Compressor rotor structure, compressor and heat pump system

Abstract

The application discloses a compressor rotor structure, a compressor and a heat pump system. The compressor rotor structure comprises a rotor core and a counterweight part. The rotor core comprises a plurality of rotor laminations, the plurality of rotor laminations are sequentially stacked along the axial direction of the rotor core, the rotor core has a boundary surface perpendicular to the axial direction of the rotor core, the boundary surface separates the plurality of rotor laminations into a first main body part and a second main body part, the first main body part is provided with a plurality of first through holes extending along the axial direction of the rotor core, and the second main body part is provided with a plurality of second through holes extending along the axial direction of the rotor core; and the counterweight part is at least partially arranged in at least one first through hole of the first main body part and / or at least one second through hole of the second main body part. The application can solve the problems that the balance block mass at the upper and lower ends of the motor rotor is large and the manufacturing cost is high in the prior art.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and more specifically, to a compressor rotor structure, a compressor, and a heat pump system. Background Technology

[0002] Rotary compressors employ a crankshaft with an eccentric structure. A piston is mounted on the eccentric portion of the crankshaft, and the piston rotates with the crankshaft under the drive of a motor, thereby compressing the refrigerant gas. Because the center of mass of the eccentric portion of the crankshaft and the piston is unbalanced with the center of rotation of the crankshaft, rotational inertia and torque are generated during the operation of the compressor.

[0003] Existing rotary compressors typically have primary and secondary balance blocks at the top and bottom of the motor rotor to balance inertial forces and torques. However, the existing balance blocks at the top and bottom of the motor rotor are relatively large, which not only affects the compressor's input performance, requiring the compressor to consume more energy to drive the shaft system, but also generates a large unbalanced centrifugal force during compressor operation, leading to increased vibration of the crankshaft in the normal direction. In addition, the manufacturing cost of the large balance blocks is high. Utility Model Content

[0004] The main objective of this application is to provide a compressor rotor structure, a compressor, and a heat pump system to solve the problem of large mass and high manufacturing cost of the balance blocks at the upper and lower ends of the motor rotor in the prior art.

[0005] According to one aspect of this application, a compressor rotor structure is provided, comprising: The rotor core includes multiple rotor laminations, which are stacked sequentially along the axial direction of the rotor core. The rotor core has an interface perpendicular to its own axial direction, which divides the multiple rotor laminations into a first main body and a second main body. The first main body is provided with multiple first through holes extending along the axial direction of the rotor core, and the second main body is provided with multiple second through holes extending along the axial direction of the rotor core. The counterweight is at least partially disposed within at least one first through hole of the first main body and / or at least one second through hole of the second main body.

[0006] Furthermore, the rotor core has a split surface parallel to its own axis. In this configuration, a plurality of first through holes are spaced apart circumferentially along the rotor core, and the split surface extends radially along the rotor core to the space between two first through holes. The first through holes on either side of the split surface that are not equipped with the counterweight are asymmetrically arranged with respect to the split surface; and / or, Multiple second through holes are spaced apart circumferentially along the rotor core. Along the radial direction of the rotor core, the split surface can extend to the space between two second through holes. The second through holes on both sides of the split surface that are not provided with the counterweight are asymmetrically arranged with respect to the split surface.

[0007] Furthermore, each of the rotor laminations is provided with a plurality of lamination holes. After the plurality of rotor laminations are stacked, the lamination holes on each rotor lamination are interconnected to form the first through hole and the second through hole. The geometric centers of the plurality of lamination holes on each rotor lamination are located on the same circle.

[0008] Furthermore, the number N of the punch holes satisfies the following relationship: 2 ≤ N < 12.

[0009] Furthermore, in two adjacent lamination holes, the line connecting the geometric center of one lamination hole to the geometric center of the rotor core is the first line, and the line connecting the geometric center of the other lamination hole to the geometric center of the rotor core is the second line. The angle θ between the first line and the second line satisfies the relationship θ = 360° / N with respect to the number of lamination holes N.

[0010] Furthermore, the rotor core is provided with a magnet slot, which is provided through the rotor core along the axial direction. Along the radial direction of the rotor core, the minimum distance D between the first through hole or the second through hole and the magnet slot satisfies the relationship: D≥2mm.

[0011] Furthermore, the rotor core is provided with a first rotor end plate and a second rotor end plate. The first rotor end plate is located on the side of the first main body that is away from the second main body, and the second rotor end plate is located on the side of the second main body that is away from the first main body. The counterweight part also includes a counterweight block located on the first rotor end plate and / or the second rotor end plate.

[0012] Furthermore, within the projection along the axis of the rotor core, the projection of the first through hole includes at least one of a circle, an oblong shape, and an ellipse; and / or, Within the projection along the axis of the rotor core, the projection of the second through hole includes at least one of a circle, an oblong shape, and an ellipse; and / or, The counterweight and the rotor core are integrally formed.

[0013] Furthermore, the rotor laminations comprise silicon steel sheets.

[0014] On the other hand, this application also provides a compressor, which includes the above-described compressor rotor structure, and the compressor includes a rotary compressor.

[0015] In another aspect, this application also provides a heat pump system, which includes the compressor described above.

[0016] Compared to the existing technology that arranges main and auxiliary balance blocks at the upper and lower ends of the motor rotor to balance inertial force and torque, this application arranges the counterweight part at least partially in the first through hole of the first main body and / or the second through hole of the second main body. In this way, it can effectively balance the rotational inertial force and torque generated when the compressor is running, reducing the mass and volume of the balance block and lowering the manufacturing cost. Attached Figure Description

[0017] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings: Figure 1 This is a schematic diagram of the rotor core disclosed in the embodiments of this application from a first-view perspective; Figure 2 This is a schematic diagram of the rotor core disclosed in the embodiments of this application from a second perspective. Figure 3 This is a side view of the rotor core disclosed in an embodiment of this application; Figure 4 This is a top view of the rotor core disclosed in the embodiments of this application; Figure 5 The embodiments disclosed in this application Figure 4 Sectional view of AA; Figure 6 The embodiments disclosed in this application Figure 4 BB section view; Figure 7 The embodiments disclosed in this application Figure 4 CC section view.

[0018] The above figures include the following reference numerals: 10. Rotor core; 101. Interface; 102. Mid-section; 11. Rotor lamination; 12. First main body; 13. Second main body; 14. Lamination hole; 15. First connecting line; 16. Second connecting line; 17. First through hole; 18. Second through hole; 20. Counterweight; 21. Counterweight block; 30. Magnet slot; 40. First rotor end plate; 50. Second rotor end plate. Detailed Implementation

[0019] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. This application will now be described in detail with reference to the accompanying drawings and embodiments.

[0020] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0021] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0022] As mentioned in the background section, existing rotary compressors typically employ primary and secondary balance blocks at both ends of the motor rotor to ensure force and torque balance during crankshaft rotation. However, the existing balance blocks at both ends of the motor rotor have a large mass, which not only affects the compressor's input performance, requiring more energy to drive the shaft system, but also generates significant unbalanced centrifugal force during compressor operation, leading to increased crankshaft vibration in the normal direction. Furthermore, the large mass of the balance blocks increases manufacturing costs. Therefore, the inventors of this application have designed a new compressor rotor structure that at least solves the problems of large mass and high manufacturing costs associated with the balance blocks at both ends of the motor rotor in existing technologies. The compressor rotor structure of this application will be described in detail below with reference to the accompanying drawings.

[0023] See Figures 1 to 2 as well as Figures 5 to 7 As shown, according to an embodiment of this application, a compressor rotor structure is provided, which includes a rotor core 10 and a counterweight 20.

[0024] The rotor core 10 includes a plurality of rotor laminations 11, which are stacked sequentially along the axial direction of the rotor core 10. The rotor core 10 has a dividing interface 101 perpendicular to its own axial direction, which divides the plurality of rotor laminations 11 into a first main body 12 and a second main body 13. The first main body 12 is provided with a plurality of first through holes 17 extending along the axial direction of the rotor core 10, and the second main body 13 is provided with a plurality of second through holes 18 extending along the axial direction of the rotor core 10. The counterweight 20 is at least partially disposed in at least one first through hole 17 of the first main body 12 and / or at least one second through hole 18 of the second main body 13. It is understood that in this application, the counterweight 20 may be at least partially disposed within the first through hole 17 of the first main body 12, or at least partially disposed within the second through hole 18 of the second main body 13, or at least partially disposed within the first through hole 17 of the first main body 12 and the second through hole 18 of the second main body 13.

[0025] When the compressor rotor structure of this application is installed on a compressor, the compressor rotor structure is fitted onto the crankshaft to drive the crankshaft to rotate. During the crankshaft rotation, due to the deviation between the crankshaft eccentricity and the center of mass of the piston and the crankshaft rotation center, the compressor generates rotational inertial force and torque during operation. In order to balance this rotational inertial force and torque, this application divides multiple rotor laminations 11 into a first main body 12 and a second main body 13 through the interface 101, and makes the counterweight 20 at least partially disposed in the first through hole 17 of the first main body 12 and / or the second through hole 18 of the second main body 13. In this way, without relying on the large mass of the balance block in the prior art, the rotational inertial force and torque can be balanced simply by flexibly adjusting the distribution position of the counterweight 20 in the first main body 12 and the second main body 13, effectively reducing the mass of the additional balance block.

[0026] Specifically, when the inertial force from the crankshaft eccentricity is more significant in a certain radial direction, a counterweight 20 can be provided in the first through hole 17 of the first main body 12 and / or the second through hole 18 of the second main body 13 on the corresponding side. The counter-centrifugal force generated by the counterweight 20 rotating synchronously with the rotor can counteract the inertial force in the aforementioned radial direction. This counterweight design avoids the mass redundancy caused by the traditional large-mass balance block being concentrated at both ends of the rotor core 10, thereby reducing the overall rotational inertia of the rotor core 10. When the compressor drive shaft system is running, it does not need to overcome an additional large mass load, the input performance is significantly improved, and energy consumption is reduced accordingly. At the same time, compared with the unbalanced centrifugal force easily caused by the large mass and concentrated distribution of traditional balance blocks, the counterweight 20 in this application adapts to the inertial force through the distribution at different positions, which can make the mass distribution during rotor rotation more uniform. The vibration of the crankshaft in the normal direction is driven by the unbalanced centrifugal force. After the centrifugal force is reduced, the impact load on the crankshaft is reduced, and the vibration problem is naturally alleviated. In addition, traditional large-mass balance weights require more raw materials and have higher manufacturing costs. This application reduces the mass of the balance weight and further reduces manufacturing costs by at least partially placing the counterweight part 20 in the first through hole 17 of the first main body part 12 and / or the second through hole 18 of the second main body part 13.

[0027] In other words, compared with the existing technology of arranging main and auxiliary balance blocks at the upper and lower ends of the motor rotor to balance inertial force and torque, this application arranges the counterweight part 20 at least partially in the first through hole 17 of the first main body part 12 and / or the second through hole 18 of the second main body part 13. In this way, it can effectively balance the rotational inertial force and torque generated when the compressor is running, reducing the mass and volume of the balance block and lowering the manufacturing cost.

[0028] Further, see Figure 4 As shown, the rotor core 10 in this embodiment has a split surface 102 parallel to its own axis; wherein, a plurality of first through holes 17 are arranged at intervals along the circumference of the rotor core 10, and along the radial direction of the rotor core 10, the split surface 102 can extend to the space between two first through holes 17, and the first through holes 17 without counterweights 20 located on both sides of the split surface 102 are asymmetrically arranged with respect to the split surface 102.

[0029] Specifically, in this embodiment, the multiple first through holes 17 are spaced circumferentially, which provides uniform installation space for the counterweight 20, avoiding excessive local concentration that could lead to rotor mass imbalance. It also accommodates the inertial force requirements at different radial positions during rotor rotation, laying the foundation for precise counterweight adjustment. Simultaneously, this embodiment asymmetrically arranges the first through holes 17 without counterweights 20 on both sides of the split plane 102, adapting to the asymmetrically distributed rotational inertial force and torque during compressor operation. When the crankshaft exhibits a more pronounced inertial force in a certain direction due to its structural characteristics, the counterweight 20 can be arranged within the first through holes 17, making the remaining first through holes 17 without counterweights 20 asymmetrically arranged. This precisely matches the balance requirements in that direction, achieving a better balance effect without adding extra mass to the balance block, further reducing the overall rotor moment of inertia and decreasing the load on the drive shaft system.

[0030] Further, see Figure 4 As shown, the rotor core 10 in this embodiment has a split surface 102 parallel to its own axis; wherein, a plurality of second through holes 18 are arranged at intervals along the circumference of the rotor core 10, and along the radial direction of the rotor core 10, the split surface 102 can extend to the space between two second through holes 18, and the second through holes 18 without counterweights 20 located on both sides of the split surface 102 are asymmetrically arranged with respect to the split surface 102.

[0031] Specifically, in this embodiment, the multiple second through holes 18 provide a uniformly distributed installation space for the counterweight 20, preventing excessive concentration of the counterweight 20 in certain areas and thus avoiding rotor mass imbalance. Simultaneously, it adapts to the inertial force requirements at different radial positions during rotor rotation, laying the foundation for subsequent precise counterweight adjustments. Furthermore, by asymmetrically arranging the second through holes 18 without counterweight 20 on both sides of the split plane 102, this embodiment can adapt to the asymmetrically distributed rotational inertial force and torque during compressor operation. When the crankshaft exhibits a more pronounced inertial force in a certain direction due to its structural characteristics, a counterweight 20 can be arranged within the second through holes 18, making the remaining second through holes 18 without counterweight 20 asymmetrically arranged. This precisely matches the balance requirements in that direction, achieving a better balance effect without adding additional counterweight mass, further reducing the overall rotor moment of inertia and decreasing the load on the drive shaft system.

[0032] Further, see Figure 4 As shown, each rotor lamination 11 in this embodiment is provided with a plurality of lamination holes 14. After the plurality of rotor laminations 11 are stacked, the lamination holes 14 on each rotor lamination 11 are interconnected to form a first through hole 17 and a second through hole 18. The geometric centers of the plurality of lamination holes 14 on each rotor lamination 11 are located on the same circle.

[0033] Specifically, in this embodiment, the geometric centers of the multiple lamination holes 14 are designed on the same circle. This ensures that when the rotor lamination 11 is subjected to external force, the stress is evenly distributed around each lamination hole 14, preventing deformation or damage in localized areas due to excessive stress concentration. This effectively improves the overall structural stability and durability of the lamination. Simultaneously, the fact that the geometric centers of the multiple lamination holes 14 are located on the same circle facilitates the lamination manufacturing process. During drilling, positioning can be performed based on the same circular trajectory, reducing positioning errors, ensuring the positional accuracy of each lamination hole 14, and lowering processing difficulty and cost.

[0034] Furthermore, in this embodiment, the number N of the punch holes 14 satisfies the relationship: 2 ≤ N < 12. For example, N can be set to 2, 3, 4, 5, 6, 7, 8, 9, 10, or 11.

[0035] Specifically, setting N to a lower limit of 2 provides a basic selection of hole positions for the balance adjustment of the rotor core 10. At least two lamination holes 14 can form counterweight mounting points in different orientations around the rotor core 10, avoiding the problem of insufficient hole positions preventing the counterweight from offsetting simple unbalanced forces, thus ensuring the basic balance requirements are met. The upper limit of N being less than 12 avoids excessive weakening of the rotor core 10 structure due to too many lamination holes 14, preventing a decrease in the overall strength of the rotor core 10 due to dense hole positions, and the risk of deformation or cracking caused by stress concentration during high-speed rotation. It also reduces the production complexity and cost increase caused by excessive hole machining.

[0036] Further, see Figure 4 As shown, in this embodiment, among two adjacent lamination holes 14, the line connecting the geometric center of one lamination hole 14 to the geometric center of the rotor core 10 is the first connecting line 15, and the line connecting the geometric center of the other lamination hole 14 to the geometric center of the rotor core 10 is the second connecting line 16. The angle θ between the first connecting line 15 and the second connecting line 16 satisfies the relationship θ = 360° / N with respect to the number of lamination holes N. For example, when N is 2, θ is 180°; when N is 3, θ is 120°; when N is 4, θ is 90°; when N is 5, θ is 72°; when N is 6, θ is 60°; when N is 7, θ is approximately 51.4°; when N is 8, θ is 45°; when N is 9, θ is 40°; when N is 10, θ is 36°; and when N is 11, θ is approximately 32.7°.

[0037] Specifically, this embodiment ensures that θ satisfies the relationship θ = 360° / N, enabling a uniform and regular spacing distribution of multiple lamination holes 14 around the rotor core 10. This avoids machining deviations in the position of the lamination holes 14 due to disordered hole distribution, improving the accuracy and consistency of the lamination hole positions. Simultaneously, this regular angular distribution allows the lamination holes 14 without counterweights 20 to be evenly distributed on the rotor core 10, preventing the concentration of lamination holes 14 from causing a decrease in local structural strength and ensuring the structural stability of the rotor during high-speed rotation.

[0038] Further, see Figures 5 to 6 As shown, in this embodiment, the rotor core 10 is provided with a magnet slot 30. The magnet slot 30 is provided through the rotor core 10 along the axial direction. Along the radial direction of the rotor core 10, the minimum distance D between the first through hole 17 or the second through hole 18 and the magnet slot 30 satisfies the relationship: D≥2mm. For example, D can be set to 2mm, 2.1mm, 2.2mm, 2.3mm, 2.4mm, 2.5mm, 2.6mm, 2.7mm, 2.8mm, 2.9mm, 3mm, etc.

[0039] Specifically, the magnet slot 30 provides an installation channel for the permanent magnet. In this embodiment, by ensuring that the minimum distance D between the first through hole 17 or the second through hole 18 and the magnet slot 30 satisfies the relationship: D≥2mm, sufficient iron core solid area can be reserved between the first through hole 17 or the second through hole 18 and the magnet slot 30. This avoids excessively weak local structures caused by the spacing between the first through hole 17 or the second through hole 18 and the magnet slot 30 being too close, thereby effectively resisting the centrifugal stress generated during high-speed rotor rotation and preventing cracking or deformation caused by stress concentration at the edges of the first through hole 17 or the second through hole 18 and the magnet slot 30. When D is less than 2mm, the iron core solid area between the first through hole 17 or the second through hole 18 and the magnet slot 30 will be significantly reduced, causing this local structure to become abnormally weak. Under the action of centrifugal stress generated by high-speed rotor rotation, stress concentration is very likely to occur in the weak area, which will then cause cracking and deformation at the edges of the first through hole 17 or the second through hole 18 or the magnet slot 30, seriously damaging the overall structural integrity of the rotor core 10 and shortening the service life of the compressor rotor structure.

[0040] Further, see Figures 5 to 6 As shown, in this embodiment, the rotor core 10 is provided with a first rotor end plate 40 and a second rotor end plate 50. The first rotor end plate 40 is located on the side of the first main body 12 away from the second main body 13, and the second rotor end plate 50 is located on the side of the second main body 13 away from the first main body 12. The counterweight part 20 also includes a counterweight block 21 located on the first rotor end plate 40 and / or the second rotor end plate 50.

[0041] Specifically, the first rotor end plate 40 and the second rotor end plate 50 can provide axial restraint and protection for the stacked rotor laminations 11, preventing axial displacement and edge wear of the laminations during high-speed rotation or assembly, while also enhancing the overall axial structural strength of the rotor core 10. Meanwhile, the counterweight 20 in this embodiment includes a counterweight block 21 located on the first rotor end plate 40 and / or the second rotor end plate 50. This counterweight block 21 can form a "built-in + external" dual counterweight combination with the counterweight inside the lamination hole 14. When the counterweight inside the lamination hole 14 is insufficient to completely offset the unbalanced force during rotor operation, additional counterweight blocks 21 can be added to the end plates for supplementary adjustment, further improving balance accuracy and adapting to more complex unbalanced operating conditions.

[0042] Further, see Figure 4 As shown, within the projection along the axis of the rotor core 10, the projection of the first through hole 17 in this embodiment includes at least one of a circle, a waist shape, and an ellipse. That is to say, in this embodiment, the projection of the first through hole 17 can be a single circle, a waist shape, or an ellipse, or it can be a combination of two shapes, such as a circle and a waist shape, a circle and an ellipse, a waist shape and an ellipse, or it can be a combination of three shapes.

[0043] Specifically, the various shapes of the first through hole 17 can accommodate the installation requirements of different types and sizes of counterweight parts 20. Meanwhile, this embodiment simplifies the structure and facilitates manufacturing by making the projection of the first through hole 17 include at least one of circular, oblong, and elliptical shapes.

[0044] Further, see Figure 4 As shown, within the projection along the axis of the rotor core 10, the projection of the second through hole 18 includes at least one of a circle, a waist shape, and an ellipse. That is to say, in this embodiment, the projection of the second through hole 18 can be a single circle, a waist shape, or an ellipse, or it can be a combination of two shapes, such as a circle and a waist shape, a circle and an ellipse, a waist shape and an ellipse, or it can be a combination of three shapes.

[0045] Specifically, the various shapes of the second through hole 18 can accommodate the installation requirements of different types and sizes of counterweight parts 20. Meanwhile, this embodiment simplifies the structure and facilitates manufacturing by allowing the projection of the second through hole 18 to include at least one of circular, oblong, and elliptical shapes.

[0046] Furthermore, in this embodiment, the counterweight 20 and the rotor core 10 are integrally formed. This allows the counterweight 20 and the rotor core 10 to form a stable, integrated structure, avoiding the problems of loosening or displacement of the counterweight 20 due to installation gaps or long-term vibration, which are common in traditional split designs. At the same time, it eliminates the need for separate processing, transportation, and assembly of the counterweight 20, reducing the number of parts, simplifying the production process, and lowering the risk of positioning deviations during assembly.

[0047] Furthermore, the rotor lamination 11 in this embodiment comprises silicon steel sheets. Specifically, silicon steel sheets themselves possess excellent magnetic permeability, which can reduce hysteresis losses and eddy current losses of the rotor core 10 during motor operation, reduce ineffective conversion of electrical energy into heat energy, improve the energy conversion efficiency of the motor, and thus reduce the overall energy consumption of the compressor. At the same time, silicon steel sheets possess a certain mechanical strength, enabling them to form a structurally stable rotor core 10 body, better supporting the weight of the counterweight 20 and the centrifugal force generated by high-speed rotation.

[0048] On the other hand, this application also provides a compressor that includes the aforementioned compressor rotor structure. Therefore, this compressor incorporates all the technical effects of the aforementioned compressor rotor structure. Since the technical effects of the compressor rotor structure have already been described in detail above, they will not be repeated here.

[0049] Specifically, the compressor in this embodiment includes a rotary compressor.

[0050] Furthermore, this application also provides a heat pump system that includes the aforementioned compressor. Therefore, this heat pump system encompasses all the technical effects of the compressor described above. Since the technical effects of the compressor have already been described in detail above, they will not be repeated here.

[0051] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0052] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0053] The above are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A compressor rotor structure, characterized in that, include: The rotor core (10) includes a plurality of rotor laminations (11), which are stacked sequentially along the axial direction of the rotor core (10). The rotor core (10) has an interface (101) perpendicular to its own axial direction, which divides the plurality of rotor laminations (11) into a first main body (12) and a second main body (13). The first main body (12) is provided with a plurality of first through holes (17) extending along the axial direction of the rotor core (10), and the second main body (13) is provided with a plurality of second through holes (18) extending along the axial direction of the rotor core (10). The counterweight (20) is at least partially disposed within at least one first through hole (17) of the first main body (12) and / or within at least one second through hole (18) of the second main body (13).

2. The compressor rotor structure according to claim 1, characterized in that, The rotor core (10) has a split surface (102) parallel to its own axis. In this configuration, a plurality of first through holes (17) are spaced apart circumferentially along the rotor core (10), and the split surface (102) extends radially between two of the first through holes (17). The first through holes (17) on both sides of the split surface (102) that are not provided with the counterweight (20) are asymmetrically arranged with respect to the split surface (102); and / or, Multiple second through holes (18) are spaced apart circumferentially along the rotor core (10). Along the radial direction of the rotor core (10), the split surface (102) can extend between two second through holes (18). The second through holes (18) located on both sides of the split surface (102) without the counterweight (20) are asymmetrically arranged with respect to the split surface (102).

3. The compressor rotor structure according to claim 1, characterized in that, Each rotor lamination (11) is provided with a plurality of lamination holes (14). After the plurality of rotor laminations (11) are stacked, the lamination holes (14) on each rotor lamination (11) are interconnected to form the first through hole (17) and the second through hole (18). The geometric centers of the plurality of lamination holes (14) on each of the rotor laminations (11) are located on the same circle.

4. The compressor rotor structure according to claim 3, characterized in that, The number N of the punch holes (14) satisfies the following relationship: 2 ≤ N < 12.

5. The compressor rotor structure according to claim 4, characterized in that, In two adjacent lamination holes (14), the line connecting the geometric center of one lamination hole (14) with the geometric center of the rotor core (10) is the first line (15), and the line connecting the geometric center of the other lamination hole (14) with the geometric center of the rotor core (10) is the second line (16). The angle θ between the first line (15) and the second line (16) satisfies the relationship θ = 360° / N with the number of lamination holes (14).

6. The compressor rotor structure according to claim 1, characterized in that, The rotor core (10) is provided with a magnet slot (30), which is provided through the rotor core (10) along the axial direction. The minimum distance D between the first through hole (17) or the second through hole (18) and the magnet slot (30) along the radial direction of the rotor core (10) satisfies the relationship: D≥2mm.

7. The compressor rotor structure according to claim 1, characterized in that, The rotor core (10) is provided with a first rotor end plate (40) and a second rotor end plate (50). The first rotor end plate (40) is located on the side of the first main body (12) away from the second main body (13), and the second rotor end plate (50) is located on the side of the second main body (13) away from the first main body (12). The counterweight (20) also includes a counterweight block (21) located on the first rotor end plate (40) and / or the second rotor end plate (50).

8. The compressor rotor structure according to any one of claims 1 to 7, characterized in that, Within the projection along the axial direction of the rotor core (10), the projection of the first through hole (17) includes at least one of a circle, a waist shape, and an ellipse; and / or, Within the projection along the axial direction of the rotor core (10), the projection of the second through hole (18) includes at least one of a circle, a waist shape, and an ellipse; and / or, The counterweight (20) and the rotor core (10) are integrally formed.

9. The compressor rotor structure according to any one of claims 1 to 7, characterized in that, The rotor laminations (11) comprise silicon steel sheets.

10. A compressor, characterized in that, The compressor includes the compressor rotor structure according to any one of claims 1 to 9, and the compressor includes a rotary compressor.

11. A heat pump system, characterized in that, The heat pump system includes the compressor of claim 10.

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