured to be circular and is fixed to the end of the rotor body 1 by bolts. The protruding portion 22 of the main balance weight 2 protrudes outward from the end of the rotor body 1 relative to the connecting portion 21. The protruding portion 22 is integrally arc-shaped and is the main body of the main balance weight 2, and the noise reduction portion is constructed on the inner wall of the protruding portion 22.

[0073] In addition, a secondary balance weight 4 is provided at the other end of the rotor body 1. The structure of the secondary balance weight 4 is similar to that of the main balance weight 2, except that the protruding structure of the secondary balance weight 4 is symmetrically located on both sides of the center of the rotor body 1 with respect to the position of the protruding portion 22 of the main balance weight 2.

[0074] Furthermore, a plurality of flow channels 5 are constructed inside the rotor body 1, and the flow channels 5 extend from one end of the rotor body 1 to the other end of the rotor body 1; among them, at least one variable-diameter channel 51 is included in the plurality of flow channels 5, and the variable-diameter channel 51 is configured to include a plurality of channel segments with inconsistent inner diameter sizes.

[0075] Specifically, as shown in the attached drawing Figure 2 、 Figure 8 andFigure 9 As shown, the internal structure of the rotor main body 1 has a flow channel 5 for air flow. In this embodiment, the structure of the flow channel 5 is further designed, and at least one variable-diameter channel 51 is designed among the multiple flow channels 5. As the name implies, the inner diameter size of the variable-diameter channel 51 is variable, that is, the variable-diameter channel 51 includes multiple channel segments, and the inner diameter sizes of these multiple channel segments are not completely the same, there are differences in the inner diameter sizes, so that the overall inner diameter size of the variable-diameter channel 51 is not completely unified. Among them, the channel segment with a larger inner diameter relatively forms an expansion cavity with an increased volume, which can cause the air flow to diffuse when entering the expansion cavity, reducing the local air flow velocity. Thus, on the basis of noise reduction based on the rib 3, the noise generated when the air flow flows at a high speed can be reduced, thereby overall enhancing the noise reduction effect of the rotor assembly.

[0076] In addition, the flow channel 5 on the rotor main body 1 is the main oil supply channel for the refrigerating oil. The air flow discharged from the cylinder is discharged to the lower cavity of the motor after passing through the upper flange and the upper muffler. The air flow in the lower cavity of the motor is discharged to the upper cavity of the motor through the flow channel 5 on the rotor main body 1, and finally discharged outside the compressor through the exhaust pipe on the upper cover. And the air flow will carry the refrigerating oil during the process of being discharged outside the compressor. In this embodiment, at the expansion cavity constructed on the flow channel 5, due to the change in the air flow velocity, a pressure difference will be formed between the upper and lower cavities of the motor, so that the refrigerating oil will not be discharged to the upper cavity of the motor along with the air flow, thereby reducing the oil discharge rate of the compressor where the rotor assembly is located, maintaining the normal operation of the compressor and the normal sealing, lubrication and cooling of the compressor parts by the refrigerating oil, and ensuring that the performance of the compressor is not affected.

[0077] Optionally, as shown in the attached drawing Figure 11 As shown, the variable-diameter channel 51 includes two first channel segments 511 and a second channel segment 512 located between the two first channel segments 511, and the inner diameter of the second channel segment 512 is larger than that of the first channel segment 511.

[0078] In addition, according to the need for noise reduction, when it is necessary to enhance the noise reduction effect on a specific frequency of noise, referring to the attached drawing Figure 12 , the sizes of the first channel segment 511 and the second channel segment 512 can be designed specifically according to the following relational formula:

[0079] f = C / (2×3.14) × SQRT[S1 / (S2×H2×H2)] × 10 3 ;

[0080] where f is the target noise reduction frequency, C is the propagation speed of sound in the air, S1 is the radial cross-sectional area of the first channel segment 511, S2 is the radial cross-sectional area of the second channel segment 512, H2 is the axial length of the second channel segment 512, and SQRT represents taking the square root.

[0081] Further, a plurality of flow channels 5 are uniformly distributed circumferentially along the rotor body 1, including a plurality of variable-diameter channels 51 and a plurality of fixed-diameter channels 52. The fixed-diameter channels 52 are configured such that the inner diameter dimensions at any part in their axial directions are equal. Among them, the plurality of variable-diameter channels 51 and the plurality of fixed-diameter channels 52 are rotationally symmetrically distributed about the axis of the rotor body 1.

[0082] Specifically, the structures of the variable-diameter channels 51 and the fixed-diameter channels 52 are respectively as shown in the accompanying drawings Figure 11 and Figure 13 As shown, for the plurality of flow channels 5 of the rotor body 1, they can be completely composed of a corresponding number of variable-diameter channels 51, or can be composed of a combination of a plurality of variable-diameter channels 51 and a plurality of fixed-diameter channels 52. In this embodiment, preferably, a scheme of combining a plurality of variable-diameter channels 51 and a plurality of fixed-diameter channels 52 to form a plurality of flow channels 5 is adopted. As shown in the accompanying drawings Figures 8 to 10 As shown, on the basis of taking into account the noise reduction effect, this scheme has a better effect of reducing the oiling rate of the compressor. In addition, referring to the accompanying drawings, the specific quantity ratio of the variable-diameter channels 51 and the fixed-diameter channels 52 and their layout manners can be set as needed. The layout manner preferably adopts a rotationally symmetric layout.

[0083] Embodiment 3

[0084] An embodiment of the present utility model provides a compressor, which includes the rotor assembly of the above embodiment, and thus has all the technical effects possessed by it.

[0085] In the description of the present utility model, it should be understood that the orientation or positional relationships indicated by the terms "upper", "lower", "bottom", "top", "front", "rear", "inner", "outer", "left", "right", etc. are based on the orientation or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present utility model.

[0086] Although the present utility model is described herein with reference to specific embodiments, it should be understood that these embodiments are only examples of the principles and applications of the present utility model. Therefore, it should be understood that many modifications can be made to the exemplary embodiments, and other arrangements can be designed, as long as they do not deviate from the spirit and scope of the present utility model defined by the appended claims. It should be understood that different dependent claims and the features described herein can be combined in a manner different from that described in the original claims. It should also be understood that the features described in connection with a single embodiment can be used in other described embodiments.

Claims

1. A rotor assembly, characterized in that, Comprising: A rotor body; And A main balance weight, which is installed at one end of the rotor body, and a noise reduction portion is constructed on the inner wall of the main balance weight; Wherein, the noise reduction portion is configured to cut the airflow that flows axially along the rotor body and generates rotation at the main balance weight as the main balance weight rotates, so as to reduce the size of the airflow vortex generated by the rotating airflow through cutting and reduce the airflow noise.

2. The rotor assembly according to claim 1, wherein, The noise reduction portion is configured as ribs protruding from the inner wall of the main balance weight, and the ribs extend along the circumferential direction of the rotor body on the inner wall of the main balance weight.

3. The rotor assembly according to claim 2, wherein The number of the ribs is one or more. When the number of the ribs is multiple, the multiple ribs are parallel to each other and are evenly and spacedly distributed in the axial direction of the rotor body.

4. The rotor assembly according to claim 2, wherein The height of the ribs protruding from the inner wall of the main balance weight ranges from 1 mm to 3 mm.

5. The rotor assembly according to claim 2, wherein, The ribs have a projection in the plane where the axis of the rotor body is located, and the angle between the projection and the radial cross-section of the rotor body is 0° to 15°.

6. The rotor assembly according to claim 1, wherein, The main balance weight includes a connecting portion and a protruding portion. The connecting portion is configured to connect the end of the rotor body, and the protruding portion protrudes outward from the end of the rotor body relative to the connecting portion. The noise reduction portion is constructed on the inner wall of the protruding portion.

7. The rotor assembly according to claim 1, characterized in that, A plurality of flow channels are constructed inside the rotor body, and the flow channels extend from one end of the rotor body to the other end of the rotor body; Wherein, at least one variable-diameter channel is included in the plurality of flow channels, and the variable-diameter channel is configured to include a plurality of channel segments with inconsistent inner diameter sizes.

8. The rotor assembly according to claim 7, wherein The variable-diameter channel includes two first channel segments and one second channel segment located between the two first channel segments, and the inner diameter of the second channel segment is larger than that of the first channel segment.

9. The rotor assembly according to claim 8, wherein, The sizes of the first channel segment and the second channel segment satisfy the following relational formula: f = C / (2 × 3.14) × SQRT[S1 / (S2 × H2 × H2)] × 10 3 ; Wherein, f is the target sound attenuation frequency, C is the propagation speed of sound in the air, S1 is the radial cross-sectional area of the first channel segment, S2 is the radial cross-sectional area of the second channel segment, H2 is the axial length of the second channel segment, and SQRT represents taking the square root.

10. The rotor assembly according to any one of claims 7 to 9, characterized in that, The plurality of flow channels are evenly distributed along the circumferential direction of the rotor body, including a plurality of variable-diameter channels and a plurality of fixed-diameter channels. The fixed-diameter channels are configured such that the inner diameter sizes at any part in the axial direction are equal; Wherein, the plurality of variable-diameter channels and the plurality of fixed-diameter channels are rotationally symmetrically distributed about the axis of the rotor body.

11. A compressor, characterized in that, Including the rotor assembly according to any one of claims 1 to 10.

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